CN213575487U

CN213575487U - Gear shifting device with buffer damping function, and centralized clutch device, parking device, differential mechanism, braking system, safety device, transmission system, module and machine comprising gear shifting device

Info

Publication number: CN213575487U
Application number: CN201922196691.8U
Authority: CN
Inventors: 王佩英
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-12-10
Filing date: 2019-12-10
Publication date: 2021-06-29
Anticipated expiration: 2029-12-10

Abstract

The utility model provides a gearshift with buffering damping function and contain device's concentrated clutch, parking device, differential mechanism, braking system, safety device, transmission system, module and machine, especially be used for the gearshift with buffering damping function of transmission technical field, including damping buffer, and/or clutch, and/or actuating device, and/or adjusting device, and/or detector device, gearshift with buffering damping function passes through damping buffer, and/or clutch, and/or actuating device, and/or adjusting device, and/or the different combinations of detector device and connection in order to realize the joint and the separation function of multiple power or motion, compare with traditional gearshift, the utility model discloses have simple structure, the reliability is high, the utility model discloses have simple structure, high, The gear shifting device has the advantages of good controllability, low control difficulty, high modularization, good universality, strong expandability, no power interruption in the gear shifting process, low manufacturing cost and the like.

Description

Gear shifting device with buffer damping function, and centralized clutch device, parking device, differential mechanism, braking system, safety device, transmission system, module and machine comprising gear shifting device

Technical Field

The utility model relates to a gearshift GD, in particular to gearshift GD with buffering damping function belongs to transmission technical field.

Background

In most cases, the power output characteristics of the power source of the machine do not match the power characteristics required by the actuator, and therefore, a special transmission system is often required to drive the actuator of the machine after the power of the power source is changed in speed or is subjected to differential speed. In addition, because the actual working conditions are complex, in many cases, a transmission system is often required to be provided with a plurality of power transmission paths, namely a plurality of gears, so as to meet the requirements of the machine (M) on various aspects such as dynamic property, economy and the like. In order to smoothly realize the switching of the transmission system among a plurality of gears and ensure that the power among the gears does not interfere with each other, a specific gear shifting device is required to be arranged.

The shifting devices are generally arranged between the power source and the actuator of the machine, between the driving shaft and the driven shaft of the machine or between the moving part and the frame of the machine. The currently common shifting devices have: one-way clutches (or overrunning clutches), centrifugal clutches, hydraulic or motor-driven friction plate clutches, electromagnetic clutches, magnetic powder clutches, ratchet clutches, dog clutches, synchronizers, and the like. The roller type one-way clutch has simple structure, but most of the roller type one-way clutch is in point and line contact, so the roller type one-way clutch has small bearing capacity, large shifting impact force, poor reliability and short service life; the ratchet wheel and the pawl of the ratchet clutch are in line and surface contact, so that the bearing capacity is high, the controllability is high, the gear shifting impact force is high, the reliability of parts is low, the service life is short, when the ratchet clutch is used as an overrunning clutch, the running noise is high in the overrunning state, the parts are seriously abraded, and the problem of inevitable power interruption exists in the gear shifting process; the centrifugal clutch has a simple structure, is easily influenced by rotating speed, has poor controllability, small bearing capacity and large gear shifting impact; the planetary overrunning clutch has larger bearing capacity, but when in an overrunning state, the incomplete gear and other gear mechanisms are easy to gear, the noise is larger, the reliability is low, and the gear shifting impact is larger; the friction plate type clutch driven by the hydraulic or motor has high reliability, smooth gear shifting, almost no gear shifting power interruption, high sliding friction control and high gear shifting comfort easily in the gear shifting process, but the hydraulic or motor driven control system is complex, the overall design and manufacturing cost of parts is high, and the friction plate is seriously abraded; the electromagnetic clutch and the magnetic powder clutch have simple structures, but have higher overall cost, lower bearing capacity, poor heat dissipation effect, lower working rotating speed and lower overall reliability than a hydraulic or motor-driven friction plate clutch; the synchronizer is simple in structure and low in cost, but the manufacturing process of parts is complex, the reliability is low, and the problems of power interruption, gear shifting impact and the like inevitably exist in the gear shifting process. Therefore, the development of the gear shifting device with simple structure, higher reliability, good controllability, low control difficulty and low manufacturing cost becomes a key technology developed in the current transmission field.

Disclosure of Invention

The utility model aims at providing a simple structure, reliability are higher, the nature controlled is good, the control degree of difficulty is low, the commonality is high, scalability is strong, the process of shifting is unpowered to be interrupted, low in manufacturing cost's gearshift GD that has the damping function, and with a concentrated clutch, parking device, differential mechanism, braking system, safety device, transmission system, module and a machine that is used for the transmission field on the basis of gearshift GD that has the damping function.

The utility model discloses a following scheme realizes:

the utility model provides a gearshift GD with buffering damping function, including buffering damping device DM, and/or clutch CM, and/or adjusting device RM, and/or actuating device AM, and/or detector device SD.

Further, the clutch device CM at least comprises a centrifugal clutch mechanism 50, and/or a one-way clutch mechanism 51, and/or a ratchet clutch mechanism 52, and/or a jaw clutch mechanism 53, and/or a gear clutch mechanism 54, and/or a lever clutch mechanism 55, and/or an operating clutch 56, and/or an automatic control clutch 57, and/or a mechanical clutch 58, and/or a manual power clutch 59, and/or an electromagnetic clutch 60, and/or a hydraulic clutch 61, and/or a pneumatic clutch 62, and/or an overrunning clutch 63, and/or a centrifugal clutch 64, and/or a safety clutch 65, and/or a mosaic clutch 66, and/or a friction clutch 67, and/or a dry clutch 68, and/or a wet clutch 69, And/or the elastic clutch 70, and/or the rigid clutch 71, and/or the one-way clutch 72, and/or the two-way clutch 73, and/or the normally-open clutch 74, and/or the normally-closed clutch 75, and/or the disc clutch 76, and/or the dog clutch 77, and/or the tooth clutch 78, and/or the cone clutch 79, and/or the friction block clutch 80, and/or the pin clutch 81, and/or the key clutch 82, and/or the race clutch 83, and/or the torsion spring clutch 84, and/or the brake band clutch 85, and/or the brake block clutch 86, and/or the clutch 87, and/or the diaphragm clutch 88, and/or the pneumatic clutch 89, and/or the roller clutch 90, and/or the wedge clutch 91, And/or ratchet clutch 92, and/or synchromesh clutch 93, and/or steel ball clutch 94, and/or magnetic particle clutch 95, and/or double-acting clutch 96, and/or speed-regulating clutch 97, and/or permanent magnet clutch 98, and/or dual clutch 99, and/or multimode clutch 100, and/or direct contact brake 101, and/or indirect contact brake 102, and/or friction brake 103, and/or non-friction brake 104, and/or normally open brake 105, and/or normally closed brake 106, and/or one-way brake 107, and/or two-way brake 108, and/or dry brake 109, and/or wet brake 110, and/or hydraulic brake 111, and/or pneumatic brake 112, And/or electromagnetic brake 113, and/or inertia brake 114, and/or gravity brake 115, and/or centrifugal brake 116, and/or mechanical brake 117, and/or manpower brake 118, and/or self-locking brake 119, and/or jaw brake 120, and/or drum brake 121, and/or band brake 122, and/or disc brake 123, and/or caliper disc brake 124, and/or fixed caliper disc brake 125, and/or floating caliper disc brake 126, and/or full disc brake 127, and/or multi-disc brake 128, and/or cone brake 129, and/or block brake 130, and/or band brake enable brake 131, and/or internal tension brake 132, and/or wedge brake 133, And/or cam brake 134, and/or plunger brake 135, and/or push-rod brake 136, and/or leading shoe brake 137, and/or trailing shoe brake 138, and/or air bag brake 139, and/or magnetic particle brake 140, and/or eddy current brake 141, and/or hysteresis brake 142, and/or eddy current brake 143, and/or retarder brake 144, and/or safety brake 145, and/or service brake 146, and/or parking brake 147, and/or double brake 148, and/or multi-mode brake 149.

The centrifugal clutch mechanism 50 comprises at least a first inner race 1, and/or a first outer race 2, and/or a first centrifugal pawl 3, and/or a first return spring 4, and/or a first left clutch carrier 5, and/or a first right clutch carrier 6, and/or a first clutch rivet 7, and/or a first cage 8, and/or a first bearing roller 9. And/or

The one-way clutch mechanism 51 at least comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch bracket 5, a first right clutch bracket 6, a first clutch rivet 7, a first retainer 8, a first bearing roller 9, a first wedge 10, a first pawl 11, a first auxiliary outer ring 12, a first limit pin 13, a first auxiliary inner ring 14, a first left clutch half 15, a first right clutch half 16, a first auxiliary right clutch half 17, a first shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first return spring 4, a first left clutch bracket 11, a first auxiliary outer ring 12, a first limit pin 13, a first auxiliary inner ring 14, a first left clutch half 15, a first right clutch half 16, a first auxiliary right clutch half 17, a first shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a second return spring, And/or the first auxiliary left half-clutch 22, and/or the first intermediate clutch 23, and/or the second limit pin 24, and/or the first shift cam 25, and/or the first drive pin 26, and/or the first centre ring 45, and/or the second sprag 46, and/or the second cage 47, and/or the second bearing roller 48.

And/or

The ratchet clutch mechanism 52 at least comprises a first inner ring 1, a first outer ring 2, a first return spring 4, and/or a first left clutch bracket 5, and/or a first right clutch bracket 6, and/or a first clutch rivet 7, a first pawl 11, and/or a first auxiliary outer ring 12, and/or a first limit pin 13, and/or a first auxiliary inner ring 14, and/or a first left half clutch 15, and/or a first right half clutch 16, and/or a first auxiliary right half clutch 17, a first shift gear sleeve 18, and/or a first limit mechanism 19, and/or a second pawl 20, and/or a second return spring 21, and/or a first auxiliary left half clutch 22, and/or a first intermediate clutch 23, and/or a second limit pin 24, and/or a first shift cam 25, And/or the first transmission pin 26, the first lever means 27, and/or the first transmission cam 28, and/or the third pawl 29, and/or the third return spring 30, and/or the fourth pawl 31, and/or the fourth return spring 32, and/or the first mid-turn 45, and/or the second lever means 49. And/or

The jaw clutch mechanism 53 at least comprises a first left half clutch 15, a first right half clutch 16, a first shifting sleeve 18, and/or a first positioning mechanism 19, and/or a first intermediate clutch 23. And/or

The gear clutch mechanism 54 at least comprises a first left half clutch 15, a first right half clutch 16, a first shifting sleeve 18, and/or a first positioning mechanism 19, and/or a first intermediate clutch 23. And/or

The lever clutch mechanism 55 at least comprises a first inner ring 1, a first outer ring 2, a first return spring 4, and/or a first left clutch bracket 5, and/or a first clutch rivet 7, a first gear shift sleeve 18, and/or a first positioning mechanism 19, a first lever mechanism 27, a first friction plate 33, a first coupling plate 34, and/or a first compensation spring 35, a first left pressure bearing plate 36, a first right pressure bearing plate 37, a first right snap ring 38, and/or a first left flange 39. And/or

The first pawls 11 include at least a first upper-half pawl 40, a first lower-half pawl 41, a first hydraulic damper 42, and/or a first spring damper 43, and/or a first material damper 44. And/or

The second pawls 20 include at least a first upper pawl half 40, a first lower pawl half 41, a first hydraulic damper 42, and/or a first spring damper 43, and/or a first material damper 44. And/or

The third pawls 29 include at least a first upper-half pawl 40, a first lower-half pawl 41, a first hydraulic damper 42, and/or a first spring damper 43, and/or a first material damper 44. And/or

The fourth pawls 31 include at least a first upper-half pawl 40, a first lower-half pawl 41, a first hydraulic damper 42, and/or a first spring damper 43, and/or a first material damper 44.

Further, the damping device DM at least comprises a friction damping buffer mechanism 201, and/or a hydraulic damping buffer mechanism 202, and/or a spring damping buffer mechanism 203, and/or a material damping buffer mechanism 204, and/or a magnetic particle damping buffer mechanism 205, and/or a pneumatic damping buffer mechanism 206, and/or an electromagnetic damping buffer mechanism 207, and/or a piezoelectric damping buffer mechanism 208, and/or a magnetostrictive damping buffer mechanism 209, and/or a magnetic hysteresis damping buffer mechanism 210, and/or an eddy current damping buffer mechanism 211, and/or a second friction plate 212, and/or a second counter plate 213, and/or a second left pressure bearing plate 214, and/or a second right pressure bearing plate 215, and/or a second left snap ring 216, and/or a second right snap ring 217, and/or a second pre-tightening spring 218, a first pre-tightening spring, a second pre-tightening spring, and a second pre-tightening spring are arranged in, And/or the second inner ring 219, and/or the second outer ring 220, and/or the second left pressure plate 221, and/or the second right pressure plate 222, and/or the second left friction block 223, and/or the second right friction block 224, and/or the second damping plate 225, and/or the second leading shoe 226, and/or the second trailing shoe 227, and/or the second damping drum 228, and/or the second pump wheel 229, and/or the second worm wheel 230, and/or the second leading wheel 231, and/or the second left half coupling 232, and/or the second right half coupling 233, and/or the second blade 234, and/or the second blade pair coupling 235, and/or the second positioning bearing 236, and/or the second separation spring 237, and/or the second oil seal 238, and/or the second damping spring 239, and/or the second right bracket 240, And/or second rivet 241, second adjustment gear sleeve 242, and/or second positioning mechanism 243, second damping lever mechanism 244, and/or second right flange 245, and/or second damping return spring 246, and/or second adjustment bracket 247.

Further, the actuating device AM at least comprises a third actuating motor 301, and/or a third actuating transmission 302, and/or a third actuating hydraulic cylinder 303, and/or a third actuating handle 304, a third actuating pneumatic cylinder 305, and/or a third actuating solenoid valve 306, and/or a third piezoelectric actuator 307, and/or a third magnetostrictive actuator 308, and/or a third memory metal actuator 309, and/or a third expending with heat and contraction with cold actuator 310, and/or a third actuating lead screw 311, and/or a third actuating nut 312, and/or a third anti-rotation guide rod 313, and/or a third actuating pin 314, and/or a third actuating link 315, and/or a third shifting fork 316, and/or a third actuating lead rod 317, and/or a motor actuating device 318, and/or a hydraulic actuating device 319, And/or manual actuation means 320, and/or pneumatic actuation means 321, and/or electromagnetic actuation means 322, and/or piezoelectric actuation means 323, and/or magnetostrictive actuation means 324, and/or memory metal actuation means 325, and/or thermal expansion and contraction actuation means 326.

Further, the adjusting device RM at least comprises a fourth adjusting motor 401, and/or a fourth adjusting transmission mechanism 402, and/or a fourth adjusting hydraulic cylinder 403, and/or a fourth adjusting handle 404, and/or a fourth adjusting pneumatic cylinder 405, and/or a fourth adjusting solenoid valve 406, and/or a fourth piezoelectric adjuster 407, and/or a fourth magnetostrictive adjuster 408, and/or a fourth memory metal adjuster 409, and/or a fourth thermal expansion and contraction adjuster 410, and/or a fourth adjusting screw 411, and/or a fourth adjusting nut 412, and/or a fourth anti-rotation guide rod 413, and/or a fourth adjusting pin 414, and/or a fourth adjusting link 415, and/or a fourth adjusting fork 416, and/or a fourth adjusting guide rod 417, and/or a fourth separating fork 418, And/or a fourth release bearing 419, and/or a fourth diaphragm spring 420, and/or a fourth diaphragm spring support pin 421, and/or a fourth diaphragm spring bearing plate 422, and/or a fourth diaphragm spring cover plate 423, and/or a fourth adjustment bracket 424, and/or a fourth adjustment bolt 425, and/or a motor adjustment device 426, and/or a hydraulic adjustment device 427, and/or a manual adjustment device 428, and/or an air pressure adjustment device 429, and/or an electromagnetic adjustment device 430, and/or a piezoelectric adjustment device 431, and/or a magnetic extension adjustment device 432, and/or a memory metal adjustment device 433, and/or a thermal expansion and contraction adjustment device 434.

The utility model also provides a concentrate clutch, parking device, differential mechanism, braking system, safety device, transmission system, module and a machine for transmission field.

Compared with the prior art, the utility model discloses a gearshift GD with buffering damping function has following advantage:

(1) simple structure, reliability are high: most parts of the gear shifting device GD are simple in structure and uncomplicated in manufacturing process; because the buffer device is added on the basis of the traditional gear shifting device, the vibration and the impact of the clutch mechanism in the power engaging and disengaging process are greatly reduced. In particular, with the conventional ratchet clutch, since the inertia load at the moment of power engagement and disengagement is large, the shock resistance thereof is poor; for the one-way clutch, the load is transmitted by adopting point or line contact, the shock resistance is poor, and the transmitted torque is small; therefore, due to the addition of the buffer device, the load borne by the ratchet clutch and the one-way clutch in the power engagement and disengagement process can be greatly reduced, and particularly, for the gear shifting device GD with the buffer damping function and adopting the friction plate type buffer device, the durability, the bearing capacity and the reliability are greatly improved due to the fact that more than one surface contact is adopted to replace the point contact or the line contact of the traditional one-way clutch, and more than one friction force is utilized to slide and rub the downstream transmission part. And because the gear shifting device GD adopts the buffer device to limit the bearing range of the power system, the whole power system is prevented from bearing overlarge torque or load, and the reliability of the whole power system can be improved by the gear shifting device GD.

(2) Good controllability and low control difficulty: part of the clutch devices of the gear shifting device GD have a self-clutch function according to actual working conditions, and other gear shifting devices are provided with special actuating devices to realize clutch operation, so that the whole gear shifting device is good in controllability; and the gear shifting device is provided with a special buffering damping device for reducing vibration and impact in the power engagement or power separation process, further, the gear shifting device GD is provided with a special adjusting device for controlling the damping of the damping device, the functional modules of the gear shifting device GD are clearly divided into time and labor, each time and the time are respectively occupied, the overlapping performance is less, the functional requirement on a control system is lower, and the development difficulty of the control system is lower.

(3) The modularization is high, the commonality is good, scalability is strong: the gear shifting device GD consists of different functional modules, only different clutch device modules are required to be changed, different buffer damping device modules are used as auxiliary materials, and an actuating device module, an adjusting device module and the like are added, so that the gear shifting device GD can almost replace all traditional gear shifting devices (a one-way clutch, a centrifugal clutch, a friction plate type clutch, an electromagnetic clutch, a magnetic powder clutch, a synchronizer, a parking device, a safety protection device (torque limit, speed limit and the like), a brake device (a traditional brake device, an IBooster and the like), a front and rear axle transfer case of an automobile, an inter-wheel anti-skid differential, a centralized synchronizer and the like); and a plurality of gear shifting functions of a transmission system can be integrated on one gear shifting device GD, so that a centralized clutch function of centralized control is realized, and a brand new view is opened up for structural transformation and new function development of the existing traditional transmission system.

(4) No power interruption of the gear shifting process: due to the adoption of the special buffering damping device, the vibration and the impact in the gear shifting joint process are small, so that the direct gear shifting can be realized under the condition of not cutting off the power.

(5) The manufacturing cost is low: the parts of the gear shifting device GD are simple in structure, modular structure design is adopted, the universality is high, the gear shifting control difficulty is low, no power interruption is caused in the gear shifting process, the application prospect is very wide, the parts and modules of the gear shifting device GD with the buffering damping function can be produced in a large batch and in a modular mode, and therefore the overall manufacturing cost is comprehensively reduced.

The above features and advantages and other features and advantages of the present invention are readily apparent from the following detailed description of the best modes for carrying out the invention when taken in connection with the accompanying drawings, wherein, however, it is to be expressly understood that all of the figures are for the purpose of illustration only and are not intended as a definition of the limits and scope of the invention.

Drawings

FIGS. 1 to 10 are 10 basic configurations of a shift device GD with a damping function, FIGS. 11 to 13 are schematic structural views of a first damping device DM, FIGS. 14 to 16 are schematic structural views of a second damping device DM, FIGS. 17 to 19 are schematic structural views of a third damping device DM, FIGS. 20 to 22 are schematic structural views of a fourth damping device DM, FIGS. 23 to 25 are schematic structural views of a fifth damping device DM, FIGS. 26 to 28 are schematic structural views of a sixth damping device DM, FIGS. 29 to 31 are schematic structural views of a seventh damping device DM, FIGS. 32 to 34 are schematic structural views of an eighth damping device DM, FIGS. 35 to 37 are schematic structural views of a ninth damping device DM, FIGS. 38 to 41 are schematic structural views of a first centrifugal clutch mechanism 50, and FIGS. 42 to 45 are schematic structural views of a second centrifugal clutch mechanism 50, FIGS. 46 to 49 are schematic structural views of a third centrifugal clutch mechanism 50, FIGS. 50 to 53 are schematic structural views of a fourth centrifugal clutch mechanism 50, FIGS. 54 to 57 are schematic structural views of a first one-way clutch mechanism 51, FIGS. 58 to 61 are schematic structural views of a second one-way clutch mechanism 51, FIGS. 62 to 65 are schematic structural views of the third one-way clutch mechanism 51, FIGS. 66 to 70 are schematic structural views of the fourth one-way clutch mechanism 51, FIGS. 71 to 74 are schematic structural views of a fifth one-way clutch mechanism 51, FIGS. 75 to 79 are schematic structural views of a sixth one-way clutch mechanism 51, FIGS. 80 to 86 are schematic structural views of a seventh one-way clutch mechanism 51, FIGS. 87 to 91 are schematic structural views of an eighth one-way clutch mechanism 51, FIGS. 92 to 97 are schematic structural views of a ninth one-way clutch mechanism 51, and FIGS. 98 to 100 are schematic structural views of a tenth one-way clutch mechanism 51, FIGS. 101 to 103 are schematic structural views of an eleventh one-way clutch mechanism 51, FIGS. 104 to 106 are schematic structural views of a twelfth one-way clutch mechanism 51, FIGS. 107 to 110 are schematic structural views of a thirteenth one-way clutch mechanism 51, FIGS. 111 to 114 are schematic structural views of the fourteenth one-way clutch mechanism 51, FIGS. 115 to 118 are schematic structural views of a first ratchet clutch mechanism 52, FIGS. 119 to 128 are schematic structural views of a second ratchet clutch mechanism 52, FIGS. 129 to 138 are schematic structural views of a third ratchet clutch mechanism 52, FIGS. 139 to 141 are schematic structural views of a fourth ratchet clutch mechanism 52, FIGS. 142 to 144 are schematic structural views of a fifth ratchet clutch mechanism 52, FIGS. 145 to 147 are schematic structural views of a sixth ratchet clutch mechanism 52, FIGS. 148 to 150 are schematic structural views of a seventh ratchet clutch mechanism 52, and FIGS. 151 to 153 are schematic structural views of an eighth ratchet clutch mechanism 52, FIGS. 154 to 156 are schematic structural views of a ninth ratchet clutch mechanism 52, FIGS. 157 to 165 are schematic structural views of a tenth ratchet clutch mechanism 52, FIGS. 166 to 173 are schematic structural views of an eleventh ratchet clutch mechanism 52, FIGS. 174 to 176 are schematic structural views of a twelfth ratchet clutch mechanism 52, FIGS. 177 to 179 are schematic structural views of a thirteenth ratchet clutch mechanism 52, FIGS. 180 to 182 are schematic structural views of a fourteenth ratchet clutch mechanism 52, FIGS. 183 to 185 are schematic structural views of a fifteenth ratchet clutch mechanism 52, FIGS. 186 to 187 are schematic structural views of a first jaw clutch mechanism 53, FIGS. 188 to 189 are schematic structural views of a second jaw clutch mechanism 53, FIGS. 190 to 191 are schematic structural views of a third jaw clutch mechanism 53, FIGS. 192 to 193 are schematic structural views of a fourth jaw clutch mechanism 53, and FIGS. 194 to 195 are schematic structural views of a fifth jaw clutch mechanism 53, FIGS. 196 to 197 are schematic structural views of a sixth jaw clutch mechanism 53, FIGS. 198 to 199 are schematic structural views of a first gear clutch mechanism 54, FIGS. 200 to 201 are schematic structural views of a second gear clutch mechanism 54, FIGS. 202 to 204 are schematic structural views of a first lever clutch mechanism 55, FIGS. 205 to 207 are schematic structural views of a second lever clutch mechanism 55, FIG. 208 is a schematic structural view of a first actuating device RM, FIG. 209 is a schematic structural view of a second actuating device RM, FIG. 210 is a schematic structural view of a third actuating device RM, FIG. 211 is a schematic structural view of a fourth actuating device RM, FIG. 212 is a schematic structural view of the first adjusting device RM, FIGS. 213 to 215 are schematic structural views of the second adjusting device RM, FIGS. 216 to 218 are schematic structural views of the third adjusting device RM, and FIGS. 219 to 220 are schematic structural views of the fourth adjusting device RM, fig. 221 is a schematic structural view of a fifth adjusting device RM, fig. 222 to 224 are schematic structural views of a first pawl having a hydraulic damping function, fig. 225 to 227 are schematic structural views of a second pawl having a hydraulic damping function, fig. 228 to 230 are schematic structural views of a third pawl having a hydraulic damping function, fig. 227 to 229 are schematic structural views of a first gear shifting device GD having a cushion damping function, fig. 231 is a schematic structural view of an overload protection function or a self-locking function between the pawl and a ratchet wheel, fig. 232 to 234 are schematic structural views of the first gear shifting device GD having a cushion damping function, fig. 235 to 237 are schematic structural views of the second gear shifting device GD having a cushion damping function, fig. 238 to 240 are schematic structural views of the third gear shifting device GD having a cushion damping function, and fig. 241 to 243 are schematic structural views of a fourth gear shifting device GD having a cushion damping function, fig. 244 to 246 are schematic structural views of a fifth gear shift device GD with a cushion damping function, fig. 247 to 249 are schematic structural views of a sixth gear shift device GD with a cushion damping function, fig. 250 to 252 are schematic structural views of a seventh gear shift device GD with a cushion damping function, fig. 253 to 255 are schematic structural views of an eighth gear shift device GD with a cushion damping function, fig. 256 to 258 are schematic structural views of a ninth gear shift device GD with a cushion damping function, fig. 259 to 261 are schematic structural views of a tenth gear shift device GD with a cushion damping function, fig. 262 to 264 are schematic structural views of an eleventh gear shift device GD with a cushion damping function, fig. 265 to 267 are schematic structural views of a twelfth gear shift device GD with a cushion damping function, and fig. 268 to 270 are schematic structural views of a thirteenth gear shift device GD with a cushion damping function, fig. 271 to 273 are schematic structural views of a fourteenth shift apparatus GD with a cushion damping function, fig. 274 to 276 are schematic structural views of a fifteenth shift apparatus GD with a cushion damping function, fig. 277 to 279 are schematic structural views of a sixteenth shift apparatus GD with a cushion damping function, fig. 280 to 282 are schematic structural views of a seventeenth shift apparatus GD with a cushion damping function, fig. 283 to 285 are schematic structural views of an eighteenth shift apparatus GD with a cushion damping function, fig. 286 to 288 are schematic structural views of a nineteenth shift apparatus GD with a cushion damping function, fig. 289 to 291 are schematic structural views of a twentieth shift apparatus GD with a cushion damping function, fig. 292 to 294 are schematic structural views of a twenty-th shift apparatus GD with a cushion damping function, and fig. 295 to 297 are schematic structural views of a twenty-second shift apparatus GD with a cushion damping function, FIGS. 298 to 300 are schematic structural views of a twenty-third type of shift device GD with a cushion damping function, FIGS. 301 to 303 are schematic structural views of a twenty-fourth type of shift device GD with a cushion damping function, FIGS. 304 to 306 are schematic structural views of a twenty-fifth type of shift device GD with a cushion damping function, FIGS. 307 to 309 are schematic structural views of a twenty-sixth type of shift device GD with a cushion damping function, FIGS. 310 to 312 are schematic structural views of a twenty-seventh type of shift device GD with a cushion damping function, FIGS. 313 to 315 are schematic structural views of a twenty-eighth type of shift device GD with a cushion damping function, FIGS. 316 to 318 are schematic structural views of a twenty-ninth type of shift device GD with a cushion damping function, FIGS. 319 to 321 are schematic structural views of a thirteen type of shift device GD with a cushion damping function, and FIGS. 322 to 324 are schematic structural views of a thirty type of shift device GD with a cushion damping function, FIGS. 325 to 327 are schematic structural views of a thirty-second shift device GD with a cushion damping function, FIGS. 328 to 330 are schematic structural views of a thirty-third shift device GD with a cushion damping function, FIGS. 331 to 333 are schematic structural views of a thirty-fourth shift device GD with a cushion damping function, FIGS. 334 to 336 are schematic structural views of a thirty-fifth shift device GD with a cushion damping function, FIGS. 337 to 339 are schematic structural views of a thirty-sixth shift device GD with a cushion damping function, FIGS. 340 to 342 are schematic structural views of a thirty-seventh shift device GD with a cushion damping function, FIGS. 343 to 345 are schematic structural views of a thirty-eighth shift device GD with a cushion damping function, FIGS. 346 to 348 are schematic structural views of a thirty-ninth shift device GD with a cushion damping function, and FIGS. 349 to 351 are schematic structural views of a forty shift device GD with a cushion damping function, fig. 352 to 354 are schematic structural views of a forty-first shift device GD with a cushion and damping function, fig. 355 to 357 are schematic structural views of a forty-second shift device GD with a cushion and damping function, fig. 358 to 360 are schematic structural views of a forty-third shift device GD with a cushion and damping function, fig. 361 to 363 are schematic structural views of a forty-fourth shift device GD with a cushion and damping function, fig. 364 to 366 are schematic structural views of a forty-fifth shift device GD with a cushion and damping function, fig. 367 to 369 are schematic structural views of a forty-sixth shift device GD with a cushion and damping function, fig. 370 to 372 are schematic structural views of a forty-seventh shift device GD with a cushion and damping function, fig. 373 to 375 are schematic structural views of a forty-eighth shift device GD with a cushion and damping function, and fig. 376 to 378 are schematic structural views of a forty-ninth shift device GD with a cushion and damping function, fig. 379 to 381 are schematic structural views of a fifty-th shift device GD with a damping function;

The labels used in the (in the figure) patents illustrate: GD-Shifting device with damping, M-machine, DM-damping device, CM-clutch device, AM-actuating device, RM-adjusting device, SD-detector device, GSD-conventional shifting device, DIF-inter-wheel differential, LHS-left half-shaft, RHS-right half-shaft, CDIF-Central differential, FDS-front drive shaft, RDS-rear drive shaft, AAG-arresting cable, GW-arresting cable guide wheel, 1-first inner ring, 2-first outer ring, 3-first centrifugal pawl, 4-first return spring, 5-first left clutch carrier, 6-first right clutch carrier, 7-first clutch rivet, 8-first retainer, 9-first bearing roller, 10-first wedge, 11-a first pawl, 12-a first auxiliary outer ring, 13-a first limit pin, 14-a first auxiliary inner ring, 15-a first left half clutch, 16-a first right half clutch, 17-a first auxiliary right half clutch, 18-a first shift gear sleeve, 19-a first positioning mechanism, 20-a second pawl, 21-a second return spring, 22-a first auxiliary left half clutch, 23-a first intermediate clutch, 24-a second limit pin, 25-a first shift cam, 26-a first drive pin, 27-a first lever mechanism, 28-a first drive cam, 29-a third pawl, 30-a third return spring, 31-a fourth pawl, 32-a fourth return spring, 33-a first friction plate, 34-a first pair of coupling plates, 35-a first compensating spring, 36-a first left bearing plate, 37-a first right bearing plate, 38-a first right snap ring, 39-a first left flange, 40-a first upper half pawl, 41-a first lower half pawl, 42-a first hydraulic damper, 43-a first spring damper, 44-a first material damper, 45-a first middle ring, 46-a second wedge, 47-a second retainer, 48-a second bearing roller, 49-a second lever mechanism, 50-a centrifugal clutch mechanism, 51-a one-way clutch mechanism, 52-a ratchet clutch mechanism, 53-a jaw clutch mechanism, 54-a gear clutch mechanism, 55-a lever clutch mechanism, 56-an operating clutch, 57-a self-controlling clutch, 58-a mechanical clutch, 59-manual clutch, 60-electromagnetic clutch, 61-hydraulic clutch, 62-pneumatic clutch, 63-overrunning clutch, 64-centrifugal clutch, 65-safety clutch, 66-embedded clutch, 67-friction clutch, 68-dry clutch, 69-wet clutch, 70-elastic clutch, 71-rigid clutch, 72-one-way clutch, 73-two-way clutch, 74-normally open clutch, 75-normally closed clutch, 76-disc clutch, 77-dog clutch, 78-tooth clutch, 79-cone clutch, 80-friction block clutch, 81-pin clutch, 82-key clutch, 83-rising clutch, 84-torsion spring clutch, 85-belt clutches, 86-pad clutches, 87-drum clutches, 88-diaphragm clutches, 89-pneumatic-tire clutches, 90-roller clutches, 91-wedge clutches, 92-ratchet clutches, 93-synchronizer clutches, 94-steel-ball clutches, 95-magnetic-particle clutches, 96-double-acting clutches, 97-speed-regulating clutches, 98-permanent-magnet clutches, 99-double clutches, 100-multimode clutches, 101-direct-contact brakes, 102-indirect-contact brakes, 103-friction brakes, 104-non-friction brakes, 105-normally-open brakes, 106-normally-closed brakes, 107-one-way brakes, 108-two-way brakes, 109-dry brakes, 110-wet brake, 111-hydraulic brake, 112-pneumatic brake, 113-electromagnetic brake, 114-inertia brake, 115-gravity brake, 116-centrifugal brake, 117-mechanical brake, 118-manual brake, 119-self-locking brake, 120-jaw brake, 121-drum brake, 122-band brake, 123-disc brake, 124-caliper disc brake, 125-fixed caliper disc brake, 126-floating caliper disc brake, 127-full disc brake, 128-multi-disc brake, 129-cone brake, 130-block brake, 131-band brake enable brake, 132-internal-tension brake, 133-wedge brake, 134-cam brake, 135-plunger brake, 136-push rod brake, 137-leading shoe brake, 138-trailing shoe brake, 139-airbag brake, 140-magnetic powder brake, 141-eddy current brake, 142-hysteresis brake, 143-eddy current brake, 144-retarder brake, 145-safety brake, 146-service brake, 147-parking brake, 148-double brake, 149-multimode brake, 201-friction damping buffer mechanism, 202-hydraulic damping buffer mechanism, 203-spring damping buffer mechanism, 204-material damping buffer mechanism, 205-magnetic powder damping buffer mechanism, 206-pneumatic damping buffer mechanism, 207-electromagnetic damping buffer mechanism, 208-piezoelectric damping buffer mechanism, 209-telescopic damping buffer mechanism, 210-hysteresis damping mechanism, 211-eddy current damping mechanism, 212-second friction plate, 213-second couple plate, 214-second left bearing plate, 215-second right bearing plate, 216-second left snap ring, 217-second right snap ring, 218-second pre-tightening spring, 219-second inner ring, 220-second outer ring, 221-second left pressure plate, 222-second right pressure plate, 223-second left friction block, 224-second right friction block, 225-second damping disc, 226-second pilot shoe, 227-second pilot shoe, 228-second damping drum, 229-second pump wheel, 230-second turbine wheel, 231-second guide wheel, 232-second left half coupling, 233-second right half coupling, 234-second blade, 235-second blade couple plate, 236-a second positioning bearing, 237-a second separation spring, 238-a second oil seal, 239-a second damping spring, 240-a second right bracket, 241-a second rivet, 242-a second adjusting gear sleeve, 243-a second positioning mechanism, 244-a second damping lever mechanism, 245-a second right flange, 246-a second damping return spring, 247-a second adjusting bracket, 301-a third actuating motor, 302-a third actuating transmission mechanism, 303-a third actuating hydraulic cylinder, 304-a third actuating handle, 305-a third actuating pneumatic cylinder, 306-a third actuating solenoid valve, 307-a third piezoelectric actuator, 308-a third magnetostrictive actuator, 309-a third memory metal actuator, 310-a third thermal expansion and contraction actuator, 311-a third actuating screw rod, 312-a third actuating nut, 313-a third anti-rotation guide rod, 314-a third actuating pin, 315-a third actuating link, 316-a third shift fork, 317-a third shift guide rod, 318-a motor actuating device, 319-a hydraulic actuating device, 320-a manual actuating device, 321-a pneumatic actuating device, 322-an electromagnetic actuating device, 323-a piezoelectric actuating device, 324-a magnetostrictive actuating device, 325-a memory metal actuating device, 326-a thermal expansion and contraction actuating device, 401-a fourth adjusting motor, 402-a fourth adjusting transmission mechanism, 403-a fourth adjusting hydraulic cylinder, 404-a fourth adjusting handle, 405-a fourth adjusting pneumatic cylinder, 406-a fourth adjusting solenoid valve, 407-a fourth piezoelectric adjuster, 408-a fourth magnetostrictive adjuster, 409-a fourth memory metal adjuster, 410-a fourth expansion and contraction adjuster, 411-a fourth adjusting screw rod, 412-a fourth adjusting nut, 413-a fourth rotation-preventing guide rod, 414-a fourth adjusting actuating pin, 415-a fourth adjusting actuating link, 416-a fourth adjusting fork, 417-a fourth adjusting stop lever, 418-a fourth separating fork, 419-a fourth separating bearing, 420-a fourth diaphragm spring, 421-a fourth diaphragm spring support pin, 422-a fourth diaphragm spring bearing plate, 423-a fourth diaphragm spring cover plate, 424-a fourth adjusting bracket, 425-a fourth adjusting bolt, 426-a motor adjusting device, 427-a hydraulic adjusting device, 428-a manual adjusting device, 429-an air pressure adjusting device, 430-an electromagnetic adjusting device, 431-a piezoelectric adjusting device, 432-a magnetic extension adjusting device, 433-a memory metal adjusting device and 434-a thermal expansion and contraction adjusting device.

Detailed Description

The present invention will be further described with reference to the following drawings and examples, but the present invention is not limited to the description of the examples. It is to be understood that only a few of the presently preferred embodiments of the invention have been described, and not all embodiments have been described. Since numerous changes may be made by those skilled in the art based on the principles of the invention, it is not intended that the invention be limited to the details shown and described, but that the invention will include all variations and modifications falling within the scope of the appended claims.

The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting. As used herein, the singular forms "a", "an", and the like may also be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises" and "comprising" are inclusive and therefore specify the presence of stated features, integers, steps, operations, elements, components, parts, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. The method steps, procedures and operations described herein should not be construed as necessarily requiring their performance in the particular order discussed or illustrated, unless specifically identified as an order of performance. It should also be understood that additional or alternative steps may be employed.

Although the terms first, second, third, etc. may be used herein to describe various parts, components, assemblies, layers and/or sections, these parts, components, assemblies, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, member, component, layer and/or section. Terms such as "first," "second," "third," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context.

Example 1

As shown in fig. 232 to 234, the shift device GD includes: centrifugal clutch mechanism 50, and damping device DM. As shown in fig. 38 to 41, the centrifugal clutch mechanism 50 includes: the clutch comprises a first inner ring 1, a first outer ring 2, a first centrifugal pawl 3, a first return spring 4, a first left clutch support 5, a first right clutch support 6 and a first clutch rivet 7. As shown in fig. 11 to 13, the cushion damper device DM includes: the second friction plate 212, the second counter plate 213, the second left bearing plate 214, the second right bearing plate 215, the second left snap ring 216, the second right snap ring 217, the second pre-tightening spring 218 and the second outer ring 220. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch support 5, the first right clutch support 6 and the first inner ring 1 are coaxially arranged. The first inner race 1, the first outer race 2, the first centrifugal pawl 3, the first return spring 4, the first right clutch bracket 6, and the first bearing roller 9 are arranged on the right side of the first left clutch bracket 5 in the axial direction. The first inner ring 1 is directly or indirectly connected with a driven member of the machine M and rotates together with the driven member of the machine M. The first outer race 2 is directly connected to the second friction plate 212 and rotates together with the second friction plate 212. The first centrifugal pawl 3 is in engagement with the first inner race 1 in an initial position. The first inner race 1 is configured with ratchet-like protrusions and/or ratchet-like recesses, and the first centrifugal pawls 3 are at least configured to have a function of engaging with or disengaging from the ratchet-like protrusions and/or ratchet-like recesses. The first centrifugal pawls 3 are uniformly mounted on the first outer race 2 and rotate together with the first outer race 2. The first return springs 4 are uniformly installed on the first outer race 2 and rotate together with the first outer race 2. The first centrifugal pawl 3 is directly connected to the first return spring 4, and the first centrifugal pawl 3 is at least configured to effect engagement or disengagement of the first centrifugal pawl 3 with the first inner race 1 under the action of centrifugal force and the elastic force of the first return spring 4. The first return spring 4 is at least configured to have elasticity, and the first return spring 4 at least has a function of gradually returning the first centrifugal pawl 3 to the initial position when the centrifugal force to which the first centrifugal pawl 3 is subjected is gradually decreased. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane. The second pair of coupling plates 213, the second left bearing plate 214, the second right bearing plate 215, the second left snap ring 216, the second right snap ring 217, the second pre-tightening spring 218, and the second outer ring 220 are coaxially arranged with the second friction plate 212. The second friction plate 212, the second counter plate 213, the second left bearing plate 214, the second right bearing plate 215, the second left snap ring 216, and the second preload spring 218 are axially disposed at one side of the second right snap ring 217. The second outer race 220 is disposed radially outward of the second friction plate 212. The second pair of coupling pieces 213 are directly connected to the second outer ring 220 in the radial direction thereof, and rotate together with the second outer ring 220. The second outer race 220 is directly or indirectly connected to the driving member of the machine M and rotates together with the driving member of the machine M. The second left bearing plate 214 is directly connected to the second outer ring 220 in a radial direction thereof, and rotates together with the second outer ring 220. The second right bearing plate 215 is directly connected to the second outer ring 220 in a radial direction thereof, and rotates together with the second outer ring 220. The second left snap ring 216 is directly connected to the second outer ring 220 in a radial direction thereof, and rotates together with the second outer ring 220. The second right snap ring 217 is directly connected to the second outer ring 220 in a radial direction thereof, and rotates together with the second outer ring 220. The second friction plate 212 includes a plurality of friction plates. The second dual tab 213 includes a plurality of dual tabs. The second friction plate 212 is directly connected to the second counter plate 213 in the axial direction thereof. The second left bearing plate 214 is directly connected to the second friction plate 212 in the axial direction thereof. The second left bearing plate 214 is directly connected to the second left snap ring 216 in the axial direction thereof. The second right bearing plate 215 is directly connected to the second friction plate 212 in the axial direction thereof. The second right bearing plate 215 is directly connected to the second preload spring 218 in the axial direction thereof. The second pretensioned spring 218 is directly connected to the second right snap ring 217 in the axial direction thereof. The second left snap ring 216 is fixedly connected to the second outer ring 220 in the axial direction thereof. The second right snap ring 217 is fixedly connected to the second outer ring 220 in the axial direction thereof. The second friction plate 212, the second counter plate 213, the second left bearing plate 214, and the second right bearing plate 215 form a friction pair and transmit power or torque under the elastic force of the second pre-tightening spring 218. When the motion, power or torque required to be transmitted by the friction pair is small, or when the vibration and impact required to be transmitted by the friction pair are small, the friction pair transmits the motion, power or torque in a static friction mode, and has a certain damping effect on the vibration and impact in the motion, power or torque transmission process. When the motion, power or torque required to be transmitted by the friction pair is excessive, or when the vibration and impact required to be transmitted by the friction pair are excessive, the friction pair eliminates the excessive motion, power or torque in the form of sliding friction and has a certain damping effect on the vibration and impact in the motion, power or torque transmission process. The friction pair formed by the second friction plate 212, the second counter plate 213, the second left bearing plate 214 and the second right bearing plate 215 under the elastic force of the second pre-tightening spring 218 operates under wet friction or dry friction conditions. The second pre-tightening spring 218 at least has a function of compensating the axial thickness reduction of the second friction plate 212 and the second counter plate 213 due to wear to some extent. When the first centrifugal pawls 3 are engaged with the first inner race 1, the second outer race 220 transmits its power or motion to the first inner race 1 sequentially through the friction pair, the first outer race 2, and the first centrifugal pawls 3.

Example 2

As shown in fig. 235 to 237, the shift device GD includes: centrifugal clutch mechanism 50, and damping device DM. The centrifugal clutch mechanism 50 is shown in fig. 42 to 45. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 2 is the same as that in embodiment 1. The centrifugal clutch mechanism 50 in embodiment 2 is similar to that in embodiment 1 except that: the centrifugal clutch mechanism 50 in embodiment 2 is added with the first cage 8 and the first bearing roller 9; the first bearing rollers 9 comprise a plurality of rollers, the first inner ring 1 is connected with the first outer ring 2 through the first bearing rollers 9, and the first bearing rollers 9 position the relative positions of the first inner ring 1 and the first outer ring 2 in the radial direction and the axial direction by direct contact; the first cage 8 has a function of isolating and guiding the first bearing roller 9, the first cage 8 holds the first bearing roller 9 in the centrifugal clutch mechanism 50, and the first cage 8 moves along with the first bearing roller 9; the first bearing rollers 9 are uniformly arranged on the first cage 8, and the first cage 8 is arranged coaxially with the first inner ring 1.

Example 3

As shown in fig. 238 to 240, the shift device GD includes: centrifugal clutch mechanism 50, and damping device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 3 is similar to that in embodiment 1 except that: the second outer race 220 of the cushion damper device DM according to embodiment 3 is connected to a driven member (not shown) of the machine M. As shown in fig. 46 to 49, the centrifugal clutch mechanism 50 in embodiment 3 is similar to that in embodiment 1, except that: the first centrifugal pawl 3 and the first return spring 4 are both mounted on the first inner race 1. The first left clutch support 5 and the first right clutch support 6 are fixedly connected with the first inner ring 1 through the first clutch rivet 7. The first centrifugal pawl 3 is in a disengaged state from the first outer race 2 in an initial position. The first inner ring 1 is directly connected to a driving member (not shown) of the machine M and rotates together with the driving member of the machine M. The second outer race 220 is directly or indirectly connected to a driven member (not shown) or a frame (not shown) of the machine M.

Example 4

As shown in fig. 241 to 243, the shift device GD includes: centrifugal clutch mechanism 50, and damping device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 4 is the same as that in embodiment 3. As shown in fig. 50 to 53, the centrifugal clutch mechanism 50 in embodiment 4 is similar to that in embodiment 3, except that: the centrifugal clutch mechanism 50 in embodiment 4 is added with the first cage 8 and the first bearing roller 9. The first bearing roller 9 includes a plurality of rollers, the first inner ring 1 is connected to the first outer ring 2 through the first bearing roller 9, and the first bearing roller 9 positions the relative position of the first inner ring 1 and the first outer ring 2 in the radial direction and the axial direction by direct contact. The first cage 8 has a function of isolating and guiding the first bearing roller 9, and the first cage 8 holds the first bearing roller 9 in the centrifugal clutch mechanism 50 and the first cage 8 moves along with the first bearing roller 9. The first bearing rollers 9 are uniformly arranged on the first cage 8, and the first cage 8 is arranged coaxially with the first inner ring 1.

Example 5

As shown in fig. 244 to 246, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. As shown in fig. 54 to 57, the one-way clutch mechanism 51 includes: the clutch comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch bracket 5, a first right clutch bracket 6, a first clutch rivet 7, a first retainer 8 and a first wedge block 10. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 5 is the same as that in embodiment 3. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch support 5, the first right clutch support 6 and the first inner ring 1 are coaxially arranged. The first inner race 1, the first outer race 2, the first return spring 4, the first right clutch carrier 6, and the first sprag 10 are arranged axially on the right side of the first left clutch carrier 5. The first inner ring 1 is directly or indirectly connected to a driving member (not shown) of the machine M and rotates together with the driving member (not shown) of the machine M. The first outer race 2 is directly connected to the second friction plate 212 and rotates together with the second friction plate 212. When the first sprag 10 is in the initial position, the first inner ring 1 is fixed to the first outer ring 2 in the forward rotation (direction indicated by an arrow in fig. 56) and is free to rotate in the reverse rotation. Under the direct action of the first return spring 4, the first sprag 10 and the first inner race 1 are in contact with each other, and the first sprag 10 and the first outer race 2 are in contact with each other. The first wedge 10 includes a plurality of wedges, the first wedge 10 is connected to the first holder 8 and rotates together with the first holder 8, and the first wedge 10 is rotatable within a certain angle range with respect to the first holder 8. The first return spring 4 includes a plurality of springs, and the first return spring 4 is directly mounted on the first holder 8 and rotates together with the first holder 8. The first return spring 4 is directly connected to the first wedge 10, and when the other restraint or load acts on the first wedge 10 less than the first return spring 4 acts on the first wedge 10, the first wedge 10 returns to the initial position by the first return spring 4. Under the action of the first inner race 1, the first outer race 2, and the first return spring 4, the first sprag 10 self-fixes the first inner race 1 to the first outer race 2 in a one-way manner in the normal rotation direction (the direction indicated by the arrow in fig. 56) and rotates in the reverse rotation direction. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane. The second outer race 220 is directly or indirectly connected to a driven member (not shown) of the machine M.

Example 6

As shown in fig. 247 to 249, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper DM in the embodiment is the same as that in embodiment 3. The one-way clutch mechanism 51 is shown in fig. 58 to 61. The one-way clutch mechanism 51 in embodiment 6 is similar to embodiment 5 except that: the one-way clutch mechanism 51 according to embodiment 6 is configured to add the first bearing roller 9, and the first inner race 1 is rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 60) and fixed in the reverse rotation direction with respect to the second inner race 2 by the first sprag 10 and the first return spring 4. The first bearing roller 9 includes a plurality of rollers, the first inner ring 1 is connected to the first outer ring 2 through the first bearing roller 9, and the first bearing roller 9 positions the relative position of the first inner ring 1 and the first outer ring 2 in the radial direction and the axial direction by direct contact. The first cage 8 has a function of separating and guiding the first bearing roller 9, and the first cage 8 holds the first bearing roller 9 in the one-way clutch mechanism 51 and the first cage 8 moves along with the first bearing roller 9. The first bearing rollers 9 are uniformly arranged on the first cage 8, and the first cage 8 is arranged coaxially with the first inner ring 1. The first sprags 10 are grooved in the portions overlapping the first bearing rollers 9 in the axial direction, so that the contact portions on the first inner ring 1 with the first bearing rollers 9 do not overlap the contact portions on the first inner ring 1 with the first sprags 10 in the axial direction, and the contact portions on the first outer ring 2 with the first bearing rollers 9 do not overlap the contact portions on the first outer ring 2 with the first sprags 10 in the axial direction.

Example 7

As shown in fig. 250 to 252, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. As shown in fig. 62 to 65, the one-way clutch mechanism 51 includes: the clutch comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7 and a first pawl 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 7 is the same as that in embodiment 3. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch support 5, the first right clutch support 6 and the first inner ring 1 are coaxially arranged. The first inner race 1, the first outer race 2, the first return spring 4, the first left clutch bracket 5, the first clutch rivet 7, and the first pawl 11 are arranged on the left side of the first right clutch bracket 6 in the axial direction. The first inner ring 1 is directly or indirectly connected to a driving member (not shown) of the machine M and rotates together with the driving member (not shown) of the machine M. The first outer race 2 is directly connected to the second friction plate 212 of the cushion damper device DM and rotates together with the second friction plate 212. The first pawls 11 are engaged with the first outer race 2 at an initial position, in which the first outer race 2 is rotatable in the forward rotation direction (the direction indicated by the arrow in fig. 64) and fixed in the reverse rotation direction with respect to the first inner race 1. When the first pawls 11 and the first outer ring 2 are in the disengaged state, the first outer ring 2 is rotatable in both the forward rotation and reverse rotation directions with respect to the first inner ring 1. The first outer race 2 is configured with at least ratchet-like projections and recesses, and the first pawls 11 are configured with at least a function of engaging with or disengaging from the ratchet-like projections and recesses. The first pawl 11 and the first outer race 2 are in contact with each other under the direct action of the first return spring 4. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first inner ring 1, the first pawl 11 rotates together with the first inner ring 1, and the first pawl 11 can rotate relative to the first inner ring 1 within a certain angle range. The first pawl 11 is connected with the first left clutch bracket 5, the first pawl 11 rotates together with the first left clutch bracket 5, and the first pawl 11 can rotate relative to the first left clutch bracket 5 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first inner race 1 and rotates together with the first inner race 1. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the first return spring 4 acts on the first pawl 11, the first pawl 11 returns to the initial position under the action of the first return spring 4. Under the action of the first inner race 1, the first outer race 2, and the first return spring 4, the first pawls 11 themselves make the first outer race 2 rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 64) and fixed in the reverse rotation direction with respect to the first inner race 1. As shown in fig. 231, when the first pawls 11 are engaged with the first outer race 2, the contact pair of the first pawls 11 and the first outer race 2 has a self-locking function: the first pawl 11 is in engagement with the first outer race 2 under the action of the first return spring 4, and the engaging force between the first pawls 11 and the first outer race 2 is F, μ is the friction coefficient between the contact surfaces of the first pawls 11 and the first outer race 2, F is the friction force between the first pawls 11 and the first outer race 2, FN is the normal acting force between the first pawls 11 and the first outer race 2, and θ is the angle between F and FN, then, within a certain load range, when θ < arctan (μ), and when the engagement force F between the first pawls 11 and the first outer race 2 is large, under the action of the engaging force F, the elastic force of the first return spring 4, and the frictional force F, the first pawls 11 and the first outer race 2 do not disengage themselves. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with first inner circle 1 fixed connection, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with first inner circle 1 fixed connection. The second outer race 220 is directly or indirectly connected to a driven member (not shown) or a frame (not shown) of the machine M.

Example 8

As shown in fig. 253 to 255, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The one-way clutch mechanism 51 is shown in fig. 66 to 70. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 8 is the same as that in embodiment 3. The one-way clutch mechanism 51 in embodiment 8 is similar to embodiment 7 except that: in embodiment 8, the one-way clutch mechanism 51 is additionally provided with the first stopper pin 13 and the first auxiliary outer race 12. The first limiting pin 13 comprises a plurality of pins, and the first limiting pin 13 is directly or indirectly fixedly connected with the first outer ring 2. The first auxiliary outer race 12 is connected to the first outer race 2 by the first stopper pin 13, and the first auxiliary outer race 12 at least has a function of being rotatable with respect to the first outer race 2 within an angular range defined by the first stopper pin 13 by the direct action of the first pawl 11. The first auxiliary outer ring 12 is coaxially arranged on the left side of the first outer ring 2 in the axial direction. As shown in fig. 68 and 69, when the first outer ring 2 rotates forward (in the direction of the arrow in fig. 68) relative to the first inner ring 1, under the direct action of the first pawls 11, after the first auxiliary outer ring 12 rotates relative to the first outer ring 2 to the angle defined by the first limit pins 13, a part of the surface of the first auxiliary outer ring 12 and a part of the surface of the first outer ring 2 are spliced to form a cylindrical surface, and the first pawls 11 rotate relative to the first outer ring 2 and contact the spliced cylindrical surface, so that noise is greatly reduced.

Example 9

As shown in fig. 256 to 258, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 9 is the same as that in embodiment 3. As shown in fig. 71 to 74, the one-way clutch mechanism 51 of embodiment 9 is similar to that of embodiment 7 except that: the first pawl 11 and the first return spring 4 are both mounted on the first outer race 2. The first left clutch bracket 5 and the first right clutch bracket 6 are fixedly connected with the first outer ring 2 through the first clutch rivet 7. The first pawls 11 are in an engaged state with the first inner race 1 at an initial position, in which the first inner race 1 is fixed in the normal rotation direction (the direction indicated by the arrow in fig. 73) and rotatable in the reverse rotation direction with respect to the first outer race 2.

Example 10

As shown in fig. 259 to 261, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 10 is the same as that in embodiment 3. The one-way clutch mechanism 51 is shown in fig. 75 to 79. In embodiment 10, the one-way clutch mechanism 51 is similar to that of embodiment 9 except that: in embodiment 10, the one-way clutch mechanism 51 is additionally provided with the first stopper pin 13 and the first auxiliary inner race 14. The first limiting pin 13 comprises a plurality of pins, and the first limiting pin 13 is directly fixedly connected with the first inner ring 1. The first auxiliary inner ring 14 is connected to the first inner ring 1 through the first limit pin 13, and the first auxiliary inner ring 14 at least has a function of being rotatable relative to the first inner ring 1 within an angular range defined by the first limit pin 13 under the direct action of the first pawl 11. The first auxiliary inner ring 14 is coaxially arranged on the right side of the first inner ring 1 in the axial direction. As shown in fig. 77 and 78, when the first inner ring 1 rotates reversely (in the reverse direction of the arrow in fig. 77) with respect to the first outer ring 2, after the first auxiliary inner ring 14 rotates with respect to the first inner ring 1 to the angle defined by the first limit pin 13 under the direct action of the first pawl 11, a part of the surface of the first auxiliary inner ring 14 is spliced with a part of the surface of the first inner ring 1 to form a cylindrical surface, and the first pawl 11 rotates with respect to the first inner ring 1 to contact the spliced cylindrical surface, so that noise is greatly reduced.

Example 11

As shown in fig. 262 to 264, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The ratchet clutch mechanism 52, as shown in fig. 119 to 128, includes: the gear shifting mechanism comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first auxiliary inner ring 14, a first gear shifting sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first gear shifting cam 25, a first transmission pin 26 and a first transmission cam 28. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 11 is similar to that in embodiment 1 except that: in embodiment 11, the second outer race 220 is fixedly connected to the first outer race 2 by the first clutch rivet 7; the second friction plate 212 is connected to a driven member (not shown) of the machine M and rotates together with the driven member (not shown) of the machine M. The actuation device AM, as shown in fig. 204, includes: a third actuating motor 301, a third actuating screw 311, a third actuating nut 312, a third prevention guide rod 313 and a third shift fork 316. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch support 5, the first right clutch support 6, the first auxiliary inner ring 14, the first gear shifting sleeve 18, the first positioning mechanism 19, the first gear shifting cam 25, the first transmission cam 28 and the first inner ring 1 are coaxially arranged. The first inner ring 1, the first outer ring 2, the first return spring 4, the first left clutch support 5, the first clutch rivet 7, the first pawl 11, the first limit pin 13, the first auxiliary inner ring 14, the first gear shift sleeve 18, the first positioning mechanism 19, the second pawl 20, the second return spring 21, the first gear shift cam 25, the first transmission pin 26, and the first transmission cam 28 are arranged on the left side of the first right clutch support 6 in the axial direction. The first inner ring 1 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with 2 fixed connection of first outer lane change, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with 2 fixed connection of first outer lane. The first pawls 11 are engaged with the first inner race 1 at an initial position, in which the first inner race 1 is fixed in a reverse rotation direction (a direction opposite to that indicated by an arrow in fig. 121) with respect to the first outer race 2. The second pawls 20 are engaged with the first inner race 1 at an initial position, in which the first inner race 1 is fixed relative to the first outer race 2 in the normal rotation direction (the direction indicated by the arrow in fig. 121). The first inner race 1, the first auxiliary inner race 14, and the first shift cam 25 are configured with ratchet-like protrusions and ratchet-like recesses, and the first pawls 11 and the second pawls 20 have at least a function of engaging with or disengaging from the ratchet-like protrusions and ratchet-like recesses. The first pawls 11 include a plurality of pawls, the first pawls 11 are mounted on the first outer race 2, the first pawls 11 rotate together with the first outer race 2, and the first pawls 11 are rotatable with respect to the first outer race 2 within a certain angular range. The first pawl 11 is connected with the first left clutch bracket 5, the first pawl 11 rotates together with the first left clutch bracket 5, and the first pawl 11 can rotate relative to the first left clutch bracket 5 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The second pawls 20 include a plurality of pawls, the second pawls 20 are mounted on the first outer race 2, the second pawls 20 rotate together with the first outer race 2, and the second pawls 20 are rotatable with respect to the first outer race 2 within a certain angular range. The second pawl 20 is directly or indirectly connected with the first left clutch support 5, the second pawl 20 rotates together with the first left clutch support 5, and the second pawl 20 can rotate relative to the first left clutch support 5 within a certain angle range. The second pawl 20 is directly or indirectly connected with the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 can rotate relative to the first right clutch support 6 within a certain angle range. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first outer race 2 and rotates together with the first outer race 2. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the elastic force of the first return spring 4 on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 includes a plurality of springs, and the second return spring 21 is installed on the first outer race 2 and rotates together with the first outer race 2. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the elastic action of the second return spring 21 on the second pawl 20, the second pawl 20 is restored to the initial position by the elastic force of the second return spring 21. When the first pawls 11 are engaged with the first inner race 1, the first inner race 1 is fixed relative to the first outer race 2 in a reverse rotation direction (reverse direction indicated by an arrow in fig. 121). When the second pawls 20 are engaged with the first inner race 1, the first inner race 1 is fixed relative to the first outer race 2 in the normal rotation direction (the direction indicated by the arrow in fig. 121). When the first pawls 11 and the second pawls 20 are engaged with the first inner ring 1, the first inner ring 1 is fixed in both the normal rotation and reverse rotation directions with respect to the first outer ring 2 within a certain load range. When the first pawls 11 are engaged with the first inner race 1 and the second pawls 20 are disengaged from the first inner race 1, the first inner race 1 is fixed in the reverse rotation direction and rotatable in the normal rotation direction with respect to the first outer race 2 within a certain load range. When the first pawls 11 are disengaged from the first inner race 1 and the second pawls 20 are engaged with the first inner race 1, the first inner race 1 is fixed in the normal rotation direction and rotatable in the reverse rotation direction with respect to the first outer race 2 within a certain load range. When the first pawls 11 and the second pawls 20 are disengaged from the first inner race 1, the first inner race 1 is rotatable in both the normal rotation and reverse rotation directions with respect to the first outer race 2 within a certain load range. As shown in fig. 231, when the first pawl 11 is engaged with the first inner ring 1 (ratchet wheel), the contact pair of the first pawl 11 and the first inner ring 1 (ratchet wheel) has a self-locking function: the first pawl 11 is in an engaged state with the first inner ring 1 (ratchet wheel) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first inner ring 1 (ratchet wheel) is F, μ is a friction coefficient between the first pawl 11 and a contact surface of the first inner ring 1 (ratchet wheel), F is a friction force between the first pawl 11 and the first inner ring 1 (ratchet wheel), FN is a normal acting force between the first pawl 11 and the first inner ring 1 (ratchet wheel), θ is an included angle between F and FN, and under a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first inner ring 1 (ratchet wheel) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first inner race 1 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 is engaged with the first inner ring 1 (ratchet wheel), the contact pair of the second pawl 20 and the first inner ring 1 (ratchet wheel) has a self-locking function: the second pawl 20 is engaged with the first inner ring 1 (ratchet wheel) under the action of the first return spring 4, the engaging force between the second pawl 20 and the first inner ring 1 (ratchet wheel) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first inner ring 1 (ratchet wheel), F is the friction force between the second pawl 20 and the first inner ring 1 (ratchet wheel), FN is the normal acting force between the second pawl 20 and the first inner ring 1 (ratchet wheel), θ is the included angle between F and FN, within a certain load range, when θ < arctan (μ) and when the engaging force F between the second pawl 20 and the first inner ring 1 (ratchet wheel) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawls 20 do not disengage themselves from the first inner race 1 (ratchet). The first shifting sleeve 18 is connected to the first left clutch carrier 5 and rotates together with the first left clutch carrier 5. The first shifting sleeve 18 is connected to the first right clutch carrier 6 and rotates together with the first right clutch carrier 6. First positioning mechanism 19 directly with first left clutch bracket 5 is connected, first positioning mechanism 19 with first left clutch bracket 5 rotates together, first positioning mechanism 19 is relative in the axial first left clutch bracket 5 is fixed. The first positioning mechanism 19 is directly connected with the first gear shifting sleeve 18, the first positioning mechanism 19 has a certain limiting effect on the first gear shifting sleeve 18 in the axial direction, and the first gear shifting sleeve 18 overcomes the effect of the first positioning mechanism 19 and selectively moves relative to the first left half clutch 15 in the axial direction. The first gear shifting sleeve 18 is provided with a series of axial positioning grooves, and the first gear shifting sleeve 18 positions five axial positions thereof within a certain range through the constraint action of the series of axial positioning grooves and the first positioning mechanism 19. The first drive pin 26 is fixedly connected to the first shift sleeve 18, and the first drive pin 26 moves back and forth with the first shift sleeve 18 in a certain range along the axial direction of the first shift sleeve 18. The first transmission pin 26 is directly connected with the first transmission cam 28 and forms a screw transmission pair, and the first transmission pin 26 moves axially in a certain range to push the first transmission cam 28 to rotate in a certain angle range relative to the first outer ring 2. The first transmission cam 28 is connected to the first outer ring 2, and the first transmission cam 28 is rotatable with respect to the first outer ring 2 within a certain angle range. The first transmission cam 28 is connected to the first left clutch carrier 5, and the first transmission cam 28 is rotatable within a certain angle range relative to the first left clutch carrier 5. The first transmission cam 28 is connected to the first right clutch carrier 6, and the first transmission cam 28 is rotatable within a certain angle range with respect to the first right clutch carrier 6. The first shift cam 25 is fixedly connected to the first transmission cam 28, and the first shift cam 25 is rotatable with the first transmission cam 28 within a certain angle range relative to the first outer ring 2. The first shift cam 25 is directly connected to the first right clutch carrier 6, and the first shift cam 25 is rotatable within a certain angular range with respect to the first right clutch carrier 6. The first shift cam 25 is connected to the first pawl 11, and the first pawl 11 can be engaged or disengaged with the first inner race 1 by the drive of the first shift cam 25. The first shift cam 25 is connected to the second pawl 20, and the second pawl 20 can be brought into an engaged or disengaged state with the first inner race 1 by the drive of the first shift cam 25. The first limiting pin 13 comprises a plurality of pins, and the first limiting pin 13 is fixedly connected with the first inner ring 1. The first auxiliary inner ring 14 is connected to the first inner ring 1 by the first stopper pin 13, and the first auxiliary inner ring 14 at least has a function of being rotatable with respect to the first inner ring 1 within an angular range defined by the first stopper pin 13 by the first pawl 11 or the second pawl 20. The first auxiliary inner ring 14 is coaxially arranged on the right side of the first inner ring 1 in the axial direction. The third actuator motor 301 is a power source of the actuator AM, a housing of the third actuator motor 301 is fixedly connected to a frame (not shown) of the machine M, a rotor of the third actuator motor 301 is fixedly connected to the third actuator screw 311 in a rotation direction, and the third actuator screw 311 rotates together with the rotor of the third actuator motor 301. The third actuating screw 311 is connected with the third actuating nut 312 through a screw pair. The third actuator nut 312 moves axially relative to the frame of the machine M. The third actuating nut 312 is fixedly connected with the third prevention guide rod 313, and the third prevention guide rod 313 moves in the axial direction relative to the frame of the machine M. The third actuator nut 312 is fixedly connected to the third shift fork 316. The third shift fork 316 is connected to the first shift sleeve 18, and the first shift sleeve 18 is selectively axially moved within a certain range with respect to the first left clutch carrier 5 by the third shift fork 316. The third actuating motor 301 sequentially passes through the third actuating screw 311, the third actuating nut 312, the third shift fork 316, the first shift sleeve 18, the first transmission pin 26 and the first transmission cam 28 to be connected with the first shift cam 25, and the first shift cam 25 is driven by the third actuating motor 301 indirectly to rotate relative to the first outer ring 2. The first positioning mechanism 19 is connected to the first shift cam 25 sequentially through the first shift sleeve 18, the first drive pin 26, and the first drive cam 28. When the action of the third actuator motor 301 on the first shift cam 25 is small, the first shift cam 25 has five determined angular rotational positions with respect to the first outer ring 2 under the indirect action of the first positioning mechanism 19: the middle position, the left 10 degree position, the right 10 degree position, the left 20 degree position, and the right 20 degree position are shown in fig. 121 to 125, respectively. When the third actuator motor 301 has a greater effect on the first shift cam 25, the first shift cam 25 rotates relative to the first outer race 2 from one of the angular rotational positions to the other angular rotational position. As shown in fig. 121, when the first shift cam 25 rotates to the intermediate position with respect to the first outer race 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, the first shift cam 25 does not restrain the first pawl 11 and the second pawl 20, the first pawl 11 and the second pawl 20 are both in the initial positions, at this time, the first pawl 11 is in the engaged state with the first inner race 1 under the action of the first return spring 4, the second pawl 20 is in the engaged state with the first inner race 1 under the action of the second return spring 21, and at this time, the first inner race 1 is fixed with respect to the first outer race 2 in both the forward rotation direction (the direction indicated by the arrow in fig. 121) and the reverse rotation direction. As shown in fig. 122, when the first shift cam 25 rotates to the left 10 degrees position relative to the first outer race 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, the first shift cam 25 has no binding action on the first pawl 11, the first pawl 11 is in an engaged state with the first inner race 1 under the action of the first return spring 4, and the second pawl 20 is in a disengaged state with the first inner race 1 under the action of the first shift cam 25. Then the first inner race 1 is fixed in the reverse rotation direction (the reverse direction indicated by the arrow in fig. 122) with respect to the first outer race 2, but the first inner race 1 is rotatable in the forward rotation direction (the direction indicated by the arrow in fig. 122) with respect to the first outer race 2. As shown in fig. 124, when the first shift cam 25 rotates to the right 10 degree position relative to the first outer race 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, the first pawl 11 is in a disengaged state from the first inner race 1 under the action of the first shift cam 25, the first shift cam 25 has no binding action on the second pawl 20, and the second pawl 20 is in an engaged state with the first inner race 1 under the action of the second return spring 21. Then the first inner ring 1 is fixed in the normal rotation direction (the direction indicated by the arrow in fig. 124) with respect to the first outer ring 2, but the first inner ring 1 is rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 124) with respect to the first outer ring 2. As shown in fig. 123, when the first shift cam 25 is rotated to the left 20 degree position with respect to the first outer race 2 by the indirect action of the third actuator motor 301 and the first positioning mechanism 19, the first pawls 11 and the second pawls 20 are in a disengaged state from the first inner race 1 by the action of the first shift cam 25. The first inner race 1 is rotatable in both the normal rotation direction (the direction indicated by the arrow in fig. 123) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 123) with respect to the first outer race 2. As shown in fig. 125, when the first shift cam 25 rotates to the right 20 degree position relative to the first outer race 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, the first pawls 11 and the second pawls 20 are in a disengaged state from the first inner race 1 under the action of the first shift cam 25. The first inner race 1 is rotatable in both the forward rotation direction (indicated by an arrow in fig. 125) and the reverse rotation direction (indicated by an arrow in fig. 125) with respect to the first outer race 2. As shown in fig. 122 and 126, when the first shift cam 25 rotates to the left 10 degrees position relative to the first outer ring 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, and when the first inner ring 1 rotates in the forward direction (the direction indicated by the arrow in fig. 122) relative to the first outer ring 2, after the first auxiliary inner ring 14 rotates to the angle defined by the first limit pin 13 relative to the first inner ring 1 under the direct action of the first pawl 11, a part of the surface of the first auxiliary inner ring 14 is split into a cylindrical surface with a part of the surface of the first inner ring 1, and the first pawl 11 rotates relative to the first inner ring 1 and contacts with the split cylindrical surface, so that noise is greatly reduced. As shown in fig. 124 and 127, when the first shift cam 25 rotates to the right 10 degrees position relative to the first outer ring 2 under the indirect action of the third actuator motor 301 and the first positioning mechanism 19, and when the first inner ring 1 rotates in the reverse direction (the reverse direction of the arrow shown in fig. 124) relative to the first outer ring 2, after the first auxiliary inner ring 14 rotates to the angle defined by the first limit pin 13 relative to the first inner ring 1 under the direct action of the second pawl 20, a part of the surface of the first auxiliary inner ring 14 is split into a cylindrical surface with a part of the surface of the first inner ring 1, and the second pawl 20 rotates relative to the first inner ring 1 and contacts with the split cylindrical surface, so that noise is greatly reduced.

Example 12

As shown in fig. 265 to 267, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The ratchet clutch mechanism 52 is shown in FIGS. 129 to 138. The cushion damper device DM is shown in fig. 11 to 13. The actuator AM, as shown in fig. 209, includes: a third actuating motor 301, a third actuating screw 311, a third actuating nut 312, a third anti-rotation guide rod 313, a third actuating pin 314 and a third actuating connecting rod 315. The ratchet clutch mechanism 52 in embodiment 12 is similar to that in embodiment 11, except that: in embodiment 12, the first shift sleeve 18, the first drive pin 26, and the first drive cam 28 are eliminated from the ratchet clutch mechanism 52; the first positioning mechanism 19 is fixedly connected with the first outer ring 2; the first positioning mechanism 19 is connected with the first shift cam 25; the first shift cam 25 interacts with the first shift cam 25 through a series of radial grooves to rotate the first shift cam 25 to five determined angular positions relative to the first outer race 2 under the driving of the third actuator motor 301, so that the first pawls 11 and the second pawls 20 are respectively engaged or disengaged with the first inner race 1, thereby allowing the shifting device GD to have a plurality of clutching states. The cushion damper device DM in embodiment 12 is similar to that in embodiment 11 except that: in embodiment 12, the second friction plate 212 is fixedly connected to a frame (not shown) of the machine M. The third actuator motor 301 is a power source of the actuator AM, a housing of the third actuator motor 301 is fixedly connected to a frame (not shown) of the machine M, a rotor of the third actuator motor 301 is connected to the third actuator screw 311, and the third actuator screw 311 rotates together with the rotor of the third actuator motor 301. The third actuating screw 311 is connected with the third actuating nut 312 through a screw pair. The third actuator nut 312 moves axially relative to the frame (not shown) of the machine M. The third actuating nut 312 is fixedly connected with the third anti-rotation guide rod 313, and the third anti-rotation guide rod 313 moves along the axial direction of the third anti-rotation guide rod 313 relative to the frame (not shown) of the machine M. The third actuator nut 312 is fixedly connected to the third actuator link 315. The third actuating link 315 is fixedly connected to the third actuating pin 314. The third actuating pin 314 is directly connected to the first shift cam 25 and the first shift cam 25 is rotatable relative to the first outer ring 2 under the direct action of the third actuating pin 314. The third actuator motor 301 is connected to the first shift cam 25 sequentially through the third actuator screw 311, the third actuator nut 312, the third actuator link 315, and the third actuator pin 314, and the first shift cam 25 is driven by the third actuator motor 301 indirectly to rotate relative to the first outer ring 2. When the action of the third actuator motor 301 on the first shift cam 25 is small, the first shift cam 25 has five determined angular rotational positions with respect to the first outer ring 2 under the direct action of the first positioning mechanism 19: the middle position, the left 10 degree position, the right 10 degree position, the left 20 degree position, and the right 20 degree position are shown in fig. 127 to 131, respectively. When the third actuator motor 301 has a greater effect on the first shift cam 25, the first shift cam 25 rotates relative to the first outer race 2 from one of the angular rotational positions to the other angular rotational position.

Example 13

As shown in fig. 268 to 270, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 13 is the same as that in embodiment 11. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 13 is the same as in embodiment 11. As shown in fig. 115 to 118, the ratchet clutch mechanism 52 includes: the gear shifting mechanism comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first gear shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21 and a first lever mechanism 27. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch bracket 5, the first right clutch bracket 6, the first shift gear sleeve 18, and the first positioning mechanism 19 are coaxially arranged with the first inner ring 1. The first inner race 1, the first outer race 2, the first return spring 4, the first left clutch support 5, the first pawl 11, the first shift gear sleeve 18, the first positioning mechanism 19, the second pawl 20, the second return spring 21, and the first lever mechanism 27 are arranged on the left side of the first right clutch support 6 in the axial direction. The first inner ring 1 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. The first inner race 1 is configured with at least ratchet-like protrusions and ratchet-like recesses, and the first pawls 11 and the second pawls 20 are configured to have at least a function of engaging with or disengaging from the ratchet-like protrusions and ratchet-like recesses. The first pawls 11 and the second pawls 20 are engaged with the first inner ring 1 at the initial position, and the first inner ring 1 is fixed to the first outer ring 2 in both the forward rotation (the direction indicated by the arrow in fig. 117) and the reverse rotation. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with 2 fixed connection in first outer lane. The first pawls 11 include a plurality of pawls, the first pawls 11 are mounted on the first outer race 2, the first pawls 11 rotate together with the first outer race 2, and the first pawls 11 are rotatable with respect to the first outer race 2 within a certain angular range. The first pawl 11 is directly connected with the first left clutch support 5, the first pawl 11 rotates together with the first left clutch support 5, and the first pawl 11 can rotate relative to the first left clutch support 5 within a certain angle range. The first pawl 11 is directly connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The second pawls 20 include a plurality of pawls, the second pawls 20 are mounted on the first outer race 2, the second pawls 20 rotate together with the first outer race 2, and the second pawls 20 are rotatable with respect to the first outer race 2 within a certain angular range. The second pawl 20 is directly connected with the first left clutch support 5, the second pawl 20 rotates together with the first left clutch support 5, and the second pawl 20 can rotate relative to the first left clutch support 5 within a certain angle range. The second pawl 20 is directly connected to the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first outer race 2 and rotates together with the first outer race 2. The first return spring 4 is connected to a first pawl 11, and when the effect of other restraint or load on the first pawl 11 is smaller than the elastic effect of the first return spring 4 on the first pawl 11, the first pawl 11 is restored to the initial position by the elastic force of the first return spring 4. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first outer race 2 and rotates together with the first outer race 2. The second return spring 21 is connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the elastic action of the second return spring 21 on the second pawl 20, the second pawl 20 returns to the initial position under the elastic action of the second return spring 21. When the first pawls 11 and the second pawls 20 are engaged with the first inner race 1, the first inner race 1 is fixed in both the forward rotation (the direction indicated by the arrow in fig. 117) and the reverse rotation with respect to the first outer race 2 within a certain load range. When the first pawls 11 and the second pawls 20 are disengaged from the first inner race 1, the first inner race 1 is rotatable in both the forward rotation (the direction indicated by the arrow in fig. 117) and the reverse rotation with respect to the first outer race 2 within a certain load range. As shown in fig. 231, when the first pawl 11 is engaged with the first inner ring 1 (ratchet wheel), the contact pair of the first pawl 11 and the first inner ring 1 (ratchet wheel) has a self-locking function: the first pawl 11 is in an engaged state with the first inner ring 1 (ratchet wheel) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first inner ring 1 (ratchet wheel) is F, μ is a friction coefficient between the first pawl 11 and a contact surface of the first inner ring 1 (ratchet wheel), F is a friction force between the first pawl 11 and the first inner ring 1 (ratchet wheel), FN is a normal acting force between the first pawl 11 and the first inner ring 1 (ratchet wheel), θ is an included angle between F and FN, and under a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first inner ring 1 (ratchet wheel) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first inner race 1 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 is engaged with the first inner ring 1 (ratchet wheel), the contact pair of the second pawl 20 and the first inner ring 1 (ratchet wheel) has a self-locking function: the second pawl 20 is engaged with the first inner ring 1 (ratchet wheel) under the action of the first return spring 4, the engaging force between the second pawl 20 and the first inner ring 1 (ratchet wheel) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first inner ring 1 (ratchet wheel), F is the friction force between the second pawl 20 and the first inner ring 1 (ratchet wheel), FN is the normal acting force between the second pawl 20 and the first inner ring 1 (ratchet wheel), θ is the included angle between F and FN, within a certain load range, when θ < arctan (μ) and when the engaging force F between the second pawl 20 and the first inner ring 1 (ratchet wheel) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawls 20 do not disengage themselves from the first inner race 1 (ratchet). The first shift sleeve 18 is connected to the first outer ring 2 and rotates together with the first outer ring 2. The first positioning mechanism 19 is connected with the first outer ring 2, the first positioning mechanism 19 rotates with the first outer ring 2, and the first positioning mechanism 19 is axially fixed relative to the first outer ring 2. The first positioning mechanism 19 is directly connected to the first shifting sleeve 18, and the first positioning mechanism 19 has a certain limiting effect on the first shifting sleeve 18 in the axial direction, and the first shifting sleeve 18 overcomes the effect of the first positioning mechanism 19 and selectively moves relative to the first outer ring 2 in the axial direction. Two axial positioning grooves are formed in the first gear shifting gear sleeve 18, and the first positioning mechanism 19 positions two axial positions of the first gear shifting gear sleeve 18 through the action of the two axial positioning grooves. The first lever mechanism 27 includes a plurality of levers, the first lever mechanism 27 is connected to the first outer race 2 and rotates together with the first outer race 2, and the first lever mechanism 27 is rotatable with respect to the first outer race 2 within a certain angular range. The first shift sleeve 18 is connected to the first pawl 11 via the first lever mechanism 27, and selective axial movement of the first shift sleeve 18 relative to the first outer race 2 within a range brings the first pawl 11 into engagement or disengagement with the first inner race 1 via the first lever mechanism 27. The first shift sleeve 18 is connected to the second pawl 20 via the first lever mechanism 27, and selective axial movement of the first shift sleeve 18 relative to the first outer race 2 within a range brings the second pawl 20 into engagement or disengagement with the first inner race 1 via the first lever mechanism 27. The third shift fork 316 is connected to the first shift sleeve 18, and the first shift sleeve 18 is selectively axially moved within a range with respect to the first outer ring 2 by the third shift fork 316. When the first shift sleeve 18 is located at the left position of the two axial positions axially relative to the first outer ring 2 under the action of the third shift fork 316, the first lever mechanism 27 has no constraint action on the first pawl 11 and the second pawl 20, the first pawl 11 is in an engaged state with the first inner ring 1 under the action of the first return spring 4, and the second pawl 20 is in an engaged state with the first inner ring 1 under the action of the second return spring 21, at this time, the first inner ring 1 is fixed in both forward rotation (the direction indicated by the arrow in fig. 117) and reverse rotation directions relative to the first outer ring 2. When the first shift sleeve 18 is located at the right position of the two axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, the first pawl 11 is in a separated state from the first inner ring 1 under the action of the first lever mechanism 27, and the second pawl 20 is in a separated state from the first inner ring 1 under the action of the first lever mechanism 27, at this time, the first inner ring 1 is rotatable in both forward rotation (the direction indicated by the arrow in fig. 117) and reverse rotation directions relative to the first outer ring 2.

Example 14

As shown in fig. 271 to 273, the shift device GD includes: lever clutch mechanism 55, actuating means AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 14 is the same as in embodiment 11. As shown in fig. 202 to 204, the lever clutch mechanism 55 includes: the clutch comprises a first inner ring 1, a first outer ring 2, a first return spring 4, a first left clutch support 5, a first clutch rivet 7, a first gear shifting sleeve 18, a first positioning mechanism 19, a first lever mechanism 27, a first friction plate 33, a first pair of coupling plates 34, a first compensation spring 35, a first left bearing plate 36, a first right bearing plate 37, a first right snap ring 38 and a first left flange 39. The first outer ring 2 is arranged coaxially outside the first inner ring 1 in the radial direction. The first outer ring 2, the first left clutch support 5, the first gear shifting gear sleeve 18, the first positioning mechanism 19, the first friction plate 33, the first dual plate 34, the first compensating spring 35, the first left bearing plate 36, the first right bearing plate 37, the first right snap ring 38, the first left flange 39 and the first inner ring 1 are coaxially arranged. The first inner ring 1, the first outer ring 2, the first return spring 4, the first left clutch support 5, the first gear shifting gear sleeve 18, the first positioning mechanism 19, the first lever mechanism 27, the first friction plate 33, the first pair of coupling plates 34, the first compensation spring 35, the first left bearing plate 36, the first right bearing plate 37, and the first right snap ring 38 are arranged on the right side of the first left flange 39. The first inner ring 1 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. The first left flange 39 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. In the initial position, the first lever mechanism 27 separates the first friction plate 33 from the first coupling plate 34, and the first inner race 1 is rotatable in both forward rotation (direction indicated by arrow in fig. 202) and reverse rotation relative to the first left flange 39. The first clutch rivet 7 comprises a plurality of rivets, and the first left clutch bracket 5 and the first left flange 39 are both fixedly connected with the first outer ring 2 through the first clutch rivet 7. The first lever mechanism 27 comprises a plurality of levers, the first lever mechanism 27 is directly connected with the first left clutch bracket 5, the first lever mechanism 27 rotates together with the first left clutch bracket 5, and the first lever mechanism 27 can rotate relative to the first left clutch bracket 5 within a certain angle range under the direct action of the first shifting gear sleeve 18. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first outer race 2 and rotates together with the first outer race 2. The first return spring 4 is connected to the first lever mechanism 27, and when the other restraint or load acts on the first lever mechanism 27 less than the first return spring 4 acts on the first lever mechanism 27, the first lever mechanism 27 returns to the initial position under the action of the first return spring 4. When the first friction plates 33 are engaged with the first pair of friction plates 34, the first inner ring 1 is fixed relative to the first outer ring 2 in both the normal rotation (the direction indicated by the arrow in fig. 202) and the reverse rotation directions within a certain load range. When the first friction plate 33 is separated from the first pair of friction plates 34, the first inner race 1 is rotatable in both the forward rotation (direction indicated by an arrow in fig. 202) and reverse rotation directions with respect to the first outer race 2 within a certain load range. The first shift sleeve 18 is connected to the first outer ring 2 and rotates together with the first outer ring 2. The first positioning mechanism 19 is connected with the first outer ring 2, the first positioning mechanism 19 rotates with the first outer ring 2, and the first positioning mechanism 19 is axially fixed relative to the first outer ring 2. Three axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions three axial positions of the first gear shifting gear sleeve 18 through the three axial positioning grooves. The first friction plate 33 includes a plurality of friction plates, and the first counter plate 34 includes a plurality of counter plates. The first shift sleeve 18 is directly connected to the first lever mechanism 27, and the first shift sleeve 18 is selectively axially moved relative to the first outer race 2 within a range to push the first lever mechanism 27 to bring the first friction plate 33 into engagement or disengagement with the first counter plate 34. The first compensation spring 35 is connected to the first lever mechanism 27 and rotates together with the first outer ring 2. The first left bearing plate 36 is connected to the first compensation spring 35 and rotates together with the first outer race 2. The first right snap ring 38 is connected to the first outer ring 2, and the first right snap ring 38 is fixed in the axial direction with respect to the first outer ring 2. The first right bearing plate 37 is connected to the first right snap ring 38 and rotates together with the first right snap ring 38. The first lever mechanism 27 sequentially presses or releases the first friction plate 33 and the first counter plate 34 through the first compensating spring 35, the first left bearing plate 36, and the first right bearing plate 37, so that the first friction plate 33 and the first counter plate 34 are in an engaged or disengaged state. The first compensation spring 35 has at least a function of compensating to some extent a reduction in axial thickness of the first friction plate 33, the first counter plate 34, the first left bearing plate 36, and the first right bearing plate 37 due to wear. The third shift fork 316 is connected to the first shift sleeve 18, and the first shift sleeve 18 is selectively axially moved within a range with respect to the first outer ring 2 by the third shift fork 316. When the first shift sleeve 18 is located at the left position of the three axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 has a small constraint effect on the first lever mechanism 27, and then the first lever mechanism 27 enables the first friction plate 33 and the first counter plate 34 to be in a separated state under the action of the first return spring 4, at this time, the first inner ring 1 can rotate in both forward and reverse directions relative to the first outer ring 2. When the first shift sleeve 18 is located at a middle position of the three axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, the first lever mechanism 27 enables the first friction plate 33 and the first coupling plate 34 to be in an engaged state under the action of the first shift sleeve 18, at this time, the first inner ring 1 is fixed relative to the first outer ring 2 in both forward and reverse directions within a certain load range, that is, a small motion, power or torque can be transmitted between the first inner ring 1 and the first outer ring 2 at this time. When the motion, power or torque to be transmitted is large, or the vibration and impact during the motion, power or torque transmission are large, the first friction plate 33 and the first pair of friction plates 34 are damped or eliminated in the form of sliding friction. When the first shift sleeve 18 is located at the right position of the three axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, the acting force of the first shift sleeve 18 on the first lever mechanism 27 is large, the first lever mechanism 27 enables the first friction plate 33 and the first counter plate 34 to be in an engaged state under the action of the first shift sleeve 18, at this time, the first inner ring 1 is fixed relative to the first outer ring 2 in the forward rotation direction and the reverse rotation direction in a large load range, that is, at this time, a large torque can be transmitted between the first inner ring 1 and the first outer ring 2.

Example 15

As shown in fig. 274 to 276, the shift device GD includes: lever clutch mechanism 55, actuating means AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 15 is the same as embodiment 11. The lever clutch mechanism 55 is shown in fig. 205 to 207. The lever clutch mechanism 55 in embodiment 15 is similar to that in embodiment 14 except that: in embodiment 15, the first compensation spring 35 is eliminated from the lever clutch mechanism 55; the first lever mechanism 27 is connected to a first left bearing plate 36, and the first lever mechanism 27 sequentially presses or releases the first friction plate 33 and the first counter plate 34 through the first left bearing plate 36 and the first right bearing plate 37, so that the first friction plate 33 and the first counter plate 34 are in an engaged or disengaged state.

Example 16

As shown in fig. 277 to 279, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 16 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 16 is the same as that in embodiment 3. As shown in fig. 186 to 187, the jaw clutch mechanism 53 includes: the gear shifting device comprises a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18 and a first positioning mechanism 19. The first right half clutch 16, the first gear shifting sleeve 18, the first positioning mechanism 19 and the first left half clutch 15 are coaxially arranged. The first right half clutch 16, the first positioning mechanism 19 and the first shifting gear sleeve 18 are axially arranged on the right side of the first left half clutch 15. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right clutch half 16 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. The first left clutch half 15 is configured with a claw-like projection or recess, and the first shift sleeve 18 is configured to have a function of engaging with or disengaging from the claw-like projection or recess. When the first shift sleeve 18 is engaged with the first left clutch half 15, the first left clutch half 15 is fixed in both the forward rotation (direction indicated by arrow in fig. 186) and reverse rotation directions relative to the first right clutch half 16 within a certain load range. When the first shift sleeve 18 is disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in both forward (direction indicated by arrow in fig. 186) and reverse directions relative to the first right clutch half 16 within a certain load range. The first gear shift sleeve 18 is connected to the first right clutch half 16 and rotates together with the first right clutch half 16, and the first gear shift sleeve 18 can move back and forth in the axial direction relative to the first right clutch half 16 under the action of the third gear shift fork 316. First positioning mechanism 19 with first right side half separation and reunion 16 is connected, first positioning mechanism 19 with first right side half separation and reunion 16 rotates together, first positioning mechanism 19 is relative in the axial first right side half separation and reunion 16 is fixed. Two axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions two axial positions of the first gear shifting gear sleeve 18 through the two axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, and the first shift sleeve 18 is selectively engaged and disengaged with the first left clutch half 15 by the third shift fork 316. When the first shift sleeve 18 is located at the left position of the two axial positions relative to the first right half clutch 16 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 and the first left half clutch 15 are in a separated state, and at this time, the first left half clutch 15 is rotatable in both forward rotation (the direction indicated by the arrow in fig. 186) and reverse rotation directions relative to the first right half clutch 16. When the first shift sleeve 18 is located at the right position of the two axial positions relative to the first right half clutch 16 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 and the first left half clutch 15 are in the engaged state, and at this time, the first left half clutch 15 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 186) and the reverse rotation direction relative to the first right half clutch 16.

Example 17

As shown in fig. 280 to 282, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 17 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 17 is the same as that in embodiment 3. The jaw clutch mechanism 53 is shown in fig. 190 to 191. The dog clutch mechanism 53 in embodiment 17 is similar to that in embodiment 16, except that: the first shift sleeve 18 of the embodiment 17 is configured with an axial male tooth structure, and the first left clutch half 15 is configured with a female groove structure that engages with or disengages from the axial male tooth structure, and the engagement and disengagement of the first shift sleeve 18 with the first left clutch half 15 is achieved by the engagement and disengagement of the axial male tooth structure with the female groove structure.

Example 18

As shown in fig. 283 to 285, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 18 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 18 is the same as that in embodiment 3. The jaw clutch mechanism 53 is shown in FIGS. 192 to 193. The dog clutch mechanism 53 in embodiment 18 is similar to that in embodiment 16, except that: the first shift sleeve 18 of the embodiment 18 is configured with a radial tooth structure, and the first left clutch half 15 is configured with a groove structure engaged with or disengaged from the radial tooth structure, and the engagement and disengagement of the first shift sleeve 18 and the first left clutch half 15 are realized by the engagement and disengagement of the radial tooth structure and the groove structure.

Example 19

As shown in fig. 286 to 288, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 19 is the same as that in embodiment 3. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 18 is the same as in embodiment 11. The jaw clutch mechanism 53, as shown in fig. 194 to 195, includes: the gear shifting device comprises a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18, a first positioning mechanism 19 and a first middle clutch 23. The first gear shifting gear sleeve 18, the first positioning mechanism 19, the first left half clutch 15, the first right half clutch 16 and the first middle clutch 23 are coaxially arranged. The first right half clutch 16, the first gear shift sleeve 18, the first positioning mechanism 19 and the first intermediate clutch 23 are arranged on the right side of the first left half clutch 15. The first left clutch half 15 passes coaxially through the first right clutch half 16. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right half clutch 16 is connected to the second friction plate 212 and rotates together with the second friction plate 212. The first intermediate clutch 23 is directly or indirectly connected to a driving member (not shown) of the machine M and rotates together with the driving member (not shown) of the machine M. The first left clutch half 15 and the first right clutch half 16 are configured with a claw-like projection and a groove, and the first shift sleeve 18 is configured to have at least a function of engaging with or disengaging from the claw-like projection and the groove. When the first shift sleeve 18 is engaged with the first left clutch half 15, the first left clutch half 15 is fixed in both the forward rotation (direction indicated by arrow in fig. 194) and reverse rotation directions relative to the first intermediate clutch 23 within a certain load range. When the first shift sleeve 18 is engaged with the first right clutch half 16, the first right clutch half 16 is fixed in both the forward rotation (direction indicated by an arrow in fig. 194) and the reverse rotation with respect to the first intermediate clutch 23 in a certain load range. When the first shift sleeve 18 is disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in both forward (direction indicated by arrow in fig. 194) and reverse directions relative to the first intermediate clutch 23 within a certain load range. When the first shift sleeve 18 is disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in both forward (direction indicated by arrow in fig. 194) and reverse directions relative to the first intermediate clutch 23 within a certain load range. The first shift sleeve 18 is connected to the first intermediate clutch 23 and rotates together with the first intermediate clutch 23, and the first shift sleeve 18 can move axially back and forth relative to the first intermediate clutch 23 under the action of the third shift fork 316. The first positioning mechanism 19 is connected with the first intermediate clutch 23, the first positioning mechanism 19 rotates together with the first intermediate clutch 23, and the first positioning mechanism 19 is axially fixed relative to the first intermediate clutch 23. Three axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions three axial positions of the first gear shifting gear sleeve 18 through the three axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, and the first shift sleeve 18 is selectively engaged with or disengaged from the first left half clutch 15 and the first right half clutch 16, respectively, by the driving of the third shift fork 316. When the first shift sleeve 18 is located at a middle position of three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18, the first left half clutch 15 and the first right half clutch 16 are both in a separated state, and at this time, the first left half clutch 15 and the first right half clutch 16 are both rotatable in forward and reverse directions relative to the first intermediate clutch 23. When the first shift sleeve gear 18 is located at a left position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve gear 18 and the first left-half clutch 15 are in an engaged state, and the first shift sleeve gear 18 and the first right-half clutch 16 are in a disengaged state, at this time, the first left-half clutch 15 is fixed in the forward rotation direction and the reverse rotation direction relative to the first intermediate clutch 23, and the first right-half clutch 16 is rotatable in the forward rotation direction and the reverse rotation direction relative to the first intermediate clutch 23. When the first shift sleeve 18 is located at the right position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 and the first right half clutch 16 are in an engaged state, and the first shift sleeve 18 and the first left half clutch 15 are in a disengaged state, at this time, the first right half clutch 16 is fixed in the forward and reverse directions relative to the first intermediate clutch 23, and the first left half clutch 15 is rotatable in the forward and reverse directions relative to the first intermediate clutch 23.

Example 20

As shown in fig. 289 to 291, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 20 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 20 is the same as that in embodiment 3. The jaw clutch mechanism 53 is shown in FIGS. 188 to 189. The dog clutch mechanism 53 in embodiment 20 is similar to that in embodiment 16, except that: the first shift sleeve 18 and the first left-half clutch 15 in the embodiment 20 are each configured with an axial spline structure, and engagement and disengagement of the first shift sleeve 18 and the first left-half clutch 15 are achieved by engagement and disengagement of the axial spline structure.

Example 21

As shown in fig. 292 to 294, the shift device GD includes: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 21 is the same as embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 21 is the same as that in embodiment 1. The dog clutch mechanism 53 is shown in fig. 196 to 197. The dog clutch mechanism 53 in embodiment 21 is similar to embodiment 19 except that: the first shift sleeve 18, the first left-half clutch 15, and the first right-half clutch 16 in embodiment 21 are each configured with an axial spline structure, and engagement and disengagement of the first shift sleeve 18 and the first left-half clutch 15 are achieved by engagement and disengagement of the axial spline structure, and engagement and disengagement of the first shift sleeve 18 and the first right-half clutch 16 are achieved by engagement and disengagement of the axial spline structure, respectively. The first left-half clutch 15 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. The first right half clutch 16 is directly or indirectly connected to and rotates with another driven member (not shown) of the machine M. The first intermediate clutch 23 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212.

Example 22

As shown in fig. 295 to 297, a shift device GD includes: gear clutch mechanism 54, damping device DM, and actuator AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 22 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 22 is the same as in embodiment 1. As shown in fig. 198 to 199, the gear clutch mechanism 54 includes: the gear shifting device comprises a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18 and a first positioning mechanism 19. The first gear shift sleeve 18 and the first positioning mechanism 19 are arranged coaxially with the first right half clutch 16. The first left clutch half 15 and the first right clutch half 16 are arranged non-coaxially. The first right half clutch 16, the first positioning mechanism 19 and the first shifting gear sleeve 18 are arranged on the right side of the first left half clutch 15. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right half clutch 16 is directly or indirectly connected with a driven member (not shown) of the machine M and rotates together with the driven member (not shown) of the machine M. The first left clutch half 15 is configured with tooth-like projections and recesses, and the first shift sleeve 18 has the function of engaging with or disengaging from the tooth-like projections and recesses. When the first shift sleeve 18 is engaged with the first left clutch half 15, the first left clutch half 15 is fixed in both the forward rotation (direction indicated by arrow in fig. 198) and reverse rotation directions relative to the first right clutch half 16 within a certain load range. When the first shift sleeve 18 is disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in both forward (direction indicated by arrow in fig. 198) and reverse directions relative to the first right clutch half 16 within a certain load range. The first gear shift sleeve 18 is connected to the first right clutch half 16 and rotates together with the first right clutch half 16, and the first gear shift sleeve 18 can move back and forth in the axial direction relative to the first right clutch half 16 under the action of the third gear shift fork 316. First positioning mechanism 19 directly or indirectly with first right side half separation and reunion 16 is connected, first positioning mechanism 19 with first right side half separation and reunion 16 rotates together, first positioning mechanism 19 is relative in the axial first right side half separation and reunion 16 is fixed. Two axial positioning grooves are formed in the first shift sleeve 18, the first positioning mechanism 19 is connected to the first shift sleeve 18, and the first positioning mechanism 19 positions two axial positions of the first shift sleeve 18 in the axial direction through the two axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, and the first shift sleeve 18 is selectively engaged and disengaged with the first left clutch half 15 by the third shift fork 316. When the first shift sleeve 18 is located at the left position of the two axial positions relative to the first right half clutch 16 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 and the first left half clutch 15 are in a separated state, and at this time, the first left half clutch 15 can rotate in the forward rotation direction and the reverse rotation direction relative to the first right half clutch 16. When the first shift sleeve 18 is located at the right position of the two axial positions relative to the first right half clutch 16 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18 and the first left half clutch 15 are in an engaged state, and at this time, the first left half clutch 15 is fixed relative to the first right half clutch 16 in both forward and reverse directions.

Example 23

As shown in fig. 298 to 300, the shift device GD includes: gear clutch mechanism 54, damping device DM, and actuator AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 23 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 23 is the same as that in embodiment 1. As shown in fig. 200 to 201, the gear clutch mechanism 54 includes: the gear shifting device comprises a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18, a first positioning mechanism 19 and a first middle clutch 23. The first shifting sleeve 18 and the first positioning mechanism 19 are arranged coaxially with the first intermediate clutch 23. The first left clutch half 15 is arranged non-coaxially with the first intermediate clutch 23. The first right half clutch 16 is arranged non-coaxially with the first intermediate clutch 23. The first right half clutch 16, the first gear shift sleeve 18, the first positioning mechanism 19 and the first intermediate clutch 23 are arranged on the right side of the first left half clutch 15. The first left-half clutch 15 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. The first right half clutch 16 is directly or indirectly connected to and rotates with another driven member (not shown) of the machine M. The first intermediate clutch 23 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first left clutch half 15 and the first right clutch half 16 are configured with tooth-shaped protrusions and grooves, and the first shift sleeve gear 18 has a function of engaging with or disengaging from the tooth-shaped protrusions and grooves. When the first shift sleeve 18 is engaged with the first left clutch half 15, the first left clutch half 15 is fixed in both the forward rotation (direction indicated by arrow in fig. 200) and reverse rotation directions relative to the first intermediate clutch 23 within a certain load range. When the first shift sleeve 18 is engaged with the first right clutch half 16, the first right clutch half 16 is fixed in both the forward rotation (direction indicated by arrow in fig. 200) and reverse rotation directions with respect to the first intermediate clutch 23 within a certain load range. When the first shift sleeve 18 is disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in both forward (direction indicated by arrow in fig. 200) and reverse directions relative to the first intermediate clutch 23 within a certain load range. When the first shift sleeve 18 is disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in both forward (direction indicated by arrow in fig. 200) and reverse directions relative to the first intermediate clutch 23 within a certain load range. The first shift sleeve 18 is directly or indirectly connected to the first intermediate clutch 23 and rotates together with the first intermediate clutch 23, and the first shift sleeve 18 can move axially back and forth relative to the first intermediate clutch 23 under the action of the third shift fork 316. The first positioning mechanism 19 is directly or indirectly connected with the first intermediate clutch 23, the first positioning mechanism 19 and the first intermediate clutch 23 rotate together, and the first positioning mechanism 19 is axially fixed relative to the first intermediate clutch 23. Three axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions three axial positions of the first gear shifting gear sleeve 18 through the three axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, and the first shift sleeve 18 is selectively engaged with or disengaged from the first left half clutch 15 and the first right half clutch 16, respectively, by the driving of the third shift fork 316. When the first shift sleeve 18 is located at a middle position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve 18, the first left half clutch 15 and the first right half clutch 16 are both in a separated state, and at this time, the first left half clutch 15 and the first right half clutch 16 are both rotatable in forward and reverse directions relative to the first intermediate clutch 23. When the first shift sleeve gear 18 is located at the left position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve gear 18 and the first left half clutch 15 are in an engaged state, and the first shift sleeve gear 18 and the first right half clutch 16 are in a disengaged state, at this time, the first left half clutch 15 is fixed in the forward direction and the reverse direction relative to the first intermediate clutch 23, and the first right half clutch 16 is rotatable in the forward direction and the reverse direction relative to the first intermediate clutch 23. When the first shift sleeve gear 18 is located at the right position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first shift sleeve gear 18 and the first right half clutch 16 are in an engaged state, and the first shift sleeve gear 18 and the first left half clutch 15 are in a disengaged state, at this time, the first right half clutch 16 is fixed in the forward rotation direction and the reverse rotation direction relative to the first intermediate clutch 23, and the first left half clutch 15 is rotatable in the forward rotation direction and the reverse rotation direction relative to the first intermediate clutch 23.

Example 24

As shown in fig. 301 to 303, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 24 is the same as that in embodiment 3. As shown in fig. 80 to 82, the one-way clutch mechanism 51 includes: the clutch comprises a first return spring 4, a first right clutch bracket 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16 and a first auxiliary right half clutch 17. The first left half clutch 15, the first right clutch carrier 6, the first auxiliary right half clutch 17 and the first right half clutch 16 are coaxially arranged. The first return spring 4, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first limit pin 13, the first left clutch half 15, and the first auxiliary right clutch half 17 are disposed on the left side of the first right clutch half 16. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right clutch half 16 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. The first pawls 11 are engaged with the first right clutch half 16 at an initial position, and the first right clutch half 16 is fixed to the first left clutch half 15 in the normal rotation direction (the direction indicated by the arrow in fig. 80) and rotatable in the reverse rotation direction. The first right clutch half 16 and the first auxiliary right clutch half 17 are configured with at least ratchet-like projections or recesses, and the first pawls 11 are configured to have at least a function of engaging with or disengaging from the ratchet-like projections or recesses. The first clutch rivet 7 comprises a plurality of rivets, and the first right clutch bracket 6 is fixedly connected with the first left half clutch 15 through the first clutch rivet 7. Under the direct action of the first return spring 4, the first pawl 11 and the first right clutch half 16 are in contact with each other. Under the direct action of the first return spring 4, the first pawl 11 and the first auxiliary right half clutch 17 are in contact with each other. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first left clutch half 15, the first pawl 11 rotates together with the first left clutch half 15, and the first pawl 11 can rotate relative to the first left clutch half 15 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The first return spring 4 comprises a plurality of springs, the first return spring 4 being mounted on the first left clutch half 15. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the first return spring 4 acts on the first pawl 11, the first pawl 11 returns to the initial position under the action of the first return spring 4. As shown in fig. 231, when the first pawl 11 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the first pawl 11 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first right half clutch 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the first pawl 11 and the first right half clutch 16 (ratchet), F is the friction force between the first pawl 11 and the first right half clutch 16 (ratchet), FN is the normal acting force between the first pawl 11 and the first right half clutch 16 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first right half clutch 16 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first right half clutch 16 (ratchet wheel) do not disengage themselves. The first limit pin 13 comprises a plurality of pins, and the first limit pin 13 is fixedly connected with the first right half clutch 16. The first auxiliary right half clutch 17 is connected to the first right half clutch 16 via the first limit pin 13, and the first auxiliary right half clutch 17 at least has a function of being rotatable with respect to the first right half clutch 16 within an angular range defined by the first limit pin 13 by a direct or indirect action of the first pawl 11. The first auxiliary right half clutch 17 is arranged coaxially inside the first right half clutch 16 in the radial direction. When the first right half clutch 16 rotates reversely (in the opposite direction of the arrow shown in fig. 80) relative to the first left half clutch 15, under the action of the first pawl 11, after the first auxiliary right half clutch 17 rotates relative to the first right half clutch 16 to the angle defined by the first limit pin 13, a part of the surface of the first auxiliary right half clutch 17 and a part of the surface of the first right half clutch 16 are radially split into a plane, and the first pawl 11 rotates relative to the first right half clutch 16 and contacts with the split plane, so that noise is greatly reduced.

Example 25

As shown in fig. 304 to 306, the shift device GD includes: a one-way clutch mechanism 51 and a cushion damper device DM. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 25 is the same as in embodiment 1. As shown in fig. 87 to 91, the one-way clutch mechanism 51 includes: the clutch comprises a first return spring 4, a first left clutch bracket 5, a first right clutch bracket 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a second pawl 20, a second return spring 21, a first auxiliary left half clutch 22, a first middle clutch 23 and a second limit pin 24. The first left half clutch 15, the first right half clutch 16, the first left clutch support 5, the first right clutch support 6, the first auxiliary right half clutch 17, the first auxiliary left half clutch 22, and the first intermediate clutch 23 are coaxially arranged. The first return spring 4, the first left clutch bracket 5, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first limit pin 13, the first left clutch half 15, the first auxiliary right clutch half 17, the second pawl 20, the second return spring 21, the first auxiliary left clutch half 22, the first intermediate clutch half 23, and the second limit pin 24 are disposed on the left side of the first right clutch half 16. The first intermediate clutch 23 passes coaxially through the first left clutch half 15. The first intermediate clutch 23 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first left-half clutch 15 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. The first right half clutch 16 is directly or indirectly connected to and rotates with another driven member (not shown) of the machine M. The first pawl 11 is engaged with the first left clutch half 15 in the initial position, in which the first left clutch half 15 is fixed in the reverse rotation direction (the reverse direction indicated by the arrow in fig. 87) and rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 87) relative to the first intermediate clutch 23. The second pawls 20 are engaged with the first right clutch half 16 in the initial position, in which the first right clutch half 16 is fixed in the reverse rotation direction (the direction indicated by the arrow in fig. 87) and rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 87) with respect to the first intermediate clutch 23. The first left clutch half 15, the first right clutch half 16, the first auxiliary left clutch half 22, and the first auxiliary right clutch half 17 are configured with ratchet-shaped protrusions or grooves, and the first pawl 11 and the second pawl 20 have at least a function of engaging with or disengaging from the ratchet-shaped protrusions or grooves. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection. Under the action of the first return spring 4, the first pawl 11 and the first left clutch half 15 are in contact with each other, and the first pawl 11 and the first auxiliary left clutch half 22 are in contact with each other. Under the action of the second return spring 21, the second pawl 20 and the first right clutch half 16 are in contact with each other, and the second pawl 20 and the first auxiliary right clutch half 17 are in contact with each other. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first intermediate clutch 23, the first pawl 11 rotates together with the first intermediate clutch 23, and the first pawl 11 is rotatable within a range of angles relative to the first intermediate clutch 23. The first pawl 11 is connected with the first left clutch bracket 5, the first pawl 11 rotates together with the first left clutch bracket 5, and the first pawl 11 can rotate relative to the first left clutch bracket 5 within a certain angle range. The second pawl 20 includes a plurality of pawls, the second pawl 20 is mounted on the first intermediate clutch 23, the second pawl 20 rotates with the first intermediate clutch 23, and the second pawl 20 is rotatable within a range of angles relative to the first intermediate clutch 23. The second pawl 20 is directly or indirectly connected to the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the first return spring 4 acts on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the action of the second return spring 21 on the second pawl 20, the second pawl 20 returns to the initial position under the elastic force of the second return spring 21. As shown in fig. 231, when the first pawl 11 and the first left clutch half 15 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first left clutch half 15 (ratchet wheel) has a self-locking function: the first pawl 11 is engaged with the first left-half clutch 15 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first left-half clutch 15 (ratchet) is F, μ is the friction coefficient between the first pawl 11 and the contact surface of the first left-half clutch 15 (ratchet), F is the friction force between the first pawl 11 and the first left-half clutch 15 (ratchet), FN is the normal acting force between the first pawl 11 and the first left-half clutch 15 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first left-half clutch 15 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first left-half clutch 15 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the second pawl 20 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the second pawl 20 is in an engaged state with the first right clutch half 16 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first right clutch half 16 (ratchet), F is the friction force between the second pawl 20 and the first right clutch half 16 (ratchet), FN is the normal acting force between the second pawl 20 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, when θ < arctan (μ) and the engaging force F between the second pawl 20 and the first right clutch half 16 (ratchet) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawl 20 does not disengage itself from the first right half clutch 16 (ratchet). The first limit pin 13 comprises a plurality of pins, and the first limit pin 13 is fixedly connected with the first left half clutch 15. The second limit pin 24 comprises a plurality of pins, and the second limit pin 24 is fixedly connected with the first right half clutch 16. The first auxiliary left-half clutch 22 is connected to the first left-half clutch 15 via the first stopper pin 13, and the first auxiliary left-half clutch 22 at least has a function of being rotatable relative to the first left-half clutch 15 within an angular range defined by the first stopper pin 13 by the action of the first pawl 11. The first auxiliary right half clutch 17 is connected to the first right half clutch 16 via the second limit pin 24, and the first auxiliary right half clutch 17 at least has a function of rotating relative to the first right half clutch 16 within an angular range defined by the second limit pin 24 by the action of the second pawl 20. In the radial direction, the first auxiliary left half clutch 22 is coaxially disposed inside the first left half clutch 15, and the first auxiliary right half clutch 17 is coaxially disposed inside the first right half clutch 16. When the first left clutch half 15 rotates forward (in the direction of arrow in fig. 87) relative to the first intermediate clutch 23, under the direct or indirect action of the first pawl 11, after the first auxiliary left clutch half 22 rotates relative to the first left clutch half 15 to the angle defined by the first limit pin 13, part of the surface of the first auxiliary left clutch half 22 and part of the surface of the first left clutch half 15 are radially engaged to form a plane, and the first pawl 11 rotates relative to the first intermediate clutch half 23 and contacts with the engaged plane, so that noise is greatly reduced. When the first right half clutch 16 rotates forward (in the direction shown by the arrow in fig. 87) relative to the first intermediate clutch 23, under the direct or indirect action of the second pawl 20, after the first auxiliary right half clutch 17 rotates relative to the first right half clutch 16 to the angle defined by the second limit pin 24, part of the surface of the first auxiliary right half clutch 17 and part of the surface of the first right half clutch 16 are radially split into a plane, so that the second pawl 20 rotates relative to the first intermediate clutch 23 and contacts with the split plane, thereby greatly reducing noise.

Example 26

As shown in fig. 307 to 309, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 26 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 26 is the same as that in embodiment 3. As shown in fig. 83 to 86, the one-way clutch mechanism 51 in embodiment 26 is similar to that in embodiment 24, except that: the one-way clutch mechanism 51 according to embodiment 26 is provided with the first shift sleeve 18 and the first positioning mechanism 19 for forcibly controlling the clutch state of the one-way clutch mechanism 51. The first gear shift sleeve 18 is connected to the first left clutch half 15 and rotates together with the first left clutch half 15, and the first gear shift sleeve 18 can axially move back and forth relative to the first left clutch half 15 under the action of the third gear shift fork 316. First positioning mechanism 19 directly with first left-hand clutch 15 is connected, first positioning mechanism 19 with first left-hand clutch 15 rotates together, first positioning mechanism 19 is relative in the axial first left-hand clutch 15 is fixed. Two axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions two axial positions of the first gear shifting gear sleeve 18 through the two axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, the first shift sleeve 18 is connected to the first pawl 11, and the first shift sleeve 18 is driven by the third shift fork 316 to selectively engage or disengage the first pawl 11 with or from the first right half clutch 16. When the first shift sleeve 18 is located at the left one of the two axial positions with respect to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are engaged with each other by the first shift sleeve 18 and the first return spring 4, and at this time, the first right clutch half 16 is fixed in the reverse rotation direction (the reverse direction indicated by the arrow in fig. 83) with respect to the first left clutch half 15 and is rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 83). When the first shift sleeve gear 18 is located at the right position of the two axial positions relative to the first left-half clutch 15 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first right-half clutch 16 are in a separated state under the action of the first shift sleeve gear 18 and the first return spring 4, and at this time, the first right-half clutch 16 can rotate in both forward and reverse directions relative to the first left-half clutch 15.

Example 27

As shown in fig. 310 to 312, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 27 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 27 is the same as that in embodiment 1. As shown in fig. 92 to 94, the one-way clutch mechanism 51 in embodiment 27 is similar to that in embodiment 25, except that: the one-way clutch mechanism 51 according to embodiment 27 is provided with the first shift sleeve 18 and the first positioning mechanism 19 for forcibly controlling the clutch state of the one-way clutch mechanism 51. The first shift sleeve 18 is connected to the first intermediate clutch 23 and rotates together with the first intermediate clutch 23, and the first shift sleeve 18 can move axially back and forth relative to the first intermediate clutch 23 under the action of the third shift fork 316. First positioning mechanism 19 directly with first intermediate clutch 23 is connected, first positioning mechanism 19 with first intermediate clutch 23 rotates together, first positioning mechanism 19 is relative in the axial first intermediate clutch 23 is fixed. Three axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions three axial positions of the first gear shifting gear sleeve 18 through the three axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, the first shift sleeve 18 is connected to the first pawl 11, the first shift sleeve 18 is connected to the second pawl 20, the first shift sleeve 18 selectively engages or disengages the first pawl 11 with the first left clutch half 15 under the driving of the third shift fork 316, and the first shift sleeve 18 selectively engages or disengages the second pawl 20 with the first right clutch half 16 under the driving of the third shift fork 316. When the first shift sleeve 18 is located at an intermediate position of the three axial positions with respect to the first intermediate clutch 23 in the axial direction by the third shift fork 316, the first pawl 11 and the first left-half clutch 15 are engaged and the second pawl 20 and the first right-half clutch 16 are engaged by the first shift sleeve 18, the first return spring 4 and the second return spring 21, and at this time, the first left-half clutch 15 and the first right-half clutch 16 are fixed in the forward direction (the direction indicated by the arrow in fig. 92) and rotatable in the reverse direction (the opposite direction indicated by the arrow in fig. 92) with respect to the first intermediate clutch 23. When the first shift sleeve 18 is located at the left position among the three axial positions with respect to the first intermediate clutch 23 in the axial direction by the third shift fork 316, the first pawl 11 and the first left clutch half 15 are in the disengaged state and the second pawl 20 and the first right clutch half 16 are in the engaged state by the first shift sleeve 18, the first return spring 4 and the second return spring 21, at this time, the first left clutch half 15 is rotatable in both the forward rotation direction and the reverse rotation direction with respect to the first intermediate clutch 23, and the first right clutch half 16 is fixed in the forward rotation direction (the direction indicated by the arrow in fig. 92) and rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 92) with respect to the first intermediate clutch 23. When the first shift sleeve 18 is located at the right position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first left-half clutch 15 are in an engaged state and the second pawl 20 and the first right-half clutch 16 are in a disengaged state under the action of the first shift sleeve 18, the first return spring 4 and the second return spring 21, at this time, the first left-half clutch 15 is fixed in the forward direction (the direction indicated by the arrow in fig. 92) and is rotatable in the reverse direction (the opposite direction indicated by the arrow in fig. 92) relative to the first intermediate clutch 23, and the first right-half clutch 16 is rotatable in both the forward direction and the reverse direction relative to the first intermediate clutch 23.

Example 28

As shown in fig. 313 to 315, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 28 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 28 is the same as that in embodiment 1. As shown in fig. 95 to 97, the one-way clutch mechanism 51 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first gear shifting sleeve 18, a first positioning mechanism 19, a first gear shifting cam 25 and a first transmission pin 26. The one-way clutch mechanism 51 according to embodiment 28 is similar to embodiment 26, except that in embodiment 28, the third shift fork 316 controls the first pawl 11 sequentially through the first shift sleeve 18, the first drive pin 26, and the first shift cam 25, so that the first pawl 11 is engaged with or disengaged from the first right half clutch 16.

Example 29

As shown in fig. 316 to 318, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 29 is the same as embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 29 is the same as that in embodiment 1. As shown in fig. 98 to 100, the one-way clutch mechanism 51 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first gear shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first auxiliary left half clutch 22, a first middle clutch 23, a second limit pin 24, a first gear shifting cam 25 and a first transmission pin 26. The one-way clutch mechanism 51 according to embodiment 29 is similar to embodiment 27 except that in embodiment 29, the third shift fork 316 sequentially passes through the first shift sleeve 18, the first drive pin 26, and the first shift cam 25 to control the first pawl 11 and the second pawl 20, respectively, so that the first pawl 11 is engaged with or disengaged from the first left clutch half 15, and the second pawl 20 is engaged with or disengaged from the first right clutch half 16.

Example 30

As shown in fig. 319 to 321, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 209. The actuating device AM in embodiment 30 is the same as in embodiment 12. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 30 is similar to that in embodiment 3 except that: the second outer ring 220 of the damping device DM of embodiment 30 is fixedly connected to a frame (not shown) of the machine M. As shown in fig. 101 to 103, the one-way clutch mechanism 51 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first positioning mechanism 19 and a first gear shifting cam 25. The one-way clutch mechanism 51 of embodiment 30 is similar to embodiment 26 except that in embodiment 30, the third actuating pin 314 controls the first pawl 11 via the first shift cam 25 to bring the first pawl 11 into an engaged or disengaged state with the first left clutch half 15.

Example 31

As shown in fig. 322 to 324, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 209. The actuating device AM in embodiment 31 is the same as in embodiment 12. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 31 is the same as that in embodiment 30. As shown in fig. 104 to 106, the one-way clutch mechanism 51 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first auxiliary left half clutch 22, a first middle clutch 23, a second limit pin 24 and a first gear shifting cam 25. The one-way clutch mechanism 51 according to embodiment 31 is similar to embodiment 27 except that in embodiment 31, the third actuating pin 314 controls the first pawl 11 and the second pawl 20 via the first shift cam 25 respectively to engage or disengage the first pawl 11 with or from the first left clutch half 15 and to engage or disengage the second pawl 20 with or from the first right clutch half 16.

Example 32

As shown in fig. 325 to 327, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 32 is the same as in embodiment 1. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 32 is the same as that in embodiment 3. As shown in fig. 139 to 141, the ratchet clutch mechanism 52 includes: the gear shifting device comprises a first return spring 4, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18, a first positioning mechanism 19, a second pawl 20 and a second return spring 21. The first left half clutch 15, the first right clutch support 6, the first gear shifting sleeve 18, the first positioning mechanism 19 and the first right half clutch 16 are coaxially arranged. The first return spring 4, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first left-half clutch 15, the first shift sleeve 18, the first positioning mechanism 19, the second pawl 20, and the second return spring 21 are axially arranged on the left side of the first right-half clutch 16. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right clutch half 16 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. The first right clutch half 16 and the first auxiliary right clutch half 17 are configured with ratchet-shaped protrusions and grooves, and the first pawls 11 and the second pawls 20 have at least a function of engaging with or disengaging from the ratchet-shaped protrusions and ratchet-shaped grooves. The first clutch rivet 7 comprises a plurality of rivets, and the first right clutch bracket 6 is fixedly connected with the first left half clutch 15 through the first clutch rivet 7. When the first pawl 11 is engaged with the first right clutch half 16 in the initial position and the second pawl 20 is engaged with the first right clutch half 16 in the initial position, the first right clutch half 16 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 139) and the reverse rotation direction (the reverse direction indicated by the arrow in fig. 139) with respect to the first left clutch half 15. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first left clutch half 15, the first pawl 11 rotates together with the first left clutch half 15, and the first pawl 11 can rotate relative to the first left clutch half 15 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The second pawl 20 comprises a plurality of pawls, the second pawl 20 is mounted on the first left clutch half 15, the second pawl 20 rotates with the first left clutch half 15, and the second pawl 20 is rotatable within a range of angles relative to the first left clutch half 15. The second pawl 20 is connected to the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first left half clutch 15 and rotates together with the first left half clutch 15. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the elastic force of the first return spring 4 on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 includes a plurality of springs, and the second return spring 21 is installed on the first left clutch half 15 and rotates together with the first left clutch half 15. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the elastic action of the second return spring 21 on the second pawl 20, the second pawl 20 is restored to the initial position by the elastic force of the second return spring 21. When the first pawls 11 and the second pawls 20 are engaged with the first right half clutch 16, the first right half clutch 16 is fixed in both the forward rotation and reverse rotation directions with respect to the first left half clutch 15 within a certain load range. When the first pawls 11 are engaged with the first right clutch half 16 and the second pawls 20 are disengaged from the first right clutch half 16, the first right clutch half 16 is fixed in the normal rotation direction (the direction indicated by the arrow in fig. 139) and is rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 139) relative to the first left clutch half 15 within a certain load range. When the first pawls 11 are disengaged from the first right clutch half 16 and the second pawls 20 are engaged with the first right clutch half 16, the first right clutch half 16 is fixed in a reverse rotation direction (a direction opposite to an arrow in fig. 139) and is rotatable in a forward rotation direction (a direction shown by an arrow in fig. 139) with respect to the first left clutch half 15 within a certain load range. When the first pawls 11 and the second pawls 20 are disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in both forward and reverse directions with respect to the first left clutch half 15 within a certain load range. As shown in fig. 231, when the first pawl 11 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the first pawl 11 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first right half clutch 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the first pawl 11 and the first right half clutch 16 (ratchet), F is the friction force between the first pawl 11 and the first right half clutch 16 (ratchet), FN is the normal acting force between the first pawl 11 and the first right half clutch 16 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first right half clutch 16 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first right half clutch 16 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the second pawl 20 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the second pawl 20 is in an engaged state with the first right clutch half 16 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first right clutch half 16 (ratchet), F is the friction force between the second pawl 20 and the first right clutch half 16 (ratchet), FN is the normal acting force between the second pawl 20 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, when θ < arctan (μ) and the engaging force F between the second pawl 20 and the first right clutch half 16 (ratchet) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawl 20 does not disengage itself from the first right half clutch 16 (ratchet). The first gear shift sleeve 18 is connected to the first left clutch half 15 and rotates together with the first left clutch half 15, and the first gear shift sleeve 18 can axially move back and forth relative to the first left clutch half 15 under the action of the third gear shift fork 316. First positioning mechanism 19 directly with first left-hand clutch 15 is connected, first positioning mechanism 19 with first left-hand clutch 15 rotates together, first positioning mechanism 19 is relative in the axial first left-hand clutch 15 is fixed. Two axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions two axial positions of the first gear shifting gear sleeve 18 through the two axial positioning grooves. The first shifting sleeve 18 is connected to the third shift fork 316, the first shifting sleeve 18 is connected to the first pawl 11, and the first shifting sleeve 18 is connected to the second pawl 20. The first shift sleeve 18 selectively engages or disengages the first pawl 11 with or from the first right half clutch 16 under the drive of the third shift fork 316, and the first shift sleeve 18 selectively engages or disengages the second pawl 20 with or from the first right half clutch 16 under the drive of the third shift fork 316. When the first shift sleeve 18 is located at the right position of the two axial positions axially relative to the first left-half clutch 15 under the action of the third shift fork 316, the first pawl 11 and the first right-half clutch 16 are in an engaged state and the second pawl 20 and the first right-half clutch 16 are in an engaged state under the actions of the first shift sleeve 18, the first return spring 4 and the second return spring 21, and at this time, the first right-half clutch 16 is fixed in the forward and reverse directions relative to the first left-half clutch 15. When the first gear shift sleeve 18 is located at the left position of the two axial positions relative to the first left half clutch 15 in the axial direction under the action of the third gear shift fork 316, the first pawl 11 and the first right half clutch 16 are in a separated state, the second pawl 20 and the first right half clutch 16 are in a separated state under the action of the first gear shift sleeve 18, the first return spring 4 and the second return spring 21, and at this time, the first right half clutch 16 is rotatable relative to the first left half clutch 15 in forward and reverse directions.

Example 33

As shown in fig. 328 to 330, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 33 is the same as in embodiment 1. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 33 is the same as that in embodiment 1. The ratchet clutch mechanism 52, as shown in fig. 148 to 150, includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch bracket 5, a first right clutch bracket 6, a first clutch rivet 7, a first pawl 11, a first left half clutch 15, a first right half clutch 16, a first gear shifting sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first middle clutch 23, a third pawl 29, a third return spring 30, a fourth pawl 31 and a fourth return spring 32. The first left clutch 15, the first left clutch support 5, the first right clutch support 6, the first right clutch 16, the first gear shift sleeve 18, the first positioning mechanism 19 and the first middle clutch 23 are coaxially arranged. The first return spring 4, the first left clutch support 5, the first right clutch support 6, the first clutch rivet 7, the first pawl 11, the first left clutch half 15, the first gear shift sleeve 18, the first positioning mechanism 19, the second pawl 20, the second return spring 21, the first intermediate clutch 23, the third pawl 29, the third return spring 30, the fourth pawl 31, and the fourth return spring 32 are arranged on the left side of the first right clutch half 16. The first intermediate clutch 23 passes coaxially through the first left clutch half 15. The first intermediate clutch 23 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first left-half clutch 15 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. The first right half clutch 16 is directly or indirectly connected to and rotates with another driven member (not shown) of the machine M. The first left clutch half 15 and the first right clutch half 16 are configured with ratchet-shaped protrusions and grooves, and the first pawl 11, the second pawl 20, the third pawl 29, and the fourth pawl 31 have at least a function of engaging with or disengaging from the ratchet-shaped protrusions and the ratchet-shaped grooves. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection. The first pawls 11 are engaged with the first left clutch half 15 in the initial position, and the second pawls 20 are engaged with the first left clutch half 15 in the initial position, in which the first left clutch half 15 is fixed in both the forward rotation (direction indicated by an arrow in fig. 148) and the reverse rotation (direction opposite to the arrow in fig. 148) with respect to the first intermediate clutch 23. The third pawl 29 is engaged with the first right clutch half 16 in the initial position, and the fourth pawl 31 is engaged with the first right clutch half 16 in the initial position, so that the first right clutch half 16 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 148) and the reverse rotation direction (the reverse direction indicated by the arrow in fig. 148) with respect to the first intermediate clutch 23. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first intermediate clutch 23, the first pawl 11 rotates together with the first intermediate clutch 23, and the first pawl 11 is rotatable within a range of angles relative to the first intermediate clutch 23. The first pawl 11 is connected with the first left clutch support 5, the first pawl 11 rotates together with the first left clutch support 5, and the first pawl 11 can rotate relative to the first left clutch support 5 within a certain angle range. The second pawl 20 includes a plurality of pawls, the second pawl 20 is mounted on the first intermediate clutch 23, the second pawl 20 rotates with the first intermediate clutch 23, and the second pawl 20 is rotatable within a range of angles relative to the first intermediate clutch 23. The second pawl 20 is connected to the first left clutch support 5, the second pawl 20 rotates together with the first left clutch support 5, and the second pawl 20 is rotatable within a certain angle range with respect to the first left clutch support 5. The third pawl 29 comprises a plurality of pawls, the third pawl 29 is mounted on the first intermediate clutch 23, the third pawl 29 rotates with the first intermediate clutch 23, and the third pawl 29 is rotatable within a range of angles relative to the first intermediate clutch 23. The third pawl 29 is connected to the first right clutch carrier 6, the third pawl 29 rotates together with the first right clutch carrier 6, and the third pawl 29 is rotatable within a certain angle range with respect to the first right clutch carrier 6. The fourth pawl 31 includes a plurality of pawls, the fourth pawl 31 is mounted on the first intermediate clutch 23, the fourth pawl 31 rotates together with the first intermediate clutch 23, and the fourth pawl 31 is rotatable within a range of angles relative to the first intermediate clutch 23. The fourth pawl 31 is connected to the first right clutch support 6, the fourth pawl 31 rotates together with the first right clutch support 6, and the fourth pawl 31 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The third return spring 30 includes a plurality of springs, and the third return spring 30 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The fourth return spring 32 includes a plurality of springs, and the fourth return spring 32 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the first return spring 4 acts on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the action of the second return spring 21 on the second pawl 20, the second pawl 20 returns to the initial position under the elastic force of the second return spring 21. The third return spring 30 is directly connected to the third pawl 29, and when the action of other restraint or load on the third pawl 29 is smaller than the action of the third return spring 30 on the third pawl 29, the third pawl 29 returns to the original position by the elastic force of the third return spring 30. The fourth return spring 32 is directly connected to the fourth pawl 31, and when the action of other restraint or load on the fourth pawl 31 is smaller than the action of the fourth return spring 32 on the fourth pawl 31, the fourth pawl 31 is restored to the initial position by the elastic force of the fourth return spring 32. When the first pawls 11 are disengaged from the first left clutch half 15, and when the second pawls 20 are disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in both forward (the direction indicated by the arrow in fig. 148) and reverse (the direction opposite to the direction indicated by the arrow in fig. 148) directions relative to the first intermediate clutch 23 within a certain load range. When the third pawls 29 are disengaged from the first right clutch half 16 and when the fourth pawls 31 are disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in both the forward rotation direction (the direction indicated by the arrow in fig. 148) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 148) relative to the first intermediate clutch 23 within a certain load range. As shown in fig. 231, when the first pawl 11 and the first left clutch half 15 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first left clutch half 15 (ratchet wheel) has a self-locking function: the first pawl 11 is engaged with the first left-half clutch 15 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first left-half clutch 15 (ratchet) is F, μ is the friction coefficient between the first pawl 11 and the contact surface of the first left-half clutch 15 (ratchet), F is the friction force between the first pawl 11 and the first left-half clutch 15 (ratchet), FN is the normal acting force between the first pawl 11 and the first left-half clutch 15 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first left-half clutch 15 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first left-half clutch 15 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 is engaged with the first left clutch half 15 (ratchet wheel), the contact pair of the second pawl 20 and the first left clutch half 15 (ratchet wheel) has a self-locking function: the second pawl 20 is engaged with the first left-half clutch 15 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first left-half clutch 15 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first left-half clutch 15 (ratchet), F is the friction force between the second pawl 20 and the first left-half clutch 15 (ratchet), FN is the normal acting force between the second pawl 20 and the first left-half clutch 15 (ratchet), and θ is the included angle between F and FN, so that under a certain load range, when θ < arctan (μ) and when the engaging force F between the second pawl 20 and the first left-half clutch 15 (ratchet) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawl 20 does not disengage itself from the first left clutch half 15 (ratchet). As shown in fig. 231, when the third pawl 29 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the third pawl 29 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the third pawl 29 is engaged with the first right clutch half 16 (ratchet) under the action of the third return spring 30, the engaging force between the third pawl 29 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the third pawl 29 and the first right clutch half 16 (ratchet), F is the friction force between the third pawl 29 and the first right clutch half 16 (ratchet), FN is the normal acting force between the third pawl 29 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, in a certain load range, when θ < arctan (μ) and when the engaging force F between the third pawl 29 and the first right clutch half 16 (ratchet) is large, the third pawl 29 is under the action of the engaging force F, the elastic force of the third return spring 30 and the friction force F, the third pawl 29 and the first right half clutch 16 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the fourth pawl 31 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the fourth pawl 31 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the fourth pawl 31 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the fourth return spring 32, the engaging force between the fourth pawl 31 and the first right half clutch 16 (ratchet) is F, μ is a friction coefficient between contact surfaces of the fourth pawl 31 and the first right half clutch 16 (ratchet), F is a friction force between the fourth pawl 31 and the first right half clutch 16 (ratchet), FN is a normal acting force between the fourth pawl 31 and the first right half clutch 16 (ratchet), and θ is an included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the fourth pawl 31 and the first right half clutch 16 (ratchet) is large, the fourth pawl 31 is under the action of the engaging force F, the elastic force of the fourth return spring 32 and the friction force F, the fourth pawl 31 does not disengage itself from the first right half clutch 16 (ratchet). The first shift sleeve 18 is connected to the first intermediate clutch 23 and rotates together with the first intermediate clutch 23, and the first shift sleeve 18 can move axially back and forth relative to the first intermediate clutch 23 under the action of the third shift fork 316. First positioning mechanism 19 directly with first intermediate clutch 23 is connected, first positioning mechanism 19 with first intermediate clutch 23 rotates together, first positioning mechanism 19 is relative in the axial first intermediate clutch 23 is fixed. Three axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions three axial positions of the first gear shifting gear sleeve 18 through the three axial positioning grooves. The first shift sleeve 18 is connected to the third shift fork 316, and the first pawl 11, the second pawl 20, the third pawl 29, the fourth pawl 31 are connected to the first shift sleeve 18. The first shift sleeve 18 selectively engages or disengages the first pawl 11 with or from the first left-half clutch 15 under the driving of the third shift fork 316, the first shift sleeve 18 selectively engages or disengages the second pawl 20 with or from the first left-half clutch 15 under the driving of the third shift fork 316, the first shift sleeve 18 selectively engages or disengages the third pawl 29 with or from the first right-half clutch 16 under the driving of the third shift fork 316, and the first shift sleeve 18 selectively engages or disengages the fourth pawl 31 with or from the first right-half clutch 16 under the driving of the third shift fork 316. When the first shift sleeve gear 18 is located at an intermediate position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, under the action of the first shift sleeve gear 18, the first return spring 4, the second return spring 21, the third return spring 30 and the fourth return spring 32, the first pawl 11, the second pawl 20 and the first left half clutch 15 are in an engaged state, the third pawl 29, the fourth pawl 31 and the first right half clutch 16 are in an engaged state, at this time, the first left half clutch 15 is fixed in the forward direction and the reverse direction relative to the first intermediate clutch 23, and the first right half clutch 16 is fixed in the forward direction and the reverse direction relative to the first intermediate clutch 23. When the first shift sleeve 18 is located at a left position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, under the action of the first shift sleeve 18, the first return spring 4, the second return spring 21, the third return spring 30 and the fourth return spring 32, the first pawl 11, the second pawl 20 and the first left-half clutch 15 are in a separated state, the third pawl 29, the fourth pawl 31 and the first right-half clutch 16 are in an engaged state, at this time, the first left-half clutch 15 is rotatable in forward and reverse directions relative to the first intermediate clutch 23, and the first right-half clutch 16 is fixed in forward and reverse directions relative to the first intermediate clutch 23. When the first shift sleeve gear 18 is located at the right position of the three axial positions relative to the first intermediate clutch 23 in the axial direction under the action of the third shift fork 316, under the action of the first shift sleeve gear 18, the first return spring 4, the second return spring 21, the third return spring 30 and the fourth return spring 32, the first pawl 11, the second pawl 20 and the first left-half clutch 15 are in an engaged state, the third pawl 29, the fourth pawl 31 and the first right-half clutch 16 are in a disengaged state, at this time, the first left-half clutch 15 is fixed in the forward direction and the reverse direction relative to the first intermediate clutch 23, and the first right-half clutch 16 is rotatable in the forward direction and the reverse direction relative to the first intermediate clutch 23.

Example 34

As shown in fig. 331 to 333, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 34 is the same as in embodiment 1. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 34 is the same as that in embodiment 3. As shown in fig. 157 to 165, the ratchet clutch mechanism 52 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first gear shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first gear shifting cam 25 and a first transmission pin 26. The first left clutch half 15, the first left clutch support 5, the first right clutch support 6, the first auxiliary right clutch half 17, the first gear shift sleeve 18, the first positioning mechanism 19, the first gear shift cam 25 and the first right clutch half 16 are coaxially arranged. The first return spring 4, the first left clutch bracket 5, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first limit pin 13, the first left half clutch 15, the first auxiliary right half clutch 17, the first shift gear sleeve 18, the first positioning mechanism 19, the second pawl 20, the second return spring 21, the first shift cam 25, and the first transmission pin 26 are arranged on the left side of the first right half clutch 16 in the axial direction. The first left clutch half 15 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first right clutch half 16 is directly or indirectly connected to and rotates with a driving member (not shown) of the machine M. When the first pawls 11 and the first right clutch half 16 are engaged in the initial position and the second pawls 20 and the first right clutch half 16 are engaged in the initial position, the first right clutch half 16 is fixed to the first left clutch half 15 in both the forward rotation direction (the direction indicated by the arrow in fig. 159) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 159). The first right clutch half 16, the first auxiliary right clutch half 17, and the first shift cam 25 are configured with ratchet-shaped protrusions and recesses, and the first pawl 11 and the second pawl 20 have at least a function of engaging with or disengaging from the ratchet-shaped protrusions and recesses. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 passes through first separation and reunion rivet 7 with first left side is half separation and reunion 15 fixed connection, first right side separation and reunion support 6 passes through first separation and reunion rivet 7 with first left side is half separation and reunion 15 fixed connection. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first left clutch half 15, the first pawl 11 rotates together with the first left clutch half 15, and the first pawl 11 can rotate relative to the first left clutch half 15 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The second pawl 20 comprises a plurality of pawls, the second pawl 20 is mounted on the first left clutch half 15, the second pawl 20 rotates with the first left clutch half 15, and the second pawl 20 is rotatable within a range of angles relative to the first left clutch half 15. The second pawl 20 is connected to the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first left half clutch 15 and rotates together with the first left half clutch 15. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the elastic force of the first return spring 4 on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first left clutch half 15 and rotates together with the first left clutch half 15. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the elastic action of the second return spring 21 on the second pawl 20, the second pawl 20 is restored to the initial position by the elastic force of the second return spring 21. When the first pawls 11 and the second pawls 20 are engaged with the first right clutch half 16, the first right clutch half 16 is fixed in both the forward rotation direction (the direction indicated by an arrow in fig. 159) and the reverse rotation direction (the direction opposite to the direction indicated by an arrow in fig. 159) with respect to the first left clutch half 15 within a certain load range. When the first pawls 11 are engaged with the first right clutch half 16 and the second pawls 20 are disengaged from the first right clutch half 16, the first right clutch half 16 is fixed in the normal rotation direction (the direction indicated by the arrow in fig. 159) and is rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 159) relative to the first left clutch half 15 within a certain load range. When the first pawls 11 are disengaged from the first right clutch half 16 and the second pawls 20 are engaged with the first right clutch half 16, the first right clutch half 16 is fixed in a reverse rotation direction (a direction opposite to an arrow in fig. 159) and is rotatable in a forward rotation direction (a direction shown by an arrow in fig. 159) relative to the first left clutch half 15 within a certain load range.

When the first pawls 11 and the second pawls 20 are disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in both the forward rotation direction (the direction indicated by an arrow in fig. 159) and the reverse rotation direction (the direction opposite to the direction indicated by an arrow in fig. 159) with respect to the first left clutch half 15 within a certain load range. As shown in fig. 231, when the first pawl 11 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the first pawl 11 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first right half clutch 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the first pawl 11 and the first right half clutch 16 (ratchet), F is the friction force between the first pawl 11 and the first right half clutch 16 (ratchet), FN is the normal acting force between the first pawl 11 and the first right half clutch 16 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first right half clutch 16 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first right half clutch 16 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the second pawl 20 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the second pawl 20 is in an engaged state with the first right clutch half 16 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first right clutch half 16 (ratchet), F is the friction force between the second pawl 20 and the first right clutch half 16 (ratchet), FN is the normal acting force between the second pawl 20 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, when θ < arctan (μ) and the engaging force F between the second pawl 20 and the first right clutch half 16 (ratchet) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawl 20 does not disengage itself from the first right half clutch 16 (ratchet). The first gear shifting sleeve 18 is connected with the first left clutch support 5 and rotates together with the first left clutch support 5, and the first gear shifting sleeve 18 can axially move back and forth relative to the first left clutch support 5 under the action of the third gear shifting fork 316. The first gear shifting sleeve 18 is connected with the first right clutch support 6 and rotates together with the first right clutch support 6, and the first gear shifting sleeve 18 can axially move back and forth relative to the first right clutch support 6 under the action of the third gear shifting fork 316. First positioning mechanism 19 with first right separation and reunion support 6 is connected, first positioning mechanism 19 with first right separation and reunion support 6 rotates together, first positioning mechanism 19 is relative in the axial first right separation and reunion support 6 is fixed. Five axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions five axial positions of the first gear shifting gear sleeve 18 through the five axial positioning grooves. The first drive pin 26 is fixedly connected to the first shift sleeve 18. The first driving pin 26 is connected with the first shift cam 25 through a screw pair, and the axial movement of the first driving pin 26 with the first shift sleeve 18 within a certain range at least pushes the first shift cam 25 to rotate relative to the first left clutch half 15 within a certain angle range. The first shift cam 25 is connected to the first left clutch half 15, and the first shift cam 25 is rotatable within a certain angle range relative to the first left clutch half 15 by the first drive pin 26. The first shift cam 25 is connected to the first left clutch carrier 5, and the first shift cam 25 is rotatable within a certain angle range relative to the first left clutch carrier 5 by the first driving pin 26. The first shift cam 25 is connected to the first right clutch bracket 6, and the first shift cam 25 can rotate in a certain angle range relative to the first right clutch bracket 6 under the action of the first transmission pin 26. The first shift cam 25 is connected to the first pawl 11, and rotation of the first shift cam 25 relative to the first left clutch half 15 within a certain range brings the first pawl 11 into engagement or disengagement with the first right clutch half 16. The first shift cam 25 is directly or indirectly connected to the second pawls 20, and rotation of the first shift cam 25 relative to the first left clutch half 15 within a certain range brings the second pawls 20 into engagement or disengagement with the first right clutch half 16. The first gear shift sleeve 18 is connected to the third gear shift fork 316, the first gear shift sleeve 18 indirectly enables the first pawl 11 and the first right half clutch 16 to be in an engaged or disengaged state under the driving of the third gear shift fork 316, and the first gear shift sleeve 18 indirectly enables the second pawl 20 and the first right half clutch 16 to be in an engaged or disengaged state under the driving of the third gear shift fork 316. As shown in fig. 157, when the first shift sleeve 18 is at the middle position of five axial positions relative to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are in the engaged state and the second pawl 20 and the first right clutch half 16 are in the engaged state by the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first right clutch half 16 is fixed in both the forward rotation direction and the reverse rotation direction relative to the first left clutch half 15. As shown in fig. 159, when the first shift sleeve 18 is located at the left 1 position of five axial positions relative to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are in a disengaged state and the second pawl 20 and the first right clutch half 16 are in an engaged state by the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first right clutch half 16 is rotatable in the forward rotation direction (the direction indicated by the arrow in fig. 159) and fixed in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 159) relative to the first left clutch half 15. As shown in fig. 160, when the first shift sleeve 18 is located at the right 1 position of five axial positions relative to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are in an engaged state and the second pawl 20 and the first right clutch half 16 are in a disengaged state under the action of the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first right clutch half 16 is fixed in the forward rotation direction (the direction indicated by the arrow in fig. 160) and rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 160) relative to the first left clutch half 15. As shown in fig. 161, when the first shift sleeve 18 is located at the left 2 position of five axial positions relative to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are in a disengaged state and the second pawl 20 and the first right clutch half 16 are in a disengaged state by the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first right clutch half 16 is rotatable relative to the first left clutch half 15 in both the forward rotation direction (the direction indicated by the arrow in fig. 161) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 161). As shown in fig. 162, when the first shift sleeve 18 is located at the right 2 position of five axial positions relative to the first left clutch half 15 in the axial direction by the third shift fork 316, the first pawl 11 and the first right clutch half 16 are in a disengaged state and the second pawl 20 and the first right clutch half 16 are in a disengaged state under the action of the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first right clutch half 16 is rotatable relative to the first left clutch half 15 in both the forward rotation direction (the direction indicated by the arrow in fig. 162) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 162). The first limit pin 13 comprises a plurality of pins, and the first limit pin 13 is fixedly connected with the first right half clutch 16. The first auxiliary right half clutch 17 is connected to the first right half clutch 16 by the first limit pin 13, and the first auxiliary right half clutch 17 at least has a function of rotating relative to the first right half clutch 16 within an angular range defined by the first limit pin 13 by the action of the first pawl 11 or the second pawl 20. The first auxiliary right half clutch 17 is arranged coaxially inside the first right half clutch 16 in the radial direction. As shown in fig. 159 and 163, when the first shift sleeve 18 is located at the left 1 position of five axial positions relative to the first left clutch half 15 in the axial direction under the action of the third shift fork 316, and when the first right clutch half 16 rotates in the forward direction (the direction indicated by the arrow in fig. 159) relative to the first left clutch half 15, after the first auxiliary right clutch half 17 rotates relative to the first right clutch half 16 to the angle defined by the first limit pin 13 under the direct action of the second pawl 20, a partial surface of the first auxiliary right clutch half 17 and a partial surface of the first right clutch half 16 are radially engaged to form a flat surface, and the second pawl 20 rotates relative to the first right clutch half 16 to contact with the engaged flat surface, so that noise is greatly reduced. As shown in fig. 160 and 164, when the first shift sleeve 18 is located at the right 1 position of five axial positions relative to the first left clutch half 15 in the axial direction under the action of the third shift fork 316, and when the first right clutch half 16 rotates in the reverse direction (the reverse direction of the arrow shown in fig. 160) relative to the first left clutch half 15, after the first auxiliary right clutch half 17 rotates to the angle defined by the first limit pin 13 relative to the first right clutch half 16 under the direct action of the first pawl 11, a partial surface of the first auxiliary right clutch half 17 and a partial surface of the first right clutch half 16 are radially combined to form a flat surface, and the first pawl 11 rotates relative to the first right clutch half 16 to contact the combined flat surface, so that noise is greatly reduced.

Example 35

As shown in fig. 334 to 336, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 35 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 35 is the same as that in embodiment 1. As shown in fig. 166 to 173, the ratchet clutch mechanism 52 includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first gear shifting gear sleeve 18, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first auxiliary left half clutch 22, a first middle clutch 23, a second limit pin 24, a first gear shifting cam 25, a first transmission pin 26, a third pawl 29, a third return spring 30, a fourth pawl 31 and a fourth return spring 32. First left side half separation and reunion 15 first left side separation and reunion support 5 first right side separation and reunion support 6 first right half separation and reunion 16 first supplementary right half separation and reunion 17 first shift gear sleeve 18 first positioning mechanism 19 first supplementary left side half separation and reunion 22 first shift cam 25 with first middle separation and reunion 23 coaxial arrangement. The first return spring 4, the first left clutch bracket 5, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first limit pin 13, the first left half clutch 15, the first auxiliary right half clutch 17, the first shift sleeve 18, the first positioning mechanism 19, the second pawl 20, the second return spring 21, the first auxiliary left half clutch 22, the first intermediate clutch 23, the second limit pin 24, the first shift cam 25, the first transmission pin 26, the third pawl 29, the third return spring 30, the fourth pawl 31, and the fourth return spring 32 are arranged on the left side of the first right half clutch 16. The first intermediate clutch 23 passes coaxially through the first left clutch half 15. The first intermediate clutch 23 is connected to the second friction plate 212 of the damper device DM and rotates together with the second friction plate 212. The first left-half clutch 15 is directly or indirectly connected to and rotates with a driven member (not shown) of the machine M. The first right half clutch 16 is directly or indirectly connected to and rotates with another driven member (not shown) of the machine M. The first pawls 11 are engaged with the first left clutch half 15 in the initial position, and the second pawls 20 are engaged with the first left clutch half 15 in the initial position, in which the first left clutch half 15 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 168) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 168) with respect to the first intermediate clutch 23. When the third pawl 29 is engaged with the first right clutch half 16 in the initial position and the fourth pawl 31 is engaged with the first right clutch half 16 in the initial position, the first right clutch half 16 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 168) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 168) with respect to the first intermediate clutch 23. The first left clutch half 15, the first right clutch half 16, the first auxiliary left clutch half 22, the first auxiliary right clutch half 17, and the first shift cam 25 are configured with ratchet-shaped protrusions or grooves, and the first pawl 11, the second pawl 20, the third pawl 29, and the fourth pawl 31 have at least a function of engaging with or disengaging from the ratchet-shaped protrusions or grooves. First separation and reunion rivet 7 includes a plurality of rivets, first left side separation and reunion support 5 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection, first right side separation and reunion support 6 pass through first separation and reunion rivet 7 with first intermediate clutch 23 fixed connection. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first intermediate clutch 23, the first pawl 11 rotates together with the first intermediate clutch 23, and the first pawl 11 is rotatable within a range of angles relative to the first intermediate clutch 23. The first pawl 11 is connected with the first left clutch support 5, the first pawl 11 rotates together with the first left clutch support 5, and the first pawl 11 can rotate relative to the first left clutch support 5 within a certain angle range. The second pawl 20 includes a plurality of pawls, the second pawl 20 is mounted on the first intermediate clutch 23, the second pawl 20 rotates with the first intermediate clutch 23, and the second pawl 20 is rotatable within a range of angles relative to the first intermediate clutch 23. The second pawl 20 is connected to the first left clutch support 5, the second pawl 20 rotates together with the first left clutch support 5, and the second pawl 20 is rotatable within a certain angle range with respect to the first left clutch support 5. The third pawl 29 comprises a plurality of pawls, the third pawl 29 is mounted on the first intermediate clutch 23, the third pawl 29 rotates with the first intermediate clutch 23, and the third pawl 29 is rotatable within a range of angles relative to the first intermediate clutch 23. The third pawl 29 is connected to the first right clutch carrier 6, the third pawl 29 rotates together with the first right clutch carrier 6, and the third pawl 29 is rotatable within a certain angle range with respect to the first right clutch carrier 6. The fourth pawl 31 includes a plurality of pawls, the fourth pawl 31 is mounted on the first intermediate clutch 23, the fourth pawl 31 rotates together with the first intermediate clutch 23, and the fourth pawl 31 is rotatable within a range of angles relative to the first intermediate clutch 23. The fourth pawl 31 is connected to the first right clutch support 6, the fourth pawl 31 rotates together with the first right clutch support 6, and the fourth pawl 31 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The third return spring 30 includes a plurality of springs, and the third return spring 30 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The fourth return spring 32 includes a plurality of springs, and the fourth return spring 32 is mounted on the first intermediate clutch 23 and rotates together with the first intermediate clutch 23. The first return spring 4 is directly connected to the first pawl 11, and when the other restraint or load acts on the first pawl 11 less than the first return spring 4 acts on the first pawl 11, the first pawl 11 returns to the initial position by the elastic force of the first return spring 4. The second return spring 21 is directly connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the action of the second return spring 21 on the second pawl 20, the second pawl 20 returns to the initial position under the elastic force of the second return spring 21. The third return spring 30 is directly connected to the third pawl 29, and when the action of other restraint or load on the third pawl 29 is smaller than the action of the third return spring 30 on the third pawl 29, the third pawl 29 returns to the original position by the elastic force of the third return spring 30. The fourth return spring 32 is directly connected to the fourth pawl 31, and when the action of other restraint or load on the fourth pawl 31 is smaller than the action of the fourth return spring 32 on the fourth pawl 31, the fourth pawl 31 is restored to the initial position by the elastic force of the fourth return spring 32. When the first pawls 11 are disengaged from the first left clutch half 15 and the second pawls 20 are engaged with the first left clutch half 15, the first left clutch half 15 is rotatable in a forward rotation direction (direction indicated by an arrow in fig. 168) and fixed in a reverse rotation direction (opposite direction indicated by an arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. When the first pawls 11 are engaged with the first left clutch half 15 and the second pawls 20 are disengaged from the first left clutch half 15, the first left clutch half 15 is fixed in the forward rotation direction (the direction indicated by the arrow in fig. 168) and is rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. When the first pawls 11 are disengaged from the first left clutch half 15 and the second pawls 20 are disengaged from the first left clutch half 15, the first left clutch half 15 is rotatable in a normal rotation direction (the direction indicated by an arrow in fig. 168) and in a reverse rotation direction (the opposite direction indicated by an arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. When the third pawls 29 are disengaged from the first right clutch half 16 and the fourth pawls 31 are engaged with the first right clutch half 16, the first right clutch half 16 is rotatable in the normal rotation direction (the direction indicated by the arrow in fig. 168) and fixed in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. When the third pawls 29 are engaged with the first right clutch half 16 and the fourth pawls 31 are disengaged from the first right clutch half 16, the first right clutch half 16 is fixed in the normal rotation direction (the direction indicated by the arrow in fig. 168) and is rotatable in the reverse rotation direction (the opposite direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. When the third pawls 29 are disengaged from the first right clutch half 16 and the fourth pawls 31 are disengaged from the first right clutch half 16, the first right clutch half 16 is rotatable in a normal rotation direction (a direction indicated by an arrow in fig. 168) and in a reverse rotation direction (a direction opposite to the direction indicated by an arrow in fig. 168) relative to the first intermediate clutch 23 within a certain load range. As shown in fig. 231, when the first pawl 11 and the first left clutch half 15 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first left clutch half 15 (ratchet wheel) has a self-locking function: the first pawl 11 is engaged with the first left-half clutch 15 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first left-half clutch 15 (ratchet) is F, μ is the friction coefficient between the first pawl 11 and the contact surface of the first left-half clutch 15 (ratchet), F is the friction force between the first pawl 11 and the first left-half clutch 15 (ratchet), FN is the normal acting force between the first pawl 11 and the first left-half clutch 15 (ratchet), and θ is the included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first left-half clutch 15 (ratchet) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawl 11 and the first left-half clutch 15 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawl 20 is engaged with the first left clutch half 15 (ratchet wheel), the contact pair of the second pawl 20 and the first left clutch half 15 (ratchet wheel) has a self-locking function: the second pawl 20 is engaged with the first left-half clutch 15 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first left-half clutch 15 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first left-half clutch 15 (ratchet), F is the friction force between the second pawl 20 and the first left-half clutch 15 (ratchet), FN is the normal acting force between the second pawl 20 and the first left-half clutch 15 (ratchet), and θ is the included angle between F and FN, so that under a certain load range, when θ < arctan (μ) and when the engaging force F between the second pawl 20 and the first left-half clutch 15 (ratchet) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawl 20 does not disengage itself from the first left clutch half 15 (ratchet). As shown in fig. 231, when the third pawl 29 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the third pawl 29 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the third pawl 29 is engaged with the first right clutch half 16 (ratchet) under the action of the third return spring 30, the engaging force between the third pawl 29 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the third pawl 29 and the first right clutch half 16 (ratchet), F is the friction force between the third pawl 29 and the first right clutch half 16 (ratchet), FN is the normal acting force between the third pawl 29 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, in a certain load range, when θ < arctan (μ) and when the engaging force F between the third pawl 29 and the first right clutch half 16 (ratchet) is large, the third pawl 29 is under the action of the engaging force F, the elastic force of the third return spring 30 and the friction force F, the third pawl 29 and the first right half clutch 16 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the fourth pawl 31 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the fourth pawl 31 and the first right clutch half 16 (ratchet wheel) has a self-locking function: the fourth pawl 31 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the fourth return spring 32, the engaging force between the fourth pawl 31 and the first right half clutch 16 (ratchet) is F, μ is a friction coefficient between contact surfaces of the fourth pawl 31 and the first right half clutch 16 (ratchet), F is a friction force between the fourth pawl 31 and the first right half clutch 16 (ratchet), FN is a normal acting force between the fourth pawl 31 and the first right half clutch 16 (ratchet), and θ is an included angle between F and FN, so that in a certain load range, when θ < arctan (μ) and when the engaging force F between the fourth pawl 31 and the first right half clutch 16 (ratchet) is large, the fourth pawl 31 is under the action of the engaging force F, the elastic force of the fourth return spring 32 and the friction force F, the fourth pawl 31 does not disengage itself from the first right half clutch 16 (ratchet). The first gear shifting sleeve 18 is connected with the first left clutch support 5 and rotates together with the first left clutch support 5, and the first gear shifting sleeve 18 can axially move back and forth relative to the first left clutch support 5 under the action of the third gear shifting fork 316. The first gear shifting sleeve 18 is connected with the first right clutch support 6 and rotates together with the first right clutch support 6, and the first gear shifting sleeve 18 can axially move back and forth relative to the first right clutch support 6 under the action of the third gear shifting fork 316. First positioning mechanism 19 with first right separation and reunion support 6 is connected, first positioning mechanism 19 with first right separation and reunion support 6 rotates together, first positioning mechanism 19 is relative in the axial first right separation and reunion support 6 is fixed. Five axial positioning grooves are formed in the first gear shifting gear sleeve 18, the first positioning mechanism 19 is connected with the first gear shifting gear sleeve 18, and the first positioning mechanism 19 axially positions five axial positions of the first gear shifting gear sleeve 18 through the five axial positioning grooves. The first drive pin 26 is fixedly connected to the first shift sleeve 18. The first driving pin 26 is connected with the first shift cam 25 through a screw pair, and the axial movement of the first driving pin 26 with the first shift sleeve 18 within a certain range at least pushes the first shift cam 25 to rotate relative to the first left clutch half 15 within a certain angle range. The first shift cam 25 is connected to the first intermediate clutch 23, and the first shift cam 25 is rotatable within a certain angle range relative to the first intermediate clutch 23 by the first drive pin 26. The first shift cam 25 is connected to the first left clutch carrier 5, and the first shift cam 25 is rotatable within a certain angle range relative to the first left clutch carrier 5 by the first driving pin 26. The first shift cam 25 is connected to the first right clutch bracket 6, and the first shift cam 25 can rotate in a certain angle range relative to the first right clutch bracket 6 under the action of the first transmission pin 26. The first shift cam 25 is connected to the first pawl 11, and rotation of the first shift cam 25 relative to the first intermediate clutch 23 within a certain range brings the first pawl 11 into engagement or disengagement with the first left clutch half 15. The first shift cam 25 is directly or indirectly connected to the second pawl 20, and rotation of the first shift cam 25 relative to the first intermediate clutch 23 within a certain range brings the second pawl 20 into engagement or disengagement with the first left clutch half 15. The first shift cam 25 is connected to the third pawl 29, and rotation of the first shift cam 25 relative to the first intermediate clutch 23 within a certain range brings the third pawl 29 into engagement or disengagement with the first right half clutch 16. The first shift cam 25 is directly or indirectly connected with the fourth pawl 31, and rotation of the first shift cam 25 relative to the first intermediate clutch 23 within a certain range brings the fourth pawl 31 into engagement or disengagement with the first right half clutch 16. The first shift sleeve 18 is connected to the third shift fork 316, the first shift sleeve 18 indirectly drives the first pawl 11 and the first left clutch half 15 to be in an engaged or disengaged state under the driving of the third shift fork 316, the first shift sleeve 18 indirectly drives the second pawl 20 and the first left clutch half 15 to be in an engaged or disengaged state under the driving of the third shift fork 316, the first shift sleeve 18 indirectly drives the third pawl 29 and the first right clutch half 16 to be in an engaged or disengaged state under the driving of the third shift fork 316, and the first shift sleeve 18 indirectly drives the fourth pawl 31 and the first right clutch half 16 to be in an engaged or disengaged state under the driving of the third shift fork 316. As shown in fig. 166, when the first shift sleeve 18 is at an intermediate position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, the first pawl 11 is in an engaged state with the first left-half clutch 15, the second pawl 20 is in an engaged state with the first left-half clutch 15, the third pawl 29 is in an engaged state with the first right-half clutch 16, and the fourth pawl 31 is in an engaged state with the first right-half clutch 16 by the first shift cam 25, the first return spring 4, and the second return spring 21, respectively, at which the arrows of the first left-half clutch 15 relative to the first intermediate clutch 23 are fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 168) and in the reverse rotation direction (the reverse direction indicated by the arrow in fig. 168), the first right half clutch 16 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 168) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 168) with respect to the first intermediate clutch 23. As shown in fig. 168, when the first shift sleeve 18 is located at the left 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, the first pawl 11 is in a disengaged state with respect to the first left-half clutch 15, the second pawl 20 is in an engaged state with respect to the first left-half clutch 15, the third pawl 29 is in a disengaged state with respect to the first right-half clutch 16, and the fourth pawl 31 is in an engaged state with respect to the first right-half clutch 16 by the first shift cam 25, the first return spring 4, and the second return spring 21, at which time, the first left-half clutch 15 is rotatable in the forward direction (the direction indicated by the arrow in fig. 168) and fixed in the reverse direction (the reverse direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23, the first right half clutch 16 is rotatable in a forward direction (direction indicated by an arrow in fig. 168) and fixed in a reverse direction (opposite direction indicated by an arrow in fig. 168) relative to the first intermediate clutch 23. As shown in fig. 169, when the first shift sleeve 18 is located at the right 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, the first pawl 11 is in an engaged state with the first left-half clutch 15, the second pawl 20 is in a disengaged state with the first left-half clutch 15, the third pawl 29 is in an engaged state with the first right-half clutch 16, and the fourth pawl 31 is in a disengaged state with the first right-half clutch 16 by the first shift cam 25, the first return spring 4, and the second return spring 21, the first left-half clutch 15 is fixed in the forward direction (the direction indicated by the arrow in fig. 169) relative to the first intermediate clutch 23 and is rotatable in the reverse direction (the reverse direction indicated by the arrow in fig. 169), the first right half clutch 16 is fixed to the first intermediate clutch 23 in a normal rotation direction (a direction indicated by an arrow in fig. 169) and is rotatable in a reverse rotation direction (a direction opposite to the direction indicated by an arrow in fig. 169). As shown in fig. 170, when the first shift sleeve 18 is axially positioned at the left 2 or right 2 position of five axial positions relative to the first intermediate clutch 23 by the third shift fork 316, the first pawl 11 and the first left clutch half 15 are in a disengaged state, the second pawl 20 and the first left clutch half 15 are in a disengaged state, the third pawl 29 and the first right clutch half 16 are in a disengaged state, and the fourth pawl 31 and the first right clutch half 16 are in a disengaged state under the action of the first shift cam 25, the first return spring 4 and the second return spring 21, and at this time, the first left clutch half 15 is rotatable relative to the first intermediate clutch 23 in both the forward direction (the direction shown by the arrow in fig. 168) and the reverse direction (the opposite direction shown by the arrow in fig. 168), the first right half clutch 16 is rotatable relative to the first intermediate clutch 23 in both a forward direction (indicated by an arrow in fig. 168) and a reverse direction (indicated by an arrow in fig. 168). The first stopper pin 13 includes a plurality of pins, and the second stopper pin 24 includes a plurality of pins. The first limit pin 13 is fixedly connected with the first left half clutch 15, and the second limit pin 24 is fixedly connected with the first right half clutch 16. The first auxiliary left-half clutch 22 is connected to the first left-half clutch 15 by the first stopper pin 13, and the first auxiliary left-half clutch 22 at least has a function of rotating relative to the first left-half clutch 15 within an angular range defined by the first stopper pin 13 by the action of the first pawl 11 or the second pawl 20. The first auxiliary right half clutch 17 is connected to the first right half clutch 16 by the second limit pin 24, and the first auxiliary right half clutch 17 at least has a function of rotating relative to the first right half clutch 16 within an angular range defined by the second limit pin 24 by the third pawl 29 or the fourth pawl 31. In the radial direction, the first auxiliary left half clutch 22 is coaxially disposed inside the first left half clutch 15, and the first auxiliary right half clutch 17 is coaxially disposed inside the first right half clutch 16. As shown in fig. 168 and 171, when the first shift sleeve 18 is located at the left 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, and when the first left-half clutch 15 is rotated in the forward direction (the direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23, a part of the surface of the first auxiliary left-half clutch 22 is radially engaged with a part of the surface of the first left-half clutch 15 to form a flat surface after the first auxiliary left-half clutch 22 is rotated to the angle defined by the first limit pin 13 relative to the first left-half clutch 15 by the second pawl 20, and the second pawl 20 is rotated relative to the first intermediate clutch 23 to contact the engaged flat surface, so that noise is greatly reduced. As shown in fig. 168 and 171, when the first shift sleeve 18 is located at the left 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, and when the first right half clutch 16 is rotated in the forward direction (the direction indicated by the arrow in fig. 168) relative to the first intermediate clutch 23, after the first auxiliary right half clutch 17 is rotated to the angle defined by the second limit pin 24 relative to the first right half clutch 16 by the fourth pawl 31, a partial surface of the first auxiliary right half clutch 17 and a partial surface of the first right half clutch 16 are radially combined to form a flat surface, so that the fourth pawl 31 is in contact with the combined flat surface when rotated relative to the first intermediate clutch 23, thereby greatly reducing noise. As shown in fig. 169 and 172, when the first shift sleeve 18 is located at the right 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316, and when the first left-half clutch 15 is rotated in the reverse direction (the opposite direction indicated by the arrow in fig. 169) relative to the first intermediate clutch 23, a part of the surface of the first auxiliary left-half clutch 22 is radially engaged with a part of the surface of the first left-half clutch 15 to form a flat surface after the first auxiliary left-half clutch 22 is rotated to the angle defined by the first limit pin 13 relative to the first left-half clutch 15 by the first pawl 11, and the second pawl 20 is in contact with the engaged flat surface when rotated relative to the first intermediate clutch 23, so that noise is greatly reduced. As shown in fig. 169 and 172, when the first shift sleeve 18 is located at the right 1 position of five axial positions relative to the first intermediate clutch 23 in the axial direction by the third shift fork 316 and when the first right half clutch 16 is rotated in the reverse direction (the opposite direction indicated by the arrow in fig. 169) relative to the first intermediate clutch 23, the partial surface of the first auxiliary right half clutch 17 and the partial surface of the first right half clutch 16 are radially combined to form a flat surface after the first auxiliary right half clutch 17 is rotated to the angle defined by the second limit pin 24 relative to the first right half clutch 16 by the third pawl 29, so that the fourth pawl 31 is in contact with the combined flat surface when rotated relative to the first intermediate clutch 23, thereby greatly reducing noise.

Example 36

As shown in fig. 337 to 339, shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 209. The actuating device AM in embodiment 36 is the same as in embodiment 12. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 36 is the same as that in embodiment 30. As shown in fig. 174 to 176, the ratchet clutch mechanism 52 includes: the gear shifting device comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first positioning mechanism 19, a second pawl 20, a second return spring 21 and a first gear shifting cam 25. The ratchet clutch mechanism 52 according to the embodiment 36 is similar to the embodiment 34, except that in the embodiment 36, the third actuating pin 314 controls the first pawl 11 and the second pawl 20 respectively through the first shift cam 25, so that the first pawl 11 is engaged or disengaged with the first left clutch half 15, and the second pawl 20 is engaged or disengaged with the first right clutch half 16.

Example 37

As shown in fig. 340 to 342, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 209. The actuating device AM in embodiment 37 is the same as in embodiment 12. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in example 37 is the same as that in example 30. The ratchet clutch mechanism 52, as shown in fig. 177 to 179, includes: the gear shifting mechanism comprises a first return spring 4, a first left clutch support 5, a first right clutch support 6, a first clutch rivet 7, a first pawl 11, a first limit pin 13, a first left half clutch 15, a first right half clutch 16, a first auxiliary right half clutch 17, a first positioning mechanism 19, a second pawl 20, a second return spring 21, a first auxiliary left half clutch 22, a first middle clutch 23, a second limit pin 24, a first gear shifting cam 25, a third pawl 29, a third return spring 30, a fourth pawl 31 and a fourth return spring 32. The ratchet clutch mechanism 52 according to embodiment 37 is similar to embodiment 35 except that in embodiment 37, the third actuating pin 314 controls the first pawl 11, the second pawl 20, the third pawl 29 and the fourth pawl 31 via the first shift cam 25 respectively to engage or disengage the first pawl 11 with or from the first left-half clutch 15 and the second pawl 20 with or from the first left-half clutch 15 and to engage or disengage the third pawl 29 with or from the first right-half clutch 16 and to engage or disengage the fourth pawl 31 with or from the first right-half clutch 16.

Example 38

As shown in fig. 343 to 345, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 38 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 38 is the same as that in embodiment 3. The ratchet clutch mechanism 52 is shown in fig. 142-144. The ratchet clutch mechanism 52 of embodiment 38 is similar to embodiment 32 except that in embodiment 38 the first pawl 11 is connected to the first shift sleeve 18 by a cotter pin arrangement and the second pawl 20 is connected to the first shift sleeve 18 by a cotter pin arrangement.

Example 39

As shown in fig. 346 to 348, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 39 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 39 is the same as in embodiment 1. The ratchet clutch mechanism 52 is shown in fig. 151 to 153. The ratchet clutch mechanism 52 according to embodiment 39 is similar to embodiment 33 except that in embodiment 38 the first pawl 11 is connected to the first shift sleeve 18 by a cotter pin structure, the second pawl 20 is connected to the first shift sleeve 18 by a cotter pin structure, the third pawl 29 is connected to the first shift sleeve 18 by a cotter pin structure, and the fourth pawl 31 is connected to the first shift sleeve 18 by a cotter pin structure.

Example 40

As shown in fig. 349 to 351, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 40 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 40 is the same as that in embodiment 3. The ratchet clutch mechanism 52 is shown in FIGS. 145 to 147. The ratchet clutch mechanism 52 according to embodiment 40 is similar to embodiment 38, except that the first pawl 11 and the second pawl 20 according to embodiment 40 are disengaged from the first right clutch half 16 in the initial position.

EXAMPLE 41

As shown in fig. 352 to 354, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 41 is the same as embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 41 is the same as that in embodiment 1. The ratchet clutch mechanism 52 is shown in FIGS. 154 to 156. The ratchet clutch mechanism 52 according to embodiment 41 is similar to embodiment 39, except that the first pawl 11 and the second pawl 20 according to embodiment 41 are both disengaged from the first left half clutch 15 in the initial position, and the third pawl 29 and the fourth pawl 31 according to embodiment 41 are both disengaged from the first right half clutch 16 in the initial position.

Example 42

As shown in fig. 355 to 357, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 42 is similar to that of embodiment 11 except that: the partial structure of the third shift fork 316 in embodiment 42 is different from that in embodiment 11. The cushion damper DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 42 is the same as that in embodiment 1. As shown in fig. 180 to 182, the ratchet clutch mechanism 52 includes: the first inner ring 1, the first outer ring 2, the first return spring 4, the first left clutch support 5, the first right clutch support 6, the first clutch rivet 7, the first pawl 11, the first positioning mechanism 19, the second pawl 20 and the second return spring 21. In the radial direction, the first outer ring 2 is arranged outside the first inner ring 1. The first outer ring 2, the first left clutch support 5, the first right clutch support 6, the first positioning mechanism 19 and the first inner ring 1 are coaxially arranged. The first inner race 1, the first outer race 2, the first return spring 4, the first right clutch bracket 6, the first clutch rivet 7, the first pawl 11, the first positioning mechanism 19, the second pawl 20, and the second return spring 21 are disposed on the right side of the first left clutch bracket 5. The first inner race 1 is connected to and rotates with a driven member (not shown) of the machine M. The first outer ring 2 is directly or indirectly connected with the second friction plate 212 of the damping device DM and rotates together with the second friction plate 212. The first pawls 11 are engaged with the first outer race 2 at the initial position, and the second pawls 20 are engaged with the first outer race 2 at the initial position, when the first outer race 2 is fixed with respect to the first inner race 1 in both the forward rotation direction (the direction indicated by the arrow in fig. 180) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 180). The first outer race 2 is configured with ratchet-like projections and recesses, and the first pawls 11 and the second pawls 20 have at least a function of engaging with and disengaging from the ratchet-like projections and the ratchet-like recesses. The first clutch rivet 7 comprises a plurality of rivets, and the first right clutch bracket 6 is fixedly connected with the first inner ring 1 through the first clutch rivet 7. The first pawl 11 comprises a plurality of pawls, the first pawl 11 is mounted on the first inner ring 1, the first pawl 11 rotates together with the first inner ring 1, and the first pawl 11 can rotate relative to the first inner ring 1 within a certain angle range. The first pawl 11 is connected with the first right clutch bracket 6, the first pawl 11 rotates together with the first right clutch bracket 6, and the first pawl 11 can rotate relative to the first right clutch bracket 6 within a certain angle range. The second pawls 20 include a plurality of pawls, the second pawls 20 are mounted on the first inner race 1, the second pawls 20 rotate together with the first inner race 1, and the second pawls 20 are rotatable with respect to the first outer race 2 within a range of angles. The second pawl 20 is connected to the first right clutch support 6, the second pawl 20 rotates together with the first right clutch support 6, and the second pawl 20 is rotatable within a certain angle range with respect to the first right clutch support 6. The first return spring 4 includes a plurality of springs, and the first return spring 4 is mounted on the first inner race 1 and rotates together with the first inner race 1. The first return spring 4 is connected to a first pawl 11, and when the effect of other restraint or load on the first pawl 11 is smaller than the elastic effect of the first return spring 4 on the first pawl 11, the first pawl 11 is restored to the initial position by the elastic force of the first return spring 4. The second return spring 21 includes a plurality of springs, and the second return spring 21 is mounted on the first inner race 1 and rotates together with the first inner race 1. The second return spring 21 is connected to the second pawl 20, and when the action of other restraint or load on the second pawl 20 is smaller than the elastic action of the second return spring 21 on the second pawl 20, the second pawl 20 returns to the initial position under the elastic action of the second return spring 21. When the first pawls 11 and the second pawls 20 are engaged with the first outer race 2, the first outer race 2 is fixed in both the forward rotation direction (the direction indicated by the arrow in fig. 180) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 180) with respect to the first inner race 1 within a certain load range. When the first pawls 11 and the second pawls 20 are disengaged from the first outer race 2, the first outer race 2 is rotatable with respect to the first inner race 1 in both the forward rotation direction (the direction indicated by the arrow in fig. 180) and the reverse rotation direction (the opposite direction indicated by the arrow in fig. 180) within a certain load range. As shown in fig. 231, when the first pawls 11 are engaged with the first outer race 2 (ratchet wheel), the contact pair of the first pawls 11 and the first outer race 2 (ratchet wheel) has a self-locking function: the first pawl 11 is engaged with the first outer ring 2 (ratchet wheel) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first outer ring 2 (ratchet wheel) is F, μ is the friction coefficient between the first pawl 11 and the contact surface of the first outer ring 2 (ratchet wheel), F is the friction force between the first pawl 11 and the first outer ring 2 (ratchet wheel), FN is the normal acting force between the first pawl 11 and the first outer ring 2 (ratchet wheel), θ is the included angle between F and FN, in a certain load range, when θ < arctan (μ) and when the engaging force F between the first pawl 11 and the first outer ring 2 (ratchet wheel) is large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F, the first pawls 11 and the first outer race 2 (ratchet wheel) do not disengage themselves. As shown in fig. 231, when the second pawls 20 are engaged with the first outer race 2 (ratchet wheel), the contact pair of the second pawls 20 and the first outer race 2 (ratchet wheel) has a self-locking function: the second pawl 20 is engaged with the first outer ring 2 (ratchet wheel) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first outer ring 2 (ratchet wheel) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first outer ring 2 (ratchet wheel), F is the friction force between the second pawl 20 and the first outer ring 2 (ratchet wheel), FN is the normal acting force between the second pawl 20 and the first outer ring 2 (ratchet wheel), θ is the included angle between F and FN, in a certain load range, when θ < arctan (μ) and when the engaging force F between the second pawl 20 and the first outer ring 2 (ratchet wheel) is large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F, the second pawls 20 do not disengage themselves from the first outer race 2 (ratchet). The first left clutch support 5 is connected with the first inner ring 1 and rotates together with the first inner ring 1, and the first left clutch support 5 can move back and forth along the axial direction relative to the first left half clutch 15 under the action of the third gear shifting fork 316. The first positioning mechanism 19 is directly connected with the first inner ring 1, the first positioning mechanism 19 and the first inner ring 1 rotate together, and the first positioning mechanism 19 is fixed relative to the first inner ring 1 in the axial direction. Two axial positioning grooves are constructed on the first left clutch support 5, the first positioning mechanism 19 is connected with the first left clutch support 5, and the first positioning mechanism 19 is axially positioned at two axial positions of the first left clutch support 5 through the two axial positioning grooves. The first left clutch bracket 5 is connected with the third shift fork 316, the first left clutch bracket 5 is connected with the first pawl 11, and the first left clutch bracket 5 is connected with the second pawl 20. The first left clutch carrier 5 selectively effects engagement or disengagement of the first pawl 11 with the first outer ring 2 under drive of the third shift fork 316, and the first shift sleeve 18 selectively effects engagement or disengagement of the second pawl 20 with the first outer ring 2 under drive of the third shift fork 316. When the first left clutch bracket 5 is located at a left position of two axial positions axially relative to the first inner race 1 under the action of the third shift fork 316, under the action of the first left clutch bracket 5, the first return spring 4 and the second return spring 21, the first pawl 11 and the first outer race 2 are in an engaged state, and the second pawl 20 and the first outer race 2 are in an engaged state, at this time, the first outer race 2 is fixed in both forward rotation (a direction indicated by an arrow in fig. 180) and reverse rotation (a direction opposite to a direction indicated by an arrow in fig. 180) relative to the first inner race 1. When the first left clutch bracket 5 is located at a right position of two axial positions relative to the first inner race 1 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first outer race 2 are in a separated state and the second pawl 20 and the first outer race 2 are in a separated state under the action of the first left clutch bracket 5, the first return spring 4 and the second return spring 21, and at this time, the first outer race 2 is rotatable relative to the first inner race 1 in both forward rotation (a direction indicated by an arrow in fig. 180) and reverse rotation (a direction opposite to a direction indicated by an arrow in fig. 180).

Example 43

As shown in fig. 358 to 360, the shift device GD includes: ratchet clutch mechanism 52, damping device DM and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 43 is the same as embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 43 is the same as that in embodiment 3. As shown in fig. 183 to 185, the ratchet clutch mechanism 52 includes: the first inner ring 1, the first outer ring 2, the first return spring 4, the first left clutch support 5, the first right clutch support 6, the first clutch rivet 7, the first pawl 11, the first positioning mechanism 19, the second pawl 20 and the second return spring 21. The ratchet clutch mechanism 52 in embodiment 43 is similar to embodiment 42 except that: in embodiment 43, the first inner ring 1 is connected to and rotates with a driving member (not shown) of the machine M. The first outer race 2 is directly or indirectly connected to the second friction plate 212 and rotates together with the second friction plate 212. The first pawls 11 are engaged with the first inner race 1 at the initial position, and the second pawls 20 are engaged with the first inner race 1 at the initial position, when the first inner race 1 is fixed with respect to the first outer race 2 in both the forward rotation direction (the direction indicated by the arrow in fig. 183) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 180). The first right clutch bracket 6 is fixedly connected with the first outer ring 2 through the first clutch rivet 7. The first pawl 11, the second pawl 20, the first return spring 4, and the second return spring 21 are all mounted on the first outer race 2. When the first pawls 11 and the second pawls 20 are disengaged from the first inner race 1, the first inner race 1 is rotatable in both the forward rotation direction (the direction indicated by the arrow in fig. 183) and the reverse rotation direction (the direction opposite to the direction indicated by the arrow in fig. 180) with respect to the first outer race 2 within a certain load range. The first left clutch support 5 is connected with the first outer ring 2 and rotates together with the first outer ring 2, and the first left clutch support 5 can move back and forth along the axial direction relative to the first outer ring 2 under the action of the third gear shifting fork 316. The first positioning mechanism 19 is directly connected with the first outer ring 2, the first positioning mechanism 19 rotates with the first outer ring 2, and the first positioning mechanism 19 is axially fixed relative to the first outer ring 2. Two axial positioning grooves are constructed on the first left clutch support 5, the first positioning mechanism 19 is connected with the first left clutch support 5, and the first positioning mechanism 19 is axially positioned at two axial positions of the first left clutch support 5 through the two axial positioning grooves. When the first left clutch bracket 5 is located at a left position of two axial positions axially relative to the first outer ring 2 under the action of the third shift fork 316, under the action of the first left clutch bracket 5, the first return spring 4 and the second return spring 21, the first pawl 11 and the first inner ring 1 are in an engaged state, and the second pawl 20 and the first inner ring 1 are in an engaged state, at this time, the first outer ring 2 is fixed in both forward rotation (a direction indicated by an arrow in fig. 183) and reverse rotation (a direction opposite to a direction indicated by an arrow in fig. 180) relative to the first inner ring 1. When the first left clutch bracket 5 is located at a right position of two axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, under the action of the first left clutch bracket 5, the first return spring 4 and the second return spring 21, the first pawl 11 and the first inner ring 1 are in a separated state, and the second pawl 20 and the first inner ring 1 are in a separated state, at this time, the first outer ring 2 is rotatable relative to the first inner ring 1 in both forward rotation (a direction indicated by an arrow in fig. 183) and reverse rotation directions (a direction indicated by an arrow in fig. 180).

Example 44

As shown in fig. 361 to 363, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 44 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 44 is the same as that in embodiment 1. The one-way clutch mechanism 51 is shown in FIGS. 107 to 110. The one-way clutch mechanism 51 in embodiment 44 is similar to the ratchet clutch mechanism 52 in embodiment 42, except that: in embodiment 44, the one-way clutch mechanism 51 eliminates the second pawls 20 and the second return springs 21 and adds the first stopper pin 13 and the first auxiliary outer race 12. The first left clutch carrier 5 selectively effects engagement or disengagement of the first pawl 11 with or from the first outer race 2 under drive of the third shift fork 316. When the first left clutch bracket 5 is located at a left position of two axial positions relative to the first inner race 1 in the axial direction by the third shift fork 316, the first pawl 11 and the first outer race 2 are in an engaged state by the first left clutch bracket 5 and the first return spring 4, and at this time, the first outer race 2 is rotatable in the forward direction (the direction indicated by the arrow in fig. 109) and fixed in the reverse direction (the reverse direction indicated by the arrow in fig. 109) relative to the first inner race 1. When the first left clutch bracket 5 is located at a right position of two axial positions relative to the first inner race 1 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first outer race 2 are in a disengaged state under the action of the first left clutch bracket 5 and the first return spring 4, and at this time, the first outer race 2 is rotatable relative to the first inner race 1 in both a forward direction (a direction indicated by an arrow in fig. 109) and a reverse direction (a reverse direction indicated by an arrow in fig. 109). The first limiting pin 13 comprises a plurality of pins, and the first limiting pin 13 is directly or indirectly fixedly connected with the first outer ring 2. The first auxiliary outer race 12 is connected to the first outer race 2 by the first stopper pin 13, and the first auxiliary outer race 12 at least has a function of being rotatable with respect to the first outer race 2 within an angular range defined by the first stopper pin 13 by the direct action of the first pawl 11. The first auxiliary outer ring 12 is arranged coaxially on the right side of the first outer ring 2 in the axial direction. As shown in fig. 109, when the first left clutch bracket 5 is located at the left position of two axial positions in the axial direction with respect to the first inner ring 1 by the third shift fork 316, and when the first outer ring 2 rotates forward (in the direction of the arrow in fig. 109) with respect to the first inner ring 1, after the first auxiliary outer ring 12 rotates to the angle defined by the first limit pin 13 with respect to the first outer ring 2 by the first pawl 11, a part of the surface of the first auxiliary outer ring 12 is split into a cylindrical surface with a part of the surface of the first outer ring 2, and the first pawl 11 rotates with respect to the first outer ring 2 to contact the split cylindrical surface, thereby greatly reducing noise.

Example 45

As shown in fig. 364 to 366, the shift device GD includes: a one-way clutch mechanism 51, a damping device DM and an actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 45 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 45 is the same as that in embodiment 1. The one-way clutch mechanism 51 is shown in FIGS. 111 to 114. The one-way clutch mechanism 51 in embodiment 45 is similar to the ratchet clutch mechanism 52 in embodiment 43, except that: in embodiment 45, the one-way clutch mechanism 51 eliminates the second pawls 20 and the second return springs 21 and adds the first stopper pin 13 and the first auxiliary inner race 14. The first left clutch carrier 5 selectively effects engagement or disengagement of the first pawl 11 with or from the first inner race 1 under drive of the third shift fork 316. When the first left clutch bracket 5 is located at a left position of two axial positions relative to the first outer race 2 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first inner race 1 are in an engaged state under the action of the first left clutch bracket 5 and the first return spring 4, and at this time, the first inner race 1 is fixed in the forward rotation direction (the direction indicated by an arrow in fig. 113) and is rotatable in the reverse rotation direction (the reverse direction indicated by an arrow in fig. 113) relative to the first outer race 2. When the first left clutch bracket 5 is located at a right position of two axial positions relative to the first outer race 2 in the axial direction under the action of the third shift fork 316, the first pawl 11 and the first inner race 1 are in a disengaged state under the action of the first left clutch bracket 5 and the first return spring 4, and at this time, the first inner race 1 is rotatable relative to the first outer race 2 in both a forward rotation direction (a direction indicated by an arrow in fig. 113) and a reverse rotation direction (a reverse direction indicated by an arrow in fig. 113). The first limiting pin 13 comprises a plurality of pins, and the first limiting pin 13 is fixedly connected with the first inner ring 1. The first auxiliary inner ring 14 is connected to the first inner ring 1 through the first limit pin 13, and the first auxiliary inner ring 14 at least has a function of being rotatable relative to the first inner ring 1 within an angular range defined by the first limit pin 13 under the direct action of the first pawl 11. The first auxiliary inner ring 14 is coaxially arranged on the right side of the first inner ring 1 in the axial direction. As shown in fig. 113, when the first left clutch bracket 5 is located at a left position of two axial positions relative to the first outer ring 2 in the axial direction under the action of the third shift fork 316, and when the first inner ring 1 is rotated reversely relative to the first outer ring 2, after the first auxiliary inner ring 14 is rotated relative to the first inner ring 1 to an angle defined by the first limit pin 13 under the action of the first pawl 11, a partial surface of the first auxiliary inner ring 14 is split into a cylindrical surface with a partial surface of the first inner ring 1, and the first pawl 11 is contacted with the split cylindrical surface when rotated relative to the first inner ring 1, so that noise is greatly reduced.

Example 46

The utility model also provides a concentrate clutch GCD, use among the concentrated clutch GCD the utility model discloses a shift unit GD, as shown in fig. 367 ~ 369, include: jaw clutch mechanism 53, damping device DM, and actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 46 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 46 is the same as that in embodiment 1. The jaw clutch mechanism 53 is shown in fig. 194 to 195. The dog clutch mechanism 53 in embodiment 46 is the same as in embodiment 19. The jaw clutch mechanism 53 is driven by the actuating device AM to realize various clutch functions, and the damping device DM has a function of damping or eliminating vibration and impact generated in the process of separating and engaging the jaw clutch mechanism 53.

Example 47

The utility model also provides a parking device PD, used in the parking device PD the utility model discloses a gearshift GD, as shown in figure 370 ~ 372, include: ratchet clutch mechanism 52, actuating device AM. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 47 is the same as in embodiment 11. The ratchet clutch mechanism 52 is shown in FIGS. 139 to 141. The ratchet clutch mechanism 52 in embodiment 47 is similar to that in embodiment 32, except that: as shown in fig. 231, when the first pawl 11 and the first right clutch half 16 (ratchet wheel) are in an engaged state, the contact pair of the first pawl 11 and the first right clutch half 16 (ratchet wheel) has an overload protection function: the first pawl 11 is in an engaged state with the first right half clutch 16 (ratchet) under the action of the first return spring 4, the engaging force between the first pawl 11 and the first right half clutch 16 (ratchet) is F, μ is the friction coefficient between the contact surfaces of the first pawl 11 and the first right half clutch 16 (ratchet), F is the friction force between the first pawl 11 and the first right half clutch 16 (ratchet), FN is the normal acting force between the first pawl 11 and the first right half clutch 16 (ratchet), θ is the included angle between F and FN, when θ > arctan (μ) and the engaging force F between the first pawl 11 and the first right half clutch 16 (ratchet) is too large, the first pawl 11 is under the action of the engaging force F, the elastic force of the first return spring 4 and the friction force F in a certain load range, the first pawl 11 is disengaged from the first right half clutch 16 (ratchet wheel). As shown in fig. 231, when the second pawl 20 is engaged with the first right clutch half 16 (ratchet wheel), the contact pair of the second pawl 20 and the first right clutch half 16 (ratchet wheel) has an overload protection function: the second pawl 20 is in an engaged state with the first right clutch half 16 (ratchet) under the action of the second return spring 21, the engaging force between the second pawl 20 and the first right clutch half 16 (ratchet) is F, μ is the friction coefficient between the second pawl 20 and the contact surface of the first right clutch half 16 (ratchet), F is the friction force between the second pawl 20 and the first right clutch half 16 (ratchet), FN is the normal acting force between the second pawl 20 and the first right clutch half 16 (ratchet), θ is the included angle between F and FN, when θ > arctan (μ) and the engaging force between the second pawl 20 and the first right clutch half 16 (ratchet) is too large, the second pawl 20 is under the action of the engaging force F, the elastic force of the second return spring 21 and the friction force F in a certain load range, the second pawl 20 is self-disengaging from the first right half clutch 16 (ratchet).

Example 48

The utility model also provides a differential mechanism DM, used in the differential mechanism DM the utility model discloses a gearshift GD, as shown in fig. 373 ~ 375, include: the ratchet clutch mechanism 52, the buffer damping device DM, the actuating device AM, the inter-wheel differential DIF, the left half shaft LHS and the right half shaft RHS. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 48 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The damper device DM according to embodiment 48 is the same as the ratchet clutch mechanism 52 according to embodiment 1, as shown in fig. 139 to 141. The ratchet clutch mechanism 52 in embodiment 48 is the same as that in embodiment 32. The differential DIF outputs power and drives a vehicle (not shown) through the left half shaft LHS and the right half shaft RHS, respectively, the first right half clutch 16 is fixedly connected with the second friction plate 212 in the rotation direction, the first left half clutch 15 is fixedly connected with the left half shaft LHS in the rotation direction, and the second outer ring 220 is fixedly connected with the casing of the inter-wheel differential DIF in the rotation direction. The ratchet clutch mechanism 52 is driven by the third actuator motor 301, thereby indirectly bringing the left half shaft LHS into engagement or disengagement with the case of the inter-wheel differential DIF. When the left half shaft LHS is in an engaged state with the case of the inter-wheel differential DIF, the left half shaft LHS is rotationally fixed relative to the case of the inter-wheel differential DIF within a certain load range; when the left half shaft LHS is in a separated state from the case of the inter-wheel differential DIF, the left half shaft LHS is rotatable in a rotational direction relative to the case of the inter-wheel differential DIF within a certain load range.

Example 49

The utility model also provides a differential mechanism DM, used in the differential mechanism DM the utility model discloses a gearshift GD, as shown in fig. 376 ~ 378, include: ratchet clutch 52, damping device DM, actuator AM, center differential CDIF, front drive shaft FDS, rear drive shaft RDS. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 49 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 49 is the same as that in embodiment 1. The ratchet clutch mechanism 52 is shown in FIGS. 139 to 141. The ratchet clutch mechanism 52 in embodiment 48 is the same as that in embodiment 32. The center differential CDIF outputs power through the front drive shaft FDS and the rear drive shaft RDS, respectively, and drives a vehicle (not shown), the first right half clutch 16 is fixedly connected to the second friction plate 212 in the rotational direction, the first left half clutch 15 is fixedly connected to the front drive shaft FDS in the rotational direction, and the second outer ring 220 is fixedly connected to the housing of the center differential CDIF in the rotational direction. The ratchet clutch mechanism 52 is driven by the third actuator motor 301, thereby indirectly bringing the front drive shaft FDS into and out of engagement with the case of the center differential CDIF. When the front drive shaft FDS is in an engaged state with the case of the center differential CDIF, the front drive shaft FDS is rotationally fixed relative to the case of the center differential CDIF within a certain load range; when the front drive shaft FDS is in a disengaged state from the case of the center differential CDIF, the front drive shaft FDS is rotatable in a rotational direction relative to the case of the center differential CDIF within a certain load range.

Example 50

The utility model also provides a safety device, used among the safety device the utility model discloses a gearshift GD, as shown in fig. 379 ~ 381, include: ratchet clutch mechanism 52, buffer damping device DM, actuating device AM, arresting cable AAG, guide wheel mechanism GW. The actuator AM is shown in fig. 208. The actuating device AM in embodiment 50 is the same as in embodiment 11. The cushion damper device DM is shown in fig. 11 to 13. The cushion damper device DM in embodiment 50 is the same as that in embodiment 1. The ratchet clutch mechanism 52 is shown in FIGS. 139 to 141. The ratchet clutch mechanism 52 in embodiment 50 is similar to that in embodiment 32 except that: the first left clutch half 15 is fixedly connected to a frame (not shown) of the safety device, and the first right clutch half 16 is connected to the second friction plate 212 and rotates together with the second friction plate 212. The arresting cable AAG is mainly used to intercept various moving objects (not shown). The arresting cable AAG is wound around the second outer ring 220, the end of the arresting cable AAG is fixedly connected to the second outer ring 220, and the first right clutch half 16 is fixedly connected to the second friction plate 212 in the rotation direction. The shift sleeve 18 is driven by the actuating device AM, so that the first pawl 11 and the second pawl 20 are engaged or disengaged with the first right clutch half 16, and the arresting cable AAG has the function of rapidly intercepting a plurality of moving objects.

Claims

1. A Gearshift Device (GD) with damping function for connecting at least two parts, members or components of a machine (M) to each other and/or for carrying out a power engagement function and/or a power disengagement function and/or for carrying out a motion engagement function and/or a motion disengagement function and/or for carrying out a deceleration, stopping or holding in a stopped condition of a moving part of said machine (M), characterized in that:

the shifting device (GD) with a damping function comprises at least a damping Device (DM), and/or a clutch device (CM), and/or an adjusting device (RM), and/or an actuating device (AM), and/or a detector device (SD);

the buffer damping Device (DM) is at least provided with a certain limiting function for the load born by the device; and/or

The damping Device (DM) is configured to have at least a function of limiting the amount of torque transmitted by itself; and/or

The damping Device (DM) is configured to have at least a function of limiting the magnitude of the load transmitted by itself; and/or

The damping Device (DM) is configured to have at least a function of limiting the magnitude of the power transmitted by itself; and/or

Said Damping Means (DM) being configured at least to limit the movement transmitted by itself; and/or

The damping Device (DM) is configured to at least have a function of limiting the magnitude of the load borne by the clutch device (CM); and/or

The damper Device (DM) is configured to have at least a function of limiting the amount of torque transmitted by the clutch device (CM); and/or

The damping Device (DM) is configured to have at least a function of limiting the magnitude of the load transmitted by the clutch device (CM); and/or

The damping Device (DM) is configured to have at least a function of limiting the magnitude of the power transmitted by the clutch device (CM); and/or

Said Damper Means (DM) being configured at least to limit the movement transmitted by said Clutch Means (CM); and/or

The damping Device (DM) is configured to have at least a certain damping function for the vibration generated during the power separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to have at least a certain damping function for the impact generated during the power separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to at least have a certain damping function for the vibration and impact generated during the power separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to at least have a function of eliminating vibration and impact generated during the power separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to have at least a certain damping function for the vibration generated during the movement separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to have at least a certain damping function for the impact generated during the movement separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to at least have a certain damping function for the vibration and impact generated during the movement separation and engagement of the clutch device (CM); and/or

The damping Device (DM) is configured to at least have a function of eliminating vibration and impact generated during the movement separation and engagement of the clutch device (CM); and/or

The buffering capacity or the damping magnitude of the buffering damping Device (DM) is adjusted or set by the structure of the DM; and/or

The damping capacity or damping magnitude of the damping Device (DM) is directly or indirectly adjusted or controlled by the adjusting device (RM); and/or

The amount of torque that can be transmitted by the damping Device (DM) is regulated or controlled directly or indirectly by the regulating device (RM); and/or

The size of the load which can be transferred by the damping Device (DM) is directly or indirectly adjusted or controlled by the adjusting device (RM); and/or

The magnitude of the power which can be transmitted by the damping Device (DM) is directly or indirectly regulated or controlled by the regulating device (RM); and/or

The size of the movement that can be transmitted by the Damping Means (DM) is adjusted or controlled directly or indirectly by the adjusting means (RM); and/or

Said Damper Means (DM) being directly or indirectly connected to said Clutch Means (CM); and/or

The cushion damper Device (DM) is arranged on a power transmission path from a power source of the machine (M) to an actuator of the machine (M);

the Clutch Means (CM) being configured at least to function as a selective engagement or disengagement; and/or

The clutch device (CM) is configured to have at least a function of selectively locking or unlocking; and/or

Said Clutch Means (CM) being configured at least to selectively engage or disengage the power of the connected moving parts; and/or

The Clutch Means (CM) being configured at least to selectively engage or disengage the movement of the coupled mobile element; and/or

Said Clutch Means (CM) being configured to have at least the function of selectively decelerating or stopping or maintaining a stopped condition the moving element to which it is connected; and/or

The clutch device (CM) is configured to have at least a function of selective one-way engagement or one-way disengagement; and/or

The clutch device (CM) is configured to have at least one function of one-way locking or one-way unlocking selectively; and/or

The clutch device (CM) is configured to have at least the function of selectively transmitting the power of the connected moving element in one direction; and/or

The clutch device (CM) is configured to have at least the function of selectively transmitting the motion of the connected moving element in one direction; and/or

The clutch device (CM) is configured to have at least the function of selectively keeping the moving part connected with the clutch device in a synchronous moving state; and/or

The Clutch Means (CM) being configured to have at least the function of selectively transmitting the power of one of the moving elements connected thereto to the other moving elements connected thereto, respectively; and/or

The Clutch Means (CM) being configured to have at least the function of selectively transmitting the motion of one of the moving elements connected thereto to the other moving elements connected thereto; and/or

The clutch device (CM) is configured to have at least the function of fixing the connected moving element in one direction selectively in the rotation direction; and/or

The clutch device (CM) is configured to have at least the function of selectively keeping the moving part connected with the clutch device in a one-way fixed state in the rotation direction; and/or

Said Clutch Means (CM) being configured to function at least as a means for selectively unidirectional acceleration or unidirectional deceleration of the coupled moving element; and/or

Said Clutch Means (CM) being configured to have at least the function of selectively decelerating or accelerating the coupled moving parts; and/or

The Clutch Means (CM) being configured to have at least the function of selectively stopping or maintaining the stopped state of the connected moving element; and/or

The clutch device (CM) has a self-disengaging and engaging function; and/or

The disengagement and engagement actions of the Clutch Means (CM) are driven or controlled directly or indirectly by the Actuation Means (AM); and/or

The clutch device (CM) has the functions of self locking and unlocking; and/or

The locking and unlocking actions of the clutch device (CM) are directly or indirectly driven or controlled by the actuating device (AM);

the actuation device (AM) is configured at least with a function of directly driving or controlling the disengagement and engagement of the clutch device (CM); and/or

-said Actuation Means (AM) are configured at least with the function of directly driving or controlling the various disengagement and engagement states of said Clutch Means (CM); and/or

The actuation device (AM) is configured at least with the function of indirectly driving or controlling the disengagement and engagement of the clutch device (CM); and/or

-said Actuation Means (AM) are configured to have at least the function of indirectly driving or controlling a plurality of disengagement states and a plurality of engagement states of said Clutch Means (CM); and/or

-said Actuation Means (AM) being configured at least with the function of directly or indirectly switching said Clutch Means (CM) between a disengaged condition and an engaged condition; and/or

-said Actuation Means (AM) being configured at least with the function of directly or indirectly switching said Clutch Means (CM) between a plurality of disengaged states and a plurality of engaged states; and/or

Said Actuating Means (AM) being directly or indirectly connected with said Clutch Means (CM); and/or

Said Actuating Means (AM) being directly or indirectly connected to the frame of said machine (M) and constrained against rotation and translation;

the adjusting device (RM) is configured to have at least a function of adjusting or controlling the magnitude of the damping directly or indirectly to the cushion damping Device (DM); and/or

The adjusting device (RM) is at least provided with a function of directly or indirectly adjusting or controlling the magnitude of the buffering capacity of the buffering damping Device (DM); and/or

Said adjusting means (RM) being directly or indirectly connected with said Damping Means (DM); and/or

Said adjusting means (RM) being connected directly or indirectly to the frame of said machine (M) and constrained against rotation and translation;

-said detector means (SD) are at least used to directly or indirectly detect the temperature, and/or the position, and/or the speed, and/or the load it is subjected to or transmits of said Damping Means (DM), and/or said Clutching Means (CM), and/or said Actuating Means (AM), and/or said adjusting means (RM); and/or

The detector device (SD) is directly or indirectly connected with the clutch device (CM); and/or

The detector device (SD) is directly or indirectly connected with the buffer damping Device (DM); and/or

The detector device (SD) is directly or indirectly connected with the actuating device (AM); and/or

The detector device (SD) is directly or indirectly connected with the adjusting device (RM); and/or

The detector device (SD) is connected directly or indirectly to the frame of the machine (M) and constrained against rotation and translation.

2. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a centrifugal clutch mechanism (50);

the centrifugal clutch mechanism (50) is configured to selectively realize the separation or the engagement of the centrifugal clutch mechanism directly or indirectly in a certain rotating speed range; and/or

The centrifugal clutch mechanism (50) is at least provided with a structure that the power of a moving part connected with the centrifugal clutch mechanism is selectively transmitted to another part connected with the centrifugal clutch mechanism by directly or indirectly utilizing centrifugal force in a certain rotating speed range; and/or

The centrifugal clutch mechanism (50) is at least provided with a structure that the motion of one moving part connected with the centrifugal clutch mechanism is selectively transmitted to the other part connected with the centrifugal clutch mechanism directly or indirectly by using centrifugal force in a certain rotating speed range; and/or

The centrifugal clutch mechanism (50) is at least provided with a function of selectively decelerating, stopping or keeping a stopped state of the connected moving parts directly or indirectly by using centrifugal force in a certain rotating speed range; and/or

The centrifugal clutch mechanism (50) is configured to at least selectively accelerate the connected moving member directly or indirectly by centrifugal force within a certain rotation speed range;

the centrifugal clutch mechanism (50) comprises at least: a first inner ring (1), a first outer ring (2), a first centrifugal pawl (3), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), and/or a first retainer (8), and/or a first bearing roller (9), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first retainer (8) being arranged coaxially with the first inner ring (1), the first outer ring (2), the first centrifugal pawl (3), the first return spring (4), And/or the first right clutch support (6), and/or the first clutch rivet (7), and/or the first cage (8), and/or the first bearing roller (9) are/is arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the moving part of the machine (M), the first centrifugal pawls (3) are in an engaged state with the first inner ring (1) in an initial position, and/or the first inner ring (1) and the first outer ring (2) are at least configured with ratchet-like projections and/or ratchet-like recesses, the first centrifugal pawls (3) are at least configured with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, and/or the first inner ring (1) and the first outer ring (2) are at least configured with tooth-like projections and/or tooth-like recesses, the first centrifugal pawls (3) are at least configured with a function of engaging with or disengaging from the tooth-like projections and/or tooth-like recesses, the first centrifugal pawl (3) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first centrifugal pawl (3) is directly or indirectly connected with the first return spring (4), the first centrifugal pawl (3) at least comprises one pawl, the first centrifugal pawl (3) at least is configured to realize the engagement or disengagement of the first centrifugal pawl (3) and the first inner ring (1) under the action of centrifugal force and the elastic force of the first return spring (4), the first return spring (4) at least comprises one spring, and the first return spring (4) at least is configured to have elasticity, and gradually decreases when the centrifugal force applied to the first centrifugal pawl (3), The first return spring (4) having at least the function of gradually returning the first centrifugal pawl (3) to the initial position, the first outer ring (2) transmitting its power or movement to the first inner ring (1) via the first centrifugal pawl (3) when the first centrifugal pawl (3) is engaged with the first inner ring (1), the first bearing roller (9) comprising at least two rollers, the first inner ring (1) being connected to the first outer ring (2) directly or indirectly via the first bearing roller (9), and/or the first bearing roller (9) having at least the function of positioning the relative position of the first inner ring (1) and the first outer ring (2) in the radial direction and/or the axial direction, the first cage (8) having at least the function of isolating and guiding the first bearing roller (9), and/or the first holder (8) has at least the function of holding the first bearing roller (9) in the centrifugal clutch mechanism (50), and/or the first holder (8) has at least the function of moving with the first bearing roller (9), the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left clutch support (5) is fixedly connected with the first outer ring (2) by the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is fixedly connected with the first outer ring (2) by the first clutch rivet (7); and/or

The centrifugal clutch mechanism (50) comprises at least: a first inner ring (1), a first outer ring (2), a first centrifugal pawl (3), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), and/or a first retainer (8), and/or a first bearing roller (9), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first retainer (8) being arranged coaxially with the first inner ring (1), the first outer ring (2), the first centrifugal pawl (3), the first return spring (4), And/or the first right clutch support (6), and/or the first clutch rivet (7), and/or the first cage (8), and/or the first bearing roller (9) are/is arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected to a moving part of the machine (M) and rotates with the moving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to a driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected to the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), the first centrifugal pawl (3) is in a separated state from the first outer ring (2) in an initial position, the first inner ring (1) and the first outer ring (2) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, and/or the first centrifugal pawl (3) is at least configured with a function of engaging with or separating from the ratchet-shaped protrusions and/or ratchet-shaped grooves, and/or the first inner ring (1) and the first outer ring (2) are at least configured with tooth-shaped protrusions and/or tooth-shaped grooves, and/or the first centrifugal pawl (3) is at least configured with the tooth-shaped protrusions and/or the tooth-shaped grooves Or a toothed groove, the first centrifugal pawl (3) being directly or indirectly connected to the first inner ring (1) and rotating together with the first inner ring (1), the first return spring (4) being directly or indirectly connected to the first inner ring (1) and rotating together with the first inner ring (1), the first centrifugal pawl (3) being directly or indirectly connected to the first return spring (4), the first centrifugal pawl (3) comprising at least one pawl, the first centrifugal pawl (3) being at least configured to self-effect engagement or disengagement of the first centrifugal pawl (3) with the first outer ring (2) under the action of centrifugal force and the spring force of the first return spring (4), the first return spring (4) comprising at least one spring, the first return spring (4) being at least configured to be resilient, -the first return spring (4) has at least the function of gradually returning the first centrifugal pawl (3) to the initial position when the centrifugal force to which the first centrifugal pawl (3) is subjected gradually decreases, -the first inner ring (1) transmits its power or motion to the first outer ring (2) via the first centrifugal pawl (3) when the first centrifugal pawl (3) is engaged with the first outer ring (2), -the first bearing roller (9) comprises at least two rollers, -the first inner ring (1) is connected to the first outer ring (2) directly or indirectly via the first bearing roller (9), -and/or the first bearing roller (9) has at least the function of positioning the relative position of the first inner ring (1) and the first outer ring (2) in the radial direction and/or in the axial direction, -the first cage (8) has at least the function of isolating and guiding the first bearing roller (9), and/or the first cage (8) has at least the function of retaining the first bearing roller (9) in the centrifugal clutch mechanism (50) and/or the first cage (8) has at least the function of moving with the first bearing roller (9), the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left clutch support (5) is fixedly connected with the first inner ring (1) by means of the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is fixedly connected with the first inner ring (1) by means of the first clutch rivet (7); and/or

The material of the first inner ring (1) at least has a certain vibration reduction or damping function; and/or

The material of the first outer ring (2) at least has certain vibration reduction or damping function; and/or

The material of the first centrifugal pawl (3) at least has a certain vibration reduction or damping function; and/or

The material of the first return spring (4) at least has a certain vibration damping or damping function; and/or

The material of the first left clutch bracket (5) at least has certain vibration reduction or damping function; and/or

The material of the first right clutch bracket (6) at least has certain vibration reduction or damping function; and/or

The material of the first clutch rivet (7) at least has certain vibration damping or damping function; and/or

The material of the first retainer (8) at least has certain vibration damping or damping function; and/or

The material of the first bearing roller (9) has at least a certain vibration or damping function.

3. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a one-way clutch mechanism (51);

the one-way clutch mechanism (51) is at least provided with a function of selectively transmitting power or movement to the connected moving part in one direction; and/or

The one-way clutch mechanism (51) is configured to have at least the function of selectively performing one-way deceleration, one-way stop or one-way keeping stop on the connected moving part; and/or

The one-way clutch mechanism (51) is configured to at least selectively maintain the connected moving parts in a one-way synchronous motion state; and/or

The one-way clutch mechanism (51) is configured to at least selectively accelerate or decelerate the one-way rotation of the connected moving part; and/or

The one-way clutch mechanism (51) is configured to have at least a function of selectively performing one-way deceleration, one-way stop or one-way holding stop of a moving part of the machine (M); and/or

The one-way clutch mechanism (51) is configured to have at least a function of selectively and unidirectionally transmitting the power or motion of one moving member connected thereto to the other member connected thereto; and/or

The one-way clutch mechanism (51) is configured to transmit the power or motion of a moving part of the machine (M) to the damping Device (DM) selectively in one direction; and/or

The one-way clutch mechanism (51) is configured to have at least a function of selectively and unidirectionally transmitting the power or motion of the cushion damper Device (DM) to a moving member of the machine (M);

The one-way clutch mechanism (51) includes at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first retainer (8), and/or a first bearing roller (9), a first sprag (10), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), the first retainer (8), and/or the first bearing roller (9) being arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first right clutch support (6), And/or the first clutch rivet (7), the first cage (8), and/or the first bearing roller (9), the first sprag (10) are/is arranged axially on one side of the first left clutch carrier (5), the first inner ring (1) is directly or indirectly connected with and rotates with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with and rotates with the cushion damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with and rotates with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with and rotates with the frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), the first wedge block (10) is in an initial position, the first inner ring (1) is unidirectionally fixed relative to the first outer ring (2) in a forward direction and unidirectionally rotatable in a reverse direction, or the first wedge block (10) is in an initial position, the first outer ring (1) is unidirectionally fixed relative to the first outer ring (2) in a forward direction and unidirectionally rotatable in a reverse direction, or the first wedge block (10) is in an, The first inner ring (1) is fixed in a unidirectional way in a reverse rotation direction and can rotate in a unidirectional way in a forward rotation direction relative to the first outer ring (2), the first wedge block (10) is in contact with the first inner ring (1) under the direct or indirect action of the first return spring (4), and/or the first wedge block (10) is in contact with the first outer ring (2) under the direct or indirect action of the first return spring (4), the first wedge block (10) comprises at least one wedge block, the first wedge block (10) is directly or indirectly connected with the first retainer (8) and rotates together with the first retainer (8), and/or the first wedge block (10) can rotate in a certain angle range relative to the first retainer (8), and the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first holder (8) and rotates together with the first holder (8), the first return spring (4) is directly or indirectly connected with the first sprag (10), the first sprag (10) restores the initial position under the action of the first return spring (4) when the action of other constraints or loads on the first sprag (10) is smaller than the action of the first return spring (4) on the first sprag (10), the first sprag (10) is at least configured to self-fix the first inner race (1) in a unidirectional forward or reverse direction with respect to the first outer race (2) under the action of the first inner race (1) and the first outer race (2) and the first return spring (4) when the first inner race (1) has a forward or reverse movement tendency with respect to the first outer race (2), and/or the first sprags (10) are at least configured to make the first inner ring (1) rotate unidirectionally in the reverse or forward direction relative to the first outer ring (2) by themselves under the action of the first inner ring (1) and the first outer ring (2) and the first return spring (4) when the first inner ring (1) has a tendency to move in reverse or forward direction relative to the first outer ring (2), the first bearing rollers (9) comprise at least two rollers, the first inner ring (1) is connected with the first outer ring (2) directly or indirectly through the first bearing rollers (9), and/or the first bearing rollers (9) are at least provided with a function of positioning in radial and/or axial direction the relative position of the first inner ring (1) and the first outer ring (2), the first cage (8) has at least the function of separating and guiding the first bearing roller (9), and/or the first cage (8) has at least the function of holding the first bearing roller (9) in the one-way clutch mechanism (51), and/or the first cage (8) has at least the function of moving with the first bearing roller (9), the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left clutch support (5) is fixedly connected with the first inner ring (1) by the first clutch rivet (7), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is fixedly connected with the first inner ring (1) by the first clutch rivet (7), and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2) by the first clutch rivet (7), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is fixedly connected with the first outer ring (2) by the first clutch rivet (7), a contact portion of the first inner ring (1) with the first bearing roller (9) axially overlaps a contact portion of the first inner ring (1) with the first sprag (10), or a contact portion of the first inner ring (1) with the first bearing roller (9) axially does not overlap a contact portion of the first inner ring (1) with the first sprag (10), and/or the contact portion on the first outer ring (2) with the first bearing roller (9) axially overlaps the contact portion on the first outer ring (2) with the first sprag (10), or the contact portion on the first outer ring (2) with the first bearing roller (9) axially does not overlap the contact portion on the first outer ring (2) with the first sprag (10); and/or

The one-way clutch mechanism (51) includes at least: a first inner ring (1), a first outer ring (2), a first middle ring (45), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first retainer (8), and/or a first bearing roller (9), a first sprag (10), a second sprag (46), a second return spring (21), a second retainer (47), and/or a second bearing roller (48), the first outer ring (2) being arranged radially outside the first middle ring (45), the first middle ring (45) being arranged outside the first inner ring (1), the first middle ring (45) being arranged between the first inner ring (1) and the first outer ring (2), the first inner ring (1), the first outer ring (2), And/or a first left clutch carrier (5), and/or a first right clutch carrier (6), the first cage (8), the second cage (47), and/or the first bearing roller (9), and/or the second bearing roller (48) are arranged coaxially with the first middle ring (45), the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first right clutch carrier (6), and/or the first clutch rivet (7), the first cage (8), and/or the first bearing roller (9), the first sprag (10), the second sprag (46), the second return spring (21), the second cage (47), and/or the second bearing roller (48) are arranged axially on one side of the first left clutch carrier (5), the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected to a frame of the machine (M), and/or the first middle ring (45) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first middle ring (45) is directly or indirectly connected to and rotates with the damping Device (DM), and/or the first middle ring (45) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first middle ring (45) is directly or indirectly fixedly connected to a frame of the machine (M), the first wedge block (10) is contacted with the first inner ring (1) under the direct or indirect action of the first return spring (4), and/or the first wedge block (10) is contacted with the first middle ring (45) under the direct or indirect action of the first return spring (4), the second wedge block (46) is contacted with the first outer ring (2) under the direct or indirect action of the second return spring (21), and/or the second wedge block (46) is contacted with the first middle ring (45) under the direct or indirect action of the second return spring (21), the first wedge block (10) is in an initial position, the first inner ring (1) is unidirectionally fixed in the forward rotation direction and unidirectionally rotatable in the reverse rotation direction relative to the first middle ring (45), or the first wedge block (10) is in an initial position, The first inner ring (1) is fixed in a unidirectional way in a reverse rotation direction and can rotate in a unidirectional way in a forward rotation direction relative to the first middle ring (45), the first outer ring (2) is fixed in a forward rotation direction and can rotate in a unidirectional way in a forward rotation direction relative to the first middle ring (45) when the second wedge block (46) is in an initial position, the first outer ring (2) is fixed in a reverse rotation direction and can rotate in a forward rotation direction relative to the first middle ring (45) when the second wedge block (46) is in an initial position, the first wedge block (10) comprises at least one wedge block, the first wedge block (10) is directly or indirectly connected with the first retainer (8) and can rotate together with the first retainer (8), and/or the first wedge block (10) can rotate in a certain angle range relative to the first retainer (8), and the first return spring (4) at least comprises one spring, and/or the first return spring (4) is directly or indirectly connected with the first cage (8) and rotates together with the first cage (8), the first return spring (4) is directly or indirectly connected with the first wedge (10), the first wedge (10) restores the initial position under the elastic force of the first return spring (4) when the effect of other constraints or loads on the first wedge (10) is smaller than the elastic force effect of the first return spring (4) on the first wedge (10), the second wedge (46) comprises at least one wedge, the second wedge (46) is directly or indirectly connected with the second cage (47) and rotates together with the second cage (47), and/or the second wedge (46) is rotatable within a certain angle range relative to the second cage (47), the second return spring (21) at least comprises one spring, and/or the second return spring (21) is directly or indirectly connected with the second retainer (47) and rotates together with the second retainer (47), the second return spring (21) is directly or indirectly connected with the second wedge (46), when the action of other restraint or load on the second wedge (46) is smaller than the action of the second return spring (21) on the second wedge (46), the second wedge (46) restores the initial position under the action of the elastic force of the second return spring (21), and when the first inner ring (1) has a forward rotation or reverse rotation movement trend relative to the first middle ring (45), under the action of the first inner ring (1), the first middle ring (45) and the first return spring (4), The first wedge block (10) is at least configured to fix the first inner ring (1) relative to the first middle ring (45) in a single direction in a forward or reverse rotation direction by itself, and/or when the first inner ring (1) has a tendency to move in a reverse or forward rotation direction relative to the first middle ring (45), under the action of the first inner ring (1) and the first middle ring (45) and the first return spring (4), the first wedge block (10) is at least configured to enable the first inner ring (1) to rotate in a single direction in a reverse or forward rotation direction relative to the first middle ring (45) by itself, and/or when the first outer ring (2) has a tendency to move in a forward or reverse rotation direction relative to the first middle ring (45), under the action of the first outer ring (2), the first middle ring (45) and the second return spring (21), The second wedge block (46) is at least configured to fix the first outer ring (2) relative to the first middle ring (45) in a single direction in a forward or reverse rotation direction by itself, and/or the second wedge block (46) is at least configured to make the first outer ring (2) rotatable in a single direction in a reverse or forward rotation direction relative to the first middle ring (45) by itself under the action of the first outer ring (2), the first middle ring (45) and the second return spring (21) when the first outer ring (2) has a tendency to move in a reverse or forward rotation direction relative to the first middle ring (45), the first bearing roller (9) comprises at least two rollers, the first inner ring (1) is connected with the first middle ring (45) directly or indirectly through the first bearing roller (9), and/or the first bearing roller (9) is at least configured to radially and/or axially connect the first inner ring (1) with the first inner ring (45) The relative position of the middle ring (45) has a positioning function, the second bearing roller (48) comprises at least two rollers, the first outer ring (2) is directly or indirectly connected with the first middle ring (45) through the second bearing roller (48), and/or the second bearing roller (48) has at least a function of positioning the relative position of the first outer ring (2) and the first middle ring (45) in the radial direction and/or the axial direction, the first retainer (8) has at least a function of isolating and guiding the first bearing roller (9), and/or the first retainer (8) has at least a function of retaining the first bearing roller (9) in the one-way clutch mechanism (51), and/or the first retainer (8) has at least a function of moving along with the first bearing roller (9), the second cage (47) has at least the function of separating and guiding the second bearing rollers (48), and/or the second cage (47) has at least the function of holding the second bearing rollers (48) in the one-way clutch mechanism (51), and/or the second cage (47) has at least the function of moving with the second bearing rollers (48), the first left clutch support (5) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left clutch support (5) is connected with the first middle ring (45) through the first clutch rivet (7), and/or the first right clutch support (6) is connected with the first middle ring (45) through the first clutch rivet (7), and/or the first left clutch support (5) is connected with the first inner ring (1) through the first clutch rivet (7), and/or the first right clutch support (6) is connected with the first inner ring (1) through the first clutch rivet (7), and/or the first left clutch support (5) is connected with the first clutch rivet (7) through the first clutch rivet (7) An outer ring (2) is fixedly connected, and/or the first right clutch support (6) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), a contact portion of the first inner ring (1) with the first bearing roller (9) is axially overlapped with a contact portion of the first inner ring (1) with the first sprag (10), or a contact portion of the first inner ring (1) with the first bearing roller (9) is axially non-overlapped with a contact portion of the first inner ring (1) with the first sprag (10), and/or a contact portion of the first middle ring (45) with the first bearing roller (9) is axially overlapped with a contact portion of the first middle ring (45) with the first sprag (10), or a contact portion of the first middle ring (45) with the first bearing roller (9) is axially overlapped with a contact portion of the first sprag (45) with the first sprag (10) (10) And/or a contact portion on the first outer race (2) with the second bearing rollers (48) and a contact portion on the first outer race (2) with the second sprags (46) in the axial direction, or a contact portion of the first outer race (2) with the second bearing roller (48) does not overlap with a contact portion of the first outer race (2) with the second sprag (46) in the axial direction, and/or the contact portion of the first center ring (45) with the second bearing roller (48) overlaps in the axial direction with the contact portion of the first center ring (45) with the second sprag (46), or the contact portion of the first center ring (45) with the second bearing roller (48) does not overlap with the contact portion of the first center ring (45) with the second sprag (46) in the axial direction; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first retainer (8), and/or a first bearing roller (9), a first sprag (10), a first left half clutch (15), a first right half clutch (16), the first right half clutch (16), and/or the first left clutch support (5), and/or the first right clutch support (6), the first retainer (8), and/or the first bearing roller (9) being arranged coaxially with the first left half clutch (15), and/or the first return spring (4), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first clutch rivet (7), The first cage (8), and/or the first bearing roller (9), the first sprag (10), the first left-half clutch (15) being arranged axially on one side of the first right-half clutch (16), the first left-half clutch (15) being directly or indirectly connected to and rotating with the driving part of the machine (M), and/or the first left-half clutch (15) being directly or indirectly connected to and rotating with the damping Device (DM), and/or the first left-half clutch (15) being directly or indirectly connected to and rotating with the driven part of the machine (M), and/or the first left-half clutch (15) being directly or indirectly fixedly connected to the machine frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first left half clutch (15) is fixed in a forward direction and can rotate in a reverse direction relative to the first right half clutch (16) when the first wedge block (10) is in an initial position, or the first wedge block (10) is in an initial position, the first left half clutch (15) is fixed in a reverse rotation direction relative to the first right half clutch (16) in a unidirectional mode and can rotate in a forward rotation direction in a unidirectional mode, and/or the first wedge block (10) and the first left half clutch (15) are in contact with each other under the direct or indirect action of the first return spring (4), and/or the first wedge block (10) and the first right half clutch (16) are in contact with each other under the direct or indirect action of the first return spring (4), and/or the first wedge block (10) comprises at least one wedge block, the first wedge block (10) is directly or indirectly connected with the first retainer (8) and rotates together with the first retainer (8), and the first wedge block (10) can rotate in a certain angle range relative to the first retainer (8), and/or the first return spring (4) comprises at least one spring, and/or the first return spring (4) is directly or indirectly connected with the first holder (8) and rotates together with the first holder (8), and/or the first return spring (4) is directly or indirectly connected with the first sprag (10), the first sprag (10) restores the initial position under the action of the spring force of the first return spring (4) when the action of other constraints or loads on the first sprag (10) is smaller than the action of the spring force of the first return spring (4) on the first sprag (10), and/or the first left half clutch (15) and the first right half clutch (16) and the first return spring (4) when the first left half clutch (15) has a tendency of forward or reverse movement with respect to the first right half clutch (16), The first wedge block (10) is at least configured to fix the first left half clutch (15) relative to the first right half clutch (16) in a single direction in a forward or reverse direction by itself, and/or the first wedge block (10) is at least configured to make the first left half clutch (15) rotatable in a single direction in a reverse or forward direction relative to the first right half clutch (16) by itself under the action of the first left half clutch (15) and the first right half clutch (16) and the first return spring (4) when the first left half clutch (15) has a tendency to move in a reverse or forward direction relative to the first right half clutch (16), and/or the first bearing roller (9) comprises at least two rollers, the first left half clutch (15) is connected to the first right half clutch (16) directly or indirectly through the first bearing roller (9), the first left half clutch (15) is connected to the first right half clutch (16) in a single direction, The first bearing roller (9) has at least the function of positioning the relative position of the first left-half clutch (15) and the first right-half clutch (16) in the radial direction and/or in the axial direction, and/or the first cage (8) has at least the function of isolating and guiding the first bearing roller (9), and/or the first cage (8) has at least the function of retaining the first bearing roller (9) in the one-way clutch mechanism (51), and/or the first cage (8) has at least the function of moving with the first bearing roller (9), and/or the first left clutch carrier (5) is directly or indirectly fixedly connected to the first left-half clutch (15), and/or the first right clutch carrier (6) is directly or indirectly fixedly connected to the first left-half clutch (15), and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first left clutch support (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first left clutch support (5) is fixedly connected with the first right half clutch (16) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first right half clutch (16) through the first clutch rivet (7), and/or the contact portion of the first left-half clutch (15) with the first bearing roller (9) radially overlaps with the contact portion of the first left-half clutch (15) with the first sprag (10), or the contact part of the first left-half clutch (15) with the first bearing roller (9) and the contact part of the first left-half clutch (15) with the first sprag (10) do not overlap in the radial direction, and/or the contact area of the first right clutch half (16) with the first bearing roller (9) and the contact area of the first right clutch half (16) with the first wedge (10) overlap in the radial direction, or the contact part of the first right clutch half (16) with the first bearing roller (9) and the contact part of the first right clutch half (16) with the first wedge (10) do not overlap in the radial direction; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4) and/or a first left clutch carrier (5) and/or a first right clutch carrier (6) and/or a first clutch rivet (7), a first cage (8) and/or a first bearing roller (9), a first wedge (10), a first left-half clutch (15), a first right-half clutch (16), a first intermediate clutch (23), a second wedge (46), a second return spring (21), a second cage (47) and/or a second bearing roller (48), the first left-half clutch (15), the first right-half clutch (16) and/or the first left clutch carrier (5) and/or the first right clutch carrier (6), the first cage (8), the second cage (47) and/or the first bearing roller (9) and/or the second bearing roller (48) being arranged coaxially with the first intermediate clutch (23), the first return spring (4) and/or the first left clutch support (5) and/or the first right clutch support (6) and/or the first clutch rivet (7), the first cage (8) and/or the first bearing roller (9), the first wedge (10), the first left half clutch (15), the first intermediate clutch (23), the second wedge (46), the second return spring (21), the second cage (47) and/or the second bearing roller (48) are arranged axially on one side of the first right half clutch (16), the first left half clutch (15) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the damping Device (DM) -a Device (DM) rotates together, and/or-the first left half-clutch (15) is directly or indirectly connected with and rotates with a driven member of the machine (M), and/or-the first left half-clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or-the first right half-clutch (16) is directly or indirectly connected with and rotates with a driving member of the machine (M), and/or-the first right half-clutch (16) is directly or indirectly connected with and rotates with the damping Device (DM), and/or-the first right half-clutch (16) is directly or indirectly connected with and rotates with a driven member of the machine (M), and/or the first right half-clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first intermediate-clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first intermediate-clutch (23) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first intermediate-clutch (23) is directly or indirectly connected with the driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first intermediate-clutch (23) is directly or indirectly fixedly connected with the frame of the machine (M), and the first wedge (10) and the first left half-clutch (15) are in contact with each other under the direct or indirect action of the first return spring (4), the first wedge block (10) and the first middle clutch (23) are contacted with each other under the direct or indirect action of the first return spring (4), the second wedge block (46) and the first right half clutch (16) are contacted with each other under the direct or indirect action of the second return spring (21), the second wedge block (46) and the first middle clutch (23) are contacted with each other under the direct or indirect action of the second return spring (21), the first wedge block (10) is in an initial position, the first left half clutch (15) is fixed in a one-way mode in a forward direction and can rotate in a one-way direction in a reverse direction relative to the first middle clutch (23) or the first wedge block (10) is in an initial position, the first left half clutch (15) is fixed in a one-way in a reverse direction and can rotate in a one-way in a forward direction relative to the first middle clutch (23), and/or the second wedge (46) is in the initial position, the first right half clutch (16) is fixed in one direction in the forward direction and can rotate in one direction in the reverse direction relative to the first middle clutch (23), or the second wedge (46) is in the initial position, the first right half clutch (16) is fixed in one direction in the reverse direction relative to the first middle clutch (23) and can rotate in one direction in the forward direction, the first wedge (10) comprises at least one wedge, the first wedge (10) is directly or indirectly connected with the first holder (8) and rotates together with the first holder (8), and/or the first wedge (10) can rotate in a certain angle range relative to the first holder (8), the first return spring (4) comprises at least one spring, and/or the first return spring (4) is directly or indirectly connected with the first holder (8) and can rotate in one direction The first retainer (8) rotates together, the first return spring (4) is directly or indirectly connected with the first wedge (10), the first wedge (10) restores the initial position under the elastic force of the first return spring (4) when the other constraint or load acts on the first wedge (10) less than the elastic force of the first return spring (4) on the first wedge (10), the second wedge (46) comprises at least one wedge, the second wedge (46) is directly or indirectly connected with the second retainer (47) and rotates together with the second retainer (47), and/or the second wedge (46) is rotatable within a certain angle range relative to the second retainer (47), the second return spring (21) comprises at least one spring, and/or the second return spring (21) is directly or indirectly connected with the first retainer (8) and rotates together with the first retainer (8) -the first cage (8) rotates together, the second return spring (21) is directly or indirectly connected to the second sprag (46), -the second sprag (46) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other constraints or loads on the second sprag (46) is less than the action of the spring force of the second return spring (21) on the second sprag (46), -the first sprag (10) is at least configured to self-fix the first left half-clutch (15) in a unidirectional manner in a forward or reverse direction with respect to the first intermediate clutch (23) under the action of the first left half-clutch (15) and the first intermediate clutch (23) and the first return spring (4) when the first left half-clutch (15) has a tendency to move in a forward or reverse direction with respect to the first intermediate clutch (23), and/or the first sprag (10) is at least configured to itself make the first left half-clutch (15) unidirectionally rotatable in the reverse or forward direction relative to the first intermediate clutch (23) under the action of the first left half-clutch (15) and the first intermediate clutch (23) and the first return spring (4) when the first left half-clutch (15) has a tendency to move in reverse or forward direction relative to the first intermediate clutch (23), and/or the second sprag (46) is at least configured to itself make the first right half-clutch (16) unidirectionally fixed in the forward or reverse direction relative to the first intermediate clutch (23) under the action of the first right half-clutch (16) and the first intermediate clutch (23) and the second return spring (21) when the first right half-clutch (16) has a tendency to move in forward or reverse direction relative to the first intermediate clutch (23), and/or when the first right half clutch (16) has a tendency to move in a reverse or forward direction relative to the first intermediate clutch (23), under the action of the first right half clutch (16) and the first intermediate clutch (23) and the second return spring (21), the second wedge (46) is at least configured to make the first right half clutch (16) rotate in a single direction relative to the first intermediate clutch (23) in the reverse or forward direction by itself, the first bearing roller (9) comprises at least two rollers, the first left half clutch (15) is connected with the first intermediate clutch (23) directly or indirectly through the first bearing roller (9), the first bearing roller (9) has at least a function of positioning relative positions of the first left half clutch (15) and the first intermediate clutch (23) in a radial direction and/or an axial direction, the second bearing rollers (48) comprise at least two rollers, the first right half clutch (16) is connected to the first intermediate clutch (23) directly or indirectly via the second bearing rollers (48), the second bearing rollers (48) have at least a function of positioning the relative position of the first right half clutch (16) and the first intermediate clutch (23) in the radial direction and/or the axial direction, the first cage (8) has at least a function of isolating and guiding the first bearing roller (9), and/or the first cage (8) has at least a function of retaining the first bearing roller (9) in the one-way clutch mechanism (51), and/or the first cage (8) has at least a function of moving with the first bearing roller (9), the second cage (47) has at least a function of isolating and guiding the second bearing rollers (48), and/or the second cage (47) has at least the function of holding the second bearing roller (48) in the one-way clutch mechanism (51), and/or the second cage (47) has at least the function of moving with the second bearing roller (48), the first left clutch carrier (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch carrier (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first left clutch carrier (5) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch carrier (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first left clutch carrier (5) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first left clutch support (5) is fixedly connected with the first middle clutch (23) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first middle clutch (23) through the first clutch rivet (7), and/or the first left clutch support (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first left clutch support (5) is fixedly connected with the first right half clutch (16) through the first clutch rivet (7), and/or the first right clutch carrier (6) is fixedly connected to the first right half clutch (16) by means of the first clutch rivet (7), the contact area of the first left half clutch (15) with the first bearing roller (9) radially overlaps with the contact area of the first left half clutch (15) with the first sprag (10), or the contact area of the first left half clutch (15) with the first bearing roller (9) radially does not overlap with the contact area of the first left half clutch (15) with the first sprag (10), the contact area of the first intermediate clutch (23) with the first bearing roller (9) radially overlaps with the contact area of the first intermediate clutch (23) with the first sprag (10), or the contact area of the first intermediate clutch (23) with the first bearing roller (9) radially overlaps with the first intermediate clutch (23) The contact portions of the wedges (10) do not overlap in the radial direction, the contact portion of the first right clutch half (16) with the second bearing roller (48) overlaps in the radial direction with the contact portion of the first right clutch half (16) with the second wedge (46), or the contact portion of the first right clutch half (16) with the second bearing roller (48) and the contact portion of the first right clutch half (16) with the second sprag (46) do not overlap in the radial direction, a contact portion of the first intermediate clutch (23) with the second bearing roller (48) radially overlaps with a contact portion of the first intermediate clutch (23) with the second sprag (46), or the contact portion of the first intermediate clutch (23) with the second bearing roller (48) and the contact portion of the first intermediate clutch (23) with the second sprag (46) do not overlap in the radial direction; and/or

The one-way clutch mechanism (51) includes at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first auxiliary outer ring (12), and/or a first limit pin (13), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12) being arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch support (5), And/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13) are/is arranged on one side of the first right clutch support (6) in the axial direction, the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a machine frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engagement state with the first outer ring (2) at an initial position, when the first outer ring (2) is unidirectionally fixed in a forward or reverse direction relative to the first inner ring (1), and/or the first pawl (11) is in a contact state with the first auxiliary outer ring (12) at an initial position -a closed state, in which the first auxiliary outer ring (12) is fixed in a unidirectional manner in a forward or reverse direction with respect to the first inner ring (1), and/or the first outer ring (2) is rotatable in a unidirectional manner in a reverse or forward direction with respect to the first inner ring (1) when the first pawl (11) is in a disengaged state with respect to the first outer ring (2), and/or the first auxiliary outer ring (12) is rotatable in a unidirectional manner in a reverse or forward direction with respect to the first inner ring (1) when the first pawl (11) is in a disengaged state with respect to the first auxiliary outer ring (12), the first inner ring (1) and the first outer ring (2) and the first auxiliary outer ring (12) being configured at least with ratchet-like projections and/or ratchet-like recesses, the first pawl (11) being configured at least with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) is in contact with the first outer ring (2) under the direct or indirect action of the first return spring (4), and/or the first pawl (11) is in contact with the first auxiliary outer ring (12) under the direct or indirect action of the first return spring (4), the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first inner ring (1), the first pawl (11) rotates together with the first inner ring (1), and/or the first pawl (11) can rotate relative to the first inner ring (1) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch support (5), the first pawl (11) rotates together with the first left clutch support (5), and/or the first pawl (11) is rotatable within an angular range relative to the first left clutch support (5), and/or the first pawl (11) is directly or indirectly connected to the first right clutch support (6), the first pawl (11) rotates with the first right clutch support (6), and/or the first pawl (11) is rotatable within an angular range relative to the first right clutch support (6), the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first inner race (1) and rotates with the first inner race (1), the first return spring (4) is directly or indirectly connected to the first pawl (11), when the effect of other constraints or loads on the first pawl (11) is smaller than the effect of the first return spring (4) on the first pawl (11), The first pawl (11) restores the initial position under the direct or indirect action of the first return spring (4), when the first outer ring (2) has a forward or reverse movement tendency relative to the first inner ring (1), under the action of the first outer ring (2) and the first return spring (4), the first pawl (11) and the first outer ring (2) are in an engaged state, at least the first pawl (11) is configured to fix the first outer ring (2) relative to the first inner ring (1) in a forward or reverse direction by itself, and/or when the first outer ring (2) has a reverse or forward movement tendency relative to the first inner ring (1), under the action of the first outer ring (2) and the first return spring (4), the first pawl (11) and the first outer ring (2) are in a disengaged state, The first pawl (11) is at least configured to make the first outer ring (2) rotate in one direction in the reverse rotation or forward rotation direction relative to the first inner ring (1) by itself, and/or when the first auxiliary outer ring (12) has a forward rotation or reverse rotation movement tendency relative to the first inner ring (1), the first pawl (11) is in an engaged state with the first auxiliary outer ring (12) under the action of the first auxiliary outer ring (12) and the first return spring (4), and the first pawl (11) is at least configured to make the first auxiliary outer ring (12) fix in one direction in the forward rotation or reverse rotation direction relative to the first inner ring (1) by itself, and/or when the first auxiliary outer ring (12) has a forward rotation or reverse rotation movement tendency relative to the first inner ring (1), the first auxiliary outer ring (12) and the first return spring (4), The first pawl (11) and the first auxiliary outer ring (12) are in a separated state, at least the first pawl (11) is configured to enable the first auxiliary outer ring (12) to rotate in a single direction in a reverse rotation direction or a forward rotation direction relative to the first inner ring (1) by itself, when the first pawl (11) and the first outer ring (2) are in an engaged state, a contact pair of the first pawl (11) and the first outer ring (2) has an overload protection function, when an acting force between the first pawl (11) and the first outer ring (2) is excessive, the first pawl (11) and the first outer ring (2) are automatically disengaged, and/or when the first pawl (11) and the first outer ring (2) are in an engaged state, the contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function, When the acting force between the first pawl (11) and the first outer ring (2) is large, the first pawl (11) and the first outer ring (2) contact pair can not be automatically disengaged, when the first pawl (11) and the first auxiliary outer ring (12) are in an engaged state, the first pawl (11) and the first auxiliary outer ring (12) contact pair has an overload protection function, when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, the first pawl (11) and the first auxiliary outer ring (12) are automatically disengaged, and/or when the first pawl (11) and the first auxiliary outer ring (12) are in an engaged state, the first pawl (11) and the first auxiliary outer ring (12) contact pair has a self-locking function, when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is large, the first pawl (11) and the first auxiliary outer ring (12) contact pair have a self-locking function, The first pawl (11) and the first auxiliary outer ring (12) contact pair can not be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left clutch bracket (5) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), the first right clutch bracket (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch bracket (6) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first limit pin (13) at least comprises one pin, and the first limit pin (13) is directly or indirectly fixedly connected with the first outer ring (2), the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the direct or indirect action of the first pawl (11), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), and under the direct or indirect action of the first pawl (11), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), when the first outer ring (2) rotates reversely or forwardly relative to the first inner ring (1), Under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, and the first pawl (11) contacts with the spliced cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first inner ring (1), a first outer ring (2), a first middle ring (45), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first auxiliary outer ring (12), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), a second pawl (20), a second return spring (21), and/or a second limit pin (24), wherein the first middle ring (45) is radially arranged between the first outer ring (2) and the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), And/or the first auxiliary outer ring (12), and/or the first auxiliary inner ring (14) is arranged coaxially with the first middle ring (45), the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first left clutch bracket (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), the second pawl (20), the second return spring (21), and/or the second limit pin (24) is arranged axially on one side of the first right clutch bracket (6), the first inner ring (1) is directly or indirectly connected with and follows the driving part of the machine (M) And/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M) And/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first middle ring (45) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first middle ring (45) is directly or indirectly connected with the damping buffer Device (DM) and rotates together with the damping buffer Device (DM), and/or the first middle ring (45) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first middle ring (45) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engaged state with the first inner ring (1) at an initial position, Wherein the first inner ring (1) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first middle ring (45), and/or the first pawl (11) is in an engaged state with the first auxiliary inner ring (14) at an initial position, wherein the first auxiliary inner ring (14) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first middle ring (45), and/or the second pawl (20) is in an engaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first middle ring (45), and/or the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first middle ring (45), the first inner ring (1) is unidirectionally rotatable in the reverse or forward direction with respect to the first middle ring (45) when the first pawls (11) are in a disengaged state with the first inner ring (1), and/or the first auxiliary inner ring (14) is unidirectionally rotatable in the reverse or forward direction with respect to the first middle ring (45) when the first pawls (11) are in a disengaged state with the first auxiliary inner ring (14), and/or the first outer ring (2) is unidirectionally rotatable in the reverse or forward direction with respect to the first middle ring (45) when the second pawls (20) are in a disengaged state with the first outer ring (2), and/or the first auxiliary outer ring (12) is unidirectionally rotatable in the reverse or forward direction with respect to the first middle ring (45) when the second pawls (20) are in a disengaged state with the first auxiliary outer ring (12), the first inner ring (1) and the first outer ring (2) and the first middle ring (45) and the first auxiliary outer ring (12), and the first auxiliary inner ring (14) are configured with at least ratchet-like protrusions and/or ratchet-like recesses, and the first pawl (11) and the second pawl (20) are configured with at least a function of engaging with or disengaging from the ratchet-like protrusions and/or ratchet-like recesses, the first pawl (11) and the first inner ring (1) are in contact with each other under the direct or indirect action of the first return spring (4), and/or the first pawl (11) and the first auxiliary inner ring (14) are in contact with each other under the direct or indirect action of the first return spring (4), and/or the second pawl (20) and the first outer ring (2) are in contact with each other under the direct or indirect action of the second return spring (21), and/or the second pawl (20) and the first auxiliary outer ring (12) are in contact with each other under the direct or indirect action of the second return spring (21), the first pawl (11) comprises at least one pawl, and/or the first pawl (11) is directly or indirectly connected with the first middle ring (45), the first pawl (11) rotates together with the first middle ring (45), the first pawl (11) can rotate relative to the first middle ring (45) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) rotates together with the first left clutch bracket (5), the first pawl (11) can rotate relative to the first left clutch bracket (5) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6) The first pawl (11) rotates together with the first right clutch carrier (6), the first pawl (11) can rotate relative to the first right clutch carrier (6) within a certain angle range, the second pawl (20) comprises at least one pawl, and/or the second pawl (20) is directly or indirectly connected with the first middle ring (45), the second pawl (20) rotates together with the first middle ring (45), the second pawl (20) can rotate relative to the first middle ring (45) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected with the first left clutch carrier (5), the second pawl (20) rotates together with the first left clutch carrier (5), the second pawl (20) can rotate relative to the first left clutch carrier (5) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected with the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the first return spring (4) is directly or indirectly connected with the first pawl (11), and the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the action of the elastic force of the second return spring (21), and when the first inner ring (1) has the trend of forward rotation or reverse rotation relative to the first middle ring (45), the first pawl (11) and the first inner ring (1) are in an engaged state under the action of the first middle ring (45) and the first return spring (4), The first pawl (11) is at least configured to fix the first inner ring (1) relative to the first middle ring (45) in a single direction in the positive or negative rotation direction by itself, and/or to separate the first pawl (11) from the first inner ring (1) under the action of the first middle ring (45) and the first return spring (4) when the first inner ring (1) has a tendency to move in the negative or positive rotation relative to the first middle ring (45), and at least configured to rotate the first inner ring (1) in a single direction in the negative or positive rotation direction relative to the first middle ring (45) by itself, and/or to return the first inner ring (2) under the action of the first middle ring (45) and the second return spring (21) when the first outer ring (2) has a tendency to move in the positive or negative rotation relative to the first middle ring (45), The second pawl (20) is in a state of engagement with the first outer ring (2), at least the second pawl (20) being configured to fix the first outer ring (2) in a single direction in a forward or reverse direction with respect to the first middle ring (45) by itself, and/or the second pawl (20) being in a state of disengagement with the first outer ring (2) under the action of the first middle ring (45) and the second return spring (21) when the first outer ring (2) has a tendency to move in a reverse or forward direction with respect to the first middle ring (45), at least the second pawl (20) being configured to rotate the first outer ring (2) in a single direction in a reverse or forward direction with respect to the first middle ring (45), and/or the first auxiliary inner ring (14) having a tendency to move in a single direction or reverse direction with respect to the first middle ring (45) when the first auxiliary inner ring (14) has a tendency to move in a single direction in a forward or reverse direction with respect to the first middle ring (45), Under the action of the first middle ring (45) and the first return spring (4), the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, at which time the first pawl (11) is at least configured to self-make the first auxiliary inner ring (14) unidirectionally fixed in the forward or reverse direction relative to the first middle ring (45), and/or under the action of the first middle ring (45) and the first return spring (4), the first pawl (11) and the first auxiliary inner ring (14) are in a disengaged state, at which time the first pawl (11) is at least configured to self-make the first auxiliary inner ring (14) unidirectionally rotatable in the reverse or forward direction relative to the first middle ring (45), when the first auxiliary inner ring (14) has a tendency to move in the reverse or forward direction relative to the first middle ring (45), and/or when the first auxiliary outer ring (12) has a forward or reverse movement tendency relative to the first middle ring (45), the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) under the action of the first middle ring (45) and the second return spring (21), when the second pawl (20) is at least configured to self-fix the first auxiliary outer ring (12) in a forward or reverse direction relative to the first middle ring (45) in a unidirectional manner, and/or when the first auxiliary outer ring (12) has a reverse or forward movement tendency relative to the first middle ring (45), the second pawl (20) is in a disengaged state with the first auxiliary outer ring (12) under the action of the first middle ring (45) and the second return spring (21), when the second pawl (20) is at least configured to self-fix the first auxiliary outer ring (12) relative to the first middle ring (45) in a disengaged state A middle ring (45) can rotate in a single direction in the reverse rotation or forward rotation direction, when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function, when an acting force between the first pawl (11) and the first inner ring (1) is overlarge, the first pawl (11) and the first inner ring (1) are automatically disengaged, and/or when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function, and when the acting force between the first pawl (11) and the first inner ring (1) is larger, the contact pair of the first pawl (11) and the first inner ring (1) cannot be automatically disengaged, and/or the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has an overload protection function, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has a self-locking function when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, and the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the second pawl (20) is in an engaged state with the first outer ring (2), the contact pair of the second pawl (20) and the first outer ring (2) has an overload protection function, the second pawl (20) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the second pawl (20) and the first outer ring (2), and/or the contact pair of the second pawl (20) and the first outer ring (2) has a self-locking function when the engaged state is performed between the second pawl (20) and the first outer ring (2), the contact pair of the second pawl (20) and the first outer ring (2) is not automatically disengaged when the applied force is large between the second pawl (20) and the first outer ring (2), and/or the second pawl (20) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary outer ring (12) has an overload protection function, the second pawl (20) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the second pawl (20) and the first auxiliary outer ring (12) has a self-locking function when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is in an engaged state, the contact pair of the second pawl (20) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is large, the first clutch rivet (7) at least comprises one rivet, and the first left clutch bracket (5) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first left clutch support (5) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first right clutch support (6) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), the second limit pin (24) at least comprises one pin, the second limit pin (24) is directly or indirectly fixedly connected with the first outer ring (2), and the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1) and under the action of the first pawl (11), The first auxiliary inner ring (14) at least has the function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range limited by the first limit pin (13), the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the second limit pin (24), And under the action of the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the second limit pin (24), the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1), and/or the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), when the first inner ring (1) rotates reversely or positively relative to the first middle ring (45), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates relative to the first inner ring (1) to the angle defined by the first limit pin (13), Part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced together to form a cylindrical surface, the first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first outer ring (2) rotates reversely or normally relative to the first middle ring (45), under the direct or indirect action of the second pawl (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the second limit pin (24) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, The second pawl (20) is in contact with the split cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary inner ring (14) being arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first right clutch support (6), And/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14) are/is arranged on one side of the first left clutch support (5) in the axial direction, the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a machine frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, when the first inner ring (1) is unidirectionally fixed in a forward or reverse direction relative to the first outer ring (2), and/or the first pawl (11) is in a contact state with the first auxiliary inner ring (14) at an initial position A closed state, in which the first auxiliary inner ring (14) is fixed in a unidirectional manner in a forward or reverse direction with respect to the first outer ring (2), the first inner ring (1) is rotatable in a unidirectional manner in a reverse or forward direction with respect to the first outer ring (2) when the first pawl (11) is in a disengaged state with respect to the first inner ring (1), and/or the first auxiliary inner ring (14) is rotatable in a unidirectional manner in a reverse or forward direction with respect to the first outer ring (2) when the first pawl (11) is in a disengaged state with respect to the first auxiliary inner ring (14), the first inner ring (1) and the first outer ring (2) and the first auxiliary inner ring (14) are at least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) is at least configured with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) is in contact with the first inner ring (1) under the direct or indirect action of the first return spring (4), and/or the first pawl (11) is in contact with the first auxiliary inner ring (14) under the direct or indirect action of the first return spring (4), the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first outer ring (2), the first pawl (11) rotates with the first outer ring (2), the first pawl (11) can rotate relative to the first outer ring (2) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) rotates with the first left clutch bracket (5), The first pawl (11) can rotate in a certain angle range relative to the first left clutch support (5), and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), the first pawl (11) rotates together with the first right clutch support (6), the first pawl (11) can rotate in a certain angle range relative to the first right clutch support (6), the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with the first pawl (11), and when the effect of other restraint or load on the first pawl (11) is smaller than the effect of the first return spring (4) on the elastic force of the first pawl (11), The first pawl (11) restores the initial position under the action of the elastic force of the first return spring (4), when the first inner ring (1) has a forward or reverse movement trend relative to the first outer ring (2), under the action of the first inner ring (1) and the first return spring (4), the first pawl (11) and the first inner ring (1) are in an engaged state, at the moment, the first pawl (11) is at least configured to fix the first inner ring (1) relative to the first outer ring (2) in a forward or reverse direction by itself, and/or when the first inner ring (1) has a forward or reverse movement trend relative to the first outer ring (2), under the action of the first inner ring (1) and the first return spring (4), the first pawl (11) and the first inner ring (1) are in a disengaged state, The first pawl (11) is at least configured to make the first inner ring (1) rotate in a single direction in a reverse rotation direction or a forward rotation direction relative to the first outer ring (2) by itself, and/or when the first auxiliary inner ring (14) has a forward rotation or reverse rotation movement tendency relative to the first outer ring (2), under the action of the first auxiliary inner ring (14) and the first return spring (4), the first pawl (11) is in an engaged state with the first auxiliary inner ring (14), and at least configured to make the first auxiliary inner ring (14) fix in a single direction in a forward rotation direction or a reverse rotation direction relative to the first outer ring (2) by itself, and/or under the action of the first auxiliary inner ring (14) and the first return spring (4), when the first auxiliary inner ring (14) has a forward rotation or reverse rotation movement tendency relative to the first outer ring (2), the first pawl (11) is at least configured to make the first auxiliary inner ring (14) fix in a single direction in a forward rotation direction or a reverse rotation direction relative, The first pawl (11) and the first auxiliary inner ring (14) are in a separated state, at least the first pawl (11) is configured to enable the first auxiliary inner ring (14) to rotate in a single direction in a reverse rotation direction or a forward rotation direction relative to the first outer ring (2) by itself, when the first pawl (11) and the first inner ring (1) are in an engaged state, a contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function, when an acting force between the first pawl (11) and the first inner ring (1) is excessive, the first pawl (11) and the first inner ring (1) are automatically disengaged, and/or when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function, When the acting force between the first pawl (11) and the first inner ring (1) is large, the first pawl (11) and the first inner ring (1) contact pair can not automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, the first pawl (11) and the first auxiliary inner ring (14) automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of self-locking, When the acting force between the first pawl (11) and the first auxiliary inner ring (14) is larger, the first pawl (11) and the first auxiliary inner ring (14) contact pair can not automatically disengage, the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left clutch bracket (5) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), the first right clutch bracket (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch bracket (6) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), and the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating for a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range defined by the first limit pin (13), the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1), and when the first inner ring (1) rotates reversely or positively relative to the first outer ring (2), Under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the first pawl (11) contacts with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), the first left half clutch (15), and/or the first right clutch bracket (6), and/or the first auxiliary right half clutch (17) being arranged coaxially with the first right half clutch (16), the first return spring (4), and/or the first right clutch bracket (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), the first right half clutch (16), And/or the first auxiliary right half clutch (17) is arranged axially on one side of the first right half clutch (16), and/or the first left half clutch (15) coaxially penetrates the first right half clutch (16), or the first right half clutch (16) coaxially penetrates the first left half clutch (15), the first right half clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with a damping Device (DM) and rotates with the damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with a frame of the machine (M) And/or the first left half clutch (15) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first left half clutch (15) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first left half clutch (15) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first left half clutch (15) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engaged state with the first right half clutch (16) at an initial position, and the first right half clutch (16) is fixed in a one-way direction in a forward or reverse rotation direction relative to the first left half clutch (15), and/or the first pawl (11) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way manner relative to the first left half clutch (15) in the forward or reverse direction, the first right half clutch (16) is rotatable in a one-way manner relative to the first left half clutch (15) in the reverse or forward direction when the first pawl (11) is in a disengaged state with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is rotatable in a one-way manner relative to the first left half clutch (15) in the reverse or forward direction when the first pawl (11) is in a disengaged state with the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) and the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) are configured with at least ratchet-shaped protrusions and/or ratchet-shaped recesses -grooves and the first pawl (11) is at least configured to engage or disengage with the ratchet-like protrusions and/or ratchet-like recesses, the first pawl (11) and the first right half clutch (16) are in contact with each other under direct or indirect action of the first return spring (4), and/or the first pawl (11) and the first auxiliary right half clutch (17) are in contact with each other under direct or indirect action of the first return spring (4), and/or the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first left half clutch (15), the first pawl (11) rotates together with the first left half clutch (15), the first pawl (11) is rotatable within an angular range relative to the first left half clutch (15), and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), the first pawl (11) rotates together with the first right clutch support (6), the first pawl (11) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), the first return spring (4) is directly or indirectly connected with the first pawl (11), and the first pawl (11) restores the initial position under the direct or indirect action of the first return spring (4) when the action of other restraint or load on the first pawl (11) is smaller than the action of the first return spring (4) on the first pawl (11), when the first right half clutch (16) has a forward or reverse rotation movement trend relative to the first left half clutch (15), the first pawl (11) and the first right half clutch (16) are in an engaged state under the action of the first right half clutch (16) and the first return spring (4), and at the same time, the first pawl (11) is at least configured to fix the first right half clutch (16) relative to the first left half clutch (15) in a forward or reverse rotation direction by itself, and/or when the first right half clutch (16) has a reverse or forward rotation movement trend relative to the first left half clutch (15), the first pawl (11) and the first right half clutch (16) are in a disengaged state under the action of the first right half clutch (16) and the first return spring (4), The first pawl (11) is at least configured to make the first right half clutch (16) rotate in a single direction in a reverse rotation or forward rotation direction relative to the first left half clutch (15) by itself, and/or when the first auxiliary right half clutch (17) has a forward rotation or reverse rotation movement trend relative to the first left half clutch (15), the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state under the action of the first auxiliary right half clutch (17) and the first return spring (4), and the first pawl (11) is at least configured to make the first auxiliary right half clutch (17) fixed in a single direction in a forward rotation or reverse rotation direction relative to the first left half clutch (15) by itself, and/or when the first auxiliary right half clutch (17) has a reverse rotation or forward rotation movement trend relative to the first left half clutch (15), the first pawl (11) is at least configured to make the first auxiliary right half clutch (17) fixed in a single direction in a reverse rotation or reverse rotation direction, Under the action of the first auxiliary right half clutch (17) and the first return spring (4), the first pawl (11) and the first auxiliary right half clutch (17) are in a separated state, at the same time, the first pawl (11) is at least configured to enable the first auxiliary right half clutch (17) to rotate in a single direction relative to the first left half clutch (15) in a reverse rotation direction or a forward rotation direction by itself, when the first pawl (11) and the first right half clutch (16) are in an engaged state, a contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function, when an acting force between the first pawl (11) and the first right half clutch (16) is overlarge, the first pawl (11) and the first right half clutch (16) are automatically disengaged, and/or when the first pawl (11) and the first right half clutch (16) are in an engaged state, The contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function, the contact pair of the first pawl (11) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is large, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has an overload protection function when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is in an engaged state, The contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has a self-locking function, when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) can not be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first right clutch bracket (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch bracket (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), the first limit pin (13) at least comprises one pin, and the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), under the direct or indirect action of the first pawl (11), the first auxiliary right half clutch (17) at least has a function of rotating a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), under the direct or indirect action of the first pawl (11), the first auxiliary right half clutch (17) at least has a function of rotating relative to the first right half clutch (16) within an angle range defined by the first limit pin (13), the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16), when the first left half clutch (15) rotates reversely or rotates forwardly relative to the first right half clutch (16), Under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially spliced to form a plane, and the first pawl (11) contacts with the spliced plane when rotating relative to the first right half clutch (16), so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a first shift gear sleeve (18), and/or a first positioning mechanism (19), wherein the first left half clutch (15), and/or the first right clutch support (6), and/or the first auxiliary right half clutch (17), the first shift gear sleeve (18), and/or the first positioning mechanism (19) are coaxially arranged with the first right half clutch (16), and the first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), The first pawl (11) and/or the first limit pin (13), the first left half clutch (15), the first right half clutch (16), and/or the first auxiliary right half clutch (17), the first shift sleeve (18), and/or the first positioning mechanism (19) are arranged axially on one side of the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first right half clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the cushion damping Device (DM) and rotates together with the cushion damping Device (DM), and/or the first right half-clutch (16) is directly or indirectly connected to and rotates with a driven member of the machine (M), and/or the first right half-clutch (16) is directly or indirectly fixedly connected to and rotates with a frame of the machine (M), and/or the first left half-clutch (15) is directly or indirectly connected to and rotates with a driving member of the machine (M), and/or the first left half-clutch (15) is directly or indirectly connected to and rotates with the damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected to and rotates with a driven member of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected to and rotates with a frame of the machine (M), the first pawl (11) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is unidirectionally fixed relative to the first left half clutch (15) in a forward or reverse direction and is unidirectionally rotatable in a reverse or forward direction, and/or the first pawl (11) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is unidirectionally fixed relative to the first left half clutch (15) in a forward or reverse direction and is unidirectionally rotatable in a reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is rotatable relative to the first left half clutch (15) at a normal and reverse direction, and/or the first pawl (11) is in a disengaged state from the first auxiliary right half clutch (17) in an initial position, in which the first auxiliary right half clutch (17) is rotatable relative to the first left half clutch (15) in both forward and reverse directions, the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) are at least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) is at least configured to have a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, and/or the first pawl (11) and the first right half clutch (16) are in contact with each other under the direct or indirect action of the first return spring (4) when the first shift sleeve (18) has no force on the first pawl (11), and/or the first pawl (11) and the first auxiliary right clutch half (17) are in contact with each other under the direct or indirect action of the first return spring (4) when the first shift sleeve (18) has no force on the first pawl (11), the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first left clutch half (15), the first pawl (11) rotates together with the first left clutch half (15), the first pawl (11) can rotate relative to the first left clutch half (15) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) rotates together with the first right clutch bracket (6), the first pawl (11) can rotate relative to the first right clutch bracket (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), the first return spring (4) is directly or indirectly connected with the first pawl (11), when other restraint or load acts on the first pawl (11) less than the action of the first return spring (4) on the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4), when the first pawl (11) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in a forward or reverse direction and can rotate in a reverse or forward direction in a one-way manner relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) is fixed in a one-way manner in the forward or reverse direction relative to the first left half clutch (15) and can rotate in a one-way manner in the reverse or forward direction within a certain load range, when the first pawl (11) is disengaged from the first right half clutch (16), the first right half clutch (16) can rotate in both the forward and reverse directions relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is disengaged from the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) can rotate in both the forward and reverse directions relative to the first left half clutch (15) within a certain load range, when the first pawl (11) is engaged with the first right half clutch (16), the first pawl (11) is engaged with the first right half clutch (16), The contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function, the first pawl (11) and the first right half clutch (16) are automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is overlarge, and/or the contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function when the first pawl (11) and the first right half clutch (16) are in an engaged state, the contact pair of the first pawl (11) and the first right half clutch (16) are not automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is large, and/or the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has an overload protection function, the first pawl (11) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is too large, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has a self-locking function when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, and the first pawl (11) and the first auxiliary right half clutch (17) are not automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first right clutch carrier (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch carrier (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), the first shift sleeve (18) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), the first left half clutch (15) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) selectively moves relative to the first left half clutch (15) in the axial direction against the effect of the first left half clutch (15), and/or at least one series of axial positioning grooves or protrusions are configured on the first left half clutch (15), the first shift sleeve (18) is configured at least in a certain range through the series of axial positioning grooves or protrusions -a function of axial positioning with respect to the first left clutch half (15), and/or-a function of axial positioning of the first shifting sleeve (18) directly or indirectly connected to the first right clutch carrier (6) and rotating with the first right clutch carrier (6), and/or-a function of axial positioning of the first shifting sleeve (18) with respect to the first right clutch carrier (6), with a certain limiting action of the first shifting sleeve (18) in the axial direction, -a function of selective movement of the first shifting sleeve (18) in the axial direction with respect to the first right clutch carrier (6) against the action of the first right clutch carrier (6), and/or-a function of at least a series of axial detents or projections configured on the first right clutch carrier (6), -a function of axial positioning of the first shifting sleeve (18) with respect to the first right clutch carrier (6) at least to a certain extent by means of the series of axial detents or projections, and/or the first positioning means (19) is directly or indirectly connected to the first left clutch half (15), the first positioning means (19) rotates together with the first left clutch half (15), the first positioning means (19) is axially fixed relative to the first left clutch half (15), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a limiting effect on the first shift sleeve (18) in the axial direction, Said first shifting sleeve (18) being selectively movable axially relative to said first left half clutch (15) against the action of said first positioning means (19) and/or said first shifting sleeve (18) being provided with a series of axial detents or protrusions, said first shifting sleeve (18) being configured at least to position at least one axial position thereof by said series of axial detents or protrusions in a range of constraint with said first positioning means (19), said first shifting sleeve (18) being directly or indirectly connected to said first pawl (11) and said first shifting sleeve (18) being selectively axially movable relative to said first left half clutch (15) in a range of at least directly or indirectly bringing said first pawl (11) into engagement or disengagement with said first right half clutch (16), and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11) and the selective axial displacement of the first shift sleeve (18) relative to the first left half-clutch (15) in a range brings at least the first pawl (11) and the first auxiliary right half-clutch (17) into or out of engagement and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve (18) is selectively axially displaced in a range relative to the first left half-clutch (15) under the drive of the actuating device (AM) and/or the first pawl (11) and the first right half-clutch (16) are brought into or out of engagement when the first shift sleeve (18) is in an intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is axially located close to the first right half clutch (16) directly or indirectly by the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is axially located away from the first right half clutch (16) directly or indirectly by the actuating device (AM), the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), And the first auxiliary right half clutch (17) has at least the function of rotating a certain angle relative to the first right half clutch (16) under the direct or indirect action of the first pawl (11), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), the first auxiliary right half clutch (17) has at least the function of rotating relative to the first right half clutch (16) within the angle range defined by the first limit pin (13) under the direct or indirect action of the first pawl (11), and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first right half clutch (16), Under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially spliced to form a plane, and the first pawl (11) contacts with the spliced plane when rotating relative to the first right half clutch (16), so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a second pawl (20), a second return spring (21), and/or a first auxiliary left half clutch (22), a first intermediate clutch (23), and/or a second limit pin (24), wherein the first left half clutch (15), the first right half clutch (16), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary right half clutch (17), and/or the first auxiliary left half clutch (22) and the first intermediate clutch (23) are coaxially arranged -the first return spring (4), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), and/or the first auxiliary right half clutch (17), the second pawl (20), the second return spring (21), and/or the first auxiliary left half clutch (22), the first intermediate clutch (23), the second limit pin (24) are arranged axially on one side of the first right half clutch (16), and/or the first intermediate clutch (23) coaxially passes through the first left half clutch (15), or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially penetrates the first right half clutch (16), or the first right half clutch (16) coaxially penetrates the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left half clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left half clutch (15) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first left half clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) -the driving part of the machine (M) rotates together, and/or-the first right half clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or-the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or-the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or-the first intermediate clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or-the first intermediate clutch (23) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first intermediate clutch (23) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engaged state with the first left half clutch (15) at an initial position, the first left half clutch (15) is fixed in a forward or reverse direction relative to the first intermediate clutch (23) in a unidirectional mode, and/or the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22) at an initial position, the first auxiliary left half clutch (22) is fixed in a forward or reverse direction relative to the first intermediate clutch (23) in a unidirectional mode, and/or the second pawl (20) is in an engaged state with the first half clutch (16) at an initial position, Wherein the first right half clutch (16) is fixed in a one-way manner in a forward or reverse direction relative to the first intermediate clutch (23), and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, wherein the first auxiliary right half clutch (17) is fixed in a one-way manner in a forward or reverse direction relative to the first intermediate clutch (23), and/or the first left half clutch (15) is rotatable in a one-way manner in a reverse or forward direction relative to the first intermediate clutch (23) when the first pawl (11) is in a disengaged state with the first left half clutch (15), and/or the first auxiliary left half clutch (22) is rotatable in a one-way direction in a reverse or reverse direction relative to the first intermediate clutch (23) when the first pawl (11) is in a disengaged state with the first auxiliary left half clutch (22) at an initial position, and/or when the second pawl (20) is in the disengaged state from the first right half clutch (16) in the initial position, the first right half clutch (16) can rotate in one direction relative to the first intermediate clutch (23) in the reverse or forward direction, and/or when the second pawl (20) is in the disengaged state from the first auxiliary right half clutch (17) in the initial position, the first auxiliary right half clutch (17) can rotate in one direction relative to the first intermediate clutch (23) in the reverse or forward direction, the first intermediate clutch (23) and the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) are at least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) and the second pawl (20) are at least configured with ratchet-like projections and/or ratchet-like recesses And/or a ratchet-like recess engagement or disengagement function, the first pawl (11) being in contact with the first left clutch half (15) under the direct or indirect action of the first return spring (4), and/or the first pawl (11) being in contact with the first auxiliary left clutch half (22) under the direct or indirect action of the first return spring (4), the second pawl (20) being in contact with the first right clutch half (16) under the direct or indirect action of the second return spring (21), and/or the second pawl (20) being in contact with the first auxiliary right clutch half (17) under the direct or indirect action of the second return spring (21), the first pawl (11) comprising at least one pawl, the first pawl (11) being directly or indirectly connected with the first intermediate clutch half (23), The first pawl (11) rotates together with the first intermediate clutch (23), the first pawl (11) is rotatable within an angular range relative to the first intermediate clutch (23), and/or the first pawl (11) is directly or indirectly connected to the first left clutch support (5), the first pawl (11) rotates together with the first left clutch support (5), the first pawl (11) is rotatable within an angular range relative to the first left clutch support (5), the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first intermediate clutch (23), the second pawl (20) rotates together with the first intermediate clutch (23), the second pawl (20) is rotatable within an angular range relative to the first intermediate clutch (23), and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected to the first pawl (11), and the second return spring (4) rotates together with the first intermediate clutch (23), When the action of other constraint or load on the first pawl (11) is smaller than the action of the first return spring (4) on the first pawl (11), the first pawl (11) returns to the initial position under the action of the elastic force of the first return spring (4), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other constraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), the second pawl (20) returns to the initial position under the action of the elastic force of the second return spring (21), when the first left half clutch (15) has a tendency of forward or reverse movement relative to the first intermediate clutch (23), under the action of the first left half clutch (15) and the first return spring (4), The first pawl (11) is engaged with the first left half clutch (15), at least the first pawl (11) being configured to fix the first left half clutch (15) in a unidirectional manner in a forward or reverse direction relative to the first intermediate clutch (23) by itself, and/or the first pawl (11) is disengaged from the first right half clutch (16) by the first left half clutch (15) and the first return spring (4) when the first left half clutch (15) has a tendency to move in a reverse or forward direction relative to the first intermediate clutch (23), at least the first pawl (11) being configured to rotate the first left half clutch (15) in a unidirectional manner in a forward or reverse direction relative to the first intermediate clutch (23) by itself, and/or the first auxiliary left half clutch (22) having a movement in a forward or reverse direction relative to the first intermediate clutch (23) when the first auxiliary left half clutch (11) has a tendency to move in a forward or reverse direction relative to the first intermediate clutch (23) by itself -on trend, under the action of the first auxiliary left half clutch (22) and the first return spring (4), the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22), while the first pawl (11) is at least configured to self-fix the first auxiliary left half clutch (22) in a one-way direction in a forward or reverse direction relative to the first intermediate clutch (23), and/or-on trend of reverse or forward movement of the first auxiliary left half clutch (22) relative to the first intermediate clutch (23), under the action of the first auxiliary left half clutch (22) and the first return spring (4), the first pawl (11) is in a disengaged state with the first auxiliary left half clutch (22), while the first pawl (11) is at least configured to self-fix the first auxiliary left half clutch (22) in a reverse or forward direction relative to the first intermediate clutch (23) Can rotate in one direction, and/or when the first right half clutch (16) has a forward or reverse rotation movement trend relative to the first middle clutch (23), the second pawl (20) and the first left half clutch (15) are in an engaged state under the action of the first right half clutch (16) and the second return spring (21), and at the same time, the second pawl (20) is at least configured to fix the first right half clutch (16) in one direction in the forward or reverse rotation direction relative to the first middle clutch (23) by itself, and/or when the first right half clutch (16) has a reverse or forward rotation movement trend relative to the first middle clutch (23), the second pawl (20) and the first right half clutch (16) are in a disengaged state under the action of the first right half clutch (16) and the second return spring (21), The second pawl (20) is at least configured to make the first right half clutch (16) rotate in a single direction in a reverse rotation direction or a forward rotation direction relative to the first middle clutch (23) by itself, and/or when the first auxiliary right half clutch (17) has a forward rotation or reverse rotation movement trend relative to the first middle clutch (23), the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) under the action of the first auxiliary right half clutch (17) and the second return spring (21), and at the same time, the second pawl (20) is at least configured to make the first auxiliary right half clutch (17) fix in a single direction in a forward rotation or a reverse rotation direction relative to the first middle clutch (23) by itself, and/or when the first auxiliary right half clutch (17) has a reverse rotation or a forward rotation trend relative to the first middle clutch (23), Under the action of the first auxiliary right half clutch (17) and the second return spring (21), the second pawl (20) and the first auxiliary right half clutch (17) are in a separated state, at the same time, the second pawl (20) is at least configured to enable the first auxiliary right half clutch (17) to rotate in a single direction relative to the first intermediate clutch (23) in a reverse rotation direction or a forward rotation direction by itself, when the first pawl (11) and the first left half clutch (15) are in an engaged state, a contact pair of the first pawl (11) and the first left half clutch (15) has an overload protection function, when an acting force between the first pawl (11) and the first left half clutch (15) is overlarge, the first pawl (11) and the first left half clutch (15) are automatically disengaged, and/or when the first pawl (11) and the first left half clutch (15) are in an engaged state, The contact pair of the first pawl (11) and the first left half clutch (15) has a self-locking function, the contact pair of the first pawl (11) and the first left half clutch (15) cannot be automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is in an engaged state, The contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) cannot be automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) is automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is excessive, and/or the contact pair of the second pawl (20) and the first right half clutch (16) is in an engaged state, The contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function, the contact pair of the second pawl (20) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is large, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has an overload protection function when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is in an engaged state, The contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) can not be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch support (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first left clutch support (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch support (6) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), the second limit pin (24) at least comprises one pin, the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) at least has the function of rotating for a certain angle relative to the first left half clutch (15), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), under the direct or indirect action of the first pawl (11), The first auxiliary left half clutch (22) has at least the function of being rotatable relative to the first left half clutch (15) within the angular range defined by the first limit pin (13), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the direct or indirect action of the second pawl (20), the first auxiliary right half clutch (17) has at least the function of being rotatable relative to the first right half clutch (16) by a certain angle, and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), under the direct or indirect action of the second pawl (20), the first auxiliary right half clutch (17) has at least the function of being rotatable relative to the first right half clutch (16) within the angular range defined by the second limit pin (24), and/or the first auxiliary left half clutch (22) is coaxially arranged on one side of the first left half clutch (15) in the radial direction, and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the first pawl (11), after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), or after the first auxiliary left half clutch (22) rotates to an angle defined by the first limit pin (13) relative to the first left half clutch (15), a partial surface of the first auxiliary left half clutch (22) and a partial surface of the first left half clutch (15) are radially combined into a plane, The first pawl (11) is in contact with the split plane when rotating relative to the first intermediate clutch (23) so as to greatly reduce noise, and/or when the first right half clutch (16) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, so that the second pawl (20) is in contact with the split plane when rotating relative to the first intermediate clutch (23), Thereby greatly reducing noise; and/or

The one-way clutch mechanism (51) includes at least: the first return spring (4), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), the first right half clutch (16), and/or the first auxiliary right half clutch (17), the first gear shift sleeve (18), and/or the first positioning mechanism (19), the second pawl (20), the second return spring (21), and/or the first auxiliary left half clutch (22), the first middle clutch (23), and/or the second limit pin (24), wherein the first left half clutch (15), the first right half clutch (16), and/or the first left clutch support (5), and/or the first right clutch support (6), And/or the first auxiliary right half clutch (17), the first shifting sleeve (18), and/or the first positioning mechanism (19), and/or the first auxiliary left half clutch (22) is arranged coaxially with the first intermediate clutch (23), and/or the first return spring (4), and/or the first left clutch carrier (5), and/or the first right clutch carrier (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), and/or the first auxiliary right half clutch (17), the first shifting sleeve (18), and/or the first positioning mechanism (19), the second pawl (20), the second return spring (21), And/or the first auxiliary left half-clutch (22), the first intermediate clutch (23), the second limit pin (24) are axially arranged on one side of the first right half-clutch (16), and/or the first intermediate clutch (23) coaxially passes through the first left half-clutch (15), or the first intermediate clutch (23) coaxially passes through the first right half-clutch (16), and/or the first left half-clutch (15) coaxially passes through the first right half-clutch (16), or the first right half-clutch (16) coaxially passes through the first left half-clutch (15), the first left half-clutch (15) is directly or indirectly connected with a driving member of the machine (M) and rotates together with the driving member of the machine (M), and/or the first left half-clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected to the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected to the frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected to the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected to the damping Device (DM) and rotates together with the damping Device (DM), and/or the first right half-clutch (16) is directly or indirectly connected to the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly fixedly connected to the frame of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first intermediate clutch (23) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engaged state with the first left half clutch (15) at an initial position, when the first left half clutch (15) is unidirectionally fixed in a reverse or reverse direction and unidirectionally rotatable in the reverse or forward direction relative to the first intermediate clutch (23), and/or the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22) at an initial position, at which the first auxiliary left half clutch (22) is fixed in a unidirectional manner in the forward or reverse direction and is rotatable in a unidirectional manner in the reverse or forward direction with respect to the first intermediate clutch (23), and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at an initial position, at which the first right half clutch (16) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first intermediate clutch (23) and is rotatable in a unidirectional manner in the reverse or forward direction, and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, at which the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction with respect to the first intermediate clutch (23) and is rotatable in a unidirectional manner in the reverse or forward direction with respect to the first intermediate clutch (23), and/or the first pawl (11) is in a disengaged state from the first left-half clutch (15) in the initial position, in which the first left-half clutch (15) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or the first pawl (11) is in a disengaged state from the first auxiliary left-half clutch (22) in the initial position, in which the first auxiliary left-half clutch (22) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or the second pawl (20) is in a disengaged state from the first right-half clutch (16) in the initial position, in which the first right-half clutch (16) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or the second pawl (20) is in a disengaged state from the first auxiliary right-half clutch (17) in the initial position, The first auxiliary right half clutch (17) can be rotated in both the forward and reverse direction relative to the first intermediate clutch (23), the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) and the first intermediate clutch (23) are at least configured with ratchet-shaped projections and/or ratchet-shaped recesses, and the first pawl (11) and the second pawl (20) are at least configured to have a function of engaging with or disengaging from the ratchet-shaped projections and/or ratchet-shaped recesses, and/or the first pawl (11) and the first left half clutch (15) are in contact with each other under the direct or indirect action of the first return spring (4) when the first shift sleeve (18) has no force on the first pawl (11), and/or the first pawl (11) is in contact with the first auxiliary left half clutch (22) under the direct or indirect action of the first return spring (4) when the first shift sleeve (18) is not acting on the first pawl (11), and/or the second pawl (20) is in contact with the first right half clutch (16) under the direct or indirect action of the second return spring (21) when the first shift sleeve (18) is not acting on the second pawl (20), and/or the second pawl (20) is in contact with the first auxiliary right half clutch (17) under the direct or indirect action of the second return spring (21) when the first shift sleeve (18) is not acting on the second pawl (20), the first pawl (11) comprising at least one pawl, the first pawl (11) is directly or indirectly connected to the first intermediate clutch (23), the first pawl (11) rotates together with the first intermediate clutch (23), the first pawl (11) can rotate relative to the first intermediate clutch (23) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected to the first left clutch support (5), the first pawl (11) rotates together with the first left clutch support (5), the first pawl (11) can rotate relative to the first left clutch support (5) within a certain angle range, the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first intermediate clutch (23), the second pawl (20) rotates together with the first intermediate clutch (23), Said second pawl (20) being rotatable within an angular range relative to said first intermediate clutch (23) and/or said second pawl (20) being directly or indirectly connected to said first right clutch support (6), said second pawl (20) being rotatable with said first right clutch support (6), said second pawl (20) being rotatable within an angular range relative to said first right clutch support (6), said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first intermediate clutch (23) and rotatable with said first intermediate clutch (23), said second return spring (21) comprising at least one spring, said second return spring (21) being directly or indirectly connected to said first intermediate clutch (23) and rotatable with said first intermediate clutch (23), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the action of the elastic force of the first return spring (4) when the action of other restraint or load on the first pawl (11) is smaller than the action of the first return spring (4) on the first pawl (11), the second return spring (21) is directly or indirectly connected with the second pawl (20), the second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21) when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), and the first pawl (11) and the first left half clutch (15) are engaged within a certain load range, The first left half clutch (15) is fixed in a unidirectional manner in the forward or reverse direction and is rotatable in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the first auxiliary left half clutch (22) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) and is rotatable in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is engaged with the first auxiliary left half clutch (22), and/or the first left half clutch (15) is rotatable in both the forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first auxiliary left half clutch (22), and/or the first pawl (11) is disengaged from the first auxiliary left half clutch (22), The first auxiliary left half clutch (22) can rotate in the forward and reverse directions relative to the first intermediate clutch (23) within a certain load range, and/or the first right half clutch (16) can be fixed in a unidirectional manner in the forward or reverse direction and can rotate in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) can be fixed in a unidirectional manner in the forward or reverse direction and can rotate in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is engaged with the first auxiliary right half clutch (17), and/or the second auxiliary left half clutch (22) can rotate in a unidirectional manner in the reverse or reverse direction relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is disengaged from the first right half clutch (16), The first right half clutch (16) can rotate in the forward and reverse directions relative to the first intermediate clutch (23) within a certain load range, and/or the first auxiliary right half clutch (17) can rotate in the forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is disengaged from the first auxiliary right half clutch (17), the contact pair of the first pawl (11) and the first left half clutch (15) has an overload protection function when the first pawl (11) and the first left half clutch (15) are in an engaged state, the first pawl (11) and the first left half clutch (15) are automatically disengaged when an excessive force is applied between the first pawl (11) and the first left half clutch (15), and/or the first pawl (11) and the first left half clutch (15) are in an engaged state The contact pair of the first pawl (11) and the first left half clutch (15) has a self-locking function, the contact pair of the first pawl (11) and the first left half clutch (15) cannot be automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is in an engaged state, The contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) cannot be automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) is automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is excessive, and/or the contact pair of the second pawl (20) and the first right half clutch (16) is in an engaged state, The contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function, the contact pair of the second pawl (20) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is large, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has an overload protection function when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is in an engaged state, The contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) can not be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch support (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first left clutch support (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch support (6) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first shifting sleeve (18) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a certain limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is axially selectively movable relative to the first intermediate clutch (23) against the effect of the first intermediate clutch (23), and/or at least one series of axial positioning grooves or projections are formed on the first intermediate clutch (23), the first shifting sleeve (18) is at least configured to perform a function of axially positioning relative to the first intermediate clutch (23) through the series of axial positioning grooves or projections in a certain range, and/or the first shifting sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5) And/or the first left clutch carrier (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively axially displaceable relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or the first left clutch carrier (5) is at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least provided with the function of axially positioning relative to the first left clutch carrier (5) within a certain range by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and rotates together with the first right clutch carrier (6), and/or the first right clutch carrier (6) has a certain limit effect on the first shift sleeve (18) in the axial direction A braking action, the first shift sleeve (18) being selectively axially displaceable relative to the first right clutch carrier (6) against the action of the first right clutch carrier (6), and/or the first right clutch carrier (6) being provided with at least one series of axial recesses or projections, the first shift sleeve (18) being designed to perform at least one function of axially positioning relative to the first right clutch carrier (6) within a certain range by means of the series of axial recesses or projections, and/or the first positioning means (19) being directly or indirectly connected to the first intermediate coupling (23), the first positioning means (19) rotating together with the first intermediate coupling (23), the first positioning means (19) being axially fixed relative to the first intermediate coupling (23), and/or the first positioning means (19) being directly or indirectly connected to the first left clutch carrier (5), The first positioning means (19) rotates together with the first left clutch carrier (5), the first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left half clutch (15) against the effect of the first positioning means (19), and/or the first shifting sleeve gear (18) is provided with a series of axial positioning grooves or bulges, the first shifting sleeve gear (18) is at least configured to position at least one axial position of the first positioning mechanism (19) through the restraining action of the series of axial positioning grooves or bulges and the first positioning mechanism in a certain range, and/or the first shifting sleeve gear (18) is directly or indirectly connected with the first pawl (11), and the first shifting sleeve gear (18) is at least directly or indirectly in a joint or separation state with the first left half clutch (15) through the selective axial movement in a certain range relative to the first intermediate clutch (23), and/or the first shifting sleeve gear (18) is directly or indirectly connected with the first pawl (11), and the first sleeve gear (18) is at least in a certain range through the axial movement in a certain range relative to the first intermediate clutch (23) Directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first auxiliary left clutch half (22), and/or directly or indirectly bringing the first shift sleeve (18) into connection with the second pawl (20) and selectively axially moving the first shift sleeve (18) relative to the first intermediate clutch (23) within a certain range brings at least the second pawl (20) into engagement or disengagement with the first right clutch half (16), and/or directly or indirectly bringing the first shift sleeve (18) into connection with the second pawl (20) and selectively axially moving the first shift sleeve (18) relative to the first intermediate clutch (23) within a certain range brings at least the second pawl (20) into engagement or disengagement with the first auxiliary right clutch half (17), and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve (18) is selectively axially displaced within a range relative to the first intermediate clutch (23) under the drive of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is in an intermediate position in the axial direction under the action of the actuating device (AM) directly or indirectly, and/or the second pawl (20) is in a position close to the first left half clutch (15) in the axial direction under the action of the actuating device (AM), The first pawl (11) is in a connected or disconnected state with the first left half clutch (15), the second pawl (20) is in a connected or disconnected state with the first right half clutch (16), and/or the first pawl (11) is in a connected or disconnected state with the first left half clutch (15), the second pawl (20) is in a connected or disconnected state with the first right half clutch (16) when the first shift sleeve (18) is in a position axially close to the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), and/or the first limit pin (13) comprises at least one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), and the second limit pin (24) comprises at least one pin, the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) at least has the function of rotating for a certain angle relative to the first left half clutch (15), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), and under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) at least has the function of rotating relative to the first left half clutch (15) within the angle range defined by the first limit pin (13), the first auxiliary left half clutch (17) is directly or indirectly connected with the first right half clutch (16), And the first auxiliary right half clutch (17) is at least provided with a function of rotating a certain angle relative to the first right half clutch (16) under the direct or indirect action of the second pawl (20), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), and the first auxiliary right half clutch (17) is at least provided with a function of rotating relative to the first right half clutch (16) within the angle range defined by the second limit pin (24) under the direct or indirect action of the second pawl (20), the first auxiliary left half clutch (22) is coaxially arranged on one side of the first left half clutch (15) in the radial direction, and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, when the first left half clutch (15) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the first pawl (11), after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), or after the first auxiliary left half clutch (22) rotates to an angle defined by the first limit pin (13) relative to the first left half clutch (15), part of the surface of the first auxiliary left half clutch (22) and part of the surface of the first left half clutch (15) are radially combined to form a plane, the first pawl (11) rotates relative to the first intermediate clutch (23) and is in contact with the combined plane, so that noise is greatly reduced, and/or when the first right half clutch (16) rotates reversely or forwardly relative to the first intermediate clutch (23), Under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially split into a plane, so that the second pawl (20) contacts with the split plane when rotating relative to the first intermediate clutch (23), and the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first left clutch carrier (5), a first right clutch carrier (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a first shift sleeve (18), and/or a first positioning mechanism (19), a first shift cam (25), and/or a first drive pin (26), wherein the first right clutch carrier (6), and/or the first left clutch carrier (5), the first right half clutch (16), and/or the first auxiliary right half clutch (17), the first shift sleeve (18), and/or the first positioning mechanism (19), the first shift cam (25) and the first left half clutch (15) are coaxially arranged, the first return spring (4) and/or the first left clutch support (5), the first right clutch support (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), the first right half clutch (16) and/or the first auxiliary right half clutch (17), the first shift gear sleeve (18) and/or the first positioning mechanism (19), the first shift cam (25) and/or the first transmission pin (26) are/is arranged on one side of the first left half clutch (15) in the axial direction, and/or the first left half clutch (15) coaxially penetrates the first right half clutch (16) or the first right half clutch (16) coaxially penetrates the first left half clutch (15), and the first left half clutch (16) is directly or indirectly connected with a driving part of the machine (M) and is connected with the driving part of the machine (M) -the driving part of the machine (M) rotates together, and/or-the first right half clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or-the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or-the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or-the first left half clutch (15) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or-the first left half clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left half clutch (15) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first left half clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first right half clutch (16) at an initial position, when the first right half clutch (16) is fixed in a one-way manner relative to the first left half clutch (15) in a forward or reverse direction and can rotate in a one-way direction in a reverse or forward direction, and/or the first pawl (11) is in an engagement state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in a forward or reverse direction and can rotate in a one-way in a reverse or forward direction relative to the first left half clutch (15), and/or the first pawl (11) is in a disengaged state in the initial position with the first right half clutch (16), in which the first right half clutch (16) is rotatable relative to the first left half clutch (15) in both forward and reverse directions, and/or the first pawl (11) is in a disengaged state in the initial position with the first auxiliary right half clutch (17), in which the first auxiliary right half clutch (17) is rotatable relative to the first left half clutch (15) in both forward and reverse directions, the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) and the first shift cam (25) are configured at least with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) is configured at least with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, and/or the first pawl (11) is in contact with the first right half clutch (16) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), and/or the first pawl (11) is in contact with the first auxiliary right half clutch (17) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), the first pawl (11) comprising at least one pawl, the first pawl (11) being directly or indirectly connected to the first left half clutch (15), the first pawl (11) rotating together with the first left half clutch (15), the first pawl (11) being rotatable relative to the first left half clutch (15) within a certain angular range, and/or the first pawl (11) is directly or indirectly connected to the first right clutch support (6), the first pawl (11) rotates together with the first right clutch support (6), the first pawl (11) is rotatable within an angular range relative to the first right clutch support (6), the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first left clutch half (15) and rotates together with the first left clutch half (15), and/or the first return spring (4) is directly or indirectly connected to the first pawl (11), the first pawl (11) returns to the initial position under the spring force of the first return spring (4) when other constraints or loads act on the first pawl (11) less than the first return spring (4) acts on the first pawl (11), when the first pawl (11) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in a one-way manner in the forward or reverse rotation direction and can rotate in a one-way manner in the reverse or forward rotation direction relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) is fixed in a one-way manner in the forward or reverse rotation direction relative to the first left half clutch (15) and can rotate in a one-way manner in the reverse or forward rotation direction within a certain load range, and/or when the first pawl (11) is disengaged from the first right half clutch (16), the first right half clutch (16) can rotate in both the forward and reverse rotation directions relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is separated from the first auxiliary right half clutch (17), within a certain load range, the first auxiliary right half clutch (17) can rotate relative to the first left half clutch (15) in both forward and reverse directions, when the first pawl (11) is in an engaged state with the first right half clutch (16), the contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function, when an acting force between the first pawl (11) and the first right half clutch (16) is excessive, the first pawl (11) and the first right half clutch (16) are automatically disengaged, and/or when the first pawl (11) is in an engaged state with the first right half clutch (16), the contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function, When the acting force between the first pawl (11) and the first right half clutch (16) is large, the first pawl (11) and the first right half clutch (16) contact pair can not automatically disengage, and/or when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the first pawl (11) and the first auxiliary right half clutch (17) contact pair has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is excessive, the first pawl (11) and the first auxiliary right half clutch (17) automatically disengage, and/or when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the first pawl (11) and the first auxiliary right half clutch (17) contact pair has the function of self-locking, and when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, When the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, the first pawl (11) and the first auxiliary right half clutch (17) contact pair cannot be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch support (5) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first left clutch support (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch support (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and the first shifting tooth sleeve (18) is directly or indirectly connected with the first left clutch support (5) and is connected with the first left clutch support (5) The clutch carrier (5) rotates together, and/or the first left clutch carrier (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or at least the first left clutch carrier (5) is provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least configured to perform the function of axial positioning relative to the first left clutch carrier (5) through the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected with the first right clutch carrier (6) and rotates together with the first right clutch carrier (6), and/or the first right clutch carrier (6) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first right clutch carrier (6) against the effect of the first right clutch carrier (6), and/or at least the first right clutch carrier (6) is provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least configured to perform the function of axial positioning relative to the first right clutch carrier (6) through the series of axial positioning grooves or projections in a certain range, and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch carrier (5), and the first positioning mechanism (19) rotates together with the first left clutch carrier (5), The first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) axially limits the first shift sleeve (18), the first shift sleeve (18) is axially selectively movable relative to the first left half clutch (15) against the action of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first shift sleeve (18), The first shifting sleeve (18) is at least configured to position at least one of its axial positions by the constraining action of the series of axial detents or protrusions with the first positioning mechanism (19) within a certain range, and/or the first drive pin (26) is directly or indirectly connected with the first shifting sleeve (18) and the first drive pin (26) rotates with the first shifting sleeve (18), and/or the first drive pin (26) is directly or indirectly connected with the first shifting cam (25), the first drive pin (26) is at least configured to push the first shifting cam (25) to rotate within a certain angular range relative to the first left half clutch (15) within a certain axial range, and/or the first shifting cam (25) is directly or indirectly connected with the first left half clutch (15), The first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first left clutch half (15) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first left clutch bracket (5), and the first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first left clutch bracket (5) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first right clutch bracket (6), and the first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first right clutch bracket (6) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first pawl (11), And the selective rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain angular range at least directly or indirectly brings the first pawl (11) and the first right half clutch (16) into an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11), and the selective rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain angular range at least directly or indirectly brings the first pawl (11) and the first auxiliary right half clutch (17) into an engaged or disengaged state, and/or the first shift gear sleeve (18) is in turn connected with the first pawl (11) via the first transmission pin (26), and the first shift cam (25) is in turn connected with the first shift pin (11), and the first shift gear sleeve (18) is in turn axially moved via the first transmission pin (26), The first shift cam (25) brings the first pawl (11) into engagement or disengagement with the first right half clutch (16), and/or the first shift sleeve (18) is connected to the first pawl (11) via the first drive pin (26) and the first shift cam (25) in that order, and axial movement of the first shift sleeve (18) brings the first pawl (11) into engagement or disengagement with the first auxiliary right half clutch (17) via the first drive pin (26) and the first shift cam (25) in that order, and/or the first shift sleeve (18) is connected directly or indirectly to the actuating device (AM) and the first shift sleeve (18) is selectively axially movable within a certain range relative to the first left half clutch (15) under drive of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is in an intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is in a position axially close to the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is in a position axially away from the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the direct or indirect action of the first pawl (11), the first auxiliary right half clutch (17) at least has the function of rotating for a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), under the direct or indirect action of the first pawl (11), the first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) within the angle range limited by the first limit pin (13), the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or normally relative to the first right half clutch (16), under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle limited by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, and the first pawl (11) contacts with the split plane when rotating relative to the first right half clutch (16), Thereby greatly reducing noise; and/or

The one-way clutch mechanism (51) includes at least: the gear shifting mechanism comprises a first right clutch support (6), a first left clutch support (5), a first right clutch support (6), a first clutch rivet (7), a first pawl (11), a first limit pin (13), a first left half clutch (15), a first right half clutch (16), a first auxiliary right half clutch (17), a first gear shifting gear sleeve (18), a first positioning mechanism (19), a second pawl (20), a second return spring (21), a first auxiliary left half clutch (22), a first middle clutch (23), a second limit pin (24), a first gear shifting cam (25) and a first transmission pin (26), wherein the first right clutch support (6), the first left clutch support (5), the first left half clutch (15), The first right half clutch (16) and/or the first auxiliary right half clutch (17), the first shifting sleeve (18) and/or the first positioning mechanism (19) and/or the first auxiliary left half clutch (22), the first shifting cam (25) and the first intermediate clutch (23) are coaxially arranged, and the first return spring (4) and/or the first left clutch bracket (5), the first right clutch bracket (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), the first left half clutch (15) and/or the first auxiliary right half clutch (17), the first shifting sleeve (18) and/or the first positioning mechanism (19), the second pawl (20), The second return spring (21), and/or the first auxiliary left half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the first shift cam (25), and/or the first transmission pin (26) are arranged axially on one side of the first right half clutch (16), and/or the first intermediate clutch (23) coaxially passes through the first left half clutch (15), or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with a driving member of the machine (M) and rotates together with the driving member of the machine (M), and/or the first left half-clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected with a driven part of the machine (M) and rotates with a driven part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates with a driving part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first right half-clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates with the machine (M) The driven part of the machine (M) rotates together, and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first middle clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first middle clutch (23) is directly or indirectly connected with the damping buffer Device (DM) and rotates together with the damping buffer Device (DM), and/or the first middle clutch (23) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first middle clutch (23) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engaged state with the first left half clutch (15) at an initial position, The first left half clutch (15) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first intermediate clutch (23) and can rotate in a one-way mode in the reverse or forward rotation direction, and/or the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22) at an initial position, the first auxiliary left half clutch (22) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first intermediate clutch (23) and can rotate in a one-way mode in the reverse or forward rotation direction, and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first intermediate clutch (23) and can rotate in a one-way mode in the reverse or reverse rotation direction, and/or the second pawl (20) is in an engaged state with the first auxiliary left half clutch (17) at an initial position, The first auxiliary right half clutch (17) is fixed in a one-way mode in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23) and can rotate in a one-way mode in the reverse rotation or forward rotation direction, and/or the first pawl (11) is in a separation state with the first left half clutch (15) in an initial position, the first left half clutch (15) can rotate in the forward rotation and reverse rotation directions relative to the first intermediate clutch (23), and/or the first pawl (11) is in a separation state with the first auxiliary left half clutch (22) in an initial position, the first auxiliary left half clutch (22) can rotate in the forward rotation and reverse rotation directions relative to the first intermediate clutch (23), and/or the second pawl (20) is in a separation state with the first right half clutch (16) in an initial position, Wherein the first right half clutch (16) is rotatable in both forward and reverse directions relative to the first intermediate clutch (23), and/or the second pawl (20) is in a disengaged state from the first auxiliary right half clutch (17) at an initial position, wherein the first auxiliary right half clutch (17) is rotatable in both forward and reverse directions relative to the first intermediate clutch (23), wherein the first intermediate clutch (23) and the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) and the first shift cam (25) are configured with at least ratchet-like projections and/or ratchet-like recesses, and wherein the first pawl (11) and the second pawl (20) are configured with at least a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, and/or the first pawl (11) is in contact with the first left half clutch (15) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), and/or the first pawl (11) is in contact with the first auxiliary left half clutch (22) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), and/or the second pawl (20) is in contact with the first right half clutch (16) under the direct or indirect action of the second return spring (21) when the first shift cam (25) is not acting on the second pawl (20), and/or the first shift cam (25) is not acting on the second pawl (20), Under the direct or indirect action of the second return spring (21), the second pawl (20) and the first auxiliary right half clutch (17) are in contact with each other, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first intermediate clutch (23), the first pawl (11) rotates together with the first intermediate clutch (23), the first pawl (11) can rotate relative to the first intermediate clutch (23) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) rotates together with the first left clutch bracket (5), the first pawl (11) can rotate relative to the first left clutch bracket (5) within a certain angle range, the second pawl (20) comprises at least one pawl, said second pawl (20) being directly or indirectly connected to said first intermediate clutch (23), said second pawl (20) rotating with said first intermediate clutch (23), said second pawl (20) being rotatable within an angular range relative to said first intermediate clutch (23), and/or said second pawl (20) being directly or indirectly connected to said first right clutch bracket (6), said second pawl (20) rotating with said first right clutch bracket (6), said second pawl (20) being rotatable within an angular range relative to said first right clutch bracket (6), said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first intermediate clutch (23) and rotating with said first intermediate clutch (23), said second return spring (21) comprising at least one spring, the second return spring (21) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the other constraint or load acts on the first pawl (11) less than the action of the first return spring (4) on the first pawl (11), the second return spring (21) is directly or indirectly connected with the second pawl (20), the second pawl (20) restores the initial position under the elastic force of the second return spring (21) when the other constraint or load acts on the second pawl (20) less than the action of the second return spring (21) on the second pawl (20), and/or the first left-hand half clutch (15) is fixed unidirectionally in the forward or reverse direction and is rotatable unidirectionally in the reverse or forward direction relative to the first intermediate clutch (23) over a load range when the first pawl (11) is engaged with the first left-hand half clutch (15), and/or the first auxiliary left-hand half clutch (22) is fixed unidirectionally in the forward or reverse direction relative to the first intermediate clutch (23) and is rotatable unidirectionally in the reverse or forward direction over a load range when the first pawl (11) is engaged with the first auxiliary left-hand half clutch (22), and/or the first left-hand half clutch (15) is rotatable relative to the first intermediate clutch (23) both in the forward and reverse direction over a load range when the first pawl (11) is disengaged from the first left-hand half clutch (15), and/or the first auxiliary left-half clutch (22) can be rotated in both forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first auxiliary left-half clutch (22), and/or the first right-half clutch (16) can be fixed in one direction in the forward or reverse direction relative to the first intermediate clutch (23) and can be rotated in one direction in the reverse or forward direction when the second pawl (20) is engaged with the first right-half clutch (16) within a certain load range, and/or the first auxiliary right-half clutch (17) can be fixed in one direction in the forward or reverse direction relative to the first intermediate clutch (23) and can be rotated in one direction in the reverse or forward direction when the second pawl (20) is engaged with the first auxiliary right-half clutch (17) within a certain load range, and/or the first right half clutch (16) can rotate relative to the first middle clutch (23) in the forward and reverse directions in a certain load range when the second pawl (20) is separated from the first right half clutch (16), and/or the first auxiliary right half clutch (17) can rotate relative to the first middle clutch (23) in the forward and reverse directions in a certain load range when the second pawl (20) is separated from the first auxiliary right half clutch (17), and the contact pair of the first pawl (11) and the first left half clutch (15) has an overload protection function when the first pawl (11) and the first left half clutch (15) are in an engaged state, and the contact pair of the first pawl (11) and the first left half clutch (15) has an overload protection function when an excessive force acts between the first pawl (11) and the first left half clutch (15), The first pawl (11) is automatically disengaged from the first left half clutch (15), and/or the contact pair of the first pawl (11) and the first left half clutch (15) has a self-locking function when the first pawl (11) and the first left half clutch (15) are in an engaged state, the contact pair of the first pawl (11) and the first left half clutch (15) is not automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, The first pawl (11) is automatically disengaged from the first auxiliary left half clutch (22), and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function when the acting force between the second pawl (20) and the first right half clutch (16) is large, and the contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function when the acting force between the second pawl (20) and the first right half clutch (16) is excessive, The second pawl (20) is automatically disengaged from the first right half clutch (16), and/or the contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) is not automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is large, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has an overload protection function when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is excessive, and the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has an overload protection function when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is excessive, The second pawl (20) is automatically disengaged from the first auxiliary right half clutch (17), and/or when the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17), the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has a self-locking function, and when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is not automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first left clutch bracket (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first middle clutch (23), and/or the first right clutch support (6) is fixedly connected with the first middle clutch (23) through the first clutch rivet (7), the first shifting gear sleeve (18) is directly or indirectly connected with the first left clutch support (5) and rotates together with the first left clutch support (5), and/or the first left clutch support (5) has a certain limiting effect on the first shifting gear sleeve (18) in the axial direction, the first shifting gear sleeve (18) overcomes the effect of the first left clutch support (5) to selectively move in the axial direction relative to the first left clutch support (5), and/or at least a series of axial positioning grooves or bulges are configured on the first left clutch support (5), The first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first left clutch support (5) via the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch support (6) and rotates together with the first right clutch support (6), and/or the first right clutch support (6) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first right clutch support (6) against the action of the first right clutch support (6), and/or the first right clutch support (6) is at least designed with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least designed to perform an axial positioning function or projection within a certain range relative to the first right clutch support (6) via the series of axial positioning grooves or projections The first right clutch support (6) has an axial positioning function, and/or the first positioning means (19) is directly or indirectly connected to the first left clutch support (5), the first positioning means (19) rotates together with the first left clutch support (5), the first positioning means (19) is axially fixed relative to the first left clutch support (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch support (6), the first positioning means (19) rotates together with the first right clutch support (6), the first positioning means (19) is axially fixed relative to the first right clutch support (6), and/or the first positioning means (19) is directly or indirectly connected to the first sleeve gear (18), and the first positioning means (19) axially limits the first sleeve gear (18) to a certain extent -said first shifting sleeve (18) is selectively axially movable with respect to said first left half clutch (15) against the action of said first positioning means (19), and/or-said first shifting sleeve (18) is provided with a series of axial detents or protrusions, -said first shifting sleeve (18) is configured at least to position at least one axial position thereof by the constraining action of said series of axial detents or protrusions within a certain range with said first positioning means (19), and/or-said first driving pin (26) is directly or indirectly connected with said first shifting sleeve (18) and said first driving pin (26) rotates with said first shifting sleeve (18), and/or-said first driving pin (26) is directly or indirectly connected with said first shifting cam (25), said first driving pin (26) being configured at least to push said first shifting male shifting cam (26) within a certain axial range A wheel (25) rotating within a certain angle range relative to the first intermediate clutch (23), and/or the first shift cam (25) being directly or indirectly connected to the first intermediate clutch (23), the first shift cam (25) being at least configured to rotate within a certain angle range relative to the first intermediate clutch (23) under the action of the first drive pin (26), and/or the first shift cam (25) being directly or indirectly connected to the first left clutch carrier (5), and the first shift cam (25) being at least configured to rotate within a certain angle range relative to the first left clutch carrier (5) under the action of the first drive pin (26), and/or the first shift cam (25) being directly or indirectly connected to the first right clutch carrier (6), and the first shift cam (25) being at least configured to rotate within a certain angle range relative to the first left clutch carrier (5) under the action of the first drive pin (26) Is rotatable within a certain angular range relative to the first right clutch support (6), and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11) and the first shift cam (25) is selectively rotatable within a certain angular range relative to the first intermediate clutch (23) at least directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first left clutch half (15), and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11) and the first shift cam (25) is selectively rotatable within a certain angular range relative to the first intermediate clutch (23) at least directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first auxiliary left clutch half (22), and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20), And the selective rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain angular range at least directly or indirectly brings the second pawl (20) into engagement or disengagement with the first right half clutch (16), and/or the selective rotation of the first shift cam (25) relative to the first left half clutch (15) at least directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary right half clutch (17), and/or the selective rotation of the first shift sleeve (18) relative to the first left half clutch (15) within a certain angular range at least directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary right half clutch (17), and/or the first shift sleeve (18) in turn engages the first drive pin (26), the first shift cam (25) engages the first pawl (11), and the first shift sleeve (18) in turn axially moves the first drive pin (26), The first gear shifting cam (25) enables the first pawl (11) and the first left half clutch (15) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) is connected with the first pawl (11) through the first transmission pin (26) and the first gear shifting cam (25) in sequence, and axial movement of the first gear shifting sleeve (18) enables the first pawl (11) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state through the first transmission pin (26) in sequence, the first gear shifting cam (25) enables the first pawl (11) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) is connected with the second pawl (20) through the first transmission pin (26) in sequence, and axial movement of the first gear shifting sleeve (18) is connected through the first transmission pin (26) in sequence, The first shift cam (25) brings the second pawl (20) into engagement or disengagement with the first right partial clutch (16), and/or the first shift sleeve (18) is connected to the second pawl (20) via the first transmission pin (26) in that order, and the first shift cam (25) is connected to the second pawl (20), and axial movement of the first shift sleeve (18) is brought into engagement or disengagement with the first auxiliary right partial clutch (17) via the first transmission pin (26) in that order, and the first shift cam (25) is connected directly or indirectly to the actuating device (AM), and the first shift sleeve (18) is selectively moved axially within a certain range relative to the first intermediate clutch (23) under the drive of the actuating device (AM), and/or when the first shift sleeve (18) is in an intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first left-half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first right-half clutch (16), and/or when the first shift sleeve (18) is in a position in the axial direction axially adjacent to the first left-half clutch (15) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first left-half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first right-half clutch (16), and/or when the first shift sleeve (18) is in the axial direction axially adjacent to the first right-half clutch (16) directly or indirectly under the action of the actuating device (AM) ) When in a certain position, the first pawl (11) is in an engaged or separated state with the first left half clutch (15), the second pawl (20) is in an engaged or separated state with the first right half clutch (16), the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), the second limit pin (24) at least comprises one pin, the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) at least has the function of rotating a certain angle relative to the first left half clutch (15), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), the first auxiliary left half clutch (22) at least has the function of rotating relative to the first left half clutch (15) within the angle range limited by the first limit pin (13) under the direct or indirect action of the first pawl (11), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and the first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) at a certain angle under the direct or indirect action of the second pawl (20), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), The first auxiliary right half clutch (17) has at least the function of being rotatable relative to the first right half clutch (16) within an angular range defined by the second limit pin (24) under the direct or indirect action of the second pawl (20), the first auxiliary left half clutch (22) being arranged coaxially in the radial direction on one side of the first left half clutch (15) and/or the first auxiliary right half clutch (17) being arranged coaxially in the radial direction on one side of the first right half clutch (16), the first auxiliary left half clutch (22) being rotated to a certain angle relative to the first left half clutch (15) or the first auxiliary left half clutch (22) being rotated to the first left half clutch (15) to a limit pin (13) under the direct or indirect action of the first pawl (11) when the first left half clutch (15) is rotated to a certain angle relative to the first intermediate clutch (23) or the first auxiliary left half clutch (22) is rotated to the first limit pin (13) After the angle of the first auxiliary left half clutch (22) and the partial surface of the first left half clutch (15) are radially combined to form a plane, the first pawl (11) rotates relative to the first intermediate clutch (23) and contacts the combined plane, so that noise is greatly reduced, and/or when the first right half clutch (16) rotates reversely or forwardly relative to the first intermediate clutch (23), the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16) under the direct or indirect action of the second pawl (20), or the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), the partial surface of the first auxiliary right half clutch (17) and the partial surface of the first auxiliary right half clutch (16) are radially combined to form a plane, So that the second pawl (20) is in contact with the split plane when rotating relative to the first intermediate clutch (23), thereby greatly reducing noise; and/or

The one-way clutch mechanism (51) includes at least: a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), and/or a first positioning mechanism (19), a first shift cam (25), wherein the first left half clutch (15), and/or the first left clutch bracket (5), and/or the first right clutch bracket (6), and/or the first auxiliary right half clutch (17), and/or the first positioning mechanism (19), the first shift cam (25) and the first right half clutch (16) are coaxially arranged, and the first return spring (4), And/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), and/or the first auxiliary right half clutch (17), and/or the first positioning mechanism (19), the first shift cam (25) are arranged on one side of the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) is directly or indirectly fixedly connected with the cushion damping Device (DM), and/or the first left half clutch (15) is directly or indirectly fixedly connected with a machine frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), the first pawl (11) is in an initial position and is in an engaged state with the first right half clutch (16), the first right half clutch (16) is fixed in a one-way mode in the positive rotation direction or the negative rotation direction relative to the first left half clutch (15) and can rotate in the one-way direction in the negative rotation direction or the negative rotation direction, and/or the first pawl (11) is in an initial position and is in an engaged state with the first auxiliary right half clutch (17), At the moment, the first auxiliary right half clutch (17) is fixed in a one-way mode in the forward rotation or reverse rotation direction relative to the first left half clutch (15) and can rotate in a one-way mode in the reverse rotation or forward rotation direction, and/or the first pawl (11) is in a separated state with the first right half clutch (16) at an initial position, at the moment, the first right half clutch (16) can rotate in the forward rotation and reverse rotation directions relative to the first left half clutch (15), and/or the first pawl (11) is in a separated state with the first auxiliary right half clutch (17) at an initial position, at the moment, the first auxiliary right half clutch (17) can rotate in the forward rotation and reverse rotation directions relative to the first left half clutch (15), and the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) and the first shift cam (25) are at least configured with ratchet-shaped bulges and/or ratchet-shaped grooves And the first pawl (11) is at least configured to engage with or disengage from the ratchet-like protrusion and/or ratchet-like recess, and/or the first pawl (11) is in contact with the first right half clutch (16) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), and/or the first pawl (11) is in contact with the first auxiliary right half clutch (17) under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11), the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first left half clutch (15), Said first pawl (11) rotating together with said first left half clutch (15), said first pawl (11) being rotatable within an angular range relative to said first left half clutch (15), and/or said first pawl (11) being directly or indirectly connected to said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first left half clutch (15) and rotating together with said first left half clutch (15), said first return spring (4) being directly or indirectly connected to said first pawl (11), when other constraints or pawl loads have a lesser effect on said first pawl (11) than said first return spring (4) The first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the first pawl (11) acts, and/or the first right half clutch (16) is fixed in a one-way mode in the forward or reverse direction and can rotate in a one-way mode in the reverse or forward direction relative to the first left half clutch (15) within a certain load range when the first pawl (11) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in a one-way mode in the forward or reverse direction relative to the first left half clutch (15) and can rotate in a one-way mode in the reverse or forward direction when the first pawl (11) is engaged with the first auxiliary right half clutch (17) within a certain load range, and/or the first pawl (11) is disengaged from the first left half clutch (16), The first right half clutch (16) can rotate in the forward and reverse directions relative to the first left half clutch (15) within a certain load range, and/or the first auxiliary right half clutch (17) can rotate in the forward and reverse directions relative to the first left half clutch (15) within a certain load range when the first pawl (11) is separated from the first auxiliary right half clutch (17), the contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function when the first pawl (11) and the first right half clutch (16) are in an engaged state, the first pawl (11) and the first right half clutch (16) are automatically disengaged when an excessive force is applied between the first pawl (11) and the first right half clutch (16), and/or the first pawl (11) and the first right half clutch (16) are in an engaged state The contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function, the contact pair of the first pawl (11) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is large, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has an overload protection function when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) automatically disengages when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is in an engaged state, The contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has a self-locking function, when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) can not be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first left clutch bracket (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), the first right clutch bracket (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch bracket (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), the first shift cam (25) is directly or indirectly connected to the first left clutch half (15) and rotates together with the first left clutch half (15), and/or the first left clutch half (15) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable over an angular range relative to the first left clutch half (15) against the effect of the first left clutch half (15), and/or at least one series of detents or projections are formed on the first left clutch half (15), the first shift cam (25) is at least configured to angularly position the first left clutch half (15) in the direction of rotation via the series of detents or projections over a range, and/or the first shift cam (25) is directly or indirectly connected to the first left clutch carrier (5) and is connected to the first left clutch carrier (5) The clutch carrier (5) rotates together, and/or the first left clutch carrier (5) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable relative to the first left clutch carrier (5) over a range of angles against the effect of the first left clutch carrier (5), and/or at least the first left clutch carrier (5) is provided with at least one series of detents or projections, the first shift cam (25) is at least configured to be angularly positioned relative to the first left clutch carrier (5) over a range of angles, and/or the first shift cam (25) is directly or indirectly connected to the first right clutch carrier (6) and rotates together with the first right clutch carrier (6), and/or the first right clutch carrier (6) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable relative to the first right clutch carrier (6) over a range of angles against the effect of the first right clutch carrier (6), and/or at least the first right clutch carrier (6) is provided with at least one series of detents or projections, the first shift cam (25) is provided with at least one range of angular positioning functions relative to the first right clutch carrier (6) in the direction of rotation via the series of detents or projections, and/or the first positioning means (19) is directly or indirectly connected to the first left clutch half (15), the first positioning means (19) rotates together with the first left clutch half (15), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25), and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable relative to the first left half clutch (15) over an angular range against the effect of the first positioning means (19), and/or the first shift cam (25) is provided with a series of positioning grooves or protrusions, the first shift cam (25) is at least configured to perform the function of angular positioning in a rotational direction relative to the first positioning mechanism (19) through the series of positioning grooves or protrusions within a certain range, and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11), and the first shift cam (25) is selectively rotated relative to the first left-half clutch (15) within a certain angular range at least directly or indirectly to bring the first pawl (11) and the first right-half clutch (16) into an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11), and the first shift cam (25) is selectively rotated relative to the first left-half clutch (15) within a certain angular range at least directly or indirectly to bring the first pawl (11) into an engaged or disengaged state The first pawl (11) is in an engaged or disengaged state with the first auxiliary right half clutch (17), and/or the first shift cam (25) is directly or indirectly connected with the actuating device (AM), and the first shift cam (25) is selectively rotated within an angular range relative to the first left half clutch (15) under the drive of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift cam (25) is in an angular intermediate position in the rotational direction under the action of the actuating device (AM) directly or indirectly, and/or the first shift cam (25) is in a side away from the angular intermediate position in the rotational direction under the action of the actuating device (AM), The first pawl (11) is in an engaged or disengaged state with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift cam (25) is directly or indirectly under the action of the actuating device (AM) on the other side away from the angular intermediate position in the rotational direction, and/or the first limit pin (13) comprises at least one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and the first auxiliary right half clutch (17) at least has the function of being rotatable by a certain angle relative to the first right half clutch (16) under the direct or indirect action of the first pawl (11), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), the first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) within the angle range limited by the first limit pin (13) under the direct or indirect action of the first pawl (11), and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16) under the direct or indirect action of the first pawl (11) when the first left half clutch (15) reversely rotates or forwardly relative to the first right half clutch (16), Or after the first auxiliary right half clutch (17) rotates relative to the first right half clutch (16) to the angle limited by the first limit pin (13), partial surface of the first auxiliary right half clutch (17) and partial surface of the first right half clutch (16) are radially split into a plane, and the first pawl (11) rotates relative to the first right half clutch (16) and contacts with the split plane, so that noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: the first positioning mechanism comprises a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), and/or a first positioning mechanism (19), a second pawl (20), a second return spring (21), and/or a first auxiliary left half clutch (22), a first intermediate clutch (23), and/or a second limit pin (24), and a first gear shifting cam (25), wherein the first left half clutch (15), and/or the first left clutch bracket (5), and/or the first right clutch bracket (6), the first right half clutch (16), And/or the first auxiliary right half clutch (17), and/or the first positioning mechanism (19), and/or the first auxiliary left half clutch (22), and/or the second limit pin (24), the first shift cam (25) is arranged coaxially with the first intermediate clutch (23), the first return spring (4), and/or the first left clutch bracket (5), the first right clutch bracket (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), and/or the first auxiliary right half clutch (17), and/or the first positioning mechanism (19), the second pawl (20), the second return spring (21), And/or the first auxiliary left half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the first shift cam (25) are axially arranged on one side of the first right half clutch (16), and/or the first intermediate clutch (23) coaxially passes through the first left half clutch (15), or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with a driving member of the machine (M) and rotates with the driving member of the machine (M), and/or the first left half clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM) -a damping Device (DM) rotates together, and/or-the first left half-clutch (15) is directly or indirectly connected to and rotates with the driven part of the machine (M), and/or-the first right half-clutch (16) is directly or indirectly connected to and rotates with the driving part of the machine (M), and/or-the first right half-clutch (16) is directly or indirectly connected to and rotates with the damping Device (DM), and/or-the first right half-clutch (16) is directly or indirectly connected to and rotates with the driven part of the machine (M), and/or-the first intermediate clutch (23) is directly or indirectly connected to and rotates with the damping Device (DM), and/or the first intermediate clutch (23) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engaged state with the first left half clutch (15) at the initial position, the first left half clutch (15) is unidirectionally fixed relative to the first intermediate clutch (23) in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction, and/or the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22) at the initial position, the first auxiliary left half clutch (22) is unidirectionally fixed relative to the first intermediate clutch (23) in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction, and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at the initial position, The first right half clutch (16) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first middle clutch (23) and can rotate in a one-way mode in the reverse or forward rotation direction, and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first middle clutch (23) and can rotate in a one-way mode in the reverse or forward rotation direction, and/or the first pawl (11) is in a separated state with the first left half clutch (15) at an initial position, the first left half clutch (15) can rotate in the forward or reverse rotation direction relative to the first middle clutch (23), and/or the first pawl (11) is in a separated state with the first auxiliary left half clutch (22) at an initial position, The first auxiliary left half clutch (22) can rotate in the forward and reverse directions relative to the first intermediate clutch (23), and/or the second pawl (20) can be in a disengaged state with the first right half clutch (16) in an initial position, the first right half clutch (16) can rotate in the forward and reverse directions relative to the first intermediate clutch (23), and/or the second pawl (20) can be in a disengaged state with the first auxiliary right half clutch (17) in an initial position, the first auxiliary right half clutch (17) can rotate in the forward and reverse directions relative to the first intermediate clutch (23), the first intermediate clutch (23) and the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) and the first shift cam (25) are at least structured With ratchet-like projections and/or ratchet-like recesses and the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-like projections and/or ratchet-like recesses and/or the first pawl (11) and the first left-hand clutch half (15) are in contact with each other under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11) and/or the first pawl (11) and the first auxiliary left-hand clutch half (22) are in contact with each other under the direct or indirect action of the first return spring (4) when the first shift cam (25) is not acting on the first pawl (11) and/or the first pawl (11) and the second auxiliary left-hand clutch half (22) are in contact with each other when the first shift cam (25) is not acting on the second pawl (20), The second pawl (20) is in contact with the first right half clutch (16) under the direct or indirect action of the second return spring (21), and/or the second pawl (20) is in contact with the first auxiliary right half clutch (17) under the direct or indirect action of the second return spring (21) when the first shift cam (25) has no force on the second pawl (20), the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first intermediate clutch (23), the first pawl (11) rotates together with the first intermediate clutch (23), the first pawl (11) can rotate relative to the first intermediate clutch (23) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch support (5), Said first pawl (11) rotating together with said first left clutch support (5), said first pawl (11) being rotatable within an angular range relative to said first left clutch support (5), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected with said first intermediate clutch (23), said second pawl (20) rotating together with said first intermediate clutch (23), said second pawl (20) being rotatable within an angular range relative to said first intermediate clutch (23), and/or said second pawl (20) being directly or indirectly connected with said first right clutch support (6), said second pawl (20) rotating together with said first right clutch support (6), said second pawl (20) being rotatable within an angular range relative to said first right clutch support (6), the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the effect of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and the second return spring (21) is directly or indirectly connected with the second pawl (20), When the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), the second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), when the first pawl (11) is engaged with the first left clutch half (15), the first left clutch half (15) is unidirectionally fixed in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary left clutch half (22), the first auxiliary left clutch half (22) is unidirectionally fixed in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or the first left-hand clutch half (15) can be rotated in both forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first left-hand clutch half (15), and/or the first auxiliary left-hand clutch half (22) can be rotated in both forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first auxiliary left-hand clutch half (22), and/or the first right-hand clutch half (16) can be fixed in one direction in either forward or reverse direction and can be rotated in one direction in either reverse or reverse direction relative to the first intermediate clutch half (23) within a certain load range when the second pawl (20) is engaged with the first right-hand clutch half (16), and/or the second pawl (20) can be engaged with the first auxiliary right-hand clutch half (17), The first auxiliary right half clutch (17) is fixed in a one-way mode in the forward rotation direction or the reverse rotation direction relative to the first middle clutch (23) and can rotate in a one-way mode in the reverse rotation direction or the forward rotation direction in a certain load range, and/or when the second pawl (20) is separated from the first right half clutch (16), the first right half clutch (16) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle clutch (23) in a certain load range, and/or when the second pawl (20) is separated from the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle clutch (23) in a certain load range, and when the first pawl (11) is in an engaged state with the first left half clutch (15), the contact pair of the first pawl (11) and the first left half clutch (15) has the work of overload protection Can automatically disengage the first pawl (11) from the first left half clutch (15) when the acting force between the first pawl (11) and the first left half clutch (15) is excessive, and/or has a self-locking function when the first pawl (11) and the first left half clutch (15) are in an engaged state, and also has a self-locking function when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or has an overload protection function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, and/or has a self-locking function when the first pawl (11) and the first left half clutch (15) are in a contact pair, The first pawl (11) is automatically disengaged from the first auxiliary left half clutch (22) when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function when the second pawl (20) and the first right half clutch (16) are in an engaged state, When the acting force between the second pawl (20) and the first right half clutch (16) is excessive, the second pawl (20) and the first right half clutch (16) are automatically disengaged, and/or when the second pawl (20) and the first right half clutch (16) are in an engaged state, a contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function, when the acting force between the second pawl (20) and the first right half clutch (16) is larger, the contact pair of the second pawl (20) and the first right half clutch (16) does not automatically disengage, and/or when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has an overload protection function, When the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is too large, the second pawl (20) and the first auxiliary right half clutch (17) are automatically disengaged, and/or when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) cannot be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, and the first left clutch bracket (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first left clutch support (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first right clutch support (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch support (6) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), the first shift cam (25) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, and the first shift cam (25) selectively rotates within a certain angle range relative to the first intermediate clutch (23) against the effect of the first intermediate clutch (23), and/or the first intermediate clutch (23) is provided with at least one series of detents or projections, the first shift cam (25) is provided with at least one range of angular positioning in relation to the first intermediate clutch (23) via the series of detents or projections, and/or the first shift cam (25) is connected directly or indirectly to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a range of angular limiting effects in the direction of rotation on the first cam shift (25), the first shift cam (25) is selectively rotatable in relation to the first left clutch carrier (5) over a range of angles against the effect of the first left clutch carrier (5), and/or the first left clutch carrier (5) is provided with at least one series of detents or projections, and/or the first shift cam (25) is provided with at least one range of detents or projections, The first shift cam (25) is at least designed to be rotationally positioned in relation to the first left clutch support (5) via the series of detents or projections within a certain range, and/or the first shift cam (25) is directly or indirectly connected to the first right clutch support (6) and rotates with the first right clutch support (6), and/or the first right clutch support (6) has a certain angular limitation in the direction of rotation on the first shift cam (25), the first shift cam (25) is selectively rotatable in relation to the first right clutch support (6) against the action of the first right clutch support (6) within a certain angular range, and/or the first right clutch support (6) is designed with at least a series of detents or projections, The first shift cam (25) is configured at least in a certain range to perform the function of angular positioning in the direction of rotation relative to the first right clutch carrier (6) by means of the series of positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected with the first intermediate clutch (23), the first positioning means (19) rotates with the first intermediate clutch (23), and/or the first positioning means (19) is directly or indirectly connected with the first left clutch carrier (5), the first positioning means (19) rotates with the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected with the first right clutch carrier (6), the first positioning means (19) rotates with the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25) and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable relative to the first left clutch half (15) over an angular range against the effect of the first positioning means (19), and/or a series of detents or projections are provided on the first shift cam (25), the first shift cam (25) is at least configured to have a function of angular positioning relative to the first positioning means (19) in the direction of rotation over a range by means of the series of detents or projections, and/or the first shift cam (25) is directly or indirectly connected to the first detent (11), And the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range brings at least the first pawl (11) directly or indirectly into engagement or disengagement with the first left-hand clutch (15), and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11), and the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range brings at least the first pawl (11) directly or indirectly into engagement or disengagement with the first auxiliary left-hand clutch (22), and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20), and the selective rotation of the first shift cam (25) relative to the first left-hand clutch (15) within a certain angular range brings at least the second pawl (20) directly or indirectly into engagement with the second pawl (22) -a right half-clutch (16) is engaged or disengaged, and/or-the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the selective rotation of the first shift cam (25) relative to the first left half-clutch (15) within a certain angular range at least directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary right half-clutch (17), and/or-the first shift cam (25) is directly or indirectly connected to the Actuating Means (AM) and the first shift cam (25) is selectively rotated relative to the first intermediate clutch (23) within a certain angular range under the drive of the Actuating Means (AM), and/or-when the first shift cam (25) is in an angular intermediate position in the rotational direction under the action of the Actuating Means (AM), The first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16) when the first shift cam (25) is directly or indirectly on a side in the rotational direction away from the angular intermediate position under the action of the Actuating Means (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15) when the first shift cam (25) is directly or indirectly on the other side in the rotational direction away from the angular intermediate position under the action of the Actuating Means (AM), The second pawl (20) and the first right half clutch (16) are in an engaged or disengaged state, the first limit pin (13) at least comprises one pin, the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), the second limit pin (24) at least comprises one pin, the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) at least has a function of rotating a certain angle relative to the first left half clutch (15), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), Under the direct or indirect action of the first pawl (11), the first auxiliary left half clutch (22) has at least the function of being rotatable relative to the first left half clutch (15) within the angular range defined by the first limit pin (13), and/or the first auxiliary right half clutch (17) is directly or indirectly connected to the first right half clutch (16), and under the direct or indirect action of the second pawl (20), the first auxiliary right half clutch (17) has at least the function of being rotatable relative to the first right half clutch (16) by a certain angle, and/or the first auxiliary right half clutch (17) is connected to the first right half clutch (16) by the second limit pin (24), under the direct or indirect action of the second pawl (20), the first auxiliary right half clutch (17) has at least the function of being rotatable relative to the first right half clutch (17) within the angular range defined by the second limit pin (24) The function of the half clutch (16) rotating, and/or the first auxiliary left half clutch (22) is arranged coaxially on one side of the first left half clutch (15) in the radial direction, and/or the first auxiliary right half clutch (17) is arranged coaxially on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the first pawl (11), after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), or after the first auxiliary left half clutch (22) rotates to an angle defined by the first limit pin (13) relative to the first left half clutch (15), a partial surface of the first auxiliary left half clutch (22) and a partial surface of the first left half clutch (15) are combined into a plane in the radial direction, The first pawl (11) is in contact with the split plane when rotating relative to the first intermediate clutch (23) so as to greatly reduce noise, and/or when the first right half clutch (16) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, so that the second pawl (20) is in contact with the split plane when rotating relative to the first intermediate clutch (23), Thereby greatly reducing noise; and/or

The one-way clutch mechanism (51) includes at least: the clutch comprises a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary outer ring (12), and/or a first positioning mechanism (19), wherein the first outer ring (2) is arranged on one side of the first inner ring (1) in the radial direction, the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12), and/or the first positioning mechanism (19) is arranged coaxially with the first inner ring (1), and the first inner ring (1), the first outer ring (2), The first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary outer ring (12), and/or the first positioning means (19) are arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with a damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping buffer Device (DM) and rotates along with the damping buffer Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engagement state with the first outer ring (2) at an initial position, and the first outer ring (2) is unidirectionally fixed relative to the first inner ring (1) in a forward or reverse direction And is unidirectionally rotatable in a reverse or forward direction, and/or the first pawl (11) is in an engaged state with the first auxiliary outer ring (12) at an initial position, at which time the first auxiliary outer ring (12) is unidirectionally fixed in the forward or reverse direction with respect to the first inner ring (1) and unidirectionally rotatable in the reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first outer ring (2) at an initial position, at which time the first outer ring (2) is rotatable in both the forward and reverse directions with respect to the first inner ring (1), and/or the first pawl (11) is in a disengaged state with the first auxiliary outer ring (12) at an initial position, at which time the first auxiliary outer ring (12) is rotatable in both the forward and reverse directions with respect to the first inner ring (1), the first inner ring (1) and the first outer ring (2) and the first auxiliary outer ring (12) are at least configured with ratchet-like protrusions and/or ratchet-like recesses, and the first pawl (11) is at least configured to engage with or disengage from the ratchet-like protrusions and/or ratchet-like recesses, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first inner ring (1), the first pawl (11) rotates with the first inner ring (1), the first pawl (11) is rotatable within a certain angular range relative to the first inner ring (1), and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), the first pawl (11) rotates with the first right clutch support (6), The first pawl (11) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), the first return spring (4) is directly or indirectly connected with the first pawl (11), when the effect of other restraint or load on the first pawl (11) is smaller than the effect of the first return spring (4) on the first pawl (11), the first pawl (11) restores the initial position under the effect of the elastic force of the first return spring (4), and/or when the first left clutch support (5) does not act on the first pawl (11), under the direct or indirect effect of the first return spring (4), The first pawl (11) and the first outer ring (2) are in contact with each other, and/or the first pawl (11) and the first auxiliary outer ring (12) are in contact with each other under the direct or indirect action of the first return spring (4) when the first left clutch support (5) has no acting force on the first pawl (11), the first outer ring (2) is fixed in a one-way manner in the forward or reverse rotation direction and can rotate in a one-way manner in the reverse or forward rotation direction relative to the first inner ring (1) when the first pawl (11) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in a one-way in the reverse or reverse rotation direction and can rotate in a one-way in the reverse or forward rotation direction relative to the first inner ring (1) when the first pawl (11) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is rotatable in both forward and reverse directions relative to the first inner ring (1) within a load range when the first pawls (11) are disengaged from the first outer ring (2), and/or the first auxiliary outer ring (12) is rotatable in both forward and reverse directions relative to the first inner ring (1) within a load range when the first pawls (11) and the second pawls (20) are disengaged from the first auxiliary outer ring (12), the pair of first pawls (11) and the first outer ring (2) having an overload protection function when the first pawls (11) and the first outer ring (2) are in an engaged state, the first pawls (11) and the first outer ring (2) being automatically disengaged from the first outer ring (2) when an excessive force is applied between the first pawls (11) and the first outer ring (2), and/or the contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function when the first pawl (11) and the first outer ring (2) are in an engaged state, the contact pair of the first pawl (11) and the first outer ring (2) cannot be automatically disengaged when a force between the first pawl (11) and the first outer ring (2) is large, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has an overload protection function when the first pawl (11) and the first auxiliary outer ring (12) are in an engaged state, the first pawl (11) and the first auxiliary outer ring (12) are automatically disengaged when the force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, and/or the first pawl (11) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the first pawl (11) and the first auxiliary outer ring (12) has a self-locking function, when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is large, the contact pair of the first pawl (11) and the first auxiliary outer ring (12) cannot be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first right clutch bracket (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch bracket (6) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), the first left clutch bracket (5) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and/or the first inner ring (1) has a certain limiting effect on the first left clutch bracket (5) in the axial direction, The first left clutch support (5) is selectively movable in the axial direction relative to the first inner ring (1) against the action of the first inner ring (1), and/or at least a series of axial positioning grooves or projections are formed on the first inner ring (1), the first left clutch support (5) is at least configured to perform the function of axial positioning relative to the first inner ring (1) through the series of axial positioning grooves or projections within a certain range, and/or the first positioning mechanism (19) is directly or indirectly connected with the first inner ring (1), the first positioning mechanism (19) rotates together with the first inner ring (1), the first positioning mechanism (19) is fixed in the axial direction relative to the first inner ring (1), and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch support (5), And the first positioning mechanism (19) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) is selectively moved relative to the first inner ring (1) in the axial direction against the effect of the first positioning mechanism (19), and/or a series of axial positioning grooves or protrusions are arranged on the first left clutch support (5), the first left clutch support (5) is at least configured to position at least one axial position thereof through the limiting effect of the series of axial positioning grooves or protrusions and the first positioning mechanism (19) within a certain range, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11), and the first left clutch support (5) is selectively moved relative to the first inner ring (1) in the axial direction within a certain range, so that the first pawl (11) and the first outer ring (1) are directly or indirectly moved 2) In the engaged or disengaged state, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range to directly or indirectly bring the first pawl (11) into the engaged or disengaged state with the first auxiliary outer ring (12), and/or the first left clutch support (5) is directly or indirectly connected with the actuating device (AM) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range under the drive of the actuating device (AM), and/or when the first left clutch support (5) is axially moved relative to the first inner ring (1) within a certain range under the action of the actuating device (AM) directly or indirectly, The first pawl (11) is in a state of engagement or disengagement with the first outer ring (2), and/or the first pawl (11) is in a state of engagement or disengagement with the first outer ring (2) when the first left clutch support (5) is in a position axially to the left remote from the first inner ring (1) directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in a state of engagement or disengagement with the first outer ring (2) when the first left clutch support (5) is in a position axially to the one side remote from the first inner ring (1) directly or indirectly under the action of the actuating device (AM), and/or the first limit pin (13) comprises at least one pin, the first limit pin (13) being fixedly connected directly or indirectly with the first outer ring (2), the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), under the action of the first pawl (11), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), under the action of the first pawl (11), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2) in the axial direction, and/or when the first outer ring (2) rotates reversely or forwardly relative to the first inner ring (1), Under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, and the first pawl (11) contacts with the spliced cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: the clutch comprises a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), and/or a first positioning mechanism (19), wherein the first outer ring (2) is arranged on one side of the first inner ring (1) in the radial direction, the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19) is arranged coaxially with the first inner ring (1), and the first inner ring (1), the first outer ring (2), The first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), and/or the first positioning means (19) are arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with a damping Device (DM) and rotates together with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping buffer Device (DM) and rotates along with the damping buffer Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, and the first inner ring (1) is unidirectionally fixed relative to the first outer ring (2) in a forward or reverse direction And is unidirectionally rotatable in the reverse rotation or forward rotation direction, and/or the first pawl (11) is in an engaged state with the first auxiliary inner ring (14) at an initial position, at which time the first auxiliary inner ring (14) is unidirectionally fixed in the forward rotation or reverse rotation direction with respect to the first outer ring (2) and unidirectionally rotatable in the reverse rotation or forward rotation direction, and/or the first pawl (11) is in a disengaged state with the first inner ring (1) at an initial position, at which time the first inner ring (1) is rotatable in both the forward rotation and reverse rotation direction with respect to the first outer ring (2), and/or the first pawl (11) is in a disengaged state with the first auxiliary inner ring (14) at an initial position, at which time the first auxiliary inner ring (14) is rotatable in both the forward rotation and reverse rotation direction with respect to the first outer ring (2), the first inner ring (1) and the first outer ring (2) and the first auxiliary inner ring (14) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, and the first pawl (11) is at least configured to engage with or disengage from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first outer ring (2), the first pawl (11) rotates with the first outer ring (2), the first pawl (11) is rotatable within a certain angular range relative to the first outer ring (2), and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) rotates with the first right clutch bracket (6), The first pawl (11) can rotate relative to the first right clutch bracket (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with the first pawl (11), when the effect of other restraint or load on the first pawl (11) is smaller than the effect of the first return spring (4) on the first pawl (11), the first pawl (11) restores the initial position under the effect of the elastic force of the first return spring (4), and/or when the first left clutch bracket (5) does not act on the first pawl (11), under the direct or indirect effect of the first return spring (4), The first pawl (11) and the first inner ring (1) are in contact with each other, and/or the first pawl (11) and the first auxiliary inner ring (14) are in contact with each other under the direct or indirect action of the first return spring (4) when the first left clutch support (5) has no acting force on the first pawl (11), the first inner ring (1) is fixed in a one-way manner in the forward or reverse rotation direction and can rotate in a one-way manner in the reverse or forward rotation direction relative to the first outer ring (2) when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in a one-way in the reverse or reverse rotation direction and can rotate in a one-way in the reverse or forward rotation direction relative to the first outer ring (2) when the first pawl (11) is engaged with the first auxiliary forward rotation inner ring (14), and/or the first inner ring (1) is rotatable in both forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is rotatable in both forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first auxiliary inner ring (14), the contact pair of the first pawl (11) and the first inner ring (1) having an overload protection function when the first pawl (11) and the first inner ring (1) are in an engaged state, the first pawl (11) and the first inner ring (1) being automatically disengaged from each other when an excessive force acts between the first pawl (11) and the first inner ring (1), and/or the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) cannot be automatically disengaged when the acting force between the first pawl (11) and the first inner ring (1) is large, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has an overload protection function when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and/or the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, The contact pair of the first pawl (11) and the first auxiliary inner ring (14) has a self-locking function, when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, the first pawl (11) and the contact pair of the first auxiliary inner ring (14) cannot be automatically disengaged, the first clutch rivet (7) at least comprises one rivet, the first right clutch bracket (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch bracket (6) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), the first left clutch bracket (5) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), and/or the first outer ring (2) has a certain limiting effect on the first left clutch bracket (5) in the axial direction, The first left clutch support (5) is selectively movable in the axial direction relative to the first outer ring (2) against the action of the first outer ring (2), and/or at least a series of axial positioning grooves or projections are formed on the first outer ring (2), the first left clutch support (5) is at least configured to perform the function of axial positioning relative to the first outer ring (2) within a certain range by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected with the first outer ring (2), the first positioning means (19) rotates with the first outer ring (2), the first positioning means (19) is fixed in the axial direction relative to the first outer ring (2), and/or the first positioning means (19) is directly or indirectly connected with the first left clutch support (5), And the first positioning mechanism (19) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) is selectively moved relative to the first outer ring (2) in the axial direction against the effect of the first positioning mechanism (19), and/or a series of axial positioning grooves or protrusions are arranged on the first left clutch support (5), the first left clutch support (5) is at least configured to position at least one axial position thereof through the limiting effect of the series of axial positioning grooves or protrusions and the first positioning mechanism (19) within a certain range, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11), and the first left clutch support (5) is selectively moved relative to the first outer ring (2) in the axial direction within a certain range, so that the first pawl (11) and the first inner ring (2) are directly or indirectly moved 1) In the engaged or disengaged state, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range to directly or indirectly bring the first pawl (11) into the engaged or disengaged state with the first auxiliary inner ring (14), and/or the first left clutch support (5) is directly or indirectly connected with the actuating device (AM) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range under the drive of the actuating device (AM), and/or when the first left clutch support (5) is axially moved relative to the first outer ring (2) within a certain range under the action of the actuating device (AM) directly or indirectly, The first pawl (11) is in a state of engagement or disengagement with the first inner ring (1), and/or the first pawl (11) is in a state of engagement or disengagement with the first inner ring (1) when the first left clutch support (5) is in a position axially to the left remote from the first outer ring (2) directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in a state of engagement or disengagement with the first inner ring (1) when the first left clutch support (5) is in a position axially to the one side remote from the first outer ring (2) directly or indirectly under the action of the actuating device (AM), and/or the first limit pin (13) comprises at least one pin, the first limit pin (13) being fixedly connected directly or indirectly with the first inner ring (1), the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range defined by the first limit pin (13), the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1), and/or when the first inner ring (1) rotates reversely or positively relative to the first outer ring (2), under the direct or indirect action of the first pawl (11), After the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the first pawl (11) rotates relative to the first inner ring (1) and is contacted with the spliced cylindrical surface, so that the noise is greatly reduced; and/or

The one-way clutch mechanism (51) includes at least: the clutch comprises a first inner ring (1), a first outer ring (2), a first middle ring (45), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first auxiliary outer ring (12), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), and/or a first positioning mechanism (19), and/or a second limit pin (24), a second pawl (20), and a second return spring (21), wherein the first middle ring (45) is located between the first inner ring (1) and the first outer ring (2) in the radial direction, the first outer ring (2) is located on one side of the first middle ring (45), and the first inner ring (1), the first outer ring (2) are located on one side of the first middle ring (45), And/or the first left clutch support (5), and/or the first right clutch support (6), and/or a first auxiliary outer ring (12), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19) is arranged coaxially with the first middle ring (45), the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), and/or the second limit pin (24), The second pawl (20) and the second return spring (21) are axially arranged on one side of the first left clutch support (5), the first middle ring (45) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first middle ring (45) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first middle ring (45) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first middle ring (45) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with a driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M) And/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, the first inner ring (1) is unidirectionally fixed in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction relative to the first middle ring (45) at the initial position, and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at the initial position, the first auxiliary inner ring (14) is unidirectionally fixed in the forward or reverse direction and unidirectionally rotatable in the reverse or forward direction relative to the first middle ring (45) at the initial position, and/or the second pawl (20) is in an engagement state with the first outer ring (2) at the initial position, the first outer ring (2) is unidirectionally fixed in the forward or reverse direction relative to the first middle ring (45) at the initial position and is unidirectionally fixed in the forward or reverse direction relative to the first middle ring (45) at the forward or reverse direction And/or the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) at an initial position, at which the first auxiliary outer ring (12) is fixed unidirectionally in the forward or reverse direction with respect to the first middle ring (45) and is rotatable unidirectionally in the reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first inner ring (1) at an initial position, at which the first inner ring (1) is rotatable in both the forward and reverse directions with respect to the first middle ring (45), and/or the first pawl (11) is in a disengaged state with the first auxiliary inner ring (14) at an initial position, at which the first auxiliary inner ring (14) is rotatable in both the forward and reverse directions with respect to the first middle ring (45), and/or the second pawl (20) is in a disengaged state with the first outer ring (2) at an initial position, Wherein the first outer ring (2) is rotatable in both forward and reverse rotation directions with respect to the first middle ring (45), and/or the second pawls (20) are in a disengaged state with respect to the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is rotatable in both forward and reverse rotation directions with respect to the first middle ring (45), wherein the first inner ring (1) and the first outer ring (2) and the first middle ring (45) and the first auxiliary outer ring (12) and the first auxiliary inner ring (14) are configured with at least ratchet-like projections and/or ratchet-like recesses, and wherein the first pawls (11) and the second pawls (20) are configured with at least a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, wherein the first pawls (11) comprise at least one pawl, said first pawl (11) being directly or indirectly connected to said first middle ring (45), said first pawl (11) rotating with said first middle ring (45), said first pawl (11) being rotatable within an angular range relative to said first middle ring (45), and/or said first pawl (11) being directly or indirectly connected to said first right clutch bracket (6), said first pawl (11) rotating with said first right clutch bracket (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch bracket (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected to said first middle ring (45), said second pawl (20) rotating with said first middle ring (45), said second pawl (20) rotating within an angular range relative to said first middle ring (45), and/or the second pawl (20) is directly or indirectly connected with the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the first return spring (4) is directly or indirectly connected with the first pawl (11), and the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the elastic force of the second pawl (20), the second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), and/or when the first left clutch bracket (5) has no action force on the first pawl (11), the first pawl (11) and the first inner ring (1) are in contact with each other under the direct or indirect action of the first return spring (4), and/or the first pawl (11) and the first auxiliary inner ring (14) are in contact with each other under the direct or indirect action of the first return spring (4) when the first left clutch support (5) has no action on the first pawl (11), and/or the second pawl (20) and the first outer ring (2) are in contact with each other under the direct or indirect action of the second return spring (21) when the first left clutch support (5) has no action on the second pawl (20), and/or the second pawl (20) and the first auxiliary outer ring (12) are in contact with each other under the direct or indirect action of the second return spring (21) when the first left clutch support (5) has no action on the second pawl (20), and when the first pawl (11) and the first inner ring (1) are engaged, The first inner ring (1) is fixed in a unidirectional manner in the forward or reverse rotation direction and is rotatable in a unidirectional manner in the reverse or forward rotation direction relative to the first middle ring (45), and/or the first auxiliary inner ring (14) is fixed in a unidirectional manner in the forward or reverse rotation direction relative to the first middle ring (45) and is rotatable in a unidirectional manner in the reverse or forward rotation direction when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is rotatable in both the forward and reverse rotation directions relative to the first middle ring (45) within a certain load range when the first pawl (11) is disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is rotatable in both the forward and reverse rotation directions relative to the first middle ring (45) within a certain load range when the first pawl (11) is disengaged from the first auxiliary inner ring (14), and/or when the second pawl (20) is engaged with the first outer ring (2), the first outer ring (2) is fixed unidirectionally in the forward or reverse rotation direction and is rotatable unidirectionally in the reverse or forward rotation direction with respect to the first center ring (45), and/or when the second pawl (20) is engaged with the first auxiliary outer ring (12), the first auxiliary outer ring (12) is fixed unidirectionally in the forward or reverse rotation direction with respect to the first center ring (45) and is rotatable unidirectionally in the reverse or forward rotation direction, and/or when the second pawl (20) is disengaged from the first outer ring (2), the first outer ring (2) is rotatable both in the forward and reverse rotation direction with respect to the first center ring (45) within a certain load range, and/or when the second pawl (20) is disengaged from the first outer ring (12), the first outer ring (2) is rotatable in the forward or reverse rotation direction with respect to the first center ring (45), and/or when the second pawl (20) is disengaged from the first auxiliary outer ring (12), The first auxiliary outer ring (12) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle ring (45) within a certain load range, when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function, when an acting force between the first pawl (11) and the first inner ring (1) is excessive, the first pawl (11) and the first inner ring (1) are automatically disengaged, and/or when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function, and when the acting force between the first pawl (11) and the first inner ring (1) is large, the contact pair of the first pawl (11) and the first inner ring (1) can not automatically disengage, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of overload protection when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of self-locking when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, and the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the contact pair of the second pawl (20) and the first outer ring (2) has an overload protection function when the second pawl (20) and the first outer ring (2) are in an engaged state, the second pawl (20) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the second pawl (20) and the first outer ring (2), and/or the contact pair of the second pawl (20) and the first outer ring (2) has a self-locking function when the second pawl (20) and the first outer ring (2) are in the engaged state, the contact pair of the second pawl (20) and the first outer ring (2) are not automatically disengaged when the excessive force is applied between the second pawl (20) and the first outer ring (2), and/or the second pawl (20) and the first auxiliary outer ring (12) are in the engaged state, The contact pair of the second pawls (20) and the first auxiliary outer ring (12) has an overload protection function, the second pawls (20) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the second pawls (20) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the second pawls (20) and the first auxiliary outer ring (12) has a self-locking function when the acting force between the second pawls (20) and the first auxiliary outer ring (12) is in an engaged state, the contact pair of the second pawls (20) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the second pawls (20) and the first auxiliary outer ring (12) is large, and/or the first clutch rivet (7) comprises at least one rivet, and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first right clutch support (6) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), and/or the first left clutch support (5) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), and/or the first middle ring (45) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) overcomes the effect of the first middle ring (45) and selectively moves relative to the first middle ring (45) in the axial direction, and/or at least a series of axial positioning grooves or bulges are configured on the first middle ring (45), and the first left clutch support (5) is at least configured with a certain range of axial positioning functions relative to the first middle ring (45) through the series of axial positioning grooves or bulges, and/or the first positioning means (19) are directly or indirectly connected to the first central ring (45), the first positioning means (19) rotate together with the first central ring (45), the first positioning means (19) are axially fixed relative to the first central ring (45), and/or the first positioning means (19) are directly or indirectly connected to the first left clutch support (5), and the first positioning means (19) have a limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) is selectively movable in the axial direction relative to the first central ring (45) against the effect of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first left clutch support (5), the first left clutch support (5) being at least configured to pass through the series of axial positioning grooves or projections and the first positioning means (45) (19) The constraint action within a certain range positions at least one axial position of the first left clutch support (5), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11), and the first left clutch support (5) selectively moves axially relative to the first middle ring (45) within a certain range to directly or indirectly enable the first pawl (11) to be in an engagement or disengagement state with the first inner ring (1), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11), and the first left clutch support (5) selectively moves axially relative to the first middle ring (45) within a certain range to directly or indirectly enable the first pawl (11) to be in an engagement or disengagement state with the first auxiliary inner ring (14), and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20), And the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a certain range to directly or indirectly enable the second pawl (20) to be in an engaged or disengaged state with the first outer ring (2), and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20), and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a certain range to directly or indirectly enable the second pawl (20) to be in an engaged or disengaged state with the first auxiliary outer ring (12), and/or the first left clutch support (5) is directly or indirectly connected with the actuating device (AM), and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a certain range under the driving of the actuating device (AM), and/or when the first shift sleeve (18) is in an intermediate position axially with respect to the first inner ring (45) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2), and/or when the first shift sleeve (18) is in a position axially to the left away from the first inner ring (45) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2), and/or when the first shift sleeve (18) is axially to the side away from the first inner ring (18) directly or indirectly under the action of the actuating device (AM) When the ring (45) is at a certain position, the first pawl (11) is in an engagement or disengagement state with the first inner ring (1), the second pawl (20) is in an engagement or disengagement state with the first outer ring (2), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the second limit pin (24) comprises at least one pin, and/or the second limit pin (24) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and the first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1) under the action of the first pawl (11), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and under the action of the first pawl (11), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range limited by the first limit pin (13), and/or the first auxiliary inner ring (14) is arranged on one side of the first inner ring (1) in the axial direction, and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) at a certain angle, and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), And under the action of the second pawl (20), the first auxiliary outer ring (12) at least has the function of being capable of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), and/or the first auxiliary outer ring (12) is arranged on one side of the first outer ring (2) in the axial direction, and/or when the first inner ring (1) rotates reversely or normally relative to the first middle ring (45), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle defined by the first limit pin (13) relative to the first inner ring (1), the partial surface of the first auxiliary inner ring (14) and the partial surface of the first inner ring (1) are combined into a cylindrical surface, The first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first outer ring (2) rotates reversely or positively relative to the first middle ring (45), under the direct or indirect action of the second pawl (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), partial surface of the first auxiliary outer ring (12) is combined with partial surface of the first outer ring (2) to form a cylindrical surface, and the second pawl (20) contacts the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The material of the first bearing roller (9) at least has certain vibration damping or damping function; and/or

The material of the first wedge block (10) at least has certain vibration damping or damping function; and/or

The first pawl (11) is made of a material at least having a certain vibration reduction or damping function; and/or

The material of the first auxiliary outer ring (12) at least has certain vibration damping or damping function; and/or

The first limiting pin (13) is made of a material which at least has a certain vibration damping or damping function; and/or

The material of the first auxiliary inner ring (14) at least has certain vibration damping or damping function; and/or

The material of the first left half clutch (15) at least has certain vibration damping or damping function; and/or

The material of the first right half clutch (16) at least has certain vibration damping or damping function; and/or

The material of the first auxiliary right half clutch (17) at least has certain vibration damping or damping function; and/or

The material of the first gear shifting sleeve (18) at least has certain vibration damping or damping function; and/or

The material of the first positioning mechanism (19) at least has certain vibration damping or damping function; and/or

The material of the second pawl (20) at least has a certain vibration reduction or damping function; and/or

The material of the second return spring (21) at least has a certain vibration reduction or damping function; and/or

The material of the first auxiliary left half clutch (22) at least has certain vibration damping or damping function; and/or

The material of the first intermediate clutch (23) at least has certain vibration damping or damping function; and/or

The material of the second limit pin (24) at least has a certain vibration reduction or damping function; and/or

The material of the first gear shifting cam (25) at least has certain vibration damping or damping function; and/or

The material of the first transmission pin (26) at least has certain vibration damping or damping function; and/or

The material of the first middle ring (45) at least has certain vibration damping or damping function; and/or

The material of the second wedge block (46) at least has certain vibration damping or damping function; and/or

The material of the second retainer (47) at least has certain vibration damping or damping function; and/or

The material of the second bearing roller (48) at least has certain vibration damping or damping function; and/or

The first pawl (11) is of a single solid structure; and/or

The first pawl (11) is formed by a plurality of parts; and/or

The second pawl (20) is of unitary solid construction; and/or

The second pawl (20) is formed from a plurality of parts; and/or

Said first pawl (11) comprising at least: a first upper half pawl (40), a first lower half pawl (41), a first hydraulic damper (42), and/or a first spring damper (43), and/or a first material damper (44); and/or

The second pawl (20) comprises at least: a first upper half pawl (40), a first lower half pawl (41), a first hydraulic damper (42), and/or a first spring damper (43), and/or a first material damper (44); and/or

The first hydraulic damper (42) comprises at least one hydraulic damper; and/or

The first hydraulic damper (42) has at least a certain vibration damping or damping effect on the power or load transmitted by the first hydraulic damper by utilizing the vibration damping and damping effect of hydraulic pressure; and/or

The first spring damper (43) comprises at least one spring damper; and/or

The first spring damper (43) has at least a certain vibration damping or damping effect on the power or load transmitted by the first spring damper by utilizing the vibration damping and damping effect of the spring; and/or

The first material damper (44) at least comprises one material damper, and the first material damper (44) at least has certain vibration damping or damping effect on the power or load transmitted by the first material damper by utilizing the vibration damping and damping effect of the viscoelastic material; and/or

Said first upper half-pawl (40) is connected at least directly or indirectly with said first lower half-pawl (41) through said first hydraulic damper (42); and/or

The power or load of the first upper-half pawl (40) is transmitted to the first lower-half pawl (41) at least directly or indirectly through the first hydraulic damper (42); and/or

The power or load of the first lower half pawl (41) is transmitted to the first upper half pawl (40) at least directly or indirectly through the first hydraulic damper (42); and/or

The first upper half-pawl (40) is connected at least directly or indirectly via the first spring damper (43) to the first lower half-pawl (41); and/or

The power or load of the first upper half pawl (40) is transmitted to the first lower half pawl (41) at least directly or indirectly through the first spring damper (43); and/or

The power or load of the first lower half pawl (41) is transmitted to the first upper half pawl (40) at least directly or indirectly through the first spring damper (43); and/or

The first upper pawl half (40) is connected to the first lower pawl half (41) at least directly or indirectly through the first material damper (44); and/or

The power or load of the first upper pawl half (40) is transmitted to the first lower pawl half (41) at least directly or indirectly through the first material damper (44); and/or

The power or load of the first lower pawl half (41) is transmitted to the first upper pawl half (40) at least directly or indirectly through the first material damper (44).

4. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a ratchet clutch mechanism (52);

the ratchet wheel clutch mechanism (52) is at least provided with a mechanism for selectively realizing the connection and disconnection of the power of the connected piece by using the connection and the disconnection of the pawl and the ratchet wheel; and/or

The ratchet clutch mechanism (52) is configured to selectively transmit the power of one of the moving members to the other moving member by using at least the engagement and disengagement of the pawl and the ratchet; and/or

The ratchet clutch mechanism (52) is configured to selectively transmit the power of one of the moving parts to the other moving parts by using the engagement and the disengagement of the pawl and the ratchet; and/or

The ratchet clutch mechanism (52) is configured to at least selectively realize the connection and disconnection of the motion of the connected piece by using the connection and disconnection of the pawl and the ratchet; and/or

The ratchet clutch mechanism (52) is configured to selectively transmit the movement of one of the moving members to the other moving member by at least engagement and disengagement of the pawl and the ratchet; and/or

The ratchet clutch mechanism (52) is configured to selectively transmit the movement of one of the moving members to the other moving members by using at least the engagement and disengagement of the pawl and the ratchet; and/or

The ratchet wheel clutch mechanism (52) is at least provided with a function of selectively keeping the moving piece connected with the ratchet wheel to rotate and accelerate or rotate and decelerate by utilizing the engagement and the disengagement of the pawl and the ratchet wheel; and/or

The ratchet clutch mechanism (52) is configured to have at least a function of selectively stopping rotation of the connected moving member by engagement and disengagement of the pawl and the ratchet; and/or

The ratchet clutch mechanism (52) is configured to have at least a function of selectively keeping the connected moving member in a stopped state by engagement and disengagement of the pawl and the ratchet;

the ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first lever mechanism (27), wherein the first outer ring (2) is arranged at one side of the first inner ring (1) in the radial direction, and the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary inner ring (14), The first shifting sleeve (18) and/or the first positioning means (19) are arranged coaxially to the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch support (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), the first shifting sleeve (18), and/or the first positioning means (19), and/or the second pawl (20), and/or the second return spring (21), the first lever means (27) are arranged axially on one side of the first right clutch support (6), the first inner ring (1) is directly or indirectly connected to the driving element of the machine (M) and follows the driving element of the machine (M) -the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or-the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates with a driven part of the machine (M), and/or-the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or-the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates with a driving part of the machine (M), and/or-the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or-the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates with a driven part of the machine (M) The movable piece rotates together, and/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, the first inner ring (1) is fixed in a forward or reverse rotation direction relative to the first outer ring (2) in a one-way mode, and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at an initial position, the first auxiliary inner ring (14) is fixed in a forward or reverse rotation direction relative to the first outer ring (2) in a one-way mode, and/or the second pawl (20) is in an engagement state with the first inner ring (1) at an initial position, the first inner ring (1) is fixed in a forward or reverse rotation direction relative to the first outer ring (2) in a one-way mode, and/or the second pawl (20) is in an engaged state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is fixed in a unidirectional manner in a reverse or forward direction with respect to the first outer ring (2), and/or the first pawl (11) is in a disengaged state with the first inner ring (1) at an initial position, when the first inner ring (1) is rotatable in a reverse or forward direction with respect to the first outer ring (2), and/or the first pawl (11) is in a disengaged state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is rotatable in a reverse or forward direction with respect to the first outer ring (2), and/or the second pawl (20) is in a disengaged state with the first inner ring (1) at an initial position, The first inner ring (1) can rotate in the forward or reverse direction relative to the first outer ring (2) at the moment, and/or the second pawl (20) is in a separation state from the first auxiliary inner ring (14) at the initial position, the first auxiliary inner ring (14) can rotate in the forward or reverse direction relative to the first outer ring (2) at the moment, the first inner ring (1), the first outer ring (2) and the first auxiliary inner ring (14) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) and the second pawl (20) are at least configured with a function of engaging with or separating from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) at least comprises one pawl, and the first pawl (11) is directly or indirectly connected with the first outer ring (2), Said first pawl (11) rotating together with said first outer ring (2), said first pawl (11) being rotatable within an angular range relative to said first outer ring (2), and/or said first pawl (11) being directly or indirectly connected to said first left clutch support (5), said first pawl (11) rotating together with said first left clutch support (5), said first pawl (11) being rotatable within an angular range relative to said first left clutch support (5), and/or said first pawl (11) being directly or indirectly connected to said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, the second pawl (20) is directly or indirectly connected to the first outer ring (2), the second pawl (20) rotates together with the first outer ring (2), the second pawl (20) can rotate relative to the first outer ring (2) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), and the second return spring (21) is directly or indirectly connected with the second pawl (20), -the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other restraint or load on the second pawl (20) is less than the action of the spring force of the second return spring (21), the first inner ring (1) being fixed unidirectionally in the forward or reverse direction with respect to the first outer ring (2) when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) being fixed unidirectionally in the forward or reverse direction with respect to the first outer ring (2) when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) being fixed unidirectionally in the reverse or reverse direction with respect to the first outer ring (2) when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward direction relative to the first outer ring (2) when the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in both the forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both the forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the second pawl (20) is disengaged from the first inner ring (1) when the first pawl (11) is engaged with the first inner ring (1), and the second pawl (20) is disengaged from the first inner ring (1), -the first inner ring (1) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first outer ring (2) within a certain load range, and/or-the first auxiliary inner ring (14) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), and/or-the first inner ring (1) is fixed in a reverse or forward direction and rotatable in a forward or reverse direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is rotatable in both the forward and reverse directions with respect to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is rotatable in both the forward and reverse directions with respect to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary inner ring (14), when the first pawl (11) is in an engaged state with the first inner ring (1), the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function, when the acting force between the first pawl (11) and the first inner ring (1) is excessive, the first pawl (11) and the first inner ring (1) are automatically disengaged, and/or when the acting force between the first pawl (11) and the first inner ring (1) is excessive, the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function, when the acting force between the first pawl (11) and the first inner ring (1) is large, the contact pair of the first pawl (11) and the first inner ring (1) is not automatically disengaged, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged, The contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of overload protection, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of self-locking when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is in an engaged state, the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the second pawl (20) and the first inner ring (1) are in an engaged state, The contact pair of the second pawl (20) and the first inner ring (1) has the function of overload protection, the second pawl (20) and the first inner ring (1) are automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is excessive, and/or the contact pair of the second pawl (20) and the first inner ring (1) has the function of self-locking when the acting force between the second pawl (20) and the first inner ring (1) is in the engaged state, the contact pair of the second pawl (20) and the first inner ring (1) is not automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is large, and/or the contact pair of the second pawl (20) and the first auxiliary inner ring (14) has the function of overload protection when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is in the engaged state, When the acting force between the second pawl (20) and the first auxiliary inner ring (14) is excessive, the second pawl (20) is automatically disengaged from the first auxiliary inner ring (14), and/or when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, a contact pair of the second pawl (20) and the first auxiliary inner ring (14) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is large, the contact pair of the second pawl (20) and the first auxiliary inner ring (14) is not automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first clutch rivet (7) comprises at least one rivet, and/or the first left clutch support (5) is fixedly connected to the first outer ring (2) by means of the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected to the first outer ring (2) by means of the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first outer ring (2) and rotates with the first outer ring (2), and/or the first outer ring (2) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first outer ring (2) against the effect of the first outer ring (2), and/or the first outer ring (2) is at least provided with a series of axial positioning grooves or projections, The first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first outer ring (2) via the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first left clutch carrier (5) against the action of the first left clutch carrier (5), and/or the first left clutch carrier (5) is at least designed with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first outer ring (2) via the series of axial positioning grooves or projections within a certain range -a function of axial positioning of the left clutch carrier (5), and/or-a function of axial positioning of the first shift sleeve (18) directly or indirectly connected to the first right clutch carrier (6) and rotating with the first right clutch carrier (6), and/or-a function of axial positioning of the first shift sleeve (18) with respect to the first right clutch carrier (6) in an axial direction, a certain limiting effect of the first shift sleeve (18) against the effect of the first right clutch carrier (6), a selective movement of the first shift sleeve (18) in an axial direction with respect to the first right clutch carrier (6) against the effect of the first right clutch carrier (6), and/or-a function of axial positioning of the first shift sleeve (18) with respect to the first right clutch carrier (6) at least over a certain range by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected to the first outer ring (2), the first positioning means (19) rotates with the first outer ring (2), the first positioning means (19) is axially fixed relative to the first outer ring (2), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch support (5), the first positioning means (19) rotates with the first left clutch support (5), the first positioning means (19) is axially fixed relative to the first left clutch support (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch support (6), the first positioning means (19) rotates with the first right clutch support (6), the first positioning means (19) is axially fixed relative to the first right clutch support (6), and/or the first positioning means (19) is directly or indirectly connected to the first shifting sleeve (18) and the first positioning means (19) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction relative to the first outer ring (2) against the effect of the first positioning means (19), and/or the first shifting sleeve (18) is provided with a series of axial positioning grooves or projections, the first shifting sleeve (18) is at least configured to position at least one axial position thereof by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shifting sleeve (18) is directly or indirectly connected to the first pawl (11), And the selective axial movement of the first shift sleeve (18) relative to the first outer ring (2) within a certain range brings at least the first pawl (11) into or out of engagement with the first inner ring (1) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected with the first pawl (11), and the selective axial movement of the first shift sleeve (18) relative to the first outer ring (2) within a certain range brings at least the first pawl (11) into or out of engagement with the first auxiliary inner ring (14) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected with the second pawl (20), and the selective axial movement of the first shift sleeve (18) relative to the first outer ring (2) within a certain range brings at least the second pawl (20) into engagement with the first inner ring (1) directly or indirectly Or a disengaged state, and/or said first shift sleeve (18) is directly or indirectly connected to said second pawl (20) and said first shift sleeve (18) is selectively axially displaced with respect to said first outer ring (2) within a range at least directly or indirectly bringing said second pawl (20) into engagement or disengagement with said first auxiliary inner ring (14), and/or said first lever mechanism (27) comprises at least one lever, and/or said first lever mechanism (27) is directly or indirectly connected to said first outer ring (2) and rotates together with said first outer ring (2), and/or said first lever mechanism (27) is directly or indirectly connected to said first left clutch bracket (5) and rotates together with said first left clutch bracket (5), and/or said first lever mechanism (27) is directly or indirectly connected to said first right clutch bracket (6) and rotates together with said first right clutch bracket (6) The clutch carrier (6) rotates together, and/or the first shift sleeve (18) is connected to the first pawl (11) via the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced relative to the first outer ring (2) within a certain range, the first pawl (11) and the first inner ring (1) are brought into an engaged or disengaged state via the first lever mechanism (27), and/or the first shift sleeve (18) is connected to the first pawl (11) via the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced relative to the first outer ring (2) within a certain range, the first pawl (11) and the first auxiliary inner ring (14) are brought into an engaged or disengaged state via the first lever mechanism (27), and/or the first shift sleeve (18) is connected to the second pawl (20) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced in a range relative to the first outer ring (2) by means of the first lever mechanism (27) to bring the second pawl (20) into engagement or disengagement with the first inner ring (1), and/or the first shift sleeve (18) is connected to the second pawl (20) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced in a range relative to the first outer ring (2) by means of the first lever mechanism (27) to bring the second pawl (20) into engagement or disengagement with the first auxiliary inner ring (14), and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM), And the first shift sleeve (18) is driven by the actuating device (AM) to selectively move axially within a certain range relative to the first outer ring (2), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1) when the first shift sleeve (18) is at a certain intermediate position axially relative to the first outer ring (2) directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), when the first shift sleeve (18) is at a certain position axially leftward away from the first outer ring (2) directly or indirectly under the action of the actuating device (AM), The second pawl (20) is in engagement or disengagement with the first inner ring (1) (16) and/or the first pawl (11) is in engagement or disengagement with the first inner ring (1) when the first shift sleeve (18) is axially on one side away from the first outer ring (2) directly or indirectly under the action of the actuating device (AM), the second pawl (20) is in engagement or disengagement with the first inner ring (1), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1) and under the action of the first pawl (11) or the second pawl (20), The first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has a function of rotating relative to the first inner ring (1) within an angle range defined by the first limit pin (13), and/or the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1) in the axial direction, and/or the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1) under the direct or indirect action of the first pawl (11) when the first inner ring (1) reversely rotates or forwardly rotates relative to the first outer ring (2), Or after the first auxiliary inner ring (14) rotates relative to the first inner ring (1) to the angle limited by the first limit pin (13), a part of the surface of the first auxiliary inner ring (14) is spliced with a part of the surface of the first inner ring (1) to form a cylindrical surface, and the first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced, and/or when the first inner ring (1) rotates forwards or backwards relative to the first outer ring (2), under the direct or indirect action of the second pawl (20), after the first auxiliary inner ring (14) rotates relative to the first inner ring (1) to a certain angle, or after the first auxiliary inner ring (14) rotates relative to the first inner ring (1) to the angle limited by the first limit pin (13), Part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the second pawl (20) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), the first gear shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the second limit pin (24), the first lever mechanism (27), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32), A second lever mechanism (49), wherein the first middle ring (45) is located between the first inner ring (1) and the first outer ring (2) in the radial direction, and the first outer ring (2) is located on one side of the first middle ring (45) in the radial direction, the first inner ring (1), the first outer ring (2), and/or the first left clutch bracket (5), and/or the first right clutch bracket (6), and/or the first auxiliary outer ring (12), and/or the first auxiliary inner ring (14), the first shift gear sleeve (18), and/or the first positioning mechanism (19) are arranged coaxially with the first middle ring (45), and/or the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first left clutch bracket (5), And/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), the first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the second limit pin (24), the first lever mechanism (27), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32), the second lever mechanism (49) are arranged axially on one side of the first right clutch bracket (6), and/or the first inner ring (1) is directly or indirectly connected with a driving member of the machine (M) And rotates with a driving member of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven member of the machine (M) and rotates with a driven member of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving member of the machine (M) and rotates with a driving member of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected to a frame of the machine (M), and/or the first middle ring (45) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first middle ring (45) is directly or indirectly connected to and rotates with the damping Device (DM), and/or the first middle ring (45) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first middle ring (45) is directly or indirectly fixedly connected to a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, when the first inner ring (1) is unidirectionally fixed in the forward or reverse direction relative to the first middle ring (45), and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is unidirectionally fixed in the forward or reverse direction relative to the first middle ring (45), and/or the second pawl (20) is in an engagement state with the first inner ring (1) at an initial position, when the first inner ring (1) is unidirectionally fixed in the reverse or forward direction relative to the first middle ring (45), and/or the second pawl (20) is in an engagement state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is unidirectionally fixed in the reverse or forward direction relative to the first middle ring (45) And/or the third pawl (29) is in engagement with the first outer ring (2) in an initial position, in which the first outer ring (2) is fixed unidirectionally in the forward or reverse direction relative to the first middle ring (45), and/or the third pawl (29) is in engagement with the first auxiliary outer ring (12) in an initial position, in which the first auxiliary outer ring (12) is fixed unidirectionally in the forward or reverse direction relative to the first middle ring (45), and/or the fourth pawl (31) is in engagement with the first outer ring (2) in an initial position, in which the first outer ring (2) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45), and/or the fourth pawl (31) is in engagement with the first auxiliary outer ring (12) in an initial position, The first auxiliary outer ring (12) is fixed in a single direction in the reverse or forward rotation direction relative to the first middle ring (45) at the moment, and/or the first pawl (11) is separated from the first inner ring (1) at the initial position, the first inner ring (1) can rotate in the reverse or forward rotation direction relative to the first middle ring (45), and/or the first pawl (11) is separated from the first auxiliary inner ring (14) at the initial position, the first auxiliary inner ring (14) can rotate in the reverse or forward rotation direction relative to the first middle ring (45), and/or the second pawl (20) is separated from the first inner ring (1) at the initial position, the first inner ring (1) can rotate in the forward or reverse rotation direction relative to the first middle ring (45), and/or the second pawl (20) is separated from the first auxiliary inner ring (14) at the initial position A disengaged state in which the first auxiliary inner ring (14) is rotatable in the normal or reverse rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in a disengaged state from the first outer ring (2) in an initial position in which the first outer ring (2) is rotatable in the reverse or normal rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in a disengaged state from the first auxiliary outer ring (12) in an initial position in which the first auxiliary outer ring (12) is rotatable in the reverse or normal rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in a disengaged state from the first outer ring (2) in an initial position in which the first outer ring (2) is rotatable in the normal or reverse rotation direction with respect to the first middle ring (45), and/or the fourth pawls (31) are disengaged from the first auxiliary outer race (12) at an initial position, in which the first auxiliary outer race (12) is rotatable in the forward or reverse rotation direction with respect to the first middle race (45), the first inner race (1) and the first outer race (2) and the first middle race (45) and the first auxiliary outer race (12) and the first auxiliary inner race (14) are configured with at least ratchet-like projections and/or ratchet-like grooves, and the first pawls (11) and the second pawls (20) and the third pawls (29) and the fourth pawls (31) are configured with at least a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like grooves, the first pawls (11) include at least one pawl, the first pawls (11) are directly or indirectly connected with the first middle race (45), and the second pawls (11) are directly or indirectly connected with or disengaged from the first middle race (45), Said first pawl (11) rotating together with said first middle ring (45), said first pawl (11) being rotatable within an angular range relative to said first middle ring (45), and/or said first pawl (11) being directly or indirectly connected to said first left clutch support (5), said first pawl (11) rotating together with said first left clutch support (5), said first pawl (11) being rotatable within an angular range relative to said first left clutch support (5), and/or said first pawl (11) being directly or indirectly connected to said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, the second pawl (20) is directly or indirectly connected to the first center ring (45), the second pawl (20) rotates together with the first center ring (45), the second pawl (20) can rotate relative to the first center ring (45) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the third pawl (29) comprises at least one pawl, the third pawl (29) is directly or indirectly connected with the first middle ring (45), the third pawl (29) rotates together with the first middle ring (45), the third pawl (29) can rotate relative to the first middle ring (45) within a certain angle range, and/or the third pawl (29) is directly or indirectly connected with the first left clutch support (5), the third pawl (29) rotates together with the first left clutch support (5), the third pawl (29) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the third pawl (29) is directly or indirectly connected with the first right clutch support (6), the third pawl (29) rotates together with the first right clutch support (6), The third pawl (29) can rotate within a certain angle range relative to the first right clutch support (6), the fourth pawl (31) comprises at least one pawl, the fourth pawl (31) is directly or indirectly connected with the first middle ring (45), the fourth pawl (31) rotates with the first middle ring (45), the fourth pawl (31) can rotate within a certain angle range relative to the first middle ring (45), and/or the fourth pawl (31) is directly or indirectly connected with the first left clutch support (5), the fourth pawl (31) rotates relative to the first left clutch support (5) within a certain angle range, and/or the fourth pawl (31) is directly or indirectly connected with the first right clutch support (6), The fourth pawl (31) rotates together with the first right clutch support (6), the fourth pawl (31) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the elastic force of the first pawl (11) is smaller than the elastic force of the first return spring (4) under the action of other restraint or load, the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the elastic action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the elastic action of the second return spring (21), the third return spring (30) at least comprises one spring, the third return spring (30) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the third return spring (30) is directly or indirectly connected with the third pawl (29), when the action of other restraint or load on the third pawl is smaller than the action of the third return spring (30) on the third pawl (29) The third pawl (29) is restored to the initial position by the elastic force of the third return spring (30) when the elastic force of the third pawl (29) acts, the fourth return spring (32) comprises at least one spring, the fourth return spring (32) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the fourth return spring (32) is directly or indirectly connected with the fourth pawl (31), the fourth pawl (31) is restored to the initial position by the elastic force of the fourth return spring (32) when the action of other restraint or load on the fourth pawl (31) is smaller than the elastic force of the fourth return spring (32) on the fourth pawl (31), and the first inner ring (1) is fixed in one direction relative to the first middle ring (45) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the forward or reverse direction relative to the first middle ring (45) when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the forward and reverse directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first inner ring (1) and the second pawl (20) is disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), and the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in a certain load range Rotatable in a reverse or forward direction, and/or when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), the first inner ring (1) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), the first auxiliary inner ring (14) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) and the second pawl (20) are disengaged from the first inner ring (1), -the first inner ring (1) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range, and/or-the first auxiliary inner ring (14) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary inner ring (14), and/or-the first outer ring (2) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first outer ring (2), and/or-the first auxiliary outer ring (12) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed relative to the first middle ring (45) in both the forward and reverse directions over a range of loads when the third pawls (29) and the fourth pawls (31) are engaged with the first outer ring (2), and/or the third pawls (29) and the fourth pawls (31) are engaged with the first auxiliary outer ring (12) over a range of loads, The first auxiliary outer ring (12) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45), and/or the first outer ring (2) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first outer ring (2) and the fourth pawls (31) are disengaged with respect to the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first auxiliary outer ring (12) and the fourth pawls (31) are disengaged with respect to the first auxiliary outer ring (12), and/or the third pawls (29) are disengaged with respect to the first middle ring (2) and the fourth pawls (31) are disengaged with the outer ring (31) The first outer ring (2) being fixed in the reverse or forward rotation direction and rotatable in the forward or reverse rotation direction with respect to the first middle ring (45) within a certain load range when the first outer ring (2) is engaged, and/or the first auxiliary outer ring (12) being fixed in the reverse or forward rotation direction with respect to the first middle ring (45) and rotatable in the forward or reverse rotation direction within a certain load range when the third pawls (29) are disengaged from the first auxiliary outer ring (12) and the fourth pawls (31) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) being rotatable in both the forward and reverse rotation direction with respect to the first middle ring (45) within a certain load range when the third pawls (29) and the fourth pawls (31) are disengaged from the first outer ring (2), and/or the first auxiliary outer ring (12) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle ring (45) within a certain load range when the third pawls (29) and the fourth pawls (31) are separated from the first auxiliary outer ring (12), the contact pair of the first pawls (11) and the first inner ring (1) has an overload protection function when the first pawls (11) and the first inner ring (1) are in an engaged state, the first pawls (11) and the first inner ring (1) are automatically disengaged when an excessive force is applied between the first pawls (11) and the first inner ring (1), and/or the contact pair of the first pawls (11) and the first inner ring (1) has a self-locking function, a self-locking function, When the acting force between the first pawl (11) and the first inner ring (1) is large, the first pawl (11) and the first inner ring (1) contact pair can not automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, the first pawl (11) and the first auxiliary inner ring (14) automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of self-locking, When the acting force between the first pawl (11) and the first auxiliary inner ring (14) is larger, the first pawl (11) and the first auxiliary inner ring (14) contact pair can not automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of overload protection, when the acting force between the second pawl (20) and the first inner ring (1) is too large, the second pawl (20) and the first inner ring (1) automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of self-locking, when the acting force between the second pawl (20) and the first inner ring (1) is larger, the second pawl (20) and the first inner ring (1) contact pair have the function of self-locking, The second pawl (20) and the first inner ring (1) contact pair can not automatically disengage, and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has an overload protection function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, the second pawl (20) and the first auxiliary inner ring (14) automatically disengage when an excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, and the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), The second pawl (20) is not automatically disengaged from the first auxiliary inner ring (14) contact pair, and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair with an overload protection function when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is automatically disengaged from the first outer ring (2) when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is not automatically disengaged from the first outer ring (2) contact pair when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has an overload protection function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), the third pawls (29) are automatically disengaged from the first auxiliary outer ring (12) when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has a self-locking function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), and the contact pair of the third pawls (29) with the first auxiliary outer ring (12) is not automatically disengaged when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has an overload protection function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the fourth pawl (31) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has a self-locking function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the contact pair of the fourth pawl (31) and the first outer ring (2) are not automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has an overload protection function, the fourth pawl (31) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has a self-locking function when the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is large, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first right clutch support (6) is directly or indirectly fixedly connected to the first center ring (45), and/or the first left clutch support (5) comprises at least one rivet, and/or the first left clutch support (7) is fixedly connected to the first center ring (45) by means of the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected to the first center ring (45) by means of the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first center ring (45) and rotates together with the first center ring (45), and/or the first center ring (45) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first center ring (45) against the effect of the first center ring (45), and/or the first center ring (45) is provided with at least one series of axial positioning grooves or projections, the first shift sleeve (18) is provided with at least one function of axial positioning relative to the first center ring (45) through the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected with the first left clutch support (5) and rotates together with the first left clutch support (5), and/or the first left clutch support (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first left clutch support (5) against the effect of the first left clutch support (5), and/or the first left clutch support (5) is provided with at least one series of axial positioning grooves or projections, The first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first left clutch support (5) via the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch support (6) and rotates together with the first right clutch support (6), and/or the first right clutch support (6) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first right clutch support (6) against the action of the first right clutch support (6), and/or the first right clutch support (6) is at least designed with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least designed to perform an axial positioning function or projection within a certain range relative to the first right clutch support (6) via the series of axial positioning grooves or projections The first right clutch bracket (6) has an axial positioning function, and/or the first positioning mechanism (19) is directly or indirectly connected with the first middle ring (45), the first positioning mechanism (19) rotates together with the first middle ring (45), the first positioning mechanism (19) is axially fixed relative to the first middle ring (45), and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch bracket (5), the first positioning mechanism (19) rotates together with the first left clutch bracket (5), the first positioning mechanism (19) is axially fixed relative to the first left clutch bracket (5), and/or the first positioning mechanism (19) is directly or indirectly connected with the first right clutch bracket (6), the first positioning mechanism (19) rotates together with the first right clutch bracket (6), The first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is axially selectively movable relative to the first center ring (45) against the effect of the first positioning means (19), and/or the first shift sleeve (18) is provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least configured to position at least one axial position thereof by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11) And a selected axial movement of the first shift sleeve (18) relative to the first inner ring (45) within a certain range brings at least the first pawl (11) into or out of engagement with the first inner ring (1) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11), and a selected axial movement of the first shift sleeve (18) relative to the first inner ring (45) within a certain range brings at least the first pawl (11) into or out of engagement with the first auxiliary inner ring (14) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected to the second pawl (20), and a selected axial movement of the first shift sleeve (18) relative to the first inner ring (45) within a certain range brings at least the second pawl (20) into or out of engagement with the first inner ring (1) directly or indirectly An engaged or disengaged state, and/or said first shift sleeve (18) being directly or indirectly connected to said second pawl (20) and said first shift sleeve (18) being selectively axially displaced within a range relative to said first intermediate ring (45) at least directly or indirectly bringing said second pawl (20) into or out of engagement with said first auxiliary inner ring (14), and/or said first shift sleeve (18) being directly or indirectly connected to said third pawl (29) and said first shift sleeve (18) being selectively axially displaced within a range relative to said first intermediate ring (45) at least directly or indirectly bringing said third pawl (29) into or out of engagement with said first outer ring (2), and/or said first shift sleeve (18) being directly or indirectly connected to said third pawl (29), And said first shift sleeve (18) being selectively axially movable within a range relative to said first intermediate ring (45) to at least directly or indirectly bring said third pawl (29) into engagement with or disengagement from said first auxiliary outer ring (12), and/or said first shift sleeve (18) being directly or indirectly connected with said fourth pawl (31), and said first shift sleeve (18) being selectively axially movable within a range relative to said first intermediate ring (45) to at least directly or indirectly bring said fourth pawl (31) into engagement with or disengagement from said first outer ring (2), and/or said first shift sleeve (18) being directly or indirectly connected with said fourth pawl (31), and said first shift sleeve (18) being selectively axially movable within a range relative to said first intermediate ring (45) to at least directly or indirectly bring said fourth pawl (31) into engagement with or disengagement from said first auxiliary outer ring (12) -an engaged or disengaged state, and/or the first lever means (27) comprises at least one lever, and/or the first lever means (27) is directly or indirectly connected with the first centre ring (45) and rotates together with the first centre ring (45), and/or the first lever means (27) is directly or indirectly connected with the first left clutch bracket (5) and rotates together with the first left clutch bracket (5), and/or the first lever means (27) is directly or indirectly connected with the first right clutch bracket (6) and rotates together with the first right clutch bracket (6), and/or the second lever means (49) comprises at least one lever, and/or the second lever means (49) is directly or indirectly connected with the first centre ring (45) and rotates together with the first centre ring (45), and/or the second lever mechanism (49) is directly or indirectly connected to the first left clutch support (5) and rotates together with the first left clutch support (5), and/or the second lever mechanism (49) is directly or indirectly connected to the first right clutch support (6) and rotates together with the first right clutch support (6), and/or the first shift sleeve (18) is connected to the first pawl (11) via the first lever mechanism (27), and an axial movement of the first shift sleeve (18) brings the first pawl (11) into or out of engagement with the first inner ring (1) via the first lever mechanism (27), and/or the first shift sleeve (18) is connected to the first pawl (11) via the first lever mechanism (27), and an axial movement of the first shift sleeve (18) directly or indirectly brings the first pawl (11) into or out of engagement with the first inner ring (1) -a first auxiliary inner ring (14) is in engaged or disengaged state, and/or-the first shift sleeve (18) is connected with the second pawl (20) by means of the first lever mechanism (27), and-an axial movement of the first shift sleeve (18) brings the second pawl (20) into engaged or disengaged state with the first inner ring (1) by means of the first lever mechanism (27), and/or-the first shift sleeve (18) is connected with the second pawl (20) by means of the first lever mechanism (27), and-an axial movement of the first shift sleeve (18) brings the second pawl (20) into engaged or disengaged state with the first auxiliary inner ring (14) by means of the first lever mechanism (27), and/or-the first shift sleeve (18) is connected with the third pawl (29) by means of the second lever mechanism (49), And the axial movement of the first shift sleeve (18) brings the third pawl (29) into or out of engagement with the first outer ring (2) via the second lever mechanism (49) and/or the first shift sleeve (18) is connected to the third pawl (29) via the second lever mechanism (49) and the axial movement of the first shift sleeve (18) directly or indirectly brings the third pawl (29) into or out of engagement with the first auxiliary outer ring (12) and/or the first shift sleeve (18) is connected to the fourth pawl (31) via the second lever mechanism (49) and the axial movement of the first shift sleeve (18) brings the fourth pawl (31) into or out of engagement with the first outer ring (2) via the second lever mechanism (49), and/or the first shift sleeve (18) is connected to the fourth pawl (31) by means of the second lever mechanism (49) and the axial movement of the first shift sleeve (18) directly or indirectly brings the fourth pawl (31) into or out of engagement with the first auxiliary outer ring (12) and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve (18) is selectively axially movable relative to the first inner ring (45) under the drive of the actuating device (AM) and/or the first pawl (11) is brought into or out of engagement with the first inner ring (1) when the first shift sleeve (18) is brought into a certain intermediate position axially relative to the first inner ring (45) directly or indirectly under the action of the actuating device (AM), The second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2) when the first shift sleeve (18) is in a position axially to the left away from the first middle ring (45) directly or indirectly under the action of the Actuating Means (AM), and/or when the first shift sleeve (18) is axially on one side away from the first middle ring (45) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2),

And/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the second limit pin (24) at least comprises one pin, and/or the second limit pin (24) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), And the first auxiliary inner ring (14) has at least the function of being rotatable relative to the first inner ring (1) within the angular range defined by the first limit pin (13) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary inner ring (14) is arranged axially on one side of the first inner ring (1), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and the first auxiliary outer ring (12) has at least the function of being rotatable relative to the first outer ring (2) at an angle under the action of the third pawl (29) or the fourth pawl (31), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), and the function of being rotatable relative to the first outer ring (2) under the action of the third pawl (29) or the fourth pawl (31), The first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), and/or the first auxiliary outer ring (12) is arranged on one side of the first outer ring (2) in the axial direction, and/or when the first inner ring (1) rotates reversely or forwardly relative to the first middle ring (45), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to the angle defined by the first limit pin (13) relative to the first inner ring (1), the partial surface of the first auxiliary inner ring (14) and the partial surface of the first inner ring (1) are combined to form a cylindrical surface, The first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first inner ring (1) rotates forwards or reversely relative to the first middle ring (45), under the direct or indirect action of the second pawl (20), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1) or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the second pawl (20) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first outer ring (2) rotates reversely or forwardly relative to the first middle ring (45), under the direct or indirect action of the third pawl (29), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) is combined with part of the surface of the first outer ring (2) to form a cylindrical surface, the third pawl (29) contacts with the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced, and/or when the first outer ring (2) rotates forwardly or reversely relative to the first middle ring (45), under the direct or indirect action of the fourth pawl (31), After the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), a part of the surface of the first auxiliary outer ring (12) and a part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, and the fourth pawl (31) contacts the spliced cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or the first auxiliary outer ring (12), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first lever mechanism (27), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12), The first shifting sleeve (18) and/or the first positioning means (19) are arranged coaxially with the first inner ring (1) and/or the first inner ring (1), the first outer ring (2), the first return spring (4) and/or the first left clutch support (5) and/or the first clutch rivet (7), the first pawl (11) and/or the first auxiliary outer ring (12) and/or the first limit pin (13), the first shifting sleeve (18) and/or the first positioning means (19) and/or the second pawl (20) and/or the second return spring (21), the first lever means (27) are arranged axially on one side of the first right clutch support (6), the first inner ring (1) is directly or indirectly connected with the main part of the machine (M) and is connected with the machine (M) M), and/or the first inner ring (1) is directly or indirectly connected with and rotates with the cushion damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with and rotates with the driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with and rotates with the frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the cushion damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the driven part of the machine (M) (M) the driven member rotates together, and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engaged state with the first outer ring (2) at an initial position, at which time the first outer ring (2) is fixed unidirectionally with respect to the first inner ring (1) in the forward or reverse direction, and/or the first pawl (11) is in an engaged state with the first auxiliary outer ring (12) at an initial position, at which time the first auxiliary outer ring (12) is fixed unidirectionally with respect to the first inner ring (1) in the forward or reverse direction, and/or the second pawl (20) is in an engaged state with the first outer ring (2) at an initial position, at which time the first outer ring (2) is fixed unidirectionally with respect to the first inner ring (1) in the forward or reverse direction, and/or the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) at an initial position, when the first auxiliary outer ring (12) is fixed unidirectionally with respect to the first inner ring (1) in the reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first outer ring (2) at an initial position, when the first outer ring (2) is rotatable with respect to the first inner ring (1) in the reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first auxiliary outer ring (12) at an initial position, when the first auxiliary outer ring (12) is rotatable with respect to the first inner ring (1) in the reverse or forward direction, and/or the second pawl (20) is in a disengaged state with respect to the first outer ring (2) at an initial position, Wherein the first outer ring (2) is rotatable in a forward or reverse direction with respect to the first inner ring (1), and/or the second pawl (20) is in a disengaged state from the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is rotatable in a forward or reverse direction with respect to the first inner ring (1), wherein the first inner ring (1), the first outer ring (2), and the first auxiliary outer ring (12) are configured with at least ratchet-like protrusions and/or ratchet-like recesses, and wherein the first pawl (11) and the second pawl (20) are configured with at least a function of engaging with or disengaging from the ratchet-like protrusions and/or ratchet-like recesses, wherein the first pawl (11) comprises at least one pawl, and wherein the first pawl (11) is directly or indirectly connected to the first inner ring (1), Said first pawl (11) rotating together with said first inner ring (1), said first pawl (11) being rotatable within an angular range relative to said first inner ring (1), and/or said first pawl (11) being directly or indirectly connected to said first left clutch support (5), said first pawl (11) rotating together with said first left clutch support (5), said first pawl (11) being rotatable within an angular range relative to said first left clutch support (5), and/or said first pawl (11) being directly or indirectly connected to said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, the second pawl (20) is directly or indirectly connected to the first inner ring (1), the second pawl (20) rotates together with the first inner ring (1), the second pawl (20) can rotate relative to the first outer ring (2) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and the second return spring (21) is directly or indirectly connected with the second pawl (20), -the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other restraining or loads on the second pawl (20) is less than the action of the spring force of the second return spring (21), the first outer ring (2) being fixed unidirectionally in relation to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is in engagement with the first outer ring (2), and/or the first auxiliary outer ring (12) being fixed unidirectionally in relation to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is in engagement with the first auxiliary outer ring (12), and/or the first outer ring (2) being fixed unidirectionally in relation to the first inner ring (1) in the reverse or reverse direction when the second pawl (20) is in engagement with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first inner ring (1) in the reverse or forward direction when the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed in both the forward and reverse directions relative to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in both the forward and reverse directions relative to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the second pawls (20) are disengaged from the first outer ring (2) when the first pawls (11) are engaged with the first outer ring (2), -the first outer ring (2) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first inner ring (1) within a certain load range, and/or-the first auxiliary outer ring (12) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first inner ring (1) within a certain load range when the first pawl (11) is engaged with the first auxiliary outer ring (12) and the second pawl (20) is disengaged from the first auxiliary outer ring (12), and/or-the first outer ring (2) is fixed in a reverse or forward direction and rotatable in a forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawl (11) is disengaged from the first outer ring (2) and the second pawl (20) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawls (11) are disengaged from the first auxiliary outer ring (12) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is rotatable in both the forward and reverse directions with respect to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are disengaged from the first outer ring (2), and/or the first auxiliary outer ring (12) is rotatable in both the forward and reverse directions with respect to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are disengaged from the first auxiliary outer ring (12), the contact pair of the first pawl (11) and the first outer ring (2) has an overload protection function when the first pawl (11) and the first outer ring (2) are in an engaged state, the first pawl (11) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the first pawl (11) and the first outer ring (2), and/or the contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function when the first pawl (11) and the first outer ring (2) are in the engaged state, the contact pair of the first pawl (11) and the first outer ring (2) are not automatically disengaged when the large force is applied between the first pawl (11) and the first outer ring (2), and/or the contact pair of the first pawl (11) and the first outer ring (2) are not automatically disengaged when the first pawl (11) and the first auxiliary outer ring (12) are in the engaged state, The contact pair of the first pawl (11) and the first auxiliary outer ring (12) has an overload protection function, the first pawl (11) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has a self-locking function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is in an engaged state, the contact pair of the first pawl (11) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is large, and/or the contact pair of the second pawl (20) and the first outer ring (2) is in an engaged state, The contact pair of the second pawl (20) and the first outer ring (2) has an overload protection function, the second pawl (20) and the first outer ring (2) are automatically disengaged when the acting force between the second pawl (20) and the first outer ring (2) is excessive, and/or the contact pair of the second pawl (20) and the first outer ring (2) has a self-locking function when the acting force between the second pawl (20) and the first outer ring (2) is in an engaged state, the contact pair of the second pawl (20) and the first outer ring (2) is not automatically disengaged when the acting force between the second pawl (20) and the first outer ring (2) is large, and/or the contact pair of the second pawl (20) and the first auxiliary outer ring (12) has an overload protection function when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is in an engaged state, When the acting force between the second pawls (20) and the first auxiliary outer ring (12) is excessive, the second pawls (20) are automatically disengaged from the first auxiliary outer ring (12), and/or when the second pawls (20) and the first auxiliary outer ring (12) are in an engaged state, a contact pair of the second pawls (20) and the first auxiliary outer ring (12) has a self-locking function, when the acting force between the second pawls (20) and the first auxiliary outer ring (12) is large, the contact pair of the second pawls (20) and the first auxiliary outer ring (12) is not automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first clutch rivet (7) comprises at least one rivet, and/or the first left clutch support (5) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and/or the first inner ring (1) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved relative to the first inner ring (1) in the axial direction against the effect of the first inner ring (1), and/or the first inner ring (1) is at least provided with a series of axial positioning grooves or projections, The first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first inner ring (1) via the series of axial positioning grooves or projections within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first left clutch carrier (5) against the action of the first left clutch carrier (5), and/or the first left clutch carrier (5) is at least designed with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first inner ring (1) via the series of axial positioning grooves or projections within a certain range -a function of axial positioning of the left clutch carrier (5), and/or-a function of axial positioning of the first shift sleeve (18) directly or indirectly connected to the first right clutch carrier (6) and rotating with the first right clutch carrier (6), and/or-a function of axial positioning of the first shift sleeve (18) with respect to the first right clutch carrier (6) in an axial direction, a certain limiting effect of the first shift sleeve (18) against the effect of the first right clutch carrier (6), a selective movement of the first shift sleeve (18) in an axial direction with respect to the first right clutch carrier (6) against the effect of the first right clutch carrier (6), and/or-a function of axial positioning of the first shift sleeve (18) with respect to the first right clutch carrier (6) at least over a certain range by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected to the first inner ring (1), the first positioning means (19) rotates together with the first inner ring (1), the first positioning means (19) is axially fixed relative to the first inner ring (1), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch support (5), the first positioning means (19) rotates together with the first left clutch support (5), the first positioning means (19) is axially fixed relative to the first left clutch support (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch support (6), the first positioning means (19) rotates together with the first right clutch support (6), the first positioning means (19) is axially fixed relative to the first right clutch support (6), and/or the first positioning means (19) is directly or indirectly connected to the first shifting sleeve (18) and the first positioning means (19) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction relative to the first inner ring (1) against the effect of the first positioning means (19), and/or the first shifting sleeve (18) is provided with a series of axial positioning grooves or projections, the first shifting sleeve (18) is at least configured to position at least one axial position thereof by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shifting sleeve (18) is directly or indirectly connected to the first pawl (11), And the selective axial movement of the first shift sleeve (18) relative to the first inner ring (1) within a certain range brings at least the first pawl (11) into or out of engagement with the first outer ring (2) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected with the first pawl (11), and the selective axial movement of the first shift sleeve (18) relative to the first inner ring (1) within a certain range brings at least the first pawl (11) into or out of engagement with the first auxiliary outer ring (12) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected with the second pawl (20), and the selective axial movement of the first shift sleeve (18) relative to the first inner ring (1) within a certain range brings at least the second pawl (20) into engagement with the first outer ring (2) directly or indirectly Or a disengaged state, and/or the first shift sleeve (18) is directly or indirectly connected with the second pawl (20) and the first shift sleeve (18) is selectively axially moved in relation to the first inner ring (1) within a certain range at least directly or indirectly bringing the second pawl (20) into engagement or disengagement with the first auxiliary outer ring (12), and/or the first lever mechanism (27) comprises at least one lever, and/or the first lever mechanism (27) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and/or the first lever mechanism (27) is directly or indirectly connected with the first left clutch bracket (5) and rotates together with the first left clutch bracket (5), and/or the first lever mechanism (27) is directly or indirectly connected with the first right clutch bracket (6) and rotates together with the first right clutch bracket (5) The clutch carrier (6) rotates together, and/or the first shift sleeve (18) is connected to the first pawl (11) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced relative to the first inner ring (1) within a certain range, the first pawl (11) and the first outer ring (2) are brought into an engaged or disengaged state by means of the first lever mechanism (27), and/or the first shift sleeve (18) is connected to the first pawl (11) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced relative to the first inner ring (1) within a certain range, the first pawl (11) and the first auxiliary outer ring (12) are brought into an engaged or disengaged state by means of the first lever mechanism (27), and/or the first shift sleeve (18) is connected to the second pawl (20) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced within a certain range relative to the first inner ring (1) by means of the first lever mechanism (27) bringing the second pawl (20) into engagement or disengagement with the first outer ring (2), and/or the first shift sleeve (18) is connected to the second pawl (20) by means of the first lever mechanism (27) and the first shift sleeve (18) is selectively axially displaced within a certain range relative to the first inner ring (1) by means of the first lever mechanism (27) bringing the second pawl (20) into engagement or disengagement with the first auxiliary outer ring (12), and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM), And the first shift sleeve (18) is driven by the actuating device (AM) to move selectively in the axial direction within a certain range relative to the first inner ring (1), and/or the first pawl (11) is in an engaged or disengaged state with the first outer ring (2), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2) when the first shift sleeve (18) is at a certain intermediate position in the axial direction relative to the first inner ring (1) directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first outer ring (2), when the first shift sleeve (18) is at a certain position axially to the left away from the first inner ring (1) directly or indirectly under the action of the actuating device (AM), The second pawl (20) is in engagement or disengagement with the first outer ring (2) and/or the first pawl (11) is in engagement or disengagement with the first outer ring (2), the second pawl (20) is in engagement or disengagement with the first outer ring (2) and/or when the first shift sleeve (18) is in a position axially on one side away from the first inner ring (1) directly or indirectly under the action of the Actuating Means (AM), and/or

The first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range limited by the first limit pin (13), and/or the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), and/or when the first outer ring (2) rotates reversely or positively relative to the first inner ring (1), under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced into a cylindrical surface, and the first pawl (11) contacts the spliced cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced, and/or when the first outer ring (2) rotates reversely or positively relative to the first inner ring (1), noise is greatly reduced, Under the direct or indirect action of the second pawls (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, and the second pawls (20) contact with the spliced cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), and/or a first drive pin (26), and/or a first drive cam (28), wherein the first outer ring (2) is arranged on one side of the first inner ring (1) in the radial direction, and the first outer ring (2), and/or the first left clutch support (5), And/or the first right clutch support (6), and/or the first auxiliary inner ring (14), the first shift sleeve (18), and/or the first positioning mechanism (19), the first shift cam (25), and/or the first drive cam (28) are arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch support (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), the first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), And/or the second return spring (21), the first shift cam (25), and/or the first drive pin (26), and/or the first drive cam (28) are/is arranged axially on one side of the first right clutch carrier (6), the first inner ring (1) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected to a machine frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with the driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first left clutch bracket (5) is directly or indirectly connected with the driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first left clutch bracket (5) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM) DM) and/or the first left clutch support (5) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first left clutch support (5) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right clutch support (6) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first right clutch support (6) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first right clutch support (6) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first right clutch support (6) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first shifting sleeve (18) is directly or indirectly connected with a driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first shifting sleeve (18) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first shifting sleeve (18) is directly or indirectly connected with a driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first shifting sleeve (18) is directly or indirectly fixedly connected with the frame of the machine (M), and the first pawl (11) is in an engaged state with the first inner ring (1) in an initial position, At the moment, the first inner ring (1) is fixed in a unidirectional way relative to the first outer ring (2) in the forward or reverse rotation direction, and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at an initial position, at the moment, the first auxiliary inner ring (14) is fixed in a unidirectional way relative to the first outer ring (2) in the forward or reverse rotation direction, and/or the second pawl (20) is in an engagement state with the first inner ring (1) at an initial position, at the moment, the first inner ring (1) is fixed in a unidirectional way relative to the first outer ring (2) in the reverse or forward rotation direction, and/or the second pawl (20) is in an engagement state with the first auxiliary inner ring (14) at an initial position, at the moment, the first auxiliary inner ring (14) is fixed in a unidirectional way relative to the first outer ring (2) in the reverse or forward rotation direction, and/or the first pawl (11) is in a disengaged state from the first inner ring (1) in an initial position, in which the first inner ring (1) is rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or the first pawl (11) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or the second pawl (20) is in a disengaged state from the first inner ring (1) in an initial position, in which the first inner ring (1) is rotatable in the forward or reverse direction with respect to the first outer ring (2), and/or the second pawl (20) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable in the forward or reverse direction with respect to the first outer ring (2) -rotating, the first inner ring (1) and the first outer ring (2) and the first auxiliary inner ring (14) and the first shift cam (25) are configured with at least ratchet-like protrusions and/or ratchet-like recesses, and the first pawls (11) and the second pawls (20) are configured with at least a function of engaging with or disengaging from the ratchet-like protrusions and/or ratchet-like recesses, the first pawls (11) comprise at least one pawl, the first pawls (11) are directly or indirectly connected with the first outer ring (2), the first pawls (11) rotate with the first outer ring (2), the first pawls (11) are rotatable within an angular range with respect to the first outer ring (2), and/or the first pawls (11) are directly or indirectly connected with the first left clutch bracket (5), Said first pawl (11) rotating together with said first left clutch support (5), said first pawl (11) being rotatable within an angular range relative to said first left clutch support (5), and/or said first pawl (11) being directly or indirectly connected with said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected with said first outer race (2), said second pawl (20) rotating together with said first outer race (2), said second pawl (20) being rotatable within an angular range relative to said first outer race (2), and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the other constraint or load acts on the first pawl (11) less than the elastic force of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the other constraint or load acts on the second pawl (20) less than the elastic force of the second return spring (21) on the second pawl (20), The second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), the first inner ring (1) is fixed in a unidirectional manner relative to the first outer ring (2) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in a unidirectional manner relative to the first outer ring (2) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in a unidirectional manner relative to the first outer ring (2) in the reverse or forward rotation direction when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in a unidirectional manner relative to the first outer ring (2) in the reverse or forward rotation direction when the second pawl (20) is engaged with the first auxiliary inner ring (14) And/or the first inner ring (1) is fixed in both forward and reverse directions relative to the first outer ring (2) within a load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both forward and reverse directions relative to the first outer ring (2) within a load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in both forward and reverse directions and rotatable in reverse or forward directions relative to the first outer ring (2) within a load range when the first pawl (11) is engaged with the first inner ring (1) and the second pawl (20) is disengaged from the first inner ring (1), and/or when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), within a certain load range, the first auxiliary inner ring (14) is fixed in the forward or reverse direction and rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), within a certain load range, the first inner ring (1) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first outer ring (2), and/or when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), The first auxiliary inner ring (14) is fixed in the reverse rotation direction or the forward rotation direction relative to the first outer ring (2) and can rotate in the forward rotation direction or the reverse rotation direction within a certain load range, and/or the first inner ring (1) can rotate in the forward rotation direction and the reverse rotation direction relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first inner ring (1), and/or the first auxiliary inner ring (14) can rotate in the forward rotation direction and the reverse rotation direction relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first auxiliary inner ring (14), and the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function when the first pawl (11) and the first inner ring (1) are in an engaged state, The first pawl (11) is automatically disengaged from the first inner ring (1) when the acting force between the first pawl (11) and the first inner ring (1) is excessive, and/or the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) does not automatically disengage when the acting force between the first pawl (11) and the first inner ring (1) is large, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and the first pawl (11) and the first auxiliary inner ring (14) have an overload protection function when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, The first pawl (11) is automatically disengaged from the first auxiliary inner ring (14), and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has a self-locking function when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the contact pair of the second pawl (20) and the first inner ring (1) has an overload protection function when the second pawl (20) and the first inner ring (1) are in an engaged state, and the second pawl (20) and the first inner ring (1) are automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is excessive, and/or the contact pair of the second pawl (20) and the first inner ring (1) has a self-locking function when the second pawl (20) and the first inner ring (1) are in an engaged state, the contact pair of the second pawl (20) and the first inner ring (1) cannot be automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is large, and/or the contact pair of the second pawl (20) and the first auxiliary inner ring (14) has an overload protection function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, the second pawl (20) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is excessive, and/or the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary inner ring (14) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is large, the second pawl (20) and the contact pair of the first auxiliary inner ring (14) can not be automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or at least one series of axial positioning grooves or projections are formed on the first left clutch carrier (5), the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first left clutch carrier (5) within a certain range by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and to the third clutch carrier (6) A right clutch support (6) rotating together, and/or the first right clutch support (6) having a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) being selectively movable in the axial direction against the effect of the first right clutch support (6) relative to the first right clutch support (6), and/or the first right clutch support (6) being at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) being at least configured to perform the function of axial positioning relative to the first right clutch support (6) through the series of axial positioning grooves or projections in a certain range, and/or the first positioning means (19) being directly or indirectly connected with the first left clutch support (5), the first positioning means (19) rotating together with the first left clutch support (5), and/or the first positioning means (19) being configured to rotate together with the first left clutch support (5), The first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) axially limits the first shift sleeve (18), the first shift sleeve (18) is axially selectively movable relative to the first left half clutch (15) against the action of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first shift sleeve (18), The first shifting sleeve (18) is at least configured to be constrained within a certain range by the series of axial positioning grooves or protrusions and the first positioning mechanism (19) to position at least one axial position thereof, and/or the first shifting sleeve (18) is directly or indirectly connected with the first pawl (11) and a selected axial movement of the first shifting sleeve (18) relative to the first outer ring (2) within a certain range at least directly or indirectly brings the first pawl (11) into engagement or disengagement with the first inner ring (1), and/or the first shifting sleeve (18) is directly or indirectly connected with the first pawl (11) and a selected axial movement of the first shifting sleeve (18) relative to the first outer ring (2) within a certain range at least directly or indirectly brings the first pawl (11) into engagement or disengagement with the first auxiliary inner ring (14) And/or said first shifting sleeve (18) is directly or indirectly connected to said second pawl (20) and said first shifting sleeve (18) is selectively axially displaced within a range relative to said first outer ring (2) at least directly or indirectly bringing said second pawl (20) into engagement or disengagement with said first inner ring (1), and/or said first shifting sleeve (18) is directly or indirectly connected to said second pawl (20) and said first shifting sleeve (18) is selectively axially displaced within a range relative to said first outer ring (2) at least directly or indirectly bringing said second pawl (20) into engagement or disengagement with said first auxiliary inner ring (14), and/or said first shifting sleeve (18) is directly or indirectly connected to said first drive cam (28), And the first shifting sleeve (18) is at least configured to push the first transmission cam (28) to rotate relative to the first outer ring (2) within a certain angle range in a certain axial range, and/or the first transmission pin (26) is directly or indirectly connected with the first shifting sleeve (18), and the first transmission pin (26) rotates together with the first shifting sleeve (18), and/or the first transmission pin (26) is directly or indirectly connected with the first transmission cam (28), the first transmission pin (26) is at least configured to rotate the first transmission cam (28) relative to the first outer ring (2) within a certain axial range, and/or the first transmission pin (26) is connected with the first transmission cam (28) through a screw transmission pair, The first drive pin (26) is axially moved within a certain range at least such that the first drive cam (28) rotates within a certain angular range relative to the first outer ring (2) and/or the first drive cam (28) is directly or indirectly connected to the first outer ring (2), the first drive cam (28) rotates together with the first outer ring (2), the first drive cam (28) rotates within a certain angular range relative to the first outer ring (2), and/or the first drive cam (28) is directly or indirectly connected to the first left clutch support (5), the first drive cam (28) rotates together with the first left clutch support (5), the first drive cam (28) rotates within an angular range relative to the first left clutch support (5), and/or the first drive cam (28) directly or indirectly rotates with the first right clutch support (6) A connection, the first transmission cam (28) rotating together with the first right clutch carrier (6), the first transmission cam (28) rotating over an angular range relative to the first right clutch carrier (6), and/or the first transmission cam (28) being directly or indirectly connected with the first shift cam (25) and the first transmission cam (28) rotating together with the first shift cam (25) over an angular range relative to the first outer ring (2), and/or the first transmission cam (28) being directly or indirectly connected with the first pawl (11) and the rotation of the first transmission cam (28) relative to the first shift sleeve (18) directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first inner ring (1), and/or the first transmission cam (28) being directly or indirectly connected with the first pawl (11), And rotation of the first drive cam (28) relative to the first shift sleeve (18) directly or indirectly brings the first pawl (11) into or out of engagement with the first auxiliary inner ring (14) and/or rotation of the first drive cam (28) relative to the first shift sleeve (18) directly or indirectly brings the second pawl (20) into or out of engagement with the first inner ring (1) and/or rotation of the first drive cam (28) relative to the first shift sleeve (18) directly or indirectly brings the second pawl (20) into or out of engagement with the first auxiliary inner ring (14), and/or the first shift cam (25) is directly or indirectly connected to the first outer ring (2), the first shift cam (25) rotates with the first outer ring (2), the first shift cam (25) rotates relative to the first outer ring (2) within a certain angular range, and/or the first shift cam (25) is directly or indirectly connected to the first left clutch support (5), the first shift cam (25) rotates with the first left clutch support (5), the first shift cam (25) rotates relative to the first left clutch support (5) within a certain angular range, and/or the first shift cam (25) is directly or indirectly connected to the first right clutch support (6), the first shift cam (25) rotates with the first right clutch support (6), The first shifting cam (25) rotates in a certain angle range relative to the first right clutch support (6), and/or the first shifting cam (25) is directly or indirectly connected with the first pawl (11) and the rotation of the first shifting cam (25) relative to the first shifting sleeve (18) directly or indirectly enables the first pawl (11) to be in an engagement or disengagement state with the first inner ring (1), and/or the first shifting cam (25) is directly or indirectly connected with the first pawl (11) and the rotation of the first shifting cam (25) relative to the first shifting sleeve (18) directly or indirectly enables the first pawl (11) to be in an engagement or disengagement state with the first auxiliary inner ring (14), and/or the first shifting cam (25) is directly or indirectly connected with the second pawl (20), And the rotation of the first shift cam (25) relative to the first shift sleeve (18) directly or indirectly causes the second pawl (20) to be in an engaged or disengaged state with the first inner race (1), and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20), and the rotation of the first shift cam (25) relative to the first shift sleeve (18) directly or indirectly causes the second pawl (20) to be in an engaged or disengaged state with the first auxiliary inner race (14), and/or the first shift sleeve (18) is connected with the first pawl (11) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and the axial movement of the first shift sleeve (18) is sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), The first transmission cam (28) and the first shifting cam (25) enable the first pawl (11) and the first inner ring (1) to be in an engaged or disengaged state, and/or the first shifting sleeve (18) is connected with the first pawl (11) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shifting cam (25), and axial movement of the first shifting sleeve (18) enables the first pawl (11) and the first auxiliary inner ring (14) to be in an engaged or disengaged state sequentially through the first transmission pin (26), the first transmission cam (28) and the first shifting cam (25), and/or the first shifting sleeve (18) is connected with the second pawl (20) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shifting cam (25), And the axial movement of the first shift sleeve (18) causes the second pawl (20) to be in an engaged or disengaged state with the first inner race (1) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and/or the first shift sleeve (18) is connected to the second pawl (20) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and the axial movement of the first shift sleeve (18) causes the second pawl (20) to be in an engaged or disengaged state with the first auxiliary inner race (14) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM), And the first shifting sleeve gear (18) is driven by the actuating device (AM) to move axially relative to the first left clutch support (5) or the first right clutch support (6) within a certain range, and/or when the first shifting sleeve gear (18) is in a certain intermediate position relative to the first left clutch support (5) or the first right clutch support (6) in the axial direction directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), and/or when the first shifting sleeve gear (18) is in a certain position away from the first left clutch support (5) or the first right clutch support (6) in the axial direction directly or indirectly under the action of the actuating device (AM), The first pawl (11) is in a connected or disconnected state with the first inner ring (1), the second pawl (20) is in a connected or disconnected state with the first inner ring (1), and/or when the first shift sleeve (18) is in a position axially far from the first left clutch support (5) or the first right clutch support (6) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in a connected or disconnected state with the first inner ring (1), the second pawl (20) is in a connected or disconnected state with the first inner ring (1), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), And the first auxiliary inner ring (14) has at least the function of rotating a certain angle relative to the first inner ring (1) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and the first auxiliary inner ring (14) has at least the function of rotating relative to the first inner ring (1) within the angle range defined by the first limit pin (13) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1), and/or the first auxiliary inner ring (14) directly or indirectly rotates under the action of the first pawl (11) when the first inner ring (1) rotates reversely or forwardly relative to the first outer ring (2), After the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), a part of the surface of the first auxiliary inner ring (14) is spliced with a part of the surface of the first inner ring (1) to form a cylindrical surface, and the first pawl (11) rotates relative to the first inner ring (1) to contact with the spliced cylindrical surface, so that noise is greatly reduced, and/or when the first inner ring (1) rotates forwards or backwards relative to the first outer ring (2), the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1) under the direct or indirect action of the second pawl (20), or the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1) A part of the surface of the first auxiliary inner ring (14) and a part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the second pawl (20) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary outer ring (12), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), and/or a first drive pin (26), and/or a first drive cam (28), wherein the first outer ring (2) is arranged on one side of the first inner ring (1) in the radial direction, and the first outer ring (2), and/or the first left clutch support (5), And/or the first right clutch support (6), and/or the first auxiliary outer ring (12), the first shift gear sleeve (18), and/or the first positioning mechanism (19), the first shift cam (25), and/or the first drive cam (28) are arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch support (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary outer ring (12), the first shift gear sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), And/or the second return spring (21), the first shift cam (25), and/or the first drive pin (26), and/or the first drive cam (28) are/is arranged axially on one side of the first right clutch carrier (6), the first inner ring (1) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected to a machine frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engagement state with the first outer ring (2) at an initial position, when the first outer ring (2) is unidirectionally fixed in a forward or reverse direction relative to the first inner ring (1), and/or the first pawl (11) is in a contact state with the first auxiliary outer ring (12) at an initial position A closed state, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first inner ring (1) in a forward or reverse direction, and/or the second pawl (20) is in an engaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is fixed in a unidirectional manner relative to the first inner ring (1) in a reverse or forward direction, and/or the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first inner ring (1) in a reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is rotatable in a forward or reverse direction relative to the first inner ring (1), and/or the first pawl (11) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, in which the first auxiliary outer ring (12) is rotatable relative to the first inner ring (1) in a reverse or forward direction, and/or the second pawl (20) is in a disengaged state from the first outer ring (2) in an initial position, in which the first outer ring (2) is rotatable relative to the first inner ring (1) in a forward or reverse direction, and/or the second pawl (20) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, in which the first auxiliary outer ring (12) is rotatable relative to the first inner ring (1) in a forward or reverse direction, the first inner ring (1) and the first outer ring (2) and the first auxiliary outer ring (12) and the first shift cam (25) being configured with at least ratchet-like projections and/or ratchet-like recesses, And the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-like protrusion and/or ratchet-like recess, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first inner ring (1), the first pawl (11) rotates with the first inner ring (1), the first pawl (11) is rotatable within an angular range relative to the first inner ring (1), and/or the first pawl (11) is directly or indirectly connected with the first left clutch support (5), the first pawl (11) rotates with the first left clutch support (5), the first pawl (11) is rotatable within an angular range relative to the first left clutch support (5), and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), The first pawl (11) rotates together with the first right clutch support (6), the first pawl (11) is rotatable within an angular range relative to the first right clutch support (6), the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected with the first inner ring (1), the second pawl (20) rotates together with the first inner ring (1), the second pawl (20) is rotatable within an angular range relative to the first outer ring (2), and/or the second pawl (20) is directly or indirectly connected with the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) is rotatable within an angular range relative to the first left clutch support (5), and/or the second pawl (20) is directly or indirectly connected with the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), the first return spring (4) is directly or indirectly connected with the first pawl (11), and the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the action of the elastic force of the second return spring (21), when the first pawl (11) is jointed with the first outer ring (2), the first outer ring (2) is fixed relative to the first inner ring (1) in a forward rotation direction or a reverse rotation direction in a one-way mode, and/or when the first pawl (11) is jointed with the first auxiliary ring (12), The first auxiliary outer ring (12) is fixed unidirectionally relative to the first inner ring (1) in a forward or reverse direction, and/or the first outer ring (2) is fixed unidirectionally relative to the first inner ring (1) in a reverse or forward direction when the second pawl (20) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first inner ring (1) in a reverse or forward direction when the second pawl (20) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed both in a forward and reverse direction relative to the first inner ring (1) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first outer ring (2), and/or the first pawl (11) and the second pawl (20) are engaged with the first auxiliary outer ring (12) -the first auxiliary outer ring (12) is fixed in both forward and reverse rotation directions relative to the first inner ring (1) within a certain load range, and/or-the first outer ring (2) is fixed in forward or reverse rotation direction and rotatable in reverse or forward rotation direction relative to the first inner ring (1) within a certain load range when the first pawl (11) is engaged with the first outer ring (2) and the second pawl (20) is disengaged from the first outer ring (2), and/or-the first auxiliary outer ring (12) is fixed in forward or reverse rotation direction and rotatable in reverse rotation or reverse rotation direction relative to the first inner ring (1) within a certain load range when the first pawl (11) is engaged with the first auxiliary outer ring (12) and the second pawl (20) is disengaged from the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawls (11) are disengaged from the first outer ring (2) and the second pawls (20) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawls (11) are disengaged from the first auxiliary outer ring (12) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first pawls (11) and the second pawls (20) are disengaged from the first inner ring (1), within a certain load range, The first outer ring (2) is rotatable in both forward and reverse rotation directions relative to the first inner ring (1), and/or the first auxiliary outer ring (12) is rotatable in both forward and reverse rotation directions relative to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are separated from the first auxiliary outer ring (12), a contact pair of the first pawls (11) and the first outer ring (2) has an overload protection function when the first pawls (11) and the first outer ring (2) are in an engaged state, the first pawls (11) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the first pawls (11) and the first outer ring (2), and/or the first pawls (11) and the first outer ring (2) are in an engaged state, The contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function, the contact pair of the first pawl (11) and the first outer ring (2) cannot be automatically disengaged when the acting force between the first pawl (11) and the first outer ring (2) is larger, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is larger, the contact pair of the first pawl (11) and the first auxiliary outer ring (12) is automatically disengaged when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is larger, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has a self-locking function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is larger, When the acting force between the first pawl (11) and the first auxiliary outer ring (12) is larger, the first pawl (11) and the first auxiliary outer ring (12) contact pair can not automatically disengage, and/or when the second pawl (20) and the first outer ring (2) are in an engaged state, the second pawl (20) and the first outer ring (2) contact pair has the function of overload protection, when the acting force between the second pawl (20) and the first outer ring (2) is too large, the second pawl (20) and the first outer ring (2) automatically disengage, and/or when the second pawl (20) and the first outer ring (2) are in an engaged state, the second pawl (20) and the first outer ring (2) contact pair has the function of self-locking, when the acting force between the second pawl (20) and the first outer ring (2) is larger, the second pawl (20) and the first outer ring (2) automatically disengage, The second pawl (20) and the first outer ring (2) contact pair are not automatically disengaged, and/or the second pawl (20) and the first outer ring (12) contact pair has an overload protection function when the second pawl (20) and the first outer ring (12) are in an engaged state, the second pawl (20) and the first outer ring (12) contact pair automatically disengage when an excessive force is applied between the second pawl (20) and the first outer ring (12), and/or the second pawl (20) and the first outer ring (12) contact pair has a self-locking function when the second pawl (20) and the first outer ring (12) are in an engaged state, the second pawl (20) and the first outer ring (12) contact pair has a self-locking function when the excessive force is applied between the second pawl (20) and the first outer ring (12), The second pawl (20) and the first auxiliary outer ring (12) are not automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first shifting tooth sleeve (18) is directly or indirectly connected with the first left clutch support (5) and rotates together with the first left clutch support (5), and/or the first left clutch carrier (5) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively axially displaceable relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or at least one series of axial positioning grooves or projections are formed on the first left clutch carrier (5), the first shift sleeve (18) is at least functionally axially positioned relative to the first left clutch carrier (5) within a certain range by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and rotates together with the first right clutch carrier (6), and/or the first right clutch carrier (6) has a limiting effect on the first shift sleeve (18) in the axial direction The first shifting tooth sleeve (18) is selectively moved in the axial direction relative to the first right clutch support (6) against the action of the first right clutch support (6), and/or at least a series of axial positioning grooves or projections are formed on the first right clutch support (6), the first shifting tooth sleeve (18) is at least configured to perform the function of axial positioning relative to the first right clutch support (6) in a certain range through the series of axial positioning grooves or projections, and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch support (5), the first positioning mechanism (19) rotates together with the first left clutch support (5), the first positioning mechanism (19) is fixed in the axial direction relative to the first left clutch support (5), and/or the first positioning mechanism (19) is directly or indirectly connected with the first right clutch support (6), The first positioning means (19) rotating together with the first right clutch carrier (6), the first positioning means (19) being axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) being directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) having a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) being selectively movable in the axial direction relative to the first left clutch half (15) against the effect of the first positioning means (19), and/or the first shift sleeve (18) being provided with a series of axial positioning grooves or projections, the first shift sleeve (18) being configured at least in such a way that at least one of its axial positions is positioned by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11) and a selected axial movement of the first shift sleeve (18) relative to the first inner ring (1) within a certain range brings at least the first pawl (11) into or out of engagement with the first outer ring (2) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11) and a selected axial movement of the first shift sleeve (18) relative to the first inner ring (1) within a certain range brings at least the first pawl (11) into or out of engagement with the first auxiliary outer ring (12) directly or indirectly, and/or the first shift sleeve (18) is directly or indirectly connected to the second pawl (20) and the first shift sleeve (18) is selectively brought axially relative to the first inner ring (1) within a certain range At least the second pawl (20) is directly or indirectly engaged or disengaged with the first outer ring (2) by the movement, and/or the first shift sleeve (18) is directly or indirectly connected with the second pawl (20) and the first shift sleeve (18) is selectively axially moved relative to the first inner ring (1) within a certain range, at least the second pawl (20) is directly or indirectly engaged or disengaged with the first auxiliary outer ring (12), and/or the first shift sleeve (18) is directly or indirectly connected with the first drive cam (28) and the first shift sleeve (18) is at least configured to push the first drive cam (28) to rotate relative to the first inner ring (1) within a certain angular range within a certain axial range, and/or the first drive pin (26) is directly or indirectly connected with the first shift sleeve (18), And the first drive pin (26) rotates together with the first shift sleeve (18), and/or the first drive pin (26) is directly or indirectly connected to the first drive cam (28), the first drive pin (26) is at least configured to push the first drive cam (28) to rotate relative to the first inner ring (1) within a certain angular range, and/or the first drive pin (26) is connected to the first drive cam (28) via a helical gear pair, movement of the first drive pin (26) in an axial direction within a certain range at least causes the first drive cam (28) to rotate relative to the first outer ring (2), and/or the first drive cam (28) is directly or indirectly connected to the first inner ring (1), the first drive cam (28) rotates together with the first inner ring (1), The first transmission cam (28) rotates relative to the first inner ring (1) within a certain angle range, and/or the first transmission cam (28) is directly or indirectly connected with the first left clutch support (5), the first transmission cam (28) rotates together with the first left clutch support (5), the first transmission cam (28) rotates relative to the first left clutch support (5) within a certain angle range, and/or the first transmission cam (28) is directly or indirectly connected with the first right clutch support (6), the first transmission cam (28) rotates together with the first right clutch support (6), the first transmission cam (28) rotates relative to the first right clutch support (6) within a certain angle range, and/or the first transmission cam (28) is directly or indirectly connected with the first gear shifting cam (25), And the first transmission cam (28) and the first shift cam (25) rotate together in a certain angle range relative to the first inner ring (1), and/or the first transmission cam (28) is directly or indirectly connected with the first pawl (11), and the rotation of the first transmission cam (28) relative to the first shift gear sleeve (18) directly or indirectly enables the first pawl (11) and the first outer ring (2) to be in an engaged or disengaged state, and/or the first transmission cam (28) is directly or indirectly connected with the first pawl (11), and the rotation of the first transmission cam (28) relative to the first shift gear sleeve (18) directly or indirectly enables the first pawl (11) and the first auxiliary outer ring (12) to be in an engaged or disengaged state, and/or the first transmission cam (28) is directly or indirectly connected with the second pawl (20), And the rotation of the first gear cam (28) relative to the first gear sleeve (18) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first outer ring (2), and/or the first gear cam (28) is directly or indirectly connected to the second pawl (20), and the rotation of the first gear cam (28) relative to the first gear sleeve (18) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary outer ring (12), and/or the first gear cam (25) is directly or indirectly connected to the first inner ring (1), the first gear cam (25) rotates together with the first inner ring (1), the first gear cam (25) rotates within an angular range relative to the first inner ring (1), and/or the first gear cam (25) directly or indirectly contacts the first left clutch carrier (5) -the connection, -the first shift cam (25) rotates together with the first left clutch carrier (5), -the first shift cam (25) rotates within an angular range with respect to the first left clutch carrier (5), and/or-the first shift cam (25) is directly or indirectly connected with the first right clutch carrier (6), -the first shift cam (25) rotates together with the first right clutch carrier (6), -the first shift cam (25) rotates within an angular range with respect to the first right clutch carrier (6), and/or-the first shift cam (25) is directly or indirectly connected with the first pawl (11), and-the rotation of the first shift cam (25) with respect to the first shift sleeve (18) directly or indirectly brings the first pawl (11) into or out of engagement with the first outer ring (2), and/or the first shift cam (25) is directly or indirectly connected to the first pawl (11) and the rotation of the first shift cam (25) relative to the first shift sleeve (18) directly or indirectly brings the first pawl (11) into or out of engagement with the first auxiliary outer ring (12), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) relative to the first shift sleeve (18) directly or indirectly brings the second pawl (20) into or out of engagement with the first outer ring (2), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) relative to the first shift sleeve (18) directly or indirectly brings the second pawl (20) into or out of engagement with the first auxiliary outer ring (12) Or a disengaged state, and/or the first shift gear sleeve (18) is connected with the first pawl (11) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and the axial movement of the first shift gear sleeve (18) sequentially passes through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25) to enable the first pawl (11) and the first outer ring (2) to be in an engaged or disengaged state, and/or the first shift gear sleeve (18) is connected with the first pawl (11) sequentially passes through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and the axial movement of the first shift gear sleeve (18) sequentially passes through the first transmission pin (26), The first transmission cam (28) and the first shift cam (25) enable the first pawl (11) and the first auxiliary outer ring (12) to be in an engaged or disengaged state, and/or the first shift sleeve (18) is connected with the second pawl (20) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and axial movement of the first shift sleeve (18) enables the second pawl (20) and the first outer ring (2) to be in an engaged or disengaged state sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and/or the first shift sleeve (18) is connected with the second pawl (20) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), And the axial movement of the first shift sleeve (18) causes the second pawl (20) to be in an engaged or disengaged state with the first auxiliary outer ring (12) sequentially through the first transmission pin (26), the first transmission cam (28) and the first shift cam (25), and/or the first shift sleeve (18) is directly or indirectly connected with the actuating device (AM), and the first shift sleeve (18) is selectively moved axially within a certain range relative to the first left clutch bracket (5) or the first right clutch bracket (6) under the drive of the actuating device (AM), and/or when the first shift sleeve (18) is in a certain intermediate position relative to the first left clutch bracket (5) or the first right clutch bracket (6) axially directly or indirectly under the action of the actuating device (AM), The first pawl (11) is in a coupled or decoupled state with the first outer ring (2), the second pawl (20) is in a coupled or decoupled state with the first outer ring (2), and/or the first shift tooth sleeve (18) is in a position axially on one side away from the first left or right clutch carrier (5, 6), directly or indirectly under the action of the actuation device (AM), when the first shift tooth sleeve (18) is in a position axially on one side away from the first left or right clutch carrier (5, 6), directly or indirectly under the action of the actuation device (AM), The first pawl (11) is in a joint or separation state with the first outer ring (2), the second pawl (20) is in a joint or separation state with the first outer ring (2), and/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has a function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), And under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of being capable of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), and/or the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), and/or when the first outer ring (2) rotates reversely or positively relative to the first inner ring (1), under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle defined by the first limit pin (13) relative to the first outer ring (2), a partial surface of the first auxiliary outer ring (12) and a partial surface of the first outer ring (2) are combined into a cylindrical surface, The first pawl (11) is in contact with the split cylindrical surface when rotating relative to the first outer ring (2) so that noise is greatly reduced, and/or when the first outer ring (2) rotates forwards or reversely relative to the first inner ring (1), under the direct or indirect action of the second pawl (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) is combined with part of the surface of the first outer ring (2) to form a cylindrical surface, and the second pawl (20) contacts with the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), wherein the first outer ring (2) is arranged at one side of the first inner ring (1) in the radial direction, and the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), The first shifting cam (25) is arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch bracket (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), the first shifting cam (25) is arranged axially on one side of the first right clutch bracket (6), the first inner ring (1) is directly or indirectly connected with a driving element of the machine (M) and rotates together with the driving element of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, when the first inner ring (1) is unidirectionally fixed in a forward or reverse rotation direction relative to the first outer ring (2), and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at an initial position, The first auxiliary inner ring (14) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first outer ring (2) at the moment, and/or the second pawl (20) is in an engagement state with the first inner ring (1) at an initial position, the first inner ring (1) is fixed in a one-way mode in the reverse or forward rotation direction relative to the first outer ring (2) at the moment, and/or the second pawl (20) is in an engagement state with the first auxiliary inner ring (14) at an initial position, the first auxiliary inner ring (14) is fixed in a one-way mode in the reverse or forward rotation direction relative to the first outer ring (2) at the moment, and/or the first pawl (11) is in a separation state with the first inner ring (1) at an initial position, and the first inner ring (1) can rotate in the reverse or forward rotation direction relative to the first outer ring (2) at the moment, and/or the first pawl (11) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable relative to the first outer ring (2) in a reverse or forward direction, and/or the second pawl (20) is in a disengaged state from the first inner ring (1) in an initial position, in which the first inner ring (1) is rotatable relative to the first outer ring (2) in a forward or reverse direction, and/or the second pawl (20) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable relative to the first outer ring (2) in a forward or reverse direction, the first inner ring (1) and the first outer ring (2) and the first auxiliary inner ring (14) and the first shift cam (25) being configured with at least ratchet-like projections and/or ratchet-like recesses, And the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-like projection and/or ratchet-like recess, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first outer ring (2), the first pawl (11) is rotatable within a certain angular range relative to the first outer ring (2), and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) is rotatable within a certain angular range relative to the first left clutch bracket (5), and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) is rotatable within a certain angular range relative to the first right clutch bracket (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected to said first outer race (2), said second pawl (20) being rotatable relative to said first outer race (2) within an angular range, and/or said second pawl (20) being directly or indirectly connected to said first left clutch bracket (5), said second pawl (20) being rotatable relative to said first left clutch bracket (5) within an angular range, and/or said second pawl (20) being directly or indirectly connected to said first right clutch bracket (6), said second pawl (20) being rotatable relative to said first right clutch bracket (6) within an angular range, said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first outer race (2) and rotatable therewith, the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the other constraint or load acts on the first pawl (11) less than the elastic force of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the other constraint or load acts on the second pawl (20) less than the elastic force of the second return spring (21) on the second pawl (20), The second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), the first inner ring (1) is fixed in a unidirectional manner relative to the first outer ring (2) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in a unidirectional manner relative to the first outer ring (2) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in a unidirectional manner relative to the first outer ring (2) in the reverse or forward rotation direction when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in a unidirectional manner relative to the first outer ring (2) in the reverse or forward rotation direction when the second pawl (20) is engaged with the first auxiliary inner ring (14) And/or the first inner ring (1) is fixed in both forward and reverse directions relative to the first outer ring (2) within a load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both forward and reverse directions relative to the first outer ring (2) within a load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in both forward and reverse directions and rotatable in reverse or forward directions relative to the first outer ring (2) within a load range when the first pawl (11) is engaged with the first inner ring (1) and the second pawl (20) is disengaged from the first inner ring (1), and/or when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), within a certain load range, the first auxiliary inner ring (14) is fixed in the forward or reverse direction and rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), within a certain load range, the first inner ring (1) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first outer ring (2), and/or when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), The first auxiliary inner ring (14) is fixed in the reverse rotation direction or the forward rotation direction relative to the first outer ring (2) and can rotate in the forward rotation direction or the reverse rotation direction within a certain load range, and/or the first inner ring (1) can rotate in the forward rotation direction and the reverse rotation direction relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first inner ring (1), and/or the first auxiliary inner ring (14) can rotate in the forward rotation direction and the reverse rotation direction relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first auxiliary inner ring (14), and the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function when the first pawl (11) and the first inner ring (1) are in an engaged state, The first pawl (11) is automatically disengaged from the first inner ring (1) when the acting force between the first pawl (11) and the first inner ring (1) is excessive, and/or the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function when the first pawl (11) and the first inner ring (1) are in an engaged state, the contact pair of the first pawl (11) and the first inner ring (1) does not automatically disengage when the acting force between the first pawl (11) and the first inner ring (1) is large, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and the first pawl (11) and the first auxiliary inner ring (14) have an overload protection function when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, The first pawl (11) is automatically disengaged from the first auxiliary inner ring (14), and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has a self-locking function when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the contact pair of the second pawl (20) and the first inner ring (1) has an overload protection function when the second pawl (20) and the first inner ring (1) are in an engaged state, and the second pawl (20) and the first inner ring (1) are automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is excessive, and/or the contact pair of the second pawl (20) and the first inner ring (1) has a self-locking function when the second pawl (20) and the first inner ring (1) are in an engaged state, the contact pair of the second pawl (20) and the first inner ring (1) cannot be automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is large, and/or the contact pair of the second pawl (20) and the first auxiliary inner ring (14) has an overload protection function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, the second pawl (20) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is excessive, and/or the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary inner ring (14) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is large, the second pawl (20) and the contact pair of the first auxiliary inner ring (14) can not be automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first outer ring (2) through the first clutch rivet (7), and/or the first shift cam (25) is directly or indirectly connected to the first outer ring (2), the first shift cam (25) rotates relative to the first outer ring (2) within a certain angular range, and/or the first outer ring (2) has a certain angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotates relative to the first outer ring (2) within a certain angular range against the effect of the first outer ring (2), and/or the first outer ring (2) is at least provided with a series of positioning grooves or projections, the first shift cam (25) is at least provided with a function of angular positioning relative to the first outer ring (2) in the direction of rotation via the series of positioning grooves or projections within a certain range, and/or the first shift cam (25) is directly or indirectly connected to the first left clutch support (5) -a connection, the first shift cam (25) rotating within an angular range relative to the first left clutch carrier (5), and/or the first left clutch carrier (5) having an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotating within an angular range relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or the first left clutch carrier (5) being configured with at least one series of detents or projections, the first shift cam (25) being configured at least to perform an angular positioning function within a range relative to the first left clutch carrier (5) via the series of detents or projections, and/or the first shift cam (25) directly or indirectly connecting the first shift cam (25) to the first right clutch carrier (6) The first right clutch support (6) rotates in a certain angle range relative to the first right clutch support (6), and/or the first right clutch support (6) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, the first shift cam (25) selectively rotates in a certain angle range relative to the first right clutch support (6) against the effect of the first right clutch support (6), and/or at least a series of positioning grooves or protrusions are configured on the first right clutch support (6), the first shift cam (25) is at least configured to perform a function of angular positioning in the rotation direction relative to the first right clutch support (6) in a certain range through the series of positioning grooves or protrusions, and/or the first positioning mechanism (19) is directly or indirectly connected with the first outer ring (2), The first positioning means (19) rotates together with the first outer ring (2), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25), and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotates relative to the first outer ring (2) within an angular range against the effect of the first positioning means (19), and/or the first shift cam (25) is provided with a series of detents or projections, the first shift cam (25) being at least configured to function in a rotational direction relative to the first positioning means (19) within a certain range by means of the series of detents or projections, and/or the first shift cam (25) being directly or indirectly connected to the first pawl (11) and a rotation of the first shift cam (25) relative to the first outer ring (2) directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first inner ring (1), and/or the first shift cam (25) being directly or indirectly connected to the first pawl (11) and a rotation of the first shift cam (25) relative to the first outer ring (2) directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first auxiliary inner ring (14), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) with respect to the first outer ring (2) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first inner ring (1) and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) with respect to the first outer ring (2) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary inner ring (14) and/or the first shift cam (25) is directly or indirectly connected to the Actuation Means (AM) and the first shift cam (25) is selectively rotated within a certain angular range with respect to the first outer ring (2) under the drive of the Actuation Means (AM), and/or when the first shift cam (25) is in a certain angular intermediate position in the direction of rotation directly or indirectly under the action of the Actuation Means (AM), the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), and/or when the first shift cam (25) is in a certain side away from the certain angular intermediate position in the direction of rotation directly or indirectly under the action of the Actuation Means (AM) When the other side is arranged, the first pawl (11) is in a joint or separation state with the first inner ring (1), the second pawl (20) is in a joint or separation state with the first inner ring (1), and/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), And under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range defined by the first limit pin (13), and/or the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1), and/or when the first inner ring (1) rotates reversely or positively relative to the first outer ring (2), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle defined by the first limit pin (13) relative to the first inner ring (1), a partial surface of the first auxiliary inner ring (14) and a partial surface of the first inner ring (1) are combined into a cylindrical surface, The first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first inner ring (1) rotates forwards or reversely relative to the first outer ring (2), under the direct or indirect action of the second pawl (20), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) is spliced with part of the surface of the first inner ring (1) to form a cylindrical surface, and the second pawl (20) contacts with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner race (1), a first outer race (2), a first middle race (45), a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first auxiliary outer race (12), and/or a first limit pin (13), and/or a first auxiliary inner race (14), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), and/or a second limit pin (24), a first shift cam (25), a first lever mechanism (27), a third pawl (29), a third return spring (30), and/or a fourth pawl (31), and/or a fourth return spring (32), the first middle ring (45) is located between the first inner ring (1) and the first outer ring (2) in the radial direction, the first outer ring (2) is located on one side of the first middle ring (45) in the radial direction, and/or the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), the first shift cam (25) is arranged coaxially with the first middle ring (45), and the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first left clutch support (5), And/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the second limit pin (24), the first shift cam (25), the first lever mechanism (27), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32) are arranged axially on one side of the first right clutch bracket (6), the first inner ring (1) being directly or indirectly connected with and rotating together with the main part of the machine (M) And/or said first inner ring (1) is directly or indirectly connected to and rotates with said Damping Means (DM), and/or said first inner ring (1) is directly or indirectly connected to and rotates with a driven part of said machine (M), and/or said first outer ring (2) is directly or indirectly connected to and rotates with a driving part of said machine (M), and/or said first outer ring (2) is directly or indirectly connected to and rotates with said Damping Means (DM), and/or said first outer ring (2) is directly or indirectly connected to and rotates with a driven part of said machine (M), and/or said first inner ring (45) is directly or indirectly fixed to and rotates with said Damping Means (DM) -a connection, and/or-the first centre ring (45) is directly or indirectly fixedly connected with the frame of the machine (M), -the first pawl (11) is in engagement with the first inner ring (1) in an initial position, when the first inner ring (1) is fixed unidirectionally in the forward or reverse direction with respect to the first centre ring (45), and/or-the first pawl (11) is in engagement with the first auxiliary inner ring (14) in an initial position, when the first auxiliary inner ring (14) is fixed unidirectionally in the forward or reverse direction with respect to the first centre ring (45), and/or-the second pawl (20) is in engagement with the first inner ring (1) in an initial position, when the first inner ring (1) is fixed unidirectionally in the reverse or forward direction with respect to the first centre ring (45), and/or-the second pawl (20) is in engagement with the first auxiliary inner ring (14) in an initial position A state in which the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in an engaged state with the first outer ring (2) at an initial position, in which the first outer ring (2) is fixed unidirectionally in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in an engaged state with the first auxiliary outer ring (12) at an initial position, in which the first auxiliary outer ring (12) is fixed unidirectionally in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in an engaged state with the first outer ring (2) at an initial position, in which the first outer ring (2) is fixed unidirectionally in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in an engaged state with the first auxiliary outer ring (12) at an initial position, when the first auxiliary outer ring (12) is fixed in a one-way manner in a reverse or forward rotation direction with respect to the first middle ring (45), and/or the first pawl (11) is in a disengaged state with the first inner ring (1) at an initial position, when the first inner ring (1) is rotatable in a reverse or forward rotation direction with respect to the first middle ring (45), and/or the first pawl (11) is in a disengaged state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is rotatable in a reverse or forward rotation direction with respect to the first middle ring (45), and/or the second pawl (20) is in a disengaged state with respect to the first inner ring (1) at an initial position, At this time, the first inner ring (1) can rotate in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the second pawl (20) is in a disengaged state from the first auxiliary inner ring (14) at an initial position, at this time, the first auxiliary inner ring (14) can rotate in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in a disengaged state from the first outer ring (2) at an initial position, at this time, the first outer ring (2) can rotate in the reverse or forward rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in a disengaged state from the first auxiliary outer ring (12) at an initial position, at this time, the first auxiliary outer ring (12) can rotate in the forward or reverse rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in a disengaged state from the first outer ring (2) at an initial position -a state in which the first outer ring (2) is rotatable in a forward or reverse rotation direction with respect to the first middle ring (45), and/or-the fourth pawls (31) are in a disengaged state with respect to the first auxiliary outer ring (12) in an initial position in which the first auxiliary outer ring (12) is rotatable in a forward or reverse rotation direction with respect to the first middle ring (45), -the first inner ring (1) and the first outer ring (2) and the first middle ring (45) and the first auxiliary outer ring (12) and the first auxiliary inner ring (14) and the first shift cam (25) are configured at least with ratchet-like projections and/or ratchet-like recesses, and-the first pawls (11) and the second pawls (20) and the third pawls (29) and the fourth pawls (31) are configured at least with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first middle ring (45), the first pawl (11) can rotate relative to the first middle ring (45) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) can rotate relative to the first left clutch bracket (5) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) can rotate relative to the first right clutch bracket (6) within a certain angle range, the second pawl (20) comprises at least one pawl, and the second pawl (20) is directly or indirectly connected with the first middle ring (45), The second pawl (20) can rotate in a certain angle range relative to the first middle ring (45), and/or the second pawl (20) is directly or indirectly connected with the first left clutch support (5), the second pawl (20) can rotate in a certain angle range relative to the first left clutch support (5), and/or the second pawl (20) is directly or indirectly connected with the first right clutch support (6), the second pawl (20) can rotate in a certain angle range relative to the first right clutch support (6), the third pawl (29) at least comprises one pawl, the first pawl (11) is directly or indirectly connected with the first middle ring (45), the third pawl (29) can rotate in a certain angle range relative to the first middle ring (45), and/or the third pawl (29) is directly or indirectly connected with the first left clutch support (5), The first pawl (11) can rotate within a certain angle range relative to the first left clutch support (5), and/or the third pawl (29) is directly or indirectly connected with the first right clutch support (6), the first pawl (11) can rotate within a certain angle range relative to the first right clutch support (6), the fourth pawl (31) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first middle ring (45), the fourth pawl (31) can rotate within a certain angle range relative to the first middle ring (45), and/or the fourth pawl (31) is directly or indirectly connected with the first left clutch support (5), the first pawl (11) can rotate within a certain angle range relative to the first left clutch support (5), and/or the fourth pawl (31) is directly or indirectly connected with the first right clutch support (6), The first pawl (11) can rotate relative to the first right clutch bracket (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the first return spring (4) is directly or indirectly connected with the first pawl (11), when the effect of other restraint or load on the first pawl (11) is smaller than the elastic effect of the first return spring (4) on the first pawl (11), the first pawl (11) restores the initial position under the elastic effect of the first return spring (4), the second return spring (21) at least comprises one spring, and the second return spring (21) is directly or indirectly connected with the first middle ring (45) and rotates together with the first outer ring (2), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the elastic action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the elastic action of the second return spring (21), the third return spring (30) at least comprises one spring, the third return spring (30) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the third return spring (30) is directly or indirectly connected with the third pawl (29), when the action of other restraint or load on the third pawl (29) is smaller than the elastic action of the third return spring (30) on the third pawl (29), The third pawl (29) is restored to the initial position by the elastic force of the third return spring (30), the fourth return spring (32) comprises at least one spring, the fourth return spring (32) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the fourth return spring (32) is directly or indirectly connected with the fourth pawl (31), the fourth pawl (31) is restored to the initial position by the elastic force of the fourth return spring (32) when the effect of other restraint or load on the fourth pawl (31) is smaller than the elastic force of the fourth return spring (32) on the fourth pawl (31), the first inner ring (1) is fixed in one direction relative to the first middle ring (45) in the forward or reverse direction when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the forward or reverse direction relative to the first middle ring (45) when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the forward and reverse directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first inner ring (1) and the second pawl (20) is disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), and the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in a certain load range Rotatable in a reverse or forward direction, and/or when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), the first inner ring (1) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), the first auxiliary inner ring (14) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) and the second pawl (20) are disengaged from the first inner ring (1), -the first inner ring (1) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range, and/or-the first auxiliary inner ring (14) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary inner ring (14), and/or-the first outer ring (2) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first outer ring (2), and/or-the first auxiliary outer ring (12) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed relative to the first middle ring (45) in both the forward and reverse directions over a range of loads when the third pawls (29) and the fourth pawls (31) are engaged with the first outer ring (2), and/or the third pawls (29) and the fourth pawls (31) are engaged with the first auxiliary outer ring (12) over a range of loads, The first auxiliary outer ring (12) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45), and/or the first outer ring (2) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first outer ring (2) and the fourth pawls (31) are disengaged with respect to the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first auxiliary outer ring (12) and the fourth pawls (31) are disengaged with respect to the first auxiliary outer ring (12), and/or the third pawls (29) are disengaged with respect to the first middle ring (2) and the fourth pawls (31) are disengaged with the outer ring (31) The first outer ring (2) being fixed in the reverse or forward rotation direction and rotatable in the forward or reverse rotation direction with respect to the first middle ring (45) within a certain load range when the first outer ring (2) is engaged, and/or the first auxiliary outer ring (12) being fixed in the reverse or forward rotation direction with respect to the first middle ring (45) and rotatable in the forward or reverse rotation direction within a certain load range when the third pawls (29) are disengaged from the first auxiliary outer ring (12) and the fourth pawls (31) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) being rotatable in both the forward and reverse rotation direction with respect to the first middle ring (45) within a certain load range when the third pawls (29) and the fourth pawls (31) are disengaged from the first outer ring (2), and/or the first auxiliary outer ring (12) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle ring (45) within a certain load range when the third pawls (29) and the fourth pawls (31) are separated from the first auxiliary outer ring (12), the contact pair of the first pawls (11) and the first inner ring (1) has an overload protection function when the first pawls (11) and the first inner ring (1) are in an engaged state, the first pawls (11) and the first inner ring (1) are automatically disengaged when an excessive force is applied between the first pawls (11) and the first inner ring (1), and/or the contact pair of the first pawls (11) and the first inner ring (1) has a self-locking function, a self-locking function, When the acting force between the first pawl (11) and the first inner ring (1) is large, the first pawl (11) and the first inner ring (1) contact pair can not automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, the first pawl (11) and the first auxiliary inner ring (14) automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of self-locking, When the acting force between the first pawl (11) and the first auxiliary inner ring (14) is larger, the first pawl (11) and the first auxiliary inner ring (14) contact pair can not automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of overload protection, when the acting force between the second pawl (20) and the first inner ring (1) is too large, the second pawl (20) and the first inner ring (1) automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of self-locking, when the acting force between the second pawl (20) and the first inner ring (1) is larger, the second pawl (20) and the first inner ring (1) contact pair have the function of self-locking, The second pawl (20) and the first inner ring (1) contact pair can not automatically disengage, and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has an overload protection function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, the second pawl (20) and the first auxiliary inner ring (14) automatically disengage when an excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, and the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), The second pawl (20) is not automatically disengaged from the first auxiliary inner ring (14) contact pair, and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair with an overload protection function when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is automatically disengaged from the first outer ring (2) when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is not automatically disengaged from the first outer ring (2) contact pair when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has an overload protection function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), the third pawls (29) are automatically disengaged from the first auxiliary outer ring (12) when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has a self-locking function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), and the contact pair of the third pawls (29) with the first auxiliary outer ring (12) is not automatically disengaged when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has an overload protection function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the fourth pawl (31) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has a self-locking function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the contact pair of the fourth pawl (31) and the first outer ring (2) are not automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has an overload protection function, the fourth pawl (31) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has a self-locking function when the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is large, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), and/or the first shift cam (25) is connected with the first middle ring (45), the first shift cam (25) rotates relative to the first middle ring (45) within a certain angle range, and/or the first middle ring (45) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, The first shifting cam (25) is selectively rotatable within a certain angular range relative to the first middle ring (45) against the action of the first middle ring (45), and/or at least a series of positioning grooves or projections are formed on the first middle ring (45), the first shifting cam (25) is at least configured to be angularly positioned in a certain range relative to the first middle ring (45) in a rotational direction by means of the series of positioning grooves or projections, and/or the first shifting cam (25) is directly or indirectly connected with the first left clutch support (5), the first shifting cam (25) is rotatable within a certain angular range relative to the first left clutch support (5), and/or the first left clutch support (5) has a certain angular limiting action in a rotational direction on the first shifting cam (25), The first shifting cam (25) is selectively rotated in a certain angle range relative to the first left clutch support (5) against the action of the first left clutch support (5), and/or at least a series of positioning grooves or protrusions are configured on the first left clutch support (5), the first shifting cam (25) is at least configured to perform the function of angular positioning in a certain range relative to the first left clutch support (5) in the rotating direction through the series of positioning grooves or protrusions, and/or the first shifting cam (25) is directly or indirectly connected with the first right clutch support (6), the first shifting cam (25) is rotated in a certain angle range relative to the first right clutch support (6), and/or the first right clutch support (6) has a certain angle limiting effect on the first shifting cam (25) in the rotating direction, The first shift cam (25) is selectively rotatable over a range of angles relative to the first right clutch carrier (6) against the action of the first right clutch carrier (6), and/or at least a series of detents or projections are formed on the first right clutch carrier (6), the first shift cam (25) is at least configured to be angularly positionable in a range of rotational directions relative to the first right clutch carrier (6) via the series of detents or projections, and/or the first positioning means (19) is directly or indirectly connected to the first center ring (45), the first positioning means (19) rotates with the first center ring (45), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates with the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25), and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable relative to the first middle ring (45) over an angular range against the effect of the first positioning means (19), and/or a series of positioning grooves or projections is provided on the first shift cam (25), the first shift cam (25) being configured at least in a range of angular positioning relative to the first positioning means (19) by means of the series of positioning grooves or projections in the direction of rotation -and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11) and the rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the first pawl (11) into engagement or disengagement with the first inner ring (1), and/or the first shift cam (25) is directly or indirectly connected with the first pawl (11) and the rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the first pawl (11) into engagement or disengagement with the first auxiliary inner ring (14), and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20) and the rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first inner ring (1), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and a rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the second pawl (20) into or out of engagement with the first auxiliary inner ring (14), and/or the first shift cam (25) is directly or indirectly connected to the third pawl (29) and a rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the third pawl (29) into or out of engagement with the first outer ring (2), and/or the first shift cam (25) is directly or indirectly connected to the third pawl (29) and a rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the third pawl (29) into or out of engagement with the first auxiliary outer ring (12), and/or the first shift cam (25) is directly or indirectly connected to the fourth pawl (31) and the rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the fourth pawl (31) into engagement or disengagement with the first outer ring (2), and/or the first shift cam (25) is directly or indirectly connected to the fourth pawl (31) and the rotation of the first shift cam (25) relative to the first mid-ring (45) directly or indirectly brings the fourth pawl (31) into engagement or disengagement with the first auxiliary outer ring (12), and/or the first shift cam (25) is directly or indirectly connected to the Actuation Means (AM) and the first shift cam (25) is selectively rotated within a certain angular range relative to the first mid-ring (45) under the drive of the Actuation Means (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2) when the first shift cam (25) is in a certain angular intermediate position in the rotational direction directly or indirectly under the action of the Actuating Means (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1) when the first shift cam (25) is in a certain side away from the certain angular intermediate position in the rotational direction directly or indirectly under the action of the Actuating Means (AM), The second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2) when the first shift cam (25) is on the other side in the rotational direction from the certain angular intermediate position directly or indirectly under the action of the Actuation Means (AM), and/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the second limit pin (24) at least comprises one pin, and/or the second limit pin (24) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), And the first auxiliary inner ring (14) has at least the function of being rotatable relative to the first inner ring (1) within the angular range defined by the first limit pin (13) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary inner ring (14) is arranged axially on one side of the first inner ring (1), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and the first auxiliary outer ring (12) has at least the function of being rotatable relative to the first outer ring (2) at an angle under the action of the third pawl (29) or the fourth pawl (31), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the second limit pin (24), and the function of being rotatable relative to the third pawl (29) or the fourth pawl (31), The first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the second limit pin (24), and/or the first auxiliary outer ring (12) is arranged on one side of the first outer ring (2) in the axial direction, and/or when the first inner ring (1) rotates reversely or forwardly relative to the first middle ring (45), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to the angle defined by the first limit pin (13) relative to the first inner ring (1), a cylindrical surface is formed by the partial surface of the first auxiliary inner ring (14) and the partial surface of the first inner ring (1), The first pawl (11) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first inner ring (1) rotates forwards or reversely relative to the first middle ring (45), under the direct or indirect action of the second pawl (20), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1) or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) and part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the second pawl (20) is contacted with the spliced cylindrical surface when rotating relative to the first inner ring (1) so as to greatly reduce noise, and/or when the first outer ring (2) rotates reversely or forwardly relative to the first middle ring (45), under the direct or indirect action of the third pawl (29), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the second limit pin (24) relative to the first outer ring (2), partial surface of the first auxiliary outer ring (12) is combined with partial surface of the first outer ring (2) to form a cylindrical surface, the third pawl (29) contacts the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced, and/or when the first outer ring (2) rotates forwardly or reversely relative to the first middle ring (45), under the direct or indirect action of the fourth pawl (31), After the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the second limit pin (24) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) and part of the surface of the first outer ring (2) are spliced to form a cylindrical surface, and the fourth pawl (31) contacts the spliced cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary outer ring (12), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), wherein the first outer ring (2) is arranged at one side of the first inner ring (1) in the radial direction, and the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or a first auxiliary outer ring (12), and/or the first positioning mechanism (19), The first shift cam (25) is arranged coaxially with the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch bracket (5), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary outer ring (12), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), the first shift cam (25) is arranged axially on one side of the first right clutch bracket (6), the first inner ring (1) is directly or indirectly connected with the cushion damping Device (DM) and rotates together with the cushion damping Device (DM), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping buffer Device (DM) and rotates along with the damping buffer Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), wherein the first pawl (11) is in an engagement state with the first outer ring (2) at an initial position, when the first outer ring (2) is unidirectionally fixed in a forward or reverse direction relative to the first inner ring (1), and/or the first pawl (11) is in a contact state with the first auxiliary outer ring (12) at the initial position A closed state, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first inner ring (1) in a forward or reverse direction, and/or the second pawl (20) is in an engaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is fixed in a unidirectional manner relative to the first inner ring (1) in a reverse or forward direction, and/or the second pawl (20) is in an engaged state with the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first inner ring (1) in a reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is rotatable in a forward or reverse direction relative to the first inner ring (1), and/or the first pawl (11) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, in which the first auxiliary outer ring (12) is rotatable relative to the first inner ring (1) in a reverse or forward direction, and/or the second pawl (20) is in a disengaged state from the first outer ring (2) in an initial position, in which the first outer ring (2) is rotatable relative to the first inner ring (1) in a forward or reverse direction, and/or the second pawl (20) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, in which the first auxiliary outer ring (12) is rotatable relative to the first inner ring (1) in a forward or reverse direction, the first inner ring (1) and the first outer ring (2) and the first auxiliary outer ring (12) and the first shift cam (25) being configured with at least ratchet-like projections and/or ratchet-like recesses, And the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-like protrusion and/or ratchet-like recess, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first inner ring (1), the first pawl (11) is rotatable within a certain angular range relative to the first inner ring (1), and/or the first pawl (11) is directly or indirectly connected with the first left clutch bracket (5), the first pawl (11) is rotatable within a certain angular range relative to the first left clutch bracket (5), and/or the first pawl (11) is directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) is rotatable within a certain angular range relative to the first right clutch bracket (6), the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first inner ring (1), the second pawl (20) is rotatable relative to the first outer ring (2) within a certain angular range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) is rotatable relative to the first left clutch support (5) within a certain angular range, and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) is rotatable relative to the first right clutch support (6) within a certain angular range, the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first inner ring (1) and rotates together with the first inner ring (1), and/or the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) returns to the initial position under the elastic force of the first return spring (4) when the other constraint or load acts on the first pawl (11) less than the elastic force of the first return spring (4) on the first pawl (11), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first inner race (1) and rotates with the first inner race (1), and/or the second return spring (21) is directly or indirectly connected with the second pawl (20), when the other constraint or load acts on the second pawl (20) less than the elastic force of the second return spring (21) on the second pawl (20), The second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), the first outer ring (2) is unidirectionally fixed relative to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is unidirectionally fixed relative to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is unidirectionally fixed relative to the first inner ring (1) in the reverse or forward direction when the second pawl (20) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is unidirectionally fixed relative to the first inner ring (1) in the reverse or forward direction when the second pawl (20) is engaged with the first auxiliary outer ring (12) And/or the first outer ring (2) is fixed in both forward and reverse directions relative to the first inner ring (1) within a load range when the first pawls (11) and the second pawls (20) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in both forward and reverse directions relative to the first inner ring (1) within a load range when the first pawls (11) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed in both forward and reverse directions and rotatable in reverse or forward directions relative to the first inner ring (1) within a load range when the first pawls (11) are engaged with the first outer ring (2) and the second pawls (20) are disengaged from the first outer ring (2), and/or when the first pawls (11) are engaged with the first auxiliary outer ring (12) and the second pawls (20) are disengaged from the first auxiliary outer ring (12), the first auxiliary outer ring (12) is fixed in the forward or reverse rotation direction and rotatable in the reverse or forward rotation direction with respect to the first inner ring (1) over a certain load range, and/or when the first pawls (11) are disengaged from the first outer ring (2) and the second pawls (20) are engaged with the first outer ring (2), the first outer ring (2) is fixed in the reverse or forward rotation direction and rotatable in the forward or reverse rotation direction with respect to the first inner ring (1) over a certain load range, and/or when the first pawls (11) are disengaged from the first auxiliary outer ring (12) and the second pawls (20) are engaged with the first auxiliary outer ring (12), The first auxiliary outer ring (12) is fixed in the reverse rotation direction or the forward rotation direction relative to the first inner ring (1) and can rotate in the forward rotation direction or the reverse rotation direction within a certain load range, and/or the first outer ring (2) can rotate in the forward rotation direction and the reverse rotation direction relative to the first inner ring (1) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first outer ring (2), and/or the first auxiliary outer ring (12) can rotate in the forward rotation direction and the reverse rotation direction relative to the first inner ring (1) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first auxiliary outer ring (12), and the contact pair of the first pawl (11) and the first outer ring (2) has an overload protection function when the first pawl (11) and the first outer ring (2) are in an engaged state, The first pawl (11) is automatically disengaged from the first outer ring (2) when the acting force between the first pawl (11) and the first outer ring (2) is excessive, and/or the contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function when the acting force between the first pawl (11) and the first outer ring (2) is in an engaged state, the contact pair of the first pawl (11) and the first outer ring (2) does not automatically disengage when the acting force between the first pawl (11) and the first outer ring (2) is large, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has an overload protection function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, and the first pawl (11) and the first auxiliary outer ring (12) have an overload protection function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, The first pawls (11) are automatically disengaged from the first auxiliary outer ring (12), and/or the contact pairs of the first pawls (11) and the first auxiliary outer ring (12) have a self-locking function when the first pawls (11) and the first auxiliary outer ring (12) are in an engaged state, the contact pairs of the first pawls (11) and the first auxiliary outer ring (12) are not automatically disengaged when a force between the first pawls (11) and the first auxiliary outer ring (12) is large, and/or the contact pairs of the second pawls (20) and the first outer ring (2) have an overload protection function when the second pawls (20) and the first outer ring (2) are in an engaged state, and the second pawls (20) and the first outer ring (2) are automatically disengaged when a force between the second pawls (20) and the first outer ring (2) is excessive, and/or the contact pair of the second pawl (20) and the first outer ring (2) has a self-locking function when the second pawl (20) and the first outer ring (2) are in an engaged state, the contact pair of the second pawl (20) and the first outer ring (2) cannot be automatically disengaged when a force between the second pawl (20) and the first outer ring (2) is large, and/or the contact pair of the second pawl (20) and the first auxiliary outer ring (12) has an overload protection function when the second pawl (20) and the first auxiliary outer ring (12) are in an engaged state, the second pawl (20) and the first auxiliary outer ring (12) are automatically disengaged when a force between the second pawl (20) and the first auxiliary outer ring (12) is excessive, and/or the second pawl (20) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary outer ring (12) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is large, the contact pair of the second pawl (20) and the first auxiliary outer ring (12) can not be automatically disengaged, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first inner ring (1) through the first clutch rivet (7), and/or the first shift cam (25) is directly or indirectly connected to the first inner ring (1), the first shift cam (25) rotates relative to the first outer ring (2) within a certain angular range, and/or the first inner ring (1) has a certain angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotates relative to the first inner ring (1) within a certain angular range against the effect of the first inner ring (1), and/or the first inner ring (1) is at least provided with a series of positioning grooves or projections, the first shift cam (25) is at least provided with a function of angular positioning relative to the first inner ring (1) in the direction of rotation via the series of positioning grooves or projections within a certain range, and/or the first shift cam (25) directly or indirectly engages or engages with the first left engagement bracket (5) -a connection, the first shift cam (25) rotating within an angular range relative to the first left clutch carrier (5), and/or the first left clutch carrier (5) having an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotating within an angular range relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or the first left clutch carrier (5) being configured with at least one series of detents or projections, the first shift cam (25) being configured at least to perform an angular positioning function within a range relative to the first left clutch carrier (5) via the series of detents or projections, and/or the first shift cam (25) directly or indirectly connecting the first shift cam (25) to the first right clutch carrier (6) The first right clutch support (6) rotates in a certain angle range relative to the first right clutch support (6), and/or the first right clutch support (6) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, the first shift cam (25) selectively rotates in a certain angle range relative to the first right clutch support (6) against the effect of the first right clutch support (6), and/or at least a series of positioning grooves or protrusions are configured on the first right clutch support (6), the first shift cam (25) is at least configured to perform a function of angular positioning in the rotation direction relative to the first right clutch support (6) in a certain range through the series of positioning grooves or protrusions, and/or the first positioning mechanism (19) is directly or indirectly connected with the first inner ring (1), The first positioning means (19) rotates together with the first inner ring (1), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25), and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) selectively rotates relative to the first inner ring (1) within an angular range against the effect of the first positioning means (19), and/or the first shift cam (25) is provided with a series of detents or projections, the first shift cam (25) being at least configured to function in a rotational direction relative to the first positioning means (19) within a certain range by means of the series of detents or projections, and/or the first shift cam (25) being directly or indirectly connected to the first pawl (11) and a rotation of the first shift cam (25) relative to the first inner race (1) directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first outer race (2), and/or the first shift cam (25) being directly or indirectly connected to the first pawl (11) and a rotation of the first shift cam (25) relative to the first inner race (1) directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first auxiliary race (12), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) relative to the first inner ring (1) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first outer ring (2) and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) relative to the first inner ring (1) directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary outer ring (12) and/or the first shift cam (25) is directly or indirectly connected to the Actuation Means (AM) and the first shift cam (25) is selectively rotated within a certain angular range relative to the first inner ring (1) under the drive of the Actuation Means (AM), and/or when the first shift cam (25) is in a certain angular intermediate position in the direction of rotation directly or indirectly under the action of the Actuation Means (AM), the first pawl (11) is in an engaged or disengaged state with the first outer ring (2), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2), and/or when the first shift cam (25) is in a certain side away from the certain angular intermediate position in the direction of rotation directly or indirectly under the action of the Actuation Means (AM) When the other side is in a state that the first pawl (11) is engaged with or separated from the first outer ring (2), the second pawl (20) is engaged with or separated from the first outer ring (2), and/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has a function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), And under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of being capable of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), and/or the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), and/or when the first outer ring (2) rotates reversely or positively relative to the first inner ring (1), under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle defined by the first limit pin (13) relative to the first outer ring (2), a partial surface of the first auxiliary outer ring (12) and a partial surface of the first outer ring (2) are combined into a cylindrical surface, The first pawl (11) is in contact with the split cylindrical surface when rotating relative to the first outer ring (2) so that noise is greatly reduced, and/or when the first outer ring (2) rotates forwards or reversely relative to the first inner ring (1), under the direct or indirect action of the second pawl (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) is combined with part of the surface of the first outer ring (2) to form a cylindrical surface, and the second pawl (20) contacts with the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first return spring (4), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), wherein the first left half clutch (15), and/or the first right clutch bracket (6), and/or the first auxiliary right half clutch (17), the first shift gear sleeve (18), and/or the first positioning mechanism (19) are coaxially arranged with the first right half clutch (16), and the first return spring (4), And/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), and/or the first auxiliary right half clutch (17), the first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21) are arranged axially on one side of the first right half clutch (16), and/or the first left half clutch (15) passes coaxially through the first right half clutch (16), or the first right half clutch (16) passes coaxially through the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with and rotates together with the driving part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected with a driven part of the machine (M) and rotates with a driven part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates with a driving part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or the first right half-clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates with the machine (M) The driven piece of the device (M) rotates together, and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way mode in the forward or reverse direction relative to the first left half clutch (15), and/or the first pawl (11) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way mode in the forward or reverse direction relative to the first left half clutch (15), and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way in the reverse or forward direction relative to the first left half clutch (15), and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way manner relative to the first left half clutch (15) in a reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is rotatable relative to the first left half clutch (15) in a reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is rotatable relative to the first left half clutch (15) in a reverse or forward direction, and/or the second pawl (20) is in a disengaged state with the first right half clutch (16) at an initial position, The first right half clutch (16) can rotate in the forward or reverse direction relative to the first left half clutch (15) at the time, and/or the second pawl (20) is in a disengaged state from the first auxiliary right half clutch (17) at the initial position, the first auxiliary right half clutch (17) can rotate in the forward or reverse direction relative to the first left half clutch (15), the first right half clutch (16), and the first auxiliary right half clutch (17) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, and the first pawl (11) and the second pawl (20) are at least configured with a function of engaging with or disengaging from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) includes at least one pawl, the first pawl (11) is directly or indirectly connected with the first left half clutch (15), and/or the second pawl (20) is in a disengaged state of disengaging from the first auxiliary right half clutch (17) in the forward or reverse direction, and the first pawl (17) is at least configured with a function of engaging with or, Said first pawl (11) rotating together with said first left clutch half (15), said first pawl (11) being rotatable within an angular range relative to said first left clutch half (15), and/or said first pawl (11) being directly or indirectly connected to said first right clutch support (6), said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected to said first left clutch half (15), said second pawl (20) rotating together with said first left clutch half (15), said second pawl (20) being rotatable within an angular range relative to said first left clutch half (15), and/or the second pawl (20) is directly or indirectly connected to the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) is rotatable within an angular range relative to the first right clutch support (6), the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected to the first left clutch half (15) and rotates together with the first left clutch half (15), and/or the first return spring (4) is directly or indirectly connected to the first pawl (11), the first pawl (11) returns to the initial position under the spring force of the first return spring (4) when the other constraint or load acts on the first pawl (11) less than the spring force of the first return spring (4) acts on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), and/or the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the elastic action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the elastic action of the second return spring (21), when the first pawl (11) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in a one-way manner relative to the first left half clutch (15) in a forward rotation or reverse rotation direction within a certain load range, and/or the first auxiliary right half clutch (17) is fixed in one way in the forward or reverse direction relative to the first left half clutch (15) in a load range when the first pawl (11) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is fixed in one way in the reverse or forward direction relative to the first left half clutch (15) in a load range when the second pawl (20) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in one way in the reverse or forward direction relative to the first left half clutch (15) in a load range when the second pawl (20) is engaged with the first auxiliary right half clutch (17), and/or the first pawl (11) and the second pawl (20) are engaged with the first right half clutch (16), -the first right half clutch (16) is fixed in both forward and reverse directions relative to the first left half clutch (15) and/or-the first auxiliary right half clutch (17) is fixed in both forward and reverse directions relative to the first left half clutch (15) in a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary right half clutch (17) and/or-the first right half clutch (16) is fixed in both forward and reverse directions relative to the first left half clutch (15) and/or-the first right half clutch (16) is fixed in either reverse or reverse direction and rotatable in either reverse or forward direction relative to the first left half clutch (15) and/or-the first pawl (11) is engaged with the first auxiliary right half clutch (17) and the second pawl (20) is disengaged from the first right half clutch (16) in a certain load range (20) When the first auxiliary right half clutch (17) is disengaged, the first auxiliary right half clutch (17) is fixed in the forward or reverse direction and can rotate in the reverse or forward direction relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is disengaged from the first right half clutch (16) and the second pawl (20) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in the reverse or forward direction and can rotate in the forward or reverse direction relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) is disengaged from the first auxiliary right half clutch (17) and the second pawl (20) is engaged with the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) is engaged, the first auxiliary right half clutch (17), the second auxiliary right half clutch (17) is engaged within a certain load range, The first auxiliary right half clutch (17) is fixed in the reverse rotation or the forward rotation direction relative to the first left half clutch (15) and can rotate in the forward rotation or the reverse rotation direction, and/or when the first pawl (11) and the second pawl (20) are separated from the first right half clutch (16), the first right half clutch (16) can rotate in the forward rotation and the reverse rotation directions relative to the first left half clutch (15) within a certain load range, and/or when the first pawl (11) and the second pawl (20) are separated from the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) can rotate in the forward rotation and the reverse rotation directions relative to the first left half clutch (15) within a certain load range, and when the first pawl (11) and the first right half clutch (16) are in the engaged state, The contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function, the first pawl (11) and the first right half clutch (16) are automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is overlarge, and/or the contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function when the first pawl (11) and the first right half clutch (16) are in an engaged state, the contact pair of the first pawl (11) and the first right half clutch (16) are not automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is large, and/or the contact pair of the first pawl (11) and the first right half clutch (16) are not automatically disengaged when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has an overload protection function, the first pawl (11) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is overlarge, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has a self-locking function when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is not automatically disengaged when the second pawl (20) and the first right half clutch (16) are in an engaged state, The contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function, the second pawl (20) and the first right half clutch (16) are automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is overlarge, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) is not automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is large, and/or the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the function of overload protection, the second pawl (20) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is overlarge, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the self-locking function when the second pawl (20) and the first auxiliary right half clutch (17) are in the engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, and/or the first right clutch bracket (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first clutch rivet (7) comprises at least one rivet, and/or the first right clutch support (6) is fixedly connected to the first left clutch half (15) by means of the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch half (15) and rotates together with the first left clutch half (15), and/or the first left clutch half (15) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left clutch half (15) against the effect of the first left clutch half (15), and/or at least one series of axial positioning grooves or projections are formed on the first left clutch half (15), the first shift sleeve (18) being configured at least in a certain range by means of the series of axial positioning grooves or projections -a function of axial positioning with respect to the first left clutch half (15), and/or-the first shifting sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and rotates with the first right clutch carrier (6), and/or-the first right clutch carrier (6) has a certain limiting effect on the first shifting sleeve (18) in the axial direction, -the first shifting sleeve (18) is selectively movable in the axial direction with respect to the first right clutch carrier (6) against the effect of the first right clutch carrier (6), and/or-the first right clutch carrier (6) is configured with at least a series of axial positioning grooves or projections, the first shifting sleeve (18) is configured with at least a certain range of axial positioning grooves or projections with respect to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch half (15), the first positioning means (19) rotates together with the first left clutch half (15), the first positioning means (19) is axially fixed relative to the first left clutch half (15), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a limiting effect on the first shift sleeve (18) in the axial direction, The first shift sleeve (18) being selectively movable in the axial direction relative to the first left half clutch (15) against the action of the first positioning means (19), and/or the first shift sleeve (18) being provided with a series of axial detents or projections, the first shift sleeve (18) being configured at least to position at least one of its axial positions by the action of the series of axial detents or projections within a certain range of constraint with the first positioning means (19), and/or the first shift sleeve (18) being directly or indirectly connected to the first pawl (11) and the selective axial movement of the first shift sleeve (18) relative to the first left half clutch (15) within a certain range at least directly or indirectly bringing the first pawl (11) into engagement or disengagement with the first right half clutch (16), and/or the first shift sleeve gear (18) is directly or indirectly connected with the first pawl (11) and the first shift sleeve gear (18) is at least directly or indirectly in an engaged or disengaged state with respect to the first left half clutch (15) by selectively axially moving the first shift sleeve gear (18) in a certain range, and/or the first shift sleeve gear (18) is directly or indirectly connected with the second pawl (20), And the selective axial displacement of the first shift sleeve (18) relative to the first left half clutch (15) within a certain range brings at least the second pawl (20) directly or indirectly into engagement or disengagement with the first auxiliary right half clutch (17) and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve (18) is selectively displaced axially within a certain range relative to the first left half clutch (15) under the drive of the actuating device (AM) and/or the first pawl (11) is brought into engagement or disengagement with the first right half clutch (16) when the first shift sleeve (18) is brought directly or indirectly into an intermediate position in the axial direction under the action of the actuating device (AM), the second pawl (20) is brought into engagement or disengagement with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is axially in a position close to the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is axially in a position away from the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) within the angle range limited by the first limit pin (13), and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16), and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first right half clutch (16), under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle limited by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, and the first pawl (11) contacts with the split plane when rotating relative to the first right half clutch (16), Thereby greatly reducing noise, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first right half clutch (16), under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, and the second pawl (20) rotates relative to the first right half clutch (16) and contacts with the combined plane, thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a first gear shift sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), and/or a first auxiliary left half clutch (22), a first intermediate clutch (23), and/or a second limit pin (24), a third pawl (29), a third return spring (30), and/or a fourth pawl (31), and/or a fourth return spring (32), the first left half clutch (15) and/or the first left clutch support (5) and/or the first right clutch support (6), the first right half clutch (16) and/or the first auxiliary right half clutch (17), the first shift sleeve (18) and/or the first positioning mechanism (19) and/or the first auxiliary left half clutch (22) are arranged coaxially with the first intermediate clutch (23), and the first return spring (4) and/or the first left clutch support (5) and/or the first right clutch support (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), the first left half clutch (15) and/or the first auxiliary right half clutch (17), The first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the first auxiliary left-half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32) are arranged axially on one side of the first right-half clutch (16), and/or the first intermediate clutch (23) passes coaxially through the first left-half clutch (15), or the first intermediate clutch (23) passes coaxially through the first right-half clutch (16), and/or the first left-half clutch (15) passes coaxially through the first right-half clutch (16), or the first right half clutch (16) coaxially penetrates the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with a driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first left half clutch (15) is directly or indirectly connected with the damping buffer Device (DM) and rotates along with the damping buffer Device (DM), and/or the first left half clutch (15) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first left half clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with a driving part of the machine (M) and rotates along with a driving part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first intermediate clutch (23) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the machine (M) The driven piece of the machine (M) rotates together, and/or the first intermediate clutch (23) is directly or indirectly fixedly connected with the frame of the machine (M), the first pawl (11) is in an engagement state with the first left half clutch (15) in an initial position, the first left half clutch (15) is fixed in a forward or reverse direction relative to the first intermediate clutch (23) in a one-way mode, and/or the first pawl (11) is in an engagement state with the first auxiliary left half clutch (22) in an initial position, the first auxiliary left half clutch (22) is fixed in a one-way mode in a forward or reverse direction relative to the first intermediate clutch (23), and/or the second pawl (20) is in an engagement state with the first left half clutch (15) in an initial position, the first left half clutch (15) is fixed in a reverse or forward direction relative to the first intermediate clutch (23) in a one-way mode, and/or the second pawl (20) is engaged with the first auxiliary left-half clutch (22) in an initial position, in which the first auxiliary left-half clutch (22) is fixed in a unidirectional manner in a reverse or forward direction with respect to the first intermediate clutch (23), and/or the first left-half clutch (15) is rotatable in a reverse or forward direction with respect to the first intermediate clutch (23) when the first pawl (11) is disengaged from the first left-half clutch (15), and/or the first auxiliary left-half clutch (22) is rotatable in a reverse or forward direction with respect to the first intermediate clutch (23) when the first pawl (11) is disengaged from the first auxiliary left-half clutch (22), and/or the second pawl (20) is disengaged from the first right-half clutch (16), The first right half clutch (16) can rotate in the forward or reverse direction relative to the first intermediate clutch (23), and/or the first auxiliary left half clutch (22) can rotate in the forward or reverse direction relative to the first intermediate clutch (23) when the second pawl (20) and the first auxiliary left half clutch (22) are in a separated state, and/or the third pawl (29) and the first right half clutch (16) are in an engaged state in an initial position, at which time the first right half clutch (16) is fixed in a one-way manner in the forward or reverse direction relative to the first intermediate clutch (23), and/or the third pawl (29) and the first auxiliary right half clutch (17) are in an engaged state in an initial position, at which time the first auxiliary right half clutch (17) is fixed in a one-way in the forward or reverse direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first right half clutch (16) at an initial position, when the first right half clutch (16) is fixed in a one-way manner in a reverse or normal direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in a reverse or normal direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in a disengaged state with the first right half clutch (16), when the first right half clutch (16) is rotatable in a reverse or normal direction relative to the first intermediate clutch (23), and/or when the third pawl (29) is in a disengaged state with the first auxiliary right half clutch (17), the first right half clutch (16) is rotatable in a reverse or normal direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in a disengaged state with the first auxiliary right half, The first auxiliary right half clutch (17) can rotate in a reverse rotation direction or a forward rotation direction relative to the first intermediate clutch (23), and/or the first right half clutch (16) can rotate in a forward rotation direction or a reverse rotation direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first right half clutch (16) are in a separated state, and/or the first auxiliary right half clutch (17) can rotate in a forward rotation direction or a reverse rotation direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first auxiliary right half clutch (17) are in a separated state, and the first left half clutch (15), the first right half clutch (16), the first auxiliary left half clutch (22), the first auxiliary right half clutch (17) and the first intermediate clutch (23) are at least provided with ratchet-shaped bulges and/or ratchet-shaped grooves, And the first pawl (11) and the second pawl (20) and the third pawl (29) and the fourth pawl (31) are at least configured to engage with or disengage from the ratchet-like projections and/or ratchet-like recesses, and/or the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first intermediate clutch (23), the first pawl (11) rotates together with the first intermediate clutch (23), the first pawl (11) is rotatable within an angular range relative to the first intermediate clutch (23), and/or the first pawl (11) is directly or indirectly connected with the first left clutch support (5), the first pawl (11) rotates together with the first left clutch support (5), the first pawl (11) is rotatable within an angular range relative to the first left clutch support (5), the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first intermediate clutch (23), the second pawl (20) rotates together with the first intermediate clutch (23), the second pawl (20) can rotate relative to the first intermediate clutch (23) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), the second pawl (20) can rotate relative to the first left clutch support (5) within a certain angle range, the third pawl (29) comprises at least one pawl, the third pawl (29) is directly or indirectly connected to the first intermediate clutch (23), and the third pawl (29) rotates together with the first intermediate clutch (23), The third pawl (29) can rotate within a certain angle range relative to the first intermediate clutch (23), and/or the third pawl (29) is directly or indirectly connected with the first right clutch support (6), the third pawl (29) rotates with the first right clutch support (6), the third pawl (29) can rotate within a certain angle range relative to the first right clutch support (6), the fourth pawl (31) comprises at least one pawl, the fourth pawl (31) is directly or indirectly connected with the first intermediate clutch (23), the fourth pawl (31) rotates with the first intermediate clutch (23), the fourth pawl (31) can rotate within a certain angle range relative to the first intermediate clutch (23), and/or the fourth pawl (31) is directly or indirectly connected with the first right clutch support (6), the first intermediate clutch support (23), the second clutch support (6) and the second clutch support (29) are connected with the second pawl (31), the second pawl (29) and the second pawl (31) can rotate with the first intermediate clutch support (23) within a certain angle range, The fourth pawl (31) rotates together with the first right clutch support (6), the fourth pawl (31) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) comprises at least one spring, the first return spring (4) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the second return spring (21) comprises at least one spring, the second return spring (21) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the third return spring (30) comprises at least one spring, and the third return spring (30) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the fourth return spring (32) comprises at least one spring, the fourth return spring (32) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other constraints or loads on the first pawl (11) is smaller than the effect of the first return spring (4) on the first pawl (11), and/or the second return spring (21) is directly or indirectly connected with the second pawl (20), the effect of other constraints or loads on the second pawl (20) is smaller than the effect of the second return spring (21) on the second pawl (20), The second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21), and/or the third return spring (30) is directly or indirectly connected to the third pawl (29), the third pawl (29) returns to the initial position under the action of the spring force of the third return spring (30) when the action of other restraint or load on the third pawl (29) is smaller than the action of the third return spring (30) on the third pawl (29), and/or the fourth return spring (32) is directly or indirectly connected to the fourth pawl (31), the fourth pawl (31) returns to the initial position under the action of the spring force of the fourth return spring (32) when the action of other restraint or load on the fourth pawl (31) is smaller than the action of the fourth return spring (32) on the fourth pawl (31), the first left-half clutch (15) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a load range when the first pawl (11) is engaged with the first left-half clutch (15), and/or the first auxiliary left-half clutch (22) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a load range when the first pawl (11) is engaged with the first auxiliary left-half clutch (22), and/or the first left-half clutch (15) is fixed in a unidirectional manner in the reverse or reverse direction relative to the first intermediate clutch (23) within a load range when the second pawl (20) is engaged with the first left-half clutch (15), and/or the second pawl (20) is engaged with the first auxiliary left-half clutch (22), -the first auxiliary left half clutch (22) is fixed in one direction in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or the first left half clutch (15) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first left half clutch (15), and/or the first auxiliary left half clutch (22) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the first pawl (11) is disengaged from the first auxiliary left half clutch (22), and/or the first left half clutch (15) is rotatable in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is disengaged from the first left half clutch (15), and/or the first auxiliary left-half clutch (22) can rotate in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the second pawl (20) is disengaged from the first auxiliary left-half clutch (22), and/or the first right-half clutch (16) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is engaged with the first right-half clutch (16), and/or the first auxiliary right-half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is engaged with the first auxiliary right-half clutch (17), and/or the fourth pawl (31) is engaged with the first right-half clutch (16), The first right half clutch (16) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is disengaged from the first right half clutch (16), and/or the first auxiliary right half clutch (17) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is disengaged from the first auxiliary right half clutch (17), and/or the first right half clutch (16) can rotate in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first right half clutch (16), and/or the first auxiliary right half clutch (17) can rotate in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first auxiliary right half clutch (17), the contact pair of the first pawl (11) and the first left half clutch (15) has an overload protection function when the first pawl (11) and the first left half clutch (15) are in an engaged state, and the first pawl (11) and the first left half clutch (15) are automatically disengaged when an excessive force acts between the first pawl (11) and the first left half clutch (15), and/or the contact pair of the first pawl (11) and the first left half clutch (15) has a self-locking function when the first pawl (11) and the first left half clutch (15) are in an engaged state, the contact pair of the first pawl (11) and the first left half clutch (15) cannot be automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function when the first pawl (11) and the first auxiliary left half clutch (22) are in an engaged state, and the first pawl (11) and the first auxiliary left half clutch (22) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left-half clutch (22) has a self-locking function when the first pawl (11) and the first auxiliary left-half clutch (22) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary left-half clutch (22) cannot be automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left-half clutch (22) is large, and/or the contact pair of the second pawl (20) and the first left-half clutch (15) has an overload protection function when the second pawl (20) and the first left-half clutch (15) are in an engaged state, and the second pawl (20) and the first left-half clutch (15) are automatically disengaged when the acting force between the second pawl (20) and the first left-half clutch (15) is excessive, and/or the contact pair of the second pawl (20) and the first left-half clutch (15) has a self-locking function when the second pawl (20) and the first left-half clutch (15) are in an engaged state, the contact pair of the second pawl (20) and the first left-half clutch (15) cannot be automatically disengaged when the acting force between the second pawl (20) and the first left-half clutch (15) is large, and/or the contact pair of the second pawl (20) and the first auxiliary left-half clutch (22) has an overload protection function when the second pawl (20) and the first auxiliary left-half clutch (22) are in an engaged state, and the second pawl (20) and the first auxiliary left-half clutch (22) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary left-half clutch (22) is excessive, and/or the contact partner of the second pawl (20) with the first auxiliary left-half clutch (22) has a self-locking function when the second pawl (20) is in the engaged state with the first auxiliary left-half clutch (22), the contact partner of the second pawl (20) with the first auxiliary left-half clutch (22) is not automatically disengaged when the force between the second pawl (20) and the first auxiliary left-half clutch (22) is greater, and/or the contact partner of the third pawl (29) with the first right-half clutch (16) has an overload protection function when the third pawl (29) is in the engaged state with the first right-half clutch (16), the third pawl (29) is automatically disengaged from the first right-half clutch (16) when the force between the third pawl (29) and the first right-half clutch (16) is greater, and/or the contact pair of the third pawl (29) and the first right half clutch (16) has a self-locking function when the third pawl (29) and the first right half clutch (16) are in an engaged state, the contact pair of the third pawl (29) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is large, and/or the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has an overload protection function when the third pawl (29) and the first auxiliary right half clutch (17) are in an engaged state, and the third pawl (29) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is excessive, and/or when the third pawl (29) is in an engaged state with the first auxiliary right half clutch (17), the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has a self-locking function, when the force between the third pawl (29) and the first auxiliary right half clutch (17) is large, the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) cannot be automatically disengaged, and/or when the fourth pawl (31) and the first right half clutch (16) are in an engaged state, the contact pair of the fourth pawl (31) and the first right half clutch (16) has an overload protection function, when the force between the fourth pawl (31) and the first right half clutch (16) is excessive, the fourth pawl (31) and the first right half clutch (16) are automatically disengaged, and/or the contact pair of the fourth pawl (31) and the first right half clutch (16) has a self-locking function when the fourth pawl (31) and the first right half clutch (16) are in an engaged state, the contact pair of the fourth pawl (31) and the first right half clutch (16) cannot be automatically disengaged when the acting force between the fourth pawl (31) and the first right half clutch (16) is larger, and/or the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has an overload protection function when the fourth pawl (31) and the first auxiliary right half clutch (17) are in an engaged state, and the fourth pawl (31) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary right half clutch (17) is too large, and/or when the fourth pawl (31) is in an engaged state with the first auxiliary right half clutch (17), the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has a self-locking function, when the force between the fourth pawl (31) and the first auxiliary right half clutch (17) is large, the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) cannot be automatically disengaged, and/or the first left clutch bracket (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch bracket (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch bracket (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), and/or the first right clutch carrier (6) is fixedly connected to the first intermediate clutch (23) by means of the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first intermediate clutch (23) against the effect of the first intermediate clutch (23), and/or at least one series of axial positioning grooves or projections are formed on the first intermediate clutch (23), and the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first intermediate clutch (23) by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or at least one series of axial positioning grooves or projections are formed on the first left clutch carrier (5), the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first left clutch carrier (5) within a certain range by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and to the third clutch carrier (6) A right clutch carrier (6) rotates together, and/or the first right clutch carrier (6) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction against the effect of the first right clutch carrier (6) relative to the first right clutch carrier (6), and/or the first right clutch carrier (6) is at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least provided with a function of axial positioning relative to the first right clutch carrier (6) in a certain range through the series of axial positioning grooves or projections, and/or the first positioning mechanism (19) is directly or indirectly connected with the first intermediate clutch (23), the first positioning mechanism (19) rotates together with the first intermediate clutch (23), and/or, The first positioning means (19) is axially fixed relative to the first intermediate clutch (23), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), the first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates together with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), And said first positioning means (19) having a limiting action in an axial direction on said first shifting sleeve (18), said first shifting sleeve (18) being selectively movable in an axial direction with respect to said first left-hand half-clutch (15) against the action of said first positioning means (19), and/or said first shifting sleeve (18) being provided with a series of axial positioning slots or projections, said first shifting sleeve (18) being configured at least to position at least one axial position thereof by means of said series of axial positioning slots or projections and said first positioning means (19) within a certain range of constraint, and/or said first shifting sleeve (18) being directly or indirectly connected to said first pawl (11), and movement of said first shifting sleeve (18) in an axial direction with respect to said first intermediate clutch (23) within a certain range of direct or indirect engagement of said first pawl (11) with said first left-hand half-clutch (15) In an engaged or disengaged state, and/or the first shift sleeve gear (18) is directly or indirectly connected to the first pawl (11) and a movement of the first shift sleeve gear (18) in an axial direction relative to the first intermediate clutch (23) within a certain range directly or indirectly brings the first pawl (11) into an engaged or disengaged state with the first auxiliary left half clutch (22), and/or the first shift sleeve gear (18) is directly or indirectly connected to the second pawl (20) and a movement of the first shift sleeve gear (18) in an axial direction relative to the first intermediate clutch (23) within a certain range directly or indirectly brings the second pawl (20) into an engaged or disengaged state with the first left half clutch (15), and/or the first shift sleeve gear (18) is directly or indirectly connected to the second pawl (20), And the first shift sleeve gear (18) is axially displaced relative to the first intermediate clutch (23) within a certain range such that the second pawl (20) is directly or indirectly in the engaged or disengaged state with the first auxiliary left clutch half (22), and/or the first shift sleeve gear (18) is directly or indirectly connected to the third pawl (29), and the first shift sleeve gear (18) is axially displaced relative to the first intermediate clutch (23) within a certain range such that the third pawl (29) is directly or indirectly in the engaged or disengaged state with the first right clutch half (16), and/or the first shift sleeve gear (18) is directly or indirectly connected to the third pawl (29), and the first shift sleeve gear (18) is axially displaced relative to the first intermediate clutch half (23) within a certain range such that the third pawl (29) is directly or indirectly in the engaged state with the first auxiliary right clutch half (17) An engaged or disengaged state, and/or the first shift sleeve gear (18) is directly or indirectly connected to the fourth pawl (31) and the first shift sleeve gear (18) is axially displaced relative to the first intermediate clutch (23) within a certain range such that the fourth pawl (31) is directly or indirectly engaged with or disengaged from the first right half clutch (16), and/or the first shift sleeve gear (18) is directly or indirectly connected to the fourth pawl (31) and the first shift sleeve gear (18) is axially displaced relative to the first intermediate clutch (23) within a certain range such that the fourth pawl (31) is directly or indirectly engaged with or disengaged from the first auxiliary right half clutch (17), and/or the first shift sleeve gear (18) is directly or indirectly connected to the actuating device (AM), And the first shift sleeve (18) is selectively axially displaced within a certain range relative to the first intermediate clutch (23) under the drive of the actuating device (AM), and/or when the first shift sleeve (18) is axially in a certain intermediate position directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16), and/or when the first shift sleeve (18) is axially in a certain position close to the first left half clutch (15) directly or indirectly under the action of the actuating device (AM) When the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16), and/or when the first shift sleeve (18) is axially located close to the first right half clutch (16) directly or indirectly under the action of the Actuating Means (AM), the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), The fourth pawl (31) is in a joint or separation state with the first right half clutch (16), and/or the first limit pin (13) at least comprises one pin, and/or the second limit pin (24) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and the first auxiliary left half clutch (22) at least has a function of rotating a certain angle relative to the first left half clutch (15) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), and the first auxiliary left half clutch (22) at least has the function of rotating relative to the first left half clutch (15) within the angle range limited by the first limit pin (13) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and the first auxiliary right half clutch (17) at least has the function of rotating a certain angle relative to the first right half clutch (16) under the action of the third pawl (29) or the fourth pawl (31), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), And the first auxiliary right half clutch (17) has at least the function of rotating relative to the first right half clutch (16) within the angle range defined by the second limit pin (24) under the action of the third pawl (29) or the fourth pawl (31), and/or the first auxiliary left half clutch (22) is coaxially arranged on one side of the first left half clutch (15), and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16), and/or the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15) under the direct or indirect action of the first pawl (11) or the first auxiliary left half clutch (22) rotates to the first limit pin relative to the first left half clutch (15) when the first left half clutch (15) rotates in reverse or forward direction relative to the first intermediate clutch (23), or the first auxiliary left half clutch (22) rotates to the first limit pin relative to the first left half clutch (15) After the angle defined by the nail (13), partial surface of the first auxiliary left half clutch (22) and partial surface of the first left half clutch (15) are radially combined to form a plane, the first pawl (11) is in contact with the combined plane when rotating relative to the first intermediate clutch (23), so that noise is greatly reduced, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first intermediate clutch (23), under the direct or indirect action of the second pawl (20), the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), or the first auxiliary left half clutch (22) rotates to the angle defined by the first limit pin (13) relative to the first left half clutch (15), the partial surface of the first auxiliary left half clutch (22) and the partial surface of the first left half clutch (15) are radially combined to form a plane A flat surface, the second pawl (20) is contacted with the split flat surface when rotating relative to the first middle clutch (23) so as to greatly reduce noise, and/or the partial surface of the first auxiliary right half clutch (17) and the partial surface of the first right half clutch (16) are radially combined into a flat surface when the first right half clutch (16) rotates relative to the first middle clutch (23) under the direct or indirect action of the third pawl (29) after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16) or the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), so that the third pawl (29) is contacted with the split flat surface when rotating relative to the first middle clutch (23), Thereby greatly reducing noise, and/or when the first right half clutch (16) rotates forwards or backwards relative to the first intermediate clutch (23), under the direct or indirect action of the fourth pawl (31), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially split into a plane, so that the fourth pawl (31) contacts with the split plane when rotating relative to the first intermediate clutch (23), thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), a first shift gear sleeve (18), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), and/or a first transmission pin (26), wherein the first left half clutch (15), and/or the first left clutch bracket (5), and/or the first right clutch bracket (6), and/or the first auxiliary right half clutch (17), The first shifting sleeve (18) and/or the first positioning means (19), the first shifting cam (25) and the first right partial clutch (16) are arranged coaxially, the first return spring (4) and/or the first left clutch carrier (5) and/or the first right clutch carrier (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), the first left partial clutch (15) and/or the first auxiliary right partial clutch (17), the first shifting sleeve (18) and/or the first positioning means (19) and/or the second pawl (20) and/or the second return spring (21), the first shifting cam (25) and/or the first transmission pin (26) are arranged axially on a right partial clutch (16) of the first right partial clutch (16) -side, and/or the first left half-clutch (15) coaxially passes through the first right half-clutch (16), or the first right half-clutch (16) coaxially passes through the first left half-clutch (15), and/or the first left half-clutch (15) is directly or indirectly connected with and rotates with the driving member of the machine (M), the first left half-clutch (15) is directly or indirectly connected with and rotates with the cushion damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected with and rotates with the driven member of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with and rotates with the driving member of the machine (M) And/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates with a driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way manner in a forward or reverse rotation direction relative to the first left half clutch (15) at the initial position, and/or the first pawl (11) is in an engaged state with the first auxiliary right half clutch (17) at the initial position, The first auxiliary right half clutch (17) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first left half clutch (15) at the moment, and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way mode in the reverse or forward rotation direction relative to the first left half clutch (15) at the moment, and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way mode in the reverse or forward rotation direction relative to the first left half clutch (15) at the moment, and/or the first pawl (11) is in a disengaged state with the first right half clutch (16) at an initial position, and the first right half clutch (16) can rotate in the reverse or forward rotation direction relative to the first left half clutch (15) at the moment, and/or the first pawl (11) is in a disengaged state from the first auxiliary right half clutch (17) in an initial position, in which the first auxiliary right half clutch (17) can be rotated in the reverse or forward direction relative to the first left half clutch (15), and/or the second pawl (20) is in a disengaged state from the first right half clutch (16) in an initial position, in which the first right half clutch (16) can be rotated in the forward or reverse direction relative to the first left half clutch (15), and/or the second pawl (20) is in a disengaged state from the first auxiliary right half clutch (17) in an initial position, in which the first auxiliary right half clutch (17) can be rotated in the forward or reverse direction relative to the first left half clutch (15), the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) and the first gear shift cam (17), (17) and (17) 25) At least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) comprising at least one pawl, the first pawl (11) being directly or indirectly connected with the first left clutch half (15), the first pawl (11) rotating with the first left clutch half (15), the first pawl (11) being rotatable within an angular range relative to the first left clutch half (15), and/or the first pawl (11) being directly or indirectly connected with the first right clutch bracket (6), the first pawl (11) rotating with the first right clutch bracket (6), the first pawl (11) being rotatable within an angular range relative to the first right clutch bracket (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected to said first left clutch half (15), said second pawl (20) rotating with said first left clutch half (15), said second pawl (20) being rotatable within an angular range relative to said first left clutch half (15), and/or said second pawl (20) being directly or indirectly connected to said first right clutch bracket (6), said second pawl (20) rotating with said first right clutch bracket (6), said second pawl (20) rotating within an angular range relative to said first right clutch bracket (6), said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first left clutch half (15) and rotating with said first left clutch half (15), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the effect of other restraint or load on the second pawl (20) is smaller than the elastic force effect of the second return spring (21) on the second pawl (20), The second pawl (20) restores the initial position under the action of the elastic force of the second return spring (21), when the first pawl (11) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in a one-way manner relative to the first left half clutch (15) in the forward or reverse direction within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary right half clutch (17), the first auxiliary right half clutch (17) is fixed in a one-way manner relative to the first left half clutch (15) in the forward or reverse direction within a certain load range, and/or when the second pawl (20) is engaged with the first right half clutch (16), the first right half clutch (16) is fixed in a one-way relative to the first left half clutch (15) in the reverse or forward direction within a certain load range, and/or the first auxiliary right half clutch (17) is fixed in one direction relative to the first left half clutch (15) in the reverse or forward direction within a certain load range when the second pawl (20) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is fixed in both the forward and reverse directions relative to the first left half clutch (15) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in both the forward and reverse directions relative to the first left half clutch (15) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary right half clutch (17), and/or when the first pawl (11) is engaged with the first right half clutch (16) and the second pawl (20) is disengaged from the first right half clutch (16), within a certain load range, the first right half clutch (16) is fixed in the forward or reverse direction relative to the first left half clutch (15) and is rotatable in the reverse or forward direction, and/or when the first pawl (11) is engaged with the first auxiliary right half clutch (17) and the second pawl (20) is disengaged from the first auxiliary right half clutch (17), within a certain load range, the first auxiliary right half clutch (17) is fixed in the forward or reverse direction relative to the first left half clutch (15) and is rotatable in the reverse or forward direction, and/or when the first pawl (11) is disengaged from the first right half clutch (16) and the second pawl (20) is engaged with the first right half clutch (16), The first right half clutch (16) is fixed in the reverse rotation or the forward rotation direction relative to the first left half clutch (15) and can rotate in the forward rotation or the reverse rotation direction within a certain load range, and/or the first auxiliary right half clutch (17) is fixed in the reverse rotation or the forward rotation direction relative to the first left half clutch (15) and can rotate in the forward rotation or the reverse rotation direction within a certain load range when the first pawl (11) is disengaged from the first auxiliary right half clutch (17) and the second pawl (20) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) can rotate in both the forward rotation and the reverse rotation direction relative to the first left half clutch (15) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first right half clutch (16), and/or the first auxiliary right half clutch (17) can rotate in the forward and reverse directions relative to the first left half clutch (15) within a certain load range when the first pawl (11) and the second pawl (20) are separated from the first auxiliary right half clutch (17), the contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function when the first pawl (11) and the first right half clutch (16) are in an engaged state, the first pawl (11) and the first right half clutch (16) are automatically disengaged when an excessive force is applied between the first pawl (11) and the first right half clutch (16), and/or the contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function when the first pawl (11) and the first right half clutch (16) are in an engaged state, When the acting force between the first pawl (11) and the first right half clutch (16) is large, the contact pair of the first pawl (11) and the first right half clutch (16) can not automatically disengage, and/or when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is excessive, the first pawl (11) and the first auxiliary right half clutch (17) automatically disengage, and/or when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has the function of self-locking, self-locking and self-locking, When the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) can not automatically disengage, and/or when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) has the function of overload protection, when the acting force between the second pawl (20) and the first right half clutch (16) is excessive, the second pawl (20) and the first right half clutch (16) automatically disengage, and/or when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) has the function of self-locking, self-locking and self-locking, When the acting force between the second pawl (20) and the first right half clutch (16) is large, the contact pair of the second pawl (20) and the first right half clutch (16) can not be automatically disengaged, and/or when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the function of overload protection, when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is excessive, the second pawl (20) and the first auxiliary right half clutch (17) are automatically disengaged, and/or when the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the function of self-locking, self-locking and self-locking, When the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, the second pawl (20) and the first auxiliary right half clutch (17) contact pair can not be automatically disengaged, and/or the first left clutch bracket (5) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch bracket (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch bracket (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first right clutch bracket (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or at least one series of axial positioning grooves or projections are formed on the first left clutch carrier (5), the first shift sleeve (18) is at least designed to perform an axial positioning function relative to the first left clutch carrier (5) within a certain range by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and to the third clutch carrier (6) A right clutch support (6) rotating together, and/or the first right clutch support (6) having a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) being selectively movable in the axial direction against the effect of the first right clutch support (6) relative to the first right clutch support (6), and/or the first right clutch support (6) being at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) being at least configured to perform the function of axial positioning relative to the first right clutch support (6) through the series of axial positioning grooves or projections in a certain range, and/or the first positioning means (19) being directly or indirectly connected with the first left clutch support (5), the first positioning means (19) rotating together with the first left clutch support (5), and/or the first positioning means (19) being configured to rotate together with the first left clutch support (5), The first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first right clutch carrier (6), the first positioning means (19) rotates with the first right clutch carrier (6), the first positioning means (19) is axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) axially limits the first shift sleeve (18), the first shift sleeve (18) is axially selectively movable relative to the first left half clutch (15) against the action of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first shift sleeve (18), The first shifting sleeve (18) is at least configured to position at least one of its axial positions by the constraining action of the series of axial detents or protrusions with the first positioning mechanism (19) within a certain range, and/or the first drive pin (26) is directly or indirectly connected with the first shifting sleeve (18) and the first drive pin (26) rotates with the first shifting sleeve (18), and/or the first drive pin (26) is directly or indirectly connected with the first shifting cam (25), the first drive pin (26) is at least configured to push the first shifting cam (25) to rotate within a certain angular range relative to the first left half clutch (15) within a certain axial range, and/or the first shifting cam (25) is directly or indirectly connected with the first left half clutch (15), The first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first left clutch half (15) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first left clutch bracket (5), and the first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first left clutch bracket (5) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first right clutch bracket (6), and the first shifting cam (25) is at least configured to be rotatable within a certain angle range relative to the first right clutch bracket (6) under the action of the first transmission pin (26), and/or the first shifting cam (25) is directly or indirectly connected with the first pawl (11), And rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the first pawl (11) into engagement or disengagement with the first right half clutch (16), and/or the first shift sleeve (18) is directly or indirectly connected with the first pawl (11), and rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the first pawl (11) into engagement or disengagement with the first auxiliary right half clutch (17), and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20), and rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the second pawl (20) into engagement or disengagement with the first right half clutch (16), and/or the first shift gear sleeve (18) is directly or indirectly connected with the second pawl (20), and the rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly enables the second pawl (20) and the first auxiliary right half clutch (17) to be in an engaged or disengaged state, and/or the first shift gear sleeve (18) is sequentially connected with the first pawl (11) through the first transmission pin (26), the first shift cam (25) and the first transmission pin (26), and the axial movement of the first shift gear sleeve (18) sequentially enables the first pawl (11) and the first right half clutch (16) to be in an engaged or disengaged state through the first transmission pin (26), the first shift cam (25), and/or the first shift gear sleeve (18) is sequentially connected with the first transmission pin (26) and the first shift cam (25) and the first auxiliary right half clutch (17) The pawl (11) is connected, the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged or separated state through the first transmission pin (26) and the first shifting cam (25) by axial movement of the first shifting gear sleeve (18), and/or the first shifting gear sleeve (18) is in an engaged or separated state through the first transmission pin (26) and the first shifting cam (25) and the second pawl (20) by axial movement of the first shifting gear sleeve (18) is in an engaged or separated state through the first transmission pin (26) and the first shifting cam (25) by axial movement of the second pawl (20) and the first right half clutch (16) by axial movement of the first shifting gear sleeve (18), and/or the first shifting gear sleeve (18) is in an engaged or separated state through the first transmission pin (26) and the first shifting cam (25) and the second pawl (20) by axial movement of the first shifting gear sleeve (18), And the axial movement of the first shift sleeve gear (18) in turn brings the second pawl (20) into engagement or disengagement with the first auxiliary right half clutch (17) via the first drive pin (26), the first shift cam (25), and/or the first shift sleeve gear (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve gear (18) is selectively moved axially within a certain range relative to the first left half clutch (15) under the drive of the actuating device (AM), and/or the first pawl (11) is brought into engagement or disengagement with the first right half clutch (16) and the second pawl (20) is brought into engagement or disengagement with the first right half clutch (16) when the first shift sleeve gear (18) is brought directly or indirectly into an intermediate position in the axial direction under the action of the actuating device (AM), and/or when the first shift sleeve gear (18) is axially in a position close to the first right half clutch (16) directly or indirectly by the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or when the first shift sleeve gear (18) is axially in a position away from the first right half clutch (16) directly or indirectly by the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) within the angle range limited by the first limit pin (13), and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first right half clutch (16), under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle limited by the first limit pin (13) relative to the first right half clutch (16), a partial surface of the first auxiliary right half clutch (17) and a partial surface of the first right half clutch (16) are radially combined into a plane, and the first pawl (11) contacts with the split plane when rotating relative to the first right half clutch (16), Thereby greatly reducing noise, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first right half clutch (16), under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, and the second pawl (20) rotates relative to the first right half clutch (16) and contacts with the combined plane, thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: the first return spring (4), and/or the first left clutch bracket (5), and/or the first right clutch bracket (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left half clutch (15), the first right half clutch (16), and/or the first auxiliary right half clutch (17), the first shift gear sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the first auxiliary left half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the first shift cam (25), and/or the first transmission pin (26), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), And/or a fourth return spring (32), wherein the first left half clutch (15) and/or the first left clutch support (5) and/or the first right clutch support (6), the first right half clutch (16) and/or the first auxiliary right half clutch (17), the first shifting gear sleeve (18) and/or the first positioning mechanism (19) and/or the first auxiliary left half clutch (22), the first shifting cam (25) and the first intermediate clutch (23) are coaxially arranged, and the first return spring (4) and/or the first left clutch support (5) and/or the first right clutch support (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), The first left half clutch (15) and/or the first auxiliary right half clutch (17), the first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the first auxiliary left half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the first shift cam (25), and/or the first transmission pin (26), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32) are arranged axially on one side of the first right half clutch (16), and/or the first intermediate clutch (23) passes coaxially through the first left half clutch (15), or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) being directly or indirectly connected with the driving member of the machine (M) and rotating together with the driving member of the machine (M), and/or the first left half clutch (15) being directly or indirectly connected with the damping Device (DM) and rotating together with the damping Device (DM), and/or the first left half clutch (15) being directly or indirectly connected with the driven member of the machine (M) and rotating together with the driven member of the machine (M), and/or the first left half clutch (15) being directly or indirectly fixedly connected with the machine frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM) -the Damping Means (DM) rotates together, and/or-the first intermediate clutch (23) is directly or indirectly connected to and rotates with the driven member of the machine (M), and/or-the first intermediate clutch (23) is directly or indirectly fixedly connected to the frame of the machine (M), the first pawl (11) being in an engaged condition with the first left half-clutch (15) in an initial position, in which the first left half-clutch (15) is fixed in a unidirectional manner in a forward or reverse direction with respect to the first intermediate clutch (23), and/or-the first pawl (11) being in an engaged condition with the first auxiliary left half-clutch (22) in an initial position, in which the first auxiliary left half-clutch (22) is fixed in a unidirectional manner in a forward or reverse direction with respect to the first intermediate clutch (23), and/or the second pawl (20) is in an engaged state with the first left-half clutch (15) in the initial position, in which the first left-half clutch (15) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the second pawl (20) is in an engaged state with the first auxiliary left-half clutch (22) in the initial position, in which the first auxiliary left-half clutch (22) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the first pawl (11) is in a disengaged state with the first left-half clutch (15), in which the first left-half clutch (15) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23), and/or in which the first pawl (11) is in a disengaged state with the first auxiliary left-half clutch (22), The first auxiliary left half clutch (22) can rotate in the reverse rotation or forward rotation direction relative to the first intermediate clutch (23), and/or the first right half clutch (16) can rotate in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23) when the second pawl (20) and the first right half clutch (16) are in a separated state, and/or the first auxiliary left half clutch (22) can rotate in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23) when the second pawl (20) and the first auxiliary left half clutch (22) are in a separated state, and/or the third pawl (29) is in an engaged state with the first right half clutch (16) at an initial position, and the first right half clutch (16) is fixed in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in the forward or reverse direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first right half clutch (16) at an initial position, when the first right half clutch (16) is fixed in a one-way manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in a disengaged state with the first right half clutch (16), The first right half clutch (16) can rotate in a reverse or forward direction relative to the first intermediate clutch (23), and/or the first auxiliary right half clutch (17) can rotate in a reverse or forward direction relative to the first intermediate clutch (23) when the third pawl (29) and the first auxiliary right half clutch (17) are in a separated state, and/or the first right half clutch (16) can rotate in a forward or reverse direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first right half clutch (16) are in a separated state, and/or the first auxiliary right half clutch (17) can rotate in a forward or reverse direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first auxiliary right half clutch (17) are in a separated state, the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) and the first shift cam (25) and the first intermediate clutch (23) are at least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) and the second pawl (20), and the third pawl (29) and the fourth pawl (31) are at least configured with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) comprising at least one pawl, the first pawl (11) being directly or indirectly connected with the first intermediate clutch (23), the first pawl (11) rotating together with the first intermediate clutch (23), the first pawl (11) being rotatable within an angular range relative to the first intermediate clutch (23), and/or the first pawl (11) is directly or indirectly connected to the first left clutch support (5), the first pawl (11) rotates together with the first left clutch support (5), the first pawl (11) is rotatable relative to the first left clutch support (5) within a certain angular range, the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first intermediate clutch (23), the second pawl (20) rotates together with the first intermediate clutch (23), the second pawl (20) is rotatable relative to the first intermediate clutch (23) within a certain angular range, and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) rotates together with the first left clutch support (5), Said second pawl (20) being rotatable within an angular range relative to said first left clutch support (5), said third pawl (29) comprising at least one pawl, said third pawl (29) being directly or indirectly connected to said first intermediate clutch (23), said third pawl (29) rotating with said first intermediate clutch (23), said third pawl (29) being rotatable within an angular range relative to said first intermediate clutch (23), and/or said third pawl (29) being directly or indirectly connected to said first right clutch support (6), said third pawl (29) rotating with said first right clutch support (6), said third pawl (29) rotating within an angular range relative to said first right clutch support (6), said fourth pawl (31) comprising at least one pawl, said fourth pawl (31) being directly or indirectly connected to said first intermediate clutch (23), said fourth pawl (31) being rotatable with said first intermediate clutch (23), said fourth pawl (31) being rotatable within an angular range relative to said first intermediate clutch (23), and/or said fourth pawl (31) being directly or indirectly connected to said first right clutch bracket (6), said fourth pawl (31) being rotatable with said first right clutch bracket (6), said fourth pawl (31) being rotatable within an angular range relative to said first right clutch bracket (6), said first return spring (4) comprising at least one spring, said first return spring (4) being directly or indirectly connected to said first intermediate clutch (23) and rotatable with said first intermediate clutch (23), said second return spring (21) comprising at least one spring, the second return spring (21) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the third return spring (30) comprises at least one spring, the third return spring (30) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the fourth return spring (32) comprises at least one spring, the fourth return spring (32) is directly or indirectly connected to the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected to the first pawl (11), and when other constraints or loads act on the first pawl (11) less than the first return spring (4) does on the first pawl (11), The first pawl (11) returns to the initial position under the action of the spring force of the first return spring (4), and/or the second return spring (21) is directly or indirectly connected to the second pawl (20), the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), and/or the third return spring (30) is directly or indirectly connected to the third pawl (29), the third pawl (29) returns to the initial position under the action of the spring force of the third return spring (30) when the action of other restraint or load on the third pawl (29) is smaller than the action of the third return spring (30) on the third pawl (29), and/or the fourth return spring (32) is directly or indirectly connected with the fourth pawl (31), when the action of other restraint or load on the fourth pawl (31) is smaller than the action of the fourth return spring (32) on the fourth pawl (31), the fourth pawl (31) restores the initial position under the action of the elastic force of the fourth return spring (32), when the first pawl (11) is engaged with the first left half clutch (15), the first left half clutch (15) is fixed in a single direction in the positive rotation or the reverse rotation direction relative to the first intermediate clutch (23) within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary left half clutch (22), the first auxiliary left half clutch (22) is fixed in a single direction in the positive rotation or the reverse rotation direction relative to the first intermediate clutch (23) within a certain load range, and/or the first left-hand clutch half (15) is fixed unidirectionally in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the second pawl (20) is engaged with the first left-hand clutch half (15), and/or the first auxiliary left-hand clutch half (22) is fixed unidirectionally in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the second pawl (20) is engaged with the first auxiliary left-hand clutch half (22), and/or the first left-hand clutch half (15) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the first pawl (11) is disengaged from the first left-hand clutch half (15), and/or the first pawl (11) is disengaged from the first auxiliary left-hand clutch half (22), The first auxiliary left-half clutch (22) being rotatable in the reverse or forward direction relative to the first intermediate clutch (23) over a load range and/or the first left-half clutch (15) being rotatable in the forward or reverse direction relative to the first intermediate clutch (23) over a load range when the second pawl (20) is disengaged from the first left-half clutch (15) and/or the first auxiliary left-half clutch (22) being rotatable in the forward or reverse direction relative to the first intermediate clutch (23) over a load range when the second pawl (20) is disengaged from the first auxiliary left-half clutch (22) and/or the first right-half clutch (16) being fixed in one direction relative to the first intermediate clutch (23) in the forward or reverse direction over a load range when the third pawl (29) is engaged with the first right-half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is engaged with the first auxiliary right half clutch (17), and/or the third pawl (29) is disengaged from the first auxiliary right half clutch (16), The first right partial clutch (16) can be rotated in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or the first auxiliary right partial clutch (17) can be rotated in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is disengaged from the first auxiliary right partial clutch (17), and/or the first right partial clutch (16) can be rotated in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first right partial clutch (16), and/or the first auxiliary right partial clutch (17) can be rotated in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first auxiliary right partial clutch (17), the contact pair of the first pawl (11) and the first left half clutch (15) has the function of overload protection when the first pawl (11) and the first left half clutch (15) are in an engaged state, the first pawl (11) and the first left half clutch (15) are automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is excessive, and/or the contact pair of the first pawl (11) and the first left half clutch (15) has the function of self-locking when the acting force between the first pawl (11) and the first left half clutch (15) is large, the contact pair of the first pawl (11) and the first left half clutch (15) is not automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is engaged The contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function in a state, the first pawl (11) and the first auxiliary left half clutch (22) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the second pawl (20) and the first left half clutch (15) are engaged, The contact pair of the second pawl (20) and the first left half clutch (15) has an overload protection function, the second pawl (20) and the first left half clutch (15) are automatically disengaged when the acting force between the second pawl (20) and the first left half clutch (15) is excessive, and/or the contact pair of the second pawl (20) and the first left half clutch (15) has a self-locking function when the acting force between the second pawl (20) and the first left half clutch (15) is in an engaged state, the contact pair of the second pawl (20) and the first left half clutch (15) is not automatically disengaged when the acting force between the second pawl (20) and the first left half clutch (15) is large, and/or the second pawl (20) and the first auxiliary left half clutch (22) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary left half clutch (22) has the function of overload protection, the second pawl (20) and the first auxiliary left half clutch (22) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the second pawl (20) and the first auxiliary left half clutch (22) has the function of self-locking when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is large, the contact pair of the second pawl (20) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the third pawl (29) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is in an engaged state, The contact pair of the third pawl (29) and the first right half clutch (16) has an overload protection function, the third pawl (29) and the first right half clutch (16) are automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is overlarge, and/or the contact pair of the third pawl (29) and the first right half clutch (16) has a self-locking function when the third pawl (29) and the first right half clutch (16) are in an engaged state, the contact pair of the third pawl (29) and the first right half clutch (16) is not automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is large, and/or the third pawl (29) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has an overload protection function, the third pawl (29) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has a self-locking function when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is large, the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is large, and/or the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (16) is engaged, The contact pair of the fourth pawl (31) and the first right half clutch (16) has an overload protection function, the fourth pawl (31) and the first right half clutch (16) are automatically disengaged when the acting force between the fourth pawl (31) and the first right half clutch (16) is overlarge, and/or the contact pair of the fourth pawl (31) and the first right half clutch (16) has a self-locking function when the fourth pawl (31) and the first right half clutch (16) are in an engaged state, the contact pair of the fourth pawl (31) and the first right half clutch (16) is not automatically disengaged when the acting force between the fourth pawl (31) and the first right half clutch (16) is large, and/or the fourth pawl (31) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has an overload protection function, the fourth pawl (31) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary right half clutch (17) is too large, and/or the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has a self-locking function when the fourth pawl (31) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary right half clutch (17) is large, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), and/or the first shifting sleeve (18) is directly or indirectly connected with the first left clutch support (5) and rotates with the first left clutch support (5), and/or the first left clutch support (5) has a certain limiting effect on the first shifting sleeve (18) in the axial direction, and the first shifting sleeve (18) overcomes the effect of the first left clutch support (5) in the axial direction -the first left clutch carrier (5) is selectively moved, and/or-at least the first left clutch carrier (5) is provided with a series of axial detents or projections, the first shift sleeve (18) is at least configured to function in axial positioning to the first left clutch carrier (5) within a certain range via the series of axial detents or projections, and/or-the first shift sleeve (18) is directly or indirectly connected to the first right clutch carrier (6) and rotates with the first right clutch carrier (6), and/or-the first right clutch carrier (6) has a certain limiting effect on the first shift sleeve (18) in axial direction, -the first shift sleeve (18) is selectively moved in axial direction relative to the first right clutch carrier (6) against the effect of the first right clutch carrier (6), and/or the first right clutch support (6) is at least provided with a series of axial positioning grooves or bulges, the first shifting gear sleeve (18) is at least configured to perform the function of axial positioning relative to the first right clutch support (6) through the series of axial positioning grooves or bulges within a certain range, and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch support (5), the first positioning mechanism (19) rotates together with the first left clutch support (5), the first positioning mechanism (19) is axially fixed relative to the first left clutch support (5), and/or the first positioning mechanism (19) is directly or indirectly connected with the first right clutch support (6), and the first positioning mechanism (19) rotates together with the first right clutch support (6), The first positioning means (19) being axially fixed relative to the first right clutch carrier (6), and/or the first positioning means (19) being directly or indirectly connected to the first shift sleeve (18) and the first positioning means (19) having a limiting effect in the axial direction on the first shift sleeve (18), the first shift sleeve (18) being axially selectively movable relative to the first left clutch half (15) against the effect of the first positioning means (19), and/or the first shift sleeve (18) being provided with a series of axial positioning grooves or projections, the first shift sleeve (18) being configured at least to position at least one of its axial positions by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first drive pin (26) is directly or indirectly connected to the first shift sleeve (18) and the first drive pin (26) rotates together with the first shift sleeve (18), and/or the first drive pin (26) is directly or indirectly connected to the first shift cam (25), the first drive pin (26) being at least configured to push the first shift cam (25) to rotate within an angular range relative to the first left clutch half (15) within an axial range, and/or the first shift cam (25) is directly or indirectly connected to the first left clutch half (15), the first shift cam (25) being at least configured to rotate relative to the first left clutch half (15) within an angular range under the action of the first drive pin (26), and/or the first shift cam (25) is directly or indirectly connected to the first left clutch support (5) and the first shift cam (25) is at least designed to be rotatable relative to the first left clutch support (5) within a certain angle range under the action of the first drive pin (26), and/or the first shift cam (25) is directly or indirectly connected to the first right clutch support (6) and the first shift cam (25) is at least designed to be rotatable relative to the first right clutch support (6) within a certain angle range under the action of the first drive pin (26), and/or the first shift cam (25) is directly or indirectly connected to the first pawl (11) and the rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angle range directly or indirectly makes the first pawl (11) to be in clutch engagement with the first left half (15) Is in an engaged or disengaged state, and/or the first shift sleeve (18) is directly or indirectly connected to the first pawl (11) and the first shift cam (25) is in a range of rotation relative to the first intermediate clutch (23) directly or indirectly bringing the first pawl (11) into an engaged or disengaged state with the first auxiliary left half clutch (22), and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the first shift cam (25) is in a range of rotation relative to the first intermediate clutch (23) directly or indirectly bringing the second pawl (20) into an engaged or disengaged state with the first left half clutch (15), and/or the first shift sleeve (18) is directly or indirectly connected to the second pawl (20) and the first shift cam (25) is in a range of rotation relative to the first intermediate clutch (23) The second pawl (20) is directly or indirectly engaged or disengaged with the first auxiliary left clutch half (22) and/or the first shift cam (25) is directly or indirectly connected with the third pawl (29) and the first shift cam (25) is directly or indirectly engaged or disengaged with the third pawl (29) and the first right clutch half (16) within a certain range of rotation relative to the first intermediate clutch (23), and/or the first shift cam (25) is directly or indirectly connected with the third pawl (29) and the first shift cam (25) is directly or indirectly engaged or disengaged with the third pawl (29) and the first intermediate clutch half (23) within a certain range of rotation relative to the first intermediate clutch (25) directly or indirectly engages or disengages the third pawl (29) and the first auxiliary right clutch half (17) and/or the first shift cam (25) is directly or indirectly connected with the fourth pawl (31), And the rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain range directly or indirectly enables the fourth pawl (31) and the first right half clutch (16) to be in an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected with the fourth pawl (31), and the rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain range directly or indirectly enables the fourth pawl (31) and the first auxiliary right half clutch (17) to be in an engaged or disengaged state, and/or the first shift gear sleeve (18) is sequentially connected with the first transmission pin (26), the first shift cam (25) is connected with the first pawl (11), and the axial movement of the first shift gear sleeve (18) is sequentially connected with the first transmission pin (26), the first right half clutch (17), The first gear shifting cam (25) enables the first pawl (11) and the first left half clutch (15) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) is connected with the first pawl (11) through the first transmission pin (26) and the first gear shifting cam (25) in sequence, and axial movement of the first gear shifting sleeve (18) enables the first pawl (11) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state through the first transmission pin (26) in sequence, the first gear shifting cam (25) enables the first pawl (11) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) is connected with the second pawl (20) through the first transmission pin (26) in sequence, and axial movement of the first gear shifting sleeve (18) is connected through the first transmission pin (26) in sequence, The first gear shifting cam (25) enables the second pawl (20) and the first left half clutch (15) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) is connected with the second pawl (20) through the first transmission pin (26) and the first gear shifting cam (25) in sequence, and axial movement of the first gear shifting sleeve (18) enables the second pawl (20) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state through the first transmission pin (26) in sequence, the first gear shifting cam (25) enables the second pawl (20) and the first auxiliary left half clutch (22) to be in an engaged or disengaged state through the first transmission pin (26) in sequence, and/or the first gear shifting sleeve (18) is connected with the third pawl (29) through the first transmission pin (26) in sequence, and axial movement of the first gear shifting sleeve (18) is connected with the first gear shifting cam (25) in sequence through the first transmission pin (26), The first gear shifting cam (25) enables the third pawl (29) and the first right half clutch (16) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) sequentially passes through the first transmission pin (26), the first gear shifting cam (25) is connected with the third pawl (29), and the axial movement of the first gear shifting sleeve (18) sequentially passes through the first transmission pin (26), the first gear shifting cam (25) enables the third pawl (29) and the first auxiliary right half clutch (17) to be in an engaged or disengaged state, and/or the first gear shifting sleeve (18) sequentially passes through the first transmission pin (26), the first gear shifting cam (25) is connected with the fourth pawl (31), and the axial movement of the first gear shifting sleeve (18) sequentially passes through the first transmission pin (26), the first gear shifting cam (25) and the fourth pawl (31), The first shift cam (25) brings the fourth pawl (31) into engagement or disengagement with the first right half clutch (16), and/or the first shift sleeve (18) is connected to the fourth pawl (31) via the first transmission pin (26) in that order, and the first shift cam (25) is connected to the fourth pawl (31), and axial movement of the first shift sleeve (18) is brought into engagement or disengagement with the first auxiliary right half clutch (17) via the first transmission pin (26) in that order, and the first shift cam (25) is connected directly or indirectly to the actuating device (AM), and the first shift sleeve (18) is selectively moved axially within a certain range relative to the first intermediate clutch (23) under drive of the actuating device (AM), and/or when the first shift sleeve (18) is in an intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first left-half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left-half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right-half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right-half clutch (16), and/or when the first shift sleeve (18) is in a position axially close to the first left-half clutch (15) directly or indirectly under the action of the actuating device (AM), the first pawl (11) is in an engaged or disengaged state with the first left-half clutch (15), The second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16) when the first shift sleeve (18) is axially located at a position close to the first right half clutch (16) directly or indirectly under the action of the actuating device (AM), and/or the first limit pin (13) comprises at least one pin, and/or the second limit pin (24) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary left half clutch (22) at least has the function of rotating a certain angle relative to the first left half clutch (15), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), And under the action of the first pawl (11) or the second pawl (20), the first auxiliary left half clutch (22) has at least the function of rotating relative to the first left half clutch (15) within the angle range defined by the first limit pin (13), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the action of the third pawl (29) or the fourth pawl (31), the first auxiliary right half clutch (17) has at least the function of rotating relative to the first right half clutch (16) for a certain angle, and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), and under the action of the third pawl (29) or the fourth pawl (31), The first auxiliary right half clutch (17) at least has the function of rotating relative to the first right half clutch (16) within the angle range limited by the second limit pin (24), and/or the first auxiliary left half clutch (22) is coaxially arranged on one side of the first left half clutch (15) in the radial direction, and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or positively relative to the first intermediate clutch (23), under the direct or indirect action of the first pawl (11), after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), or after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15) and the first limit pin (13), A partial surface of the first auxiliary left half clutch (22) and a partial surface of the first left half clutch (15) are radially combined to form a plane, the first pawl (11) is in contact with the combined plane when rotating relative to the first intermediate clutch (23) so as to greatly reduce noise, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first intermediate clutch (23), the partial surface of the first auxiliary left half clutch (22) and the partial surface of the first left half clutch (15) are radially combined to form a plane after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15) under the direct or indirect action of the second pawl (20), or the partial surface of the first auxiliary left half clutch (22) rotates to an angle defined by the first limit pin (13) relative to the first left half clutch (15), The second pawl (20) is in contact with the split plane when rotating relative to the first intermediate clutch (23) so as to greatly reduce noise, and/or when the first right half clutch (16) rotates reversely or forwardly relative to the first intermediate clutch (23), under the direct or indirect action of the third pawl (29), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, so that the third pawl (29) is in contact with the split plane when rotating relative to the first intermediate clutch (23), Thereby greatly reducing noise, and/or when the first right half clutch (16) rotates forwards or backwards relative to the first intermediate clutch (23), under the direct or indirect action of the fourth pawl (31), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially split into a plane, so that the fourth pawl (31) contacts with the split plane when rotating relative to the first intermediate clutch (23), thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: a first return spring (4), and/or a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), a first shift cam (25), the first left half clutch (15), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary right half clutch (17), and/or the first positioning mechanism (19), the first shift cam (25) and the first right half clutch (16) being arranged coaxially, and/or the first return spring (4), and/or the first left clutch carrier (5), and/or the first right clutch carrier (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), the first left clutch half (15), and/or the first auxiliary right clutch half (17), the first shift sleeve (18), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), the first shift cam (25) is arranged axially on one side of the first right clutch half (16), and/or the first left clutch half (15) coaxially passes through the first right clutch half (16), or the first right clutch half (16) coaxially passes through the first left clutch half (15), the first left half clutch (15) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first left half clutch (15) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with a driving part of the machine (M) and rotates along with a driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M), and the first pawl (11) is in an engaged state with the first right half clutch (16) at an initial position, The first right half clutch (16) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first left half clutch (15) at the moment, and/or the first pawl (11) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, the first auxiliary right half clutch (17) is fixed in a one-way mode in the forward or reverse rotation direction relative to the first left half clutch (15) at the moment, and/or the second pawl (20) is in an engaged state with the first right half clutch (16) at an initial position, the first right half clutch (16) is fixed in a one-way mode in the reverse or forward rotation direction relative to the first left half clutch (15) at the moment, and/or the second pawl (20) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, and the first auxiliary right half clutch (17) is fixed in a one-way in the reverse or forward rotation direction relative to the first left half clutch (15) at the moment, and/or the first pawl (11) is in a disengaged state with the first right half clutch (16) in an initial position, the first right half clutch (16) can rotate in the reverse rotation or forward rotation direction relative to the first left half clutch (15), and/or the first pawl (11) is in a disengaged state with the first auxiliary right half clutch (17) in an initial position, the first auxiliary right half clutch (17) can rotate in the reverse rotation or forward rotation direction relative to the first left half clutch (15), and/or the second pawl (20) is in a disengaged state with the first right half clutch (16) in an initial position, the first right half clutch (16) can rotate in the forward rotation or reverse rotation direction relative to the first left half clutch (15), and/or the second pawl (20) is in a disengaged state with the first auxiliary right half clutch (17) in an initial position, The first auxiliary right half clutch (17) can rotate in the forward or reverse direction relative to the first left half clutch (15), the first left half clutch (15) and the first right half clutch (16) and the first auxiliary right half clutch (17) and the first shift cam (25) are at least provided with ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) and the second pawl (20) are at least provided with the function of engaging with or disengaging from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first left half clutch (15), the first pawl (11) can rotate relative to the first left half clutch (15) in a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), The first pawl (11) can rotate relative to the first right clutch bracket (6) within a certain angle range, the second pawl (20) at least comprises one pawl, the second pawl (20) is directly or indirectly connected with the first left clutch half (15), the second pawl (20) can rotate relative to the first left clutch half (15) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected with the first right clutch bracket (6), the second pawl (20) can rotate relative to the first right clutch bracket (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly fixedly connected with the first left clutch half (15), the first return spring (4) is directly or indirectly connected with the first pawl (11), When the action of other restraint or load on the first pawl (11) is smaller than the elastic action of the first return spring (4) on the first pawl (11), the first pawl (11) restores to the initial position under the elastic action of the first return spring (4), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly fixedly connected with the first left half clutch (15), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the elastic action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the elastic action of the second return spring (21), and when the first pawl (11) is connected with the first right half clutch (16), The first right half clutch (16) is fixed in one way relative to the first left half clutch (15) in the forward or reverse direction within a certain load range, and/or the first auxiliary right half clutch (17) is fixed in one way relative to the first left half clutch (15) in the forward or reverse direction within a certain load range when the first pawl (11) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is fixed in one way relative to the first left half clutch (15) in the reverse or forward direction within a certain load range when the second pawl (20) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in one way relative to the first left half clutch (15) in the reverse or forward direction within a certain load range when the second pawl (20) is engaged with the first auxiliary right half clutch (17), and/or when the first pawl (11) and the second pawl (20) are engaged with the first right half clutch (16), within a certain load range, the first right half clutch (16) is fixed in both the forward and reverse directions relative to the first left half clutch (15), and/or when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary right half clutch (17), within a certain load range, the first auxiliary right half clutch (17) is fixed in both the forward and reverse directions relative to the first left half clutch (15), and/or when the first pawl (11) is engaged with the first right half clutch (16) and the second pawl (20) is disengaged from the first right half clutch (16), within a certain load range, the first right half clutch (16) is fixed in either the forward or reverse direction relative to the first left half clutch (15) and is fixable in either the forward or reverse direction and in either the forward or reverse direction relative to the first left half clutch (15) -an upper rotation, and/or-when the first pawl (11) is engaged with the first auxiliary right half clutch (17) and the second pawl (20) is disengaged from the first auxiliary right half clutch (17), within a certain load range-the first auxiliary right half clutch (17) is fixed in the forward or reverse direction relative to the first left half clutch (15) and rotatable in the reverse or forward direction, and/or-when the first pawl (11) is disengaged from the first right half clutch (16) and the second pawl (20) is engaged with the first right half clutch (16), within a certain load range-the first right half clutch (16) is fixed in the reverse or reverse direction relative to the first left half clutch (15) and rotatable in the forward or reverse direction, and/or-when the first pawl (11) is disengaged from the first auxiliary right half clutch (17) and the second pawl (20) is disengaged from the first auxiliary right half clutch (16), (17) and/or rotatable in the reverse direction, and/or vice versa, and/or-when the first pawl (11) is disengaged from the first auxiliary right half clutch (16) 17) When engaged, the first auxiliary right half clutch (17) is fixed in the reverse rotation or forward rotation direction relative to the first left half clutch (15) and rotatable in the forward rotation or reverse rotation direction, and/or the first right half clutch (16) is rotatable in both the forward rotation and reverse rotation directions relative to the first left half clutch (15) in a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first right half clutch (16), and/or the first auxiliary right half clutch (17) is rotatable in both the forward rotation and reverse rotation directions relative to the first left half clutch (15) in a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary right half clutch (17), and the first auxiliary right half clutch (17) is rotatable in both the forward rotation and reverse rotation directions relative to the first left half clutch (15) when the first pawl (11) and the first left half clutch (16) are engaged, The contact pair of the first pawl (11) and the first right half clutch (16) has an overload protection function, the first pawl (11) and the first right half clutch (16) are automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is overlarge, and/or the contact pair of the first pawl (11) and the first right half clutch (16) has a self-locking function when the first pawl (11) and the first right half clutch (16) are in an engaged state, the contact pair of the first pawl (11) and the first right half clutch (16) are not automatically disengaged when the acting force between the first pawl (11) and the first right half clutch (16) is large, and/or the contact pair of the first pawl (11) and the first right half clutch (16) are not automatically disengaged when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has an overload protection function, the first pawl (11) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is overlarge, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) has a self-locking function when the first pawl (11) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary right half clutch (17) is large, and/or the contact pair of the first pawl (11) and the first auxiliary right half clutch (17) is not automatically disengaged when the second pawl (20) and the first right half clutch (16) are in an engaged state, The contact pair of the second pawl (20) and the first right half clutch (16) has an overload protection function, the second pawl (20) and the first right half clutch (16) are automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is overlarge, and/or the contact pair of the second pawl (20) and the first right half clutch (16) has a self-locking function when the second pawl (20) and the first right half clutch (16) are in an engaged state, the contact pair of the second pawl (20) and the first right half clutch (16) is not automatically disengaged when the acting force between the second pawl (20) and the first right half clutch (16) is large, and/or the second pawl (20) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the function of overload protection, the second pawl (20) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is overlarge, and/or the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) has the self-locking function when the second pawl (20) and the first auxiliary right half clutch (17) are in the engaged state, the contact pair of the second pawl (20) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the second pawl (20) and the first auxiliary right half clutch (17) is large, and/or the first left clutch bracket (5) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first left half clutch (15) through the first clutch rivet (7), and/or the first shift cam (25) is directly or indirectly connected with the first left half clutch (15) and rotates together with the first left half clutch (15), and/or the first left half clutch (15) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, The first shift cam (25) is selectively rotatable in an angular range relative to the first left clutch half (15) against the action of the first left clutch half (15), and/or at least a series of detents or projections are formed on the first left clutch half (15), the first shift cam (25) is at least configured to be angularly positionable in a rotational direction relative to the first left clutch half (15) in a range by means of the series of detents or projections, and/or the first shift cam (25) is directly or indirectly connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), and/or the first left clutch carrier (5) has an angular limiting action in the rotational direction on the first shift cam (25), and the first shift cam (25) is rotatable relative to the first left clutch carrier (5) against the action of the first left clutch carrier (5) The clutch support (5) is selectively rotatable within a certain angle range, and/or the first left clutch support (5) is at least provided with a series of positioning grooves or protrusions, the first shift cam (25) is at least configured to have a function of angular positioning in a certain range in a rotating direction relative to the first left clutch support (5) through the series of positioning grooves or protrusions, and/or the first shift cam (25) is directly or indirectly connected with the first right clutch support (6) and rotates together with the first right clutch support (6), and/or the first right clutch support (6) has a certain angle limiting effect in the rotating direction on the first shift cam (25), and the first shift cam (25) is selectively rotatable within a certain angle range relative to the first right clutch support (6) against the effect of the first right clutch support (6), and/or the first right clutch support (6) is provided with at least one series of positioning grooves or projections, the first shift cam (25) is provided with at least one function of angular positioning in a rotation direction relative to the first right clutch support (6) within a certain range via the series of positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected with the first left clutch half (15), the first positioning means (19) rotates together with the first left clutch half (15), and/or the first positioning means (19) is directly or indirectly connected with the first left clutch support (5), the first positioning means (19) rotates together with the first left clutch support (5), and/or the first positioning means (19) is directly or indirectly connected with the first right clutch support (6), The first positioning means (19) rotates together with the first right clutch carrier (6) and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25) and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable over an angular range relative to the first left clutch half (15) against the effect of the first positioning means (19), and/or a series of positioning grooves or projections are provided on the first shift cam (25), the first shift cam (25) is at least configured to perform an angular positioning function in the direction of rotation relative to the first positioning means (19) over a range by means of the series of positioning grooves or projections, and/or the first shift cam (25) is directly or indirectly connected to the first pawl (11) And rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the first pawl (11) and the first right half clutch (16) into an engaged or disengaged state, and/or rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the first pawl (11) and the first auxiliary right half clutch (17) into an engaged or disengaged state, and/or rotation of the first shift cam (25) relative to the first left half clutch (15) within a certain range directly or indirectly brings the second pawl (20) and the first right half clutch (16) into an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected to the second pawl (20) and the rotation of the first shift cam (25) relative to the first left half-clutch (15) within a certain range directly or indirectly brings the second pawl (20) into engagement or disengagement with the first auxiliary right half-clutch (17), and/or the first shift cam (25) is directly or indirectly connected to the actuating device (AM) and the first shift cam (25) is selectively rotated relative to the first left half-clutch (15) within a certain angular range under the drive of the actuating device (AM), and/or the first pawl (11) is brought into engagement or disengagement with the first right half-clutch (16) when the first shift cam (25) is brought into an angular intermediate position in the rotational direction under the action of the actuating device (AM) directly or indirectly, The second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), and/or the first pawl (11) is in an engaged or disengaged state with the first right half clutch (16), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (20), the second pawl (20) is in an engaged or disengaged state with the first right half clutch (16), the first shift cam (25) is directly or indirectly in another side in the rotational direction with the actuating device (AM), the second shift cam (25) is in an engaged or disengaged state with the first right half clutch (16), and/or the first limit pin (13) at least comprises one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary right half clutch (17) at least has the function of rotating the first auxiliary right half clutch (16) within the angle range limited by the first limit pin (13) ) A rotation function, and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first right half clutch (16), under the direct or indirect action of the first pawl (11), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle limited by the first limit pin (13) relative to the first right half clutch (16), a partial surface of the first auxiliary right half clutch (17) and a partial surface of the first right half clutch (16) are radially combined into a plane, and when the first pawl (11) rotates relative to the first right half clutch (16), the partial surface of the first auxiliary right half clutch (17) and the partial surface of the first right half clutch (16) are in contact, Thereby greatly reducing noise, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first right half clutch (16), under the direct or indirect action of the second pawl (20), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to an angle defined by the first limit pin (13) relative to the first right half clutch (16), part of the surface of the first auxiliary right half clutch (17) and part of the surface of the first right half clutch (16) are radially combined into a plane, and the second pawl (20) rotates relative to the first right half clutch (16) and contacts with the combined plane, thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: a first return spring (4), and/or a first left clutch bracket (5), and/or a first right clutch bracket (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), a first left half clutch (15), a first right half clutch (16), and/or a first auxiliary right half clutch (17), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), and/or a first auxiliary left half clutch (22), a first intermediate clutch (23), and/or a second limit pin (24), a first shift cam (25), a third pawl (29), a third return spring (30), and/or a fourth pawl (31), and/or a fourth return spring (32), the first left half clutch (15) and/or the first left clutch support (5) and/or the first right clutch support (6), the first right half clutch (16) and/or the first auxiliary right half clutch (17) and/or the first positioning mechanism (19) and/or the first auxiliary left half clutch (22), the first shift cam (25) and the first intermediate clutch (23) are coaxially arranged, and the first return spring (4) and/or the first left clutch support (5) and/or the first right clutch support (6) and/or the first clutch rivet (7), the first pawl (11) and/or the first limit pin (13), the first left half clutch (15) and/or the first auxiliary right half clutch (17), And/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the first auxiliary left-half clutch (22), the first intermediate clutch (23), and/or the second limit pin (24), the first shift cam (25), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32) are arranged axially on one side of the first right-half clutch (16), and/or the first intermediate clutch (23) passes coaxially through the first left-half clutch (15), or the first intermediate clutch (23) passes coaxially through the first right-half clutch (16), and/or the first left-half clutch (15) passes coaxially through the first right-half clutch (16), or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left half clutch (15) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left half clutch (15) is directly or indirectly connected with the driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first intermediate clutch (23) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engaged state with the first left half clutch (15) at an initial position, the first left half clutch (15) is fixed in a one-way manner in a forward or reverse direction relative to the first intermediate clutch (23), and/or the first pawl (11) is in an engaged state with the first auxiliary left half clutch (22) at an initial position, the first auxiliary left half clutch (22) is fixed in a forward or reverse direction relative to the first intermediate clutch (23), and/or the first auxiliary left half clutch (22) is in an engaged state in a forward or reverse direction relative to the first intermediate clutch (23) The first pawl (20) is fixed in a one-way manner in the rotating direction in an initial position and the first left half clutch (15) is in an engaged state, the first left half clutch (15) is fixed in a one-way manner in the reverse or forward rotating direction relative to the first intermediate clutch (23) in the initial position, the second pawl (20) is in an engaged state with the first auxiliary left half clutch (22) in the initial position, the first auxiliary left half clutch (22) is fixed in a one-way manner in the reverse or forward rotating direction relative to the first intermediate clutch (23), the first pawl (11) is fixed in a one-way manner in the reverse or forward rotating direction relative to the first intermediate clutch (23) in the initial position, and/or the first pawl (11) is in a disengaged state with the first pawl (15) and the first auxiliary left half clutch (22), the first left half clutch (15) can rotate in the reverse or forward rotating direction relative to the first intermediate clutch (23), and/or the first pawl (11) is in a disengaged state, The first auxiliary left half clutch (22) can rotate in the reverse rotation or forward rotation direction relative to the first intermediate clutch (23), and/or the first right half clutch (16) can rotate in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23) when the second pawl (20) and the first right half clutch (16) are in a separated state, and/or the first auxiliary left half clutch (22) can rotate in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23) when the second pawl (20) and the first auxiliary left half clutch (22) are in a separated state, and/or the third pawl (29) is in an engaged state with the first right half clutch (16) at an initial position, and the first right half clutch (16) is fixed in the forward rotation or reverse rotation direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in the forward or reverse direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first right half clutch (16) at an initial position, when the first right half clutch (16) is fixed in a one-way manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the fourth pawl (31) is in an engaged state with the first auxiliary right half clutch (17) at an initial position, when the first auxiliary right half clutch (17) is fixed in a one-way manner in the reverse or forward direction relative to the first intermediate clutch (23), and/or the third pawl (29) is in a disengaged state with the first right half clutch (16), The first right half clutch (16) can rotate in a reverse or forward direction relative to the first intermediate clutch (23), and/or the first auxiliary right half clutch (17) can rotate in a reverse or forward direction relative to the first intermediate clutch (23) when the third pawl (29) and the first auxiliary right half clutch (17) are in a separated state, and/or the first right half clutch (16) can rotate in a forward or reverse direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first right half clutch (16) are in a separated state, and/or the first auxiliary right half clutch (17) can rotate in a forward or reverse direction relative to the first intermediate clutch (23) when the fourth pawl (31) and the first auxiliary right half clutch (17) are in a separated state, the first left half clutch (15) and the first right half clutch (16) and the first auxiliary left half clutch (22) and the first auxiliary right half clutch (17) and the first shift cam (25) and the first intermediate clutch (23) are at least configured with ratchet-like projections and/or ratchet-like recesses, and the first pawl (11) and the second pawl (20) and the third pawl (29) and the fourth pawl (31) are at least configured with a function of engaging with or disengaging from the ratchet-like projections and/or ratchet-like recesses, the first pawl (11) comprising at least one pawl, the first pawl (11) being directly or indirectly connected with the first intermediate clutch (23), the first pawl (11) being rotatable within a certain angular range relative to the first intermediate clutch (23), and/or the first pawl (11) is directly or indirectly connected to the first left clutch support (5), the first pawl (11) is rotatable within an angular range relative to the first left clutch support (5), the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected to the first intermediate clutch (23), the second pawl (20) is rotatable within an angular range relative to the first intermediate clutch (23), and/or the second pawl (20) is directly or indirectly connected to the first left clutch support (5), the second pawl (20) is rotatable within an angular range relative to the first left clutch support (5), the third pawl (29) comprises at least one pawl, the third pawl (29) is directly or indirectly connected to the first intermediate clutch (23), Said third pawl (29) being rotatable within an angular range relative to said first intermediate clutch (23) and/or said third pawl (29) being directly or indirectly connected to said first right clutch support (6), said third pawl (29) being rotatable within an angular range relative to said first right clutch support (6), said fourth pawl (31) comprising at least one pawl, said fourth pawl (31) being directly or indirectly connected to said first intermediate clutch (23), said fourth pawl (31) being rotatable within an angular range relative to said first intermediate clutch (23), and/or said fourth pawl (31) being directly or indirectly connected to said first right clutch support (6), said fourth pawl (31) being rotatable within an angular range relative to said first right clutch support (6), said first return spring (4) comprising at least one spring, the first return spring (4) is directly or indirectly fixedly connected with the first intermediate clutch (23), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly fixedly connected with the first intermediate clutch (23), the third return spring (30) at least comprises one spring, the third return spring (30) is directly or indirectly fixedly connected with the first intermediate clutch (23), the fourth return spring (32) at least comprises one spring, the fourth return spring (32) is directly or indirectly fixedly connected with the first intermediate clutch (23), the first return spring (4) is directly or indirectly connected with the first pawl (11), and when the action of other constraint or load on the first pawl (11) is smaller than the action of the first return spring (4) on the first pawl (11), the second return spring (4) is connected with the first pawl (11), The first pawl (11) returns to the initial position under the action of the spring force of the first return spring (4), the second return spring (21) is directly or indirectly connected with the second pawl (20), the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other restraint or load on the second pawl (20) is smaller than the action of the second return spring (21) on the second pawl (20), the third return spring (30) is directly or indirectly connected with the third pawl (29), and the third pawl (29) returns to the initial position under the action of the spring force of the third return spring (30) when the action of other restraint or load on the third pawl (29) is smaller than the action of the third return spring (30) on the third pawl (29), the fourth return spring (32) is directly or indirectly connected with the fourth pawl (31), when the action of other restraint or load on the fourth pawl (31) is smaller than the action of the fourth return spring (32) on the fourth pawl (31), the fourth pawl (31) restores the initial position under the elastic force of the fourth return spring (32), when the first pawl (11) is engaged with the first left half clutch (15), the first left half clutch (15) is fixed in a one-way manner in the forward or reverse rotation direction relative to the first intermediate clutch (23) within a certain load range, and/or when the first pawl (11) is engaged with the first auxiliary left half clutch (22), the first auxiliary left half clutch (22) is fixed in a one-way in the forward or reverse rotation direction relative to the first intermediate clutch (23) within a certain load range, and/or the first left-hand clutch half (15) is fixed unidirectionally in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the second pawl (20) is engaged with the first left-hand clutch half (15), and/or the first auxiliary left-hand clutch half (22) is fixed unidirectionally in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the second pawl (20) is engaged with the first auxiliary left-hand clutch half (22), and/or the first left-hand clutch half (15) is rotatable in the reverse or forward direction relative to the first intermediate clutch (23) within a load range when the first pawl (11) is disengaged from the first left-hand clutch half (15), and/or the first pawl (11) is disengaged from the first auxiliary left-hand clutch half (22), The first auxiliary left-half clutch (22) being rotatable in the reverse or forward direction relative to the first intermediate clutch (23) over a load range and/or the first left-half clutch (15) being rotatable in the forward or reverse direction relative to the first intermediate clutch (23) over a load range when the second pawl (20) is disengaged from the first left-half clutch (15) and/or the first auxiliary left-half clutch (22) being rotatable in the forward or reverse direction relative to the first intermediate clutch (23) over a load range when the second pawl (20) is disengaged from the first auxiliary left-half clutch (22) and/or the first right-half clutch (16) being fixed in one direction relative to the first intermediate clutch (23) in the forward or reverse direction over a load range when the third pawl (29) is engaged with the first right-half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is engaged with the first auxiliary right half clutch (17), and/or the first right half clutch (16) is fixed in a unidirectional manner in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is engaged with the first right half clutch (16), and/or the first auxiliary right half clutch (17) is fixed in a unidirectional manner in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is engaged with the first auxiliary right half clutch (17), and/or the third pawl (29) is disengaged from the first auxiliary right half clutch (16), The first right partial clutch (16) can be rotated in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range, and/or the first auxiliary right partial clutch (17) can be rotated in the reverse or forward direction relative to the first intermediate clutch (23) within a certain load range when the third pawl (29) is disengaged from the first auxiliary right partial clutch (17), and/or the first right partial clutch (16) can be rotated in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first right partial clutch (16), and/or the first auxiliary right partial clutch (17) can be rotated in the forward or reverse direction relative to the first intermediate clutch (23) within a certain load range when the fourth pawl (31) is disengaged from the first auxiliary right partial clutch (17), the contact pair of the first pawl (11) and the first left half clutch (15) has the function of overload protection when the first pawl (11) and the first left half clutch (15) are in an engaged state, the first pawl (11) and the first left half clutch (15) are automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is excessive, and/or the contact pair of the first pawl (11) and the first left half clutch (15) has the function of self-locking when the acting force between the first pawl (11) and the first left half clutch (15) is large, the contact pair of the first pawl (11) and the first left half clutch (15) is not automatically disengaged when the acting force between the first pawl (11) and the first left half clutch (15) is large, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is engaged The contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has an overload protection function in a state, the first pawl (11) and the first auxiliary left half clutch (22) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) has a self-locking function when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, the contact pair of the first pawl (11) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary left half clutch (22) is large, and/or the second pawl (20) and the first left half clutch (15) are engaged, The contact pair of the second pawl (20) and the first left half clutch (15) has an overload protection function, the second pawl (20) and the first left half clutch (15) are automatically disengaged when the acting force between the second pawl (20) and the first left half clutch (15) is excessive, and/or the contact pair of the second pawl (20) and the first left half clutch (15) has a self-locking function when the acting force between the second pawl (20) and the first left half clutch (15) is in an engaged state, the contact pair of the second pawl (20) and the first left half clutch (15) is not automatically disengaged when the acting force between the second pawl (20) and the first left half clutch (15) is large, and/or the second pawl (20) and the first auxiliary left half clutch (22) are in an engaged state, The contact pair of the second pawl (20) and the first auxiliary left half clutch (22) has the function of overload protection, the second pawl (20) and the first auxiliary left half clutch (22) are automatically disengaged when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is excessive, and/or the contact pair of the second pawl (20) and the first auxiliary left half clutch (22) has the function of self-locking when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is large, the contact pair of the second pawl (20) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the second pawl (20) and the first auxiliary left half clutch (22) is large, and/or the contact pair of the third pawl (29) and the first auxiliary left half clutch (22) is not automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is in an engaged state, The contact pair of the third pawl (29) and the first right half clutch (16) has an overload protection function, the third pawl (29) and the first right half clutch (16) are automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is overlarge, and/or the contact pair of the third pawl (29) and the first right half clutch (16) has a self-locking function when the third pawl (29) and the first right half clutch (16) are in an engaged state, the contact pair of the third pawl (29) and the first right half clutch (16) is not automatically disengaged when the acting force between the third pawl (29) and the first right half clutch (16) is large, and/or the third pawl (29) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has an overload protection function, the third pawl (29) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is excessive, and/or the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) has a self-locking function when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is large, the contact pair of the third pawl (29) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the third pawl (29) and the first auxiliary right half clutch (17) is large, and/or the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (16) is engaged, The contact pair of the fourth pawl (31) and the first right half clutch (16) has an overload protection function, the fourth pawl (31) and the first right half clutch (16) are automatically disengaged when the acting force between the fourth pawl (31) and the first right half clutch (16) is overlarge, and/or the contact pair of the fourth pawl (31) and the first right half clutch (16) has a self-locking function when the fourth pawl (31) and the first right half clutch (16) are in an engaged state, the contact pair of the fourth pawl (31) and the first right half clutch (16) is not automatically disengaged when the acting force between the fourth pawl (31) and the first right half clutch (16) is large, and/or the fourth pawl (31) and the first auxiliary right half clutch (17) are in an engaged state, The contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has an overload protection function, the fourth pawl (31) and the first auxiliary right half clutch (17) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary right half clutch (17) is too large, and/or the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) has a self-locking function when the fourth pawl (31) and the first auxiliary right half clutch (17) are in an engaged state, the contact pair of the fourth pawl (31) and the first auxiliary right half clutch (17) is not automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary right half clutch (17) is large, and/or the first left clutch support (5) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first intermediate clutch (23), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first left clutch support (5) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), and/or the first right clutch support (6) is fixedly connected with the first intermediate clutch (23) through the first clutch rivet (7), and/or the first shift cam (25) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a certain angle limiting effect on the first shift cam (25) in the rotation direction, The first shifting cam (25) is selectively rotatable in an angular range relative to the first intermediate clutch (23) against the action of the first intermediate clutch (23), and/or at least a series of detents or projections are formed on the first intermediate clutch (23), the first shifting cam (25) is at least configured to be angularly positionable in a rotational direction relative to the first intermediate clutch (23) in a range by means of the series of detents or projections, and/or the first shifting cam (25) is directly or indirectly connected to the first left clutch carrier (5) and rotates with the first left clutch carrier (5), and/or the first left clutch carrier (5) has an angular limiting action in the rotational direction against the first shifting cam (25), and the first shifting cam (25) is rotatable relative to the first left clutch carrier (5) against the action of the first left clutch carrier (5) The clutch support (5) is selectively rotatable within a certain angle range, and/or the first left clutch support (5) is at least provided with a series of positioning grooves or protrusions, the first shift cam (25) is at least configured to have a function of angular positioning in a certain range in a rotating direction relative to the first left clutch support (5) through the series of positioning grooves or protrusions, and/or the first shift cam (25) is directly or indirectly connected with the first right clutch support (6) and rotates together with the first right clutch support (6), and/or the first right clutch support (6) has a certain angle limiting effect in the rotating direction on the first shift cam (25), and the first shift cam (25) is selectively rotatable within a certain angle range relative to the first right clutch support (6) against the effect of the first right clutch support (6), and/or the first right clutch support (6) is provided with at least one series of positioning grooves or projections, the first shift cam (25) is provided with at least one range of angular positioning function relative to the first right clutch support (6) via the series of positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected with the first intermediate clutch (23), the first positioning means (19) rotates together with the first intermediate clutch (23), and/or the first positioning means (19) is directly or indirectly connected with the first left clutch support (5), the first positioning means (19) rotates together with the first left clutch support (5), and/or the first positioning means (19) is directly or indirectly connected with the first right clutch support (6), The first positioning means (19) rotates together with the first right clutch carrier (6) and/or the first positioning means (19) is directly or indirectly connected to the first shift cam (25) and the first positioning means (19) has an angular limiting effect on the first shift cam (25) in the direction of rotation, the first shift cam (25) is selectively rotatable over an angular range relative to the first left clutch half (15) against the effect of the first positioning means (19), and/or a series of positioning grooves or projections are provided on the first shift cam (25), the first shift cam (25) is at least configured to perform an angular positioning function in the direction of rotation relative to the first positioning means (19) over a range by means of the series of positioning grooves or projections, and/or the first shift cam (25) is directly or indirectly connected to the first pawl (11) And in that a selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the first pawl (11) into or out of engagement with the first left-hand clutch half (15), and/or in that the first shift cam (25) is directly or indirectly connected to the first pawl (11), and in that a selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the first pawl (11) into or out of engagement with the first auxiliary left-hand clutch half (22), and/or in that the first shift cam (25) is directly or indirectly connected to the second pawl (20), and in that a selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the second pawl (20) into or out of engagement with the first left-hand clutch half (15) In an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected with the second pawl (20) and the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the second pawl (20) into an engaged or disengaged state with the first auxiliary left half clutch (22), and/or the first shift cam (25) is directly or indirectly connected with the third pawl (29) and the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the third pawl (29) into an engaged or disengaged state with the first right half clutch (16), and/or the first shift cam (25) is directly or indirectly connected with the third pawl (29), And the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the third pawl (29) into or out of engagement with the first auxiliary right partial clutch (17), and/or the first shift cam (25) is directly or indirectly connected with the fourth pawl (31), and the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the fourth pawl (31) into or out of engagement with the first right partial clutch (16), and/or the first shift cam (25) is directly or indirectly connected with the fourth pawl (31), and the selective rotation of the first shift cam (25) relative to the first intermediate clutch (23) within a certain angular range directly or indirectly brings the fourth pawl (31) into or out of engagement with the first auxiliary right partial clutch (17) ) In an engaged or disengaged state, and/or the first shift cam (25) is directly or indirectly connected with the actuating device (AM) and the first shift cam (25) is selectively rotated in an angular range with respect to the first intermediate clutch (23) under the drive of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16) when the first shift cam (25) is in an angular intermediate position in the rotational direction under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15), the second pawl (20) is in an engaged or disengaged state with the first left half clutch (15), the third pawl (29) is in an engaged or disengaged state with the first right half clutch (16), the fourth pawl (31) is in an engaged or disengaged state with the first right half clutch (16) when the first shift cam (25) is on a certain side in the rotational direction away from the certain angular intermediate position directly or indirectly under the action of the actuating device (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first left half clutch (15) when the first shift cam (25) is on the other side in the rotational direction away from the certain angular intermediate position directly or indirectly under the action of the actuating device (AM), The second pawl (20) is in a joint or separation state with the first left half clutch (15), the third pawl (29) is in a joint or separation state with the first right half clutch (16), the fourth pawl (31) is in a joint or separation state with the first right half clutch (16), and/or the first limit pin (13) comprises at least one pin, and/or the second limit pin (24) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first left half clutch (15), and/or the second limit pin (24) is directly or indirectly fixedly connected with the first right half clutch (16), and/or the first auxiliary left half clutch (22) is directly or indirectly connected with the first left half clutch (15), And the first auxiliary left half clutch (22) has at least a function of rotating a certain angle relative to the first left half clutch (15) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary left half clutch (22) is connected with the first left half clutch (15) through the first limit pin (13), and the first auxiliary left half clutch (22) has at least a function of rotating relative to the first left half clutch (15) within the angle range defined by the first limit pin (13) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary right half clutch (17) is directly or indirectly connected with the first right half clutch (16), and the first auxiliary left half clutch (22) has a function of rotating relative to the first left half clutch (15) under the action of the third pawl (29) or the fourth pawl (31), The first auxiliary right half clutch (17) at least has a function of rotating a certain angle relative to the first right half clutch (16), and/or the first auxiliary right half clutch (17) is connected with the first right half clutch (16) through the second limit pin (24), and under the action of the third pawl (29) or the fourth pawl (31), the first auxiliary right half clutch (17) at least has a function of rotating relative to the first right half clutch (16) within the angle range defined by the second limit pin (24), and/or the first auxiliary left half clutch (22) is coaxially arranged on one side of the first left half clutch (15) in the radial direction, and/or the first auxiliary right half clutch (17) is coaxially arranged on one side of the first right half clutch (16) in the radial direction, and/or when the first left half clutch (15) rotates reversely or forwardly relative to the first middle clutch (23) When the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15) under the direct or indirect action of the first pawl (11), or after the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15), part of the surface of the first auxiliary left half clutch (22) and part of the surface of the first left half clutch (15) are radially combined to form a plane, the first pawl (11) rotates relative to the first intermediate clutch (23) and is in contact with the combined plane, so that the noise is greatly reduced, and/or when the first left half clutch (15) rotates forwards or backwards relative to the first intermediate clutch (23), under the direct or indirect action of the second pawl (20), the first auxiliary left half clutch (22) rotates to a certain angle relative to the first left half clutch (15) After the first auxiliary left half clutch (22) rotates to the angle limited by the first limit pin (13) relative to the first left half clutch (15), part of the surface of the first auxiliary left half clutch (22) and part of the surface of the first left half clutch (15) are radially spliced to form a plane, the second pawl (20) rotates relative to the first intermediate clutch (23) and is in contact with the spliced plane, so that noise is greatly reduced, and/or when the first right half clutch (16) rotates reversely or normally relative to the first intermediate clutch (23), under the direct or indirect action of the third pawl (29), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16), or after the first auxiliary right half clutch (17) rotates to the angle limited by the second limit pin (24) relative to the first right half clutch (16), Partial surface of the first auxiliary right half clutch (17) and partial surface of the first right half clutch (16) are radially split into a plane, so that the third pawl (29) is in contact with the split plane when rotating relative to the first intermediate clutch (23), thereby greatly reducing noise, and/or when the first right half clutch (16) rotates forward or backward relative to the first intermediate clutch (23), after the first auxiliary right half clutch (17) rotates to a certain angle relative to the first right half clutch (16) under the direct or indirect action of the fourth pawl (31), or after the first auxiliary right half clutch (17) rotates to an angle defined by the second limit pin (24) relative to the first right half clutch (16), partial surface of the first auxiliary right half clutch (17) and partial surface of the first right half clutch (16) are radially split into a plane, So that the fourth pawl (31) is in contact with the split plane when rotating relative to the first intermediate clutch (23), thereby greatly reducing noise; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary outer ring (12), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12), and/or the first positioning mechanism (19) being arranged coaxially with the first inner ring (1), the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary outer ring (12), and/or the first positioning means (19), and/or the second pawl (20), and/or the second return spring (21) are/is arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a damping cushion Device (DM), and/or the first inner ring (1) is directly or indirectly connected with and rotates with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with a driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with and rotates with a driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first outer ring (2) at an initial position, the first outer ring (2) is unidirectionally fixed in the forward or reverse rotation direction relative to the first inner ring (1) at the initial position, and/or the first pawl (11) is in an engagement state with the first auxiliary outer ring (12) at the initial position, the first auxiliary outer ring (12) is unidirectionally fixed in the forward or reverse rotation direction relative to the first inner ring (1), and/or the second pawl (20) is in an engagement state with the first outer ring (2) at the initial position, the first outer ring (2) is unidirectionally fixed in the reverse or forward rotation direction relative to the first inner ring (1), and/or the second pawl (20) is in an engagement state with the first auxiliary outer ring (12) at the initial position, the first auxiliary outer ring (12) is unidirectionally fixed in the reverse or forward rotation direction relative to the first inner ring (1) at the initial position And/or the first pawl (11) is in a disengaged state from the first outer ring (2) in an initial position, at which time the first outer ring (2) is rotatable in the reverse or forward direction with respect to the first inner ring (1), and/or the first pawl (11) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, at which time the first auxiliary outer ring (12) is rotatable in the reverse or forward direction with respect to the first inner ring (1), and/or the second pawl (20) is in a disengaged state from the first outer ring (2) in an initial position, at which time the first outer ring (2) is rotatable in the forward or reverse direction with respect to the first inner ring (1), and/or the second pawl (20) is in a disengaged state from the first auxiliary outer ring (12) in an initial position, The first auxiliary outer ring (12) can rotate in the forward or reverse direction relative to the first inner ring (1), the first inner ring (1) and the first outer ring (2) and the first auxiliary outer ring (12) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, and the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first inner ring (1), the first pawl (11) rotates with the first inner ring (1), the first pawl (11) can rotate relative to the first inner ring (1) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), The first pawl (11) rotates together with the first right clutch support (6), the first pawl (11) can rotate relative to the first right clutch support (6) within a certain angle range, the second pawl (20) comprises at least one pawl, the second pawl (20) is directly or indirectly connected with the first inner ring (1), the second pawl (20) rotates together with the first inner ring (1), the second pawl (20) can rotate relative to the first outer ring (2) within a certain angle range, and/or the second pawl (20) is directly or indirectly connected with the first right clutch support (6), the second pawl (20) rotates together with the first right clutch support (6), the second pawl (20) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and the second return spring (21) is directly or indirectly connected with the second pawl (20), -the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other restraining or loads on the second pawl (20) is less than the action of the spring force of the second return spring (21), the first outer ring (2) being fixed unidirectionally in relation to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is in engagement with the first outer ring (2), and/or the first auxiliary outer ring (12) being fixed unidirectionally in relation to the first inner ring (1) in the forward or reverse direction when the first pawl (11) is in engagement with the first auxiliary outer ring (12), and/or the first outer ring (2) being fixed unidirectionally in relation to the first inner ring (1) in the reverse or reverse direction when the second pawl (20) is in engagement with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first inner ring (1) in the reverse or forward direction when the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed in both the forward and reverse directions relative to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in both the forward and reverse directions relative to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the second pawls (20) are disengaged from the first outer ring (2) when the first pawls (11) are engaged with the first outer ring (2), -the first outer ring (2) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first inner ring (1) within a certain load range, and/or-the first auxiliary outer ring (12) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first inner ring (1) within a certain load range when the first pawl (11) is engaged with the first auxiliary outer ring (12) and the second pawl (20) is disengaged from the first auxiliary outer ring (12), and/or-the first outer ring (2) is fixed in a reverse or forward direction and rotatable in a forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawl (11) is disengaged from the first outer ring (2) and the second pawl (20) is engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first inner ring (1) within a certain load range when the first pawls (11) are disengaged from the first auxiliary outer ring (12) and the second pawls (20) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is rotatable in both the forward and reverse directions with respect to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are disengaged from the first outer ring (2), and/or the first auxiliary outer ring (12) is rotatable in both the forward and reverse directions with respect to the first inner ring (1) within a certain load range when the first pawls (11) and the second pawls (20) are disengaged from the first auxiliary outer ring (12), the contact pair of the first pawl (11) and the first outer ring (2) has an overload protection function when the first pawl (11) and the first outer ring (2) are in an engaged state, the first pawl (11) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the first pawl (11) and the first outer ring (2), and/or the contact pair of the first pawl (11) and the first outer ring (2) has a self-locking function when the first pawl (11) and the first outer ring (2) are in the engaged state, the contact pair of the first pawl (11) and the first outer ring (2) are not automatically disengaged when the large force is applied between the first pawl (11) and the first outer ring (2), and/or the contact pair of the first pawl (11) and the first outer ring (2) are not automatically disengaged when the first pawl (11) and the first auxiliary outer ring (12) are in the engaged state, The contact pair of the first pawl (11) and the first auxiliary outer ring (12) has an overload protection function, the first pawl (11) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary outer ring (12) has a self-locking function when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is in an engaged state, the contact pair of the first pawl (11) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary outer ring (12) is large, and/or the contact pair of the second pawl (20) and the first outer ring (2) is in an engaged state, The contact pair of the second pawl (20) and the first outer ring (2) has an overload protection function, the second pawl (20) and the first outer ring (2) are automatically disengaged when the acting force between the second pawl (20) and the first outer ring (2) is excessive, and/or the contact pair of the second pawl (20) and the first outer ring (2) has a self-locking function when the acting force between the second pawl (20) and the first outer ring (2) is in an engaged state, the contact pair of the second pawl (20) and the first outer ring (2) is not automatically disengaged when the acting force between the second pawl (20) and the first outer ring (2) is large, and/or the contact pair of the second pawl (20) and the first auxiliary outer ring (12) has an overload protection function when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is in an engaged state, When the acting force between the second pawl (20) and the first auxiliary outer ring (12) is excessive, the second pawl (20) is automatically disengaged from the first auxiliary outer ring (12), and/or when the second pawl (20) is in an engaged state with the first auxiliary outer ring (12), the contact pair of the second pawl (20) and the first auxiliary outer ring (12) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary outer ring (12) is large, the contact pair of the second pawl (20) and the first auxiliary outer ring (12) is not automatically disengaged, and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first right clutch support (6) is connected with the first inner ring through the first clutch rivet (7) The ring (1) is fixedly connected, and/or the first left clutch support (5) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and/or the first inner ring (1) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) overcomes the effect of the first inner ring (1) and selectively moves relative to the first inner ring (1) in the axial direction, and/or the first inner ring (1) is at least provided with a series of axial positioning grooves or bulges, the first left clutch support (5) is at least configured to perform the function of axially positioning relative to the first inner ring (1) through the series of axial positioning grooves or bulges in a certain range, and/or the first positioning mechanism (19) is directly or indirectly connected with the first inner ring (1), The first positioning means (19) rotating together with the first inner ring (1), the first positioning means (19) being axially fixed relative to the first inner ring (1), and/or the first positioning means (19) being directly or indirectly connected to the first left clutch support (5), and the first positioning means (19) having a limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) being selectively movable in the axial direction relative to the first inner ring (1) against the effect of the first positioning means (19), and/or the first left clutch support (5) being provided with a series of axial positioning grooves or projections, the first left clutch support (5) being configured at least to position at least one of its axial positions by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range to directly or indirectly enable the first pawl (11) to be in an engaged or disengaged state with the first outer ring (2), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range to directly or indirectly enable the first pawl (11) to be in an engaged or disengaged state with the first auxiliary outer ring (12), and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range The second pawl (20) is directly or indirectly engaged or disengaged with the first outer ring (2) by axial movement, and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range to directly or indirectly engage or disengage the second pawl (20) with the first auxiliary outer ring (12), and/or the first left clutch support (5) is directly or indirectly connected with the actuating device (AM) and the first left clutch support (5) is selectively axially moved relative to the first inner ring (1) within a certain range under the drive of the actuating device (AM) and/or the first left clutch support (5) is axially moved relative to the first inner ring (2) within a certain range under the drive of the actuating device (AM) directly or indirectly The first pawl (11) is in an engaged or disengaged state with the first outer ring (2), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2) when the ring (1) is in an intermediate position, and/or the first pawl (11) is in an engaged or disengaged state with the first outer ring (2) when the first left clutch bracket (5) is axially at a position axially to the left away from the first inner ring (1) directly or indirectly under the action of the Actuating Means (AM), the second pawl (20) is in an engaged or disengaged state with the first outer ring (2), and/or the first pawl (11) is in an engaged or disengaged state with the first outer ring (2) when the first left clutch bracket (5) is axially at a position axially at a side away from the first inner ring (1) directly or indirectly under the action of the Actuating Means (AM), The second pawl (20) is in engagement with or disengaged from the first outer ring (2), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary outer ring (12) at least has the function of rotating the angle range defined by the first limit pin (13) The function of rotating relative to the first outer ring (2) is/are carried out, and/or the first auxiliary outer ring (12) is coaxially arranged on one side of the first outer ring (2), and/or when the first outer ring (2) rotates reversely or forwardly relative to the first inner ring (1), under the direct or indirect action of the first pawl (11), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) is combined with part of the surface of the first outer ring (2) to form a cylindrical surface, and the first pawl (11) contacts with the combined cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced, and/or when the first outer ring (2) rotates forwards or reversely relative to the first inner ring (1), under the direct or indirect action of the second pawl (20), after the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2), or after the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2), part of the surface of the first auxiliary outer ring (12) is combined with part of the surface of the first outer ring (2) to form a cylindrical surface, and the second pawl (20) contacts with the combined cylindrical surface when rotating relative to the first outer ring (2), so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), the first outer ring (2) being arranged radially on one side of the first inner ring (1), the first outer ring (2), and/or the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19) being arranged coaxially with the first inner ring (1), the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first limit pin (13), and/or the first auxiliary inner ring (14), and/or the first positioning means (19), and/or the second pawl (20), and/or the second return spring (21) are/is arranged axially on one side of the first left clutch support (5), the first inner ring (1) is directly or indirectly connected to and rotates with a driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected to and rotates with a damping cushion Device (DM), and/or the first inner ring (1) is directly or indirectly connected with and rotates with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with a driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with and rotates with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with and rotates with a driven part of the machine (M), and/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engagement state with the first inner ring (1) at an initial position, and the first inner ring (1) is unidirectionally fixed in the forward or reverse direction relative to the first outer ring (2) at the initial position, and/or the first pawl (11) is in an engagement state with the first auxiliary inner ring (14) at the initial position, and the first auxiliary inner ring (14) is unidirectionally fixed in the forward or reverse direction relative to the first outer ring (2), and/or the second pawl (20) is in an engagement state with the first inner ring (1) at the initial position, and the first inner ring (1) is unidirectionally fixed in the reverse or forward direction relative to the first outer ring (2), and/or the second pawl (20) is in an engagement state with the first auxiliary inner ring (14) at the initial position, and the first auxiliary inner ring (14) is unidirectionally fixed in the reverse or forward direction relative to the first outer ring (2) at the initial position And/or the first pawl (11) is in a disengaged state from the first inner ring (1) in an initial position, at which time the first inner ring (1) is rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or the first pawl (11) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, at which time the first auxiliary inner ring (14) is rotatable in the reverse or forward direction with respect to the first outer ring (2), and/or the second pawl (20) is in a disengaged state from the first inner ring (1) in an initial position, at which time the first inner ring (1) is rotatable in the forward or reverse direction with respect to the first outer ring (2), and/or the second pawl (20) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, The first auxiliary inner ring (14) can rotate in the forward or reverse direction relative to the first outer ring (2), the first inner ring (1) and the first outer ring (2) and the first auxiliary inner ring (14) are at least configured with ratchet-shaped protrusions and/or ratchet-shaped grooves, and the first pawl (11) and the second pawl (20) are at least configured to engage with or disengage from the ratchet-shaped protrusions and/or ratchet-shaped grooves, the first pawl (11) comprises at least one pawl, the first pawl (11) is directly or indirectly connected with the first outer ring (2), the first pawl (11) rotates with the first outer ring (2), the first pawl (11) can rotate relative to the first outer ring (2) within a certain angle range, and/or the first pawl (11) is directly or indirectly connected with the first right clutch support (6), Said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected with said first outer race (2), said second pawl (20) rotating together with said first outer race (2), said second pawl (20) being rotatable within an angular range relative to said first outer race (2), and/or said second pawl (20) being directly or indirectly connected with said first right clutch support (6), said second pawl (20) rotating together with said first right clutch support (6), said second pawl (20) being rotatable within an angular range relative to said first right clutch support (6), the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), the first return spring (4) is directly or indirectly connected with a first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the effect of other restraint or load on the first pawl (11) is smaller than the elastic force effect of the first return spring (4) on the first pawl (11), the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), and the second return spring (21) is directly or indirectly connected with the second pawl (20), -the second pawl (20) returns to the initial position under the action of the spring force of the second return spring (21) when the action of other constraints or loads on the second pawl (20) is less than the action of the spring force of the second return spring (21) on the second pawl (20), -the first inner ring (1) is fixed unidirectionally in relation to the first outer ring (2) in the forward or reverse direction when the first pawl (11) is engaged with the first inner ring (1), and/or-the first auxiliary inner ring (14) is fixed unidirectionally in relation to the first outer ring (2) in the forward or reverse direction when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or-the first inner ring (1) is fixed unidirectionally in relation to the first outer ring (2) in the reverse or forward direction when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally relative to the first outer ring (2) in the reverse or forward direction when the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in both the forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both the forward and reverse directions relative to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the second pawl (20) is disengaged from the first inner ring (1) when the first pawl (11) is engaged with the first inner ring (1), and the second pawl (20) is disengaged from the first inner ring (1), -the first inner ring (1) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first outer ring (2) within a certain load range, and/or-the first auxiliary inner ring (14) is fixed in a forward or reverse direction and rotatable in a reverse or forward direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), and/or-the first inner ring (1) is fixed in a reverse or forward direction and rotatable in a forward or reverse direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in the reverse or forward direction and rotatable in the forward or reverse direction with respect to the first outer ring (2) within a certain load range when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is rotatable in both the forward and reverse directions with respect to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is rotatable in both the forward and reverse directions with respect to the first outer ring (2) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary inner ring (14), when the first pawl (11) is in an engaged state with the first inner ring (1), the contact pair of the first pawl (11) and the first inner ring (1) has an overload protection function, when the acting force between the first pawl (11) and the first inner ring (1) is excessive, the first pawl (11) and the first inner ring (1) are automatically disengaged, and/or when the acting force between the first pawl (11) and the first inner ring (1) is excessive, the contact pair of the first pawl (11) and the first inner ring (1) has a self-locking function, when the acting force between the first pawl (11) and the first inner ring (1) is large, the contact pair of the first pawl (11) and the first inner ring (1) is not automatically disengaged, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged, The contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of overload protection, the first pawl (11) and the first auxiliary inner ring (14) are automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, and/or the contact pair of the first pawl (11) and the first auxiliary inner ring (14) has the function of self-locking when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is in an engaged state, the contact pair of the first pawl (11) and the first auxiliary inner ring (14) is not automatically disengaged when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is large, and/or the second pawl (20) and the first inner ring (1) are in an engaged state, The contact pair of the second pawl (20) and the first inner ring (1) has the function of overload protection, the second pawl (20) and the first inner ring (1) are automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is excessive, and/or the contact pair of the second pawl (20) and the first inner ring (1) has the function of self-locking when the acting force between the second pawl (20) and the first inner ring (1) is in the engaged state, the contact pair of the second pawl (20) and the first inner ring (1) is not automatically disengaged when the acting force between the second pawl (20) and the first inner ring (1) is large, and/or the contact pair of the second pawl (20) and the first auxiliary inner ring (14) has the function of overload protection when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is in the engaged state, When the acting force between the second pawl (20) and the first auxiliary inner ring (14) is excessive, the second pawl (20) is automatically disengaged from the first auxiliary inner ring (14), and/or when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, a contact pair of the second pawl (20) and the first auxiliary inner ring (14) has a self-locking function, when the acting force between the second pawl (20) and the first auxiliary inner ring (14) is large, the contact pair of the second pawl (20) and the first auxiliary inner ring (14) is not automatically disengaged, and/or the first right clutch support (6) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first clutch rivet (7) at least comprises one rivet, and/or the first right clutch support (6) is connected with the first clutch rivet (7) through the first clutch rivet (7) An outer ring (2) is fixedly connected, and/or the first left clutch support (5) is directly or indirectly connected with the first outer ring (2) and rotates with the first outer ring (2), and/or the first outer ring (2) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) overcomes the effect of the first outer ring (2) and selectively moves relative to the first outer ring (2) in the axial direction, and/or the first outer ring (2) is at least provided with a series of axial positioning grooves or bulges, the first left clutch support (5) is at least provided with a function of axially positioning relative to the first outer ring (2) through the series of axial positioning grooves or bulges in a certain range, and/or the first positioning mechanism (19) is directly or indirectly connected with the first outer ring (2), The first positioning means (19) rotating together with the first outer ring (2), the first positioning means (19) being axially fixed relative to the first outer ring (2), and/or the first positioning means (19) being directly or indirectly connected to the first left clutch support (5) and the first positioning means (19) having a limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) being selectively movable in the axial direction relative to the first outer ring (2) against the effect of the first positioning means (19), and/or the first left clutch support (5) being provided with a series of axial positioning grooves or projections, the first left clutch support (5) being configured at least to position at least one of its axial positions by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range to directly or indirectly enable the first pawl (11) to be in an engaged or disengaged state with the first inner ring (1), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range to directly or indirectly enable the first pawl (11) to be in an engaged or disengaged state with the first auxiliary inner ring (14), and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range The second pawl (20) is directly or indirectly engaged or disengaged with the first inner ring (1) by axial movement, and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range to directly or indirectly engage or disengage the second pawl (20) with the first auxiliary inner ring (14), and/or the first left clutch support (5) is directly or indirectly connected with the actuating device (AM) and the first left clutch support (5) is selectively axially moved relative to the first outer ring (2) within a certain range under the drive of the actuating device (AM) and/or the first left clutch support (5) is axially moved relative to the first outer ring (2) under the action of the actuating device (AM) directly or indirectly The first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1) when the ring (2) is in an intermediate position, and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1) when the first left clutch bracket (5) is in a position axially leftward away from the first outer ring (2) directly or indirectly under the action of the Actuating Means (AM), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1) when the first left clutch bracket (5) is in a position axially leftward away from the first outer ring (2) directly or indirectly under the action of the Actuating Means (AM), The second pawl (20) is in a state of engagement or disengagement with the first inner ring (1), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and the first auxiliary inner ring (14) at least has a function of rotating a certain angle relative to the first inner ring (1) under the action of the first pawl (11) or the second pawl (20), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and the first auxiliary inner ring (14) at least has a function of rotating the certain angle relative to the first inner ring (1) under the action of the first pawl (11) or the second pawl (20) within a range of angles limited by the first limit pin (13) A function of rotating relative to the first inner ring (1) internally, and/or the first auxiliary inner ring (14) is coaxially arranged on one side of the first inner ring (1) in the axial direction, and/or when the first inner ring (1) rotates reversely or positively relative to the first outer ring (2), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), a part of the surface of the first auxiliary inner ring (14) and a part of the surface of the first inner ring (1) are spliced to form a cylindrical surface, and the first pawl (11) contacts the spliced cylindrical surface when rotating relative to the first inner ring (1), So that the noise is greatly reduced, and/or when the first inner ring (1) rotates forwards or reversely relative to the first outer ring (2), under the direct or indirect action of the second pawl (20), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) is combined with part of the surface of the first inner ring (1) to form a cylindrical surface, and the second pawl (20) rotates relative to the first inner ring (1) to contact with the combined cylindrical surface, so that the noise is greatly reduced; and/or

The ratchet clutch mechanism (52) comprises at least: a first inner ring (1), a first outer ring (2), a first middle ring (45), a first return spring (4), a first left clutch support (5), and/or a first right clutch support (6), and/or a first clutch rivet (7), a first pawl (11), and/or a first auxiliary outer ring (12), and/or a first limit pin (13), and/or a first auxiliary inner ring (14), and/or a first positioning mechanism (19), and/or a second pawl (20), and/or a second return spring (21), and/or a second limit pin (24), a third pawl (29), a third return spring (30), and/or a fourth pawl (31), and/or a fourth return spring (32), wherein the first middle ring (45) is positioned between the first inner ring (1) and the first outer ring (2) in the radial direction, And the first outer ring (2) is located on one side of the first middle ring (45) in the radial direction, and/or the first inner ring (1), the first outer ring (2), the first left clutch support (5), and/or the first right clutch support (6), and/or the first auxiliary outer ring (12), and/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19) is arranged coaxially with the first middle ring (45), and the first inner ring (1), the first outer ring (2), the first middle ring (45), the first return spring (4), and/or the first right clutch support (6), and/or the first clutch rivet (7), the first pawl (11), and/or the first auxiliary outer ring (12), and/or the first limit pin (13), And/or the first auxiliary inner ring (14), and/or the first positioning mechanism (19), and/or the second pawl (20), and/or the second return spring (21), and/or the second limit pin (24), the third pawl (29), the third return spring (30), and/or the fourth pawl (31), and/or the fourth return spring (32) are/is arranged axially on one side of the first left clutch support (5), the first middle ring (45) is directly or indirectly connected with and rotates with the active part of the machine (M), and/or the first middle ring (45) is directly or indirectly connected with and rotates with the cushion damping Device (DM), and/or the first middle ring (45) is directly or indirectly connected with and rotates with the passive part of the machine (M) And rotating with a driven member of the machine (M), and/or the first middle ring (45) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with a driving member of the machine (M) and rotating with a driving member of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotating with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven member of the machine (M) and rotating with a driven member of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving member of the machine (M) and rotating with a driving member of the machine (M) -the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates with the damping Device (DM), and/or-the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates with the driven part of the machine (M), and/or-the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), the first pawl (11) is in an engaged state with the first inner ring (1) in an initial position, when the first inner ring (1) is fixed unidirectionally with respect to the first middle ring (45) in a forward or reverse direction, and/or-the first pawl (11) is in an engaged state with the first auxiliary inner ring (14) in an initial position, when the first auxiliary inner ring (14) is fixed unidirectionally with respect to the first middle ring (45) in a forward or reverse direction, and/or the second pawl (20) is in an engaged state with the first inner ring (1) at an initial position, when the first inner ring (1) is fixed unidirectionally in the reverse or forward direction with respect to the first middle ring (45), and/or the second pawl (20) is in an engaged state with the first auxiliary inner ring (14) at an initial position, when the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward direction with respect to the first middle ring (45), and/or the third pawl (29) is in an engaged state with the first outer ring (2) at an initial position, when the first outer ring (2) is fixed unidirectionally in the forward or reverse direction with respect to the first middle ring (45), and/or the third pawl (29) is in an engaged state with the first auxiliary outer ring (12) at an initial position, Wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first middle ring (45) in the forward or reverse direction, and/or the fourth pawl (31) is in an engaged state with the first outer ring (2) at an initial position, wherein the first outer ring (2) is fixed in a unidirectional manner relative to the first middle ring (45) in the reverse or forward direction, and/or the fourth pawl (31) is in an engaged state with the first auxiliary outer ring (12) at an initial position, wherein the first auxiliary outer ring (12) is fixed in a unidirectional manner relative to the first middle ring (45) in the reverse or forward direction, and/or the first pawl (11) is in a disengaged state with the first forward inner ring (1) at an initial position, wherein the first inner ring (1) is rotatable relative to the first middle ring (45) in the reverse or reverse direction, and/or the first pawl (11) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable relative to the first middle ring (45) in the reverse rotation or forward rotation direction, and/or the second pawl (20) is in a disengaged state from the first inner ring (1) in an initial position, in which the first inner ring (1) is rotatable relative to the first middle ring (45) in the forward rotation or reverse rotation direction, and/or the second pawl (20) is in a disengaged state from the first auxiliary inner ring (14) in an initial position, in which the first auxiliary inner ring (14) is rotatable relative to the first middle ring (45) in the forward rotation or reverse rotation direction, and/or the third pawl (29) is in a disengaged state from the first outer ring (2) in an initial position, At this time, the first outer ring (2) is rotatable in the reverse rotation or forward rotation direction with respect to the first middle ring (45), and/or the third pawl (29) is in a disengaged state from the first auxiliary outer ring (12) at an initial position, at this time, the first auxiliary outer ring (12) is rotatable in the reverse rotation or forward rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in a disengaged state from the first outer ring (2) at an initial position, at this time, the first outer ring (2) is rotatable in the forward rotation or reverse rotation direction with respect to the first middle ring (45), and/or the fourth pawl (31) is in a disengaged state from the first auxiliary outer ring (12) at an initial position, at this time, the first auxiliary outer ring (12) is rotatable in the forward rotation or reverse rotation direction with respect to the first middle ring (45), the first inner ring (1) and the first middle ring (2) and the first middle ring (45) and the first pawl (31) are rotatable in the reverse rotation or forward rotation direction The first auxiliary outer ring (12) and the first auxiliary inner ring (14) are at least configured with ratchet-like protrusions and/or ratchet-like recesses, and the first pawls (11) and the second pawls (20) and the third pawls (29) and the fourth pawls (31) are at least configured to engage with or disengage from the ratchet-like protrusions and/or ratchet-like recesses, the first pawls (11) comprise at least one pawl, the first pawls (11) are directly or indirectly connected with the first middle ring (45), the first pawls (11) rotate together with the first middle ring (45), the first pawls (11) are rotatable within an angular range relative to the first middle ring (45), and/or the first pawls (11) are directly or indirectly connected with the first right clutch bracket (6), Said first pawl (11) rotating together with said first right clutch support (6), said first pawl (11) being rotatable within an angular range relative to said first right clutch support (6), said second pawl (20) comprising at least one pawl, said second pawl (20) being directly or indirectly connected with said first centre ring (45), said second pawl (20) rotating together with said first centre ring (45), said second pawl (20) being rotatable within an angular range relative to said first centre ring (45), and/or said second pawl (20) being directly or indirectly connected with said first right clutch support (6), said second pawl (20) rotating together with said first right clutch support (6), said second pawl (20) being rotatable within an angular range relative to said first right clutch support (6), the third pawl (29) comprises at least one pawl, the third pawl (29) is directly or indirectly connected with the first middle ring (45), the third pawl (29) rotates together with the first middle ring (45), the third pawl (29) can rotate relative to the first middle ring (45) within a certain angle range, and/or the third pawl (29) is directly or indirectly connected with the first left clutch support (5), the third pawl (29) rotates together with the first left clutch support (5), the third pawl (29) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the third pawl (29) is directly or indirectly connected with the first right clutch support (6), the third pawl (29) rotates together with the first right clutch support (6), The third pawl (29) can rotate within a certain angle range relative to the first right clutch support (6), the fourth pawl (31) comprises at least one pawl, the fourth pawl (31) is directly or indirectly connected with the first middle ring (45), the fourth pawl (31)) rotates together with the first middle ring (45), the fourth pawl (31) can rotate relative to the first middle ring (45) within a certain angle range, and/or the fourth pawl (31) is directly or indirectly connected with the first left clutch support (5), the fourth pawl (31) rotates together with the first left clutch support (5), the fourth pawl (31) can rotate relative to the first left clutch support (5) within a certain angle range, and/or the fourth pawl (31) is directly or indirectly connected with the first right clutch support (6), The fourth pawl (31) rotates together with the first right clutch support (6), the fourth pawl (31) can rotate relative to the first right clutch support (6) within a certain angle range, the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the first return spring (4) is directly or indirectly connected with the first pawl (11), the first pawl (11) restores the initial position under the elastic force of the first return spring (4) when the elastic force of the first pawl (11) is smaller than the elastic force of the first return spring (4) under the action of other restraint or load, the second return spring (21) at least comprises one spring, the second return spring (21) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the second return spring (21) is directly or indirectly connected with the second pawl (20), when the action of other restraint or load on the second pawl (20) is smaller than the elastic action of the second return spring (21) on the second pawl (20), the second pawl (20) restores to the initial position under the elastic action of the second return spring (21), the third return spring (30) at least comprises one spring, the third return spring (30) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the third return spring (30) is directly or indirectly connected with the third pawl (29), when the action of other restraint or load on the third pawl is smaller than the action of the third return spring (30) on the third pawl (29) The third pawl (29) is restored to the initial position by the elastic force of the third return spring (30) when the elastic force of the third pawl (29) acts, the fourth return spring (32) comprises at least one spring, the fourth return spring (32) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), the fourth return spring (32) is directly or indirectly connected with the fourth pawl (31), the fourth pawl (31) is restored to the initial position by the elastic force of the fourth return spring (32) when the action of other restraint or load on the fourth pawl (31) is smaller than the elastic force of the fourth return spring (32) on the fourth pawl (31), and the first inner ring (1) is fixed in one direction relative to the first middle ring (45) in the forward or reverse rotation direction when the first pawl (11) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the forward or reverse direction relative to the first middle ring (45) when the first pawl (11) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed unidirectionally in the reverse or forward direction relative to the first middle ring (45) when the second pawl (20) is engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed unidirectionally in the forward and reverse directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are engaged with the first auxiliary inner ring (14), and/or the first inner ring (1) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first inner ring (1) and the second pawl (20) is disengaged from the first inner ring (1), and/or the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in reverse or forward rotation directions within a certain load range when the first pawl (11) is engaged with the first auxiliary inner ring (14) and the second pawl (20) is disengaged from the first auxiliary inner ring (14), and the first auxiliary inner ring (14) is fixed in forward or reverse rotation directions with respect to the first middle ring (45) and is rotatable in a certain load range Rotatable in a reverse or forward direction, and/or when the first pawl (11) is disengaged from the first inner ring (1) and the second pawl (20) is engaged with the first inner ring (1), the first inner ring (1) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) is disengaged from the first auxiliary inner ring (14) and the second pawl (20) is engaged with the first auxiliary inner ring (14), the first auxiliary inner ring (14) is fixed in the reverse or forward direction relative to the first middle ring (45) and rotatable in the forward or reverse direction within a certain load range, and/or when the first pawl (11) and the second pawl (20) are disengaged from the first inner ring (1), -the first inner ring (1) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range, and/or-the first auxiliary inner ring (14) is rotatable in both forward and reverse rotation directions relative to the first middle ring (45) within a certain load range when the first pawl (11) and the second pawl (20) are disengaged from the first auxiliary inner ring (14), and/or-the first outer ring (2) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first outer ring (2), and/or-the first auxiliary outer ring (12) is fixed unidirectionally in either forward or reverse rotation directions relative to the first middle ring (45) when the third pawl (29) is engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed unidirectionally relative to the first middle ring (45) in the forward or reverse direction when the fourth pawls (31) are engaged with the first auxiliary outer ring (12), and/or the first outer ring (2) is fixed relative to the first middle ring (45) in both the forward and reverse directions over a range of loads when the third pawls (29) and the fourth pawls (31) are engaged with the first outer ring (2), and/or the third pawls (29) and the fourth pawls (31) are engaged with the first auxiliary outer ring (12) over a range of loads, The first auxiliary outer ring (12) is fixed in both forward and reverse rotation directions with respect to the first middle ring (45), and/or the first outer ring (2) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first outer ring (2) and the fourth pawls (31) are disengaged with respect to the first outer ring (2), and/or the first auxiliary outer ring (12) is fixed in forward or reverse rotation directions and rotatable in reverse or forward rotation directions with respect to the first middle ring (45) within a certain load range when the third pawls (29) are engaged with the first auxiliary outer ring (12) and the fourth pawls (31) are disengaged with respect to the first auxiliary outer ring (12), and/or the third pawls (29) are disengaged with respect to the first middle ring (2) and the fourth pawls (31) are disengaged with the outer ring (31) Said first outer ring (2) being fixed in a reverse or forward direction and rotatable in a forward or reverse direction relative to said first centre ring (45) over a range of loads when said first outer ring (2) is engaged, and/or said first auxiliary outer ring (12) being fixed in a reverse or forward direction and rotatable in a forward or reverse direction relative to said first centre ring (45) over a range of loads when said third pawls (29) are disengaged from said first auxiliary outer ring (12) and said fourth pawls (31) are engaged with said first auxiliary outer ring (12), and/or said first outer ring (2) being rotatable in both forward and reverse directions relative to said first centre ring (45) over a range of loads when said third pawls (29) and said fourth pawls (31) are disengaged from said first outer ring (2), and/or the first auxiliary outer ring (12) can rotate in the forward rotation direction and the reverse rotation direction relative to the first middle ring (45) within a certain load range when the third pawls (29) and the fourth pawls (31) are separated from the first auxiliary outer ring (12), the contact pair of the first pawls (11) and the first inner ring (1) has an overload protection function when the first pawls (11) and the first inner ring (1) are in an engaged state, the first pawls (11) and the first inner ring (1) are automatically disengaged when an excessive force is applied between the first pawls (11) and the first inner ring (1), and/or the contact pair of the first pawls (11) and the first inner ring (1) has a self-locking function, a self-locking function, When the acting force between the first pawl (11) and the first inner ring (1) is large, the first pawl (11) and the first inner ring (1) contact pair can not automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of overload protection, when the acting force between the first pawl (11) and the first auxiliary inner ring (14) is excessive, the first pawl (11) and the first auxiliary inner ring (14) automatically disengage, and/or when the first pawl (11) and the first auxiliary inner ring (14) are in an engaged state, the first pawl (11) and the first auxiliary inner ring (14) contact pair has the function of self-locking, When the acting force between the first pawl (11) and the first auxiliary inner ring (14) is larger, the first pawl (11) and the first auxiliary inner ring (14) contact pair can not automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of overload protection, when the acting force between the second pawl (20) and the first inner ring (1) is too large, the second pawl (20) and the first inner ring (1) automatically disengage, and/or when the second pawl (20) and the first inner ring (1) are in an engaged state, the second pawl (20) and the first inner ring (1) contact pair has the function of self-locking, when the acting force between the second pawl (20) and the first inner ring (1) is larger, the second pawl (20) and the first inner ring (1) contact pair have the function of self-locking, The second pawl (20) and the first inner ring (1) contact pair can not automatically disengage, and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has an overload protection function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, the second pawl (20) and the first auxiliary inner ring (14) automatically disengage when an excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), and/or the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the second pawl (20) and the first auxiliary inner ring (14) are in an engaged state, and the second pawl (20) and the first auxiliary inner ring (14) contact pair has a self-locking function when the excessive force is applied between the second pawl (20) and the first auxiliary inner ring (14), The second pawl (20) is not automatically disengaged from the first auxiliary inner ring (14) contact pair, and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair with an overload protection function when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is automatically disengaged from the first outer ring (2) when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the third pawl (29) is automatically disengaged from the first outer ring (2) contact pair when the third pawl (29) is in an engaged state with the first outer ring (2), the third pawl (29) is not automatically disengaged from the first outer ring (2) contact pair when an excessive force is applied between the third pawl (29) and the first outer ring (2), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has an overload protection function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), the third pawls (29) are automatically disengaged from the first auxiliary outer ring (12) when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the third pawls (29) with the first auxiliary outer ring (12) has a self-locking function when the third pawls (29) are in an engaged state with the first auxiliary outer ring (12), and the contact pair of the third pawls (29) with the first auxiliary outer ring (12) is not automatically disengaged when an excessive force is applied between the third pawls (29) and the first auxiliary outer ring (12), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has an overload protection function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the fourth pawl (31) and the first outer ring (2) are automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the contact pair of the fourth pawl (31) and the first outer ring (2) has a self-locking function when the fourth pawl (31) and the first outer ring (2) are in an engaged state, the contact pair of the fourth pawl (31) and the first outer ring (2) are not automatically disengaged when an excessive force is applied between the fourth pawl (31) and the first outer ring (2), and/or the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, The contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has an overload protection function, the fourth pawl (31) and the first auxiliary outer ring (12) are automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is excessive, and/or the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) has a self-locking function when the fourth pawl (31) and the first auxiliary outer ring (12) are in an engaged state, the contact pair of the fourth pawl (31) and the first auxiliary outer ring (12) is not automatically disengaged when the acting force between the fourth pawl (31) and the first auxiliary outer ring (12) is large, and/or the first right clutch bracket (6) is directly or indirectly fixedly connected with the first middle ring (45), and/or the first clutch rivet (7) comprises at least one rivet, and/or the first right clutch support (6) is fixedly connected with the first middle ring (45) through the first clutch rivet (7), and/or the first left clutch support (5) is directly or indirectly connected with the first middle ring (45) and rotates together with the first middle ring (45), and/or the first middle ring (45) has a certain limiting effect on the first left clutch support (5) in the axial direction, the first left clutch support (5) selectively moves relative to the first middle ring (45) in the axial direction against the effect of the first middle ring (45), and/or the first middle ring (45) is at least provided with a series of axial positioning grooves or bulges, and the first left clutch support (5) is at least configured to be relative to the first middle ring (45) through the series of axial positioning grooves or bulges in a certain range 45) The first positioning mechanism (19) is directly or indirectly connected with the first middle ring (45), the first positioning mechanism (19) rotates together with the first middle ring (45), the first positioning mechanism (19) is fixed relative to the first middle ring (45) in the axial direction, and/or the first positioning mechanism (19) is directly or indirectly connected with the first left clutch bracket (5), the first positioning mechanism (19) has a certain limiting effect on the first left clutch bracket (5) in the axial direction, the first left clutch bracket (5) selectively moves relative to the first middle ring (45) in the axial direction against the effect of the first positioning mechanism (19), and/or a series of axial positioning grooves or protrusions are arranged on the first left clutch bracket (5), The first left clutch support (5) is at least configured to position at least one axial position thereof through a range of constraining actions of the series of axial positioning grooves or protrusions and the first positioning mechanism (19), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a range to directly or indirectly bring the first pawl (11) into an engaged or disengaged state with the first inner ring (1), and/or the first left clutch support (5) is directly or indirectly connected with the first pawl (11) and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a range to directly or indirectly bring the first pawl (11) into an engaged or disengaged state with the first auxiliary inner ring (14) And/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a certain range to directly or indirectly enable the second pawl (20) to be in an engagement or disengagement state with the first inner ring (1), and/or the first left clutch support (5) is directly or indirectly connected with the second pawl (20) and the first left clutch support (5) is selectively axially moved relative to the first middle ring (45) within a certain range to directly or indirectly enable the second pawl (20) to be in an engagement or disengagement state with the first auxiliary inner ring (14), and/or the first left clutch support (5) is directly or indirectly connected with the third pawl (29), And the first left clutch support (5) is selectively axially moved within a certain range relative to the first middle ring (45) to directly or indirectly enable the third pawl (29) to be in an engaged or disengaged state with the first outer ring (2), and/or the first left clutch support (5) is directly or indirectly connected with the third pawl (29), and the first left clutch support (5) is selectively axially moved within a certain range relative to the first middle ring (45) to directly or indirectly enable the third pawl (29) to be in an engaged or disengaged state with the first auxiliary outer ring (12), and/or the first left clutch support (5) is directly or indirectly connected with the fourth pawl (31), and the first left clutch support (5) is selectively axially moved within a certain range relative to the first middle ring (45) to directly or indirectly enable the fourth pawl (31) to be in an engaged or engaged state with the first outer ring (2) -a disengaged condition, and/or said first left clutch support (5) is directly or indirectly connected to said fourth pawl (31) and said first left clutch support (5) is selectively axially displaced with respect to said first centre ring (45) within a certain range directly or indirectly bringing said fourth pawl (31) into engagement or disengagement with said first auxiliary outer ring (12), and/or said first left clutch support (5) is directly or indirectly connected to said Actuating Means (AM) and said first left clutch support (5) is selectively axially displaced with respect to said first centre ring (45) within a certain range under the drive of said Actuating Means (AM), and/or when said first shift sleeve (18) is axially displaced with respect to said first centre ring (45) within a certain range under the action of said Actuating Means (AM), directly or indirectly, The first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2), the fourth pawl (31) is in an engaged or disengaged state with the first outer ring (2), and/or the first pawl (11) is in an engaged or disengaged state with the first inner ring (1), the second pawl (20) is in an engaged or disengaged state with the first inner ring (1), the third pawl (29) is in an engaged or disengaged state with the first outer ring (2) when the first shift sleeve (18) is in a position axially to the left away from the first middle ring (45) directly or indirectly under the action of the Actuating Means (AM), The fourth pawl (31) is in engagement or disengagement with the first outer ring (2) and/or the first pawl (11) is in engagement or disengagement with the first inner ring (1), the second pawl (20) is in engagement or disengagement with the first inner ring (1), the third pawl (29) is in engagement or disengagement with the first outer ring (2), the fourth pawl (31) is in engagement or disengagement with the first outer ring (2), and/or the first limit pin (13) comprises at least one pin, and/or the first limit pin (13) is in fixed connection with the first inner ring (1) directly or indirectly, when the first shift sleeve (18) is in a position axially on one side away from the first middle ring (45) directly or indirectly under the action of the actuating device (AM), and/or the second limit pin (24) comprises at least one pin, and/or the second limit pin (24) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first auxiliary inner ring (14) is directly or indirectly connected with the first inner ring (1), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has the function of rotating a certain angle relative to the first inner ring (1), and/or the first auxiliary inner ring (14) is connected with the first inner ring (1) through the first limit pin (13), and under the action of the first pawl (11) or the second pawl (20), the first auxiliary inner ring (14) at least has the function of rotating relative to the first inner ring (1) within the angle range defined by the first limit pin (13), and/or the first auxiliary inner ring (14) is arranged axially on one side of the first inner ring (1), and/or the first auxiliary outer ring (12) is directly or indirectly connected with the first outer ring (2), and under the action of the third pawl (29) or the fourth pawl (31), the first auxiliary outer ring (12) at least has the function of rotating a certain angle relative to the first outer ring (2), and/or the first auxiliary outer ring (12) is connected with the first outer ring (2) through the first limit pin (13), and under the action of the third pawl (29) or the fourth pawl (31), the first auxiliary outer ring (12) at least has the function of rotating relative to the first outer ring (2) within the angle range defined by the first limit pin (13), and/or the first auxiliary outer ring (12) is arranged axially on one side of the first outer ring (2) And/or when the first inner ring (1) rotates reversely or forwardly relative to the first middle ring (45), under the direct or indirect action of the first pawl (11), after the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), partial surface of the first auxiliary inner ring (14) is spliced with partial surface of the first inner ring (1) to form a cylindrical surface, the first pawl (11) rotates relative to the first inner ring (1) to be in contact with the spliced cylindrical surface, so that noise is greatly reduced, and/or when the first inner ring (1) rotates forwardly or reversely relative to the first middle ring (45), under the direct or indirect action of the second pawl (20), After the first auxiliary inner ring (14) rotates to a certain angle relative to the first inner ring (1), or after the first auxiliary inner ring (14) rotates to an angle limited by the first limit pin (13) relative to the first inner ring (1), part of the surface of the first auxiliary inner ring (14) is spliced with part of the surface of the first inner ring (1) to form a cylindrical surface, and the second pawl (20) contacts with the spliced cylindrical surface when rotating relative to the first inner ring (1), so that the noise is greatly reduced, and/or when the first outer ring (2) rotates reversely or forwardly relative to the first middle ring (45), the first auxiliary outer ring (12) rotates to a certain angle relative to the first outer ring (2) under the direct or indirect action of the third pawl (29), or the first auxiliary outer ring (12) rotates to an angle limited by the first limit pin (13) relative to the first outer ring (2) A part of the surface of the first auxiliary outer ring (12) is spliced with a part of the surface of the first outer ring (2) to form a cylindrical surface, the third pawl (29) is contacted with the spliced cylindrical surface when rotating relative to the first outer ring (2), so that noise is greatly reduced, and/or the part of the surface of the first auxiliary outer ring (12) is spliced with the surface of the spliced cylindrical surface when the first outer ring (2) rotates relative to the first middle ring (45) in forward rotation or reverse rotation, after the first auxiliary outer ring (12) rotates relative to the first outer ring (2) to a certain angle under the direct or indirect action of the fourth pawl (31), or the part of the surface of the first auxiliary outer ring (12) is spliced with the surface of the first outer ring (2) to a cylindrical surface when the first auxiliary outer ring (12) rotates relative to the first outer ring (2) to an angle defined by the first limit pin (13), and the fourth pawl (31) is contacted with the spliced cylindrical surface when rotating relative to the first outer ring (2) Thereby greatly reducing noise; and/or

The material of the first lever mechanism (27) at least has certain vibration damping or damping function; and/or

The material of the first transmission cam (28) at least has certain vibration damping or damping function; and/or

The material of the third pawl (29) at least has certain vibration reduction or damping function; and/or

The material of the third return spring (30) at least has a certain vibration reduction or damping function; and/or

The material of the fourth pawl (31) at least has a certain vibration reduction or damping function; and/or

The material of the fourth return spring (32) at least has certain vibration reduction or damping function; and/or

The material of the second lever mechanism (49) at least has certain vibration damping or damping function; and/or

The first pawl (11) is of a single solid structure; and/or

The first pawl (11) is formed by a plurality of parts; and/or

The second pawl (20) is of unitary solid construction; and/or

The second pawl (20) is formed from a plurality of parts; and/or

The third pawl (29) is of a single solid structure; and/or

The third pawl (29) is formed from a plurality of parts; and/or

The fourth pawl (31) is of a single solid structure; and/or

The fourth pawl (31) is formed from a plurality of parts; and/or

Said third pawl (29) comprising at least: a first upper half pawl (40), a first lower half pawl (41), a first hydraulic damper (42), and/or a first spring damper (43), and/or a first material damper (44); and/or

Said fourth pawl (31) comprising at least: a first upper half pawl (40), a first lower half pawl (41), a first hydraulic damper (42), and/or a first spring damper (43), and/or a first material damper (44); and/or

The first hydraulic damper (42) comprises at least one hydraulic damper; and/or

The first spring damper (43) comprises at least one spring damper; and/or

5. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a jaw clutch mechanism (53);

the jaw clutch mechanism (53) is configured to selectively realize the connection and disconnection of the power of the connected part by using at least the connection and disconnection of a driving half clutch with teeth or grooves and a driven half clutch with teeth or grooves; and/or

The jaw clutch mechanism (53) is configured to selectively transmit the power of one of the moving members connected to the jaw clutch mechanism to the other moving member by using at least the engagement and disengagement of the driving half clutch with teeth and the driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to selectively transmit the power of one of the moving parts to the other moving parts by using at least the engagement and disengagement of the driving half clutch with teeth and the driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to selectively realize the connection and the disconnection of the movement of the connected part by using at least the connection and the disconnection of a driving half clutch with teeth or grooves and a driven half clutch with teeth or grooves; and/or

The jaw clutch mechanism (53) is configured to selectively transmit the motion of one of the moving members connected thereto to the other moving member by using at least engagement and disengagement of a driving half clutch with teeth and a driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to selectively transmit the motion of one of the moving parts to the other moving parts by using at least the engagement and disengagement of a driving half clutch with teeth and a driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to at least have a function of selectively keeping the moving member connected with the jaw clutch mechanism rotating and accelerating or rotating and decelerating by using the engagement and disengagement of the driving half clutch with teeth and the driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to have at least a function of selectively stopping the rotation of the connected moving member by engagement and disengagement of a driving half clutch with teeth and a driven half clutch with teeth; and/or

The jaw clutch mechanism (53) is configured to have at least a function of selectively holding a moving member connected thereto in a stopped state by engagement and disengagement of a driving half clutch with teeth and a driven half clutch with teeth;

the jaw clutch mechanism (53) comprises at least: a first left half clutch (15), a first right half clutch (16), a first shifting gear sleeve (18) and/or a first positioning mechanism (19), wherein the first shifting gear sleeve (18) and/or the first positioning mechanism (19) are coaxially arranged with the first left half clutch (15) and/or the first right half clutch (16) and the first left half clutch (15) are coaxially or non-coaxially arranged, wherein the first right half clutch (16) and/or the first positioning mechanism (19) and the first shifting gear sleeve (18) are axially arranged on one side of the first left half clutch (15) and/or the first left half clutch (15) coaxially penetrates the first right half clutch (16) and/or the first right half clutch (16) coaxially penetrates the first left half clutch (15), wherein the first left half clutch (15) is directly or indirectly connected with a driving part of the machine (M) and is connected with the machine (M) (M) and/or the first left half-clutch (15) is directly or indirectly connected with the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected with the driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with a frame of the machine (M), the first left half clutch (15) and the first right half clutch (16) are at least configured with claw-shaped bulges and/or grooves, and the first shifting gear sleeve (18) is at least configured with a function of being engaged with or disengaged from the claw-shaped bulges and/or grooves, when the first shifting gear sleeve (18) is engaged with the first left half clutch (15), the first left half clutch (15) is fixed relative to the first right half clutch (16) in a certain load range in both forward and reverse directions, and/or when the first shifting gear sleeve (18) is disengaged from the first left half clutch (15), the first left half clutch (15) is fixed relative to the first right half clutch (16) in both forward and reverse directions, and/or when the first shifting gear sleeve (18) is disengaged from the first left half clutch (15), The first left half clutch (15) can rotate in the forward rotation direction and the reverse rotation direction relative to the first right half clutch (16) within a certain load range, when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, a contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has an overload protection function, when an acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is overlarge, the first shifting gear sleeve (18) and the first left half clutch (15) are automatically separated, and/or when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, the contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has a self-locking function, and when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is larger, The first shift sleeve (18) is also not automatically disengaged from the first left clutch half (15), the first shift sleeve (18) is directly or indirectly connected to the first right clutch half (16) and rotates together with the first right clutch half (16), and/or the first right clutch half (16) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first right clutch half (16) against the effect of the first right clutch half (16), and/or at least one series of axial positioning grooves or projections are formed on the first right clutch half (16), the first shift sleeve (18) is at least configured to perform an axial positioning function relative to the first right clutch half (16) through the series of axial positioning grooves or projections within a certain range, and/or the first positioning means (19) is directly or indirectly connected to the first right partial clutch (16), the first positioning means (19) rotates together with the first right partial clutch (16), the first positioning means (19) is axially fixed relative to the first right partial clutch (16), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first right partial clutch (16) against the effect of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first shift sleeve (18), the first shift sleeve (18) being configured at least such that it is connected to the first certain positioning grooves or projections via the series of axial positioning grooves or projections The constraining action of the position mechanism (19) within a certain range positions at least one axial position thereof, and/or the first shift sleeve (18) is directly or indirectly connected with the actuating device (AM) and the first shift sleeve (18) is selectively engaged and disengaged with the first left half clutch (15) under the driving of the actuating device (AM), and/or the first shift sleeve (18) is in a disengaged state with the first left half clutch (15) when the first shift sleeve (18) is in a certain position axially far away from the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), and/or the first shift sleeve (18) is in a certain position axially near the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), The first shift sleeve (18) is in engagement with the first left clutch half (15); and/or

The jaw clutch mechanism (53) comprises at least: a first left half clutch (15), a first right half clutch (16), a first shifting sleeve (18), and/or a first positioning mechanism (19), a first intermediate clutch (23), the first shifting sleeve (18), and/or the first positioning mechanism (19) being arranged coaxially with the first intermediate clutch (23), and/or the first left half clutch (15) being arranged coaxially or non-coaxially with the first intermediate clutch (23), and/or the first right half clutch (16) being arranged coaxially or non-coaxially with the first intermediate clutch (23), the first left half clutch (15), the first shifting sleeve (18), and/or the first positioning mechanism (19), the first intermediate clutch (23) being arranged axially on one side of the first right half clutch (16), and/or the first intermediate clutch (23) coaxially passing through the first left half clutch (15), and/or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), and/or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) being directly or indirectly connected with the driving member of the machine (M) and rotating together with the driving member of the machine (M), and/or the first left half clutch (15) being directly or indirectly connected with the damping Device (DM) and rotating together with the damping Device (DM), and/or the first left half clutch (15) being directly or indirectly connected with the driven member of the machine (M) and rotating together with the driven member of the machine (M), and/or the first left half clutch (15) being directly or indirectly fixedly connected with the machine frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the damping Device (DM) A damper Device (DM) rotating together, and/or the first intermediate clutch (23) being directly or indirectly connected to and rotating with a driven part of the machine (M), and/or the first intermediate clutch (23) being directly or indirectly fixedly connected to a machine frame of the machine (M), the first left half clutch (15) and the first right half clutch (16) and the first intermediate clutch (23) being at least configured with claw-like projections and/or recesses, and the first shift sleeve (18) being at least configured with a function of engaging with or disengaging from the claw-like projections and/or recesses, the first left half clutch (15) being fixed in both forward and reverse directions relative to the first intermediate clutch (23) over a certain load range when the first shift sleeve (18) is engaged with the first left half clutch (15), and/or when the first shift sleeve (18) is engaged with the first right half clutch (16), within a certain load range, the first right half clutch (16) is fixed relative to the first intermediate clutch (23) in both forward and reverse directions, and/or when the first shift sleeve (18) is disengaged from the first left half clutch (15), the first left half clutch (15) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or when the first shift sleeve (18) is disengaged from the first right half clutch (16), within a certain load range, the first right half clutch (16) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, when the first shift sleeve (18) is engaged with the first left half clutch (15), the first right half clutch (16) is engaged with the first left half clutch (15), The contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has an overload protection function, the first shifting gear sleeve (18) and the first left half clutch (15) are automatically separated when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is overlarge, and/or the contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has a self-locking function when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, the first shifting gear sleeve (18) and the first left half clutch (15) are not automatically separated when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is larger, and/or the first shifting gear sleeve (18) and the first right half clutch (16) are in an engaged state, The contact pair of the first shift gear sleeve (18) and the first right half clutch (16) has an overload protection function, the first shift gear sleeve (18) and the first right half clutch (16) are automatically separated when the acting force between the first shift gear sleeve (18) and the first right half clutch (16) is too large, and/or the contact pair of the first shift gear sleeve (18) and the first right half clutch (16) has a self-locking function when the first shift gear sleeve (18) and the first right half clutch (16) are in an engaged state, the first shift gear sleeve (18) and the first right half clutch (16) are not automatically separated when the acting force between the first shift gear sleeve (18) and the first right half clutch (16) is large, and the first shift gear sleeve (18) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction relative to the first intermediate clutch (23) against the effect of the first intermediate clutch (23), and/or at least one series of axial positioning grooves or projections are formed on the first intermediate clutch (23), the first shifting sleeve (18) is at least designed to perform the function of axial positioning relative to the first intermediate clutch (23) within a certain range by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected to the first intermediate clutch (23), the first positioning means (19) rotates together with the first intermediate clutch (23), the first positioning means (19) is fixed in the axial direction relative to the first intermediate clutch (23), and/or the first positioning means (19) is directly or indirectly connected to the first shifting sleeve (18) and the first positioning means (19) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction with respect to the first intermediate clutch (23) against the effect of the first positioning means (19), and/or the first shifting sleeve (18) is provided with a series of axial positioning grooves or projections, the first shifting sleeve (18) is at least configured to position at least one axial position thereof by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shifting sleeve (18) is directly or indirectly connected to the actuating device (AM), And the first shift sleeve (18) is driven by the actuating device (AM) to move axially in a certain range relative to the first intermediate clutch (23) selectively, and/or when the first shift sleeve (18) is in a certain intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) is in a disengaged state with the first left half clutch (15), the first shift sleeve (18) is in a disengaged state with the first right half clutch (16), and/or when the first shift sleeve (18) is in a certain position in the axial direction close to the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) is in an engaged state with the first left half clutch (15), The first shift sleeve (18) and the first right half clutch (16) are in a disengaged state, and/or when the first shift sleeve (18) is in a position close to the first right half clutch (16) in the axial direction directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) and the first left half clutch (15) are in a disengaged state, and the first shift sleeve (18) and the first right half clutch (16) are in an engaged state; and/or

The material of the first intermediate clutch (23) at least has certain vibration damping or damping function.

6. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a gear clutch mechanism (54);

the gear clutch mechanism (54) is configured to selectively realize the connection and disconnection of the power of the connected member by using the connection and disconnection of at least a toothed driving gear and a toothed driven gear; and/or

The gear clutch mechanism (54) is configured to selectively transmit the power of one of the moving members to the other moving member by engaging and disengaging at least a toothed driving gear and a toothed driven gear; and/or

The gear clutch mechanism (54) is configured to selectively transmit the power of one of the moving members to the other moving members by engaging and disengaging at least a toothed driving gear and a toothed driven gear; and/or

The gear clutch mechanism (54) is configured to selectively engage and disengage the motion of the connected member by at least engaging and disengaging a toothed driving gear and a toothed driven gear; and/or

The gear clutch mechanism (54) is configured to selectively transmit the motion of one of the moving members to the other moving member by engaging and disengaging at least a toothed driving gear and a toothed driven gear; and/or

The gear clutch mechanism (54) is configured to selectively transmit the motion of one of the moving members to the other moving members by engaging and disengaging at least one of the toothed driving gear and the toothed driven gear; and/or

The gear clutch mechanism (54) is configured to at least have a function of selectively keeping the moving member connected with the gear clutch mechanism in rotation acceleration or rotation deceleration by utilizing the engagement and the disengagement of the toothed driving gear and the toothed driven gear; and/or

The gear clutch mechanism (54) is configured to have at least a function of selectively stopping the rotation of the connected moving member by the engagement and disengagement of the toothed driving gear and the toothed driven gear; and/or

The gear clutch mechanism (54) is configured to have at least a function of selectively holding a moving member connected thereto in a stopped state by engagement and disengagement of a toothed drive gear and a toothed driven gear;

the gear clutch mechanism (54) includes at least: a first left half clutch (15), a first right half clutch (16), a first shifting gear sleeve (18) and/or a first positioning mechanism (19), wherein the first shifting gear sleeve (18) and/or the first positioning mechanism (19) are coaxially arranged with the first right half clutch (16) and/or the first left half clutch (15) and the first right half clutch (16) are coaxially or non-coaxially arranged, wherein the first right half clutch (16) and/or the first positioning mechanism (19) and the first shifting gear sleeve (18) are axially arranged on one side of the first left half clutch (15) and/or the first left half clutch (15) coaxially penetrates the first right half clutch (16) and/or the first right half clutch (16) coaxially penetrates the first left half clutch (15), wherein the first left half clutch (15) is directly or indirectly connected with a driving part of the machine (M) and is connected with the machine (M) (M) and/or the first left half-clutch (15) is directly or indirectly connected with the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first left half-clutch (15) is directly or indirectly connected with the driven part of the machine (M) and rotates with the driven part of the machine (M), and/or the first left half-clutch (15) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates with the driving part of the machine (M), and/or the first right half-clutch (16) is directly or indirectly connected with the cushion damping Device (DM) and rotates with the cushion damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with a frame of the machine (M), the first left half clutch (15) and the first right half clutch (16) are at least configured with tooth-shaped bulges and/or grooves, and the first shifting gear sleeve (18) is at least configured to have the function of being engaged with or separated from the tooth-shaped bulges and/or grooves, when the first shifting gear sleeve (18) is engaged with the first left half clutch (15), within a certain load range, the first left half clutch (15) is fixed relative to the first right half clutch (16) in the forward and reverse directions, and/or when the first shifting gear sleeve (18) is disengaged from the first left half clutch (15), the first shifting gear sleeve (15) is fixed relative to the first right half clutch (15) in the forward and reverse directions, and/or when the first shifting gear sleeve (18) is disengaged from the first left half clutch (15), The first left half clutch (15) can rotate in the forward rotation direction and the reverse rotation direction relative to the first right half clutch (16) within a certain load range, when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, a contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has an overload protection function, when an acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is overlarge, the first shifting gear sleeve (18) and the first left half clutch (15) are automatically separated, and/or when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, the contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has a self-locking function, and when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is larger, The first shift sleeve (18) is also not automatically disengaged from the first left clutch half (15), the first shift sleeve (18) is directly or indirectly connected to the first right clutch half (16) and rotates together with the first right clutch half (16), and/or the first right clutch half (16) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively moved in the axial direction relative to the first right clutch half (16) against the effect of the first right clutch half (16), and/or at least one series of axial positioning grooves or projections are formed on the first right clutch half (16), the first shift sleeve (18) is at least configured to perform an axial positioning function relative to the first right clutch half (16) through the series of axial positioning grooves or projections within a certain range, and/or the first positioning means (19) is directly or indirectly connected to the first right partial clutch (16), the first positioning means (19) rotates together with the first right partial clutch (16), the first positioning means (19) is axially fixed relative to the first right partial clutch (16), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), and the first positioning means (19) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first right partial clutch (16) against the effect of the first positioning means (19), and/or a series of axial positioning grooves or projections are provided on the first shift sleeve (18), the first shift sleeve (18) being configured at least such that it is connected to the first certain positioning grooves or projections via the series of axial positioning grooves or projections The constraining action of the position mechanism (19) within a certain range positions at least one axial position thereof, and/or the first shift sleeve (18) is directly or indirectly connected with the actuating device (AM) and the first shift sleeve (18) is selectively engaged and disengaged with the first left half clutch (15) under the driving of the actuating device (AM), and/or the first shift sleeve (18) is in a disengaged state with the first left half clutch (15) when the first shift sleeve (18) is in a certain position axially far away from the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), and/or the first shift sleeve (18) is in a certain position axially near the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), The first shift sleeve (18) is in engagement with the first left clutch half (15); and/or

The gear clutch mechanism (54) includes at least: a first left half clutch (15), a first right half clutch (16), a first shifting sleeve (18), and/or a first positioning mechanism (19), a first intermediate clutch (23), the first shifting sleeve (18), and/or the first positioning mechanism (19) being arranged coaxially with the first intermediate clutch (23), the first left half clutch (15) being arranged coaxially or non-coaxially with the first intermediate clutch (23), and/or the first right half clutch (16) being arranged coaxially or non-coaxially with the first intermediate clutch (23), the first left half clutch (15), the first shifting sleeve (18), and/or the first positioning mechanism (19), the first intermediate clutch (23) being arranged axially on one side of the first right half clutch (16), and/or the first intermediate clutch (23) coaxially passing through the first left half clutch (15), and/or the first intermediate clutch (23) coaxially passes through the first right half clutch (16), and/or the first left half clutch (15) coaxially passes through the first right half clutch (16), and/or the first right half clutch (16) coaxially passes through the first left half clutch (15), the first left half clutch (15) being directly or indirectly connected with the driving member of the machine (M) and rotating together with the driving member of the machine (M), and/or the first left half clutch (15) being directly or indirectly connected with the damping Device (DM) and rotating together with the damping Device (DM), and/or the first left half clutch (15) being directly or indirectly connected with the driven member of the machine (M) and rotating together with the driven member of the machine (M), and/or the first left half clutch (15) being directly or indirectly fixedly connected with the machine frame of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first right half clutch (16) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first right half clutch (16) is directly or indirectly connected with the driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first right half clutch (16) is directly or indirectly fixedly connected with the frame of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the driving part of the machine (M) and rotates along with the driving part of the machine (M), and/or the first intermediate clutch (23) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM) -a damping Device (DM) rotates together, and/or-the first intermediate clutch (23) is directly or indirectly connected to and rotates with a driven part of the machine (M), and/or-the first intermediate clutch (23) is directly or indirectly fixedly connected to a frame of the machine (M), -the first left half clutch (15) and the first right half clutch (16) and the first intermediate clutch (23) are at least configured with toothed projections and/or recesses, and-the first shift sleeve (18) is at least configured with a function of engaging or disengaging with the toothed projections and/or recesses, -the first left half clutch (15) is fixed in both forward and reverse directions relative to the first intermediate clutch (23) within a certain load range when the first shift sleeve (18) is engaged with the first left half clutch (15), and/or when the first shift sleeve (18) is engaged with the first right half clutch (16), within a certain load range, the first right half clutch (16) is fixed relative to the first intermediate clutch (23) in both forward and reverse directions, and/or when the first shift sleeve (18) is disengaged from the first left half clutch (15), within a certain load range, the first left half clutch (15) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or when the first shift sleeve (18) is disengaged from the first right half clutch (16), within a certain load range, when the first shift sleeve (18) is engaged with the first right half clutch (15), the first right half clutch (16) is rotatable relative to the first intermediate clutch (23) in both forward and reverse directions, and/or when the first shift sleeve (18) is engaged with the first left half clutch (15), The contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has an overload protection function, the first shifting gear sleeve (18) and the first left half clutch (15) are automatically separated when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is overlarge, and/or the contact pair of the first shifting gear sleeve (18) and the first left half clutch (15) has a self-locking function when the first shifting gear sleeve (18) and the first left half clutch (15) are in an engaged state, the first shifting gear sleeve (18) and the first left half clutch (15) are not automatically separated when the acting force between the first shifting gear sleeve (18) and the first left half clutch (15) is larger, and/or the first shifting gear sleeve (18) and the first right half clutch (16) are in an engaged state, The contact pair of the first shift gear sleeve (18) and the first right half clutch (16) has an overload protection function, the first shift gear sleeve (18) and the first right half clutch (16) are automatically separated when the acting force between the first shift gear sleeve (18) and the first right half clutch (16) is too large, and/or the contact pair of the first shift gear sleeve (18) and the first right half clutch (16) has a self-locking function when the first shift gear sleeve (18) and the first right half clutch (16) are in an engaged state, the first shift gear sleeve (18) and the first right half clutch (16) are not automatically separated when the acting force between the first shift gear sleeve (18) and the first right half clutch (16) is large, and the first shift gear sleeve (18) is directly or indirectly connected with the first intermediate clutch (23) and rotates together with the first intermediate clutch (23), and/or the first intermediate clutch (23) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction relative to the first intermediate clutch (23) against the effect of the first intermediate clutch (23), and/or at least one series of axial positioning grooves or projections are formed on the first intermediate clutch (23), the first shifting sleeve (18) is at least designed to perform the function of axial positioning relative to the first intermediate clutch (23) within a certain range by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected to the first intermediate clutch (23), the first positioning means (19) rotates together with the first intermediate clutch (23), the first positioning means (19) is fixed in the axial direction relative to the first intermediate clutch (23), and/or the first positioning means (19) is directly or indirectly connected to the first shifting sleeve (18) and the first positioning means (19) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction with respect to the first intermediate clutch (23) against the effect of the first positioning means (19), and/or the first shifting sleeve (18) is provided with a series of axial positioning grooves or projections, the first shifting sleeve (18) is at least configured to position at least one axial position thereof by the limiting effect of the series of axial positioning grooves or projections and the first positioning means (19) within a certain range, and/or the first shifting sleeve (18) is directly or indirectly connected to the actuating device (AM), And the first shift sleeve (18) is driven by the actuating device (AM) to move axially in a certain range relative to the first intermediate clutch (23) selectively, and/or when the first shift sleeve (18) is in a certain intermediate position in the axial direction directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) is in a disengaged state with the first left half clutch (15), the first shift sleeve (18) is in a disengaged state with the first right half clutch (16), and/or when the first shift sleeve (18) is in a certain position in the axial direction close to the first left half clutch (15) directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) is in an engaged state with the first left half clutch (15), The first shift sleeve (18) and the first right half clutch (16) are in a disengaged state, and/or when the first shift sleeve (18) is in a position close to the first right half clutch (16) in the axial direction directly or indirectly under the action of the actuating device (AM), the first shift sleeve (18) and the first left half clutch (15) are in a disengaged state, and the first shift sleeve (18) and the first right half clutch (16) are in an engaged state; and/or

7. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: a lever clutch mechanism (55);

the lever clutch mechanism (55) is at least provided with a lever for operating the connection and the disconnection of the main friction plate and the driven friction plate so as to selectively realize the connection and the disconnection of the power of the connected piece; and/or

The lever clutch mechanism (55) is configured to at least selectively transmit the power of one of the moving members to the other moving member by operating the engagement and disengagement of the driving friction plate and the driven friction plate with a lever; and/or

The lever clutch mechanism (55) is configured to at least use a lever to operate the connection and disconnection of the main friction plate and the driven friction plate so as to selectively transmit the power of one moving part to the other moving parts; and/or

The lever clutch mechanism (55) is configured to at least have an engaging and disengaging function for operating the engaging and disengaging of the driving friction plate and the driven friction plate by a lever so as to selectively realize the moving of the connected member; and/or

The lever clutch mechanism (55) is configured to have at least one of the moving members selectively transmitting the movement of one of the moving members to the other moving member by operating the engagement and disengagement of the master friction plate and the slave friction plate with a lever; and/or

The lever clutch mechanism (55) is configured to at least selectively transmit the motion of one of the moving members to the other moving members by operating the engagement and disengagement of the driving friction plate and the driven friction plate with a lever; and/or

The lever clutch mechanism (55) is configured to have at least a function of selectively keeping the moving member connected thereto rotationally accelerated or rotationally decelerated by operating the engagement and disengagement of the driving friction plate and the driven friction plate with a lever; and/or

The lever clutch mechanism (55) is configured to have at least a function of selectively stopping rotation of a moving member connected thereto by operating engagement and disengagement of a main friction plate and a driven friction plate with a lever; and/or

The lever clutch mechanism (55) is configured to have at least a function of selectively holding a moving member connected thereto in a rotating or fixed state by operating engagement and disengagement of a driving friction plate and a driven friction plate with a lever;

the lever clutch mechanism (55) comprises at least: the gear shifting device comprises a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), a first clutch rivet (7), a first shifting gear sleeve (18), a first positioning mechanism (19), a first lever mechanism (27), a first friction plate (33), a first dual plate (34), a first compensation spring (35), a first left bearing plate (36), a first right bearing plate (37), a first right snap ring (38) and/or a first left flange (39), wherein the first outer ring (2) is coaxially arranged on one side of the first inner ring (1) in the radial direction, and the first outer ring (2) and/or the first left clutch support (5), the first shifting gear sleeve (18) and/or the first positioning mechanism (19), the first friction plate (33), The first couple plate (34) and/or the first compensation spring (35), the first left bearing plate (36), the first right bearing plate (37), the first right snap ring (38) and/or the first left flange (39) are coaxially arranged with the first inner ring (1), the first outer ring (2), the first return spring (4) and/or the first left clutch bracket (5) and/or the first clutch rivet (7), the first shift gear sleeve (18) and/or the first positioning mechanism (19), the first lever mechanism (27), the first friction plate (33), the first couple plate (34) and/or the first compensation spring (35), the first left plate (36), the first right bearing plate (37), The first right snap ring (38) is arranged axially on one side of the first left flange (39), and/or the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first clutch rivet (7), the first shifting sleeve (18), and/or the first positioning mechanism (19), the first lever mechanism (27), the first friction plate (33), the first counter plate (34), and/or the first compensating spring (35), the first left bearing plate (36), the first right bearing plate (37), and the first right snap ring (38) are arranged axially on one side of the first left clutch bracket (5), the first inner ring (1) is directly or indirectly connected with and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with a driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M) And/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first left clutch support (5) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left clutch support (5) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left clutch support (5) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first left clutch support (5) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first left flange (39) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left flange (39) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first left flange (39) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first left flange (39) is directly or indirectly fixedly connected with a frame of the machine (M), the first lever mechanism (27) enables the first friction plate (33) and the first counter plate (34) to be in an engagement state when in an initial position, the first inner ring (1) is fixed relative to the first outer ring (2) in forward and reverse directions within a certain load range, or the first lever mechanism (27) enables the first friction plate (33) and the first counter plate (34) to be in a separation state when in the initial position, At the moment, the first inner ring (1) can rotate in the forward rotation direction and the reverse rotation direction relative to the first outer ring (2), the first lever mechanism (27) at least comprises a lever, the first lever mechanism (27) is directly or indirectly connected with the first outer ring (2), the first lever mechanism (27) rotates together with the first outer ring (2), the first lever mechanism (27) can rotate relative to the first outer ring (2) within a certain angle range under the action of the first shifting gear sleeve (18) directly or indirectly, and/or the first lever mechanism (27) is directly or indirectly connected with the first left clutch bracket (5), the first lever mechanism (27) rotates together with the first left clutch bracket (5), and the first lever mechanism (27) can rotate relative to the first left clutch bracket (5) within a certain angle range under the action of the first shifting gear sleeve (18) directly or indirectly And/or the first lever mechanism (27) is directly or indirectly connected with the first left flange (39), the first lever mechanism (27) rotates together with the first left flange (39), the first lever mechanism (27) is directly or indirectly rotatable relative to the first right clutch bracket (6) within a certain angle range under the action of the first shift gear sleeve (18), the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first outer ring (2) and rotates together with the first outer ring (2), and/or the first return spring (4) is directly or indirectly connected with the first lever mechanism (27), and when the action of other restraint or load on the first lever mechanism (27) is smaller than the action of the first return spring (4) on the first lever mechanism (27), The first lever mechanism (27) restores the initial position under the action of the first return spring (4), the first inner ring (1) is fixed relative to the first outer ring (2) in forward and reverse directions within a certain load range when the first friction plate (33) is engaged with the first counter plate (34), the first inner ring (1) is rotatable relative to the first outer ring (2) in forward and reverse directions within a certain load range when the first friction plate (33) is disengaged from the first counter plate (34), the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left flange (39) is directly or indirectly fixedly connected with the first outer ring (2), and/or the first left clutch carrier (5) is fixedly connected to the first outer ring (2) by means of the first clutch rivet (7), and/or the first left flange (39) is fixedly connected to the first outer ring (2) by means of the first clutch rivet (7), the first shift sleeve (18) is directly or indirectly connected to the first outer ring (2) and rotates together with the first outer ring (2), and/or the first outer ring (2) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first outer ring (2) against the effect of the first outer ring (2), and/or at least one series of axial detents or projections are formed on the first outer ring (2), by means of which the first shift sleeve (18) is at least configured in a certain range -a function of axial positioning with respect to the first outer ring (2), and/or-the first shift sleeve (18) is directly or indirectly connected to the first left clutch carrier (5) and rotates with the first left clutch carrier (5), and/or-the first left clutch carrier (5) has a certain limiting effect on the first shift sleeve (18) in the axial direction, -the first shift sleeve (18) is selectively movable in the axial direction with respect to the first left clutch carrier (5) against the effect of the first left clutch carrier (5), and/or-the first left clutch carrier (5) is configured with at least a series of axial positioning grooves or projections, the first shift sleeve (18) is configured at least in a certain range of axial positioning with respect to the first left clutch carrier (5) by means of the series of axial positioning grooves or projections, and/or the first shift sleeve (18) is directly or indirectly connected to the first left flange (39) and rotates together with the first left flange (39), and/or the first left flange (39) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first left flange (39) against the effect of the first left flange (39), and/or the first left flange (39) is at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least provided with a function of axial positioning relative to the first left flange (39) through the series of axial positioning grooves or projections in a certain range, and/or the first positioning means (19) is directly or indirectly connected to the first outer ring (2), The first positioning means (19) rotates together with the first outer ring (2), the first positioning means (19) is axially fixed relative to the first outer ring (2), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), the first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first left flange (39), the first positioning means (19) rotates together with the first left flange (39), the first positioning means (19) is axially fixed relative to the first left flange (39), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), And said first positioning means (19) having a limiting effect in an axial direction on said first shifting sleeve (18), said first shifting sleeve (18) being selectively axially movable with respect to said first outer ring (2) against the action of said first positioning means (19), and/or said first shifting sleeve (18) being provided with a series of axial positioning slots or projections, said first shifting sleeve (18) being configured to position at least one axial position thereof at least by the action of said series of axial positioning slots or projections and said first positioning means (19) within a certain range of constraint, and/or said first shifting sleeve (18) being directly or indirectly connected to said first lever means (27), and said first shifting sleeve (18) being selectively axially movable with respect to said first outer ring (2) within a certain range of at least direct or indirect contact of said first friction plate (33) with said first counter plate (18), (b) 34) In the engaged or disengaged state, and/or the first compensating spring (35) is directly or indirectly connected to the first lever arrangement (27), the first compensating spring (35) rotates with the first outer ring (2), the first compensating spring (35) moves axially within a certain range relative to the first outer ring (2) directly or indirectly under the action of the first lever arrangement (27), or the first left bearing plate (36) is directly or indirectly connected to the first lever arrangement (27), the first left bearing plate (36) rotates with the first outer ring (2), the first left bearing plate (36) moves axially within a certain range relative to the first outer ring (2) directly or indirectly under the action of the first lever arrangement (27), and/or the first compensating spring (35) is provided at least to compensate the first friction plate (33) and the first coupling plate (33) to some extent 34) A function of axial thickness reduction due to wear, and/or the first left bearing plate (36) is directly or indirectly connected with the first compensation spring (35), the first left bearing plate (36) rotates together with the first outer ring (2), and/or the first left bearing plate (36) moves axially relative to the first outer ring (2) within a certain range under the action of the first compensation spring (35), and/or the first pair of counter plates (34), and/or the first friction plate (33) is directly or indirectly connected with the first left bearing plate (36), and/or the first pair of counter plates (34) is directly or indirectly connected with the first left bearing plate (36), and/or the first friction plate (33) is directly or indirectly connected with the first right bearing plate (37), and/or the first counter plate (34) is directly or indirectly connected to the first right bearing plate (37), and/or the first friction plate (33) is directly or indirectly connected to the first counter plate (34), and/or the first friction plate (33) is directly or indirectly connected to the first inner ring (1), the first friction plate (33) rotates with the first inner ring (1), or the first friction plate (33) is directly or indirectly connected to the first outer ring (2), the first friction plate (33) rotates with the first outer ring (2), and/or the first friction plate (33) moves axially within a certain range with respect to the first inner ring (1) directly or indirectly by the action of the first counter plate (34), and/or the first left bearing plate (36), and/or the first right bearing plate (37), or the first friction plate (33) is directly or indirectly axially moved in a certain range relative to the first outer ring (2) under the action of the first pair of plates (34) and/or the first left bearing plate (36) and/or the first right bearing plate (37), and/or the first pair of plates (34) is directly or indirectly connected with the first inner ring (1), the first pair of plates (34) rotates together with the first inner ring (1), or the first pair of plates (34) is directly or indirectly connected with the first outer ring (2), the first pair of plates (34) rotates together with the first outer ring (2), and/or the first pair of plates (34) is directly or indirectly axially moved in a certain range relative to the first inner ring (1) under the action of the first friction plate (33) and/or the first left bearing plate (36) and/or the first right bearing plate (37) And/or said first counter plate (34) moves axially with respect to said first outer ring (2) within a certain range, directly or indirectly under the action of said first friction plate (33), and/or said first left bearing plate (36), and/or said first right bearing plate (37) is directly or indirectly connected to said first right snap ring (38), said first right bearing plate (37) rotates with said first outer ring (2), and/or said first right bearing plate (37) moves axially with respect to said first outer ring (2) within a certain range, directly or indirectly under the action of said first friction plate (33), and/or said first counter plate (34), and/or said first friction plate (33) comprises at least one friction plate, said first friction plate (33) being connected to said first inner ring (1) and moving with said first inner ring (1) Rotating together, the first friction disk (33) being movable in the axial direction relative to the first inner ring (1), or the first friction disk (33) being connected to the first outer ring (2) and rotating together with the first outer ring (2), the first friction disk (33) being movable in the axial direction relative to the first outer ring (2), or the first friction disk (33) being connected to the first left flange (39) and rotating together with the first left flange (39), the first friction disk (33) being movable in the axial direction relative to the first left flange (39), or the first friction disk (33) being connected to the first left clutch carrier (5) and rotating together with the first left clutch carrier (5), the first friction disk (33) being movable in the axial direction relative to the first left clutch carrier (5), and/or the first dual disk (34) comprising at least one dual disk, and/or the first doubler plate (34) is connected with the first left flange (39) and rotates together with the first left flange (39), the first doubler plate (34) is movable in the axial direction with respect to the first left flange (39), or the first doubler plate (34) is connected with the first outer ring (2) and rotates together with the first outer ring (2), the first doubler plate (34) is movable in the axial direction with respect to the first outer ring (2), or the first doubler plate (34) is connected with the first inner ring (1) and rotates together with the first inner ring (1), the first doubler plate (34) is movable in the axial direction with respect to the first inner ring (1), or the first doubler plate (34) is connected with the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), The first coupling plate (34) is axially movable relative to the first left clutch carrier (5) and/or the first left bearing plate (36) is connected to the first left flange (39) and rotates with the first left flange (39), the first left bearing plate (36) is axially movable relative to the first left flange (39), or the first left bearing plate (36) is connected to the first outer ring (2) and rotates with the first outer ring (2), the first left bearing plate (36) is axially movable relative to the first outer ring (2), or the first left bearing plate (36) is connected to the first inner ring (1) and rotates with the first inner ring (1), the first left bearing plate (36) is axially movable relative to the first inner ring (1), or the first left bearing plate (36) is connected to the first left clutch carrier (5) and rotates with the first left clutch carrier (5) The carrier (5) rotates together, the first left bearing plate (36) is movable in the axial direction relative to the first left clutch carrier (5), and/or the first right bearing plate (37) is connected to the first left flange (39) and rotates together with the first left flange (39), the first right bearing plate (37) is movable in the axial direction relative to the first left flange (39), or the first right bearing plate (37) is connected to the first outer ring (2) and rotates together with the first outer ring (2), the first right bearing plate (37) is movable in the axial direction relative to the first outer ring (2), or the first right bearing plate (37) is connected to the first inner ring (1) and rotates together with the first inner ring (1), the first right bearing plate (37) is movable in the axial direction relative to the first inner ring (1), or the first right bearing plate (37) is connected with the first left clutch support (5) and rotates together with the first left clutch support (5), the first right bearing plate (37) is movable in the axial direction relative to the first left clutch support (5), and/or the first right snap ring (38) is fixedly connected in the axial direction relative to the first left flange (39), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first outer ring (2), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first inner ring (1), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first left clutch support (5), and/or the first shift tooth sleeve (18) is directly or indirectly connected with the actuating device (AM), and the first shift tooth sleeve (18) is driven by the actuating device (AM) in a certain range relative to the first outer ring (2) -selectively axially and/or in which said first friction plate (33) is in engagement or disengagement with said first counter plate (34) when said first shift sleeve (18) is axially in a left position with respect to said first outer ring (2) directly or indirectly under the action of said Actuating Means (AM), and/or in which said first friction plate (33) is in disengagement or engagement with said first counter plate (34) when said first shift sleeve (18) is axially in a right position with respect to said first outer ring (2) directly or indirectly under the action of said Actuating Means (AM); and/or

The lever clutch mechanism (55) comprises at least: the gear shifting device comprises a first inner ring (1), a first outer ring (2), a first return spring (4), a first left clutch support (5), a first clutch rivet (7), a first shifting gear sleeve (18), a first positioning mechanism (19), a first lever mechanism (27), a first friction plate (33), a first dual plate (34), a first compensation spring (35), a first left bearing plate (36), a first right bearing plate (37), a first right snap ring (38) and/or a first left flange (39), wherein the first outer ring (2) is coaxially arranged on one side of the first inner ring (1) in the radial direction, and the first outer ring (2) and/or the first left clutch support (5), the first shifting gear sleeve (18) and/or the first positioning mechanism (19), the first friction plate (33), The first coupling plate (34), and/or the first compensating spring (35), the first left bearing plate (36), the first right bearing plate (37), the first right snap ring (38), and/or the first left flange (39) are coaxially arranged with the first inner ring (1), and/or the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first left clutch bracket (5), and/or the first clutch rivet (7), the first shift gear sleeve (18), and/or the first positioning mechanism (19), the first lever mechanism (27), the first friction plate (33), the first coupling plate (34), and/or the first compensating spring (35), the first left bearing plate (36), The first right bearing plate (37), the first right snap ring (38) are arranged on one side of the first left flange (39) in the axial direction, and/or the first inner ring (1), the first outer ring (2), the first return spring (4), and/or the first clutch rivet (7), the first shift sleeve (18), and/or the first positioning mechanism (19), the first lever mechanism (27), the first friction plate (33), the first pair of coupling plates (34), and/or the first compensation spring (35), the first left bearing plate (36), the first right bearing plate (37), and the first right snap ring (38) are arranged on one side of the first left clutch bracket (5) in the axial direction, the first inner ring (1) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first inner ring (1) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first inner ring (1) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M), and/or the first inner ring (1) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with a driving part of the machine (M) and rotates along with a driving part of the machine (M), and/or the first outer ring (2) is directly or indirectly connected with the damping Device (DM) and rotates along with the damping Device (DM), and/or the first outer ring (2) is directly or indirectly connected with a driven part of the machine (M) and rotates along with a driven part of the machine (M) And/or the first outer ring (2) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first left clutch support (5) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left clutch support (5) is directly or indirectly connected with the damping Device (DM) and rotates together with the damping Device (DM), and/or the first left clutch support (5) is directly or indirectly connected with a driven part of the machine (M) and rotates together with the driven part of the machine (M), and/or the first left clutch support (5) is directly or indirectly fixedly connected with a frame of the machine (M), and/or the first left flange (39) is directly or indirectly connected with a driving part of the machine (M) and rotates together with the driving part of the machine (M), and/or the first left flange (39) is directly or indirectly connected with the buffer damping Device (DM) and rotates along with the buffer damping Device (DM), and/or the first left flange (39) is directly or indirectly connected with a driven part of the machine (M) and rotates along with the driven part of the machine (M), and/or the first left flange (39) is directly or indirectly fixedly connected with a frame of the machine (M), the first lever mechanism (27) enables the first friction plate (33) and the first counter plate (34) to be in an engagement state when in an initial position, the first outer ring (2) is fixed relative to the first inner ring (1) in forward and reverse directions within a certain load range when in an initial position, or the first lever mechanism (27) enables the first friction plate (33) and the first counter plate (34) to be in a separation state when in an initial position, The first outer ring (2) can rotate in the forward rotation direction and the reverse rotation direction relative to the first inner ring (1) within a certain load range, the first lever mechanism (27) comprises at least one lever, the first lever mechanism (27) is directly or indirectly connected with the first inner ring (1), the first lever mechanism (27) rotates together with the first inner ring (1), the first lever mechanism (27) directly or indirectly rotates relative to the first inner ring (1) within a certain angle range under the action of the first shifting gear sleeve (18), and/or the first lever mechanism (27) is directly or indirectly connected with the first left clutch bracket (5), the first lever mechanism (27) rotates together with the first left clutch bracket (5), and the first lever mechanism (27) directly or indirectly rotates relative to the first left clutch bracket (1) within a certain angle range under the action of the first shifting gear sleeve (18) A bracket (5) rotates, and/or the first lever mechanism (27) is directly or indirectly connected with the first left flange (39), the first lever mechanism (27) rotates together with the first left flange (39), the first lever mechanism (27) rotates relative to the first left flange (39) within a certain angle range under the action of the first shifting gear sleeve (18), the first return spring (4) at least comprises one spring, the first return spring (4) is directly or indirectly connected with the first inner ring (1) and rotates together with the first inner ring (1), and/or the first return spring (4) is directly or indirectly connected with the first lever mechanism (27), when the action of other restraint or load on the first lever mechanism (27) is smaller than the action of the first return spring (4) on the first lever mechanism (27), The first lever mechanism (27) restores the initial position under the action of the first return spring (4), the first outer ring (2) is fixed relative to the first inner ring (1) in forward and reverse directions within a certain load range when the first friction plate (33) is engaged with the first counter plate (34), the first outer ring (2) is rotatable relative to the first inner ring (1) in forward and reverse directions within a certain load range when the first friction plate (33) is disengaged from the first counter plate (34), the first clutch rivet (7) at least comprises one rivet, the first left clutch bracket (5) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left flange (39) is directly or indirectly fixedly connected with the first inner ring (1), and/or the first left clutch carrier (5) is fixedly connected to the first inner ring (1) by means of the first clutch rivet (7), and/or the first left flange (39) is fixedly connected to the first inner ring (1) by means of the first clutch rivet (7), and/or the first shift sleeve (18) is directly or indirectly connected to the first inner ring (1) and rotates together with the first inner ring (1), and/or the first inner ring (1) has a certain limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction relative to the first inner ring (1) against the effect of the first inner ring (1), and/or at least one series of axial positioning grooves or projections are formed on the first inner ring (1), the first shift sleeve (18) being at least configured in a certain range by means of the series of axial positioning grooves or projections A function of axially positioning the recesses or projections relative to the first inner ring (1), and/or a function of axially positioning the first shift sleeve (18) directly or indirectly connected to the first left clutch carrier (5) and rotating with the first left clutch carrier (5), and/or a function of axially limiting the first shift sleeve (18), the first shift sleeve (18) being selectively axially movable relative to the first left clutch carrier (5) against the action of the first left clutch carrier (5), and/or a function of axially positioning the first shift sleeve (18) relative to the first left clutch carrier (5) at least to a certain extent by means of the series of axial recesses or projections, the first shift sleeve (18) being configured at least to a certain extent, and/or the first shift sleeve (18) is directly or indirectly connected to the first left flange (39) and rotates together with the first left flange (39), and/or the first left flange (39) has a limiting effect on the first shift sleeve (18) in the axial direction, the first shift sleeve (18) is selectively movable in the axial direction against the first left flange (39) against the effect of the first left flange (39), and/or the first left flange (39) is at least provided with a series of axial positioning grooves or projections, the first shift sleeve (18) is at least provided with a function of axial positioning in a certain range relative to the first left flange (39) by means of the series of axial positioning grooves or projections, and/or the first positioning means (19) is directly or indirectly connected to the first inner ring (1), The first positioning means (19) rotates together with the first inner ring (1), the first positioning means (19) is axially fixed relative to the first inner ring (1), and/or the first positioning means (19) is directly or indirectly connected to the first left clutch carrier (5), the first positioning means (19) rotates together with the first left clutch carrier (5), the first positioning means (19) is axially fixed relative to the first left clutch carrier (5), and/or the first positioning means (19) is directly or indirectly connected to the first left flange (39), the first positioning means (19) rotates together with the first left flange (39), the first positioning means (19) is axially fixed relative to the first left flange (39), and/or the first positioning means (19) is directly or indirectly connected to the first shift sleeve (18), And the first positioning means (19) has a limiting effect on the first shifting sleeve (18) in the axial direction, the first shifting sleeve (18) is selectively movable in the axial direction relative to the first inner ring (1) against the action of the first positioning means (19), and/or the first shifting sleeve (18) is provided with a series of axial positioning slots or protrusions, the first shifting sleeve (18) is at least configured to position at least one axial position thereof by the limited action of the series of axial positioning slots or protrusions and the first positioning means (19), and/or the first shifting sleeve (18) is directly or indirectly connected to the first lever means (27), and the selective axial movement of the first shifting sleeve (18) relative to the first inner ring (1) within a certain range at least directly or indirectly causes the first friction plate (33) and the first counter plate (18) 34) In the engaged or disengaged state, and/or the first compensating spring (35) is directly or indirectly connected to the first lever arrangement (27), the first compensating spring (35) rotates with the first inner ring (1), the first compensating spring (35) is directly or indirectly axially movable within a certain range relative to the first inner ring (1) under the action of the first lever arrangement (27), or the first left bearing plate (36) is directly or indirectly connected to the first lever arrangement (27), the first left bearing plate (36) rotates with the first inner ring (1), the first left bearing plate (36) is directly or indirectly axially movable within a certain range relative to the first inner ring (1) under the action of the first lever arrangement (27), and/or the first compensating spring (35) is provided at least to compensate the first friction plate (33) and the first coupling plate (33) to some extent 34) A function of axial thickness reduction due to wear, and/or the first left bearing plate (36) is directly or indirectly connected with the first compensation spring (35), the first left bearing plate (36) rotates together with the first inner ring (1), and/or the first left bearing plate (36) moves axially relative to the first inner ring (1) within a certain range under the action of the first compensation spring (35), and/or the first pair of counter plates (34), and/or the first friction plate (33) is directly or indirectly connected with the first left bearing plate (36), and/or the first pair of counter plates (34) is directly or indirectly connected with the first left bearing plate (36), and/or the first friction plate (33) is directly or indirectly connected with the first right bearing plate (37), and/or the first counter plate (34) is directly or indirectly connected to the first right bearing plate (37), and/or the first friction plate (33) is directly or indirectly connected to the first counter plate (34), and/or the first friction plate (33) is directly or indirectly connected to the first inner ring (1), the first friction plate (33) rotates with the first inner ring (1), or the first friction plate (33) is directly or indirectly connected to the first outer ring (2), the first friction plate (33) rotates with the first outer ring (2), and/or the first friction plate (33) moves axially within a certain range with respect to the first inner ring (1) directly or indirectly by the action of the first counter plate (34), and/or the first left bearing plate (36), and/or the first right bearing plate (37), or the first friction plate (33) is directly or indirectly axially moved in a certain range relative to the first outer ring (2) under the action of the first pair of plates (34) and/or the first left bearing plate (36) and/or the first right bearing plate (37), and/or the first pair of plates (34) is directly or indirectly connected with the first inner ring (1), the first pair of plates (34) rotates together with the first inner ring (1), or the first pair of plates (34) is directly or indirectly connected with the first outer ring (2), the first pair of plates (34) rotates together with the first outer ring (2), and/or the first pair of plates (34) is directly or indirectly axially moved in a certain range relative to the first inner ring (1) under the action of the first friction plate (33) and/or the first left bearing plate (36) and/or the first right bearing plate (37) -moving and/or said first counter plate (34) axially moves within a certain range with respect to said first outer ring (2) directly or indirectly under the action of said first friction plate (33) and/or said first left bearing plate (36) and/or said first right bearing plate (37), and/or said first right bearing plate (37) is directly or indirectly connected with said first right snap ring (38), said first right bearing plate (37) rotates with said first inner ring (1), and/or said first right bearing plate (37) axially moves within a certain range with respect to said first inner ring (1) directly or indirectly under the action of said first friction plate (33) and/or said first counter plate (34), and/or said first friction plate (33) comprises at least one friction plate, and/or the first friction disk (33) is connected to the first inner ring (1) and rotates together with the first inner ring (1), the first friction disk (33) is movable in the axial direction relative to the first inner ring (1), or the first friction disk (33) is connected to the first outer ring (2) and rotates together with the first outer ring (2), the first friction disk (33) is movable in the axial direction relative to the first outer ring (2), or the first friction disk (33) is connected to the first left flange (39) and rotates together with the first left flange (39), the first friction disk (33) is movable in the axial direction relative to the first left flange (39), or the first friction disk (33) is connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), The first friction plate (33) is axially movable relative to the first left clutch carrier (5), and/or the first pair of plates (34) comprises at least one pair plate, and/or the first pair of plates (34) is connected to the first left flange (39) and rotates with the first left flange (39), the first pair of plates (34) is axially movable relative to the first left flange (39), or the first pair of plates (34) is connected to the first outer ring (2) and rotates with the first outer ring (2), the first pair of plates (34) is axially movable relative to the first outer ring (2), or the first pair of plates (34) is connected to the first inner ring (1) and rotates with the first inner ring (1), the first pair of plates (34) is axially movable relative to the first inner ring (1), or the first coupling plate (34) is connected to the first left clutch carrier (5) and rotates together with the first left clutch carrier (5), the first coupling plate (34) is axially movable relative to the first left clutch carrier (5), and/or the first left bearing plate (36) is connected to the first left flange (39) and rotates together with the first left flange (39), the first left bearing plate (36) is axially movable relative to the first left flange (39), or the first left bearing plate (36) is connected to the first outer ring (2) and rotates together with the first outer ring (2), the first left bearing plate (36) is axially movable relative to the first outer ring (2), or the first left bearing plate (36) is connected to the first inner ring (1) and rotates together with the first inner ring (1), The first left bearing plate (36) being axially movable relative to the first inner ring (1), or the first left bearing plate (36) being connected with the first left clutch support (5) and rotating together with the first left clutch support (5), the first left bearing plate (36) being axially movable relative to the first left clutch support (5), and/or the first right bearing plate (37) being connected with the first left flange (39) and rotating together with the first left flange (39), the first right bearing plate (37) being axially movable relative to the first left flange (39), or the first right bearing plate (37) being connected with the first outer ring (2) and rotating together with the first outer ring (2), the first right bearing plate (37) being axially movable relative to the first outer ring (2), or the first right bearing plate (37) is connected with the first inner ring (1) and rotates together with the first inner ring (1), the first right bearing plate (37) is movable in the axial direction relative to the first inner ring (1), or the first right bearing plate (37) is connected with the first left clutch bracket (5) and rotates together with the first left clutch bracket (5), the first right bearing plate (37) is movable in the axial direction relative to the first left clutch bracket (5), and/or the first right snap ring (38) is fixedly connected in the axial direction relative to the first left flange (39), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first outer ring (2), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first inner ring (1), or the first right snap ring (38) is fixedly connected in the axial direction relative to the first left clutch bracket (5), and/or the first shift sleeve (18) is directly or indirectly connected to the actuating device (AM) and the first shift sleeve (18) is selectively axially movable relative to the first inner ring (1) within a range under the drive of the actuating device (AM), and/or the first friction plate (33) is in an engaged or disengaged state with the first counter plate (34) when the first shift sleeve (18) is axially at a left end position with respect to the first inner ring (1) directly or indirectly under the action of the Actuating Means (AM), and/or the first friction plate (33) is in a disengaged or engaged state with the first counter plate (34) when the first shift sleeve (18) is at a right end position axially with respect to the first inner ring (1) directly or indirectly under the action of the Actuating Means (AM); and/or

The material of the first friction plate (33) at least has a certain vibration damping or damping function; and/or

The material of the first coupling piece (34) at least has certain vibration damping or damping function; and/or

The material of the first compensation spring (35) at least has certain vibration damping or damping function; and/or

The material of the first left bearing plate (36) at least has certain vibration damping or damping function; and/or

The material of the first right bearing plate (37) at least has certain vibration damping or damping function; and/or

The first right clamping ring (38) is made of a material which at least has a certain vibration reduction or damping function; and/or

The material of the first left flange (39) at least has certain vibration damping or damping function.

8. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Clutch Means (CM) comprising at least: an operating clutch (56), and/or an automatic clutch (57), and/or a mechanical clutch (58), and/or a manual clutch (59), and/or an electromagnetic clutch (60), and/or a hydraulic clutch (61), and/or a pneumatic clutch (62), and/or an overrunning clutch (63), and/or a centrifugal clutch (64), and/or a safety clutch (65), and/or a nested clutch (66), and/or a friction clutch (67), and/or a dry clutch (68), and/or a wet clutch (69), and/or a resilient clutch (70), and/or a rigid clutch (71), and/or a one-way clutch (72), and/or a two-way clutch (73), and/or a normally open clutch (74), And/or a normally closed clutch (75), and/or a disk clutch (76), and/or a dog clutch (77), and/or a tooth clutch (78), and/or a cone clutch (79), and/or a friction block clutch (80), and/or a pin clutch (81), and/or a key clutch (82), and/or a race clutch (83), and/or a torsion spring clutch (84), and/or a belt clutch (85), and/or a block clutch (86), and/or a drum clutch (87), and/or a diaphragm clutch (88), and/or a pneumatic clutch (89), and/or a roller clutch (90), and/or a sprag clutch (91), and/or a ratchet clutch (92), and/or a synchronizing clutch (93), And/or a steel ball clutch (94), and/or a magnetic particle clutch (95), and/or a double-acting clutch (96), and/or a speed-regulating clutch (97), and/or a permanent-magnet clutch (98), and/or a double clutch (99), and/or a multi-mode clutch (100), and/or a direct-contact brake (101), and/or a non-direct-contact brake (102), and/or a friction brake (103), and/or a non-friction brake (104), and/or a normally-open brake (105), and/or a normally-closed brake (106), and/or a one-way brake (107), and/or a two-way brake (108), and/or a friction brake (103), and/or a dry brake (110), and/or a hydraulic brake (111), And/or a pneumatic brake (112), and/or an electromagnetic brake (113), and/or an inertia brake (114), and/or a gravity brake (115), and/or a centrifugal brake (116), and/or a mechanical brake (117), and/or a human brake (118), and/or a self-locking brake (119), and/or a dog brake (120), and/or a drum brake (121), and/or a band brake (122), and/or a disc brake (123), and/or a caliper disc brake (124), and/or a fixed caliper disc brake (125), and/or a floating caliper disc brake (126), and/or an all-disc brake (127), and/or a multi-disc brake (128), and/or a cone brake (129), And/or a block brake (130), and/or a band-type brake-enable brake (131), and/or an internal-expanding brake (132), and/or a wedge-type brake (133), and/or a cam brake (134), and/or a plunger brake (135), and/or a push-rod brake (136), and/or a leading shoe brake (137), and/or a trailing shoe brake (138), and/or an air bag brake (139), and/or a magnetic particle brake (140), and/or an eddy-current brake (141), and/or a hysteresis brake (142), and/or an eddy-current brake (143), and/or a retarder brake (144), and/or a safety brake (145), and/or a service brake (146), and/or a parking brake (147), And/or a dual brake (148), and/or a multi-mode brake (149);

The operating clutch (56) at least has a clutch function realized by directly or indirectly operating the combination element; and/or

The self-control clutch (57) at least has a function that the combination element has self-clutch function when some performance parameters of the driving part or the driven part of the self-control clutch change; and/or

The mechanical clutch (58) at least has the function of realizing the clutch under the direct action of a mechanical mechanism; and/or

The manual clutch (59) at least has the function of realizing the clutch under the direct or indirect action of manpower; and/or

The electromagnetic clutch (60) at least has the function of realizing the clutch under the direct or indirect action of electromagnetic force; and/or

The hydraulic clutch (61) at least has the function of realizing the clutch under the direct or indirect action of the hydraulic pressure; and/or

The pneumatic clutch (62) at least has the function of realizing the clutch under the direct or indirect action of gas pressure; and/or

The overrunning clutch (63) is at least provided when the speed of the driving part or the driven part changes; or when the rotation direction of the driving part or the driven part is changed, the clutch has the function of self-clutch; and/or

The centrifugal clutch (64) at least has the function of realizing the clutch under the direct or indirect action of the centrifugal force of the centrifugal body; and/or

The safety clutch (65) has at least the function of directly or indirectly ensuring that the torque or the rotating speed transmitted by the safety clutch does not exceed a certain limit value; and/or

The embedded clutch (66) at least comprises a joint element of a driving part or a driven part thereof, and realizes the clutch function by adopting a mechanical embedded pair; and/or

The friction clutch (67) at least comprises a driving part or a driven part of the engaging element, and realizes the clutch function by adopting a friction pair; and/or

The dry clutch (68) at least comprises a joint element of a driving part or a driven part thereof, and realizes the clutch function by adopting a friction pair under the dry friction condition; and/or

The wet clutch (69) is at least provided with a joint element of a driving part or a driven part thereof, and the clutch function is realized by adopting a friction pair under the wet friction condition; and/or

The elastic clutch (70) at least has the functions of elasticity and damping action on the power or motion transmitted by the elastic clutch; and/or

The rigid clutch (71) has at least a function of rigid and undamped to the power or motion transmitted by the rigid clutch; and/or the one-way clutch (72); and/or

The bidirectional clutch (73) has at least the function of transmitting power or motion in the forward and reverse rotation directions; and/or

The normally open clutch (74) is at least provided with a clutch of which the engaging element is in a disengaged state when the operating force is removed; and/or

The normally closed clutch (75) is at least provided with a clutch, the engaging element of which is in an engaged state after the operating force is removed; and/or

The disc clutch (76) at least has the function of realizing the clutch by directly or indirectly utilizing the friction pair formed by the end surfaces of the circular ring sheets; and/or

The jaw clutch (77) at least has a clutch function realized by directly or indirectly utilizing a jogged pair consisting of claw-shaped parts; and/or

The tooth clutch (78) at least has the function of realizing the clutch by directly or indirectly utilizing the jogged pair consisting of tooth parts; and/or

The conical clutch (79) at least has the function of realizing the clutch by directly or indirectly utilizing a friction pair consisting of conical surfaces; and/or

The friction block clutch (80) at least has a clutch function realized by directly or indirectly utilizing a friction pair formed by the end surface of the friction block and a coupling part; and/or

The pin type clutch (81) at least has a clutch function realized by directly or indirectly utilizing a jogged pair consisting of a pin and a pin seat part; and/or

The key type clutch (82) at least has a clutch function realized by directly or indirectly utilizing a jogged pair consisting of keys and key seat parts; and/or

The piston ring clutch (83) at least has the function of directly or indirectly realizing the clutch by using a friction pair consisting of the outer cylindrical surface of the piston ring and a coupling part; and/or

The torsion spring clutch (84) at least has the function of realizing the clutch by directly or indirectly utilizing a friction pair formed by an inner cylindrical surface of a torsion spring and a coupling part; and/or

The brake band clutch (85) at least has the function of directly or indirectly utilizing a friction pair formed by a friction material and a coupling part fixed on the inner cylindrical surface of the brake band to realize the clutch; and/or

The brake block clutch (86) at least has the function of directly or indirectly realizing the clutch by using a friction pair formed by a friction material and a coupling part fixed on the outer cylindrical surface of the brake block; and/or

The drum clutch (87) at least has a clutch function realized by directly or indirectly utilizing a friction pair consisting of cylinders; and/or

The diaphragm clutch (88) at least has the function of directly or indirectly utilizing air pressure to be applied to the friction pair through a diaphragm to realize the clutch; and/or

The pneumatic tire clutch (89) at least has the function of directly or indirectly applying air pressure to the friction pair through a pneumatic tire to realize the clutch; and/or

The roller clutch (90) at least has a clutch function realized by directly or indirectly utilizing a friction pair consisting of the rollers, the star wheel and the rollers and the roller paths; and/or

The wedge clutch (91) at least has a clutch function realized by directly or indirectly utilizing a friction pair consisting of a wedge, an inner raceway and an outer raceway; and/or

The ratchet clutch (92) at least has the function of realizing the clutch by directly or indirectly utilizing an embedded pair consisting of a ratchet and a pawl; and/or

The synchronous clutch (93) at least has the functions of automatically engaging after the rotation speed of the driving part and the driven part is synchronous, and automatically disengaging when a certain rotation speed difference exists between the driving part and the driven part; and/or

The steel ball clutch (94) at least has the function of utilizing a steel ball as a centrifugal body and realizing the clutch function under the direct or indirect action of the centrifugal force of the steel ball; and/or

The magnetic powder clutch (95) at least comprises a magnetic powder clutch, wherein magnetic powder is filled in a gap between a driving part and a driven part of the magnetic powder clutch, and the clutch function is realized directly or indirectly by means of the binding force between the magnetic powder and the friction force between the magnetic powder and a working surface; and/or

Said double-acting clutch (96) having at least the function of selectively transmitting the power or motion of one of its driving parts to its two driven parts, respectively; and/or

The speed regulation clutch (97) at least has the function that the rotating speed of the driving part is constant, and the stepless speed regulation is carried out on the driven part directly or indirectly by using the oil film action; and/or

The permanent magnet clutch (98) at least has the function of realizing the clutch by utilizing the magnetic force of a magnetic material; and/or

The double clutch (99) is provided at least with a function of transmitting power or motion between one driving part and two driven parts thereof respectively and with an engaging or disengaging function; and/or

The multimode clutch (100) is provided at least with the function of transmitting power or motion between a driving part and at least one driven part thereof and has a plurality of engaging or disengaging functions; and/or

The direct contact type brake (101) at least has the function of realizing the braking of a moving part thereof through the direct contact between a braking part and the moving part thereof; and/or

The non-direct contact type brake (102) at least has the function of realizing the braking of a moving part thereof through the non-direct contact between a braking part and the moving part thereof; and/or

The friction brake (103) at least has the function of realizing the braking of the moving part through a friction pair formed between the braking part and the moving part; and/or

The non-friction brake (104) at least has the function of realizing the braking of the moving part through a non-friction pair formed between the braking part and the moving part; and/or

The normally open brake (105) at least has the function of not having the braking action on the moving part when the driving part stops working; and/or

The normally closed brake (106) at least has the function of braking the moving part when the driving part stops working; and/or

The one-way brake (107) at least has the function of generating or eliminating braking action on a moving part in one moving direction; and/or

The bidirectional brake (108) at least has the function of generating or eliminating braking action on a moving part in two moving directions; and/or

The dry brake (109) has at least the function of generating or eliminating the braking action on the moving part under the dry friction condition; and/or

The wet brake (110) at least has the function of generating or eliminating braking action on a moving part under wet friction conditions; and/or

The hydraulic brake (111) at least has the function of generating or eliminating braking action on a moving part of the hydraulic brake by directly or indirectly utilizing hydraulic pressure; and/or

The pneumatic brake (112) at least has the function of directly or indirectly utilizing the gas pressure to generate or eliminate the braking action on the moving part; and/or

The electromagnetic brake (113) at least has the function of directly or indirectly utilizing electromagnetic force to generate or eliminate braking action on a moving part of the electromagnetic brake; and/or

The inertia brake (114) at least has the function of directly or indirectly utilizing inertia force to generate or eliminate braking action on a moving part of the inertia brake; and/or

The gravity brake (115) at least has the function of directly or indirectly utilizing gravity to generate or eliminate braking action on a moving part of the gravity brake; and/or

The centrifugal brake (116) at least has the function of directly or indirectly utilizing centrifugal force to generate or eliminate braking action on a moving part of the centrifugal brake; and/or

The mechanical brake (117) at least has the function of directly or indirectly utilizing the action of the mechanical mechanism to generate or eliminate the braking action on the moving part; and/or

The manual brake (118) at least has the function of directly or indirectly utilizing the action of the manual force to generate or eliminate the braking action on the moving part; and/or

The self-locking brake (119) at least has the function of directly or indirectly utilizing the action of the mechanical self-weight of the moving part to generate or eliminate the braking action on the moving part; and/or

The jaw brake (120) at least has the function of directly or indirectly utilizing the embedding pair formed by the direct contact of the moving part and the braking part to generate or eliminate the braking action on the moving part; and/or

The drum brake (121) at least has the function of generating or eliminating the braking action on a moving part of the drum brake by directly or indirectly utilizing a friction pair formed by directly contacting a cylindrical surface; and/or

The band brake (122) at least has the function of generating or eliminating braking action on a moving part of the band brake by directly or indirectly utilizing a friction pair formed by direct contact of a brake band; and/or

The disc brake (123) at least has the function of generating or eliminating braking action on a moving part of the disc brake by directly or indirectly utilizing a friction pair formed by direct contact of the end surface of the disc; and/or

The caliper disc brake (124) at least has the function of generating or eliminating braking action on a moving part of the caliper disc brake by directly or indirectly utilizing a friction pair formed by the direct contact between the end surface of the brake disc and the brake caliper; and/or

The fixed caliper disc brake (125) at least has the functions that the caliper is fixed, the pressurizing mechanisms are arranged on the two sides of the brake disc, and the friction pair formed by the direct contact of the disc end surface and the caliper generates or eliminates the braking action on a moving part of the brake disc; and/or

The floating caliper disc brake (126) at least has the function that the caliper floats, only one side of the brake disc is provided with a pressurizing mechanism, and the floating caliper generates pressing force on the other side of the brake disc so as to generate or eliminate braking action on a moving part of the brake disc; and/or

The full-disc brake (127) at least has the function of directly or indirectly utilizing the friction pair of the whole disc end surface to generate or eliminate the braking action on the moving part; and/or

The multi-plate disc brake (128) at least has the function of directly or indirectly utilizing a plurality of friction pairs to generate or eliminate braking action on moving parts of the multi-plate disc brake; and/or

The conical brake (129) at least has the function of directly or indirectly utilizing a friction pair formed by a conical surface to generate or eliminate the braking action on a moving part; and/or

The block brake (130) at least has the function of directly or indirectly utilizing a friction pair formed by the cylindrical surface of the pad and a moving part thereof to generate or eliminate the braking action on the moving part; and/or

The band-type brake enables the brake (131) to have at least the function of directly or indirectly utilizing the function of a friction pair formed by pressing the brake component against the outer surface of the moving component of the brake component to generate or eliminate the braking action on the moving component of the brake component; and/or

The internal expanding brake (132) at least has the function of generating or eliminating braking action on a moving part of the internal expanding brake by a friction pair formed by directly or indirectly pressing the outer surface of the brake part against the moving part; and/or

The wedge type brake (133) at least has the function of generating or eliminating braking action on a moving part of the wedge type brake by a friction pair formed by directly or indirectly forcing a braking part of the wedge type brake to be pressed against the moving part of the wedge type brake; and/or

The cam brake (134) at least has the function of directly or indirectly forcing the brake part to be in contact with or separated from the moving part by using a cam so as to generate or eliminate brake action on the moving part; and/or

The plunger brake (135) at least has the function of directly or indirectly using the plunger to force the brake part to contact or separate from the moving part thereof so as to generate or eliminate the brake action on the moving part thereof; and/or

The push rod brake (136) at least has the function of directly or indirectly using a push rod to force the brake part to contact or separate from the moving part thereof so as to generate or eliminate brake action on the moving part thereof; and/or

The leading shoe brake (137) at least has the function of directly or indirectly utilizing a friction pair formed by the direct contact of the leading shoe and the cylindrical surface to generate or eliminate the braking action on a moving part of the leading shoe brake; and/or

The slave shoe brake (138) at least has the function of directly or indirectly utilizing a friction pair formed by the direct contact of the slave shoe and the cylindrical surface to generate or eliminate the braking action on a moving part of the slave shoe brake; and/or

The air bag brake (139) at least has the function of directly or indirectly utilizing the air bag to generate or eliminate the braking action on the moving part; and/or

The magnetic powder brake (140) at least has the function of directly or indirectly utilizing the electromagnetic force among the magnetic powder and the friction force between the magnetic powder and the working surface to generate or eliminate the braking action on a moving part; and/or

The electric eddy current brake (141) at least has the function of directly or indirectly utilizing the eddy current action generated by electromagnetic induction to generate or eliminate the braking action on a moving part; and/or

The hysteresis brake (142) at least has the function of directly or indirectly utilizing hysteresis to generate or eliminate braking action on a moving part of the hysteresis brake; and/or

The eddy current brake (143) at least has the function of directly or indirectly utilizing the eddy current action of the liquid to generate or eliminate the braking action on the moving part; and/or

The retarder brake (144) at least has the function of reducing the rotating speed of the moving part but not stopping the moving part; and/or

The safety brake (145) at least has the function of generating or eliminating braking action on the moving part when the torque or the rotating speed transmitted by the moving part exceeds a certain limit value; and/or

The service brake (146) has at least a function of decelerating and stopping the moving machine in running; and/or

The parking brake (147) has at least a function of holding a stationary moving machine in a stopped state; and/or

The double brake (148) at least has the function of generating or eliminating braking action on two moving parts thereof; and/or

The multi-mode brake (149) has at least a function of generating or eliminating a plurality of braking actions on one or more moving parts.

9. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said Damping Means (DM) comprising at least: a friction buffer damping mechanism (201), and/or a hydraulic buffer damping mechanism (202), and/or a spring buffer damping mechanism (203), and/or a material buffer damping mechanism (204), and/or a magnetic powder buffer damping mechanism (205), and/or a pneumatic buffer damping mechanism (206), and/or an electromagnetic buffer damping mechanism (207), and/or a piezoelectric buffer damping mechanism (208), and/or a magnetostrictive buffer damping mechanism (209), and/or a hysteresis damping mechanism (210), and/or an eddy current damping mechanism (211);

the friction buffer damping mechanism (201) is at least provided with the function of damping or eliminating the vibration and impact generated in the process of separating and engaging the clutch device (CM) by utilizing various damping actions or friction actions of the components; and/or

The friction buffer damping mechanism (201) is at least provided with the function of damping or eliminating dynamic vibration and impact of one part of the machine (M) by utilizing various damping actions or friction actions of the components; and/or

The friction buffer damping mechanism (201) is configured to at least have the function of transmitting power by various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of limiting the transmitted power by utilizing various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of buffering transmitted power vibration and impact by utilizing various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of damping transmitted power vibration and impact by utilizing various damping actions or friction actions; and/or

The friction damping mechanism (201) is configured to have at least the function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The friction damping mechanism (201) is configured to have at least a function of transmitting a part or all of the power of a component of the machine (M) to the clutch device (CM); and/or

The friction buffer damping mechanism (201) is at least provided with a function of selectively limiting the transmitted power by using the friction action of the component; and/or

The friction buffer damping mechanism (201) is configured to at least have a function of selectively limiting the magnitude of the transmitted impact by utilizing various damping actions or friction actions of the components thereof; and/or

The friction buffer damping mechanism (201) is configured to at least have a function of selectively limiting the magnitude of the transmitted vibration by utilizing various damping actions or friction actions of the components thereof; and/or

The friction buffer damping mechanism (201) is at least provided with a function of selectively limiting the transmitted torque by utilizing various damping actions or friction actions of components; and/or

The friction buffer damping mechanism (201) is at least provided with a function of selectively limiting the transmitted load by various damping actions or friction actions of the components; and/or

The friction buffer damping mechanism (201) is configured to have at least a function of transmitting motion by various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of limiting the transmitted motion by utilizing various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of buffering transmitted motion vibration and impact by utilizing various damping actions or friction actions; and/or

The friction buffer damping mechanism (201) is at least provided with a function of damping the transmitted motion vibration and impact by various damping actions or friction actions; and/or

Said friction damping mechanism (201) being configured to have at least the function of transmitting part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

The friction damping mechanism (201) is configured to have at least the function of transmitting part or all of the movement of a component of the machine (M) to the clutch device (CM); and/or

The friction damping mechanism (201) is configured to have at least a function of selectively restricting the transmitted motion by the friction action of the members thereof;

the hydraulic buffer damping mechanism (202) is at least provided with the function of damping or eliminating vibration and impact generated in the process of separating and connecting the clutch device (CM) by utilizing various damping actions and buffer actions of the pressurized fluid on mechanical structures; and/or

The hydraulic buffer damping mechanism (202) is at least provided with the function of damping or eliminating dynamic vibration and impact of one component of the machine (M) by utilizing various damping effects and buffering effects of the pressurized fluid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of limiting the transmitted power by utilizing various damping actions and buffering actions of the pressurized fluid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of buffering transmitted power vibration and impact by utilizing various damping actions and buffering actions of the pressurized liquid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of damping transmitted power vibration and impact by utilizing various damping functions and buffering functions of the pressurized liquid on a mechanical structure; and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of transmitting a part of or the whole of the power of a component of the machine (M) to the clutch device (CM); and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively limiting the magnitude of transmitted power by utilizing various damping actions and cushioning actions of the pressurized fluid on the mechanical structure; and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively limiting the magnitude of transmitted impact by utilizing various damping actions and cushioning actions of the pressurized fluid on the mechanical structure; and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively limiting the magnitude of transmitted vibration by utilizing various damping actions and damping actions of the pressurized fluid on the mechanical structure; and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively limiting the magnitude of transmitted torque by utilizing various damping actions and damping actions of the pressurized fluid on the mechanical structure; and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively limiting the magnitude of the transmitted load by utilizing various damping actions and cushioning actions of the pressurized fluid on the mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with the function of transmitting motion by utilizing various damping actions and buffer actions of the pressurized fluid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of limiting transmitted movement by utilizing various damping actions and buffer actions of the pressurized fluid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of buffering transmitted motion vibration and impact by utilizing various damping actions and buffering actions of the pressurized liquid on a mechanical structure; and/or

The hydraulic buffer damping mechanism (202) is at least provided with a function of damping the transmitted motion vibration and impact by utilizing various damping functions and buffering functions of the pressurized liquid on the mechanical structure; and/or

Said hydraulic cushion damping mechanism (202) being configured to function at least to transmit part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

Said hydraulic cushion damping mechanism (202) being configured to have at least the function of transmitting part or all of the movement of a component of said machine (M) to said clutch device (CM); and/or

The hydraulic cushion damping mechanism (202) is configured to have at least a function of selectively restricting the transmitted motion by a friction action of a member thereof;

the spring buffer damping mechanism (203) is at least provided with the function of damping or eliminating the vibration and impact generated in the process of separating and connecting the clutch device (CM) by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with the function of damping or eliminating dynamic vibration and impact of one part of the machine (M) by utilizing the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of limiting the transmitted power by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of buffering transmitted power vibration and impact by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of damping transmitted power vibration and impact by using damping action of various springs; and/or

The spring-damper damping mechanism (203) is configured to have at least a function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The spring-damper damping mechanism (203) is configured to have at least a function of transmitting a part or all of power of a component of the machine (M) to the clutch device (CM); and/or

The spring buffer damping mechanism (203) is at least provided with a function of selectively limiting the transmitted power by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is configured to have at least a function of selectively limiting the magnitude of the transmitted impact by the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of selectively limiting the transmitted vibration by the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of selectively limiting the transmitted torque by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of selectively limiting the magnitude of the transmitted load by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is configured to have at least a function of transmitting motion by damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of limiting the transmitted motion by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of buffering transmitted motion vibration and impact by using the damping action of various springs; and/or

The spring buffer damping mechanism (203) is at least provided with a function of damping the transmitted motion vibration and impact by using the damping action of various springs; and/or

-said spring-damper mechanism (203) is configured to have at least the function of transmitting part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

Said spring-damper damping mechanism (203) being configured to transmit at least part or all of the movement of a component of said machine (M) to said clutch device (CM); and/or

The spring-damper mechanism (203) is configured to have at least a function of selectively restricting the transmitted motion by a friction action of a member thereof;

the material buffer damping mechanism (204) is at least provided with the function of damping or eliminating the vibration and impact generated in the process of separating and jointing the clutch device (CM) by utilizing the viscoelastic damping characteristics of various materials or various shock absorption buffer materials; and/or

The material buffer damping mechanism (204) is configured to at least have the function of damping or eliminating dynamic vibration and impact of one component of the machine (M) by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing and buffering materials; and/or

The material buffer damping mechanism (204) is at least provided with a function of utilizing the viscoelastic damping characteristics of various materials or various vibration absorption buffer materials to limit the transmitted power; and/or

The material buffering damping mechanism (204) is at least provided with a certain buffering function on the transmitted dynamic vibration and impact by utilizing the viscoelastic damping characteristics of various materials or various vibration absorption buffering materials; and/or

The material buffering damping mechanism (204) is at least provided with the function of utilizing the viscoelastic damping characteristics of various materials or various shock absorption buffering materials to have certain damping on the transmitted dynamic vibration and impact; and/or

-said material damping mechanism (204) is configured to have at least the function of transmitting part or all of the power of said clutch device (CM) to other components of said machine (M); and/or

The material buffer damping mechanism (204) is configured to at least have a function of transmitting part or all of power of one component of the machine (M) to the clutch device (CM); and/or

The material buffer damping mechanism (204) is configured to at least have a function of selectively limiting the magnitude of the transmitted power by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material buffer damping mechanism (204) is configured to at least have a function of selectively limiting the magnitude of the transmitted impact by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material buffer damping mechanism (204) is configured to at least have a function of selectively limiting the magnitude of the transmitted vibration by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material buffer damping mechanism (204) is configured to at least have the function of selectively limiting the magnitude of the transmitted torque by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material buffer damping mechanism (204) is configured to at least have a function of selectively limiting the magnitude of the transmitted load by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material cushioning damping mechanism (204) is configured to have at least a function of transferring motion by utilizing viscoelastic damping characteristics of various materials or various shock-absorbing cushioning materials; and/or

The material buffer damping mechanism (204) is configured to have at least a function of restricting the transmitted motion by utilizing the viscoelastic damping characteristics of various materials or various shock-absorbing buffer materials; and/or

The material buffering damping mechanism (204) is at least provided with a function of buffering the transmitted motion vibration and impact by utilizing the viscoelastic damping characteristics of various materials or various vibration absorption buffering materials; and/or

The material buffering damping mechanism (204) is at least provided with the function of utilizing the viscoelastic damping characteristics of various materials or various shock absorption buffering materials to have certain damping on the transmitted motion vibration and impact; and/or

-said material damping mechanism (204) is configured to have at least the function of transmitting part or all of the movement of said clutch device (CM) to other components of said machine (M); and/or

-said material damping mechanism (204) is configured to have at least the function of transmitting part or all of the movement of a component of said machine (M) to said clutch device (CM); and/or

The material cushioning damping mechanism (204) is configured to at least function to selectively restrict transmitted motion by friction of its components;

The magnetic powder buffering and damping mechanism (205) is at least provided with the function of attenuating or eliminating the vibration and impact generated in the separation and connection process of the clutch device (CM) by utilizing the action of a magnetic field on magnetic powder or magnetic fluid; and/or

The magnetic powder buffering and damping mechanism (205) is at least provided with the function of attenuating or eliminating dynamic vibration and impact of one part of the machine (M) by utilizing the action of a magnetic field on magnetic powder or magnetic fluid; and/or

The magnetic powder buffering and damping mechanism (205) is at least provided with a function of limiting the transmitted power by utilizing the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering and damping mechanism (205) is at least provided with a function of buffering transmitted power vibration and impact by utilizing the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering damping mechanism (205) is at least provided with a function of realizing certain damping on the transmitted power vibration and impact by utilizing the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is configured to at least have the function of transmitting part or all of the power of the clutch device (CM) to other parts of the machine (M) by using the action of a magnetic field on magnetic powder or magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is configured to at least have the function of transmitting part or all of the power of one component of the machine (M) to the clutch device (CM) by using the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is configured to have at least a function of selectively limiting the magnitude of the transmitted power by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is configured to have at least a function of selectively limiting the magnitude of the transmitted impact by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering damping mechanism (205) is configured to have at least a function of selectively limiting the magnitude of the transmitted vibration by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is at least provided with a function of selectively limiting the transmitted torque by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffer damping mechanism (205) is configured to have at least a function of selectively limiting the magnitude of the transmitted load by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering damping mechanism (205) is configured to have at least a function of transferring motion by utilizing the action of a magnetic field on magnetic powder or magnetic fluid; and/or

The magnetic powder buffering damping mechanism (205) is at least provided with a function of limiting the motion transmitted by the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering and damping mechanism (205) is at least provided with a function of buffering transmitted motion vibration and impact by utilizing the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic powder buffering damping mechanism (205) is at least provided with a function of damping the transmitted motion vibration and impact by utilizing the action of a magnetic field on the magnetic powder or the magnetic fluid; and/or

The magnetic particle damping mechanism (205) is configured to have at least the function of transmitting part or all of the movement of the clutch device (CM) to other components of the machine (M); and/or

The magnetic particle damping mechanism (205) is configured to have at least the function of transmitting part or all of the movement of a component of the machine (M) to the clutch device (CM); and/or

The magnetic particle damping mechanism (205) is configured to have at least a function of selectively restricting the transmitted motion by a friction action of a member thereof;

The pneumatic buffer damping mechanism (206) is at least provided with the function of damping or eliminating the vibration and impact generated in the process of separating and connecting the clutch device (CM) by utilizing various damping effects and buffering effects of pressurized gas on mechanical structures; and/or

The pneumatic buffer damping mechanism (206) is configured to at least have the function of damping or eliminating dynamic vibration and impact of one component of the machine (M) by utilizing various damping effects and buffering effects of pressurized gas on mechanical structures; and/or

The pneumatic buffer damping mechanism (206) is at least provided with a function of limiting the transmitted power by utilizing various damping actions and buffering actions of pressurized gas on a mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is at least provided with a function of buffering transmitted power vibration and impact by utilizing various damping functions and buffering functions of pressurized gas on a mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is at least provided with a function of damping transmitted dynamic vibration and impact by utilizing various damping functions and buffering functions of pressurized gas on a mechanical structure; and/or

The pneumatic cushion damping mechanism (206) is configured to have at least a function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The pneumatic cushion damping mechanism (206) is configured to transmit at least a part of or the whole power of a component of the machine (M) to the clutch device (CM); and/or

The pneumatic buffer damping mechanism (206) is configured to have at least a function of selectively limiting the magnitude of the transmitted power by utilizing various damping effects and buffering effects of the pressurized gas on the mechanical structure; and/or

The pneumatic cushion damping mechanism (206) is configured to have at least a function of selectively limiting the magnitude of transmitted impact by utilizing various damping and cushioning effects of pressurized gas on the mechanical structure; and/or

The pneumatic cushion damping mechanism (206) is configured to have at least a function of selectively limiting the magnitude of transmitted vibration by utilizing various damping and damping effects of pressurized gas on a mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is configured to at least have a function of selectively limiting the magnitude of the transmitted torque by utilizing various damping actions and buffering actions of the pressurized gas on the mechanical structure; and/or

The pneumatic cushion damping mechanism (206) is configured to have at least a function of selectively limiting the magnitude of a transmitted load by utilizing various damping actions and cushioning actions of pressurized gas on a mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is configured to at least have the function of transmitting motion by utilizing various damping effects and buffering effects of pressurized gas on mechanical structures; and/or

The pneumatic buffer damping mechanism (206) is configured to at least have the function of utilizing the compressed gas to have certain limitation on the transmitted motion for various damping effects and buffering effects of the mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is at least provided with a function of buffering transmitted motion vibration and impact by utilizing various damping functions and buffering functions of pressurized gas on a mechanical structure; and/or

The pneumatic buffer damping mechanism (206) is configured to at least have a function of damping the transmitted motion vibration and impact by utilizing various damping effects and buffering effects of the pressurized gas on the mechanical structure; and/or

-said pneumatic cushion damping mechanism (206) is configured to have at least the function of transmitting part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

-said pneumatic cushion damping mechanism (206) is configured to have at least the function of transmitting part or all of the movement of a component of said machine (M) to said clutch device (CM); and/or

The pneumatic cushion damping mechanism (206) is configured to selectively restrict the transmitted motion by at least the friction of its components;

the electromagnetic buffer damping mechanism (207) is configured to at least have the function of attenuating or eliminating vibration and impact generated in the process of separating and connecting the clutch device (CM) by utilizing the electromagnetic induction effect of a conductor to an electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to at least have a function of attenuating or eliminating dynamic vibration and impact of one component of the machine (M) by utilizing an electromagnetic induction effect of a conductor on an electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is at least provided with a function of limiting the transmitted power by utilizing the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of buffering transmitted power vibration and impact by utilizing the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of damping transmitted dynamic vibration and impact by utilizing the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic damping buffer mechanism (207) is configured to have at least the function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The electromagnetic damping buffer mechanism (207) is configured to have at least a function of transmitting a part of or the whole of the power of a component of the machine (M) to the clutch device (CM); and/or

The electromagnetic buffer damping mechanism (207) is configured to at least have a function of selectively limiting the magnitude of the transmitted power by using the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to at least have a function of selectively limiting the magnitude of the transmitted impact by using the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of selectively limiting the magnitude of the transmitted vibration by using the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to at least selectively limit the transmitted torque by utilizing the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to at least have a function of selectively limiting the magnitude of the transmitted load by using the electromagnetic induction effect of the conductor on the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of transmitting motion by utilizing an electromagnetic induction effect of a conductor on an electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of restricting the transmitted motion by utilizing the electromagnetic induction effect of the conductor to the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is at least provided with a function of buffering the transmitted motion vibration and impact by utilizing the electromagnetic induction effect of the conductor to the electromagnetic field; and/or

The electromagnetic buffer damping mechanism (207) is configured to have at least a function of damping the transmitted motion vibration and impact by utilizing the electromagnetic induction effect of the conductor to the electromagnetic field; and/or

-said electromagnetic damping means (207) are configured to have at least the function of transmitting part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

-said electromagnetic damping means (207) are configured to transmit at least part or all of the motion of a component of said machine (M) to said clutch device (CM); and/or

The electromagnetic damping buffer mechanism (207) is configured to have at least a function of selectively restricting the transmitted motion by the friction action of the members thereof;

the piezoelectric buffer damping mechanism (208) is at least provided with the function of damping or eliminating the vibration and impact generated in the process of separating and connecting the clutch device (CM) by using the piezoelectric effect of materials; and/or

The piezoelectric damping mechanism (208) is configured to at least have the function of damping or eliminating dynamic vibration and impact of one component of the machine (M) by utilizing the piezoelectric effect of materials; and/or

The piezoelectric buffer damping mechanism (208) is at least provided with a function of limiting the transmitted power by utilizing the piezoelectric effect of a material; and/or

The piezoelectric buffer damping mechanism (208) is at least provided with a function of buffering transmitted dynamic vibration and impact by utilizing the piezoelectric effect of a material; and/or

The piezoelectric buffer damping mechanism (208) is at least provided with a function of damping transmitted dynamic vibration and impact by utilizing the piezoelectric effect of a material; and/or

The piezoelectric damping mechanism (208) is configured to have at least a function of transmitting part or all of the power of the clutch device (CM) to other components of the machine (M); and/or

The piezoelectric damping mechanism (208) is configured to transmit at least a part of or the whole power of a component of the machine (M) to the clutch device (CM); and/or

The piezoelectric damping mechanism (208) is configured to at least selectively limit the magnitude of the transmitted power by using the piezoelectric effect of the material; and/or

The piezoelectric damping mechanism (208) is configured to at least selectively limit the magnitude of the transmitted impact by using the piezoelectric effect of the material; and/or

The piezoelectric damping mechanism (208) is configured to at least selectively limit the magnitude of the transmitted vibration by using the piezoelectric effect of the material; and/or

The piezoelectric damping buffer mechanism (208) is at least configured to selectively limit the transmitted torque by using the piezoelectric effect of the material; and/or

The piezoelectric damping mechanism (208) is configured to at least selectively limit the magnitude of the transmitted load by using the piezoelectric effect of the material; and/or

The piezoelectric damping mechanism (208) is configured to at least have a function of transmitting motion by using a piezoelectric effect of a material; and/or

The piezoelectric damping mechanism (208) is configured to have at least a function of restricting the transmitted motion by utilizing the piezoelectric effect of the material; and/or

The piezoelectric buffer damping mechanism (208) is at least provided with a function of buffering the transmitted motion vibration and impact by utilizing the piezoelectric effect of materials; and/or

The piezoelectric buffer damping mechanism (208) is at least provided with a function of damping the transmitted motion vibration and impact by utilizing the piezoelectric effect of the material; and/or

-said piezoelectric damping means (208) are configured to have at least the function of transmitting part or all of the movements of said clutch device (CM) to other components of said machine (M); and/or

The piezoelectric damping mechanism (208) is configured to transmit at least part or all of the motion of a component of the machine (M) to the clutch device (CM); and/or

The piezoelectric damping mechanism (208) is configured to selectively restrict the transmitted motion by at least the friction of the members thereof;

the magnetostrictive buffer damping mechanism (209) is at least provided with the function of attenuating or eliminating vibration and impact generated in the process of separating and connecting the clutch device (CM) by utilizing the stretching effect of a magnetic conductive material under a magnetic field; and/or

The magnetostrictive damping mechanism (209) is at least provided with the function of attenuating or eliminating the dynamic vibration and impact of one part of the machine (M) by utilizing the stretching effect of a magnetic conductive material under a magnetic field; and/or

The magnetostrictive damping mechanism (209) is at least provided with a function of limiting the transmitted power by utilizing the expansion and contraction effect of the magnetic conductive material under a magnetic field; and/or

The magnetostrictive damping mechanism (209) is at least provided with a certain damping function on the transmitted power vibration and impact by utilizing the expansion effect of the magnetic conductive material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with a function of damping the transmitted power vibration and impact by utilizing the expansion effect of the magnetic conductive material under a magnetic field; and/or

Said magnetostrictive damping mechanism (209) being configured to have at least the function of transmitting part or all of the power of said clutch device (CM) to other components of said machine (M); and/or

Said magnetostrictive damping mechanism (209) is configured to have at least the function of transmitting part or all of the power of a component of said machine (M) to said clutch device (CM); and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with the function of selectively limiting the transmitted power by utilizing the stretching effect of the magnetic conductive material under the magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with the function of selectively limiting the transmitted impact magnitude by utilizing the stretching effect of a magnetic conductive material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with the function of selectively limiting the transmitted vibration by utilizing the stretching effect of the magnetic conductive material under the magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with the function of selectively limiting the transmitted torque by utilizing the stretching effect of a magnetic conductive material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with a function of selectively limiting the magnitude of the transmitted load by utilizing the stretching effect of the magnetic conductive material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with the function of transmitting motion by utilizing the stretching effect of a magnetic conductive material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with a function of limiting the transmitted motion by utilizing the expansion and contraction effect of the magnetic conductive material under a magnetic field; and/or

The magnetostrictive damping mechanism (209) is at least provided with a function of buffering the transmitted motion vibration and impact by utilizing the expansion effect of the magnetic material under a magnetic field; and/or

The magnetostrictive buffer damping mechanism (209) is at least provided with a function of damping the transmitted motion vibration and impact by utilizing the expansion effect of the magnetic conductive material under a magnetic field; and/or

-said magnetostrictive damping mechanism (209) is configured to have at least the function of transmitting part or all of the movement of said clutch device (CM) to other components of said machine (M); and/or

-said magnetostrictive damping mechanism (209) is configured to have at least the function of transmitting part or all of the motion of a component of said machine (M) to said clutch device (CM); and/or

The magnetostrictive damping mechanism (209) is configured to at least selectively limit the transmitted motion by the friction action of its components; and/or

Said Damping Means (DM) comprising at least: a friction buffer damping mechanism (201), wherein the friction buffer damping mechanism (201) at least has the functions of utilizing various friction effects to transmit power and having certain damping or damping action on vibration and impact in the power transmission process, and/or the friction buffer damping mechanism (201) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the friction buffer damping mechanism (201) can be selectively controlled by the adjusting device, and/or the friction buffer damping mechanism (201) is directly or indirectly connected with a driving part of the machine (M), the friction buffer damping mechanism (201) rotates along with the driving part of the machine (M), and the friction buffer damping mechanism (201) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the friction buffer damping mechanism (201) is directly or indirectly connected with the clutch device (CM), the friction buffer damping mechanism (201) rotates along with the clutch device (CM), the friction buffer damping mechanism (201) is fixed or unfixed relative to the clutch device (CM) in the axial direction, or the friction buffer damping mechanism (201) is directly or indirectly connected with a driven part of the machine (M), the friction buffer damping mechanism (201) rotates along with the driven part of the machine (M), the friction buffer damping mechanism (201) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction, or the friction buffer damping mechanism (201) is directly or indirectly connected with a rack of the machine (M), and the friction buffer damping mechanism (201) is fixed in the forward rotation direction and the reverse rotation direction relative to the rack of the machine (M), The friction buffer damping mechanism (201) is fixed or unfixed in the axial direction relative to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: a hydraulic buffer damping mechanism (202), wherein the hydraulic buffer damping mechanism (202) at least has the functions of utilizing hydraulic pressure and various liquid damping effects to transmit power and having certain damping or damping effects on vibration and impact in the power transmission process, and/or the hydraulic buffer damping mechanism (202) at least comprises a hydraulic torque converter, and/or a hydraulic coupler, and/or a hydraulic retarder, and/or a viscoelastic damper, and/or a hydraulic small hole damper, and/or the hydraulic buffer damping mechanism (202) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the hydraulic buffer damping mechanism (202) can be selectively controlled by the adjusting device, and/or the hydraulic buffer damping mechanism (202) is directly or indirectly connected with a driving part of the machine (M), The hydraulic buffer damping mechanism (202) rotates along with the driving part of the machine (M), the hydraulic buffer damping mechanism (202) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the hydraulic buffer damping mechanism (202) is directly or indirectly connected with the clutch device (CM), the hydraulic buffer damping mechanism (202) rotates along with the clutch device (CM), the hydraulic buffer damping mechanism (202) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the hydraulic buffer damping mechanism (202) is directly or indirectly connected with the driven part of the machine (M), the hydraulic buffer damping mechanism (202) rotates along with the driven part of the machine (M), and the hydraulic buffer damping mechanism (202) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction thereof, or the hydraulic buffer damping mechanism (202) is directly or indirectly connected with the frame of the machine (M), the hydraulic buffer damping mechanism (202) is fixed relative to the frame of the machine (M) in the forward rotation direction and the reverse rotation direction, and the hydraulic buffer damping mechanism (202) is fixed or unfixed relative to the frame of the machine (M) in the axial direction; and/or

Said Damping Means (DM) comprising at least: a spring buffer damping mechanism (203), wherein the spring buffer damping mechanism (203) at least has the functions of utilizing the elastic force of the spring and the damping effect of the spring to transmit power and having certain damping or damping action on vibration and impact in the power transmission process, and/or the spring buffer damping mechanism (203) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the spring buffer damping mechanism (203) can be selectively controlled by the adjusting device, and/or the spring buffer damping mechanism (203) is directly or indirectly connected with a driving part of the machine (M), the spring buffer damping mechanism (203) rotates along with the driving part of the machine (M), and the spring buffer damping mechanism (203) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the spring buffer damping mechanism (203) is directly or indirectly connected with the clutch device (CM), the spring buffer damping mechanism (203) rotates along with the clutch device (CM), the spring buffer damping mechanism (203) is fixed or not fixed relative to the clutch device (CM) in the axial direction, or the spring buffer damping mechanism (203) is directly or indirectly connected with a driven part of the machine (M), the spring buffer damping mechanism (203) rotates along with the driven part of the machine (M), the spring buffer damping mechanism (203) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction, or the spring buffer damping mechanism (203) is directly or indirectly connected with a rack of the machine (M), and the spring buffer damping mechanism (203) is fixed or not fixed relative to the rack of the machine (M) in the forward rotation direction and the reverse rotation direction, The spring buffer damping mechanism (203) is fixed or not fixed relative to the frame of the machine (M) in the axial direction of the spring buffer damping mechanism; and/or

Said Damping Means (DM) comprising at least: a material buffering and damping mechanism (204), wherein the material buffering and damping mechanism (204) at least has the functions of utilizing the viscoelastic damping effect of the material and the material to transmit power and having certain damping or damping effect on vibration and impact in the power transmission process, and/or the material buffering and damping mechanism (204) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the material buffering and damping mechanism (204) can be selectively controlled by the adjusting device, and/or the material buffering and damping mechanism (204) is directly or indirectly connected with a driving part of the machine (M), the material buffering and damping mechanism (204) rotates along with the driving part of the machine (M), and the material buffering and damping mechanism (204) is fixed or unfixed in the axial direction relative to the driving part of the machine (M), or the material buffer damping mechanism (204) is directly or indirectly connected with the clutch device (CM), the material buffer damping mechanism (204) rotates along with the clutch device (CM), the material buffer damping mechanism (204) is fixed or not fixed relative to the clutch device (CM) in the axial direction, or the material buffer damping mechanism (204) is directly or indirectly connected with a driven part of the machine (M), the material buffer damping mechanism (204) rotates along with the driven part of the machine (M), the material buffer damping mechanism (204) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction, or the material buffer damping mechanism (204) is directly or indirectly connected with a frame of the machine (M), and the material buffer damping mechanism (204) is fixed or not fixed relative to the frame of the machine (M) in the forward rotation direction and the reverse rotation direction, The material buffer damping mechanism (204) is fixed or not fixed relative to the frame of the machine (M) in the axial direction of the material buffer damping mechanism; and/or

Said Damping Means (DM) comprising at least: a magnetic powder buffering and damping mechanism (205), wherein the magnetic powder buffering and damping mechanism (205) at least has the functions of utilizing magnetic powder to transmit power under the action of an electric field and having certain attenuation or damping effect on vibration and impact in the power transmission process, and/or the magnetic powder buffering and damping mechanism (205) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the magnetic powder buffering and damping mechanism (205) can be selectively controlled by the adjusting device, and/or the magnetic powder buffering and damping mechanism (205) is directly or indirectly connected with a driving part of the machine (M), the magnetic powder buffering and damping mechanism (205) rotates along with the driving part of the machine (M), and the magnetic powder buffering and damping mechanism (205) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction of the magnetic powder buffering and damping mechanism (205), or the magnetic powder buffering damping mechanism (205) is directly or indirectly connected with the clutch device (CM), the magnetic powder buffering damping mechanism (205) rotates along with the clutch device (CM), the magnetic powder buffering damping mechanism (205) is fixed or unfixed relative to the clutch device (CM) in the axial direction, or the magnetic powder buffering damping mechanism (205) is directly or indirectly connected with a driven part of the machine (M), the magnetic powder buffering damping mechanism (205) rotates along with the driven part of the machine (M), the magnetic powder buffering damping mechanism (205) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction, or the magnetic powder buffering damping mechanism (205) is directly or indirectly connected with a rack of the machine (M), the magnetic powder buffering damping mechanism (205) is fixed or unfixed relative to the rack of the machine (M) in the forward rotation direction and the reverse rotation direction, The magnetic powder buffer damping mechanism (205) is fixed or unfixed in the axial direction relative to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: a pneumatic cushion damping mechanism (206), wherein the pneumatic cushion damping mechanism (206) at least has the functions of transmitting power by using pneumatic pressure and various gas damping effects and having certain damping or damping effects on vibration and impact in the power transmission process, and/or the pneumatic cushion damping mechanism (206) is directly or indirectly connected with the adjusting device, the torque and the damping magnitude which can be transmitted by the pneumatic cushion damping mechanism (206) can be selectively controlled by the adjusting device, and/or the pneumatic cushion damping mechanism (206) is directly or indirectly connected with a driving part of the machine (M), the pneumatic cushion damping mechanism (206) rotates along with the driving part of the machine (M), and the pneumatic cushion damping mechanism (206) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the air pressure buffer damping mechanism (206) is directly or indirectly connected with the clutch device (CM), the air pressure buffer damping mechanism (206) rotates along with the clutch device (CM), the air pressure buffer damping mechanism (206) is fixed or unfixed relative to the clutch device (CM) in the axial direction, or the air pressure buffer damping mechanism (206) is directly or indirectly connected with a driven part of the machine (M), the air pressure buffer damping mechanism (206) rotates along with the driven part of the machine (M), the air pressure buffer damping mechanism (206) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction, or the air pressure buffer damping mechanism (206) is directly or indirectly connected with a frame of the machine (M), and the air pressure buffer damping mechanism (206) is fixed in the forward rotation direction and the reverse rotation direction relative to the frame of the machine (M), The pneumatic buffer damping mechanism (206) is fixed or non-fixed in the axial direction relative to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: the electromagnetic buffer damping mechanism (207) at least has the functions of transmitting power by using an electromagnetic effect and having certain attenuation or damping effect on vibration and impact in the power transmission process, and/or the electromagnetic buffer damping mechanism (207) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the electromagnetic buffer damping mechanism (207) can be selectively controlled by the adjusting device, and/or the electromagnetic buffer damping mechanism (207) is directly or indirectly connected with a driving part of the machine (M), the electromagnetic buffer damping mechanism (207) rotates along with the driving part of the machine (M), the electromagnetic buffer damping mechanism (207) is fixed or unfixed in the axial direction relative to the driving part of the machine (M), or the electromagnetic buffer damping mechanism (207) is directly or indirectly connected with the clutch device (CM), The electromagnetic damping buffer mechanism (207) rotates with the clutch device (CM), the electromagnetic damping buffer mechanism (207) is fixed or non-fixed relative to the clutch device (CM) in the axial direction, or the electromagnetic buffer damping mechanism (207) is directly or indirectly connected with a driven part of the machine (M), the electromagnetic buffer damping mechanism (207) rotates along with the driven part of the machine (M), and the electromagnetic buffer damping mechanism (207) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction thereof, or the electromagnetic buffering damping mechanism (207) is directly or indirectly connected with the frame of the machine (M), the electromagnetic buffering damping mechanism (207) is fixed relative to the frame of the machine (M) in the forward rotation direction and the reverse rotation direction, and the electromagnetic buffering damping mechanism (207) is fixed or unfixed relative to the frame of the machine (M) in the axial direction; and/or

Said Damping Means (DM) comprising at least: a piezoelectric damping buffer mechanism (208), wherein the piezoelectric damping buffer mechanism (208) at least has the functions of utilizing the material and the piezoelectric effect to transmit power and having certain damping or damping effect on vibration and impact in the power transmission process, and/or the piezoelectric damping buffer mechanism (208) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the piezoelectric damping buffer mechanism (208) can be selectively controlled by the adjusting device, and/or the piezoelectric damping buffer mechanism (208) is directly or indirectly connected with the driving part of the machine (M), the piezoelectric damping buffer mechanism (208) rotates along with the driving part of the machine (M), and the piezoelectric damping buffer mechanism (208) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the piezoelectric buffer damping mechanism (208) is directly or indirectly connected with the clutch device (CM), the piezoelectric buffer damping mechanism (208) rotates along with the clutch device (CM), the piezoelectric buffer damping mechanism (208) is fixed or unfixed relative to the clutch device (CM) in the axial direction, or the piezoelectric buffer damping mechanism (208) is directly or indirectly connected with a driven part of the machine (M), the piezoelectric buffer damping mechanism (208) rotates along with the driven part of the machine (M), the piezoelectric buffer damping mechanism (208) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction, or the piezoelectric buffer damping mechanism (208) is directly or indirectly connected with a frame of the machine (M), and the piezoelectric buffer damping mechanism (208) is fixed in the forward rotation direction and the reverse rotation direction relative to the frame of the machine (M), The piezoelectric damping mechanism (208) is fixed or non-fixed in the axial direction relative to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: a magnetostrictive buffer damping mechanism (209), wherein the magnetostrictive buffer damping mechanism (209) at least has the functions of transmitting power by using the expansion effect of the material and the magnetic conductive material under the action of a magnetic field and having a certain attenuation or damping effect on vibration and impact in the power transmission process, and/or the magnetostrictive buffer damping mechanism (209) is directly or indirectly connected with the adjusting device, the torque and the damping which can be transmitted by the magnetostrictive buffer damping mechanism (209) can be selectively controlled by the adjusting device, and/or the magnetostrictive buffer damping mechanism (209) is directly or indirectly connected with the driving part of the machine (M), the magnetostrictive buffer damping mechanism (209) rotates along with the driving part of the machine (M), and the magnetostrictive buffer damping mechanism (209) is fixed or not fixed relative to the driving part of the machine (M) in the axial direction thereof, or the magnetostrictive buffer damping mechanism (209) is directly or indirectly connected with the clutch device (CM), the magnetostrictive buffer damping mechanism (209) rotates along with the clutch device (CM), the magnetostrictive buffer damping mechanism (209) is fixed or unfixed relative to the clutch device (CM) in the axial direction of the magnetostrictive buffer damping mechanism, or the magnetostrictive buffer damping mechanism (209) is directly or indirectly connected with a driven part of the machine (M), the magnetostrictive buffer damping mechanism (209) rotates along with a driven part of the machine (M), the magnetostrictive buffer damping mechanism (209) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction of the magnetostrictive buffer damping mechanism, or the magnetostrictive buffer damping mechanism (209) is directly or indirectly connected with a rack of the machine (M), the magnetostrictive buffer damping mechanism (209) is fixed or unfixed relative to the rack of the machine (M) in the forward and reverse directions, The magnetostrictive damping mechanism (209) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: hysteresis damping mechanism (210), hysteresis damping mechanism (210) possesses at least and utilizes the hysteresis effect of ferromagnetic material itself and ferromagnetic material to transmit power and have the function of certain decay or damping action to vibration and impact in the power transmission process, and/or hysteresis damping mechanism (210) directly or indirectly with adjusting device is connected, and the torque size and the damping size that hysteresis damping mechanism (210) can transmit can be controlled by adjusting device selectivity, and/or hysteresis damping mechanism (210) directly or indirectly with the driving part of machine (M) is connected, hysteresis damping mechanism (210) rotates along with the driving part of machine (M), hysteresis damping mechanism (210) is fixed or not fixed in its axial relative to the driving part of machine (M), or hysteresis damping mechanism (210) directly or indirectly with Clutch (CM) is connected, Said hysteresis damping mechanism (210) rotating with said Clutch Means (CM), said hysteresis damping mechanism (210) being fixed or non-fixed in its axial direction with respect to said Clutch Means (CM), or the hysteresis damping mechanism (210) is directly or indirectly connected with the driven part of the machine (M), the hysteresis damping mechanism (210) rotates with the driven part of the machine (M), the hysteresis damping mechanism (210) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the hysteresis damping mechanism (210) is directly or indirectly connected with the frame of the machine (M), the hysteresis damping mechanism (210) is fixed relative to the frame of the machine (M) in the forward and reverse directions, and the hysteresis damping mechanism (210) is fixed or unfixed relative to the frame of the machine (M) in the axial direction; and/or

Said Damping Means (DM) comprising at least: the eddy current damping mechanism (211) at least has the functions of transmitting power by using the eddy current effect of liquid and having certain attenuation or damping effect on vibration and impact in the power transmission process, and/or the eddy current damping mechanism (211) is directly or indirectly connected with the adjusting device, the torque and the damping amount which can be transmitted by the eddy current damping mechanism (211) can be selectively controlled by the adjusting device, and/or the eddy current damping mechanism (211) is directly or indirectly connected with the driving part of the machine (M), the eddy current damping mechanism (211) rotates along with the driving part of the machine (M), the eddy current damping mechanism (211) is fixed or not fixed relative to the driving part of the machine (M) in the axial direction of the eddy current damping mechanism, or the eddy current damping mechanism (211) is directly or indirectly connected with the clutch device (CM), Said eddy current damping means (211) rotating with said Clutch Means (CM), said eddy current damping means (211) being fixed or non-fixed in its axial direction with respect to said Clutch Means (CM), or the eddy current damping mechanism (211) is directly or indirectly connected with a driven part of the machine (M), the eddy current damping mechanism (211) rotates with the driven part of the machine (M), the eddy current damping mechanism (211) is fixed or non-fixed relative to the driven part of the machine (M) in the axial direction thereof, or the eddy current damping mechanism (211) is directly or indirectly connected with the frame of the machine (M), the eddy current damping mechanism (211) is fixed relative to the frame of the machine (M) in the forward rotation direction and the reverse rotation direction, and the eddy current damping mechanism (211) is fixed or unfixed relative to the frame of the machine (M) in the axial direction; and/or

Said Damping Means (DM) comprising at least: a second friction plate (212), a second counter plate (213), and/or a second left bearing plate (214), and/or a second right bearing plate (215), and/or a second left snap ring (216), and/or a second right snap ring (217), a second pre-tightening spring (218), and/or a second inner ring (219), and/or a second outer ring (220), wherein the second counter plate (213), and/or the second left bearing plate (214), and/or the second right bearing plate (215), and/or the second left snap ring (216), and/or the second right snap ring (217), the second pre-tightening spring (218), and/or the second inner ring (219), and/or the second outer ring (220) are arranged coaxially with the second friction plate (212), and the second friction plate (212), The second counter plate (213) and/or the second left bearing plate (214) and/or the second right bearing plate (215) and/or the second left snap ring (216), the second preload spring (218) and/or the second inner ring (219) and/or the second outer ring (220) are/is arranged axially on one side of the second right snap ring (217), the second outer ring (220) is arranged radially on one side of the second inner ring (219), the second friction plate (212) is connected directly or indirectly to the second inner ring (219) in the radial direction thereof, the second friction plate (212) rotates together with the second inner ring (219), the second friction plate (212) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second friction plate (212) is connected directly or indirectly to the second outer ring (220) in the radial direction thereof, The second friction disk (212) rotates with the second outer ring (220), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the second outer ring (220), or the second friction disk (212) is directly or indirectly connected in its radial direction to the driving part of the machine (M), the second friction disk (212) rotates with the driving part of the machine (M), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the driving part of the machine (M), or the second friction disk (212) is directly or indirectly connected in its radial direction to the clutch device (CM), the second friction disk (212) rotates with the clutch device (CM), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the clutch device (CM), or the second friction disk (212) is directly or indirectly connected in its radial direction to the driven part of the machine (M), The second friction plate (212) rotates with a driven part of the machine (M), the second friction plate (212) is fixed or non-fixed relative to the driven part of the machine (M) in the axial direction thereof, or the second friction plate (212) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second friction plate (212) is fixed or non-fixed relative to the frame of the machine (M) in both the forward and reverse directions, the second friction plate (212) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second counter plate (213) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second counter plate (213) rotates with the second inner ring (219), the second counter plate (213) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second counter plate (213) is directly or indirectly connected in its radial direction to the second outer ring (220), the second counter plate (213) rotates with the second outer ring (220), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the second outer ring (220), or the second counter plate (213) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second counter plate (213) rotates with the driving member of the machine (M), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the driving member of the machine (M), or the second counter plate (213) is directly or indirectly connected in its radial direction to the clutch device (CM), the second counter plate (213) rotates with the clutch device (CM), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the clutch device (CM), or the second counter-piece (213) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second counter-piece (213) rotates with a driven part of the machine (M), the second counter-piece (213) is fixed or not fixed in its axial direction with respect to a driven part of the machine (M), or the second counter-piece (213) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second counter-piece (213) is fixed or not fixed in both forward and reverse directions with respect to the frame of the machine (M), the second counter-piece (213) is fixed or not fixed in its axial direction with respect to the frame of the machine (M), and/or the second inner ring (219) is directly or indirectly connected in its radial direction to a driving part of the machine (M), the second inner ring (219) rotates with a driving part of the machine (M), The second couple plate (213) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction with the driven member of the machine (M), the second inner ring (219) rotates with the driven member of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the frame of the machine (M), the second inner ring (219) is fixed in both forward and reverse directions with respect to the frame of the machine (M), The second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction with the driving part of the machine (M), the second outer ring (220) rotates with the driving part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second outer ring (220) rotates with the driven part of the machine (M), The second outer ring (220) is fixed or non-fixed in the axial direction thereof relative to a driven member of the machine (M), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second outer ring (220) is fixed in both forward and reverse directions relative to the frame of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second left bearing plate (214) rotates together with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed in the axial direction thereof relative to the second inner ring (219), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), The second left bearing plate (214) rotates with the second outer ring (220), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the second outer ring (220), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the driving member of the machine (M), the second left bearing plate (214) rotates with the driving member of the machine (M), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the driving member of the machine (M), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the clutch device (CM), the second left bearing plate (214) rotates with the clutch device (CM), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the clutch device (CM), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the driven member of the machine (M) -a member connection, the second left bearing plate (214) rotating with a driven member of the machine (M), the second left bearing plate (214) being fixed or non-fixed in its axial direction with respect to a driven member of the machine (M), or the second left bearing plate (214) being directly or indirectly connected in its radial direction with a frame of the machine (M), the second left bearing plate (214) being fixed in both forward and reverse directions with respect to the frame of the machine (M), the second left bearing plate (214) being fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second right bearing plate (215) being directly or indirectly connected in its radial direction with the second inner ring (219), the second right bearing plate (215) rotating with the second inner ring (219), the second right bearing plate (215) being fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second right bearing plate (215) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second right bearing plate (215) rotates together with the second outer ring (220), the second right bearing plate (215) is fixed or unfixed in the axial direction thereof with respect to the second outer ring (220), or the second right bearing plate (215) is directly or indirectly connected with the driving member of the machine (M) in the radial direction thereof, the second right bearing plate (215) rotates together with the driving member of the machine (M), the second right bearing plate (215) is fixed or unfixed in the axial direction thereof with respect to the driving member of the machine (M), or the second right bearing plate (215) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second right bearing plate (215) rotates together with the clutch device (CM), The second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with a driven member of the machine (M), the second right bearing plate (215) rotates with a driven member of the machine (M), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to a driven member of the machine (M), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with a frame of the machine (M), the second right bearing plate (215) is fixed or non-fixed in both forward and reverse directions with respect to the frame of the machine (M), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second left snap ring (216) is directly or indirectly connected in its radial direction with the second inner ring (219), or the second left snap ring (216) is connected in its radial direction with the second inner ring (219), The second left snap ring (216) rotates with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the second outer ring (220) in the radial direction thereof, the second left snap ring (216) rotates with the second outer ring (220), the second left snap ring (216) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the driving member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates with the driving member of the machine (M), the second left snap ring (216) is fixed or non-fixed relative to the driving member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the clutch device (CM) in the radial direction thereof, The second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driven member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with a driven member of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driven member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second left snap ring (216) is fixed relative to the frame of the machine (M) in both forward and reverse directions, and the second left snap ring (216) is fixed or unfixed relative to the frame of the machine (M) in the axial direction thereof, and/or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second inner ring (219), said second right snap ring (217) rotates with said second inner ring (219), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second inner ring (219), or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second outer ring (220), said second right snap ring (217) rotates with said second outer ring (220), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second outer ring (220), or said second right snap ring (217) is directly or indirectly connected in its radial direction to a driving element of said machine (M), said second right snap ring (217) rotates with a driving element of said machine (M), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to a driving element of said machine (M), or the second right snap ring (217) is directly or indirectly connected with the clutch device (CM) in the radial direction, the second right snap ring (217) rotates along with the clutch device (CM), the second right snap ring (217) is fixed or not fixed relative to the clutch device (CM) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a driven part of the machine (M) in the radial direction, the second right snap ring (217) rotates along with a driven part of the machine (M), the second right snap ring (217) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction, the second right snap ring (217) is fixed or not fixed relative to the frame of the machine (M) in the forward and reverse directions, and the second right snap ring (217) is fixed relative to the frame of the machine (M) in the forward and reverse directions, The second right snap ring (217) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second pretension spring (218) rotates with the second inner ring (219), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), the second pretension spring (218) rotates with the second outer ring (220), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the active part of the machine (M), the second pretension spring (218) rotates with the active part of the machine (M), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), The second preloading spring (218) rotates with the clutch device (CM), or the second preloading spring (218) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second preloading spring (218) rotates with the driven part of the machine (M), or the second preloading spring (218) is directly or indirectly connected in its radial direction to a machine frame of the machine (M), the second preloading spring (218) is fixed in both forward and reverse directions relative to the machine frame of the machine (M), and/or the second friction plate (212) comprises at least one friction plate, and/or the second counter plate (213) comprises at least one counter plate, and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second counter plate (213), and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second left snap ring (216) And/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second preload spring (218), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second left pressure plate (214) is directly or indirectly connected in its axial direction to the second friction plate (212), and/or the second left pressure plate (214) is directly or indirectly connected in its axial direction to the second pair of counter plates (213), and/or the second left bearing plate (214) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected with the second left snap ring (216) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second pair of coupling plates (213) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pair of coupling pieces (213) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second left bearing plate (214) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pre-tension spring (218) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pair of coupling pieces (213) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second right bearing plate (215) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pre-tension spring (218) in the axial direction thereof, and/or the second friction plate (212) and the second counter plate (213) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the second left bearing plate (214) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the second right bearing plate (215) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the friction pair transmits torque in the form of static friction when the torque transmitted by the machine (M) to the friction damping mechanism is small, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is small, and/or when the torque transmitted by the machine (M) to the friction damping mechanism is too large, Or when the impact transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the vibration transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the impact transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the vibration transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, the friction pair eliminates the overlarge torque in a sliding friction mode and has a certain damping effect on the vibration and the impact in the power transmission process, and/or the friction pair formed by the second friction plate (212) and the second pair of coupling plates (213) under the elastic force action of the second pre-tightening spring (218) directly or indirectly works under the wet friction or dry friction condition, and/or the friction pair formed by the second left bearing plate (214) and the second friction plate (212) under the elastic force action of the second pre-tightening spring (218) directly or indirectly works under the wet friction or dry friction condition, and/or the friction pair formed by the second right bearing plate (215) and the second friction plate (212) under the elastic force action of the second pre-tightening spring (218) directly or indirectly works under the wet friction or dry friction condition, and/or the second pre-tightening spring (218) at least has the function of compensating the axial thickness reduction of the second friction plate (212) and the second counter plate (213) caused by the abrasion to a certain extent, and/or the second pre-tightening spring (218) at least has the function of compensating the axial thickness reduction of the second left bearing plate (214) and the second friction plate (212) caused by the abrasion to a certain extent, and/or the second pre-tightening spring (218) at least has the function of compensating the axial thickness reduction of the second right bearing plate (215) and the second friction plate (212) caused by abrasion to a certain extent; and/or

Said Damping Means (DM) comprising at least: a second friction plate (212), a second left pressure plate (221), a second right pressure plate (222), and/or a second left snap ring (216), and/or a second right snap ring (217), a second pre-tension spring (218), and/or a second inner ring (219), and/or a second outer ring (220), the second left pressure plate (221), the second right pressure plate (222), and/or the second left snap ring (216), and/or the second right snap ring (217), the second pre-tension spring (218), and/or the second inner ring (219), and/or the second outer ring (220) being arranged coaxially with the second friction plate (212), the second left pressure plate (221), the second right pressure plate (222), and/or the second left snap ring (216), the second pre-tension spring (218), And/or the second inner ring (219), and/or the second outer ring (220) are/is arranged axially on the side of the second right snap ring (217), the second outer ring (220) is arranged radially on the side of the second inner ring (219), the second friction plate (212) is connected radially directly or indirectly to the second inner ring (219), the second friction plate (212) rotates with the second inner ring (219), the second friction plate (212) is fixed or non-fixed axially relative to the second inner ring (219), or the second friction plate (212) is connected radially directly or indirectly to the second outer ring (220), the second friction plate (212) rotates with the second outer ring (220), the second friction plate (212) is fixed or non-fixed axially relative to the second outer ring (220), or the second friction plate (212) is directly or indirectly connected in its radial direction to the driving part of the machine (M), the second friction plate (212) rotates together with the driving part of the machine (M), the second friction plate (212) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second friction plate (212) is directly or indirectly connected in its radial direction to the clutch device (CM), the second friction plate (212) rotates together with the clutch device (CM), the second friction plate (212) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second friction plate (212) is directly or indirectly connected in its radial direction to the driven part of the machine (M), the second friction plate (212) rotates together with the driven part of the machine (M), the second friction plate (212) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second friction disk (212) is directly or indirectly connected in its radial direction to the machine frame of the machine (M), the second friction disk (212) is fixed in both the forward and reverse directions relative to the machine frame of the machine (M), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the machine frame of the machine (M), and/or the second left pressure plate (221) is directly or indirectly connected in its radial direction to the second inner ring (219), the second left pressure plate (221) rotates with the second inner ring (219), the second left pressure plate (221) is fixed or non-fixed in its axial direction relative to the second inner ring (219), or the second left pressure plate (221) is directly or indirectly connected in its radial direction to the second outer ring (220), the second left pressure plate (221) rotates with the second outer ring (220), the second left pressure plate (221), The second left pressure plate (221) is fixed or non-fixed in the axial direction relative to the second outer ring (220), or the second left pressure plate (221) is directly or indirectly connected with the driving part of the machine (M) in the radial direction, the second left pressure plate (221) rotates along with the driving part of the machine (M), the second left pressure plate (221) is fixed or non-fixed in the axial direction relative to the driving part of the machine (M), or the second left pressure plate (221) is directly or indirectly connected with the clutch device (CM) in the radial direction, the second left pressure plate (221) rotates along with the clutch device (CM), the second left pressure plate (221) is fixed or non-fixed in the axial direction relative to the clutch device (CM), or the second left pressure plate (221) is directly or indirectly connected with the driven part of the machine (M) in the radial direction, and the second left pressure plate (221) is fixed or non-fixed in the axial direction relative to the clutch device (CM), or the second left pressure plate (, -the second left pressure plate (221) rotates with a driven part of the machine (M), the second left pressure plate (221) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or-the second left pressure plate (221) is connected in its radial direction directly or indirectly to a frame of the machine (M), -the second left pressure plate (221) is fixed in both forward and reverse directions with respect to the frame of the machine (M), the second left pressure plate (221) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or-the second right pressure plate (222) is connected in its radial direction directly or indirectly to the second inner ring (219), -the second right pressure plate (222) rotates with the second inner ring (219), the second right pressure plate (222) is fixed or non-fixed in its axial direction with respect to the second inner ring (219), or said second right pressure plate (222) is directly or indirectly connected in its radial direction to said second outer ring (220), said second right pressure plate (222) rotates with said second outer ring (220), said second right pressure plate (222) is fixed or non-fixed in its axial direction with respect to said second outer ring (220), or said second right pressure plate (222) is directly or indirectly connected in its radial direction to the driving member of said machine (M), said second right pressure plate (222) rotates with the driving member of said machine (M), said second right pressure plate (222) is fixed or non-fixed in its axial direction with respect to the driving member of said machine (M), or said second right pressure plate (222) is directly or indirectly connected in its radial direction to said clutch device (CM), said second right pressure plate (222) rotates with said clutch device (CM), said second right pressure plate (222) is fixed or non-fixed in its axial direction with respect to said clutch device (CM), or said second right pressure plate (222) is directly or indirectly connected in its radial direction to the driven part of the machine (M), said second right pressure plate (222) rotates with the driven part of the machine (M), said second right pressure plate (222) is fixed or not fixed in its axial direction with respect to the driven part of the machine (M), or said second right pressure plate (222) is directly or indirectly connected in its radial direction to the frame of the machine (M), said second right pressure plate (222) is fixed in both forward and reverse directions with respect to the frame of the machine (M), said second right pressure plate (222) is fixed or not fixed in its axial direction with respect to the frame of the machine (M), and/or said second inner ring (219) is directly or indirectly connected in its radial direction to the driving part of the machine (M), said second inner ring (219) rotates with the driving part of the machine (M), The second couple plate (213) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction with the driven member of the machine (M), the second inner ring (219) rotates with the driven member of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the frame of the machine (M), the second inner ring (219) is fixed in both forward and reverse directions with respect to the frame of the machine (M), The second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction with the driving part of the machine (M), the second outer ring (220) rotates with the driving part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second outer ring (220) rotates with the driven part of the machine (M), The second outer ring (220) is fixed or non-fixed in the axial direction relative to a driven member of the machine (M), or the second outer ring (220) is directly or indirectly connected with a frame of the machine (M) in the radial direction, the second outer ring (220) is fixed in both forward and reverse directions relative to the frame of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction relative to the frame of the machine (M), and/or the second left snap ring (216) is directly or indirectly connected with the second inner ring (219) in the radial direction, the second left snap ring (216) rotates with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed in the axial direction relative to the second inner ring (219), or the second left snap ring (216) is directly or indirectly connected with the second outer ring (220) in the radial direction, The second left snap ring (216) rotates along with the second outer ring (220), the second left snap ring (216) is fixed or unfixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driving member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with the driving member of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driving member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driven member of the machine (M) in the radial direction thereof, The second left snap ring (216) rotates along with a driven part of the machine (M), the second left snap ring (216) is fixed or unfixed in the axial direction thereof relative to the driven part of the machine (M), or the second left snap ring (216) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second left snap ring (216) is fixed or unfixed in both forward and reverse directions relative to the frame of the machine (M), the second left snap ring (216) is fixed or unfixed in the axial direction thereof relative to the frame of the machine (M), and/or the second right snap ring (217) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second right snap ring (217) rotates along with the second inner ring (219), the second right snap ring (217) is fixed or unfixed in the axial direction thereof relative to the second inner ring (219), or the second right snap ring (217) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second right snap ring (217) rotates along with the second outer ring (220), the second right snap ring (217) is fixed or unfixed relative to the second outer ring (220) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with a driving member of the machine (M) in the radial direction thereof, the second right snap ring (217) rotates along with a driving member of the machine (M), the second right snap ring (217) is fixed or unfixed relative to a driving member of the machine (M) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second right snap ring (217) rotates along with the clutch device (CM), the second right snap ring (217) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with a driven part of the machine (M) in the radial direction thereof, the second right snap ring (217) rotates along with the driven part of the machine (M), the second right snap ring (217) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second right snap ring (217) is fixed or not fixed relative to the frame of the machine (M) in forward and reverse directions, the second right snap ring (217) is fixed or not fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second pre-tension spring (218) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, and the second pre-tension spring (218) rotates along with the second inner ring (219), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the second outer ring (220), the second pretensioning spring (218) rotates with the second outer ring (220), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the active part of the machine (M), the second pretensioning spring (218) rotates with the active part of the machine (M), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the clutch device (CM), the second pretensioning spring (218) rotates with the clutch device (CM), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the passive part of the machine (M), the second pretensioning spring (218) rotates with the passive part of the machine (M), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the machine frame of the machine (M), The second pretension spring (218) is fixed relative to a frame of the machine (M) in forward and reverse directions, and/or the second friction plate (212) is directly or indirectly connected with the second left pressure plate (221) in the axial direction thereof, the second friction plate (212) is directly or indirectly connected with the second right pressure plate (222) in the axial direction thereof, and/or the second left pressure plate (221) is directly or indirectly connected with the second pretension spring (218) in the axial direction thereof, and/or the second left pressure plate (221) is directly or indirectly connected with the second left snap ring (216) in the axial direction thereof, and/or the second right pressure plate (222) is directly or indirectly connected with the second pretension spring (218) in the axial direction thereof, and/or the second right pressure plate (222) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second left pressure plate (221) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second right pressure plate (222) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second left pressure plate (221) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the second right snap ring (222) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or when the torque transmitted by the machine (M) to the friction damping mechanism is small, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is small, the friction pair transmits torque in a static friction mode, and/or when the torque transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the impact transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the vibration transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the impact transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the vibration transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, the friction pair eliminates overlarge torque in a sliding friction mode and has certain attenuation on vibration and impact in the power transmission process And/or a friction pair formed by the second left pressure plate (221) and the second friction plate (212) under the action of the elastic force of the second pre-tightening spring (218) directly or indirectly works under the condition of wet friction or dry friction, and/or the second right pressure plate (222) and the second friction plate (212) directly or indirectly form a friction pair under the action of the elastic force of the second pre-tightening spring (218) to work under the condition of wet friction or dry friction, and/or the second pretension spring (218) has at least the function of compensating the axial thickness reduction of the second left pressure plate (221) and the second friction plate (212) due to abrasion to a certain extent, and/or the second pre-tightening spring (218) at least has the function of compensating the axial thickness reduction of the second right pressure plate (222) and the second friction plate (212) caused by abrasion to a certain extent; and/or

Said Damping Means (DM) comprising at least: a second left friction block (223), a second right friction block (224), a second damping disc (225), and/or a second left snap ring (216), and/or a second right snap ring (217), a second pre-tensioning spring (218), and/or a second inner ring (219), and/or a second outer ring (220), the second left friction block (223) being arranged coaxially or non-coaxially with the second damping disc (225), and/or the second right friction block (224) being arranged coaxially or non-coaxially with the second damping disc (225), and/or the second left snap ring (216), and/or the second right snap ring (217), and/or the second pre-tensioning spring (218), and/or the second inner ring (219), and/or the second outer ring (220) being arranged coaxially with the second damping disc (225), the second left friction block (223), The second right friction block (224), the second damping disk (225), and/or the second left snap ring (216), the second pretensioned spring (218), and/or the second inner ring (219), and/or the second outer ring (220) are arranged axially on one side of the second right snap ring (217), the second outer ring (220) is arranged radially on one side of the second inner ring (219), and/or the second damping disk (225) is connected directly or indirectly to the second inner ring (219) in its radial direction, the second damping disk (225) rotates with the second inner ring (219), the second damping disk (225) is fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second damping disk (225) is connected directly or indirectly to the second outer ring (220) in its radial direction, The second damping disk (225) rotates with the second outer ring (220), the second damping disk (225) is fixed or non-fixed in its axial direction relative to the second outer ring (220), or the second damping disk (225) is directly or indirectly connected in its radial direction to the driving part of the machine (M), the second damping disk (225) rotates with the driving part of the machine (M), the second damping disk (225) is fixed or non-fixed in its axial direction relative to the driving part of the machine (M), or the second damping disk (225) is directly or indirectly connected in its radial direction to the clutch device (CM), the second damping disk (225) rotates with the clutch device (CM), the second damping disk (225) is fixed or non-fixed in its axial direction relative to the clutch device (CM), or the second damping disk (225) is directly or indirectly connected in its radial direction to the driven part of the machine (M), The second damping disk (225) rotates with a driven part of the machine (M), the second damping disk (225) is fixed or non-fixed in its axial direction relative to the driven part of the machine (M), or the second damping disk (225) is connected in its radial direction directly or indirectly to a frame of the machine (M), the second damping disk (225) is fixed in both forward and reverse directions relative to the frame of the machine (M), the second damping disk (225) is fixed or non-fixed in its axial direction relative to the frame of the machine (M), and/or the second left friction block (223) is connected in its radial direction directly or indirectly to the second inner ring (219), the second left friction block (223) rotates with the second inner ring (219), the second left friction block (223) is fixed or non-fixed in its axial direction relative to the second inner ring (219), or the second left friction block (223) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second left friction block (223) rotates with the second outer ring (220), the second left friction block (223) is fixed or unfixed relative to the second outer ring (220) in the axial direction thereof, or the second left friction block (223) is directly or indirectly connected with the driving member of the machine (M) in the radial direction thereof, the second left friction block (223) rotates with the driving member of the machine (M), the second left friction block (223) is fixed or unfixed relative to the driving member of the machine (M) in the axial direction thereof, or the second left friction block (223) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second left friction block (223) rotates with the clutch device (CM), or the second left friction block (223) rotates with the clutch device (CM), The second left friction block (223) is fixed or non-fixed in the axial direction thereof relative to the clutch device (CM), or the second left friction block (223) is directly or indirectly connected in the radial direction thereof to a driven member of the machine (M), the second left friction block (223) rotates together with the driven member of the machine (M), the second left friction block (223) is fixed or non-fixed in the axial direction thereof relative to the driven member of the machine (M), or the second left friction block (223) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second left friction block (223) is fixed or non-fixed in the forward and reverse directions relative to the frame of the machine (M), the second left friction block (223) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second right friction block (224) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), The second right friction block (224) rotates with the second inner ring (219), the second right friction block (224) is fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second right friction block (224) is directly or indirectly connected in its radial direction with the second outer ring (220), the second right friction block (224) rotates with the second outer ring (220), the second right friction block (224) is fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second right friction block (224) is directly or indirectly connected in its radial direction with a driving member of the machine (M), the second right friction block (224) rotates with a driving member of the machine (M), the second right friction block (224) is fixed or non-fixed in its axial direction with respect to a driving member of the machine (M), or the second right friction block (224) is directly or indirectly connected in its radial direction with the clutch device (CM) -said second right friction block (224) rotates with said Clutch Means (CM), said second right friction block (224) is fixed or non-fixed in its axial direction with respect to said Clutch Means (CM), or said second right friction block (224) is directly or indirectly connected in its radial direction with a driven part of said machine (M), said second right friction block (224) rotates with a driven part of said machine (M), said second right friction block (224) is fixed or non-fixed in its axial direction with respect to a driven part of said machine (M), or said second right friction block (224) is directly or indirectly connected in its radial direction with a frame of said machine (M), said second right friction block (224) is fixed in both forward and reverse rotation directions with respect to the frame of said machine (M), said second right friction block (224) is fixed or non-fixed in its axial direction with respect to the frame of said machine (M), and/or the second inner ring (219) is directly or indirectly connected in its radial direction to a driving member of the machine (M), the second inner ring (219) rotates with the driving member of the machine (M), the second pair of doublers (213) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction to the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction to a driven member of the machine (M), the second inner ring (219) rotates with a driven member of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second inner ring (219) is directly or indirectly connected to the frame of the machine (M) in the radial direction thereof, the second inner ring (219) is fixed in both the forward and reverse directions with respect to the frame of the machine (M), the second inner ring (219) is fixed or non-fixed in the axial direction thereof with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected to the driving member of the machine (M) in the radial direction thereof, the second outer ring (220) rotates together with the driving member of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the driving member of the machine (M), or the second outer ring (220) is directly or indirectly connected to the clutch device (CM) in the radial direction thereof, the second outer ring (220) rotates together with the clutch device (CM), The second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof to a driven member of the machine (M), the second outer ring (220) rotates together with the driven member of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the driven member of the machine (M), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second outer ring (220) is fixed or non-fixed in both forward and reverse directions with respect to the frame of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the frame of the machine (M), and/or the second left snap ring (216) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), or the second left snap ring (216) is fixed in the radial direction thereof, The second left snap ring (216) rotates with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the second outer ring (220) in the radial direction thereof, the second left snap ring (216) rotates with the second outer ring (220), the second left snap ring (216) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the driving member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates with the driving member of the machine (M), the second left snap ring (216) is fixed or non-fixed relative to the driving member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the clutch device (CM) in the radial direction thereof, The second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driven member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with a driven member of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driven member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second left snap ring (216) is fixed relative to the frame of the machine (M) in both forward and reverse directions, and the second left snap ring (216) is fixed or unfixed relative to the frame of the machine (M) in the axial direction thereof, and/or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second inner ring (219), said second right snap ring (217) rotates with said second inner ring (219), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second inner ring (219), or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second outer ring (220), said second right snap ring (217) rotates with said second outer ring (220), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second outer ring (220), or said second right snap ring (217) is directly or indirectly connected in its radial direction to a driving element of said machine (M), said second right snap ring (217) rotates with a driving element of said machine (M), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to a driving element of said machine (M), or the second right snap ring (217) is directly or indirectly connected with the clutch device (CM) in the radial direction, the second right snap ring (217) rotates along with the clutch device (CM), the second right snap ring (217) is fixed or not fixed relative to the clutch device (CM) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a driven part of the machine (M) in the radial direction, the second right snap ring (217) rotates along with a driven part of the machine (M), the second right snap ring (217) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction, the second right snap ring (217) is fixed or not fixed relative to the frame of the machine (M) in the forward and reverse directions, and the second right snap ring (217) is fixed relative to the frame of the machine (M) in the forward and reverse directions, The second right snap ring (217) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second pretension spring (218) rotates with the second inner ring (219), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), the second pretension spring (218) rotates with the second outer ring (220), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the active part of the machine (M), the second pretension spring (218) rotates with the active part of the machine (M), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), The second pretension spring (218) rotates together with the clutch device (CM), or the second pretension spring (218) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second pretension spring (218) rotates together with the driven part of the machine (M), or the second pretension spring (218) is directly or indirectly connected in its radial direction to a machine frame of the machine (M), the second pretension spring (218) is fixed in both forward and reverse directions relative to the machine frame of the machine (M), and/or the second damping disk (225) is directly or indirectly connected in its axial direction to the second left friction block (223), and/or the second damping disk (225) is directly or indirectly connected in its axial direction to the second right friction block (224), and/or the second left friction block (223) is directly or indirectly connected in its axial direction to the second pretension spring (218), and/or the second left friction block (223) is directly or indirectly connected with the second left snap ring (216) in the axial direction thereof, and/or the second right friction block (224) is directly or indirectly connected with the second pre-tension spring (218) in the axial direction thereof, and/or the second right friction block (224) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second left friction block (223) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pre-tension spring (218) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second right friction block (224) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pre-tension spring (218) in the axial direction thereof, and/or the second left friction block (223) and the second damping disk (225) form a friction pair directly or indirectly under the elastic force of the second pretension spring (218), and/or the second right friction block (224) and the second damping disk (225) form a friction pair directly or indirectly under the elastic force of the second pretension spring (218), and/or the friction pair transmits torque in the form of static friction when the torque transmitted by the machine (M) to the friction damping mechanism is small, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is small, and/or the friction pair transmits torque in the form of static friction when the torque transmitted by the machine (M) to the friction damping mechanism is too large, or when the impact transmitted by the machine (M) to the friction damping mechanism is too large, or when the vibration transmitted by the machine (M) to the friction damping mechanism is too large, Or when the torque transmitted to the friction damping mechanism by the clutch device (CM) is too large, or when the impact transmitted to the friction damping mechanism by the clutch device (CM) is too large, or when the vibration transmitted to the friction damping mechanism by the clutch device (CM) is too large, the friction pair eliminates the excessive torque in the form of sliding friction and has certain damping effect on the vibration and the impact in the power transmission process, and/or the friction pair formed by the second left friction block (223) and the second damping disk (225) under the elastic force action of the second pre-tightening spring (218) directly or indirectly works under the condition of wet friction or dry friction, and/or the friction pair formed by the second right friction block (224) and the second damping disk (225) under the elastic force action of the second pre-tightening spring (218) directly or indirectly works under the condition of wet friction or dry friction, and/or the second pre-tensioning spring (218) has at least the function of compensating the axial thickness reduction of the second left friction block (223) and the second damping disc (225) due to wear to some extent, and/or the second pre-tensioning spring (218) has at least the function of compensating the axial thickness reduction of the second right friction block (224) and the second damping disc (225) due to wear to some extent; and/or

Said Damping Means (DM) comprising at least: a second pilot shoe (226), a second slave shoe (227), a second damping drum (228), a second pretension spring (218), and/or a second inner ring (219), and/or a second outer ring (220), the second pilot shoe (226) being arranged coaxially or non-coaxially with the second damping drum (228), and/or the second slave shoe (227) being arranged coaxially or non-coaxially with the second damping drum (228), and/or the second pretension spring (218), and/or the second inner ring (219), and/or the second outer ring (220) being arranged coaxially with the second damping drum (228), and/or the second pilot shoe (226), the second slave shoe (227), the second damping drum (228), and/or the second inner ring (219), and/or the second outer ring (220) being arranged axially on the side of the second pretension spring (218), the second outer ring (220) is arranged radially on one side of the second inner ring (219), and/or the second inner ring (219) and the second outer ring (220) are at least designed with toothed projections and/or recesses, and the second leading shoe (226) and the second trailing shoe (227) and the second damping drum (228) and the second pretensioned spring (218) are at least designed with a function of engaging with the toothed projections and/or recesses, the second damping drum (228) being connected directly or indirectly in its radial direction to the second inner ring (219), the second damping drum (228) rotating with the second inner ring (219), the second damping drum (228) being fixed or not fixed in its axial direction to the second inner ring (219), or the second damping drum (228) being connected directly or indirectly in its radial direction to the second outer ring (220), The second damping drum (228) rotates with the second outer ring (220), the second damping drum (228) is fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second damping drum (228) is directly or indirectly connected in its radial direction with a driving member of the machine (M), the second damping drum (228) rotates with a driving member of the machine (M), the second damping drum (228) is fixed or non-fixed in its axial direction with respect to a driving member of the machine (M), or the second damping drum (228) is directly or indirectly connected in its radial direction with the clutch device (CM), the second damping drum (228) rotates with the clutch device (CM), the second damping disc (225) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second damping drum (228) is directly or indirectly connected in its radial direction with a driven member of the machine (M), The second damping drum (228) rotating with the driven member of the machine (M), the second damping drum (228) being fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second damping drum (228) being connected in its radial direction directly or indirectly to the frame of the machine (M), the second damping drum (228) being fixed in both forward and reverse directions with respect to the frame of the machine (M), the second damping drum (228) being fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second pilot shoe (226) being connected in its radial direction directly or indirectly to the second inner ring (219), the second pilot shoe (226) rotating with the second inner ring (219), the second pilot shoe (226) being fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second pilot shoe (226) is connected in its radial direction directly or indirectly to the second outer ring (220), the second pilot shoe (226) rotates with the second outer ring (220), the second pilot shoe (226) is fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second pilot shoe (226) is connected in its radial direction directly or indirectly to the driving part of the machine (M), the second pilot shoe (226) rotates with the driving part of the machine (M), the second pilot shoe (226) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second pilot shoe (226) is connected in its radial direction directly or indirectly to the clutch device (CM), the second pilot shoe (226) rotates with the clutch device (CM), the second pilot shoe (226) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second pilot shoe (226) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second pilot shoe (226) rotates with the driven part of the machine (M), the second pilot shoe (226) is fixed or not fixed in its axial direction with respect to the driven part of the machine (M), or the second pilot shoe (226) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second pilot shoe (226) is fixed in both forward and reverse directions with respect to the frame of the machine (M), the second pilot shoe (226) is fixed or not fixed in its axial direction with respect to the frame of the machine (M), and/or the second pilot shoe (227) is directly or indirectly connected in its radial direction to the second inner ring (219), the second pilot shoe (227) rotates with the second inner ring (219), or the second pilot shoe (227) rotates with the second inner ring (219), The second slave shoe (227) is fixed or non-fixed in the axial direction thereof with respect to the second inner ring (219), or the second slave shoe (227) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), the second slave shoe (227) rotates together with the second outer ring (220), the second slave shoe (227) is fixed or non-fixed in the axial direction thereof with respect to the second outer ring (220), or the second slave shoe (227) is directly or indirectly connected in the radial direction thereof to the driving member of the machine (M), the second slave shoe (227) rotates together with the driving member of the machine (M), the second slave shoe (227) is fixed or non-fixed in the axial direction thereof with respect to the driving member of the machine (M), or the second slave shoe (227) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), the second slave shoe (227) rotates together with the clutch device (CM), and the second slave shoe (227) rotates together with the clutch device (CM), The second slave shoe (227) is fixed or non-fixed in the axial direction thereof relative to the clutch device (CM), or the second slave shoe (227) is directly or indirectly connected in the radial direction thereof to a driven member of the machine (M), the second slave shoe (227) rotates together with the driven member of the machine (M), the second slave shoe (227) is fixed or non-fixed in the axial direction thereof relative to the driven member of the machine (M), or the second slave shoe (227) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second slave shoe (227) is fixed or non-fixed in both the forward and reverse directions relative to the frame of the machine (M), the second slave shoe (227) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second inner ring (219) is directly or indirectly connected in the radial direction thereof to an active member of the machine (M), The second inner ring (219) rotates with the driving part of the machine (M), the second pair of coupling plates (213) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second inner ring (219) rotates with the driven part of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the machine frame of the machine (M), The second inner ring (219) is fixed in both forward and reverse rotation directions with respect to the frame of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction with the driving part of the machine (M), the second outer ring (220) rotates with the driving part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in its radial direction with the driven part of the machine (M) -the second outer ring (220) rotates with a driven part of the machine (M), -the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or-the second outer ring (220) is directly or indirectly connected in its radial direction with a frame of the machine (M), -the second outer ring (220) is fixed in both forward and reverse directions with respect to the frame of the machine (M), -the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or-the second pretension spring (218) is directly or indirectly connected in its radial direction with the second inner ring (219), -the second pretension spring (218) rotates with the second inner ring (219), or-the second pretension spring (218) is directly or indirectly connected in its radial direction with the second outer ring (220), -the second pretension spring (218) rotates with the second inner ring (219), or-the second pretension spring (218) is directly or indirectly connected in its radial direction, The second pretension spring (218) rotates with the second outer ring (220), or the second pretension spring (218) is connected directly or indirectly in its radial direction to the active part of the machine (M), the second pretension spring (218) rotates with the active part of the machine (M), or the second pretension spring (218) is connected directly or indirectly in its radial direction to the clutch device (CM), the second pretension spring (218) rotates with the clutch device (CM), or the second pretension spring (218) is connected directly or indirectly in its radial direction to the passive part of the machine (M), the second pretension spring (218) rotates with the passive part of the machine (M), or the second pretension spring (218) is connected directly or indirectly in its radial direction to the machine frame of the machine (M), the second pretension spring (218) is fixed in both the forward and reverse directions relative to the machine frame of the machine (M), and/or the second damping drum (228) is directly or indirectly connected in the radial direction thereof to the second pilot shoe (226), and/or the second damping drum (228) is directly or indirectly connected in the radial direction thereof to the second pilot shoe (227), and/or the second pilot shoe (226) is directly or indirectly connected to the second pretensioning spring (218), the second pilot shoe (227) is directly or indirectly connected to the second pretensioning spring (218), the second pilot shoe (226) and the second pilot shoe (227) form a friction pair with the second damping drum (228) under the spring force of the second pretensioning spring (218), the friction pair transmitting torque in the form of static friction when the torque transmitted by the machine (M) to the friction damping mechanism is small, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is small, and/or when the torque transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the impact transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the vibration transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the impact transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the vibration transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, the friction pair eliminates the overlarge torque in the form of sliding friction and has certain damping effect on the vibration and the impact in the power transmission process, and/or the second leading shoe (226) and the second trailing shoe (227) directly or indirectly form a friction pair with the second damping drum (228) under the action of the elastic force of the second pre-tightening spring (218) in wet friction or dry friction mode -operating under frictional conditions, and/or the second pre-tensioning spring (218) has at least the function of compensating to some extent the reduction in radial thickness due to wear of the second leading shoe (226), the second trailing shoe (227), the second damping drum (228); and/or

Said Clutch Means (CM) comprising at least: a second friction plate (212), a second couple plate (213), and/or a second left bearing plate (214), and/or a second right bearing plate (215), and/or a second left snap ring (216), and/or a second right snap ring (217), a second pre-tightening spring (218), and/or a second inner ring (219), and/or a second outer ring (220), and/or a second right bracket (240), and/or a second rivet (241), a second adjusting gear sleeve (242), and/or a second positioning mechanism (243), a second damping lever mechanism (244), and/or a second right flange (245), and/or a second damping return spring (246), wherein the second couple plate (213), and/or the second left bearing plate (214), and/or the second right bearing plate (215), and/or the second left snap ring (216), And/or the second right snap ring (217), the second pre-tensioning spring (218), and/or the second inner ring (219), and/or the second outer ring (220), and/or the second right bracket (240), the second adjusting gear sleeve (242), and/or the second positioning mechanism (243), the second damping lever mechanism (244), and/or the second right flange (245) are arranged coaxially with the second friction plate (212), the second counter plate (213), and/or the second left bearing plate (214), and/or the second right bearing plate (215), and/or the second left snap ring (216), the second pre-tensioning spring (218), and/or the second inner ring (219), and/or the second outer ring (220), And/or the second right bracket (240), and/or the second rivet (241), the second adjusting gear sleeve (242), and/or the second positioning mechanism (243), the second damping lever mechanism (244), and/or the second right flange (245), and/or the second damping return spring (246) are/is arranged axially on one side of the second right snap ring (217), the second outer ring (220) is arranged radially coaxially on one side of the second inner ring (219), the second friction plate (212) is connected in its radial direction directly or indirectly with the second inner ring (219), the second friction plate (212) rotates together with the second inner ring (219), the second friction plate (212) is fixed or non-fixed in its axial direction relative to the second inner ring (219), or the second friction plate (212) is connected in its radial direction directly or indirectly with the second outer ring (220), The second friction disk (212) rotates with the second outer ring (220), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the second outer ring (220), or the second friction disk (212) is directly or indirectly connected in its radial direction to the driving part of the machine (M), the second friction disk (212) rotates with the driving part of the machine (M), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the driving part of the machine (M), or the second friction disk (212) is directly or indirectly connected in its radial direction to the clutch device (CM), the second friction disk (212) rotates with the clutch device (CM), the second friction disk (212) is fixed or non-fixed in its axial direction relative to the clutch device (CM), or the second friction disk (212) is directly or indirectly connected in its radial direction to the driven part of the machine (M), The second friction plate (212) rotates with a driven part of the machine (M), the second friction plate (212) is fixed or non-fixed relative to the driven part of the machine (M) in the axial direction thereof, or the second friction plate (212) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second friction plate (212) is fixed or non-fixed relative to the frame of the machine (M) in both the forward and reverse directions, the second friction plate (212) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second counter plate (213) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second counter plate (213) rotates with the second inner ring (219), the second counter plate (213) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second counter plate (213) is directly or indirectly connected in its radial direction to the second outer ring (220), the second counter plate (213) rotates with the second outer ring (220), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the second outer ring (220), or the second counter plate (213) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second counter plate (213) rotates with the driving member of the machine (M), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the driving member of the machine (M), or the second counter plate (213) is directly or indirectly connected in its radial direction to the clutch device (CM), the second counter plate (213) rotates with the clutch device (CM), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the clutch device (CM), or the second counter-piece (213) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second counter-piece (213) rotates with a driven part of the machine (M), the second counter-piece (213) is fixed or not fixed in its axial direction with respect to a driven part of the machine (M), or the second counter-piece (213) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second counter-piece (213) is fixed or not fixed in both forward and reverse directions with respect to the frame of the machine (M), the second counter-piece (213) is fixed or not fixed in its axial direction with respect to the frame of the machine (M), and/or the second inner ring (219) is directly or indirectly connected in its radial direction to a driving part of the machine (M), the second inner ring (219) rotates with a driving part of the machine (M), The second couple plate (213) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction with the driven member of the machine (M), the second inner ring (219) rotates with the driven member of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction with the frame of the machine (M), the second inner ring (219) is fixed in both forward and reverse directions with respect to the frame of the machine (M), The second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction with the driving part of the machine (M), the second outer ring (220) rotates with the driving part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second outer ring (220) rotates with the driven part of the machine (M), The second outer ring (220) is fixed or non-fixed in the axial direction thereof relative to a driven member of the machine (M), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof to a frame of the machine (M), the second outer ring (220) is fixed in both forward and reverse directions relative to the frame of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second left bearing plate (214) rotates together with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed in the axial direction thereof relative to the second inner ring (219), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), The second left bearing plate (214) rotates with the second outer ring (220), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the second outer ring (220), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the driving member of the machine (M), the second left bearing plate (214) rotates with the driving member of the machine (M), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the driving member of the machine (M), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the clutch device (CM), the second left bearing plate (214) rotates with the clutch device (CM), the second left bearing plate (214) is fixed or non-fixed in the axial direction thereof with respect to the clutch device (CM), or the second left bearing plate (214) is directly or indirectly connected in the radial direction thereof with the driven member of the machine (M) -a member connection, the second left bearing plate (214) rotating with a driven member of the machine (M), the second left bearing plate (214) being fixed or non-fixed in its axial direction with respect to a driven member of the machine (M), or the second left bearing plate (214) being directly or indirectly connected in its radial direction with a frame of the machine (M), the second left bearing plate (214) being fixed in both forward and reverse directions with respect to the frame of the machine (M), the second left bearing plate (214) being fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second right bearing plate (215) being directly or indirectly connected in its radial direction with the second inner ring (219), the second right bearing plate (215) rotating with the second inner ring (219), the second right bearing plate (215) being fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second right bearing plate (215) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second right bearing plate (215) rotates together with the second outer ring (220), the second right bearing plate (215) is fixed or unfixed in the axial direction thereof with respect to the second outer ring (220), or the second right bearing plate (215) is directly or indirectly connected with the driving member of the machine (M) in the radial direction thereof, the second right bearing plate (215) rotates together with the driving member of the machine (M), the second right bearing plate (215) is fixed or unfixed in the axial direction thereof with respect to the driving member of the machine (M), or the second right bearing plate (215) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second right bearing plate (215) rotates together with the clutch device (CM), The second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with a driven member of the machine (M), the second right bearing plate (215) rotates with a driven member of the machine (M), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to a driven member of the machine (M), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with a frame of the machine (M), the second right bearing plate (215) is fixed or non-fixed in both forward and reverse directions with respect to the frame of the machine (M), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second left snap ring (216) is directly or indirectly connected in its radial direction with the second inner ring (219), or the second left snap ring (216) is connected in its radial direction with the second inner ring (219), The second left snap ring (216) rotates with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the second outer ring (220) in the radial direction thereof, the second left snap ring (216) rotates with the second outer ring (220), the second left snap ring (216) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the driving member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates with the driving member of the machine (M), the second left snap ring (216) is fixed or non-fixed relative to the driving member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected to the clutch device (CM) in the radial direction thereof, The second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driven member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with a driven member of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driven member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second left snap ring (216) is fixed relative to the frame of the machine (M) in both forward and reverse directions, and the second left snap ring (216) is fixed or unfixed relative to the frame of the machine (M) in the axial direction thereof, and/or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second inner ring (219), said second right snap ring (217) rotates with said second inner ring (219), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second inner ring (219), or said second right snap ring (217) is directly or indirectly connected in its radial direction to said second outer ring (220), said second right snap ring (217) rotates with said second outer ring (220), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to said second outer ring (220), or said second right snap ring (217) is directly or indirectly connected in its radial direction to a driving element of said machine (M), said second right snap ring (217) rotates with a driving element of said machine (M), said second right snap ring (217) is fixed or non-fixed in its axial direction with respect to a driving element of said machine (M), or the second right snap ring (217) is directly or indirectly connected with the clutch device (CM) in the radial direction, the second right snap ring (217) rotates along with the clutch device (CM), the second right snap ring (217) is fixed or not fixed relative to the clutch device (CM) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a driven part of the machine (M) in the radial direction, the second right snap ring (217) rotates along with a driven part of the machine (M), the second right snap ring (217) is fixed or not fixed relative to the driven part of the machine (M) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction, the second right snap ring (217) is fixed or not fixed relative to the frame of the machine (M) in the forward and reverse directions, and the second right snap ring (217) is fixed relative to the frame of the machine (M) in the forward and reverse directions, The second right snap ring (217) is fixed or non-fixed in the axial direction thereof relative to the frame of the machine (M), and/or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second pretension spring (218) rotates with the second inner ring (219), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), the second pretension spring (218) rotates with the second outer ring (220), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the active part of the machine (M), the second pretension spring (218) rotates with the active part of the machine (M), or the second pretension spring (218) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), The second pretensioning spring (218) rotates with the clutch device (CM), or the second pretensioning spring (218) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second pretensioning spring (218) rotates with the driven part of the machine (M), or the second pretensioning spring (218) is directly or indirectly connected in its radial direction to a machine frame of the machine (M), the second pretensioning spring (218) is fixed in both forward and reverse directions relative to the machine frame of the machine (M), and/or the second adjusting toothed sleeve (242) is directly or indirectly connected to the adjusting device (RM), and the second adjusting toothed sleeve (242) is selectively axially moved within a certain range relative to the second adjusting toothed sleeve (242) under the drive of the adjusting device (RM), and/or the second adjusting toothed sleeve (242) is directly or indirectly movable in its radial direction to the second outer ring (220) ) -a connection, -the second adjusting gear sleeve (242) rotating together with the second outer ring (220), -the second adjusting gear sleeve (242) being at least configured to be movable in the axial direction relative to the second outer ring (220), or-the second adjusting gear sleeve (242) being directly or indirectly connected in its radial direction with the second inner ring (219), -the second adjusting gear sleeve (242) rotating together with the second inner ring (219), -the second adjusting gear sleeve (242) being at least configured to be movable in the axial direction relative to the second inner ring (219), or-the second adjusting gear sleeve (242) being directly or indirectly connected in its radial direction with a driving part of the machine (M), -the second adjusting gear sleeve (242) rotating together with a driving part of the machine (M), -the second adjusting gear sleeve (242) being movable in its axial direction relative to a driving part of the machine (M), or the second adjusting toothed sleeve (242) is directly or indirectly connected in its radial direction to the clutch device (CM), the second adjusting toothed sleeve (242) rotates with the clutch device (CM), the second adjusting toothed sleeve (242) is movable in its axial direction relative to the clutch device (CM), or the second adjusting toothed sleeve (242) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second adjusting toothed sleeve (242) rotates with a driven part of the machine (M), the second adjusting toothed sleeve (242) is movable in its axial direction relative to a driven part of the machine (M), or the second adjusting toothed sleeve (242) is directly or indirectly connected in its radial direction to a machine frame of the machine (M), the second adjusting toothed sleeve (242) is fixed in both forward and reverse directions relative to the machine frame of the machine (M), The second adjusting toothed sleeve (242) is movable in the axial direction thereof relative to the machine (M), and/or the second adjusting toothed sleeve (242) is connected in the radial direction thereof directly or indirectly to the second right carrier (240), the second adjusting toothed sleeve (242) rotates together with the second right carrier (240), the second adjusting toothed sleeve (242) is at least designed to be movable in the axial direction relative to the second right carrier (240), or the second adjusting toothed sleeve (242) is connected in the radial direction thereof directly or indirectly to the second right flange (245), the second adjusting toothed sleeve (242) rotates together with the second right flange (245), the second adjusting toothed sleeve (242) is at least designed to be movable in the axial direction relative to the second right flange (245), and/or the second outer ring (220) is at least designed to have a limiting effect on the second adjusting toothed sleeve (242) in the axial direction, The second adjusting gear sleeve (242) is at least designed to be axially movable within a certain range relative to the second outer ring (220) against the limiting effect of the second outer ring (220), or the second inner ring (219) is at least designed to have a certain limiting effect on the second adjusting gear sleeve (242) in the axial direction, the second adjusting gear sleeve (242) is at least designed to be axially movable within a certain range relative to the second inner ring (219) against the limiting effect of the second inner ring (219), or the drive of the machine (M) is at least designed to have a certain limiting effect on the second adjusting gear sleeve (242) in the axial direction, the second adjusting gear sleeve (242) is at least designed to be axially movable within a certain range relative to the drive of the machine (M) against the limiting effect of the drive of the machine (M), or the clutch device (CM) is at least designed to axially limit the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) is at least designed to axially move relative to the clutch device (CM) within a certain range against the limiting effect of the clutch device (CM), or the driven part of the machine (M) is at least designed to axially limit the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) is at least designed to axially move relative to the driven part of the machine (M) within a certain range against the limiting effect of the driven part of the machine (M), or the machine frame of the machine (M) is at least designed to axially limit the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) is at least designed to axially move relative to the driven part of the machine (M) within a certain range against the limiting effect of the machine frame -moving the frame of the machine (M), or-the second right support (240) is at least configured to axially limit the second adjustment toothed sleeve (242), -the second adjustment toothed sleeve (242) is at least configured to axially move within a certain range with respect to the second right support (240) against the limiting effect of the second right support (240), or-the second right flange (245) is at least configured to axially limit the second adjustment toothed sleeve (242), -the second adjustment toothed sleeve (242) is at least configured to axially move within a certain range with respect to the second right flange (245) against the limiting effect of the second right flange (245), and/or-a series of axial positioning slots is provided on the second adjustment toothed sleeve (242), -the second adjustment toothed sleeve (242) is at least configured to axially move within a certain range with respect to the second right flange (245) via the axial positioning slots, and-the second adjustment toothed sleeve (220) is at least configured to axially restrict within a certain range with respect to the second adjustment toothed sleeve (242) Acting to position at least one of its axial positions, and/or on the second adjusting toothed sleeve (242) a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least in such a way as to position at least one of its axial positions by means of a range of constraint actions of the axial positioning slots with the second inner ring (219), and/or on the second adjusting toothed sleeve (242) a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least in such a way as to position at least one of its axial positions by means of a range of constraint actions of the axial positioning slots with the driving member of the machine (M), and/or on the second adjusting toothed sleeve (242) a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least in such a way as to position at least one of its axial positions by means of a range of constraint actions of the axial positioning slots with the clutch device (CM), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) is at least configured to position at least one axial position thereof through the constraint action of the axial positioning slots and the driven member of the machine (M) within a certain range, and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) is at least configured to position at least one axial position thereof through the constraint action of the axial positioning slots and the frame of the machine (M) within a certain range, and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) is at least configured to position at least one axial position thereof through the constraint action of the axial positioning slots and the second right bracket (240) within a certain range, and/or the second adjusting gear sleeve (242) is provided with a series of axial positioning grooves, the second adjusting gear sleeve (242) is at least configured to position at least one axial position thereof through the constraining action of the axial positioning grooves and the second right flange (245) within a certain range, and/or the second positioning mechanism (243) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second positioning mechanism (243) rotates along with the second outer ring (220), the second positioning mechanism (243) is at least configured to be movable relative to the second outer ring (220) in the axial direction, or the second positioning mechanism (243) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second positioning mechanism (243) rotates along with the second inner ring (219), the second positioning mechanism (243) is at least configured to be movable relative to the second inner ring (219) in the axial direction, or the second positioning means (243) is directly or indirectly connected in its radial direction to the driving part of the machine (M), the second positioning means (243) rotates with the driving part of the machine (M), the second positioning means (243) is at least configured to be movable in the axial direction relative to the driving part of the machine (M), or the second positioning means (243) is directly or indirectly connected in its radial direction to the clutch device (CM), the second positioning means (243) rotates with the clutch device (CM), the second positioning means (243) is at least configured to be movable in the axial direction relative to the clutch device (CM), or the second positioning means (243) is directly or indirectly connected in its radial direction to the driven part of the machine (M), the second positioning means (243) rotates with the driven part of the machine (M), The second positioning means (243) is at least configured to be axially movable relative to a driven part of the machine (M), or the second positioning means (243) is connected radially thereof directly or indirectly to a frame of the machine (M), the second positioning means (243) is fixedly connected to the frame of the machine (M) in both forward and reverse directions, the second positioning means (243) is at least configured to be axially movable relative to the frame of the machine (M), or the second positioning means (243) is connected radially thereof directly or indirectly to the second right bracket (240), the second positioning means (243) rotates with the second right bracket (240), the second positioning means (243) is at least configured to be axially fixed or non-fixed relative to the second right bracket (240), or the second positioning means (243) is connected radially thereof directly or indirectly to the second right flange (245), The second positioning means (243) rotates with the second right flange (245), the second positioning means (243) is at least axially fixed or non-fixed relative to the second right flange (245), and/or the second adjusting toothed sleeve (242) is directly or indirectly connected in its radial direction to the second positioning means (243), the second adjusting toothed sleeve (242) is at least axially movable relative to the second positioning means (243), and/or the second positioning means (243) is at least axially limited relative to the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) is at least axially limited relative to the second positioning means (243) over a certain range, against the limiting effect of the second positioning means (243), and/or a series of axial positioning grooves are provided on the second adjusting toothed sleeve (242), The second adjusting gear sleeve (242) is at least configured to position at least one axial position of the second positioning mechanism (243) through the constraint action of the axial positioning groove and the second positioning mechanism (243) within a certain range, and/or the second rivet (241) at least comprises one rivet, and/or the second right bracket (240) is directly or indirectly fixedly connected with the second outer ring (220), and/or the second right bracket (240) is fixedly connected with the second outer ring (220) through the second rivet (241), and/or the second right flange (245) is directly or indirectly fixedly connected with the second outer ring (220), and/or the second right flange (245) is fixedly connected with the second outer ring (220) through the second rivet (241), and/or the second right bracket (240) and the second right flange (245) are fixedly connected with the second outer ring (220) through the second rivet (241) -the connection, and/or the second friction plate (212) comprises at least one friction plate, and/or the second counter plate (213) comprises at least one counter plate, the second friction plate (212) is directly or indirectly connected in its axial direction to the second counter plate (213), and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second pretension spring (218), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second pair of counter plates (213) is directly or indirectly connected to the second right snap ring (217) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected to the second friction plate (212) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected to the second pair of counter plates (213) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected to the second preload spring (218) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected to the second left snap ring (216) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected to the second friction plate (212) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected to the second pair of counter plates (213) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second right bearing plate (215) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second counter plate (213) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second left bearing plate (214) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second counter plate (213) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second right bearing plate (215) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second damping lever mechanism (244) comprises at least one lever, and/or the second damping lever mechanism (244) is directly or indirectly connected with the second outer ring (220), the second damping lever mechanism (244) rotates together with the second outer ring (220), the second damping lever mechanism (244) rotates relative to the second outer ring (220) within a certain angle range directly or indirectly under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with the second inner ring (219), the second damping lever mechanism (244) rotates together with the second inner ring (219), the second damping lever mechanism (244) directly or indirectly rotates relative to the second inner ring (219) within a certain angle range under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with the driving part of the machine (M), the second damping lever mechanism (244) rotates together with the driving part of the machine (M), the second damping lever mechanism (244) directly or indirectly rotates relative to the driving part of the machine (M) within a certain angle range under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with the clutch device (CM), The second damping lever mechanism (244) rotates together with the clutch device (CM), the second damping lever mechanism (244) rotates relative to the clutch device (CM) within a certain angle range under the action of the second adjusting gear sleeve (242) directly or indirectly, or the second damping lever mechanism (244) is directly or indirectly connected with a driven part of the machine (M), the second damping lever mechanism (244) rotates together with a driven part of the machine (M), the second damping lever mechanism (244) rotates relative to the driven part of the machine (M) within a certain angle range under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with a frame of the machine (M), and the second damping lever mechanism (244) is fixed relative to the frame of the machine (M) in the rotating direction, The second damping lever mechanism (244) directly or indirectly rotates relative to the frame of the machine (M) within a certain angle range under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with the second right bracket (240), the second damping lever mechanism (244) rotates together with the second right bracket (240), the second damping lever mechanism (244) directly or indirectly rotates relative to the second right bracket (240) within a certain angle range under the action of the second adjusting gear sleeve (242), or the second damping lever mechanism (244) is directly or indirectly connected with the second right flange (245), the second damping lever mechanism (244) rotates together with the second right flange (245), and the second damping lever mechanism (244) directly or indirectly rotates relative to the second right flange within a certain angle range under the action of the second adjusting gear sleeve (242) (245) -the second damping lever mechanism (244) is rotated and/or the second damping lever mechanism (244) in an initial position brings the second friction plate (212) and the second counter plate (213) into a pressed state in an initial position, or the second damping lever mechanism (244) in an initial position brings the second friction plate (212) and the second counter plate (213) into a separated state in an initial position, and/or the second damping return spring (246) comprises at least one spring, and/or the second damping return spring (246) is directly or indirectly connected with the second outer ring (220), the second damping return spring (246) rotates together with the second outer ring (220), and/or the second damping return spring (246) is directly or indirectly connected with the second right carrier (240), the second damping return spring (246) rotates together with the second right carrier (240), and/or the second damped return spring (246) is directly or indirectly connected to the second right support (240), the second damped return spring (246) rotates with the second right support (240), and/or the second damped return spring (246) is directly or indirectly connected to the second damped lever mechanism (244), the second damped lever mechanism (244) returns to the initial position under the spring force of the second damped return spring (246) when the effect of other constraints or loads on the second damped lever mechanism (244) is less than the effect of the second damped return spring (246) on the second damped lever mechanism (244), and/or the second adjustment sleeve (242) is directly or indirectly connected to the adjustment device (RM), and/or the second left snap ring (216) is directly or indirectly connected to the second damped lever mechanism (244), the second left snap ring (244) is directly or indirectly connected to the second damped lever mechanism (244), The second left snap ring (216) directly or indirectly moves axially relative to the second outer ring (220) within a certain range under the action of the second damping lever mechanism (244), or the second right snap ring (217) is directly or indirectly connected with the second damping lever mechanism (244), the second right snap ring (217) directly or indirectly moves axially relative to the second outer ring (220) within a certain range under the action of the second damping lever mechanism (244), or the second pre-tightening spring (218) is directly or indirectly connected with the second damping lever mechanism (244), the second pre-tightening spring (218) rotates together with the second outer ring (220), and the second pre-tightening spring (218) directly or indirectly moves axially relative to the second outer ring (220) within a certain range under the action of the second damping lever mechanism (244), or the second left bearing plate (214) is directly or indirectly connected with the second damping lever mechanism (244), the second left bearing plate (214) rotates with the second outer ring (220), the second left bearing plate (214) directly or indirectly moves axially within a certain range relative to the second outer ring (220) under the action of the second damping lever mechanism (244), and/or the second left bearing plate (214) is directly or indirectly connected with the second preload spring (218), the second left bearing plate (214) rotates with the second outer ring (220), and/or the second left bearing plate (214) directly or indirectly moves axially within a certain range relative to the second outer ring (220) under the action of the second preload spring (218), and/or the second counter plate (213), and/or the second friction plate (212), and/or the second pretensioned spring (218) has at least the function of compensating to some extent the reduction in axial thickness of the second friction plate (212) and the second counter plate (213) as a result of wear, and/or the second friction plate (212) is fixed in the forward or reverse direction relative to the second counter plate (213) within a certain load range when the second friction plate (212) and the second counter plate (213) are directly or indirectly engaged by the second adjustment sleeve (242), and/or the second friction plate (212) is free to rotate in the forward or reverse direction relative to the second counter plate (213) within a certain load range when the second friction plate (212) and the second counter plate (213) are directly or indirectly disengaged by the second adjustment sleeve (242), and/or when the second adjusting gear sleeve (242) is driven by the actuating device (AM) to move to different positions relative to the second friction plate (212) in the axial direction, the pressing force between the second friction plate (212) and the second pair of counter plates (213) is different, the torque which can be transmitted between the second friction plate (212) and the second pair of counter plates (213) through a friction pair is different, and the buffering and damping of the power between the second friction plate (212) and the second pair of counter plates (213) are different; and/or

Said Damping Means (DM) comprising at least: a second friction plate (212), a second counter plate (213), and/or a second left bearing plate (214), and/or a second right bearing plate (215), and/or a second left snap ring (216), and/or a second right snap ring (217), a second pre-tensioning spring (218), and/or a second inner ring (219), and/or a second outer ring (220), a second adjusting gear sleeve (242), and/or a second positioning mechanism (243), and/or a second adjusting bracket (247), wherein the second counter plate (213), and/or the second left bearing plate (214), and/or the second right bearing plate (215), and/or the second left snap ring (216), and/or the second right snap ring (217), the second pre-tensioning spring (218), and/or the second inner ring (219), and/or the second outer ring (220) is arranged coaxially with the second friction plate (212), the second friction disk (212), the second counter plate (213), and/or the second left bearing plate (214), and/or the second right bearing plate (215), and/or the second left snap ring (216), the second preload spring (218), and/or the second inner ring (219), and/or the second outer ring (220) are arranged axially on one side of the second right snap ring (217), and/or the second outer ring (220) is arranged radially on one side of the second inner ring (219), and/or the second inner ring (219) and the second outer ring (220) are at least configured with toothed projections and/or grooves, and a second friction disk (212) and the second counter plate (213) and the second left bearing plate (214) and the second right bearing plate (215) and the second left snap ring (216) and the second right snap ring (217) and the second preload plate (216) The spring (218) is at least configured to engage with the toothed projection and/or the groove, the second friction plate (212) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second friction plate (212) rotates together with the second inner ring (219), the second friction plate (212) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second friction plate (212) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second friction plate (212) rotates together with the second outer ring (220), the second friction plate (212) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second friction plate (212) is directly or indirectly connected with the driving member of the machine (M) in the radial direction thereof, the second friction plate (212) rotates together with the driving member of the machine (M), and, The second friction plate (212) is fixed or non-fixed in the axial direction thereof relative to the driving element of the machine (M), or the second friction plate (212) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), the second friction plate (212) rotates together with the clutch device (CM), the second friction plate (212) is fixed or non-fixed in the axial direction thereof relative to the clutch device (CM), or the second friction plate (212) is directly or indirectly connected in the radial direction thereof to the driven element of the machine (M), the second friction plate (212) rotates together with the driven element of the machine (M), the second friction plate (212) is fixed or non-fixed in the axial direction thereof relative to the driven element of the machine (M), or the second friction plate (212) is directly or indirectly connected in the radial direction thereof to the frame of the machine (M), The second friction plate (212) is fixed relative to the frame of the machine (M) in the forward and reverse directions, the second friction plate (212) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second counter plate (213) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second counter plate (213) rotates along with the second inner ring (219), the second counter plate (213) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second counter plate (213) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second counter plate (213) rotates along with the second outer ring (220), the second counter plate (213) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second counter plate (213) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second counter plate (213) rotates with the driving member of the machine (M), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the driving member of the machine (M), or the second counter plate (213) is directly or indirectly connected in its radial direction to the clutch device (CM), the second counter plate (213) rotates with the clutch device (CM), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the clutch device (CM), or the second counter plate (213) is directly or indirectly connected in its radial direction to the driven member of the machine (M), the second counter plate (213) rotates with the driven member of the machine (M), the second counter plate (213) is fixed or not fixed in its axial direction with respect to the driven member of the machine (M), or the second counter plate (213) is directly or indirectly connected in its radial direction to the frame of the machine (M), the second counter plate (213) is fixed in both the forward and reverse directions with respect to the frame of the machine (M), the second counter plate (213) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second inner ring (219) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second inner ring (219) rotates with the driving member of the machine (M), the second counter plate (213) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction to the clutch device (CM), the second inner ring (219) rotates with the clutch device (CM), The second inner ring (219) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second inner ring (219) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second inner ring (219) rotates with the driven part of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second inner ring (219) is fixed or non-fixed in both forward and reverse directions with respect to the frame of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction to a driving part of the machine (M), and/or the clutch device (CM) is connected to a driving part of the machine (M), and/or the second inner, The second outer ring (220) rotates with the driving part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second outer ring (220) rotates with the driven part of the machine (M), the second outer ring (220) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second outer ring (220) is directly or indirectly connected in its radial direction with the machine frame of the machine (M), The second outer ring (220) is fixed relative to the frame of the machine (M) in forward and reverse rotation directions, the second outer ring (220) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second left bearing plate (214) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second left bearing plate (214) rotates along with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second left bearing plate (214) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second left bearing plate (214) rotates along with the second outer ring (220), the second left bearing plate (214) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second left bearing plate (214) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second left bearing plate (214) rotates with the driving member of the machine (M), the second left bearing plate (214) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second left bearing plate (214) is directly or indirectly connected in its radial direction to the clutch device (CM), the second left bearing plate (214) rotates with the clutch device (CM), the second left bearing plate (214) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second left bearing plate (214) is directly or indirectly connected in its radial direction to the driven member of the machine (M), the second left bearing plate (214) rotates with the driven member of the machine (M), The second left bearing plate (214) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second left bearing plate (214) is directly or indirectly connected in its radial direction to the frame of the machine (M), the second left bearing plate (214) is fixed in both forward and reverse directions with respect to the frame of the machine (M), the second left bearing plate (214) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second right bearing plate (215) is directly or indirectly connected in its radial direction to the second inner ring (219), the second right bearing plate (215) rotates with the second inner ring (219), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second right bearing plate (215) is directly or indirectly connected in its radial direction to the second ring (220), The second right bearing plate (215) rotates with the second outer ring (220), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with the driving member of the machine (M), the second right bearing plate (215) rotates with the driving member of the machine (M), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with the clutch device (CM), the second right bearing plate (215) rotates with the clutch device (CM), the second right bearing plate (215) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second right bearing plate (215) is directly or indirectly connected in its radial direction with the driven member of the machine (M) -a member connection, the second right bearing plate (215) rotating with a driven member of the machine (M), the second right bearing plate (215) being fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second right bearing plate (215) being directly or indirectly connected in its radial direction with a frame of the machine (M), the second right bearing plate (215) being fixed or non-fixed in both forward and reverse directions with respect to the frame of the machine (M), the second right bearing plate (215) being fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second left snap ring (216) being directly or indirectly connected in its radial direction with the second inner ring (219), the second left snap ring (216) rotating with the second inner ring (219), the second left snap ring (216) being fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second left snap ring (216) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second left snap ring (216) rotates along with the second outer ring (220), the second left snap ring (216) is fixed or unfixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driving member of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with a driving member of the machine (M), the second left snap ring (216) is fixed or unfixed relative to a driving member of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driven part of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with the driven part of the machine (M), the second left snap ring (216) is fixed or unfixed in the axial direction thereof relative to the driven part of the machine (M), or the second left snap ring (216) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second left snap ring (216) is fixed or unfixed in the forward and reverse directions relative to the frame of the machine (M), the second left snap ring (216) is fixed or unfixed in the axial direction thereof relative to the frame of the machine (M), and/or the second right snap ring (217) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second right snap ring (217) rotates along with the second inner ring (219), The second right snap ring (217) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second right snap ring (217) rotates along with the second outer ring (220), the second right snap ring (217) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with a driving member of the machine (M) in the radial direction thereof, the second right snap ring (217) rotates along with the driving member of the machine (M), the second right snap ring (217) is fixed or non-fixed relative to the driving member of the machine (M) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, and the second right snap ring (217) is fixed or non-fixed relative to the driving member of the machine (M), The second right snap ring (217) rotates along with the clutch device (CM), the second right snap ring (217) is fixed or non-fixed relative to the clutch device (CM) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a driven part of the machine (M) in the radial direction, the second right snap ring (217) rotates along with a driven part of the machine (M), the second right snap ring (217) is fixed or non-fixed relative to the driven part of the machine (M) in the axial direction, or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction, the second right snap ring (217) is fixed in the forward rotation direction and the reverse rotation direction relative to the frame of the machine (M), and the second right snap ring (217) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction, and/or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the second inner ring (219), the second pretensioning spring (218) rotates with the second inner ring (219), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the second outer ring (220), the second pretensioning spring (218) rotates with the second outer ring (220), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the active part of the machine (M), the second pretensioning spring (218) rotates with the active part of the machine (M), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the clutch device (CM), the second pretensioning spring (218) rotates with the clutch device (CM), or the second pretensioning spring (218) is connected directly or indirectly in its radial direction to the passive part of the machine (M), The second pretensioning spring (218) rotates together with a driven part of the machine (M), or the second pretensioning spring (218) is directly or indirectly connected in the radial direction thereof to a machine frame of the machine (M), the second pretensioning spring (218) is fixed in both the forward and reverse directions relative to the machine frame of the machine (M), and/or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), the second adjusting toothed sleeve (242) rotates together with the second inner ring (219), or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to the second outer ring (220), the second adjusting toothed sleeve (242) rotates together with the second outer ring (220), or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to a driving part of the machine (M), The second adjusting toothed sleeve (242) rotates together with the driving part of the machine (M), or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to the clutch device (CM), the second adjusting toothed sleeve (242) rotates together with the clutch device (CM), or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to the driven part of the machine (M), the second adjusting toothed sleeve (242) rotates together with the driven part of the machine (M), or the second adjusting toothed sleeve (242) is directly or indirectly connected in the radial direction thereof to the machine frame of the machine (M), the second adjusting toothed sleeve (242) is fixed in both the forward and reverse directions relative to the machine frame of the machine (M), and/or the second positioning means (243) is directly or indirectly connected in the radial direction thereof to the second inner ring (219), The second positioning means (243) rotating with the second inner ring (219), or the second positioning means (243) being directly or indirectly connected in its radial direction to the second outer ring (220), the second positioning means (243) rotating with the second outer ring (220), or the second positioning means (243) being directly or indirectly connected in its radial direction to the driving part of the machine (M), the second positioning means (243) rotating with the driving part of the machine (M), or the second positioning means (243) being directly or indirectly connected in its radial direction to the clutch device (CM), the second positioning means (243) rotating with the clutch device (CM), or the second positioning means (243) being directly or indirectly connected in its radial direction to the driven part of the machine (M), the second positioning means (243) rotating with the driven part of the machine (M), or the second positioning means (243) are directly or indirectly connected in their radial direction to the frame of the machine (M), the second positioning means (243) are fixed in relation to the frame of the machine (M) in both the forward and reverse directions, and/or the second adjusting carriage (247) is directly or indirectly connected in their radial direction to the second inner ring (219), the second adjusting carriage (247) rotates with the second inner ring (219), or the second adjusting carriage (247) is directly or indirectly connected in its radial direction to the second outer ring (220), the second adjusting carriage (247) rotates with the second outer ring (220), or the second adjusting carriage (247) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second adjusting carriage (247) rotates with the driving member of the machine (M), or the second adjusting carriage (247) is directly or indirectly connected in its radial direction to the clutch device (CM), the second adjusting carriage (247) rotates with the clutch device (CM), or the second adjusting carriage (247) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second adjusting carriage (247) rotates with a driven part of the machine (M), or the second adjusting carriage (247) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second adjusting carriage (247) is fixed in both forward and reverse directions relative to the frame of the machine (M), and/or the second friction plate (212) comprises at least one friction plate, and/or the second counter plate (213) comprises at least one counter plate, and/or the second friction plate (212) is directly or indirectly connected in its axial direction to the second counter plate (213), and/or the second friction disk (212) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second friction disk (212) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second friction disk (212) is directly or indirectly connected in its axial direction to the second pretension spring (218), and/or the second friction disk (212) is directly or indirectly connected in its axial direction to the second adjustment carrier (247), and/or the second friction disk (212) is directly or indirectly connected in its axial direction to the second adjustment sleeve (242), and/or the second counter disk (213) is directly or indirectly connected in its axial direction to the second pretension spring (218), and/or the second counter disk (213) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second adjustment bracket (247), and/or the second counter plate (213) is directly or indirectly connected in its axial direction to the second adjustment sleeve (242), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second friction plate (212), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second counter plate (213), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second preload spring (218), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second left snap ring (216), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second adjustment bracket (247), and/or the second left bearing plate (214) is directly or indirectly connected in its axial direction to the second adjustment toothed sleeve (242), and/or the second right bearing plate (215) is directly or indirectly connected in its axial direction to the second friction plate (212), and/or the second right bearing plate (215) is directly or indirectly connected in its axial direction to the second pair of coupling plates (213), and/or the second right bearing plate (215) is directly or indirectly connected in its axial direction to the second pretensioner spring (218), and/or the second right bearing plate (215) is directly or indirectly connected in its axial direction to the second right snap ring (217), and/or the second right bearing plate (215) is directly or indirectly connected in its axial direction to the second adjustment bracket (247), and/or the second right bearing plate (215) is directly or indirectly connected with the second adjusting toothed sleeve (242) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pair of coupling plates (213) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second left bearing plate (214) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second adjusting bracket (247) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second adjusting toothed sleeve (242) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second friction plate (212) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pair of coupling plates (213) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second right bearing plate (215) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second pre-tightening spring (218) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second adjusting bracket (247) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second adjusting toothed sleeve (242) in the axial direction thereof, and/or the second adjusting toothed sleeve (242) is directly or indirectly connected with the adjusting device (RM), And the second adjusting gear sleeve (242) is selectively axially movable within a certain range relative to the second adjusting gear sleeve (242) upon actuation of the adjusting device (RM), and/or the second outer ring (220) is at least designed to axially limit the second adjusting gear sleeve (242), the second adjusting gear sleeve (242) is at least designed to axially move relative to the second outer ring (220) within a certain range against the limiting effect of the second outer ring (220), or the second inner ring (219) is at least designed to axially limit the second adjusting gear sleeve (242), the second adjusting gear sleeve (242) is at least designed to axially move relative to the second inner ring (219) within a certain range against the limiting effect of the second inner ring (219), or a drive element of the machine (M) is at least designed to axially limit the second adjusting gear sleeve (242) ) Having a limiting effect, the second adjusting toothed sleeve (242) being at least configured to move axially within a certain range relative to the driving part of the machine (M) against the limiting effect of the driving part of the machine (M), or the clutch device (CM) being at least configured to have a limiting effect on the second adjusting toothed sleeve (242) in the axial direction, the second adjusting toothed sleeve (242) being at least configured to move axially within a certain range relative to the clutch device (CM) against the limiting effect of the clutch device (CM), or a driven part of the machine (M) being at least configured to have a limiting effect on the second adjusting toothed sleeve (242) in the axial direction, the second adjusting toothed sleeve (242) being at least configured to move axially within a certain range relative to a driven part of the machine (M) against the limiting effect of the driven part of the machine (M), or the machine frame (M) is at least configured to axially limit the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) is at least configured to axially move within a certain range relative to the machine frame (M) against the limiting of the machine frame (M), or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) is at least configured to position at least one axial position thereof by the limiting of the axial positioning slots and the second outer ring (220), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) is at least configured to position at least one axial position thereof by the limiting of the axial positioning slots and the second inner ring (219), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least to position at least one axial position thereof by means of a range of constraint actions of the axial positioning slots with the driving member of the machine (M), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least to position at least one axial position thereof by means of a range of constraint actions of the axial positioning slots with the clutch device (CM), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least to position at least one axial position thereof by means of a range of constraint actions of the axial positioning slots with the driven member of the machine (M), and/or the second adjusting toothed sleeve (242) is provided with a series of axial positioning slots, the second adjusting toothed sleeve (242) being configured at least to position at least one of its axial positions by means of a constraining action of the axial positioning slots within a certain range with respect to the frame of the machine (M), and/or the second adjusting toothed sleeve (242) being connected in its radial direction directly or indirectly to the second positioning means (243), the second adjusting toothed sleeve (242) being configured at least to be movable in its axial direction with respect to the second positioning means (243), and/or the second positioning means (243) being configured at least to have a limiting action in the axial direction with respect to the second adjusting toothed sleeve (242), the second adjusting toothed sleeve (242) being configured at least to move within a certain range in the axial direction with respect to the second positioning means (243) against the limiting action of the second positioning means (243), and/or the second adjusting gear sleeve (242) is provided with a series of axial positioning grooves, the second adjusting gear sleeve (242) is at least configured to position at least one axial position thereof through the constraint action of the axial positioning grooves and the second positioning mechanism (243) within a certain range, and/or the second friction plate (212) and the second counter plate (213) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the second left pressure bearing plate (214) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or the second right pressure bearing plate (215) and the second friction plate (212) form a friction pair directly or indirectly under the elastic force of the second pre-tightening spring (218), and/or when the torque transmitted by the machine (M) to the friction damping mechanism is small, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is small, the friction pair transmits torque in a static friction mode, and/or when the torque transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the impact transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the vibration transmitted by the machine (M) to the friction damping mechanism is overlarge, or when the torque transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the impact transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, or when the vibration transmitted by the clutch device (CM) to the friction damping mechanism is overlarge, the friction pair eliminates overlarge torque in a sliding friction mode and has certain attenuation on vibration and impact in the power transmission process And/or the friction pair formed by the second friction plate (212) and the second counter plate (213) directly or indirectly under the elastic force of the second pre-tightening spring (218) works under wet friction or dry friction, and/or the friction pair formed by the second left pressure bearing plate (214) and the second friction plate (212) directly or indirectly under the elastic force of the second pre-tightening spring (218) works under wet friction or dry friction, and/or the friction pair formed by the second right pressure bearing plate (215) and the second friction plate (212) directly or indirectly under the elastic force of the second pre-tightening spring (218) works under wet friction or dry friction, and/or the second pre-tightening spring (218) at least has the function of compensating the axial thickness reduction of the second friction plate (212) and the second counter plate (213) caused by wear to a certain extent, and/or the second pretension spring (218) has at least the function of compensating to some extent the axial thickness reduction of the second left pressure plate (214) and the second friction plate (212) due to wear, and/or the second pretension spring (218) has at least the function of compensating to some extent the axial thickness reduction of the second right pressure plate (215) and the second friction plate (212) due to wear, and/or the adjustment device (RM) has in turn the second adjustment toothed sleeve (242), and/or the second adjustment bracket (247), and/or the second left snap ring (216), and/or the second left pressure plate (214), and/or the second friction plate (212), and/or the second counter plate (213), and/or the second right pressure plate (215), And/or the second right snap ring (217) is connected with the second pre-tightening spring (218), the elastic deformation of the second pre-tightening spring (218) indirectly driven by the adjusting device (RM) can also be changed, and further the torque bearing capacity and the damping magnitude of the friction pair indirectly controlled by the adjusting device (RM) can also be changed; and/or

Said Damping Means (DM) comprising at least: a second pump wheel (229), a second worm wheel (230), a second guide wheel (231), and/or a second left half coupling (232), and/or a second right half coupling (233), the second worm wheel (230), the second guide wheel (231), and/or the second left half coupling (232), and/or the second right half coupling (233) being arranged coaxially with the second pump wheel (229), the second guide wheel (231) being arranged axially between the second pump wheel (229) and the second worm wheel (230), the second pump wheel (229), the second worm wheel (230), the second guide wheel (231), and/or the second left half coupling (232) being arranged axially on one side of the second right half coupling (233), and/or the damping Device (DM) being provided at least with the second pump wheel (229), The damping action between the second worm wheel (230), the second guide wheel (231) and the fluid has a certain damping and damping effect on the power transmission of the Clutch Mechanism (CM), and/or the damping Device (DM) at least has a certain damping and damping effect on the power transmission of the machine (M) by the damping action between the second pump wheel (229), the second worm wheel (230), the second guide wheel (231) and the fluid, and/or the second pump wheel (229) is directly or indirectly connected with the second left half coupling (232) in the radial direction thereof, the second pump wheel (229) rotates with the second left half coupling (232), the second pump wheel (229) is fixed or unfixed in the axial direction thereof with respect to the second left half coupling (232), or the second pump wheel (229) is directly or indirectly connected with the second right half coupling (233) in the radial direction thereof, The second pump wheel (229) rotates together with the second right half coupling (233), the second pump wheel (229) is fixed or non-fixed in its axial direction with respect to the second right half coupling (233), or the second pump wheel (229) is directly or indirectly connected in its radial direction with a driving part of the machine (M), the second pump wheel (229) rotates together with a driving part of the machine (M), the second pump wheel (229) is fixed or non-fixed in its axial direction with respect to a driving part of the machine (M), or the second pump wheel (229) is directly or indirectly connected in its radial direction with the clutch device (CM), the second pump wheel (229) rotates together with the clutch device (CM), the second pump wheel (229) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), and/or the second worm wheel (230) is directly or indirectly connected in its radial direction with the second left half coupling (232), The second worm wheel (230) rotates along with the second left coupling half (232), the second worm wheel (230) is fixed or non-fixed relative to the second left coupling half (232) in the axial direction thereof, or the second worm wheel (230) is directly or indirectly connected with the second right coupling half (233) in the radial direction thereof, the second worm wheel (230) rotates along with the second right coupling half (233), the second worm wheel (230) is fixed or non-fixed relative to the second right coupling half (233) in the axial direction thereof, or the second worm wheel (230) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second worm wheel (230) rotates along with the clutch device (CM), the second worm wheel (230) is fixed or non-fixed relative to the clutch device (CM) in the axial direction thereof, or the second worm wheel (230) is directly or indirectly connected with a driven member of the machine (M) in the radial direction thereof, The second worm wheel (230) rotates along with a driven part of the machine (M), the second worm wheel (230) is fixed or unfixed in the axial direction relative to the driven part of the machine (M), and/or the second guide wheel (231) is directly or indirectly fixedly connected with a frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: a second pump wheel (229), a second worm wheel (230), and/or a second left half coupling (232), and/or a second right half coupling (233), wherein the second worm wheel (230), and/or the second left half coupling (232), and/or the second right half coupling (233) are coaxially arranged with the second pump wheel (229), the second worm wheel (230), and/or the second left half coupling (232) are axially arranged on one side of the second right half coupling (233), and/or the damping Device (DM) at least has a certain damping and damping effect on the power transmission of the Clutch Mechanism (CM) by using the damping effect between the second pump wheel (229), the second worm wheel (230), and the liquid, and/or the damping Device (DM) at least has a certain damping and damping effect by using the second pump wheel (229), the second worm wheel (230), and the liquid, The damping effect between the second worm wheel (230) and the liquid has a certain vibration damping and damping effect on the power transmission of the machine (M), and/or the second pump wheel (229) is directly or indirectly connected with the second left half coupling (232) in the radial direction thereof, the second pump wheel (229) rotates along with the second left half coupling (232), the second pump wheel (229) is fixed or non-fixed relative to the second left half coupling (232) in the axial direction thereof, or the second pump wheel (229) is directly or indirectly connected with the second right half coupling (233) in the radial direction thereof, the second pump wheel (229) rotates along with the second right half coupling (233), the second pump wheel (229) is fixed or non-fixed relative to the second right half coupling (233) in the axial direction thereof, or the second pump wheel (229) is directly or indirectly connected with the driving part of the machine (M) in the radial direction thereof, The second pump wheel (229) rotates with the driving part of the machine (M), the second pump wheel (229) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second pump wheel (229) is directly or indirectly connected in its radial direction with the clutch device (CM), the second pump wheel (229) rotates with the clutch device (CM), the second pump wheel (229) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), and/or the second worm wheel (230) is directly or indirectly connected in its radial direction with the second left half coupling (232), the second worm wheel (230) rotates with the second left half coupling (232), the second worm wheel (230) is fixed or non-fixed in its axial direction with respect to the second left half coupling (232), or the second worm wheel (230) is directly or indirectly connected in its radial direction with the second right half coupling (233), The second worm wheel (230) rotates together with the second right half coupling (233), the second worm wheel (230) is fixed or non-fixed in its axial direction with respect to the second right half coupling (233), or the second worm wheel (230) is directly or indirectly connected in its radial direction with the clutch device (CM), the second worm wheel (230) rotates together with the clutch device (CM), the second worm wheel (230) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second worm wheel (230) is directly or indirectly connected in its radial direction with a driven part of the machine (M), the second worm wheel (230) rotates together with a driven part of the machine (M), the second worm wheel (230) is fixed or non-fixed in its axial direction with respect to a driven part of the machine (M), and/or the second worm wheel (230) is connected in its radial direction directly or indirectly with a machine frame of the machine (M), The second worm wheel (230) is fixed relative to the frame of the machine (M) in the forward and reverse directions, and the second worm wheel (230) is fixed or unfixed relative to the frame of the machine (M) in the axial direction; and/or

Said Damping Means (DM) comprising at least: a second pump wheel (229), a second worm wheel (230), and/or a second left half coupling (232), and/or a second right half coupling (233), wherein the second worm wheel (230), and/or the second left half coupling (232), and/or the second right half coupling (233) are coaxially arranged with the second pump wheel (229), the second worm wheel (230), and/or the second left half coupling (232) are axially arranged on one side of the second right half coupling (233), and/or the damping Device (DM) at least has a certain damping and damping effect on the power transmission of the Clutch Mechanism (CM) by using the damping effect between the second pump wheel (229), the second worm wheel (230), and the liquid, and/or the damping Device (DM) at least has a certain damping and damping effect by using the second pump wheel (229), the second worm wheel (230), and the liquid, The damping effect between the second worm wheel (230) and the liquid has a certain vibration damping and damping effect on the power transmission of the machine (M), and/or the second pump wheel (229) is directly or indirectly connected with the second left half coupling (232) in the radial direction thereof, the second pump wheel (229) rotates along with the second left half coupling (232), the second pump wheel (229) is fixed or non-fixed relative to the second left half coupling (232) in the axial direction thereof, or the second pump wheel (229) is directly or indirectly connected with the second right half coupling (233) in the radial direction thereof, the second pump wheel (229) rotates along with the second right half coupling (233), the second pump wheel (229) is fixed or non-fixed relative to the second right half coupling (233) in the axial direction thereof, or the second pump wheel (229) is directly or indirectly connected with the driving part of the machine (M) in the radial direction thereof, -the second impeller (229) rotates with the driving part of the machine (M), the second impeller (229) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or-the second impeller (229) is directly or indirectly connected in its radial direction with the clutch device (CM), -the second impeller (229) rotates with the clutch device (CM), -the second impeller (229) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), and/or-the second worm wheel (230) is directly or indirectly connected in its radial direction with the frame of the machine (M), -the second worm wheel (230) is fixed in both the forward and reverse directions with respect to the frame of the machine (M), -the second worm wheel (230) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M); and/or

Said Damping Means (DM) comprising at least: a second blade (234), a second blade pair (235), and/or a second positioning bearing (236), and/or a second left snap ring (216), and/or a second right snap ring (217), and/or a second separation spring (237), a second inner ring (219), a second outer ring (220), and/or a second oil seal (238), the second blade (234), the second blade pair (235), and/or the second positioning bearing (236), and/or the second left snap ring (216), and/or the second right snap ring (217), and/or the second separation spring (237), and/or the second inner ring (219), and/or the second outer ring (220), and/or the second oil seal (238) being arranged coaxially with the second inner ring (219), and/or the second inner ring (219) and/or the second outer ring (220) being configured with at least toothed projections and toothed projections And/or grooves, and the second blade (234) and the second blade couple (235) are at least configured to function in engagement with the toothed projections and/or grooves, the second blade (234) being connected in its radial direction directly or indirectly to the second inner ring (219), the second blade (234) rotating with the second inner ring (219), the second blade (234) being fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second blade (234) being connected in its radial direction directly or indirectly to the second outer ring (220), the second blade (234) rotating with the second outer ring (220), the second blade (234) being fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second blade (234) being connected in its radial direction directly or indirectly to an active part of the machine (M), The second blade (234) rotates with the driving part of the machine (M), the second blade (234) is fixed or non-fixed in its axial direction with respect to the driving part of the machine (M), or the second blade (234) is directly or indirectly connected in its radial direction with the clutch device (CM), the second blade (234) rotates with the clutch device (CM), the second blade (234) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second blade (234) is directly or indirectly connected in its radial direction with the driven part of the machine (M), the second blade (234) rotates with the driven part of the machine (M), the second blade (234) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second blade (234) is directly or indirectly connected in its radial direction with the frame of the machine (M), The second blades (234) are fixed in both forward and reverse rotation directions with respect to the frame of the machine (M), the second blades (234) are fixed or non-fixed in their axial direction with respect to the frame of the machine (M), and/or the second counter-piece (213) is connected in its radial direction directly or indirectly to the second inner ring (219), the second counter-piece (213) rotates with the second inner ring (219), the second counter-piece (213) is fixed or non-fixed in its axial direction with respect to the second inner ring (219), or the second counter-piece (213) is connected in its radial direction directly or indirectly to the second outer ring (220), the second counter-piece (213) rotates with the second outer ring (220), the second counter-piece (213) is fixed or non-fixed in its axial direction with respect to the second outer ring (220), or the second counter-piece (213) is connected in its radial direction directly or indirectly to the main drive element of the machine (M) -said second counter-piece (213) rotates with the driving member of said machine (M), said second counter-piece (213) is fixed or non-fixed in its axial direction with respect to the driving member of said machine (M), or said second counter-piece (213) is directly or indirectly connected in its radial direction with said Clutch Means (CM), said second counter-piece (213) rotates with said Clutch Means (CM), said second counter-piece (213) is fixed or non-fixed in its axial direction with respect to said Clutch Means (CM), or said second counter-piece (213) is directly or indirectly connected in its radial direction with the driven member of said machine (M), said second counter-piece (213) rotates with the driven member of said machine (M), said second counter-piece (213) is fixed or non-fixed in its axial direction with respect to the driven member of said machine (M), or said second counter-piece (213) is directly or indirectly connected in its radial direction with the machine frame of said machine (M), The second pair of coupling plates (213) is fixed relative to the frame of the machine (M) in both forward and reverse directions, the second pair of coupling plates (213) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second inner ring (219) is directly or indirectly connected to the driving member of the machine (M) in the radial direction thereof, the second inner ring (219) rotates together with the driving member of the machine (M), the second pair of coupling plates (213) is fixed or non-fixed relative to the driving member of the machine (M) in the axial direction thereof, or the second inner ring (219) is directly or indirectly connected to the clutch device (CM) in the radial direction thereof, the second inner ring (219) rotates together with the clutch device (CM), the second inner ring (219) is fixed or non-fixed relative to the clutch device (CM) in the axial direction thereof, or the second inner ring (219) is directly or indirectly connected in its radial direction to a driven part of the machine (M), the second inner ring (219) rotates with the driven part of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the driven part of the machine (M), or the second inner ring (219) is directly or indirectly connected in its radial direction to a frame of the machine (M), the second inner ring (219) is fixed in both forward and reverse directions with respect to the frame of the machine (M), the second inner ring (219) is fixed or non-fixed in its axial direction with respect to the frame of the machine (M), and/or the second outer ring (220) is directly or indirectly connected in its radial direction to a driving part of the machine (M), the second outer ring (220) rotates with the driving part of the machine (M), The second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the driving member of the machine (M), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof with the clutch device (CM), the second outer ring (220) rotates with the clutch device (CM), the second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the clutch device (CM), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof with the driven member of the machine (M), the second outer ring (220) rotates with the driven member of the machine (M), the second outer ring (220) is fixed or non-fixed in the axial direction thereof with respect to the driven member of the machine (M), or the second outer ring (220) is directly or indirectly connected in the radial direction thereof with the frame of the machine (M), the second outer ring (220) is fixed or non-fixed in the forward and reverse directions with respect to the frame of the machine (M), or the second outer ring (220) is fixed in the forward and reverse directions, The second outer ring (220) is fixed or non-fixed relative to a frame of the machine (M) in the axial direction thereof, and/or the second left snap ring (216) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second left snap ring (216) rotates along with the second inner ring (219), the second left snap ring (216) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second left snap ring (216) rotates along with the second outer ring (220), the second left snap ring (216) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with a driving member of the machine (M) in the radial direction thereof, and/or a second left snap ring (216) is fixed or non-fixed relative to the driving member of the machine (M, The second left snap ring (216) rotates along with the driving part of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driving part of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the clutch device (CM) in the radial direction thereof, the second left snap ring (216) rotates along with the clutch device (CM), the second left snap ring (216) is fixed or unfixed relative to the clutch device (CM) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the driven part of the machine (M) in the radial direction thereof, the second left snap ring (216) rotates along with the driven part of the machine (M), the second left snap ring (216) is fixed or unfixed relative to the driven part of the machine (M) in the axial direction thereof, or the second left snap ring (216) is directly or indirectly connected with the frame of the machine (M) in the radial direction thereof, The second left snap ring (216) is fixed relative to a frame of the machine (M) in forward and reverse directions, the second left snap ring (216) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second right snap ring (217) is directly or indirectly connected with the second inner ring (219) in the radial direction thereof, the second right snap ring (217) rotates along with the second inner ring (219), the second right snap ring (217) is fixed or non-fixed relative to the second inner ring (219) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected with the second outer ring (220) in the radial direction thereof, the second right snap ring (217) rotates along with the second outer ring (220), and the second right snap ring (217) is fixed or non-fixed relative to the second outer ring (220) in the axial direction thereof, or the second right snap ring (217) is directly or indirectly connected in its radial direction to the driving member of the machine (M), the second right snap ring (217) rotates with the driving member of the machine (M), the second right snap ring (217) is fixed or non-fixed in its axial direction with respect to the driving member of the machine (M), or the second right snap ring (217) is directly or indirectly connected in its radial direction to the clutch device (CM), the second right snap ring (217) rotates with the clutch device (CM), the second right snap ring (217) is fixed or non-fixed in its axial direction with respect to the clutch device (CM), or the second right snap ring (217) is directly or indirectly connected in its radial direction to the driven member of the machine (M), the second right snap ring (217) rotates with the driven member of the machine (M), the second right snap ring (217) is fixed or non-fixed in its axial direction with respect to the driven member of the machine (M), or the second right snap ring (217) is directly or indirectly connected with a frame of the machine (M) in the radial direction thereof, the second right snap ring (217) is fixed relative to the frame of the machine (M) in both forward and reverse directions, the second right snap ring (217) is fixed or unfixed relative to the frame of the machine (M) in the axial direction thereof, and/or the second vane (234) comprises at least one vane, and/or the second vane dual (235) comprises at least one dual, and/or the second positioning bearing (236) has at least a certain axial and/or radial supporting and positioning function for the connected member, and/or the second oil seal (238) has at least a certain sealing function for the connected member, and/or the second separation spring (237) has at least the function of evening the spacing between the blades of the second blade (234), and/or the second separation spring (237) has at least the function of evening the spacing between the pairs of blades of the second blade pair (235), and/or the second inner ring (219) is connected to the second outer ring (220) via the second positioning bearing (236), and/or the second inner ring (219) is connected to the clutch device (CM) via the second positioning bearing (236), and/or the second inner ring (219) is connected to the drive of the machine (M) via the second positioning bearing (236), and/or the second inner ring (219) is connected to the driven of the machine (M) via the second positioning bearing (236), and/or the second inner ring (219) is connected to the machine frame via the second positioning bearing (236) The bearing (236) is connected, and/or the second outer ring (220) is connected with the clutch device (CM) through the second positioning bearing (236), and/or the second outer ring (220) is connected with the driving part of the machine (M) through the second positioning bearing (236), and/or the second outer ring (220) is connected with the driven part of the machine (M) through the second positioning bearing (236), and/or the second outer ring (220) is connected with the frame of the machine (M) through the second positioning bearing (236), and/or the second inner ring (219) is connected with the second outer ring (220) through the second oil seal (238), and the space between the second inner ring (219) and the second outer ring (220) is filled with hydraulic oil, and/or the second inner ring (219) is connected with the clutch device (CM) through the second oil seal (238), And hydraulic oil is filled between the second inner ring (219) and the clutch device (CM), and/or the second inner ring (219) and the driving part of the machine (M) are connected through the second oil seal (238), hydraulic oil is filled between the second inner ring (219) and the driving part of the machine (M), and/or the second inner ring (219) and the driven part of the machine (M) are connected through the second oil seal (238), hydraulic oil is filled between the second inner ring (219) and the driven part of the machine (M), and/or the second inner ring (219) and the frame of the machine (M) are connected through the second oil seal (238), hydraulic oil is filled between the second inner ring (219) and the frame of the machine (M), and/or the second outer ring (220) and the clutch device (CM) are connected through the second oil seal (238), And the second outer ring (220) and the clutch device (CM) are filled with hydraulic oil, and/or the second outer ring (220) and the driving part of the machine (M) are connected through the second oil seal (238), and hydraulic oil is filled between the second outer ring (220) and the driving part of the machine (M), and/or the second outer ring (220) and the driven part of the machine (M) are connected through the second oil seal (238), and hydraulic oil is filled between the second outer ring (220) and the driven part of the machine (M), and/or the second outer ring (220) and the frame of the machine (M) are connected through the second oil seal (238), and hydraulic oil is filled between the second outer ring (220) and the frame of the machine (M), and/or the second blade (234) is directly or indirectly connected with the second left snap ring (216) in the axial direction thereof, and/or the second blade (234) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second blade (234) is directly or indirectly connected with the second separation spring (237) in the axial direction thereof, and/or the second blade pair (235) is directly or indirectly connected with the second left snap ring (216) in the axial direction thereof, and/or the second blade pair (235) is directly or indirectly connected with the second right snap ring (217) in the axial direction thereof, and/or the second blade pair (235) is directly or indirectly connected with the second separation spring (237) in the axial direction thereof, and/or a gap is present between the second blade pair (235) in the axial direction thereof, and the gap is filled with hydraulic oil, and the second blade (234) transmits power to the second blade pair through a viscoelastic effect on the gap liquid to the second blade pair (217) in the axial direction thereof, and/or the second blade pair (234) transmits power to the second blade pair through a viscoelastic effect on the gap liquid -said doublet (235), and/or said second bladeset (235) transmitting power to said second blades (234) by a viscoelastic effect on the gap fluid, and/or said gap being of different size, the amount of torque transmittable by said Damper (DM) and the amount of damping of vibrations and shocks being different, said gap being either preset or selectively adjustable by said adjusting means (RM), and/or when the torque transmitted by said machine (M) to said Damper (DM) is excessive, or when the shock transmitted by said machine (M) to said Damper (DM) is excessive, or when the vibration transmitted by said machine (M) to said Damper (DM) is excessive, or when the torque transmitted by said Clutch Means (CM) to said Damper (DM) is excessive, Or when the impact transmitted to the buffer damping Device (DM) by the clutch device (CM) is too large or the vibration transmitted to the buffer damping Device (DM) by the clutch device (CM) is too large, the liquid in the gap eliminates the excessive torque in a hydraulic damping mode and has certain damping effect on the vibration and the impact in the power transmission process; and/or

Said Damping Means (DM) comprising at least: a second damping spring (239) and/or a second left half coupling (232) and/or a second right half coupling (233), the second left half coupling (232) being arranged coaxially with the second right half coupling (233), the second left half coupling (232) being directly or indirectly connected in its radial direction with the driving part of the machine (M), the second left half coupling (232) rotating with the driving part of the machine (M), the second left half coupling (232) being fixed or non-fixed in its axial direction relative to the driving part of the machine (M), or the second left half coupling (232) being directly or indirectly connected in its radial direction with the clutch device (CM), the second left half coupling (232) rotating with the clutch device (CM), the second left half coupling (232) being fixed or non-fixed in its axial direction relative to the clutch device (CM), or the second left half coupling (232) is directly or indirectly connected with the driven part of the machine (M) in the radial direction thereof, the second left half coupling (232) rotates along with the driven part of the machine (M), the second left half coupling (232) is fixed or unfixed in the axial direction thereof relative to the driven part of the machine (M), or the second left half coupling (232) is directly or indirectly connected with the frame of the machine (M) in the radial direction thereof, the second left half coupling (232) is fixed or unfixed in the forward and reverse directions relative to the frame of the machine (M), the second left half coupling (232) is fixed or unfixed in the axial direction thereof relative to the frame of the machine (M), and/or the second right half coupling (233) is directly or indirectly connected with the driving part of the machine (M) in the radial direction thereof, the second right half coupling (233) rotates along with the driving part of the machine (M), The second right half coupling (233) is axially fixed or non-fixed relative to the driving part of the machine (M), or the second right half coupling (233) is radially directly or indirectly connected with the clutch device (CM), the second right half coupling (233) rotates along with the clutch device (CM), the second right half coupling (233) is axially fixed or non-fixed relative to the clutch device (CM), or the second right half coupling (233) is radially directly or indirectly connected with the driven part of the machine (M), the second right half coupling (233) rotates along with the driven part of the machine (M), the second right half coupling (233) is axially fixed or non-fixed relative to the driven part of the machine (M), or the second right half coupling (233) is radially or indirectly connected with the machine frame of the machine (M), The second right half coupling (233) is fixed relative to the frame of the machine (M) in the forward rotation and reverse rotation directions, the second right half coupling (233) is fixed or non-fixed relative to the frame of the machine (M) in the axial direction, the second damping spring (239) comprises at least one spring, the second damping spring (239) at least has vibration damping and damping effects on the power transmission of the buffer damping Device (DM) by using the spring, and/or the second damping spring (239) at least has vibration damping and damping effects on the power transmission of the Clutch Mechanism (CM) by using the spring, and/or the second left half coupling (232) and the second right half coupling (233) are connected by using the second damping spring (239), and/or the second left half coupling (232) is connected with the clutch device (CM) through the second damping spring (239), and/or the second left half coupling (232) is connected with the driving part of the machine (M) through the second damping spring (239), and/or the second left half coupling (232) is connected with the driven part of the machine (M) through the second damping spring (239), and/or the second left half coupling (232) is connected with the frame of the machine (M) through the second damping spring (239), and/or the second right half coupling (233) is connected with the clutch device (CM) through the second damping spring (239), and/or the second right half coupling (233) is connected with the driving part of the machine (M) through the second damping spring (239), and/or the second right half coupling (233) is connected with the driven part of the machine (M) through the second damping spring (239), and/or the second right half coupling (233) is connected with the frame of the machine (M) through the second damping spring (239), and/or the clutch device (CM) is connected with the driving part of the machine (M) through the second damping spring (239), and/or the clutch device (CM) is connected with the driven part of the machine (M) through the second damping spring (239), and/or the clutch device (CM) is connected with the frame of the machine (M) through the second damping spring (239), and/or the driving part of the machine (M) is connected with the driven part of the machine (M) through the second damping spring (239), and/or the driving part of the machine (M) is connected with the frame of the machine (M) through the second damping spring (239), and/or the driven part of the machine (M) is connected with the frame of the machine (M) through the second damping spring (239), and/or the second damping spring (239) has a certain damping effect on vibration and impact in the power transmission process in a spring damping mode when the impact transmitted by the machine (M) to the buffer damping Device (DM) is overlarge, or when the vibration transmitted by the clutch device (CM) to the buffer damping Device (DM) is overlarge.

10. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

the Actuation Means (AM) comprise at least: -motor actuation means (318), and/or hydraulic actuation means (319), and/or manual actuation means (320), and/or pneumatic actuation means (321), and/or electromagnetic actuation means (322), and/or piezoelectric actuation means (323), and/or magnetostrictive actuation means (324), and/or memory metal actuation means (325), and/or thermal expansion and contraction actuation means (326);

the motor actuating device (318) is configured to at least function to directly or indirectly utilize the engagement or disengagement of a motor-driven clutch device (CM); and/or

The hydraulic actuating device (319) is configured at least with the function of driving the engagement or disengagement of the clutch device (CM) directly or indirectly with a hydraulic cylinder; and/or

The manual actuation device (320) is configured to at least function directly or indirectly with engagement or disengagement of a human-powered clutch device (CM); and/or

Said pneumatic actuating means (321) being configured at least to function directly or indirectly by means of engagement or disengagement of various pneumatic cylinder-driven Clutch Means (CM); and/or

The electromagnetic actuating device (322) is configured to at least have the function of directly or indirectly driving the engagement or disengagement of the clutch device (CM) by various electromagnets; and/or

The piezoelectric actuator (323) is configured to have at least a function of driving engagement or disengagement of the clutch device (CM) directly or indirectly by using a piezoelectric effect of various piezoelectric materials; and/or

The magnetostrictive actuation device (324) is at least configured to drive the clutch device (CM) to be engaged or disengaged by directly or indirectly utilizing the expansion and contraction of various magnetic conductive materials under the action of a magnetic field; and/or

The memory metal actuating device (325) is configured to have at least a function of directly or indirectly utilizing a shape memory effect of various memory metals to effect engagement or disengagement of the clutch device (CM); and/or

The thermal expansion and contraction actuating device (326) is configured to at least realize the function of directly or indirectly utilizing the thermal expansion and contraction effect of various materials to realize the connection or disconnection of the clutch device (CM);

the Actuation Means (AM) comprise at least: a third actuating motor (301) and/or a third actuating transmission mechanism (302), wherein the third actuating motor (301) is a power source of the actuating device (AM), a shell of the third actuating motor (301) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third actuating motor (301), the third actuating transmission mechanism (302) at least has a variable speed transmission function for the power of the third actuating motor (301), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power, the rotating speed, the load, the rotating angle, the displacement, the movement or the direction of the third actuating motor (301), and/or the third actuating transmission mechanism (302) is directly or indirectly connected with the clutch device (CM), The third actuating motor (301) is connected with the clutch device (CM) through the third actuating transmission mechanism (302), and/or the third actuating motor (301) selectively actuates the clutch device (CM) through the third actuating transmission mechanism (302) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating hydraulic cylinder (303) and/or a third actuating transmission mechanism (302), wherein the third actuating hydraulic cylinder (303) is a power source of the actuating device (AM), a cylinder body of the third actuating hydraulic cylinder (303) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third actuating hydraulic cylinder (303), the third actuating transmission mechanism (302) at least has a variable speed transmission function for the power of the third actuating hydraulic cylinder (303), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power, load, displacement, movement or direction of the third actuating hydraulic cylinder (303), and/or the third actuating transmission mechanism (302) is directly or indirectly connected with the clutch device (CM), The third actuating hydraulic cylinder (303) is connected with the clutch device (CM) through the third actuating transmission mechanism (302), and/or the third actuating hydraulic cylinder (303) selectively actuates the clutch device (CM) through the third actuating transmission mechanism (302) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the third actuating hydraulic cylinder (303); and/or

The Actuation Means (AM) comprise at least: a third actuating handle (304) and/or a third actuating transmission (302), the third actuating handle (304) being connected to the machine frame (M) and the third actuating handle (304) being rotatable relative to the machine frame (M) within an angular range, the third actuating handle (304) being directly or indirectly connected to the clutch device (CM), manual power being used to selectively effect various engagement or disengagement actions of the clutch device (CM) directly or indirectly via the actuating handle (84), and/or the third actuating handle (304) being directly or indirectly connected to the third actuating transmission (302), the third actuating transmission (302) being directly or indirectly connected to the clutch device (CM), manual power being used to selectively effect various engagement or disengagement actions of the clutch device (CM) via the third actuating handle (304) and the third actuating transmission (302) in turn, and/or the third actuating transmission mechanism (302) has at least the function of transmitting the power of the third actuating handle (304) in a variable speed, and/or the third actuating transmission mechanism (302) has at least the function of transmitting the power, load, displacement or direction of the third actuating handle (304); and/or

The Actuation Means (AM) comprise at least: a third actuating pneumatic cylinder (305) and/or a third actuating transmission mechanism (302), wherein the third actuating pneumatic cylinder (305) is a power source of the actuating device (AM), a cylinder body of the third actuating pneumatic cylinder (305) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engagement or disengagement actions under the direct or indirect actuation of the third actuating pneumatic cylinder (305), the third actuating transmission mechanism (302) at least has a variable-speed transmission function for the power of the third actuating pneumatic cylinder (305), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power, load, displacement, movement or direction of the third actuating pneumatic cylinder (305), and/or the third actuating transmission mechanism (302) is directly or indirectly connected with the clutch device (CM), Said third actuating pneumatic cylinder (305) being connected to said Clutch Means (CM) through said third actuating transmission (302), and/or said third actuating pneumatic cylinder (305) selectively actuating said Clutch Means (CM) through said third actuating transmission (302) so as to cause said Clutch Means (CM) to selectively effect various engagement or disengagement actions under the control of said third actuating pneumatic cylinder (305); and/or

The Actuation Means (AM) comprise at least: a third actuating electromagnetic valve (306) and/or a third actuating transmission mechanism (302), wherein the third actuating electromagnetic valve (306) is a power source of the actuating device (AM), a shell of the third actuating electromagnetic valve (306) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third actuating electromagnetic valve (306), the third actuating transmission mechanism (302) at least has a variable speed transmission function for the power of the third actuating electromagnetic valve (306), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power, load, displacement, movement or direction of the third actuating electromagnetic valve (306), and/or the third actuating transmission mechanism (302) is directly or indirectly connected with the clutch device (CM), The third actuating solenoid valve (306) is connected with the clutch device (CM) through the third actuating transmission mechanism (302), and/or the third actuating solenoid valve (306) selectively actuates the clutch device (CM) through the third actuating transmission mechanism (302) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the third actuating solenoid valve (306); and/or

The Actuation Means (AM) comprise at least: a third piezoelectric actuator (307) and/or a third actuating transmission mechanism (302), wherein the third piezoelectric actuator (307) is a power source of the actuating device (AM), the third piezoelectric actuator (307) at least has a function of outputting power by utilizing a piezoelectric effect or a piezoelectric inverse effect, a shell of the third piezoelectric actuator (307) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third piezoelectric actuator (307), the third actuating transmission mechanism (302) at least has a variable speed transmission function for the power of the third piezoelectric actuator (307), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power, load, displacement, movement or direction of the third piezoelectric actuator (307), and/or said third actuation transmission (302) is directly or indirectly connected to said Clutch Means (CM), said third piezoelectric actuator (307) is connected to said Clutch Means (CM) through said third actuation transmission (302), and/or said third piezoelectric actuator (307) selectively actuates said Clutch Means (CM) through said third actuation transmission (302) so as to cause said Clutch Means (CM) to selectively perform various engagement or disengagement actions under the control of said third piezoelectric actuator (307); and/or

The Actuation Means (AM) comprise at least: a third magnetostrictive actuator (308) and/or a third actuation transmission mechanism (302), wherein the third magnetostrictive actuator (308) is a power source of the actuation device (AM), the third magnetostrictive actuator (308) at least has a function of outputting power by utilizing a magnetostrictive effect or a magnetostrictive reverse effect, a shell of the third magnetostrictive actuator (308) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third magnetostrictive actuator (308), the third actuation transmission mechanism (302) at least has a variable speed transmission function for the power of the third magnetostrictive actuator (308), and/or the third actuation transmission mechanism (302) at least has a function of transmitting the power of the third magnetostrictive actuator (308), -a function of load, displacement, movement or direction, and/or-said third actuator transmission (302) is directly or indirectly connected to said Clutch Means (CM), -said third magnetostrictive actuator (308) is connected to said Clutch Means (CM) through said third actuator transmission (302), and/or-said third magnetostrictive actuator (308) selectively actuates said Clutch Means (CM) through said third actuator transmission (302) so as to enable said Clutch Means (CM) to selectively perform various engagement or disengagement actions under the control of said third magnetostrictive actuator (308); and/or

The Actuation Means (AM) comprise at least: a third memory metal actuator (309) and/or a third actuation transmission mechanism (302), wherein the third memory metal actuator (309) is a power source of the actuation device (AM), the third memory metal actuator (309) at least has a function of outputting power by utilizing a shape memory effect of memory metal, a housing of the third memory metal actuator (309) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under direct or indirect actuation of the third memory metal actuator (309), the third actuation transmission mechanism (302) at least has a variable speed transmission function for the power of the third memory metal actuator (309), and/or the third actuation transmission mechanism (302) at least has a function of transmitting the power of the third memory metal actuator (309), -a function of load, displacement, movement or direction, and/or said third actuation transmission (302) is directly or indirectly connected to said Clutch Means (CM), said third memory metal actuator (309) is connected to said Clutch Means (CM) through said third actuation transmission (302), and/or said third memory metal actuator (309) selectively actuates said Clutch Means (CM) through said third actuation transmission (302) so as to cause said Clutch Means (CM) to selectively perform various engagement or disengagement actions under the control of said third memory metal actuator (309); and/or

The Actuation Means (AM) comprise at least: a third expansion and contraction actuator (310) and/or a third actuating transmission mechanism (302), wherein the third expansion and contraction actuator (310) is a power source of the actuating device (AM), the third expansion and contraction actuator (310) at least has a function of outputting power by utilizing the expansion and contraction effect, a shell of the third expansion and contraction actuator (310) is fixedly connected with a rack of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the third expansion and contraction actuator (310), the third actuating transmission mechanism (302) at least has a variable-speed transmission function on the power of the third expansion and contraction actuator (310), and/or the third actuating transmission mechanism (302) at least has a function of transmitting the power of the third expansion and contraction actuator (310), -a function of load, displacement, movement or direction, and/or the third actuator transmission (302) is directly or indirectly connected to the Clutch Means (CM), the third actuator (310) is connected to the Clutch Means (CM) via the third actuator transmission (302), and/or the third actuator (310) selectively actuates the Clutch Means (CM) via the third actuator transmission (302) so as to selectively effect various engagement or disengagement actions of the Clutch Means (CM) under the control of the third actuator (310); and/or

The Actuation Means (AM) comprise at least: a third actuating motor (301), a third actuating screw (311), a third actuating nut (312), and/or a third anti-rotation guide rod (313), a third shift fork (316), wherein the third actuating motor (301) is a power source of the actuating device (AM), a housing of the third actuating motor (301) is fixedly connected with a frame of the machine (M), a rotor of the third actuating motor (301) is directly or indirectly connected with the third actuating screw (311), and the third actuating screw (311) rotates together with the rotor of the third actuating motor (301), the third actuating screw (311) is directly or indirectly connected with the third actuating nut (312) through a thread pair, the third actuating nut (312) moves in the axial direction of the machine (M) relative to the frame of the machine, and/or the third actuating nut (312) is directly or indirectly fixedly connected with the third anti-rotation guide rod (313), and/or a third shift fork (316), The third anti-rotation guide rod (313) moves in the axial direction relative to the frame of the machine (M), the third actuating nut (312) is directly or indirectly fixedly connected with the third shifting fork (316), the third shifting fork (316) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the third shifting fork (316), the third actuating motor (301) is sequentially connected with the third actuating screw rod (311), the third actuating nut (312) and the third shifting fork (316) and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating motor (301), a third actuating screw (311), a third actuating nut (312), a third shift fork (316), and/or a third shift rod (317), the third actuating motor (301) being a power source of the actuating device (AM), a housing of the third actuating motor (301) being fixedly connected to a frame of the machine (M), a rotor of the third actuating motor (301) being directly or indirectly connected to the third actuating screw (311), and the third actuating screw (311) rotating together with the rotor of the third actuating motor (301), the third actuating screw (311) being directly or indirectly connected to the third actuating nut (312) by a thread pair, the third actuating nut (312) moving in an axial direction relative to the frame of the machine (M), and/or the third actuating nut (312) being directly or indirectly fixedly connected to the third shift fork (316), and/or the third shift fork (316) is directly or indirectly fixedly connected with the third shift guide bar (317) and the third shift guide bar (317) moves in the axial direction relative to the frame of the machine (M), the third shift fork (316) is directly or indirectly connected with the clutch device (CM) and the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the third shift fork (316), the third actuating motor (301) is connected with the clutch device (CM) sequentially through the third actuating screw (311), the third actuating nut (312) and the third shift fork (316), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating motor (301), a third actuating screw (311), a third actuating nut (312), a third shift fork (316), wherein the third actuating motor (301) is a power source of the actuating device (AM), a housing of the third actuating motor (301) is fixedly connected with a frame of the machine (M), a rotor of the third actuating motor (301) is directly or indirectly connected with the third actuating nut (312), and the third actuating nut (312) rotates together with the rotor of the third actuating motor (301), the third actuating screw (311) and the third actuating nut (312) are directly or indirectly connected through a thread pair, the third actuating screw (311) moves in an axial direction relative to the frame of the machine (M), and/or the third actuating screw (311) is directly or indirectly fixedly connected with the third shift fork (316), the third gear shifting fork (316) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the third gear shifting fork (316), the third actuating motor (301) is sequentially connected with the clutch device (CM) through the third actuating screw rod (311), the third actuating nut (312) and the third gear shifting fork (316), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating motor (301), a third actuating screw (311), a third actuating nut (312), a third shift fork (316), a third shift rod (317), wherein the third actuating motor (301) is a power source of the actuating device (AM), a housing of the third actuating motor (301) and a frame of the machine (M) are fixed to each other, a rotor of the third actuating motor (301) is directly or indirectly connected with the third actuating nut (312), and the third actuating nut (312) rotates together with the rotor of the third actuating motor (301), the third actuating screw (311) and the third actuating nut (312) are directly or indirectly connected through a thread pair, the third actuating screw (311) moves in an axial direction relative to the frame of the machine (M), and/or the third actuating screw (311) is directly or indirectly fixed to the third shift fork (316), and/or the third shift fork (316) is directly or indirectly fixedly connected with the third shift guide bar (317) and the third shift guide bar (317) moves in the axial direction relative to the frame of the machine (M), the third shift fork (316) is directly or indirectly connected with the clutch device (CM) and the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the third shift fork (316), the third actuating motor (301) is connected with the clutch device (CM) sequentially through the third actuating screw (311), the third actuating nut (312) and the third shift fork (316), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating motor (301), a third actuating screw (311), a third actuating nut (312), and/or a third anti-rotation guide rod (313), and/or a third actuating pin (314), and/or a third actuating link (315), wherein the third actuating motor (301) is a power source of the actuating device (AM), a housing of the third actuating motor (301) is fixedly connected with a frame of the machine (M), a rotor of the third actuating motor (301) is directly or indirectly connected with the third actuating screw (311), and the third actuating screw (311) rotates together with the rotor of the third actuating motor (301), the third actuating screw (311) and the third actuating nut (312) are directly or indirectly connected through a screw pair, and the third actuating nut (312) moves in an axial direction relative to the frame of the machine (M), and/or the third actuating nut (312) is directly or indirectly fixedly connected with the third anti-rotation guide rod (313) and the third anti-rotation guide rod (313) moves in the axial direction relative to the frame of the machine (M), and/or the third actuating nut (312) is directly or indirectly connected with the clutch device (CM) and the clutch device (CM) selectively realizes various engaging or disengaging actions directly or indirectly under the action of the third actuating nut (312), and/or the third actuating nut (312) is directly or indirectly fixedly connected with the third actuating link (315), and/or the third actuating link (315) is directly or indirectly connected with the third actuating pin (314), and/or the third actuating pin (314) is directly or indirectly connected with the clutch device (CM) and the clutch device (CM) is directly or indirectly selectively under the action of the third actuating pin (314) -various engagement or disengagement actions are carried out, said third actuation motor (301) being connected in turn to said Clutch Means (CM) through said third actuation screw (311), said third actuation nut (312), and/or said third actuation link (315), and/or said third actuation pin (314), and said Clutch Means (CM) being selectively brought into various engagement or disengagement actions under the indirect action of said third actuation motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuation motor (301), a third actuation screw (311), a third actuation nut (312), and/or a third actuation pin (314), and/or a third actuation link (315), and/or a third shift rod (317), the third actuation motor (301) being the power source of the actuation device (AM), the housing of the third actuation motor (301) being fixedly connected to the frame of the machine (M), the rotor of the third actuation motor (301) being directly or indirectly connected to the third actuation screw (311), and the third actuation screw (311) rotating with the rotor of the third actuation motor (301), the third actuation screw (311) being directly or indirectly connected to the third actuation nut (312) by a screw pair, the third actuation nut (312) moving axially relative to the frame of the machine (M), and/or said third actuating nut (312) is directly or indirectly fixedly connected to said third shift guide (317) and said third shift guide (317) is axially displaced relative to the frame of said machine (M), and/or said third actuating nut (312) is directly or indirectly connected to said Clutch Means (CM) and said Clutch Means (CM) is directly or indirectly selectively engaged or disengaged by the action of said third actuating nut (312), and/or said third actuating nut (312) is directly or indirectly connected to said third actuating link (315) and/or said third actuating link (315) is directly or indirectly connected to said third actuating pin (314) and/or said third actuating pin (314) is directly or indirectly connected to said Clutch Means (CM) and said Clutch Means (CM) is selectively engaged by the action of said third actuating pin (314) Various engaging or disengaging actions are carried out, and/or the third actuating motor (301) is connected with the clutch device (CM) through the third actuating screw rod (311), the third actuating nut (312), the third actuating connecting rod (315) and/or the third actuating pin (314) in sequence, and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuator motor (301), a third actuator screw (311), a third actuator nut (312), and/or a third actuator pin (314), and/or a third actuator link (315), the third actuator motor (301) being the power source of the actuator device (AM), the housing of the third actuator motor (301) being fixedly connected to the frame of the machine (M), the rotor of the third actuator motor (301) being directly or indirectly connected to the third actuator nut (312), and the third actuator nut (312) rotating with the rotor of the third actuator motor (301), the third actuator screw (311) being directly or indirectly connected to the third actuator nut (312) by a screw pair, the third actuator screw (311) moving axially relative to the frame of the machine (M), and/or the third actuator screw (311) being directly or indirectly connected to the clutch device (CM), And the clutch device (CM) is directly or indirectly used for realizing various engaging or disengaging actions under the action of the third actuating screw rod (311), and/or the third actuating screw rod (311) is directly or indirectly connected with the third actuating connecting rod (315), and/or the third actuating connecting rod (315) is directly or indirectly connected with the third actuating pin (314), and/or the third actuating pin (314) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) is directly or indirectly used for realizing various engaging or disengaging actions under the action of the third actuating pin (314), and/or the third actuating motor (301) is sequentially used for realizing various engaging or disengaging actions through the third actuating nut (312), the third actuating screw rod (311), and/or the third actuating connecting rod (315), And/or the third actuating pin (314) is connected to the clutch device (CM) and the clutch device (CM) selectively carries out various engaging or disengaging actions under the indirect action of the third actuating motor (301); and/or

The Actuation Means (AM) comprise at least: a third actuating hydraulic cylinder (303), and/or a third anti-rotation guide rod (313), a third shifting fork (316), wherein the third actuating hydraulic cylinder (303) is a power source of the actuating device (AM), a shell of the third actuating hydraulic cylinder (303) is fixedly connected with a frame of the machine (M), a piston of the third actuating hydraulic cylinder (303) is directly or indirectly connected with the third shifting fork (316), the third shifting fork (316) is directly or indirectly connected with the third anti-rotation guide rod (313), the third anti-rotation guide rod (313) moves in the axial direction relative to the frame of the machine (M), the third shifting fork (316) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) selectively realizes various engaging or disengaging actions directly or indirectly under the action of the third shifting fork (316), the third actuating hydraulic cylinder (303) is connected with the clutch device (CM) through the third gear shifting fork (316), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating hydraulic cylinder (303); and/or

The Actuation Means (AM) comprise at least: a third actuating hydraulic cylinder (303), a third shifting fork (316) and/or a third shifting rod (317), wherein the third actuating hydraulic cylinder (303) is a power source of the actuating device (AM), a shell of the third actuating hydraulic cylinder (303) is fixedly connected with a frame of the machine (M), a piston of the third actuating hydraulic cylinder (303) is directly or indirectly connected with the third shifting fork (316), the third shifting fork (316) is directly or indirectly connected with the third shifting rod (317), the third shifting rod (317) moves in the axial direction relative to the frame of the machine (M), the third shifting fork (316) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) selectively realizes various engaging or disengaging actions directly or indirectly under the action of the third shifting fork (316), the third actuating hydraulic cylinder (303) is connected with the clutch device (CM) through the third gear shifting fork (316), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the third actuating hydraulic cylinder (303); and/or

The Actuation Means (AM) comprise at least: a third actuating hydraulic cylinder (303), and/or a third anti-rotation guide rod (313), and/or a third actuating pin (314), and/or a third actuating link (315), the third actuating hydraulic cylinder (303) being a power source of the actuating device (AM), a housing of the third actuating hydraulic cylinder (303) being fixedly connected to a frame of the machine (M), a piston of the third actuating hydraulic cylinder (303) being directly or indirectly connected to the third actuating link (315), the third actuating link (315) being directly or indirectly connected to the third anti-rotation guide rod (313), and the third anti-rotation guide rod (313) moving in an axial direction relative to the frame of the machine (M), the third actuating link (315) being directly or indirectly connected to the third actuating pin (314), and/or the third actuating pin (314) being directly or indirectly connected to the clutch device (CM), The clutch device (CM) is directly or indirectly under the action of the third actuating pin (314) to selectively realize various engaging or disengaging actions, the third actuating hydraulic cylinder (303) is connected with the clutch device (CM) through the third actuating connecting rod (315) and the third actuating pin (314) in sequence, and the clutch device (CM) is selectively realized under the indirect action of the third actuating hydraulic cylinder (303) to realize various engaging or disengaging actions; and/or

The Actuation Means (AM) comprise at least: a third actuating cylinder (303), and/or a third actuating pin (314), and/or a third actuating link (315), and/or a third shift rod (317), the third actuating cylinder (303) being the power source of the actuating device (AM), the housing of the third actuating cylinder (303) being fixedly connected to the frame of the machine (M), the piston of the third actuating cylinder (303) being directly or indirectly connected to the third actuating link (315), and/or the third actuating link (315) being directly or indirectly connected to the third shift rod (317), and the third shift rod (317) being axially movable relative to the frame of the machine (M), and/or the third actuating link (315) being directly or indirectly connected to the third actuating pin (314), and/or the third pin (314) being directly or indirectly connected to the clutch device (CM), And the clutch device (CM) can selectively realize various engaging or disengaging actions under the action of the third actuating pin (314) directly or indirectly, and/or the third actuating hydraulic cylinder (303) is connected with the clutch device (CM) through the third actuating connecting rod (315) and the third actuating pin (314) in turn, and the clutch device (CM) can selectively realize various engaging or disengaging actions under the action of the third actuating hydraulic cylinder (303) indirectly.

11. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

said adjusting means (RM) comprise at least: a motor adjusting device (426), and/or a hydraulic adjusting device (427), and/or a manual adjusting device (428), and/or an air pressure adjusting device (429), and/or an electromagnetic adjusting device (430), and/or a piezoelectric adjusting device (431), and/or a magnetic extension adjusting device (432), and/or a memory metal adjusting device (433), and/or a thermal expansion and contraction adjusting device (434);

the motor adjusting device (426) is at least provided with a function of directly or indirectly adjusting the damping magnitude or the damping effect of the damping Device (DM) by using a motor; and/or

The hydraulic adjusting device (427) is at least configured to adjust the damping magnitude or the damping effect of the damping Device (DM) by a hydraulic cylinder directly or indirectly; and/or

The manual adjusting device (428) is at least provided with a function of manually adjusting the damping magnitude or the damping effect of the damping Device (DM) by human power directly or indirectly; and/or

The electromagnetic adjusting device (430) is at least provided with a function of adjusting the damping magnitude or the damping effect of the buffer damping Device (DM) directly or indirectly by utilizing an electromagnet; and/or

The air pressure adjusting device (429) is at least provided with a function of adjusting the damping magnitude or the damping effect of the damping Device (DM) by a pneumatic cylinder directly or indirectly; and/or

The piezoelectric adjusting device (431) is at least provided with the function of directly or indirectly adjusting the damping magnitude or the damping effect of the damping Device (DM) by utilizing the piezoelectric effect of the piezoelectric material; and/or

The magnetic extension adjusting device (432) is at least provided with a function of adjusting the damping size or the damping effect of the buffer damping Device (DM) directly or indirectly by utilizing the extension and retraction of a magnetic conductive material under the action of a magnetic field; and/or

The memory metal adjusting device (433) is at least provided with the function of adjusting the damping size or the buffering effect of the buffering damping Device (DM) directly or indirectly by utilizing the shape memory effect of the memory metal; and/or

The expansion and contraction adjusting device (434) is configured to at least have the function of directly or indirectly adjusting the damping size or the damping effect of the damping Device (DM) by utilizing the expansion and contraction effect of the material;

said adjusting means (RM) comprise at least: a fourth adjusting motor (401) and/or a fourth adjusting transmission mechanism (402), wherein the fourth adjusting motor (401) is a power source of the actuating device (AM), a shell of the fourth adjusting motor (401) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the fourth adjusting motor (401), the fourth adjusting transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth adjusting motor (401), and/or the fourth adjusting transmission mechanism (402) at least has a function of transmitting the power, the rotating speed, the load, the rotating angle, the displacement or the direction of the fourth adjusting motor (401), and/or the fourth adjusting transmission mechanism (402) is directly or indirectly connected with the clutch device (CM), The fourth adjusting motor (401) is connected with the clutch device (CM) through the fourth adjusting transmission mechanism (402), and/or the fourth adjusting motor (401) selectively actuates the clutch device (CM) through the fourth adjusting transmission mechanism (402) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403) and/or a fourth adjusting transmission mechanism (402), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the actuating device (AM), a cylinder body of the fourth adjusting hydraulic cylinder (403) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the fourth adjusting hydraulic cylinder (403), the fourth adjusting transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth adjusting hydraulic cylinder (403), and/or the fourth adjusting transmission mechanism (402) at least has a function of transmitting the power, load, displacement or direction of the fourth adjusting hydraulic cylinder (403), and/or the fourth adjusting transmission mechanism (402) is directly or indirectly connected with the clutch device (CM), The fourth adjusting hydraulic cylinder (403) is connected with the clutch device (CM) through the fourth adjusting transmission mechanism (402), and/or the fourth adjusting hydraulic cylinder (403) selectively actuates the clutch device (CM) through the fourth adjusting transmission mechanism (402) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the fourth adjusting hydraulic cylinder (403); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting handle (404) and/or a fourth adjusting transmission mechanism (402), wherein the fourth adjusting handle (404) is connected with the frame of the machine (M), the fourth adjusting handle (404) rotates relative to the frame of the machine (M) within a certain angle range, and/or the fourth adjusting handle (404) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) can be selectively engaged or disengaged by manpower directly or indirectly through the fourth adjusting handle (404), and/or the fourth adjusting handle (404) is directly or indirectly connected with the fourth adjusting transmission mechanism (402), the fourth adjusting transmission mechanism (402) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) can be selectively engaged or disengaged by manpower sequentially passing through the fourth adjusting handle (404) and the fourth adjusting transmission mechanism (402) A disengaging action, and/or the fourth adjustment transmission mechanism (402) has a function of transmitting power of at least the fourth adjustment handle (404) in a variable speed, and/or the fourth adjustment transmission mechanism (402) has a function of transmitting power, load, displacement or direction of at least the fourth adjustment handle (404); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting pneumatic cylinder (405) and/or a fourth adjusting transmission mechanism (402), wherein the fourth adjusting pneumatic cylinder (405) is a power source of the actuating device (AM), a cylinder body of the fourth adjusting pneumatic cylinder (405) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the fourth adjusting pneumatic cylinder (405), the fourth adjusting transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth adjusting pneumatic cylinder (405), and/or the fourth adjusting transmission mechanism (402) at least has a function of transmitting the power, load, displacement or direction of the fourth adjusting pneumatic cylinder (405), and/or the fourth adjusting transmission mechanism (402) is directly or indirectly connected with the clutch device (CM), Said fourth adjusting pneumatic cylinder (405) being connected to said Clutch Means (CM) through said fourth adjusting transmission (402) and/or said fourth adjusting pneumatic cylinder (405) selectively actuating said Clutch Means (CM) through said fourth adjusting transmission (402) so as to cause said Clutch Means (CM) to selectively effect various engagement or disengagement actions under the control of said fourth adjusting pneumatic cylinder (405); and/or

Said adjusting means (RM) comprise at least: a fourth regulating electromagnetic valve (406) and/or a fourth regulating transmission mechanism (402), wherein the fourth regulating electromagnetic valve (406) is a power source of the actuating device (AM), a shell of the fourth regulating electromagnetic valve (406) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under the direct or indirect actuation of the fourth regulating electromagnetic valve (406), the fourth regulating transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth regulating electromagnetic valve (406), and/or the fourth regulating transmission mechanism (402) at least has a function of transmitting the power, load, displacement or direction of the fourth regulating electromagnetic valve (406), and/or the fourth regulating transmission mechanism (402) is directly or indirectly connected with the clutch device (CM), The fourth regulating solenoid valve (406) is connected with the clutch device (CM) through the fourth regulating transmission mechanism (402), and/or the fourth regulating solenoid valve (406) selectively actuates the clutch device (CM) through the fourth regulating transmission mechanism (402) so as to enable the clutch device (CM) to selectively realize various engaging or disengaging actions under the control of the fourth regulating solenoid valve (406); and/or

Said adjusting means (RM) comprise at least: a fourth piezoelectric actuator (407) and/or a fourth actuator transmission (402), the fourth piezoelectric actuator (407) being a power source of the Actuator (AM), the fourth piezoelectric actuator (407) having at least a function of outputting power by utilizing a piezoelectric effect or a piezoelectric reverse effect, a housing of the fourth piezoelectric actuator (407) being fixedly connected to a frame of the machine (M), the clutch device (CM) being selectively brought into various engagement and disengagement actions upon direct or indirect actuation of the fourth piezoelectric actuator (407), the fourth actuator transmission (402) having at least a function of transmitting power of the fourth piezoelectric actuator (407) at a variable speed, and/or the fourth actuator transmission (402) having at least a function of transmitting power, load, displacement or direction of the fourth piezoelectric actuator (407), and/or the fourth regulating gear (402) is directly or indirectly connected to the clutch device (CM), the fourth piezoelectric actuator (407) is connected to the clutch device (CM) via the fourth regulating gear (402), and/or the fourth regulating solenoid valve (406) selectively actuates the clutch device (CM) via the fourth regulating gear (402) in order to selectively effect various engagement or disengagement actions of the clutch device (CM) under the control of the fourth piezoelectric actuator (407); and/or

Said adjusting means (RM) comprise at least: a fourth magnetostrictive actuator (408) and/or a fourth adjusting transmission mechanism (402), wherein the fourth magnetostrictive actuator (408) is a power source of the actuating device (AM), the fourth magnetostrictive actuator (408) has at least a function of outputting power by using a magnetostrictive effect or a magnetostrictive reverse effect, a housing of the fourth magnetostrictive actuator (408) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engaging or disengaging actions under direct or indirect actuation of the fourth magnetostrictive actuator (408), the fourth adjusting transmission mechanism (402) has at least a variable speed transmission function for the power of the fourth magnetostrictive actuator (408), and/or the fourth adjusting transmission mechanism (402) has at least a function of transmitting the power of the fourth magnetostrictive actuator (408), -a function of load, displacement or direction, and/or said fourth adjustment transmission (402) is directly or indirectly connected to said Clutch Means (CM), said fourth magnetostrictive regulator (408) is connected to said Clutch Means (CM) through said fourth adjustment transmission (402), and/or said fourth magnetostrictive regulator (408) selectively actuates said Clutch Means (CM) through said fourth adjustment transmission (402) so as to selectively enable various engagement or disengagement actions of said Clutch Means (CM) under the control of said fourth magnetostrictive regulator (408); and/or

Said adjusting means (RM) comprise at least: a fourth memory metal regulator (409) and/or a fourth regulation transmission mechanism (402), wherein the fourth memory metal regulator (409) is a power source of the actuating device (AM), the fourth memory metal regulator (409) at least has a function of outputting power by utilizing a shape memory effect of memory metal, a shell of the fourth memory metal regulator (409) is fixedly connected with a frame of the machine (M), the clutch device (CM) selectively realizes various engagement or disengagement actions under direct or indirect actuation of the fourth memory metal regulator (409), the fourth regulation transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth memory metal regulator (409), and/or the fourth regulation transmission mechanism (402) at least has a function of transmitting the power of the fourth memory metal regulator (409), -a function of load, displacement or direction, and/or said fourth adjusting gear (402) is directly or indirectly connected to said Clutch Means (CM), said fourth memory metal adjuster (409) is connected to said Clutch Means (CM) through said fourth adjusting gear (402), and/or said fourth memory metal adjuster (409) selectively actuates said Clutch Means (CM) through said fourth adjusting gear (402) so as to selectively enable various engagement or disengagement actions of said Clutch Means (CM) under the control of said fourth memory metal adjuster (409); and/or

Said adjusting means (RM) comprise at least: a fourth expansion and contraction regulator (410) and/or a fourth regulation transmission mechanism (402), wherein the fourth expansion and contraction regulator (410) is a power source of the actuating device (AM), the fourth expansion and contraction regulator (410) at least has a function of outputting power by utilizing an expansion and contraction effect, a shell of the fourth expansion and contraction regulator (410) is fixedly connected with a rack of the machine (M), a clutch device (CM) selectively realizes various engagement or disengagement actions under direct or indirect actuation of the fourth expansion and contraction regulator (410), the fourth regulation transmission mechanism (402) at least has a variable speed transmission function for the power of the fourth expansion and contraction regulator (410), and/or the fourth regulation transmission mechanism (402) at least has a function of transmitting the power of the fourth expansion and contraction regulator (410), -a function of load, displacement or direction, and/or the fourth adjustment transmission (402) is directly or indirectly connected to the Clutch Means (CM), the fourth expansion-contraction regulator (410) is connected to the Clutch Means (CM) via the fourth adjustment transmission (402), and/or the fourth expansion-contraction regulator (410) selectively actuates the Clutch Means (CM) via the fourth adjustment transmission (402) so as to selectively effect various engagement or disengagement actions of the Clutch Means (CM) under the control of the fourth expansion-contraction regulator (410); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth anti-rotation guide rod (413), a fourth adjusting fork (416), the fourth adjusting motor (401) is the power source of the adjusting device (RM), the housing of the fourth adjusting motor (401) is fixedly connected with the frame of the machine (M), the rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting screw (411), and the fourth adjusting screw (411) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) is directly or indirectly connected with the fourth adjusting nut (412) through a thread pair, the fourth adjusting nut (412) moves in the axial direction relative to the frame of the machine (M), and the fourth adjusting nut (412) is directly or indirectly connected with the fourth anti-rotation guide rod (413), The fourth anti-rotation guide rod (413) moves in the axial direction relative to the frame of the machine (M), the fourth adjusting nut (412) is directly or indirectly connected with the fourth adjusting shifting fork (416), the fourth adjusting shifting fork (416) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) is directly or indirectly used for selectively realizing various engaging or disengaging actions under the action of the fourth adjusting shifting fork (416), the fourth adjusting motor (401) is sequentially connected with the fourth adjusting screw rod (411), the fourth adjusting nut (412) and the fourth adjusting shifting fork (416) and is connected with the clutch device (CM), and the clutch device (CM) is selectively used for realizing various engaging or disengaging actions under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), a fourth adjusting fork (416), and/or a fourth adjusting guide (417), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected to a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected to the fourth adjusting screw (411), and the fourth adjusting screw (411) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) and the fourth adjusting nut (412) are directly or indirectly connected by a screw pair, the fourth adjusting nut (412) moves in an axial direction relative to the frame of the machine (M), and the fourth adjusting nut (412) is directly or indirectly connected to the fourth adjusting fork (416), the fourth adjusting fork (416) is directly or indirectly connected with the fourth adjusting guide rod (417), the fourth adjusting guide rod (417) moves axially relative to the frame of the machine (M), the fourth adjusting fork (416) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the fourth adjusting fork (416), the fourth adjusting motor (401) is sequentially connected with the clutch device (CM) through the fourth adjusting screw rod (411), the fourth adjusting nut (412) and the fourth adjusting fork (416), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and a fourth adjusting fork (416), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected to a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected to the fourth adjusting nut (412), and the fourth adjusting nut (412) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) and the fourth adjusting nut (412) are directly or indirectly connected through a thread pair, the fourth adjusting screw (411) moves in an axial direction relative to the frame of the machine (M), and the fourth adjusting screw (411) is directly or indirectly connected to the fourth adjusting fork (416), the fourth adjusting fork (416) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) is directly or indirectly under the action of the fourth adjusting fork (416) to selectively realize various engagement or disengagement actions, the fourth adjusting motor (401) is sequentially connected with the clutch device (CM) through the fourth adjusting screw rod (411), the fourth adjusting nut (412) and the fourth adjusting fork (416), and the clutch device (CM) is selectively realized under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), a fourth adjusting fork (416), and a fourth adjusting guide (417), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected to a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected to the fourth adjusting nut (412), and the fourth adjusting nut (412) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) and the fourth adjusting nut (412) are directly or indirectly connected by a screw pair, the fourth adjusting screw (411) moves in an axial direction relative to the frame of the machine (M), and the fourth adjusting screw (411) is directly or indirectly connected to the fourth adjusting fork (416), the fourth adjusting fork (416) is directly or indirectly connected with the fourth adjusting guide rod (417), the fourth adjusting guide rod (417) moves axially relative to the frame of the machine (M), the fourth adjusting fork (416) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) selectively realizes various engaging or disengaging actions under the action of the fourth adjusting fork (416), the fourth adjusting motor (401) is sequentially connected with the clutch device (CM) through the fourth adjusting screw rod (411), the fourth adjusting nut (412) and the fourth adjusting fork (416), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth anti-rotation guide rod (413), and/or a fourth adjusting pin (414), and/or a fourth adjusting link (415), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected with a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting screw (411), and the fourth adjusting screw (411) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) is directly or indirectly connected with the fourth adjusting nut (412) through a thread pair, and the fourth adjusting nut (412) moves in an axial direction relative to the frame of the machine (M), the fourth adjusting nut (412) is directly or indirectly connected with the fourth anti-transduction rod (413), the fourth anti-rotation guide rod (413) moves in the axial direction relative to the frame of the machine (M), the fourth adjusting nut (412) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) selectively realizes various engagement or disengagement actions under the action of the fourth adjusting nut (412), the fourth adjusting nut (412) is directly or indirectly connected with the fourth adjusting connecting rod (415), the fourth adjusting connecting rod (415) is directly or indirectly connected with the fourth adjusting pin (414), the fourth adjusting pin (414) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) selectively realizes various engagement or disengagement actions under the action of the fourth adjusting pin (414), the fourth adjusting motor (401) is connected with the clutch device (CM) sequentially through the fourth adjusting screw rod (411), the fourth adjusting nut (412), the fourth adjusting connecting rod (415) and the fourth adjusting pin (414), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth adjusting pin (414), and/or a fourth adjusting link (415), and/or a fourth adjusting guide (417), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected with a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting screw (411), and the fourth adjusting screw (411) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) and the fourth adjusting nut (412) are directly or indirectly connected through a thread pair, and the fourth adjusting nut (412) moves in an axial direction relative to the frame of the machine (M), said fourth adjusting nut (412) being directly or indirectly connected to said fourth adjusting stem (417) and said fourth adjusting stem (417) moving axially relative to the frame of said machine (M), and/or said fourth adjusting nut (412) being directly or indirectly connected to said Clutch Means (CM) and said Clutch Means (CM) being directly or indirectly selectively put into various engagement or disengagement actions under the action of said fourth adjusting nut (412), said fourth adjusting nut (412) being directly or indirectly connected to said fourth adjusting link (415), said fourth adjusting link (415) being directly or indirectly connected to said fourth adjusting pin (414), said fourth adjusting pin (414) being directly or indirectly connected to said Clutch Means (CM) and said Clutch Means (CM) being directly or indirectly selectively put into various engagement or disengagement actions under the action of said fourth adjusting pin (414), the fourth adjusting motor (401) is connected with the clutch device (CM) sequentially through the fourth adjusting screw rod (411), the fourth adjusting nut (412), the fourth adjusting connecting rod (415) and the fourth adjusting pin (414), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting motor (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth adjusting pin (414), and/or a fourth adjusting link (415), the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixedly connected with a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting nut (412), and the fourth adjusting nut (412) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) is directly or indirectly connected with the fourth adjusting nut (412) through a screw pair, the fourth adjusting screw (411) moves in an axial direction relative to the frame of the machine (M), and the fourth adjusting screw (411) is directly or indirectly connected with the clutch device (CM), a second adjusting pin (414) is connected with the clutch device (CM), and a second adjusting pin (415), The clutch device (CM) is directly or indirectly connected with the fourth adjusting screw rod (411) to selectively realize various engaging or disengaging actions, the fourth adjusting screw rod (411) is directly or indirectly connected with the fourth adjusting connecting rod (415), the fourth adjusting connecting rod (415) is directly or indirectly connected with the fourth adjusting pin (414), the fourth adjusting pin (414) is directly or indirectly connected with the clutch device (CM), the clutch device (CM) is directly or indirectly connected with the clutch device (414) to selectively realize various engaging or disengaging actions, the fourth adjusting motor (401) is sequentially connected with the clutch device (CM) through the fourth adjusting nut (412), the fourth adjusting screw rod (411), the fourth adjusting connecting rod (415) and the fourth adjusting pin (414), and said Clutch Means (CM) selectively effecting various engagement or disengagement actions under the indirect action of said fourth regulating electrical machine (401); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth anti-rotation guide rod (413), a fourth separation fork (418), a fourth separation bearing (419), a fourth diaphragm spring (420), a fourth diaphragm spring support pin (421), and/or a fourth diaphragm spring pressure bearing disc (422), a fourth diaphragm spring cover plate (423), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixed with a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting screw (411), and the fourth adjusting screw (411) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting screw (411) is directly or indirectly connected with the fourth adjusting nut (412) through a screw pair, the fourth adjusting nut (412) moves axially relative to the frame of the machine (M), and/or the fourth adjusting nut (412) is directly or indirectly connected to the fourth anti-transduction rod (413) and the fourth anti-rotation rod (413) moves axially relative to the frame of the machine (M), and/or the fourth disconnecting fork (418) is directly or indirectly connected to the frame of the machine (M), the fourth adjusting nut (412) is directly or indirectly connected to the fourth disconnecting fork (418), the fourth disconnecting fork (418) is rotatable within a certain angular range relative to the frame of the machine (M) under the action of the fourth adjusting nut (412), and/or the fourth disconnecting fork (418) is directly or indirectly connected to the fourth disconnecting bearing (419), and the fourth disconnecting bearing (419) moves axially along the fourth disconnecting fork (418) under the action of the fourth disconnecting fork, and/or the fourth release bearing (419) is directly or indirectly connected to the fourth diaphragm spring (420), and/or the fourth diaphragm spring (420) is connected to the fourth diaphragm spring cover plate (423) via the fourth diaphragm spring support pin (421), and/or the fourth diaphragm spring cover plate (423) is directly or indirectly connected to the damping Device (DM), and/or the fourth diaphragm spring (420) is directly or indirectly connected to the damping Device (DM), and/or the damping Device (DM) is selectively adjusted in its load-bearing and damping dimensions directly or indirectly under the action of the fourth diaphragm spring (420), and/or the fourth diaphragm spring (420) is directly or indirectly connected to the fourth diaphragm spring pressure plate (422), and/or the fourth diaphragm spring pressure plate (422) is directly or indirectly connected to the damping Device (DM) -connecting, and/or the cushion Damper Means (DM) is selectively adjustable in its load capacity and damping capacity directly or indirectly by the fourth diaphragm spring bearing disc (422), and/or the fourth diaphragm spring (420) is in an initial state, the load capacity and damping capacity of the cushion Damper Means (DM) are at a maximum, or the fourth diaphragm spring (420) is in an initial state, the load capacity and damping capacity of the cushion Damper Means (DM) are at a minimum, or the fourth diaphragm spring (420) is in an initial state, the load capacity and damping capacity of the cushion Damper Means (DM) are at an intermediate state, or the fourth diaphragm spring (420) has at least a function of restoring its initial state by the fourth diaphragm spring bearing pin (421) when the fourth release bearing (419) exerts a smaller force on the fourth diaphragm spring (420), and/or the fourth adjusting motor (401) is connected with the buffer damping Device (DM) sequentially through the fourth adjusting screw rod (411), the fourth adjusting nut (412), the fourth release fork (418), the fourth release bearing (419), the fourth diaphragm spring (420) and/or the fourth diaphragm spring pressure bearing plate (422), and the buffer damping Device (DM) is controlled indirectly by the fourth adjusting motor (401) to selectively adjust the bearing capacity and the damping magnitude thereof, so that the buffer damping Device (DM) has different damping and buffering characteristics, and/or the fourth diaphragm spring (420) is provided with at least the function of compensating to some extent the reduction of the axial thickness of the second friction plate (212) and the second counter plate (213) of the damper Device (DM) due to wear; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), a fourth release fork (418), a fourth release bearing (419), a fourth diaphragm spring (420), a fourth diaphragm spring bearing pin (421), and/or a fourth diaphragm spring bearing plate (422), a fourth diaphragm spring cover plate (423), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixed with a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected with the fourth adjusting nut (412), the fourth adjusting nut (412) rotates together with the rotor of the fourth adjusting motor (401), and the fourth adjusting nut (412) is directly or indirectly connected with the fourth adjusting screw (411) through a screw pair, the fourth adjusting screw (411) moves in the axial direction of the machine (M) relative to the machine frame, and/or the fourth shift fork (418) is directly or indirectly connected to the machine frame of the machine (M), the fourth adjusting screw (411) is directly or indirectly connected to the fourth shift fork (418), the fourth shift fork (418) can rotate in a certain angle range relative to the machine frame of the machine (M) under the action of the fourth adjusting screw (411), and/or the fourth shift fork (418) is directly or indirectly connected to the fourth release bearing (419), and the fourth release bearing (419) moves in the axial direction under the action of the fourth shift fork (418), and/or the fourth release bearing (419) is directly or indirectly connected to the fourth diaphragm spring (420), and/or the fourth diaphragm spring (420) is supported by the fourth diaphragm spring support pin (421) and the fourth diaphragm spring support pin (421) The fourth diaphragm spring cover plate (423) is connected, and/or the fourth diaphragm spring cover plate (423) is directly or indirectly connected with the damping Device (DM), and/or the fourth diaphragm spring (420) is directly or indirectly connected with the damping Device (DM), and/or the damping Device (DM) is directly or indirectly under the action of the fourth diaphragm spring (420) to selectively adjust the load size and the damping size thereof, and/or the fourth diaphragm spring (420) is directly or indirectly connected with the fourth diaphragm spring pressure bearing plate (422), and/or the fourth diaphragm spring pressure bearing plate (422) is directly or indirectly connected with the damping Device (DM), and/or the damping Device (DM) is directly or indirectly under the action of the fourth diaphragm spring pressure bearing plate (422) to selectively adjust the load size and the damping size thereof, and/or the bearing capacity and the damping magnitude of the buffer damping Device (DM) are in the maximum state when the fourth diaphragm spring (420) is in the initial state, or the bearing capacity and the damping magnitude of the buffer damping Device (DM) are in the minimum state when the fourth diaphragm spring (420) is in the initial state, or the bearing capacity and the damping magnitude of the buffer damping Device (DM) are in the intermediate state when the fourth diaphragm spring (420) is in the initial state, or the fourth diaphragm spring (420) at least has the function of recovering the initial state under the action of the fourth diaphragm spring supporting pin (421) when the acting force of the fourth release bearing (419) on the fourth diaphragm spring (420) is small, and/or the fourth adjusting motor (401) sequentially passes through the fourth adjusting nut (412), The fourth adjusting screw rod (411), the fourth release fork (418), the fourth release bearing (419), the fourth diaphragm spring (420), and/or the fourth diaphragm spring pressure-bearing disc (422) are connected with the damping Device (DM), and the damping Device (DM) selectively adjusts the bearing capacity and damping magnitude thereof under the indirect control of the fourth adjusting motor (401), so that the damping Device (DM) has different damping and buffering characteristics, and/or the fourth diaphragm spring (420) at least has the function of compensating the reduction of the axial thickness of the second friction plate (212) and the second counter plate (213) of the damping Device (DM) due to wear to a certain extent; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), and/or a fourth rotation-preventing guide rod (413), a fourth disengaging fork (418), a fourth disengaging bearing (419), and/or a fourth adjusting bracket (424), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixed to a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected to the fourth adjusting screw (411), the fourth adjusting screw (411) and the rotor of the fourth adjusting motor (401) rotate together, the fourth adjusting screw (411) and the fourth adjusting nut (412) are directly or indirectly connected by a thread pair, the fourth adjusting nut (412) moves in an axial direction relative to the frame of the machine (M), and/or the fourth adjusting nut (412) is directly or indirectly connected to the fourth anti-rotation rod (413) and the fourth anti-rotation rod (413) moves axially relative to the frame of the machine (M), and/or the fourth shift fork (418) is directly or indirectly connected to the frame of the machine (M), the fourth adjusting nut (412) is directly or indirectly connected to the fourth shift fork (418), the fourth shift fork (418) is rotatable within a certain angle range relative to the frame of the machine (M) under the action of the fourth adjusting nut (412), and/or the fourth shift fork (418) is directly or indirectly connected to the fourth release bearing (419) and the fourth release bearing (419) moves axially along the fourth shift fork (418) under the action of the fourth release fork, and/or the fourth release bearing (419) is directly or indirectly connected to the damping Device (DM) -the connection, and/or the cushion and Damper Means (DM) are/is selectively adjustable in their load capacity and damping capacity directly or indirectly by the fourth release bearing (419), and/or the fourth release bearing (419) is connected to the fourth adjusting bracket (424), and/or the fourth adjusting bracket (424) is directly or indirectly connected to the cushion and Damper Means (DM), and/or the cushion and Damper Means (DM) are selectively adjustable in their load capacity and damping capacity directly or indirectly by the fourth adjusting bracket (424), and/or the fourth adjusting bracket (424) is in its initial state, the load capacity and damping capacity of the cushion and Damper Means (DM) are at their maximum, or the fourth adjusting bracket (424) is in its initial state, the load capacity and damping capacity of the cushion and Damper Means (DM) are at its minimum, or the fourth adjusting bracket (424) is in an initial state, the bearing capacity and the damping magnitude of the damping Device (DM) are in an intermediate state, and/or when the acting force of the fourth release bearing (419) on the fourth adjusting bracket (424) is small, the fourth adjusting bracket (424) at least has the function of recovering the initial state under the action of the damping Device (DM), and/or the fourth adjusting motor (401) is connected with the damping Device (DM) through the fourth adjusting screw rod (411), the fourth adjusting nut (412), the fourth release fork (418), the fourth release bearing (419) and/or the fourth adjusting bracket (424) in sequence, and the damping Device (DM) selectively adjusts the bearing capacity and the damping magnitude under the indirect control of the fourth adjusting motor (401), So that the damping and Dampening Means (DM) have different damping and dampening characteristics, and/or the fourth adjustment bracket (424) has at least the function of compensating to some extent the reduction in the axial thickness of the second friction plate (212) and the second counter plate (213) of the damping and Dampening Means (DM) due to wear; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting motor (401), a fourth adjusting screw (411), a fourth adjusting nut (412), a fourth shift fork (418), a fourth release bearing (419), and/or a fourth adjusting bracket (424), wherein the fourth adjusting motor (401) is a power source of the adjusting device (RM), a housing of the fourth adjusting motor (401) is fixed to a frame of the machine (M), a rotor of the fourth adjusting motor (401) is directly or indirectly connected to the fourth adjusting nut (412), and the fourth adjusting nut (412) rotates together with the rotor of the fourth adjusting motor (401), the fourth adjusting nut (412) is directly or indirectly connected to the fourth adjusting screw (411) through a screw pair, and the fourth adjusting screw (411) moves in the axial direction of the machine (M) relative to the frame of the machine, and/or the fourth release fork (418) is directly or indirectly connected to the machine frame (M), the fourth adjusting screw (411) is directly or indirectly connected to the fourth release fork (418), the fourth release fork (418) is rotatable within a certain angle range relative to the machine frame (M) under the action of the fourth adjusting screw (411), and/or the fourth release fork (418) is directly or indirectly connected to the fourth release bearing (419), and the fourth release bearing (419) is axially movable along the fourth release fork (418) under the action of the fourth release fork, and/or the fourth release bearing (419) is directly or indirectly connected to the damping Device (DM), and/or the damping Device (DM) is selectively adjustable in its load-carrying size and its damping size under the action of the fourth release bearing (419), and/or the fourth release bearing (419) is connected with the fourth adjusting bracket (424), and/or the fourth adjusting bracket (424) is directly or indirectly connected with the damping Device (DM), and/or the damping Device (DM) is directly or indirectly selectively adjusted in the load-bearing capacity and the damping capacity under the action of the fourth adjusting bracket (424), and/or the load-bearing capacity and the damping capacity of the damping Device (DM) are in the maximum state when the fourth adjusting bracket (424) is in the initial state, or the load-bearing capacity and the damping capacity of the damping Device (DM) are in the minimum state when the fourth adjusting bracket (424) is in the initial state, or the load-bearing capacity and the damping capacity of the damping Device (DM) are in the intermediate state when the fourth adjusting bracket (424) is in the initial state, and/or when the acting force of the fourth release bearing (419) on the fourth adjusting bracket (424) is small, the fourth adjusting bracket (424) at least has the function of recovering the initial state under the action of the buffer damping Device (DM), and/or the fourth adjusting motor (401) is connected with the buffer damping Device (DM) through the fourth adjusting nut (412), the fourth adjusting screw rod (411), the fourth release fork (418), the fourth release bearing (419) and/or the fourth adjusting bracket (424) in sequence, and the buffer damping Device (DM) selectively adjusts the bearing capacity and the damping magnitude under the indirect control of the fourth adjusting motor (401) so as to enable the buffer damping Device (DM) to have different damping and buffering characteristics, and/or the fourth adjusting bracket (424) at least has the function of compensating the buffer damping device to a certain Degree (DM) DM) and the axial thickness reduction of the second friction plate (212) and the second counter plate (213) due to wear; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403) and/or a fourth anti-rotation guide rod (413), a fourth adjusting fork (416), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the adjusting device (RM), a shell of the fourth adjusting hydraulic cylinder (403) is fixedly connected with a frame of the machine (M), a piston of the fourth adjusting hydraulic cylinder (403) is directly or indirectly connected with the fourth adjusting fork (416), and/or the fourth adjusting fork (416) is directly or indirectly connected with the fourth anti-rotation guide rod (413), the fourth anti-rotation guide rod (413) moves in the axial direction relative to the frame of the machine (M), and/or the fourth adjusting fork (416) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) selectively realizes various engaging or disengaging actions directly or indirectly under the action of the fourth adjusting fork (416), and/or the fourth adjusting hydraulic cylinder (403) is connected with the clutch device (CM) through the fourth adjusting shifting fork (416), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting hydraulic cylinder (403); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403), a fourth adjusting fork (416), and/or a fourth adjusting guide (417), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the adjusting device (RM), a housing of the fourth adjusting hydraulic cylinder (403) is fixedly connected with a frame of the machine (M), a piston of the fourth adjusting hydraulic cylinder (403) is directly or indirectly connected with the fourth adjusting fork (416), and/or the fourth adjusting fork (416) is directly or indirectly connected with a fourth adjusting guide (417), the fourth adjusting guide (417) moves in an axial direction relative to the frame of the machine (M), and/or the fourth adjusting fork (416) is directly or indirectly connected with the clutch device (CM), and the clutch device (CM) selectively realizes various engaging or disengaging actions directly or indirectly under the action of the fourth adjusting fork (416), and/or the fourth adjusting hydraulic cylinder (403) is connected with the clutch device (CM) through the fourth adjusting shifting fork (416), and the clutch device (CM) selectively realizes various engaging or disengaging actions under the indirect action of the fourth adjusting hydraulic cylinder (403); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403) and/or a fourth anti-rotation guide rod (413) and/or a fourth adjusting pin (414) and/or a fourth adjusting connecting rod (415), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the adjusting device (RM), a shell of the fourth adjusting hydraulic cylinder (403) is fixedly connected with a frame of the machine (M), a piston of the fourth adjusting hydraulic cylinder (403) is directly or indirectly fixedly connected with the fourth adjusting connecting rod (415), and/or the fourth adjusting connecting rod (415) is directly or indirectly connected with the fourth anti-rotation guide rod (413), and the fourth anti-rotation guide rod (413) moves in an axial direction relative to the frame of the machine (M), and/or the fourth adjusting connecting rod (415) is directly or indirectly connected with the fourth adjusting pin (414), and/or the fourth adjusting pin (414) is directly or indirectly connected with the clutch device (CM), And the clutch device (CM) can realize various engaging or disengaging actions directly or indirectly under the action of the fourth adjusting pin (414), and/or the fourth adjusting hydraulic cylinder (403) is connected with the clutch device (CM) through the fourth adjusting connecting rod (415) and the fourth adjusting pin (414) in sequence, and the clutch device (CM) can realize various engaging or disengaging actions selectively under the indirect action of the fourth adjusting hydraulic cylinder (403); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403) and/or a fourth adjusting pin (414) and/or a fourth adjusting link (415) and/or a fourth adjusting guide (417), the fourth adjusting hydraulic cylinder (403) being the power source of the adjusting device (RM), the housing of the fourth adjusting hydraulic cylinder (403) being fixedly connected to the frame of the machine (M), the piston of the fourth adjusting hydraulic cylinder (403) being directly or indirectly connected to the fourth adjusting link (415), and/or the fourth adjusting link (415) being directly or indirectly connected to the fourth adjusting guide (417), and the fourth adjusting guide (417) moving in the axial direction relative to the frame of the machine (M), and/or the fourth adjusting link (415) being fixedly connected to the fourth adjusting pin (414), and/or the fourth adjusting pin (414) being directly or indirectly connected to the clutch device (CM), And the clutch device (CM) can realize various engaging or disengaging actions directly or indirectly under the action of the fourth adjusting pin (414), and/or the fourth adjusting hydraulic cylinder (403) is connected with the clutch device (CM) through the fourth adjusting connecting rod (415) and the fourth adjusting pin (414) in sequence, and the clutch device (CM) can realize various engaging or disengaging actions selectively under the indirect action of the fourth adjusting hydraulic cylinder (403); and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403), a fourth release fork (418), a fourth release bearing (419), a fourth diaphragm spring (420), a fourth diaphragm spring support pin (421), and/or a fourth diaphragm spring bearing plate (422), a fourth diaphragm spring cover plate (423), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the adjusting device (RM), a housing of the fourth adjusting hydraulic cylinder (403) is fixed with a frame of the machine (M), the fourth release fork (418) is directly or indirectly connected with the frame of the machine (M), the fourth adjusting hydraulic cylinder (403) is directly or indirectly connected with the fourth release fork (418), and the fourth release fork (418) can rotate within a certain angle range relative to the frame of the machine (M) directly or indirectly under the action of the fourth adjusting hydraulic cylinder (403), and/or the fourth release fork (418) is directly or indirectly connected to the fourth release bearing (419) and the fourth release bearing (419) is moved axially under the action of the fourth release fork (418), and/or the fourth release bearing (419) is directly or indirectly connected to the fourth diaphragm spring (420), and/or the fourth diaphragm spring (420) is fixedly connected to the fourth diaphragm spring cover plate (423) via the fourth diaphragm spring bearing pin (421), and/or the fourth diaphragm spring cover plate (423) is directly or indirectly fixedly connected to the damping Device (DM), and/or the fourth diaphragm spring (420) is directly or indirectly connected to the damping Device (DM), and/or the damping Device (DM) is selectively adjusted in its load-bearing and damping dimensions directly or indirectly under the action of the fourth diaphragm spring (420), and/or the fourth diaphragm spring (420) is directly or indirectly connected with the fourth diaphragm spring pressure-bearing disc (422), and/or the fourth diaphragm spring pressure-bearing disc (422) is directly or indirectly connected with the cushion damping Device (DM), and/or the cushion damping Device (DM) is directly or indirectly selectively adjusted in the load-bearing capacity and the damping capacity under the action of the fourth diaphragm spring pressure-bearing disc (422), and/or the load-bearing capacity and the damping capacity of the cushion damping Device (DM) are in the maximum state when the fourth diaphragm spring (420) is in the initial state, or the load-bearing capacity and the damping capacity of the cushion damping Device (DM) are in the minimum state when the fourth diaphragm spring (420) is in the initial state, or the load-bearing capacity and the damping capacity of the cushion damping Device (DM) are in the intermediate state when the fourth diaphragm spring (420) is in the initial state, or when the acting force of the fourth release bearing (419) on the fourth diaphragm spring (420) is small, the fourth diaphragm spring (420) has at least the function of recovering the initial state under the action of the fourth diaphragm spring support pin (421), and/or the fourth adjusting hydraulic cylinder (403) is connected with the damping Device (DM) sequentially through the fourth release fork (418), the fourth release bearing (419), the fourth diaphragm spring (420) and/or the fourth diaphragm spring pressure bearing plate (422), and the damping Device (DM) selectively adjusts the bearing capacity and the damping magnitude under the indirect control of the fourth adjusting hydraulic cylinder (403) so that the damping Device (DM) has different damping and buffering characteristics, and/or the fourth diaphragm spring (420) has at least the second friction compensating the damping Device (DM) to a certain extent A function of the axial thickness reduction of the wiper blade (212) and the second counter blade (213) due to wear; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting hydraulic cylinder (403), a fourth disengaging fork (418), a fourth disengaging bearing (419) and/or a fourth adjusting bracket (424), wherein the fourth adjusting hydraulic cylinder (403) is a power source of the adjusting device (RM), a housing of the fourth adjusting hydraulic cylinder (403) is fixedly connected with a frame of the machine (M), the fourth disengaging fork (418) is directly or indirectly connected with the frame of the machine (M), the fourth adjusting hydraulic cylinder (403) is directly or indirectly connected with the fourth disengaging fork (418), the fourth disengaging fork (418) can rotate in a certain angle range relative to the frame of the machine (M) under the direct or indirect action of the fourth adjusting hydraulic cylinder (403), and/or the fourth disengaging fork (418) is directly or indirectly connected with the fourth disengaging bearing (419), And the fourth release bearing (419) moves along the axial direction thereof under the action of the fourth release fork (418), and/or the fourth release bearing (419) is directly or indirectly connected with the damping Device (DM), and/or the damping Device (DM) is directly or indirectly selectively adjusted in the load size and the damping size under the action of the fourth release bearing (419), and/or the fourth release bearing (419) is connected with the fourth adjusting bracket (424), and/or the fourth adjusting bracket (424) is directly or indirectly connected with the damping Device (DM), and/or the damping Device (DM) is directly or indirectly selectively adjusted in the load size and the damping size under the action of the fourth adjusting bracket (424), and/or the fourth adjusting bracket (424) is in an initial state, The bearing capacity and the damping size of the buffer damping Device (DM) are in the maximum state, or the bearing capacity and the damping size of the buffer damping Device (DM) are in the minimum state when the fourth adjusting bracket (424) is in the initial state, or the bearing capacity and the damping size of the buffer damping Device (DM) are in the intermediate state when the fourth adjusting bracket (424) is in the initial state, and/or the fourth adjusting bracket (424) at least has the function of recovering the initial state under the action of the buffer damping Device (DM) when the acting force of the fourth release bearing (419) on the fourth adjusting bracket (424) is small, and/or the fourth adjusting hydraulic cylinder (403) is connected with the buffer damping Device (DM) through the fourth release fork (418), the fourth release bearing (419) and/or the fourth adjusting bracket (424) in sequence, and the buffer damping Device (DM) is selectively adjusted in the load bearing capacity and damping magnitude under the indirect control of the fourth adjusting hydraulic cylinder (403), so that the buffer damping Device (DM) has different damping and buffering characteristics, and/or the fourth adjusting bracket (424) is at least provided with the function of compensating the axial thickness reduction of the second friction plate (212) and the second pair of coupling plates (213) of the buffer damping Device (DM) due to abrasion to a certain extent; and/or

Said adjusting means (RM) comprise at least: a fourth adjusting bolt (425) and a fourth adjusting bracket (424), wherein the fourth adjusting bolt (425) at least comprises a bolt, the fourth adjusting bracket (424) is connected with the buffering damping Device (DM) through the fourth adjusting bolt (425), and/or the fourth adjusting bolt (425) at least has the function of manually adjusting the bearing capacity and the damping size of the buffering damping Device (DM), and/or the fourth adjusting bracket (424) directly or indirectly presses or releases the second pre-tightening spring (218) in the buffering damping Device (DM) under the action of the fourth adjusting bolt (425), so that the bearing capacity and the damping size of the buffering damping Device (DM) are set by the fourth adjusting bolt (425), and/or the fourth adjusting bracket (424) at least has the function of compensating the second friction plate (212) and the first friction plate (424) of the buffering damping Device (DM) to a certain extent The reduction in axial thickness of the two pairs of doublets (213) due to wear.

12. The shifting apparatus with a cushion damping function (GD) of claim 1, characterized in that:

the gear shifting device (GD) with the buffer damping function is formed by the buffer damping Device (DM) alone; and/or

The shifting device (GD) with a damping function is formed by the clutch device (CM) alone; and/or

The shifting device (GD) with a damping function is formed by the adjusting device (RM) alone; and/or

The shifting device with a cushion damping function (GD) is constituted solely by the actuating device (AM); and/or

The gear shifting device (GD) with a cushion and damping function is composed of the clutch device (CM) and the cushion and damping Device (DM), and the clutch device (CM) is directly or indirectly connected with the cushion and damping Device (DM); and/or

The shifting device (GD) with a damping function is formed by the damping Device (DM) and the adjusting device (RM), and the damping Device (DM) is directly or indirectly connected to the adjusting device (RM); and/or

The shifting device (GD) with a damping function is formed by the clutch device (CM) and the actuating device (AM), and the clutch device (CM) is directly or indirectly connected with the actuating device (AM); and/or

The shifting device (GD) with a cushion-damping function is formed by the cushion-damping Device (DM), the clutch device (CM) and the adjusting device (RM), and the clutch device (CM) is directly or indirectly connected with the cushion-damping Device (DM) which is directly or indirectly connected with the adjusting device (RM); and/or

The shifting device (GD) with a cushion and damping function is composed of the clutch device (CM), the cushion and damping Device (DM) and the actuating device (AM), and the clutch device (CM) is directly or indirectly connected with the cushion and damping Device (DM) and the clutch device (CM) is directly or indirectly connected with the actuating device (AM); and/or

The shifting device (GD) with a cushion-damping function is formed by the clutch device (CM), the cushion-damping Device (DM), the actuating device (AM) and the adjusting device (RM), and the clutch device (CM) is directly or indirectly connected with the cushion-damping Device (DM), the cushion-damping Device (DM) is directly or indirectly connected with the adjusting device (RM), and the clutch device (CM) is directly or indirectly connected with the actuating device (AM); and/or

The driving part of the machine (M) is directly or indirectly connected with the gear shifting device (GD) with the buffer damping function and the driven part of the machine (M); and/or

The driven part of the machine (M) is directly or indirectly connected with the gear shifting device (GD) with the buffer damping function and a frame of the machine (M); and/or

The active part of the machine (M) is connected with the passive part of the machine (M) directly or indirectly through the damping Device (DM) which rotates with the passive part of the machine (M); and/or

The driven part of the machine (M) is directly or indirectly connected with the frame of the machine (M) through the buffer damping Device (DM); and/or

The passive part of the machine (M) is connected with the flexible part of the machine (M) directly or indirectly through the buffer damping Device (DM); and/or

The adjusting device (RM) is directly or indirectly connected with a frame of the machine (M); and/or

The actuation device (AM) is connected directly or indirectly to the frame of the machine (M); and/or

Said Damper Means (DM) being arranged coaxially or non-coaxially with said Clutch Means (CM); and/or

Said Damping Means (DM) being arranged coaxially with said adjusting means (RM); and/or

Said Actuating Means (AM) being arranged coaxially or non-coaxially with said Clutch Means (CM); and/or

The damping Device (DM) is arranged coaxially or non-coaxially with the active part of the machine (M); and/or

The damping Device (DM) is arranged coaxially or non-coaxially with the driven part of the machine (M); and/or

The clutch device (CM) is arranged coaxially or non-coaxially with the driven member of the machine (M); and/or

Said Clutch Means (CM) being arranged coaxially or non-coaxially with a flexible member of said machine (M); and/or

In an axial direction, the damping Device (DM) is located between the active part of the machine (M) and the passive part of the machine (M); and/or

The Actuating Means (AM) is arranged axially on one side of the Damping Means (DM); and/or

-said Actuating Means (AM) are arranged radially on one side of said Damping Means (DM); and/or

The adjusting device (RM) is arranged axially on one side of the damping Device (DM); and/or

The adjusting device (RM) is arranged radially on one side of the damping Device (DM).

13. A concentrated clutch device (GCD) for transmission field applying a gear shift device (GD) with a damping function according to any one of claims 1 to 12 to realize a concentrated clutch function, characterized in that:

the central clutch device (GCD) is configured to have at least a plurality of clutch or brake functions; and/or

The concentrated clutch device (GCD) is configured to have at least a function of connecting two or more moving members; and/or

Said collective clutch device (GCD) being configured to connect at least one active component of said machine (M) and said collective clutch device (GCD) being configured to connect at least two passive components of said machine (M); and/or

Said central clutch device (GCD) being configured to have at least the function of selectively braking the moving parts of two or more of said machines (M); and/or

The concentrated clutch device (GCD) is configured to have at least the function of selectively transmitting the power or motion of at least one active component of the machine (M) to a plurality of passive components of the machine (M); and/or

The concentrated clutch device (GCD) is configured to have at least a function of selectively transmitting the power or motion of one moving member connected thereto to another moving member connected thereto; and/or

The concentrated clutch device (GCD) is configured to have at least the function of transmitting the power or motion of one moving element connected with the GCD to another element connected with the GCD in a one-way mode selectively; and/or

The concentrated clutch device (GCD) is configured to have at least the function of selectively transmitting the power or movement of one moving part connected with the GCD to another part connected with the GCD directly or indirectly by using centrifugal force in a certain rotating speed range; and/or

The concentrated clutch device (GCD) is configured to have at least the function of selectively transmitting the power or motion of one moving element connected with the GCD to other connected moving elements respectively; and/or

The concentrated clutch device (GCD) is configured to have at least the function of selectively transmitting the power or the movement of two or more moving members connected with the GCD to the other moving member respectively; and/or

The concentrated clutch device (GCD) is configured to have at least the function of selectively transmitting the power of two or more moving parts connected with the GCD to other two or more moving parts connected with the GCD respectively; and/or

Said central clutch device (GCD) being configured at least to selectively maintain the rotational acceleration or deceleration of one or more moving parts connected thereto; and/or

Said central clutch device (GCD) being configured at least to selectively maintain one or more moving parts connected thereto in a rotationally fixed state; and/or

The concentrated clutch device (GCD) comprises at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1 to 12; and/or

At least one shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 is used as a component or assembly of the concentrated clutch device (GCD); and/or

The machine (M) is provided with at least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 for implementing a plurality of clutching or braking functions of the machine (M).

14. Parking Device (PD) for transmission applications applying a gear shift device (GD) with damping function according to any of claims 1-12 for parking function, characterized in that:

the Parking Device (PD) is configured to have at least a parking brake function; and/or

The Parking Device (PD) comprises at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1 to 12; and/or

The Parking Device (PD) adopts at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1-12 as a component or assembly thereof; and/or

At least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 is used in said machine (M) for achieving a parking brake function.

15. A Differential (DM) for a drive field applying a shifting device (GD) with a cushion damping function according to any one of claims 1 to 12 to realize a differential function, characterized in that:

the Differential (DM) is configured to have at least a differential function; and/or

The Differential (DM) comprises at least an inter-wheel differential and a central differential for a vehicle; and/or

-at least one gear shifting device (GD) with damping function according to any one of claims 1 to 12 is included in the Differential (DM); and/or

-at least one gear shifting device (GD) with damping function according to any one of claims 1 to 12 is used in the Differential (DM) as a component or assembly thereof; and/or

At least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 is used in said machine (M) for the purpose of carrying out a speed-changing and/or differential function.

16. A Brake System (BS) for transmission field applying a gear shift device (GD) with a damping function according to any one of claims 1 to 12 for braking function, characterized in that:

the Braking System (BS) is configured at least with a service braking function; and/or

The Brake System (BS) comprises at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1 to 12; and/or

The Brake System (BS) at least adopts one gear shifting device (GD) with a buffer damping function as one of claims 1 to 12 as a component or assembly thereof; and/or

At least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 is used in said machine (M) for achieving a braking function.

17. A safety device for transmission field applying a shift device (GD) with a damping function according to any one of claims 1 to 12 for safety protection function, characterized in that:

the safety device is at least provided with a certain function of limiting the size of the load transmitted by the safety device; and/or

The safety device is at least provided with a function of limiting the transmitted torque; and/or

The safety device is at least provided with a certain function of limiting the transmitted rotating speed; and/or

The safety device is at least provided with a certain function of limiting the transmitted power; and/or

The safety device is configured to have at least some function of limiting the movement transmitted by the safety device; and/or

The safety device comprises at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1 to 12; and/or

The safety device adopts at least one gear shifting device (GD) with a buffer damping function as one of claims 1 to 12 as a component or assembly thereof; and/or

The machine (M) adopts at least one gear shifting device (GD) with a buffer damping function as claimed in any one of claims 1 to 12 for achieving the function of safety protection of the machine (M).

18. A Transmission System (TS) for transmission applications applying a gear shift device (GD) with damping function according to any one of claims 1 to 12 for transmission functions, characterized in that:

-said Transmission System (TS) is configured at least with a speed-changing and/or differential function; and/or

The Transmission System (TS) is configured to at least have an execution device for transmitting power of a power source of the machine (M) to the machine (M) after speed change or differential transmission; and/or

-said Transmission System (TS) comprises at least one shifting device (GD) with damping function according to any one of claims 1 to 12; and/or

-at least one gear shifting device (GD) with damping function according to any one of claims 1 to 12 is used in the Transmission System (TS) as a component or assembly thereof; and/or

At least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12 is used in the machine (M) for the purpose of transmitting power or motion.

19. A module (NMO) for transmission applications, applying a Gearshift Device (GD) with damping function according to any of claims 1 to 12 for transmission functions, characterized in that:

Said module (NMO) has at least a clutching function for the transmission of its power or motion; and/or

Said module (NMO) having at least a braking function for the transmission of its power or motion; and/or

Said module (NMO) having at least the function of limiting the torque, speed or movement it transmits; and/or

Said module (NMO) having at least a damping function for the transmission of its power or motion; and/or

-at least one Gearshift Device (GD) with damping function according to any of claims 1 to 12 is included in the module (NMO); and/or

-in said module (NMO) at least one shifting device (GD) with damping function according to any of claims 1 to 12 is used as a component or assembly thereof; and/or

-at least one Gearshift Device (GD) with damping function according to any of claims 1 to 12 is used in the module (NMO) for transmitting motion and power.

20. A machine for implementing a power or power conversion function using a shift device (GD) with a cushion damping function as set forth in any one of claims 1 to 12, characterized in that:

the machine is configured to perform at least a conversion function to achieve different power or different energy; and/or

The machine comprises at least one gear shifting device (GD) with a damping function as claimed in any one of claims 1 to 12; and/or

The machine at least adopts a gear shifting device (GD) with a buffer damping function as a part or a component of the machine, wherein the gear shifting device (GD) is as defined in any one of claims 1-12; and/or

The machine is characterized in that at least one gear shifting device (GD) with the buffer damping function according to any one of claims 1-12 is adopted to realize the conversion function of different powers or different energies of the machine.