CN116357686A

CN116357686A - Dual clutch structure and transmission using same

Info

Publication number: CN116357686A
Application number: CN202310233541.8A
Authority: CN
Inventors: 刘建平
Original assignee: Fujian Zhongqing Transmission Technology Co ltd
Current assignee: Fujian Zhongqing Transmission Technology Co ltd
Priority date: 2023-03-13
Filing date: 2023-03-13
Publication date: 2023-06-30

Abstract

The invention relates to a double clutch structure and a transmission using the double clutch structure, wherein the double clutch structure comprises a normally closed clutch, a normally open clutch and a gear transmission mechanism, the normally closed clutch and the normally open clutch are interlocked through one or more interlocking pieces, and the interlocking pieces are part of the normally closed clutch or part of the normally open clutch or are independently arranged from the normally closed clutch or the normally open clutch; when the linkage piece is a normally closed clutch drum or a supporting plate of the normally closed clutch, the normally closed clutch drum or the supporting plate of the normally closed clutch is in spline sliding connection with a normally open clutch hub through a spline; this double clutch structure and use derailleur reasonable in design of this double clutch structure, double clutch can process respectively, install respectively, is favorable to improving manufacturing efficiency, and separation and the combination of two clutches of an actuator control practice thrift the cost simultaneously.

Description

Dual clutch structure and transmission using same

Technical Field

The invention relates to the field of transmissions, in particular to the field of transmissions of double clutches.

Background

In the traditional transmission field, one clutch corresponds to one actuator, and the separation and combination actions of two clutches are controlled respectively, so that the two actuators are large in size, high in cost, high in energy consumption and complex in structure, in order to ensure that the gear shifting process of the transmission is smooth, rapid and power-free, the control difficulty is high, friction plates are seriously worn and even burnt due to the fact that the two clutches are combined simultaneously easily due to the influence of factors, along with the development of a new energy automobile, the technology of controlling the two clutches by one actuation is developed, one actuator is reduced by one control technology, and the problem of the gear shifting process is effectively solved, but the existing one control technology and two technologies have the problems of complex structure, high manufacturing difficulty and insufficient exertion of volume optimization, and the axial acting force of a gear shifting mechanism acts on a transmission mechanism, so that extra axial resistance is caused for the transmission mechanism and energy loss is increased.

Disclosure of Invention

The invention aims to provide a double clutch structure and a transmission using the double clutch structure, the double clutch structure and the transmission using the double clutch structure are reasonable in design, double clutches can be respectively processed and respectively installed, the manufacturing efficiency is improved, and meanwhile, one actuator controls the separation and combination of two clutches, so that the cost is saved.

The double clutch structure of the invention is characterized in that: the clutch mechanism comprises a normally-closed clutch, a normally-open clutch and a gear transmission mechanism, wherein the normally-closed clutch and the normally-open clutch are interlocked through one or more linkage pieces, and the linkage pieces are part of the normally-closed clutch or part of the normally-open clutch or are independently arranged from the normally-closed clutch or the normally-open clutch;

when the linkage piece is a normally closed clutch drum or a supporting plate of the normally closed clutch, the normally closed clutch drum or the supporting plate of the normally closed clutch is in spline sliding connection with a normally open clutch hub through a spline;

when the linkage piece is independently arranged, the linkage piece is in axial sliding connection and rotary direction transmission connection with the normally closed clutch and the normally open clutch;

the linkage mode of the double clutch is that one actuator controls the separation and combination of two clutches, and when the normally closed clutch is separated, the normally open clutch is combined; in contrast, the normally closed clutch is engaged and the normally open clutch is disengaged, and the pressure of the normally closed clutch is reduced by a value equal to the pressure of the normally open clutch during the disengagement of the normally closed clutch, and the pressure of the normally closed clutch is increased by a value equal to the pressure of the normally open clutch during the engagement of the normally closed clutch.

Further, the normally closed clutch comprises a normally closed clutch drum and a normally closed clutch hub, a pressure plate is arranged between the normally closed clutch drum and the normally closed clutch hub, the pressure plate is in axial sliding connection with the normally closed clutch drum and in transmission connection with the rotation direction, a plurality of first elastic bodies are arranged between the left side of the normally closed clutch drum and the pressure plate, the first elastic bodies are compression springs, the compression springs are uniformly distributed along the circumference, two ends of the compression springs are respectively abutted to the normally closed clutch drum and the pressure plate, a first friction pair is arranged on the right side of the pressure plate, the first friction pair comprises a plurality of first outer plates and a first inner plate, the first outer plates and the first inner plates are arranged in a staggered manner, the outer periphery of the first outer plates is in sliding connection with the normally closed clutch drum through a spline, the inner periphery of the first inner plates is in sliding connection with the normally closed clutch hub through a spline, a supporting plate is arranged on the right side of the first friction pair, a clamping spring is arranged on the right side of the supporting plate, and the right side of the normally closed clutch drum is limited by the clamping spring to move to the maximum right position; the right side of the normally closed clutch is provided with a normally open clutch, the normally open clutch comprises a normally open clutch drum and a normally open clutch hub, a second friction pair is arranged between the normally open clutch drum and the normally open clutch hub, the second friction pair comprises a second outer plate and a second inner plate, the second outer plate and the second inner plate are arranged in a staggered mode, the periphery of the second outer plate is in sliding connection with the normally open clutch drum through a spline, and the periphery of the second inner plate is in sliding connection with the normally open clutch hub through a spline.

Further, when the linkage member is independently arranged, the inner periphery on the right side of the linkage member is in sliding connection with the normally open clutch hub through a spline, the inner periphery on the left side of the linkage member is provided with a plurality of axial spline-shaped long convex parts, correspondingly, the right side of the normally closed clutch drum is provided with a plurality of axially inwards concave groove parts corresponding to the spline-shaped long convex parts, and the spline-shaped long convex parts penetrate into the axially inwards concave groove parts, so that the linkage member is in transmission connection with the normally closed clutch in the axial sliding and rotating directions; correspondingly, the periphery of the pressure plate is radially provided with a plurality of radial tooth-shaped convex parts corresponding to the groove parts of the normally closed clutch drum, the radial tooth-shaped convex parts penetrate through the groove parts of the normally closed clutch drum, which are axially concave, so that the connection of axial sliding and rotation direction transmission is formed, and the right side of the radial tooth-shaped convex parts of the pressure plate is abutted with the left side of the spline-shaped long convex parts of the linkage piece.

Further, the normally closed clutch drum is not provided with a groove part which is concave in the axial direction, correspondingly, the normally closed clutch drum is provided with a plurality of hole parts at the corresponding position of the periphery of the pressure plate, the periphery of the pressure plate is provided with a force application block through the hole parts, the force application block is fixedly connected with the pressure plate in a welding or bolt connection mode, correspondingly, the left side of the linkage piece is provided with a plurality of axial long tooth-shaped convex parts, no axial spline-shaped long convex parts are arranged, and the long tooth-shaped convex parts of the linkage piece pass through the middle of the adjacent force application blocks, so that the linkage piece is in transmission connection with the pressure plate in the axial sliding and rotating directions.

Further, the outer side or the periphery of the pressure plate is provided with a circular ring fixedly connected with the force application block, the circular ring increases the strength of the pressure plate and force application block combination body, and the deformation of the inner periphery of the pressure plate is reduced.

Further, the linkage piece is a part of the normally closed clutch, the linkage piece is a supporting piece, the supporting piece is in sliding connection with the normally open clutch hub through an inner peripheral spline, and accordingly, the compression spring is arranged on the right side of the first friction pair, and two ends of the compression spring are respectively abutted against the pressure plate and the supporting piece; the linkage piece is a part of a normally closed clutch, the linkage piece is a normally closed clutch drum, the normally closed clutch drum is in sliding connection with a normally open clutch hub through a right inner peripheral spline, correspondingly, the compression spring is arranged on the right side of the first friction pair, and the supporting plate is arranged on the left side of the normally closed clutch drum; when the linkage piece is a part of the normally closed clutch, no matter the supporting plate is the linkage piece or the normally closed clutch drum is the linkage piece, the switching pushing disc is correspondingly arranged on the left side of the normally closed clutch drum, the right side of the switching pushing disc is provided with a long tooth-shaped convex part, and the long tooth-shaped convex part of the switching pushing disc is mutually nested with the Zhou Chixing part outside the pressure disc, so that the switching pushing disc can synchronously rotate with the pressure disc, and axial pressure is applied to the normally open clutch through the right side of the normally closed clutch drum.

Further, a plurality of second elastic bodies are uniformly distributed between the right side of the first second outer sheet at the left side of the second friction pair and the shell, two ends of each second elastic body are respectively abutted against the first second outer sheet at the left side and the shell, when the piston is in the leftmost state, the second elastic bodies are in a free state between the first second outer sheet and the shell, namely, a certain gap is formed between the friction sheet at the left side of the normally closed clutch drum and the pushing disc, or a certain gap is formed between the linkage piece and the first second inner sheet at the left side; the normally closed clutch and the normally open clutch can be a multi-plate wet clutch, a dry clutch or a compound clutch.

The transmission of the double clutch structure is characterized in that: the transmission body is internally and sequentially provided with an actuator, a piston, a push disc, a friction plate and a baffle plate from left to right, the push disc is arranged on the right side of the piston and is opposite to the friction plate, the push disc is in sliding connection with the baffle plate through an inner peripheral spline, the baffle plate is fixedly connected with a normally open clutch drum, a return spring is arranged between the baffle plate and the piston, a normally closed clutch is arranged on the right side of the friction plate in the normally open clutch drum, when a linkage piece is independently arranged, the friction plate is fixed on the left side surface of the normally closed clutch drum, and when the normally closed clutch or a part of the normally open clutch is used as the linkage piece, the friction plate is fixed on the left side surface of the switching push disc; when the linkage piece is independently arranged, the linkage piece is arranged between the normally-closed clutch and the normally-open clutch friction pair, and the friction plate and the normally-closed clutch drum or the switching disc are fixedly connected due to the sliding connection of the dual plate (pushing disc) of the friction plate and the normally-open clutch drum, and the normally-closed clutch drum or the switching disc is in sliding connection with the normally-open clutch hub through the linkage piece, so that the friction plate and the dual plate (pushing disc) thereof can be respectively regarded as a part of the second friction pair.

Further, the planetary gear structure comprises a sun gear, a gear ring and a planet carrier assembly when the gear transmission mechanism is of a planetary gear structure, the planet carrier assembly comprises a planet carrier, planet gears, planet axles and bearings in the middle of the planet gears and the planet axles, the gear ring is arranged on the periphery of the sun gear, a plurality of planet gears are uniformly distributed between the sun gear and the gear ring and are connected with the sun gear and the gear ring in a gear meshing mode, the planet gears are rotatably connected with the planet axles through the bearings, two ends of the planet axles are fixedly connected with the planet carrier, so that a planet row is formed, the sun gear and a normally closed clutch hub are fixedly connected with the input shaft or are connected with a spline respectively, the gear ring is fixedly connected with a normally open clutch hub or is made into a whole, and the normally open clutch drum is fixedly connected with a shell or is made into a whole.

Further, when the gear transmission mechanism is a fixed shaft gear mechanism, two driving shafts are arranged, a first driving shaft and a second driving shaft are fixedly connected with a normally open clutch hub or are in spline connection or are integrally formed, the second driving shaft is fixedly connected with a normally closed clutch hub or are in spline connection or are integrally formed, the first driving shaft is provided with a first driving gear, a first driven shaft is correspondingly arranged, the first driven shaft is provided with a first driven gear and an intermediate gear, the first driven gear and the intermediate gear are fixedly connected with the first driven shaft, the corresponding output shaft is provided with an output gear, the output gear is fixedly connected with the output shaft, the first driving gear is meshed with the first driven gear according to the conventional technology, and the intermediate gear is meshed with the output gear on the output shaft according to the conventional technology, so that the two-gear transmission with the direct gear of the speed ratio 1 is formed.

The invention has the beneficial effects that:

1. the two clutches can be respectively processed and installed, so that the quality control is convenient, and the manufacturing efficiency is improved;

2. the linkage piece and the normally closed clutch drum are arranged in a nested manner, so that the material use is reduced, and the space is optimized;

3. one actuator controls two clutches to save cost, save energy, reduce cost and reduce volume;

4. the actuator can control two clutches simultaneously only by providing axial acting force of one clutch, so that the cost and energy are further saved;

5. the clutch is easy to control, quick and smooth gear shifting is easy to realize, the gear shifting process is not interrupted by power, and the clutch is prevented from being separated simultaneously and has foolproof effect;

description of the drawings:

FIG. 1 is a schematic cross-sectional configuration of an embodiment of a transmission of the present invention;

FIG. 2 is a partial view of FIG. 1;

FIG. 3 is a schematic cross-sectional configuration of the normally closed clutch drum, pressure plate and linkage of FIG. 1;

FIG. 4 is a perspective view of one embodiment of the normally closed clutch drum of FIG. 1;

FIG. 5 is a perspective view of one embodiment of the linkage of FIG. 1;

FIG. 6 is a perspective view of one embodiment of the platen of FIG. 1;

FIGS. 7 and 8 are perspective views of another embodiment of a platen;

FIG. 9 is a schematic cross-sectional configuration of a normally closed clutch with a linkage disposed on a normally closed clutch support plate;

FIG. 10 is a schematic perspective view of the transfer push plate of FIG. 9;

FIG. 11 is a schematic cross-sectional configuration of a fixed shaft two speed transmission with speed ratio 1;

FIG. 12 is a schematic cross-sectional configuration of a multi-speed dual clutch fixed shaft transmission;

FIG. 13 is a schematic perspective view of a normally closed clutch drum without an inner groove portion;

FIG. 14 is a schematic perspective view of a linkage without axial spline shaped elongated protrusions;

FIG. 15 is a schematic perspective view of an embodiment of a normally open clutch drum;

FIG. 16 is a schematic view of a perspective configuration of one embodiment of a support sheet;

fig. 17 is a schematic perspective view of an embodiment of a pusher tray.

The specific embodiment is as follows:

the double clutch structure comprises a normally closed clutch A, a normally open clutch B and a gear transmission mechanism, wherein the two clutches A and B realize linkage interlocking through one or more linkage pieces C, and the linkage pieces are part of the normally closed clutch or part of the normally open clutch or are independently arranged from the normally closed clutch or the normally open clutch.

Optionally, the linkage member is a normally closed clutch drum or a normally closed clutch support plate, and the normally closed clutch drum or the normally closed clutch support plate is in spline sliding connection with the normally open clutch hub through a spline; for convenient processing and installation, the linkage piece is preferably arranged independently, when the linkage piece is arranged independently, the linkage piece is connected with the normally closed clutch and the normally open clutch in an axial sliding connection and a rotation direction transmission connection,

The linkage mode of the double clutch is that one actuator controls the separation and combination of two clutches, and when the normally closed clutch is separated, the normally open clutch is combined; in contrast, the normally closed clutch is combined and the normally open clutch is separated from time to time, the pressure of the normally closed clutch is reduced to be equal to that of the normally open clutch in the process of separating the normally closed clutch, and the pressure of the normally closed clutch is increased to be equal to that of the normally open clutch in the process of combining the normally closed clutch; the gear transmission mechanism is a planetary gear mechanism, and can also be a fixed shaft gear mechanism.

Both the normally closed clutch and the normally open clutch may be one of a multiplate wet clutch, a dry clutch, a compound clutch such as that of patent application No. 2022228036368 (a compound clutch), or other forms of clutches such as that of prior patent 202210932073.9 (a brake arrangement, transmission, vehicle, and method of operation), preferably both the normally closed clutch and the normally open clutch are multiplate wet clutches.

Specifically, as shown in fig. 1 and 2, the normally closed clutch a comprises a normally closed clutch drum A1 and a normally closed clutch hub A2, a pressure plate 1 is arranged between the normally closed clutch drum A1 and the normally closed clutch hub A2, the pressure plate 1 is in axial sliding connection with the normally closed clutch drum A1, a plurality of first elastic bodies 2 are arranged between the normally closed clutch drum A1 and the pressure plate 1, the first elastic bodies 2 can be one or a plurality of compression springs, belleville springs, diaphragm springs, wave springs or other elastic materials, preferably the compression springs are uniformly distributed or symmetrically distributed along the circumference, two ends of the compression springs are respectively abutted against the normally closed clutch drum A1 and the pressure plate 1, a first friction pair 3 is arranged on the right side of the pressure plate, the first friction pair comprises a plurality of first outer plates 4 and a first inner plate 5, the first outer plates 4 and the first inner plates 5 are arranged in a staggered manner, the outer periphery of the first outer plates 4 is in sliding connection with the normally closed clutch drum A1 through splines, the inner periphery of the first inner plates 5 is in sliding connection with the normally closed clutch hub A2 through the splines, a support plate 6 is arranged on the right side of the first friction pair 3, and the support plate 6 is in sliding connection with the right side of the normally closed clutch drum 7 through the support plate 6, and the right side of the support plate 7 is limited by the right side of the support plate is arranged on the right side of the support plate 7; the right side of the normally closed clutch is provided with a normally open clutch B, the normally open clutch B comprises a normally open clutch drum B1 and a normally open clutch hub B2, a second friction pair 8 is arranged between the normally open clutch drum and the normally open clutch hub, the second friction pair comprises a second outer sheet 9 and a second inner sheet 10, the second outer sheet and the second inner sheet are arranged in a staggered mode, the outer periphery of the second outer sheet 9 is in sliding connection with the normally open clutch drum B1 through a spline, and the inner periphery of the second inner sheet 10 is in sliding connection with the normally open clutch hub B2 through a spline.

When the linkage member C is independently arranged (as shown in fig. 4 and 5), the inner periphery of the right side of the linkage member C is in sliding connection with the normally open clutch hub B2 through a spline C1, a plurality of axial spline-shaped long protruding parts C2 are arranged on the inner periphery of the left side of the linkage member, correspondingly, a plurality of axially inwards concave groove parts A3 corresponding to the spline-shaped long protruding parts C2 are arranged on the right side of the normally closed clutch drum A1, and the spline-shaped long protruding parts C2 penetrate into the axially inwards concave groove parts A3, so that the linkage member and the normally closed clutch are in transmission connection in the axial sliding and rotating directions; a spline groove A4 which is in spline fit with the first outer plate is arranged on the normally closed clutch drum A1; correspondingly, the periphery of the pressure plate 1 is radially provided with a plurality of radial tooth-shaped convex parts 101 corresponding to the groove parts of the normally closed clutch drum, the radial tooth-shaped convex parts 101 penetrate through the groove parts A3 of the normally closed clutch drum, which are axially concave, so as to form axial sliding and rotation direction transmission connection, and the right side of the radial tooth-shaped convex parts of the pressure plate is abutted with the left side of the spline-shaped long convex parts of the linkage piece; the linkage piece is provided with the spline-shaped long convex part or the long tooth-shaped convex part, so that the contact area between the linkage piece and the pressure plate is increased, the force arm of the pressure plate at the periphery of the pressure plate is shortened, and the deformation of the inner periphery of the pressure plate is reduced.

Optionally, in order to ensure the strength of the clutch drum, the normally closed clutch drum A1 is not provided with a groove portion A3 recessed in the axial direction, correspondingly, the normally closed clutch drum is provided with a plurality of hole portions 104 (shown in fig. 13) at corresponding positions of the outer periphery of the pressure plate, a force application block 102 (shown in fig. 7) is arranged at the outer periphery of the pressure plate through the hole portions, the force application block is fixedly connected with the pressure plate in a welding or bolting way, correspondingly, the left side of the linkage member is provided with a plurality of axial long tooth-shaped protruding portions, no axial spline-shaped long protruding portions (shown in fig. 14) are arranged, and the long protruding portions of the linkage member penetrate through the middle of the adjacent force application blocks, so that axial sliding and rotating direction transmission connection is formed between the long protruding portions of the linkage member and the pressure plate.

Alternatively, outside the clutch drum, the force application block 102 is fixedly connected by a circular ring 103 (as shown in fig. 8) so as to increase the strength of the combination of the pressure plate and the force application block and reduce the deformation amount of the inner periphery of the pressure plate.

Alternatively, the linkage member is not separately arranged, the linkage member C is a part of a normally closed clutch, the linkage member is a supporting plate C3 (shown in fig. 9), the supporting plate is in sliding connection with the normally open clutch hub B2 through an inner peripheral spline, and accordingly, the compression spring 11 is arranged on the right side of the first friction pair 3, and two ends of the compression spring are respectively abutted against the pressure plate 1 and the supporting plate C3; the linkage part is a part of a normally-closed clutch and is a normally-closed clutch drum, the normally-closed clutch drum is in sliding connection with a normally-open clutch hub through a right inner peripheral spline (a supporting plate can be fixedly connected with the normally-closed clutch drum, when a supporting plate C3 is fixedly connected with a normally-closed clutch drum B2 and the supporting plate serves as the linkage part and is equivalent to the clutch drum serving as the linkage part, the combination of the two is shown in fig. 15 and 16, namely, as shown in fig. 9), correspondingly, a compression spring is arranged on the right side of a first friction pair, and the supporting plate is arranged on the left side of the normally-closed clutch drum instead; when the linkage piece is a part of the normally closed clutch, no matter the supporting plate is the linkage piece or the normally closed clutch drum is the linkage piece, the switching pushing disc 12 (shown in fig. 10) is correspondingly arranged on the left side of the normally closed clutch drum, the long tooth-shaped convex part 13 is arranged on the right side of the switching pushing disc, the long tooth-shaped convex part 13 of the switching pushing disc is mutually nested with the tooth-shaped part on the periphery of the pressure disc 1, so that the switching pushing disc can synchronously rotate with the pressure disc, and axial pressure is applied to the normally open clutch through the right side of the normally closed clutch drum.

Optionally, in order to generate enough clearance between the second inner sheet 9 and the second outer sheet 10 more quickly after the pressure of the normally open clutch is removed, a plurality of second elastic bodies 14 are uniformly distributed between the right side of the first second outer sheet on the left side of the second friction pair 8 and the shell, two ends of each second elastic body are respectively abutted against the first second outer sheet on the left side and the shell, preferably, when the piston is in the leftmost state, the second elastic bodies have a free state between the first second outer sheet and the shell, namely, a certain clearance is formed between the friction sheet on the left side of the normally closed clutch drum and the pushing disc, or a certain clearance is formed between the linkage piece and the first second inner sheet on the left side.

The transmission body is internally and sequentially provided with an actuator 15, a push disc 16, a friction plate 17 and a baffle 18 from left to right, most of the actuators are suitable for the application, such as a hydraulic piston structure, a pneumatic piston structure, an electromagnetic structure, a motor driving screw rod structure and the like, preferably the pneumatic piston structure, a piston cylinder 19 is fixedly connected with a normally-open clutch drum B1 or integrally formed, the push disc 16 is arranged on the right side of a piston 21 and is opposite to the friction plate 17, a push disc massage friction plate pair plate requires processing, the push disc is in sliding connection with the baffle through an inner peripheral spline, the baffle 18 is fixedly connected with the normally-open clutch drum B1, a return spring 20 (shown in figures 1 and 2) is arranged between the baffle 18 and the piston, the normally-closed clutch is arranged on the right side of the friction plate in the normally-open clutch drum, when a linkage piece is singly arranged, the friction plate is fixed on the left side of the normally-closed clutch drum, and the friction plate is fixed on the left side of the switching push disc when part of the normally-closed clutch is used as a linkage piece; when the linkage piece is independently arranged, the linkage piece is arranged between the normally closed clutch and the normally open clutch friction pair, and because the dual piece (push disc) of the friction piece is in sliding connection with the normally open clutch drum, the friction piece is fixedly connected with the normally closed clutch drum or the switching disc, the normally closed clutch drum or the switching disc is in sliding connection with the normally open clutch hub through the linkage piece, therefore, the friction piece and the dual piece (push disc) thereof can be respectively regarded as a part of the second friction pair (the friction piece is a flat piece, the friction piece and the dual piece (push disc) thereof are arranged so as to avoid the friction between the piston and the normally closed clutch drum, see fig. 17, the friction piece, the dual piece, the inner piece and the outer piece are in a concept (the friction piece can be regarded as one of the second inner piece, the dual piece (push disc) can be regarded as one of the second outer piece), and the friction piece (the inner piece) and the dual piece (the outer piece) are connected with which part in a conventional technology, different terms are adopted so as to conveniently explain the positions, and the combined state section is omitted, and if the friction piece, the normally closed clutch drum and the normally closed clutch drum are damaged or the normally closed clutch drum and the pressure release friction drum are damaged.

As shown in fig. 1, the present application further includes an input shaft 21 and an output shaft 22, when the gear transmission mechanism is a planetary gear structure, the planetary gear structure includes a sun gear 23, a gear ring 24 and a planet carrier assembly, the planet carrier assembly includes a planet carrier 25, a planet gear 26, a planet wheel shaft 27 and a bearing 28 in the middle of the planet gear and the planet wheel shaft, the gear ring 24 is disposed at the periphery of the sun gear 23, a plurality of planet gears 26 are uniformly distributed between the sun gear 23 and the gear ring 24, the plurality of planet gears 26 are connected with the sun gear 23 and the gear ring 24 in a gear meshing manner, the planet gears 26 are rotationally connected with the planet wheel shaft 27 through the bearing, both ends of the planet wheel shaft 27 are fixedly connected with the planet carrier 25, thereby forming a planetary gear row, the sun gear 23 and the normally closed clutch hub A2 are fixedly connected with the input shaft or are respectively connected with a spline, the gear ring gear 24 is fixedly connected with the normally open clutch hub B2 or is made into a whole, preferably, the normally open clutch hub is made into a whole, the normally open clutch hub A1 is fixedly connected with a housing 29 or is made into a whole, preferably, the housing is made into a normally open clutch hub, and the output shaft is fixedly connected with the planet carrier or is in sliding connection.

When the gear transmission mechanism is a fixed shaft gear mechanism (as shown in fig. 11), two driving shafts are provided, a first driving shaft 30 and a second driving shaft 31, the first driving shaft 30 is fixedly connected or splined or integrally formed with a normally open clutch drum B2, the second driving shaft 31 is fixedly connected or splined or integrally formed with a normally closed clutch hub A2, preferably, the second driving shaft 31 is fixedly connected with an output shaft 32, the first driving shaft 30 is provided with a first driving gear 33, a first driven shaft 34 is correspondingly provided, the first driven shaft is provided with a first driven gear 35 and an intermediate gear 36, the first driven gear 35 and the intermediate gear 36 are respectively fixedly connected with the first driven shaft 34, the output shaft is correspondingly provided with an output gear 37, the output gear 37 is fixedly connected with the output shaft 32, the first driving gear 33 is meshed with the first driven gear 36 through gears, and the intermediate gear 36 is meshed with the output gear 37 through gears, so that a two-gear transmission with a direct gear of the speed ratio 1 is formed.

Alternatively, the gear and shift mechanisms may be provided in a conventional dual clutch fixed shaft transmission technique to form a two or more gear dual clutch fixed shaft transmission (as shown in fig. 12).

Principle of operation

Planetary gear transmission (as shown in fig. 1 and 2)

The thrust of the piston is F (variable), the maximum is Fmax, the pressure of the compression spring is N1 in an initial state, the lowest combined pressure of the normally open clutch meeting the transmission requirement is N2, the friction force of each axial moving part and the resistance of the return spring are not counted, fmax is larger than N1, fmax is larger than or equal to N2, in order to better prevent the two clutches from being locked at the same time, preferably, N2 is larger than N1, and the larger N2-N1 is more beneficial to gear shifting smoothness and gear shifting speed improvement

1. The initial state is as follows: the actuator does not apply axial thrust to the push disc, the piston is in the leftmost position under the effect of the return spring, the normally open clutch is not subjected to axial pressure, the piston is in a separation state, the compression spring extrudes the first friction pair through the pressure plate on one hand, on the other hand, the compression spring extrudes the first friction pair through the clutch drum, the clamp spring and the supporting plate, the normally closed clutch is in a combination state under the effect of the compression spring, the sun gear is synchronous with the gear ring through the input shaft and the clutch hub by the normally closed clutch, so that the carrier is clamped to be synchronous, the transmission is in a direct gear state at the moment, namely in a second gear state, a second gear power transmission route is from the input shaft to the planetary gear, the carrier and the output shaft through the normally closed clutch, the gear ring and the sun gear respectively, and the vehicle can still be blocked and claudied directly if a power source of the actuator fails at the moment.

2. In the case where neither the input shaft nor the output shaft is rotating: the actuator applies axial force to the push disc, and pushes the friction plate, the normally closed clutch and the linkage piece through the push disc, so as to push the second friction pair, and eliminate the gap between the second friction pair; the pressure of the actuator acting on the pushing disc is gradually increased, the pressure acting on the normally closed clutch drum through the friction plate is gradually increased, partial pressure is counteracted until all the pressure acting on the clutch drum through the compression springs, the pressure N1-F born by the first friction pair is gradually reduced until the pressure is 0, namely F-N1=0, and correspondingly the pressure born by the second friction pair is F, namely the pressure born by the second friction pair is gradually increased; after that, as the linkage piece is limited by the second friction pair, the pressure plate is limited by the linkage piece, the pressure plate cannot continue to move right, the pressure acting on the normally closed clutch drum increases along with the increase, the normally closed clutch drum extrudes the compression spring to continue to move right, a gap is generated between the first friction pairs in the process, the normally closed clutch drum is gradually separated, and correspondingly, the pressure acting on the second friction pair through the compression spring, the pressure plate and the linkage piece continuously increases along with the increase of F; when the right side surface of the normally closed clutch drum is abutted against the right side of the linkage piece, the continuously increased thrust of the push disc acts on the second friction pair through the normally closed clutch drum and the linkage piece, namely, one part of acting force of the push disc acts on the linkage piece through the normally closed clutch drum, the compression spring and the pressure plate, and the other part directly acts on the linkage piece through the normally closed clutch drum and finally acts on the second friction pair until the designed maximum value Fmax is reached, at the moment, the second friction pair is completely combined, the gear ring is braked according to the motion rule of the planetary gear, at the moment, the speed ratio is the maximum, and the state is in a first gear state.

3. Reversing: at this time, if the input shaft is reversed, the sun gear is driven to be reversed, and according to the motion rule of the planetary gear, the planetary carrier is reversed and the output shaft is driven to be reversed under the condition that the gear ring is braked, so that the vehicle is reversed in a first gear ratio.

4. One gear advances: at the moment, if the input shaft rotates positively, the sun gear is driven to rotate positively, and under the condition that the gear ring is braked according to the motion rule of the planetary gear, the planet carrier also rotates positively, the output shaft is driven to rotate positively, and the vehicle advances at a first gear ratio; feeding in a first gear advancing process: when the transmission is applied to a new energy automobile, the running direction of the automobile keeps advancing when feeding is carried out in a first gear, the output shaft is pulled forwards and reversely, the output shaft still rotates forwards, the gear ring is braked, and the sun rotates forwards at the moment according to the motion rule of the planetary gear, and the sun rotates forwards at the same time relative to the output shaft, so that the power transmission route is transmitted to the driving motor from the wheels through the output shaft, the planet carrier assembly, the sun wheel and the input shaft to generate power;

5. upshift from first gear to second gear: gradually removing the axial thrust of the actuator under the condition of first gear advance, gradually reducing the pressure F of the pushing disc along with the clutch drum in the removing process, correspondingly gradually reducing the pressure F of the second friction pair from Fmax to 0 along with the pressure F of the pushing disc, and then gradually separating; correspondingly, the normally closed clutch drum gradually moves leftwards, the right side surface is separated from contact with the linkage piece, the supporting plate is driven by the clamp spring to press the first friction pair, so that the gap between the first friction pair is gradually reduced, the gap is eliminated, the friction pair is glidingly ground and combined, the normally closed clutch pressure in the process is gradually added to N1 from 0 according to the change rule of N1-F, the complete combination is realized, and then the piston moves to the leftmost position under the action of the return spring; in the second friction pair pressure reducing process, the input torque is controlled at a certain level so as to prevent the input torque from exceeding the binding force moment of the second clutch at the moment to cause the inversion of the gear ring, in the normal-closed clutch slip-grinding binding process, the normal-open clutch still has certain pressure, in order to prevent the two clutches from being simultaneously combined and generating a short-time locking phenomenon, gear shifting is blocked, certain input torque needs to be ensured, the two clutches can have simultaneous slip-grinding time, and the gear shifting smoothness is realized through half-linkage power exchange; the sliding friction of the normally closed clutch is eliminated from the gap between the second friction pairs until the binding force moment of the normally closed clutch is larger than the input torque, the sum of the reverse moment of the planet wheel received by the gear ring and the binding moment of the second friction pair is smaller than the binding moment of the normally closed clutch until the pressure received by the second friction pair is 0, namely the normally closed clutch is separated in the sliding friction process, the normally open clutch is combined in the sliding friction process, the normally closed clutch is combined, the sun wheel and the gear ring clamp the planet carrier assembly to be synchronous, and the transmission state is changed into a second gear state of a speed ratio 1.

When the second gear is fed, the vehicle keeps advancing in the running direction, the output shaft still rotates positively, the normally closed clutch keeps being combined, the sun gear and the gear ring still clamp the planet carrier assembly to be synchronous, the planet carrier reversely drags the sun gear to rotate positively, the same rotating speed as the output shaft is achieved, and the feeding power transmission route is opposite to the second gear driving transmission route;

6. downshifts from second gear to first gear: under the condition of second gear forward, the actuator applies pressure to the push disc and gradually increases, after that, the axial movement and axial stress change of each element of the normally closed clutch and the normally open clutch are the same as those of step 2, the pressure born by the normally open clutch is gradually increased along with F and gradually reduced along with F until F=N1, therefore, when N1> F >0, the friction pairs of the normally closed clutch and the normally open clutch are all subjected to certain pressure, in order to prevent the two clutches from being combined at the same time, a short-time locking phenomenon occurs, gear shifting is carried out, the input torque needs to be ensured to be within a certain range, the two clutches can have simultaneous sliding time and the gear ring cannot rotate reversely, and the smoothness of gear shifting is realized through half-linkage exchange power; the slipping of the normally-open clutch is started from the moment when the gap between the second friction pair is eliminated until the braking torque of the normally-open clutch is larger than the reverse moment received by the gear ring, and the slipping of the normally-closed clutch is started from the moment when the input torque is larger than the binding force torque of the normally-closed clutch to complete separation, namely the normally-closed clutch is separated in the slipping process, and the normally-open clutch is combined in the slipping process; the normally open clutch is combined, the gear ring is braked, the transmission is in a state of sun gear input, gear ring braking and planet carrier output, and the speed ratio is the highest at the moment according to the motion rule of the planet gears.

(II) fixed shaft two speed Transmission with direct speed (as shown in FIG. 11)

Let the number of teeth of the first driving gear be Z1, the number of teeth of the first driven gear be Z2, the number of teeth of the intermediate gear be Z3, the number of teeth of the output gear be Z4, the speed ratio i= (Z2/Z1) × (Z4/Z3) and i >1 of the transmission of the first driving gear to the output gear, namely the speed ratio i of the power transmitted from the first driving shaft.

1. The initial state is as follows: the actuator does not exert axial thrust to pushing disc, the piston is in leftmost position under return spring's effect, normally open clutch does not receive axial pressure, be in the separation state, compression spring extrudees first friction pair through the pressure disk on the one hand, on the other hand, through clutch drum, jump ring, the first friction pair of backing sheet extrusion, make normally closed clutch be in the combined state under compression spring effect, because second driving shaft is connected with normally closed clutch transmission, again because second driving shaft and output shaft fixed connection, first driving shaft is connected with normally open clutch transmission, so the derailleur is in the second state that the speed ratio is 1 at this moment, if the power supply of actuator loses efficacy this moment, the vehicle still can direct keep off the limp, the power transmission route: input shaft-normally open clutch hub-linkage-normally closed clutch-second drive shaft-output shaft.

2. In the case where neither the input shaft nor the output shaft is rotating: the actuator applies axial force to the push disc, and pushes the friction plate, the normally closed clutch and the linkage piece through the push disc, so as to push the second friction pair, and eliminate the gap between the second friction pair; the pressure of the actuator acting on the pushing disc is gradually increased, the pressure acting on the normally closed clutch drum through the friction plate is gradually increased, partial pressure is counteracted until all the pressure acting on the clutch drum through the compression springs, the pressure N1-F born by the first friction pair is gradually reduced until the pressure is 0, namely N1-F=0, and correspondingly the pressure born by the second friction pair is F, namely the pressure born by the second friction pair is gradually increased; after that, as the pressure plate is limited by the linkage part, the linkage part is limited by the second friction pair, the pressure plate cannot continue to move right, the pressure acting on the normally closed clutch drum increases along with the increase, the normally closed clutch drum extrudes the compression spring to continue to move right, a gap is generated between the first friction pairs in the process, the normally closed clutch drum is gradually separated, and correspondingly, the pressure acting on the second friction pair through the compression spring, the pressure plate and the linkage part continuously increases along with the increase of F; when the right side surface of the normally closed clutch drum is abutted against the right side of the linkage piece, the continuously increased thrust of the pushing disc acts on the second friction pair through the normally closed clutch drum and the linkage piece, namely, one part of acting force of the pushing disc acts on the linkage piece through the normally closed clutch drum, the compression spring and the pressure plate, the other part directly acts on the linkage piece through the normally closed clutch drum and finally acts on the second friction pair until reaching the designed maximum value Fmax, at the moment, the second friction pair is completely combined, namely, the normally open clutch is in a combined state, power is transmitted from the first driving shaft, at the moment, the first friction pair is in a first gear state with a speed ratio of i, and the power transmission route is as follows: input shaft-normally open clutch-first driving shaft-first driving gear-first driven gear-driven shaft-intermediate gear-output shaft.

3. Reversing: at this time, if the input shaft is reversed, the first shaft is driven to be reversed by the normally open clutch, and correspondingly, the output shaft is reversed according to the gear transmission rule of the fixed shaft, so that reversing is realized, and the power transmission route is the same as that of the step 2.

4. One gear advances: at this time, if the input shaft rotates positively, the first shaft is driven to rotate positively through the normally open clutch, the output shaft rotates positively according to the motion rule of the fixed shaft gear, the vehicle advances at a first gear ratio, and the power transmission route is the same as that of the step 2; feeding in a first gear advancing process: when the transmission is applied to a new energy automobile, the running direction of the automobile keeps advancing during one-gear power feeding, the output shaft forwards and reversely drags, the output shaft still forwards rotates, and according to the motion rule of the fixed shaft gear, at the moment, the transmission is input to forward rotate, and the transmission is up-speed and forward rotated relative to the output shaft, and the power transmission route is opposite to the one-gear power transmission route.

5. Upshift from first gear to second gear: gradually removing the axial thrust of the actuator under the condition of first gear advance, gradually reducing the pressure F of the pushing disc along with the clutch drum in the removing process, correspondingly gradually reducing the pressure F of the second friction pair from Fmax to 0 along with the pressure F of the pushing disc, and then gradually separating; correspondingly, the normally closed clutch drum moves leftwards gradually, the right side surface is separated from the engagement contact with the linkage piece, and the support is driven by the clamp spring to press the first friction pair, so that the gap between the first friction pair is gradually reduced, the friction pair is in sliding friction and combined, the normally closed clutch pressure in the process is gradually added to N1 from 0 according to the change rule of N1-F, the complete combination is realized, and then the piston moves to the leftmost position under the action of the return spring. In the second friction pair pressure reducing process, the input torque is controlled at a certain level so as to prevent the input rotational speed from increasing to influence the upshift quality, in the normally closed clutch sliding and grinding combining process, the normally open clutch still has certain pressure, in order to prevent the two clutches from being combined simultaneously and a short-time locking phenomenon from occurring, gear shifting is caused, certain input torque needs to be ensured, the two clutches can have the simultaneous sliding and grinding time, and the gear shifting smoothness is realized through half-linkage power exchange; the normally open clutch is separated, the normally closed clutch is combined, power is directly output from the input shaft to the second driving shaft through the normally closed clutch and then output from the output shaft, and the transmission state is changed into a second gear state of a speed ratio 1.

When the second gear is fed, the vehicle keeps advancing in the driving direction, the output shaft rotates positively, the normally closed clutch keeps being combined, and the normal rotation is input according to the motion rule of the fixed shaft gear, and the same rotating speed as the output shaft is achieved, so that the feeding power transmission route is opposite to the second gear driving transmission route.

7. Downshifts from second gear to first gear: under the condition of second gear forward, the actuator applies pressure to the push disc and gradually increases, after that, the axial movement and axial stress change of each element of the normally closed clutch and the normally open clutch are the same as those of step 2, the pressure born by the normally open clutch is gradually increased along with F at the beginning of clearance elimination of the second friction pair, and the pressure N1-F born by the normally closed clutch is gradually reduced along with F until F=N1, so that when N1> F >0, the friction pairs of the normally closed clutch and the normally open clutch are all subjected to certain pressure, in order to prevent the two clutches from being combined at the same time, a short-time locking phenomenon occurs, gear shifting is blocked, the input torque needs to be ensured to be within a certain range, the two clutches can have simultaneous sliding time, and the smoothness of gear shifting is realized through half-linkage exchange power; the normally closed clutch is disengaged and the normally open clutch is engaged, power is transferred from the input shaft to the first driveshaft via the normally open clutch, and the transmission is shifted from second to first gear.

The beneficial effects are that:

5. the clutch is easy to control, quick and smooth gear shifting is easy to realize, the gear shifting process is unpowered and interrupted, and the clutch is prevented from being separated simultaneously and is combined with a foolproof effect simultaneously.

Claims

1. A dual clutch structure, characterized by: the clutch mechanism comprises a normally-closed clutch, a normally-open clutch and a gear transmission mechanism, wherein the normally-closed clutch and the normally-open clutch are interlocked through one or more linkage pieces, and the linkage pieces are part of the normally-closed clutch or part of the normally-open clutch or are independently arranged from the normally-closed clutch or the normally-open clutch;

2. The dual clutch structure as set forth in claim 1, wherein: the normally-closed clutch comprises a normally-closed clutch drum and a normally-closed clutch hub, a pressure plate is arranged between the normally-closed clutch drum and the normally-closed clutch hub, the pressure plate is in axial sliding connection with the normally-closed clutch drum and in transmission connection with the rotation direction, a plurality of first elastic bodies are arranged between the left side of the normally-closed clutch drum and the pressure plate, the first elastic bodies are compression springs, the plurality of compression springs are uniformly distributed along the circumference, two ends of the compression springs are respectively abutted to the left side of the normally-closed clutch drum and the pressure plate, a first friction pair is arranged on the right side of the pressure plate, the first friction pair comprises a plurality of first outer plates and a first inner plate, the first outer plates and the first inner plates are arranged in a staggered manner, the outer periphery of the first outer plates is in sliding connection with the normally-closed clutch drum through a spline, the inner periphery of the first inner plates is in sliding connection with the normally-closed clutch hub through a spline, a clamp spring is arranged on the right side of the support plate, and the normally-closed clutch drum on the right side of the support plate, and the clamp spring limits the right-side of the support plate to move to the maximum position; the right side of the normally closed clutch is provided with a normally open clutch, the normally open clutch comprises a normally open clutch drum and a normally open clutch hub, a second friction pair is arranged between the normally open clutch drum and the normally open clutch hub, the second friction pair comprises a second outer plate and a second inner plate, the second outer plate and the second inner plate are arranged in a staggered mode, the periphery of the second outer plate is in sliding connection with the normally open clutch drum through a spline, and the periphery of the second inner plate is in sliding connection with the normally open clutch hub through a spline.

3. The dual clutch structure as set forth in claim 2, wherein: when the linkage piece is independently arranged, the inner periphery on the right side of the linkage piece is in sliding connection with the normally open clutch hub through a spline, the inner periphery on the left side of the linkage piece is provided with a plurality of axial spline-shaped long convex parts, correspondingly, the right side of the normally closed clutch drum is provided with a plurality of axially inwards concave groove parts corresponding to the spline-shaped long convex parts, and the spline-shaped long convex parts penetrate into the axially inwards concave groove parts, so that the linkage piece is connected with the normally closed clutch in a transmission way in an axial sliding and rotating direction; correspondingly, the periphery of the pressure plate is radially provided with a plurality of radial tooth-shaped convex parts corresponding to the groove parts of the normally closed clutch drum, the radial tooth-shaped convex parts penetrate through the groove parts of the normally closed clutch drum, which are axially concave, so that the connection of axial sliding and rotation direction transmission is formed, and the right side of the radial tooth-shaped convex parts of the pressure plate is abutted with the left side of the spline-shaped long convex parts of the linkage piece.

4. A dual clutch structure as claimed in claim 3, wherein: the normally closed clutch drum is not provided with a groove part which is axially concave, correspondingly, the normally closed clutch drum is provided with a plurality of hole parts at the corresponding position of the periphery of the pressure plate, the periphery of the pressure plate is provided with a force application block through the hole parts, the force application block is fixedly connected with the pressure plate in a welding or bolt connection mode, correspondingly, the left side of the linkage piece is provided with a plurality of axial long tooth-shaped convex parts, no axial spline-shaped long convex parts are arranged, and the long convex parts of the linkage piece pass through the middle of the adjacent force application blocks, so that the linkage piece is in axial sliding and rotation direction transmission connection with the pressure plate.

5. The dual clutch structure as set forth in claim 4, wherein: the outer side or the periphery of the pressure plate is provided with a circular ring fixedly connected with the force application block, the strength of the pressure plate and force application block combination body is increased by the circular ring, and the deformation of the inner periphery of the pressure plate is reduced.

6. The dual clutch structure as set forth in claim 2, wherein: the linkage piece is a part of the normally closed clutch and is a supporting piece, the supporting piece is in sliding connection with the normally open clutch hub through an inner peripheral spline, and accordingly, the compression spring is arranged on the right side of the first friction pair, and two ends of the compression spring are respectively abutted against the pressure plate and the supporting piece; the linkage piece is a part of a normally closed clutch, the linkage piece is a normally closed clutch drum, the normally closed clutch drum is in sliding connection with a normally open clutch hub through a right inner peripheral spline, correspondingly, the compression spring is arranged on the right side of the first friction pair, and the supporting plate is arranged on the left side of the normally closed clutch drum; when the linkage piece is a part of the normally closed clutch, no matter the supporting plate is the linkage piece or the normally closed clutch drum is the linkage piece, the switching pushing disc is correspondingly arranged on the left side of the normally closed clutch drum, the right side of the switching pushing disc is provided with a long tooth-shaped convex part, and the long tooth-shaped convex part of the switching pushing disc is mutually nested with the Zhou Chixing part outside the pressure disc, so that the switching pushing disc can synchronously rotate with the pressure disc, and axial pressure is applied to the normally open clutch through the right side of the normally closed clutch drum.

7. The dual clutch structure as set forth in claim 2, wherein: a plurality of second elastic bodies are uniformly distributed between the right side of a first outer sheet and the left side of the second friction pair and the shell, two ends of each second elastic body are respectively abutted against the first outer sheet and the second outer sheet on the left side, and when the piston is in the leftmost state, the second elastic bodies are in a free state between the first outer sheet and the second outer sheet, namely a certain gap is reserved between the friction sheet on the left side of the normally closed clutch drum and the pushing disc, or a certain gap is reserved between the linkage piece and the first inner sheet on the left side; the normally closed clutch and the normally open clutch can be a multi-plate wet clutch, a dry clutch or a compound clutch.

8. A transmission employing the dual clutch structure of any one of claims 1-7, characterized by: the transmission body is internally and sequentially provided with an actuator, a push disc, a friction plate and a baffle plate from left to right, the push disc is arranged on the right side of a piston of the actuator and is opposite to the friction plate, the push disc is in sliding connection with the baffle plate through an inner peripheral spline, the baffle plate is fixedly connected with a normally open clutch drum, a return spring is arranged between the baffle plate and the piston, a normally closed clutch is arranged on the right side of the friction plate in the normally open clutch drum, when a linkage piece is independently arranged, the friction plate is fixed on the left side surface of the normally closed clutch drum, and when the normally closed clutch or a part of the normally open clutch is used as the linkage piece, the friction plate is fixed on the left side surface of the switching push disc; when the linkage piece is independently arranged, the linkage piece is arranged between the normally-closed clutch and the normally-open clutch friction pair, and the friction plate is fixedly connected with the normally-closed clutch drum or the switching disc due to the sliding connection of the dual plate (pushing disc) of the friction plate and the normally-open clutch drum, and the normally-closed clutch drum or the switching disc is in sliding connection with the normally-open clutch hub through the linkage piece, so that the friction plate and the pushing disc can be respectively regarded as a part of the second friction pair.

9. A transmission as claimed in claim 8, wherein: the planetary gear structure comprises a sun gear, a gear ring and a planet carrier assembly, wherein the planet carrier assembly comprises a planet carrier, planet gears, a planet wheel shaft and bearings in the middle of the planet wheel and the planet wheel shaft, the gear ring is arranged on the periphery of the sun gear, a plurality of planet gears are uniformly distributed between the sun gear and the gear ring and are connected with the sun gear and the gear ring in a gear meshing mode, the planet gears are rotationally connected with the planet wheel shaft through the bearings, two ends of the planet wheel shaft are fixedly connected with the planet carrier, so that a planet row is formed, the sun gear and a normally closed clutch hub are fixedly connected with the input shaft or are connected with a spline respectively, the gear ring is fixedly connected with the normally open clutch hub or is made into a whole, the normally open clutch drum is fixedly connected with a shell or is made into a whole, and the output shaft is fixedly connected with the planet carrier or is connected with the spline in a sliding mode.

10. A transmission as claimed in claim 8, wherein: when the gear transmission mechanism is a fixed shaft gear mechanism, two driving shafts are arranged, a first driving shaft and a second driving shaft are fixedly connected with a normally open clutch hub or are in spline connection or are integrally formed, the second driving shaft is fixedly connected with a normally closed clutch hub or are in spline connection or are integrally formed, the first driving shaft is provided with a first driving gear, a first driven shaft is correspondingly arranged, the first driven shaft is provided with a first driven gear and an intermediate gear, the first driven gear and the intermediate gear are fixedly connected with the first driven shaft, the corresponding output shaft is provided with an output gear, the output gear is fixedly connected with the output shaft, the first driving gear is meshed with the first driven gear according to the conventional technology, and the intermediate gear is meshed with the output gear on the output shaft according to the conventional technology, so that a two-gear transmission with a speed ratio of 1 is formed.