CN219728470U

CN219728470U - Centrifugal transmission mechanism of shaftless automatic transmission device and shaftless automatic transmission device

Info

Publication number: CN219728470U
Application number: CN202221299563.1U
Authority: CN
Inventors: 沈万伦; 沈颖; 刘美铃
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-05-27
Filing date: 2022-05-27
Publication date: 2023-09-22
Anticipated expiration: 2032-05-27

Abstract

The utility model belongs to the field of mechanical speed changing devices for bicycles, motorcycles or tricycles, and in particular relates to a centrifugal transmission mechanism of an automatic shaftless speed changing device and the automatic shaftless speed changing device, wherein the centrifugal transmission mechanism of the automatic shaftless speed changing device comprises a supporting shaft and a transmission sleeve which is arranged at one end of the supporting shaft and is in clearance fit with the supporting shaft, the other end of the supporting shaft is fixedly connected with an output shaft, a supporting seat is further arranged on the supporting shaft between the output shaft and the transmission sleeve, and the supporting seat is in clearance fit with the supporting shaft; the centrifugal assembly is arranged on the supporting seat and comprises a guide rod fixed on the supporting seat and a transmission block in sliding connection with the guide rod. The shaftless automatic speed change device has the advantages of simple integral structure, small volume, low manufacturing cost, easy processing, more attractive appearance after loading and easy use.

Description

Centrifugal transmission mechanism of shaftless automatic transmission device and shaftless automatic transmission device

Technical Field

The utility model relates to the field of mechanical speed changing devices for bicycles, motorcycles or tricycles, in particular to a centrifugal transmission mechanism of a shaftless automatic speed changing device and the shaftless automatic speed changing device.

Background

The traditional shifting process of shifting gears of a multi-gear bicycle, a motorcycle or a tricycle depends on a transmission system to transmit power, wherein the bicycle mainly shifts by finger dialing; the multi-gear motorcycle mainly adopts a pedal to shift gears; the manual tricycle generally does not need to be shifted, and the motor tricycle mainly shifts by a rocking shift lever. The gear shifting mode mainly has the following defects: (1) In a gear shifting system of 'finger shifting', pedal shifting and 'rocking gear lever' shifting, auxiliary devices such as a gear shifting control mechanism, a control rope and a rod are additionally arranged outside a bicycle, the whole gear shifting system is complex, and the control and operation difficulties of manual gear shifting in the riding process of a bicycle or a motorcycle are high; in addition, in the process of realizing gear shifting by manual control, a rider can easily scatter attention, and certain potential safety hazards exist. (2) The chain and the sprocket of transmission power are directly exposed in the air, often can receive the influence of wind blow, sun shine, drenches and foreign objects such as dust, muddy, stone, operational environment is poor, consequently the wearing and tearing or the trouble appear in the shift system easily to influence transmission system's transmission efficiency and life. (3) The transmission efficiency of the chain transmission power is lower, and the physical effort of a rider is increased to a certain extent.

Aiming at the defects of the gear shifting mode, the prior art improves the gear shifting mode, and as disclosed in the patent with the publication number of CN111661231A, a ratchet telescopic mechanism for a shaftless automatic transmission and the shaftless automatic transmission are proposed, and the gear shifting mechanism comprises a ratchet seat, a ratchet mechanism and a transmission sleeve penetrating the ratchet seat and provided with a sliding key and a concave on the side surface; the ratchet mechanism comprises a connecting rod mechanism, ratchet teeth and rollers, wherein the ratchet teeth and the rollers are respectively fixed at two ends of the connecting rod mechanism, the connecting rod mechanism is movably arranged in a ratchet seat, the ratchet teeth correspond to ratchet rings of a driven gear set of the speed changer, and the rollers correspond to the depressions; the two ends of the transmission sleeve are respectively fixed with a support I and a support II, a spring I is arranged between the support I and the ratchet seat, a spring II is arranged between the support II and the ratchet seat, the spring I and the spring II are respectively fixedly connected with the ratchet seat, and a spring III is arranged at the lower end of the ratchet I. The automatic gear shifting device not only can realize automatic gear shifting, but also can avoid dispersing the attention of a rider during riding so as to reduce potential safety hazards; and the transmission efficiency can be improved, and the service life can be prolonged. However, the device disclosed in the patent has a large overall volume for small-wheel-diameter bicycles, motorcycles or tricycles, is inconvenient to install during loading, and affects arrangement and attractiveness.

Accordingly, there is a need in the art for an improved ratchet telescoping mechanism for a shaftless automatic transmission and shaftless automatic transmission that optimizes some of the components thereof to further address the deficiencies in the prior art.

Disclosure of Invention

The utility model aims to provide a centrifugal transmission mechanism of a shaftless automatic speed change device, which has the advantages of simple structure, small volume, easy processing, low manufacturing cost, more attractive appearance and easy use after loading under the condition of ensuring the realization of a gear shifting function.

The technical scheme adopted for realizing the purpose of the utility model is as follows:

the centrifugal transmission mechanism of the shaftless automatic speed change device comprises a support shaft and a transmission sleeve which is arranged at one end of the support shaft and is in clearance fit with the support shaft, the other end of the support shaft is rotationally connected with an output shaft, a supporting seat is further arranged on the support shaft between the output shaft and the transmission sleeve, and the supporting seat is in clearance fit with the support shaft; the centrifugal transmission assembly comprises a guide rod fixed on the supporting seat and a transmission block in sliding connection with the guide rod;

the centrifugal assembly further comprises a fixed pull rod I and a movable pull rod II, wherein one end of the fixed pull rod I is hinged with the transmission block, and the other end of the fixed pull rod I is hinged with an end cover on the output shaft; one end of the movable pull rod II is hinged with the transmission block, and the other end of the movable pull rod II is hinged with the transmission sleeve;

The device also comprises an elastic connecting piece, wherein two ends of the elastic connecting piece are respectively fixed at the middle parts of the fixed pull rod I and the movable pull rod II, and the middle part of the elastic connecting piece is hinged with the transmission block.

Further, the number of the centrifugal transmission components is more than two groups; more than two groups of balls I are arranged between the supporting seat and the supporting shaft, each group of balls I is more than one, and each group of balls I corresponds to one group of centrifugal transmission assembly in position.

Further, an opening is formed in a contact area of the transmission block and the supporting seat, a pin shaft is arranged in the opening, and a pin hole matched with the pin shaft is formed in one end, connected with the transmission block, of the fixed pull rod I; the end cover is fixed with a hinged support I, and the fixed pull rod I is hinged with the end cover through the hinged support I;

one end of the movable pull rod II connected with the transmission block is provided with a pin hole matched with the pin shaft in the opening of the transmission block; the transmission sleeve is fixedly provided with a hinged support II, and the movable pull rod II is hinged with the transmission sleeve through the hinged support II.

Further, the elastic connecting piece is a torsion spring II, one end of the torsion spring II is fixedly connected with the fixed pull rod I, and the other end of the torsion spring II is fixedly connected with the movable pull rod II; the middle part of the torsion spring II is hinged with a pin shaft in the opening of the transmission block.

The utility model aims to provide a shaftless automatic speed change device which is simple in structure, small in size, easy to process, low in manufacturing cost, attractive in appearance and easy to use after loading.

The technical scheme adopted for realizing the other purpose of the utility model is as follows:

the shaftless automatic speed change device comprises an input end and an output end, wherein the output end comprises a support shaft and a ratchet telescopic mechanism arranged at one end of the support shaft, and a driven gear set is arranged outside the ratchet telescopic mechanism; the other end of the supporting shaft is rotationally connected with the output shaft; a centrifugal transmission mechanism is also arranged between the ratchet telescopic mechanism and the output shaft;

the output end also comprises an output seat and an end cover, the end cover is fixedly connected with the output shaft, and the output seat is matched with the end cover through a spline;

the input end comprises a transmission mechanism with an input shaft and a spline shaft, the input shaft and the spline shaft are arranged in parallel with the support shaft, and the input shaft and the spline shaft are rotationally connected through a transmission shaft; the spline shaft is provided with a driving gear set matched with the driven gear set.

Further, two ends of the transmission shaft are respectively fixed with a gear II and a gear III through a spline, wherein the gear II is matched with the input shaft, and the gear III is matched with the spline shaft;

the input shaft is fixed with a gear I meshed with a gear II through a spline, the driving gear set is integrated with a gear IV meshed with a gear III, and the driving gear set and the gear IV are integrated into a whole.

Further, the ratchet telescopic mechanism comprises a ratchet seat, a ratchet mechanism and a transmission sleeve penetrating through the ratchet seat and provided with a sliding key and a concave on the side surface; the ratchet mechanism comprises a connecting rod mechanism, a ratchet I and a roller wheel, wherein the ratchet I and the roller wheel are respectively fixed at two ends of the connecting rod mechanism, the connecting rod mechanism is movably arranged in a ratchet seat, the ratchet I corresponds to a ratchet ring of a driven gear set of the speed changer, and the roller wheel corresponds to a recess on the transmission sleeve; a bracket I and a bracket II are respectively fixed at two ends of the transmission sleeve, a spring I is arranged between the bracket I and the ratchet seat, a spring II is arranged between the bracket II and the ratchet seat, and the spring I and the spring II are respectively fixedly connected with the ratchet seat; the lower end of the ratchet I is provided with a spring III.

Further, a sliding plate with a ball mounting groove is arranged on the outer circle of the bracket I, and a ball IV is placed in the ball mounting groove; the output seat is provided with an axial groove matched with the ball IV.

Further, gear stabilizing assemblies are arranged on two sides of the ball mounting groove, and each gear stabilizing assembly comprises a gear reducing stabilizing assembly and an gear increasing stabilizing assembly; the gear-reducing stabilizing assembly comprises a torsion spring I, a torsion spring II, a positioning seat I, a positioning seat II, a limiting hole II and more than two limiting holes I formed in the output seat, wherein the limiting holes II are formed in the sliding plate, the torsion spring I is fixed on the positioning seat I and corresponds to the limiting holes I, the torsion spring II is fixed on the positioning seat II and corresponds to the limiting holes II, the positioning seat I is fixed on the outer circumference of the output seat, and the positioning seat II is fixed on the inner circumference of the sliding plate; the gear-up stabilizing assembly comprises a torsion spring III, a torsion spring IV, a positioning seat III, a positioning seat IV, a limiting hole IV and more than two limiting holes III formed in the output seat, wherein the limiting holes IV are formed in the sliding plate, the torsion spring III is fixed on the positioning seat III and corresponds to the limiting holes III, the torsion spring IV is fixed on the positioning seat IV and corresponds to the limiting holes IV, the positioning seat III is fixed on the outer circumference of the output seat, and the positioning seat IV is fixed on the inner circumference of the sliding plate; the installation direction of the torsion spring I is opposite to that of the torsion spring III, and the installation direction of the torsion spring II is opposite to that of the torsion spring IV; the torsion spring I is in partial contact with the torsion spring II; torsion spring III is in partial contact with spring IV.

Further, the number of the ratchet telescopic mechanisms is more than two, more than two groups of balls II are arranged between the transmission sleeve and the support shaft, and each group of balls II corresponds to one group of ratchet telescopic mechanisms in position.

The working principle of the utility model is as follows: the pedal is fixed on the input shaft, the rear wheel is fixed on the output shaft, the pedal rotates synchronously with the input shaft, and the rear wheel rotates synchronously with the output shaft. When the automatic transmission works at a certain low gear, the pedal is quickly stepped, the input shaft is quickly rotated and drives the driving gear set to quickly rotate through the transmission mechanism, the driving gear drives each driven gear to quickly rotate, the ratchet telescopic mechanism, the sliding plate and the output seat to rotate, and the output seat drives the output shaft and the rear wheel to quickly rotate. When the rotating speed of the output seat is slightly higher than the set rotating speed of a first gear, the centrifugal transmission assembly gets rid of the control of a torsion spring III of a certain gear up-shift stabilizing assembly to perform centrifugal motion, the transmission block moves outwards along a guide rod under the action of the centrifugal force to compress a torsion spring II, because the end cover cannot axially move and can only circumferentially rotate, the hinged seat I drives the transmission block to rotate through the fixed pull rod I and the hinged seat II together by moving the pull rod II, the transmission block moves away from a supporting shaft under the action of the centrifugal force, the hinged seat I limits the fixed pull rod I to axially move, the fixed pull rod I rotates clockwise as shown in fig. 2 around the pin shaft center of the hinged seat I, the transmission block drives the movable pull rod II to rotate around the pin shaft center of the hinged seat II, meanwhile, the movable pull rod II drives the transmission sleeve to move leftwards, the ratchet seat cannot synchronously move leftwards with the transmission sleeve under the action of inertia and relatively to the transmission sleeve, the spring II compresses, the roller of the ratchet telescopic mechanism lifts along the concave right inclined surface on the transmission sleeve, the connecting rod mechanism moves to drive the ratchet seat I to separate from the engaged driven gear ratchet seat I, and the ratchet seat I simultaneously passes through the compression spring seat III; when the transmission sleeve is about to reach the position of the first gear, the moving speed is gradually reduced, when the spring II is compressed to the set limit position, the ratchet seat is acted by the continuous thrust of the spring II, the roller moves leftwards at the right horizontal section of the recess of the transmission sleeve, when the roller moves to the top high-point edge of the recess right side of the transmission sleeve, a small amount of ratchet I enters the meshing area of the first gear ratchet II, as the roller is still at the right high-point horizontal section of the recess right side of the transmission sleeve, the ratchet I does not extend outwards, when the roller continues to move leftwards to enter the central position of the recess of the transmission sleeve, the connecting rod mechanism moves, and meanwhile, the ratchet seat drives the ratchet I to move leftwards to be aligned with the axial position of the ratchet ring of the driven gear of the first gear; simultaneously, the ratchet I stretches outwards under the pushing of the spring III, and when the large diameter point of the first gear ratchet ring is matched with the ratchet I, the ratchet I stretches outwards smoothly, so that power transmission can be realized; if the small diameter point of the ratchet II is matched with the ratchet I at the moment, the ratchet I is limited after a small amount of extension; when the rotating speed of the first gear ratchet ring is higher than that of the ratchet seat, the ratchet I slides backwards to a large diameter point along the ratchet inclined plane of the ratchet II, and simultaneously, the ratchet I extends outwards under the pushing of the spring III to form matched transmission power; if the rotating speed of the first gear ratchet ring is higher than that of the ratchet seat at the moment, the ratchet I is compressed by the ratchet inclined surface of the ratchet II, the ratchet I pushes the spring seat to compress the spring III, and when the ratchet seat continuously rotates, the spring III and the ratchet I repeatedly compress and return until the pedal is stepped to enable the rotating speed of the ratchet ring of the first gear driven gear to be higher than that of the ratchet seat, and the ratchet ring drives the ratchet seat to transmit torque; the rotational speed of the input shaft is unchanged, but the bicycle running speed will be in accordance with the set high first gear speed.

When the rotating speed of the output seat is slightly lower than the set rotating speed of one gear, the vector resultant force of the torsion spring II and the transmission block pushes the fixed pull rod I and the movable pull rod II to open towards two sides. When the transmission sleeve moves rightwards, the ratchet seat cannot move rightwards synchronously with the transmission sleeve under the action of inertia, but moves leftwards relative to the transmission sleeve, the spring I compresses, the roller of the ratchet mechanism lifts upwards along the inclined plane on the left side of the recess on the transmission sleeve, the connecting rod mechanism moves to drive the ratchet I to retract into the ratchet seat to separate from the engaged ratchet ring of the driven gear, and meanwhile, the ratchet I pushes the spring seat to compress the spring III; when the transmission sleeve is about to reach a first gear position, the movement speed is reduced, the ratchet seat is under the continuous thrust action of the spring I, the roller moves rightwards at the left horizontal section of the recess of the transmission sleeve, when the roller moves to the top high-point edge of the recess left side of the transmission sleeve, the ratchet I enters a meshing area of the ratchet II in a small amount, as the roller is still at the left high-point horizontal section of the recess of the transmission sleeve, the ratchet I does not extend outwards, when the roller moves rightwards to enter the central position of the recess of the transmission sleeve, the ratchet seat drives the ratchet I to move rightwards while the connecting rod mechanism moves and is aligned with the axial position of the ratchet ring of the driven gear with the first gear, meanwhile, the ratchet I extends outwards under the pushing of the spring III, and when the large-diameter point of the first gear ratchet ring is matched with the ratchet I, the ratchet I extends outwards smoothly, and power transmission can be realized; if the small diameter point of the ratchet II is matched with the ratchet I at the moment, the ratchet I is limited after a small amount of extension; when the rotating speed of the first gear ratchet ring is higher than that of the ratchet seat, the ratchet I slides backwards to a large diameter point along the ratchet inclined plane of the ratchet II, and simultaneously, the ratchet I extends outwards under the pushing of the spring III to form matched transmission power; if the rotating speed of the first gear ratchet ring is lower than that of the ratchet seat at the moment, the ratchet I slides forwards on the ratchet inclined surface of the ratchet II to be compressed, the ratchet I pushes the spring seat to compress the spring III, and when the ratchet seat continuously rotates, the spring III and the ratchet I repeatedly compress and return until the pedal is stepped to enable the rotating speed of the ratchet ring of the first gear driven gear to be lower than that of the ratchet seat, and the ratchet ring drives the ratchet seat to transmit torque; the speed of the input shaft is unchanged, but the bicycle running speed will run at the set low first gear speed.

The utility model has the beneficial effects that:

(1) Compared with the existing shaftless automatic speed changing device, the centrifugal transmission mechanism is small in size, and on the basis, the part of the structural position of the input end is changed from the left side of the driving gear set to the right side of the driving gear set, so that the overall size of the transmission is reduced; the ratchet seat and the transmission sleeve are reversely arranged, so that the space occupied by each accessory is reasonably planned, and the volume of the whole device is further reduced;

(2) The centrifugal transmission mechanism has the advantages that the structure is further simplified, the installation and the disassembly are convenient, the processing cost is reduced, the production efficiency is improved, the loading and the use are easy, and the vehicle is more attractive;

(3) The utility model adopts the ratchet telescopic mechanism of the shaftless automatic speed changing device and the shaftless automatic speed changing device, cancels auxiliary devices such as a gear shifting control mechanism, a control rope, a rod and the like, realizes automatic gear shifting, avoids the distraction of a rider during riding, reduces potential safety hazards and improves the use experience and feeling of people;

(4) The utility model can improve the transmission efficiency by 3-5%, prolong the service life, has strong practicability and can effectively reduce the physical consumption of the riders.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the present utility model will be further described with reference to the accompanying drawings and embodiments, in which the drawings in the following description are only some embodiments of the present utility model, and other drawings may be obtained by those skilled in the art without inventive effort:

fig. 1 is a schematic cross-sectional view of a shaftless automatic transmission according to the present utility model.

Fig. 2 is a schematic view of a partially enlarged structure of the centrifugal transmission mechanism of the present utility model.

FIG. 3 is another schematic cross-sectional view of a ratchet telescoping mechanism for a shaftless automatic transmission of the present utility model.

FIG. 4 is a schematic top view of the ratchet telescoping mechanism for a shaftless automatic transmission of the present utility model.

FIG. 5 is a schematic cross-sectional view of the ratchet telescoping mechanism of the present utility model mated with a ratchet ring for a shaftless automatic transmission.

FIG. 6 is a schematic view of the positional relationship of the power block and gear stabilizing assembly arrangement in the present utility model.

Fig. 7 is a schematic view of a power take-off end cap according to the present utility model.

FIG. 8 is a cross-sectional view taken at A-A of FIG. 6, showing a schematic axial position of the shift stabilizing assembly retarding downshift and control displacement.

FIG. 9 is a cross-sectional view taken at B-B of FIG. 6, showing a schematic axial position of the shift stabilizing assembly retarding upshift, control displacement.

Fig. 10 is a schematic view of the shutter structure of the ratchet telescoping mechanism.

In the figure: 1. the gear assembly comprises an input shaft, a 2-connecting rod mechanism, a 3-gear I, a 4-input end, a 5-spline shaft, a 6-gear II, a 7-support seat, a 10-box I, a 11-driving gear set, a 12-driven gear set, a 13-spring II, a 14-transmission block, a 15-five-gear driving gear, a 16-four-gear driving gear, a 17-three-gear driving gear, a 18-two-gear driving gear, a 19-first-gear driving gear, a 20-positioning pin, a 21-limiting hole II, a first-gear driving gear and a second-gear driving gear. 22 ratchet pockets, 23 ratchet teeth I, 24 mounting holes, 25 springs III, 26 levers, 27 rollers, 28 springs I, 29 driving pockets, 30 sliding keys, 31 limiting holes III, 32 balls II, 33 balls III, 34 baffles, 35 bearings I, 36 five-gear driven gears, 37 four-gear driven gears, 38 three-gear driven gears, 39 two-gear driven gears, 40 first-gear driven gears, 33 balls III, 34. 41, limit seat IV, 42, seat II, 45, guide rod, 46, ball mounting groove, 47, track, 48, moving seat II, 49, torsion spring II, 50, ratchet II, 51, support shaft, 52, 53, fixed seat I, 54, seat I, 55, bearing, 56, ball I, 57, seat 58, displacement rod, 59, spring seat 60, end cap, 61, gear IV, 62, axial groove, 63, torsion spring I, 64, recess 65, bracket I, 66, gear III, 67, bracket II, 69, transmission shaft, 71, limit seat, 72, limit groove 73, retainer ring 76, slide plate 77, output seat 78, positioning seat II, 79, torsion spring II, 80, torsion spring IV, 81, torsion spring I, 82, positioning seat I, 83, torsion spring III, positioning seat III, and torsion spring III 85. Limiting holes I, 86, supporting seats, 87, ratchet rings, 88, ratchet seats, 89, balls IV, 91, small diameter points and 92, large diameter points.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present utility model more apparent, the following description will be made in detail with reference to the technical solutions in the embodiments of the present utility model, and it is apparent that the described embodiments are some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by a person skilled in the art without any inventive effort, are intended to be within the scope of the present utility model, based on the embodiments of the present utility model.

As shown in fig. 1 and 2, the centrifugal transmission mechanism of the shaftless automatic transmission device comprises a support shaft 51 and a transmission sleeve 29 arranged at one end of the support shaft 51 and in clearance fit with the support shaft 51, wherein the other end of the support shaft 51 is rotationally connected with an output shaft 52, a supporting seat 57 is further arranged on the support shaft 51 between the output shaft 52 and the transmission sleeve 29, and the supporting seat 57 is in clearance fit with the support shaft 51; the support seat 57 is provided with a centrifugal transmission assembly, and the centrifugal transmission assembly comprises a guide rod 45 fixed on the support seat 57 and a transmission block 14 in sliding connection with the guide rod 45;

the centrifugal assembly further comprises a fixed pull rod I53 and a movable pull rod II48, wherein one end of the fixed pull rod I53 is hinged with the transmission block 14, and the other end of the fixed pull rod I53 is hinged with an end cover 60 on the output shaft 52; one end of the movable pull rod II48 is hinged with the transmission block 14, and the other end is hinged with the transmission sleeve 29;

The device also comprises an elastic connecting piece, wherein two ends of the elastic connecting piece are respectively fixed at the middle parts of the fixed pull rod I53 and the movable pull rod II48, and the middle part of the elastic connecting piece is hinged with the transmission block 14. As particularly shown in fig. 1 and 2.

Further, as shown in fig. 6, the number of centrifugal components is two or more; more than two groups of balls I56 are arranged between the supporting seat 57 and the supporting shaft 51, more than one ball I56 is arranged in each group, and each group of balls I56 corresponds to one group of centrifugal transmission assembly.

Further, as shown in fig. 1 and 2, an opening is arranged at the contact area of the transmission block 14 and the supporting seat 57, a pin shaft is arranged in the opening, and a pin hole matched with the pin shaft is arranged at one end of the fixed pull rod I53 connected with the transmission block 14; the end cover 60 is fixed with a hinged support I54, and the fixed pull rod I53 is hinged with the end cover 60 through the hinged support I54;

one end of the movable pull rod II48 connected with the transmission block 14 is provided with a pin hole matched with a pin shaft in an opening of the transmission block 14; the transmission sleeve 29 is fixedly provided with a hinged support II44, and the movable pull rod II48 is hinged with the transmission sleeve 29 through the hinged support II 44.

Further, as shown in fig. 1 and 2, the elastic connecting piece is a torsion spring II49, one end of the torsion spring II49 is fixedly connected with the fixed pull rod I53, and the other end is fixedly connected with the movable pull rod II 48; the middle part of the torsion spring II49 is hinged with a pin shaft in the opening of the transmission block 14;

In the centrifugal transmission mechanism of the utility model, the supporting seat 57 and the transmission block 14 synchronously move left and right on the supporting shaft 51, the transmission block 14 can move away from the supporting shaft 51 on the guide rod 45 under the action of centrifugal force, and when the centrifugal force is reduced, the transmission block 14 moves close to the supporting shaft 51 along the guide rod 45 under the action of the torsion spring II49, so that the transmission sleeve 29 moves left or right on the supporting shaft 51. The resilient connecting element of the present utility model may be a spring, torsion spring or other resilient material. When the elastic connecting piece is a spring, two springs are provided, one end of each spring is fixedly connected with the fixed pull rod I53, and the other end of each spring is fixedly connected with the transmission block 14; the other end is fixedly connected with the movable pull rod II48, and the other end is fixedly connected with the transmission block 14. When the elastic connecting piece is a torsion spring, one end of the torsion spring is fixedly connected with the fixed pull rod I53, the annular part in the middle of the torsion spring II49 is hinged with a pin shaft in the opening of the transmission block 14, and the other end of the torsion spring II49 is fixedly connected with the movable pull rod II 48;

in one embodiment of the utility model, the centrifugal transmission mechanism comprises three groups of transmission blocks 14, a hinged support I54, a hinged support II44, a fixed pull rod I53, a movable pull rod II48 and a torsion spring II 49; the end cover 60 is provided with a hinged support I54, the transmission sleeve 29 is provided with a hinged support II44, the hinged support I54 and the hinged support II44 are arranged on the circumferences with the same diameter, and the hinged support I54 and the hinged support I144 are arranged at 60 degrees from the ball mounting groove 46 on the sliding plate 76 and the axial groove 62 on the output seat 77; the hinge support I54 and the hinge support II44 are movably connected with the fixed pull rod I53 and the movable pull rod II48 through pin shafts, the lengths of the fixed pull rod I53 and the movable pull rod II48 are equal, the other ends of the fixed pull rod I53 and the movable pull rod II48 are hinged with the transmission block 14 through pin shafts, a torsion spring II49 is further arranged on mounting pin shafts of the transmission block 14, the fixed pull rod I53 and the movable pull rod II48, two ends of the torsion spring II49 are respectively connected and fixed with the fixed pull rod I53 and the movable pull rod II48, the action of the torsion spring II49 is to ensure that when the speed of the shaftless automatic speed changing device is reduced to be slightly lower than a certain low gear set rotating speed or stops rotating, the vector resultant force of the transmission block 14 and the torsion spring II49 can timely push the mechanisms such as the transmission sleeve 29 to a certain low gear or a first gear position to the right, when the shaftless automatic speed changing device stops rotating, the transmission block 14 returns to a position attached to the outer surface of the support block 57 under the action of the torsion spring II49, (namely, solid line positions of the transmission block 14 in fig. 1 and 2 and 6) and the support block 14 in a solid line position of the support block 49, namely when the running speed of a bicycle or a motorcycle is slightly lower than the set rotating speed, the resultant force vector of the torsion spring II is pushed by the torsion spring II and the vector force of the transmission block 14 moves to the support sleeve 29 to the right through the fixed pull rod I53 and the torsion spring II to the right gear position of the support the transmission sleeve 29 and the transmission sleeve 29 to move to the axial direction of the transmission sleeve 57.

As shown in fig. 1 and 2, the fixed tie rod I53, the movable tie rod II48 and the torsion spring II49 are mounted on the driving block 14 through pins, and the path 47 formed by the pin motion path of the shaftless automatic transmission is up-shifted from first gear to fifth gear. Namely, a fixed pull rod I53 arranged on a hinged support I54 takes the pin shaft center of the hinged support I54 as a circle center, the distance between the pin shaft hole centers at two ends of the fixed pull rod I53 as a radius, and a motion track line 47 of a pin shaft on a transmission block 14 is drawn along the clockwise direction; the movable pull rod II48 takes the pin shaft center of the hinged support II44 as a circle center, takes the distance between the pin shaft hole centers at two ends of the movable pull rod II48 as a radius, and pulls the hinged support II44 and the transmission sleeve 29 to move leftwards on the support shaft 51 while one end of the movable pull rod II48 rotates anticlockwise around the hinged support II44 along with the transmission block 14; and (3) a gear reduction process: the resultant vector force of the drive block 14 and torsion spring II49 urges the mechanisms in opposite motion.

In this embodiment, as shown in fig. 1, 2 and 6, the supporting seat 57 is an equilateral triangle, two groups of guide rods 45 are arranged on each side, two holes corresponding to the positions of the guide rods 45 are arranged on each group of transmission blocks 14, the transmission blocks 14 are movably mounted on the guide rods 45, particularly as shown in fig. 1, 2 and 6, when a bicycle or a motorcycle runs, the rear wheel drives the transmission blocks 14 to rotate through the end cover 60, the hinged support I54, the fixed pull rod I53, the movable pull rod II48, the hinged support II44 and the transmission sleeve 29, the transmission blocks 14 can slide outwards on the guide rods 45 under the action of centrifugal force, three groups of balls I56 are arranged in the supporting seat 57, each group of two balls I56 are uniformly distributed in three independent ball grooves in the supporting seat 57, the three independent mounting grooves correspond to three corners of the triangle, the three groups of transmission blocks 14 are integrally connected through guide rods 45 by the bearing seat 57, so that the axial positions of the three groups of transmission blocks 14 are consistent, the axial acting force of the three groups of movable pull rods II48 on the transmission sleeve 29 is ensured to be equal, and the problem that the three groups of transmission blocks 14 and the three groups of fixed pull rods I53 and the movable pull rods II48 connected with the three groups of transmission blocks 14 are inconsistent in axial movement due to the fact that the three groups of transmission blocks 14 are subjected to external force action in an uncertain direction outside centrifugal force due to different positions when a road surface jolts or brakes is avoided, so that the difficulty in gear maintenance or gear shifting is caused is avoided; in order to make the vector resultant force of the three sets of transmission blocks 14 and the torsion springs II49 act on the transmission sleeve 29 consistent in any case, the number and the axial arrangement length of the balls I56 can be appropriately increased, and the balls I56 can effectively reduce the friction force between the bearing seat 57 and the support shaft 51; in other embodiments, the driving blocks 14 may be associated as a whole in other ways, so that two or more groups of driving blocks 14 always maintain consistent axial positions.

In the utility model, the ratchet seat 88 and the transmission block 14 have to keep proper quality so as to meet the requirements of the automatic transmission on speed change and gear shift, and other parts can be made of light materials according to the requirements on strength, rigidity and the like on the premise of meeting the requirements, so that the whole quality of the transmission is reduced, and the effects of light weight of the vehicle, sensitive and accurate gear shift and the like are achieved.

When the speed of the bicycle or the motorcycle is gradually increased from zero to slightly higher than the second-gear rotating speed, the vector resultant force of the three groups of transmission blocks 14 and the torsion spring II49 sequentially overcomes various friction resistance and the elasticity of the three groups of torsion springs III83 of the upshift stabilizing assembly and the torsion spring II79 of the downshift stabilizing assembly, the three groups of transmission blocks 14 move outwards, the fixed pull rod I53 rotates clockwise around the hinged support I54, and the three groups of transmission blocks 14 drive the hinged support II44 and the transmission sleeve 29 to move left axially through the movable pull rod II48 respectively; simultaneously, the transmission block 14 drives the supporting seat 57 to axially move left through the guide rod 45, and the bicycle or the motorcycle is changed from first gear to second gear.

When the running speed of the bicycle or the motorcycle is reduced from the second gear to a speed slightly lower than the first gear set speed, the vector resultant force of the three groups of transmission blocks 14 and the torsion spring II49 overcomes various friction resistance and the elasticity of the torsion spring I81 of the downshift stabilizing component and the torsion spring IV80 of the upshift stabilizing component in sequence, the transmission sleeve 29 is pushed to move axially and rightwards, and meanwhile, the transmission block 14 drives the supporting seat 57 to move axially and rightwards through the guide rod 45, and the bicycle or the motorcycle is changed from the second gear to the first gear.

As shown in fig. 1, the shaftless automatic transmission comprises an input end 4 and an output end, wherein the output end comprises a support shaft 51 and a ratchet telescopic mechanism arranged at one end of the support shaft 51, and a driven gear set 12 is arranged outside the ratchet telescopic mechanism; the other end of the supporting shaft 51 is rotatably connected with an output shaft 52; a centrifugal transmission mechanism is also arranged between the ratchet telescopic mechanism and the output shaft 52;

the output end also comprises an output seat 77 and an end cover 60, the end cover 60 is fixedly connected with the output shaft 52, and the output seat 77 and the end cover 60 can be integrally designed and are matched through spline connection and positioned through a clamping ring;

the input end 4 comprises a transmission mechanism with an input shaft 1 and a spline shaft 5, the input shaft 1 and the spline shaft 5 are arranged in parallel with the support shaft 51, and the input shaft 1 and the spline shaft 5 are rotationally connected through a transmission shaft 69; the spline shaft 5 is provided with a driving gear set 11 matched with a driven gear set 12.

Further, two ends of the transmission shaft 69 are respectively fixed with a gear II6 and a gear III66 through a spline, wherein the gear II6 is matched with the input shaft 1, and the gear III66 is matched with the spline shaft 5;

the input shaft 1 is fixedly provided with a gear I3 meshed with a gear II6 through a spline, the driving gear set 11 is integrated with a gear IV61 meshed with a gear III66, and the driving gear set 11 and the gear IV61 are integrated into a whole; gear II6 mates with gear I3 mounted on input shaft 1 and gear III66 mates with gear IV61 integrated on spline shaft 5.

Further, an outer circular slide plate 76 with a ball mounting groove 46 is arranged on the bracket I65, and a ball IV89 is arranged in the ball mounting groove 46; the output seat 77 is provided with an axial groove 62 matching the ball IV 89.

As shown in fig. 1 to 10, in one embodiment of the present utility model, the shaftless automatic transmission can be assembled into a shaftless automatic transmission after the case is added. The shaftless automatic transmission comprises a box I10, a box II43, a supporting shaft 51 and a speed change mechanism arranged in the box, wherein the speed change mechanism comprises an input end 4, a gear shifting gear and a centrifugal transmission mechanism; the support shaft 51 is mounted in the transmission case II43 and the output shaft 52 by bearings; the ratchet telescopic mechanism is sleeved on the supporting shaft 51; the input end 4 comprises a transmission mechanism with an input shaft 1 and a spline shaft 5; the gear shifting gear comprises a driving gear set 11 and a driven gear set 12 with ratchet gears 87, the driving gear set 11 and the gears IV61 are integrated into a whole and are fixed on a spline shaft 5 through splines, the driven gear set 12 comprises more than two driven gears corresponding to the driving gears, the driven gears are connected through bearings I35, the bearings I35 arranged on the inner ring of the left end face of the five-gear driven gear 36 are matched with the outer ring of the right end of the output seat 77, and the bearings I35 arranged on the outer ring of the right end face of the first-gear driven gear 40 are matched with the inner ring of the box body II43 to realize axial fixation; the ratchet telescopic mechanism is movably arranged in a through hole formed after the ratchet ring 87 of the driven gear set 12 is assembled; the balls IV89 are placed in the three groups of ball mounting grooves 46 arranged on the outer circle sliding plate 76 of the support I65 and are matched with the three groups of axial grooves 62 on the output seat 77 to realize synchronous rotation and axial displacement gear shifting, and meanwhile, the torque of a driven gear of a certain gear is transmitted to the output seat 77 through the ratchet seat 88, the transmission sleeve 29, the support I65 and the balls IV89, and then is transmitted to the driving wheel through the end cover 60 and the output shaft 52.

As shown in fig. 1 to 5, the ratchet telescoping mechanism comprises a ratchet seat 88, a ratchet mechanism, and a transmission sleeve 29 penetrating the ratchet seat 88 and having a sliding key 30 and a recess 64 on the side surface; the ratchet mechanism comprises a connecting rod mechanism 2, ratchet teeth I23 and a roller 27 which are respectively fixed at two ends of the connecting rod mechanism 2, the connecting rod mechanism 2 is movably arranged in a ratchet seat 88, the ratchet teeth I23 correspond to a ratchet ring 87 of the driven gear set 12 of the speed changer, and the roller 27 corresponds to a concave 64; a bracket I65 and a bracket II67 are respectively fixed at two ends of the transmission sleeve 29, a spring I28 is arranged between the bracket I65 and the ratchet seat 88, a spring II13 is arranged between the bracket II67 and the ratchet seat 88, and the spring I28 and the spring II13 are respectively fixedly connected with the ratchet seat 88; the lower end of the ratchet I23 is provided with a spring III25.

In the utility model, when the transmission sleeve 29 moves leftwards rapidly, the ratchet seat 88 cannot move leftwards synchronously with the transmission sleeve 29 under the inertia effect, the ratchet seat 88 moves rightwards relative to the transmission sleeve 29 to compress the spring II13, the roller 27 of the ratchet mechanism lifts upwards along the right inclined plane of the concave 64 on the transmission sleeve 29 and moves rightwards along the horizontal track, the link mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88, the ratchet I23 is separated from the meshed ratchet ring 87 of the driven gear, and the spring III25 is compressed by the spring seat 59; when the transmission sleeve 29 is about to reach the position of the last gear, the moving speed gradually decreases, the ratchet seat 88 moves leftwards to the balance point relative to the transmission sleeve 29 under the continuous thrust of the spring II13, namely the roller 27 gradually moves leftwards to the center position of the concave 64, the link mechanism 2 moves, and the spring III25 pushes the ratchet I23 to extend out of the ratchet seat 88 to be meshed with the ratchet ring 87 of the driven gear of the last gear.

When the transmission sleeve 29 moves right quickly, the ratchet seat 88 cannot move right synchronously with the transmission sleeve 29 under the inertia effect, the ratchet seat 88 moves left relative to the transmission sleeve 29 to compress the spring I28, the roller 27 of the ratchet mechanism lifts up along the left inclined plane of the concave 64 on the transmission sleeve 29 and moves left along the horizontal track, the link mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88 and separate from the engaged ratchet ring 87 of the driven gear, and the ratchet I23 compresses the spring III25 through the spring seat 59; when the transmission sleeve 29 is about to reach the next gear, the moving speed gradually decreases, the ratchet seat 88 gradually returns to the balance point under the continuous thrust of the spring I28, namely, the roller 27 gradually moves right to the center position of the recess 64, the link mechanism 2 moves, and the spring III25 pushes the ratchet I23 to extend out of the ratchet seat 88 to be meshed with the ratchet ring 87 of the driven gear of the next gear.

In this embodiment, the bracket I65 and the bracket II67 are respectively fixed at two ends of the transmission sleeve 29 by a snap ring, and in another embodiment, the bracket I65 and the bracket II67 may be further fixed with the transmission sleeve 29 by an integrated arrangement, a bonding fixation, a fastening piece fixation, a welding fixation, or the like. The support I65 and the support II67 are provided with more than two groups of bulges in the central area between every two groups of sliding keys 30, so that the maximum displacement of the ratchet seat 88 is limited, and the springs I28 and II13 are prevented from being damaged.

As shown in fig. 5, more than one set of balls III33 is provided between the driving sleeve 29 and the ratchet seat 88, each set of balls III33 including more than one ball III33. The function of the balls III33 is to reduce the axial movement friction between the drive sleeve 29 and the ratchet seat 88. In this embodiment, the driving sleeve 29 and the ratchet seat 88 are provided with a sliding key 30 and a sliding groove at corresponding positions, the sliding key 30 on the driving sleeve 29 and the sliding groove on the ratchet seat 88 form a channel for accommodating the ball III33, and the ball III33 is placed in the channel. In order to further reduce friction force and reduce manufacturing difficulty and processing cost, the channel for accommodating the ball III33 in the embodiment is a blind hole formed in a position corresponding to the sliding grooves of the sliding key 30 and the ratchet seat 88 of the driving sleeve 29, the ball III33 is placed in the blind hole and matched with the blind hole, the opening end of the blind hole is provided with a baffle 34, the baffle 34 is positioned by a clamping ring, the baffle 34 can be fixed on the ratchet seat 88 by a fastener such as a screw, a pin shaft and the like, and the baffle 34 has the function of preventing the ball III33 from rolling out of the blind hole. The baffle 34 is provided with 3 positioning pins 20, and the function of the positioning pins 20 is to prevent the baffle 34 from rotating, so that the contact between the groove of the baffle 34 and the sliding key 30 on the transmission sleeve 29 is avoided, and the follow-up effect between the ratchet seat 88 and the transmission sleeve 29 is influenced.

As shown in fig. 1, 3 and 5, in this embodiment, three sliding keys 30 are uniformly distributed on the side surface of the transmission sleeve 29, and other embodiments may also have other groups of sliding keys 30; a set of balls III33 is provided on each side of each sliding key 30 between the driving sleeve 29 and the ratchet seat 88, each set of balls III33 comprising five balls III33. The function of this is to further reduce the axial friction between the drive sleeve 29 and the ratchet seat 88 while ensuring a balanced torque transmission and axial movement between the drive sleeve 29 and the ratchet seat 88. In other embodiments, other sets of balls III33 are provided between the drive sleeve 29 and the ratchet seat 88, each set of balls III33 including other numbers of balls III33.

As shown in fig. 1, 3 and 5, one or more ratchet mechanisms are provided within the ratchet seat 88. The function of the plurality of ratchet mechanisms is to further ensure torque transfer balance and reduce the stress of the individual ratchet teeth after ratchet seat 88 is engaged with ratchet ring 87 of driven gear set 12 via ratchet teeth I23. In this embodiment, three ratchet mechanisms are provided in the ratchet seat 88, each of which is disposed between two sets of slide keys 30 on the side surface of the drive sleeve 29. In another embodiment, other numbers of ratchet mechanisms are provided within the ratchet seat 88.

As shown in fig. 3, 4 and 5, in the present embodiment, the link mechanism 2 includes a displacement rod 58, a lever 26 and a ratchet I23, two ends of the displacement rod 58 are respectively connected with the roller 27 and the lever 26 through a pin, the lever 26 is rotationally fixed on a support 86 in a ratchet seat 88 through a pin and a torsion spring I63, a limit groove 72 is formed in the ratchet I23, a limit block 71 slidably disposed in the limit groove 72 is fixed on the lever 26, the limit groove 72 is formed in the ratchet I23, and a spring seat 59 is disposed between the ratchet I23 and the spring III 25. The link mechanism 2 has low cost and high transmission efficiency. In another embodiment, the linkage mechanism 2 may be another mechanism that can move up and down through the roller 27 to drive the ratchet I23 to stretch and retract, such as a four-bar linkage mechanism 2. The torsion spring I63 is used for ensuring that the track surface of the roller 27 is always attached to the track surface of the transmission sleeve 29, when the roller 27 is positioned at the center of the recess 64 of the transmission sleeve 29, if the rotating speed of the ratchet seat 88 is greater than that of the ratchet ring 87, the ratchet I23 is compressed by the ratchet inclined surface of the ratchet II50 and moves up and down, the link mechanism 2 and the roller 27 are kept motionless, noise is reduced, and the reliability and the service life of the link mechanism 2 are improved. When the roller 27 is positioned at the high level on both sides of the recess 64, the spring III25 and the torsion spring I63 are in a compressed state, and the ratchet I23 is retracted into the ratchet seat 88.

As shown in fig. 3 and 4, in this embodiment, in order to reduce manufacturing difficulty and processing cost, the ratchet seat 88 is provided with the mounting hole 24 therein, the link mechanism 2 further includes the ratchet sleeve 22 and the support 86 both fixed in the mounting hole 24 by the positioning ring 73, the ratchet I23 is slidably disposed in the ratchet sleeve 22, and the lever 26 is movably disposed in the support 86. During installation, the lever 26 passes through the support 86, the ratchet sleeve 22 is sleeved on the ratchet I23, the three groups of connecting rod mechanisms 2 are firstly arranged in the ratchet seat 88, the ratchet sleeve 22 and the support 86 are sequentially fixed in the mounting hole 24 through the positioning ring 73, so that the manufacturing difficulty and the processing cost are reduced, the use reliability is improved, the mounting and dismounting difficulty is reduced, the purpose of arranging the connecting rod mechanisms 2 in the ratchet seat 88 is achieved, and the positioning ring 73 is positioned through the clamping ring.

As shown in fig. 1, in order to reduce the overall size of the transmission as much as possible, the position of part of the structure of the input end 4 is changed from the left side of the driving gear set 11 to the right side of the driving gear set 11; the first-gear driving gear 19, the second-gear driving gear 18, the third-gear driving gear 17, the fourth-gear driving gear 16, the fifth-gear driving gear 15 and the gear IV61 of the primary driving gear set 11 are respectively and independently designed and assembled to form a whole; the driving gears of five gears and the gear IV61 are integrated into a whole, and can be formed into a whole through fastening pieces, welding and the like, and the transmission is assembled with the spline shaft 5 through the spline, so that the size of the transmission is reduced, the transmission is more convenient to load and arrange, and the aesthetic effect is improved. In order to ensure that the gear III66 does not interfere with the inner ring of the driving gear at the first gear position, the diameter of the gear III66 can be properly adjusted, and the realization of transmission can be met by properly right-shifting the axial position of the gear IV61 in the inner ring of the driving gear or properly reducing the diameter of the gear IV 61; the transmission ratio of the input end 4 can be comprehensively adjusted through the gear I3, the gear II6, the gear III66 and the gear IV61, so that the optimal transmission ratio is obtained.

In order to minimize the overall dimension of the transmission, the ratchet seat 88 and the transmission sleeve 29 are reversely installed, three groups of sliding plates 76 with ball mounting grooves 46 are additionally arranged on the outer circle of the bracket I65 at intervals of 120 degrees, the sliding plates 76 and the bracket I65 are integrally designed, and balls IV89 arranged in the ball mounting grooves 46 on the sliding plates 76 are matched with the axial grooves 62 on the output seat 77. When the transmission sleeve 29 moves axially, the transmission sleeve 29 drives the support I65 and the ball IV89 in the ball mounting groove 46 on the sliding plate 76 to move axially in the axial groove 62 on the output seat 77 to realize synchronous rotation and gear shift, meanwhile, the ball IV89 transmits the power on the ratchet ring 87 of a certain gear driven gear to the output seat 77 through the ratchet II50, the ratchet I23, the ratchet seat 88, the transmission sleeve 29 and the support I65, and then the power is transmitted to the rear wheel of a bicycle or a motorcycle through the spline fit of the output seat 77 and the end cover 60 to push the vehicle to move forwards. The slide plate 76 and the bracket I65 may be connected by welding, bolts, or the like.

Three groups of gear stabilizing assemblies are arranged on two sides of the ball mounting groove 46 of the three groups of sliding plates 76 arranged on the support I65, each group of gear stabilizing assemblies comprises an upshift stabilizing assembly and a downshift stabilizing assembly, the gear stabilizing assemblies on the sliding plates 76 correspond to the gear stabilizing assemblies on the output seat 77, and form a matching relationship, namely, the downshift stabilizing assembly torsion spring II79 on the sliding plates 76 is matched with the downshift stabilizing assembly torsion spring I81 on the output seat 77, so that when a bicycle or a motorcycle runs in a certain gear, the running speed of the bicycle or the motorcycle is not lower than the set rotating speed of one gear, the bicycle or the motorcycle keeps working stably in a certain gear, and the gear stabilizing assemblies prevent the transmission sleeve 29 from moving rightwards; the upshift stabilizing assembly torsion spring IV80 on the slide plate 76 cooperates with the upshift stabilizing assembly torsion spring III83 on the output seat 77 to keep the bicycle or motorcycle stably operating in a certain gear when the bicycle or motorcycle is traveling in a certain gear at a speed not higher than the set rotational speed of the first gear, and the gear stabilizing assembly prevents the transmission sleeve 29 from moving left.

The working principle of the automatic transmission is as follows: the pedals are fixed on the input shaft 1, the rear wheels are fixed on the output shaft 52, the pedals rotate synchronously with the input shaft 1, and the rear wheels rotate synchronously with the end cover 60.

When the pedal is stepped on rapidly, the input shaft 1 drives the spline shaft 5 to rotate rapidly through the transmission mechanism, so that the driving gear, the driven gear, the ratchet telescopic mechanism, the sliding plate 76, the output seat 77 and the rear wheel are driven to rotate; when the rotation speed of the output seat 77 is slightly greater than the set rotation speed of the first gear, the three groups of transmission blocks 14 do centrifugal motion, the three groups of transmission blocks 14 compress the torsion spring II49, and the fixed pull rod I53 drives the movable pull rod II48 and the transmission sleeve 29 to move left through the transmission blocks 14. When the transmission sleeve 29 moves leftwards, the ratchet seat 88 cannot synchronously move leftwards with the transmission sleeve 29 under the inertia action, but moves rightwards relative to the transmission sleeve 29, the spring II13 is compressed, the roller 27 of the ratchet mechanism is lifted upwards along the right inclined plane of the concave 64 on the transmission sleeve 29 and then moves rightwards along the horizontal section, the connecting rod mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88 and separate from the meshed ratchet ring 87 of the driven gear, and meanwhile, the ratchet I23 compresses the spring III25 through the spring seat 59; when the transmission sleeve 29 is about to reach the position of the first gear, the moving speed is gradually reduced, the ratchet seat 88 is under the continuous thrust of the spring II13, the roller 27 moves leftwards at the right horizontal section of the recess 64 of the transmission sleeve 29, when the roller 27 moves to the top edge of the right side of the recess 64 of the transmission sleeve 29, the ratchet I23 axially enters the meshing area of the first gear high II50 a small amount, the ratchet I23 is not outwards extended because the roller 27 is still at the right horizontal section of the recess 64 of the transmission sleeve 29, and when the roller 27 continues to move leftwards to enter the central position of the recess 64 of the transmission sleeve 29, the ratchet seat 88 drives the ratchet I23 to move leftwards while the link mechanism 2 moves to be aligned with the axial position of the ratchet ring 87 of the first gear high driven gear; simultaneously, the ratchet I23 extends outwards under the pushing of the spring III25, and when the large diameter point 92 of the high first-gear ratchet ring 87 is matched with the ratchet I23, the ratchet I23 extends outwards smoothly, so that power transmission can be realized; if the small diameter point 91 of the ratchet II50 is matched with the ratchet I23 at the moment, the ratchet I23 is limited after a small amount of overhanging; when the rotating speed of the first-gear ratchet ring 87 is higher than that of the ratchet seat 88, the ratchet I23 slides backwards along the ratchet inclined surface of the ratchet II50 to a large diameter point 92, and simultaneously, the ratchet I23 extends outwards under the pushing of the spring III25 to form matched transmission power; if the rotating speed of the first gear ratchet ring 87 is higher than that of the ratchet seat 88 at the moment, the ratchet I23 is compressed by the ratchet inclined surface of the ratchet II50, the ratchet I23 compresses the spring III25, when the ratchet seat 88 continuously rotates, the spring III25 and the ratchet I23 repeatedly compress and return until the pedal is stepped to enable the rotating speed of the ratchet ring 87 of the first gear driven gear to be higher than that of the ratchet seat 88, and the ratchet ring 87 drives the ratchet seat 88 to transmit torque; the speed of the input shaft 1 is unchanged, but the bicycle running speed will be in accordance with the set high first gear speed. Spring I28 and spring II13 are suitably prestressed when the roller 27 on the ratchet seat 88 is in the rest position.

When the rotation speed of the output seat 77 is slightly less than the set rotation speed of one gear, vector resultant force of the three groups of transmission blocks 14 and the torsion spring II49 pushes the power block 14, the fixed pull rod I53 and the movable pull rod II48 to drive the transmission sleeve 29 to move rightwards, and the transmission block 14 pushes the support seat 57 to move rightwards along the guide rod 45 on the support seat 57 towards the center of the support shaft 51, namely, the transmission block 14 rotates anticlockwise around the hinge support I54 under the control of the fixed pull rod I53. When the transmission sleeve 29 moves rightwards, the ratchet seat 88 cannot synchronously move rightwards with the transmission sleeve 29 under the inertia action, but moves leftwards relative to the transmission sleeve 29, the spring I28 is compressed, the roller 27 of the ratchet telescopic mechanism is lifted upwards along the left inclined plane of the concave 64 on the transmission sleeve 29 and then continues to move leftwards along the horizontal section, the connecting rod mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88 and separate from the meshed ratchet ring 87 of the driven gear, and meanwhile, the ratchet I23 pushes the spring seat 59 to compress the spring III25; when the transmission sleeve 29 is about to reach the lower first gear position for decelerating movement, the ratchet seat 88 is acted by the continuous thrust of the spring I28, the roller 27 moves rightward at the left horizontal section of the recess 64 of the transmission sleeve 29, when the roller 27 moves to the left top edge of the recess 64 of the transmission sleeve 29, the ratchet I23 axially enters the meshing area of the ratchet II50 a small amount, because the roller 27 is still at the left horizontal section of the recess 64 of the transmission sleeve 29, the ratchet I23 does not extend, when the roller 27 moves rightward and enters the central position of the recess 64 of the transmission sleeve 29, the link mechanism 2 moves while the ratchet seat 88 drives the ratchet I23 to move rightward and aligns with the axial position of the ratchet II50 of the lower first gear driven gear, and meanwhile, the ratchet I23 extends under the pushing of the spring III25, when the large diameter point 92 of the lower first gear ratchet II50 is matched with the ratchet I23, the ratchet I23 extends smoothly, and power transmission can be realized; if the small diameter point 91 of the ratchet II50 is matched with the ratchet I23 at the moment, the ratchet I23 is limited after a small amount of overhanging; when the rotation speed of the first-gear ratchet ring 87 is lower than that of the ratchet seat 88, the ratchet I23 slides backwards along the ratchet inclined surface of the ratchet II50 to a large diameter point 92, and simultaneously, the ratchet I23 extends outwards under the pushing of the spring III25 to form matched transmission power; if the rotation speed of the first gear ratchet ring 87 is lower than that of the ratchet seat 88 at the moment, the ratchet I23 slides forwards on the ratchet inclined surface of the ratchet II50 to be compressed, the ratchet I23 pushes the spring seat 59 to compress the spring III25, when the ratchet seat 88 continuously rotates, the spring III25 and the ratchet I23 repeatedly compress and return until the pedal is stepped to enable the rotation speed of the ratchet ring 87 of the first gear driven gear to be lower than that of the ratchet seat 88, and the ratchet ring 87 drives the ratchet seat 88 to transmit torque; the speed of the input shaft 1 is unchanged, but the bicycle running speed will be in accordance with the set low first gear speed.

In the utility model, the right end face of each gear driven gear is provided with the inner ring of the bearing 35, the left end face of each gear driven gear is provided with the outer ring of the bearing 35, and the gears are matched with each other through the installation of the inner ring of the bearing 35, the outer ring of the bearing 35 and the roller bearing 35, so that the rotation positioning is realized, and when the driven gears and the driving gears are meshed for rotation, the driven gears rotate according to the respective transmission ratios.

As shown in fig. 1, 3 and 6, the function of the ball IV89 is: the balls IV89 mounted in the ball mounting grooves 46 on the slide plate 76 are matched with the axial grooves 62 on the output seat 77, and the balls IV89 can drive the output seat 77 to synchronously rotate circumferentially while shifting gears along with the left or right movement of the bracket I65. In this embodiment, the balls IV89 are three sets of two balls IV89, and in other embodiments, the number of balls IV89 in each set may include one or more other numbers, and each displacement transmission assembly includes the slide plate 76, the ball mounting groove 46, the balls IV89, and the axial groove 62. In another embodiment, the displacement transmission assembly can drive the output seat 77 to rotate circumferentially without moving axially when the bracket I65 moves left or right. In this embodiment, the axial slot 62 length meets the one to five shift requirements.

In one embodiment of the present utility model, three centrifugal transmission assemblies are arranged in the output seat 77 with the supporting shaft 51 as the center and at intervals of 120 °, and the transmission blocks 14 can be made of materials with higher density according to requirements, so as to meet the requirements of arrangement in a limited space and realization of functions, and be beneficial to reducing the overall weight of the transmission and obtaining the optimal gear shifting effect.

As shown in fig. 1, in one embodiment of the present utility model, the driving gear set 11 includes a five-gear driving gear 15, a four-gear driving gear 16, a three-gear driving gear 17, a two-gear driving gear 18, and a first-gear driving gear 19 in order from left to right, and the driven gear set 12 includes a five-gear driven gear 36, a four-gear driven gear 37, a three-gear driven gear 38, a two-gear driven gear 39, and a first-gear driven gear 40 in order from left to right, which correspond to the driving gear set 11. In another embodiment, the number of driving gears included in the driving gear set 11 is another, the number of driven gears included in the driven gear set is another, and so on.

As shown in fig. 6, 8 and 9, three sets of gear stabilizing assemblies are further arranged on the output seat 77 and the sliding plate 76 at intervals of 120 degrees, and each set of gear stabilizing assemblies comprises a gear-down stabilizing assembly and a gear-up stabilizing assembly; the gear-reducing stabilizing assembly comprises a torsion spring I81, a torsion spring II79, a positioning seat I82, a positioning seat II78, a limiting hole II21 and more than two limiting holes I85 formed in the output seat 77, wherein the limiting holes II21 are formed in the sliding plate 76, the torsion spring I81 is fixed on the positioning seat I82 and corresponds to the limiting holes I85, the torsion spring II79 is fixed on the positioning seat II78 and corresponds to the limiting holes II21, the positioning seat I82 is fixed on the output seat 77, and the positioning seat II78 is fixed on the sliding plate 76; the upshift stabilizing assembly comprises a torsion spring III83, a torsion spring IV80, a positioning seat III84, a positioning seat IV42, a limiting hole IV41 and more than two limiting holes III31 formed on the output seat 77, wherein the limiting holes IV41 are formed on the sliding plate 76, the torsion spring III83 is fixed on the positioning seat III84 and corresponds to the limiting holes III31, the torsion spring IV80 is fixed on the positioning seat IV42 and corresponds to the limiting holes IV41, the positioning seat III84 is fixed on the output seat 77, and the positioning seat IV42 is fixed on the sliding plate 76; torsion spring I81 is mounted in the opposite direction to torsion spring III83, and torsion spring II79 is mounted in the opposite direction to torsion spring IV 80. Torsion spring I81 is in partial contact with torsion spring II 79; torsion spring III83 is in partial contact with torsion spring IV 80. The gear stabilizing assembly is operative to stabilize the output socket 77 in a certain set rotational speed range, and the shaftless automatic transmission can be continuously operated in a certain gear, maintaining the gear relatively stable, i.e., maintaining the ratchet teeth I23 in engagement with the ratchet teeth II50 of the ratchet ring 87 of the driven gear of the certain gear. In this embodiment, three sets of gear stabilizing assemblies are disposed at positions corresponding to 120 ° circumferential intervals between the outer side of the bracket I65 and the inner side of the output seat 77.

In this embodiment: positioning seat I82, positioning seat III84 set on the outer circumference of output seat 77, positioning seat II78, positioning seat IV42 set on the inner circumference of slide plate 76, and in other embodiments, other manners or other positions may be used to implement the functions of the downshift and upshift stabilizing assemblies.

In this embodiment, the number of sets of gear stabilizing assemblies is three, and the three sets of gear stabilizing assemblies are circumferentially and uniformly distributed. As shown in fig. 6, the limiting hole I85 and the limiting hole III31 each include four, the torsion spring I81 and the torsion spring III83 each include four, the limiting hole II21 and the limiting hole IV41 each include one, and the torsion spring II79 and the torsion spring IV80 each include one. In fig. 8, the solid line position of the limiting hole II21 and the torsion spring II79 is a second gear, and the broken line position is a third gear; in fig. 9, the solid line position of the limiting hole IV41 and the torsion spring IV80 is a first gear, and the broken line position is a second gear. In fig. 8, the first gear position is provided with no torsion spring I81 and no limiting hole I85, and the torsion spring I81 and the limiting hole I85 are respectively positioned in the second gear, the third gear, the fourth gear and the fifth gear from right to left; in fig. 9, the fifth gear position has no torsion spring III83 and no limiting hole III31, and the torsion spring III83 and the limiting hole III31 are located in the first gear, the second gear, the third gear and the fourth gear from right to left respectively. When the torsion spring II79 is positioned at the second gear, the third gear, the fourth gear and the fifth gear, the contact part of the torsion spring II79 is always positioned at the left side of the torsion spring I81 of each gear, as shown in the position relationship between the broken line position of the torsion spring II79 at the second gear and the third gear and the torsion spring I81 of the second gear and the third gear in FIG. 8; when the torsion spring IV80 is located at the first gear, the second gear, the third gear and the fourth gear, the contact portion of the torsion spring IV80 is always located at the right side of the torsion spring III83 of each gear, such as the positional relationship between the broken line torsion spring IV80 of the first gear and the second gear and the torsion spring III83 of the first gear and the second gear in fig. 9.

In other embodiments, the numbers of the driving gear, the driven gear, the gear-reducing stabilizing component, the gear-increasing stabilizing component, the limiting hole I85, the limiting hole II21, the limiting hole III31, the limiting hole IV41, the torsion spring I81, the torsion spring II79, the torsion spring III83 and the torsion spring IV80 can be other numbers matched with the numbers of the driving gear and the driven gear, and the number of the gear-increasing stabilizing component can be other numbers. In this embodiment, the five-gear driven gear 36, the four-gear driven gear 37, the three-gear driven gear 38, the two-gear driven gear 39 and the corresponding ratchet ring 87 on the first-gear driven gear 40 are respectively the same in parameter structure as the five-gear ratchet ring 87, the four-gear ratchet ring 87, the three-gear ratchet ring 87, the two-gear ratchet ring 87 and the one-gear ratchet ring 87, as shown in fig. 5.

In one embodiment of the present utility model, the ratchet ring 87 has a plurality of ratchet teeth II50, and the small diameter point 91 of the ratchet ring 87 refers to the position of the ratchet surface of the ratchet teeth II50 closest to the center of the ratchet ring 87; the large diameter point 92 of the ratchet ring 87 refers to the position of the ratchet surface of the ratchet II50 farthest from the center of the ratchet ring 87.

As shown in FIG. 1, when the rotation speed of the output seat 77 is reduced to be slightly lower than a certain lower gear set rotation speed or the rotation is stopped, the vector resultant force of the transmission block 14 and the torsion spring II49 drives the fixed pull rod I53 and the movable pull rod II48 to push the hinge support II44 and the transmission sleeve 29 to move rightwards through the transmission block 14, the three groups of transmission blocks 14 and the torsion spring II49 are in time sharing to overcome the spring force of the three groups of gear stabilizing assemblies, so that the transmission sleeve 29 drives the ratchet I23 on the ratchet seat 88 to accurately reach the set gear position, the vector resultant force of the transmission block 14 and the torsion spring II49 is balanced again, and the transmission continuously works stably in a certain lower gear.

As shown in fig. 1, 2 and 6, the torsion spring II49 has a suitable prestress to the driving block 14, and when the bicycle or motorcycle is stopped, the torsion spring II49 needs to ensure that the driving block 14 is attached to the outer surface of the supporting seat 57 at any position, as shown in fig. 6, where the driving block 14 is located in the solid line position.

As shown in fig. 1, the transmission mechanism comprises a transmission shaft 69, and an input shaft 1 and a spline shaft 5 which are respectively arranged at two ends of the transmission shaft 69, wherein the input shaft 1 and the spline shaft 5 are parallel; the two ends of the transmission shaft 69 are respectively fixed with a gear II6 and a gear III66 through splines, the input shaft 1 is fixed with a gear I3 meshed with the gear II6 through splines, and the driving gear set 11 is integrated with a gear IV61 meshed with the gear III 66. The transmission mechanism functions to transmit the power of the input shaft 1 to the spline shaft 5, thereby rotating the driving gear set 11 mounted on the spline shaft 5.

Further, the input shaft 1 and the spline shaft 5 are provided with a supporting seat 7 through bearing sleeves. The support base 7 is used for supporting the transmission shaft 69. In another embodiment, the transmission mechanism may be other transmission mechanisms capable of driving the spline shaft 5 to rotate under the condition that the input shaft 1 rotates. The transmission shaft 69 is perpendicular to the input shaft 1 and the spline shaft 5.

The transmission sleeve 29 of the ratchet telescopic mechanism is sleeved on the supporting shaft 51, and a ball II32 is arranged between the transmission sleeve 29 and the supporting shaft 51. In this embodiment, three sets of balls II32 are provided, each set of balls II32 being disposed at 120 ° intervals, and in other embodiments, other sets of balls II32 may be provided, which are capable of moving the driving sleeve 29 on the support shaft 51.

The supporting shaft 51 is installed on the box body II43 and the end cover 60 through bearings, the right end of the supporting shaft 51 is provided with the transmission sleeve 29 and the ratchet seat 88 through the ball II32, the left end of the supporting shaft 51 is provided with the supporting seat 57 and the centrifugal transmission component through the ball I56, the supporting shaft 51 has the function of ensuring that the central axes of the transmission sleeve 29, the ratchet seat 88 and the through holes of the ratchet ring 87 formed by the centrifugal transmission component and the driven gear group coincide, the left and right movement of the transmission sleeve 29 is realized, the left and right follow-up of the ratchet seat 88 creates conditions, and the gear shifting of the ratchet mechanism is realized for the centrifugal transmission mechanism.

Spring I28, spring II13 and spring III25 are all tower springs, and in other embodiments, spring I28, spring II13, spring III25 may be other types of springs that function identically to the tower springs in the present utility model.

In order to protect the gear transmission mechanism from being affected by invasion of foreign objects, meanwhile, the gear transmission mechanism is ensured not to cause injury or influence to a user in the using process, lubricating oil is filled in the box body, friction resistance of the transmission mechanism is reduced, transmission efficiency can be improved, working reliability of the mechanism, sensitivity of movement and accuracy of gear shifting are further improved, and the box body of the shaftless automatic transmission device comprises a box body I10 for mounting an input shaft 1, a gear I3 and a gear II6, and a box body II43 for mounting and fixing a main gear, a driven gear, a gear shifting mechanism and the like.

In order to ensure that the ratchet I23 firstly axially enters a certain gear ring 87 to be matched during gear shifting, the roller 27 moves to the center of the concave 64 at the highest position on the left side or the right side of the concave 64, and the overhanging length of the ratchet I23 can be properly shortened on the premise that three groups of ratchet I23 meet the requirement of contact strength and the inclined surface angle of the concave 64 is kept unchanged, namely, the width of the concave 64 is reduced by reducing the depth of the concave 64, and the overhanging position of the ratchet I23 is delayed; on the premise of ensuring that each function of the connecting rod is realized, the proportion of the left lever 26 of the pin shaft to the right lever 26 of the pin shaft is properly increased to reduce the depth of the concave 64 and the width of the concave 64 so as to delay the overhanging position of the ratchet I23, and the axial width of the ratchet I23 can be properly increased to ensure that the ratchet I23 firstly axially enters the meshing area of a certain gear ratchet ring 87 to be matched when the gear is changed, as shown in figures 1 and 3.

The working principle of the integral shaftless automatic speed changing device is as follows;

the gear shifting mechanism comprises: the three groups of the hinged support I54, the fixed pull rod I53, the transmission block 14, the torsion spring II49, the movable pull rod II48, the hinged support II44, the sliding plate 76, the ball IV89, the torsion spring I81, the torsion spring II79, the torsion spring III83 and the torsion spring IV80 are respectively, and the transmission sleeve 29, the ratchet seat 88 and the components, the spring I28, the spring II13, the bracket I65 and the bracket II67 are respectively. The torsion spring II49 has proper pretightening force at the initial position, when the output seat 77 stops rotating, the torsion spring II49 can push the transmission block 14 back to the initial position, namely, the solid line position of the transmission block 14 in fig. 1, 2 and 6, the transmission sleeve 29 is in movable fit with the support shaft 51 through three groups of balls II32, the rotation and axial movement can be realized, the support I65 and the support II67 are sleeved at the left end and the right end of the transmission sleeve 29, the snap ring is positioned, the transmission sleeve 29 is matched with the ratchet seat 88 through the sliding key 30 and the sliding groove, the circumferential positioning is realized through the connection of the balls III33, and the axial elastic positioning of the ratchet seat 88 is realized through the springs I28 and II13 fixed on the ratchet seat 88.

As shown in fig. 9, the upshift stabilizing assembly operates in: when the rotating speed of the ratchet seat 88 is slightly higher than the set rotating speed of the first gear, the centrifugal force of the transmission block 14 is larger than the elastic force of the torsion spring II49, the transmission block 14 compresses the torsion spring II49 through the fixed pull rod I53 and the movable pull rod II48, the movable pull rod II48 drives the gear shifting mechanism to move left through the hinged support II44, the torsion spring IV80 on the sliding plate 76 is blocked by the torsion spring III83, the component force of the centrifugal force of the three groups of transmission blocks 14 in the axial direction can overcome the blocking of the three groups of torsion springs III83, the torsion spring IV80 is supported by the wall of the limiting hole IV41, the torsion spring III83 is pushed to rotate clockwise around the mounting pin for a certain angle, the torsion spring IV80 passes through the torsion spring III83 and enters a first gear area, and the torsion spring III83 is then reset and attached to the limiting hole III 31; before displacement is completed, the torsion spring II79 is blocked by the torsion spring I81, the torsion spring I81 is supported by the wall of the limiting hole I85, the torsion spring II79 is pushed to rotate clockwise around the mounting pin for a certain angle, the torsion spring II79 enters the left side of the torsion spring I81 to displace a small amount and then stops, namely, the vector resultant force of the transmission block 14 and the torsion spring II49 in the axial direction reaches balance again, the torsion spring II79 is attached to the wall of the limiting hole II21 in a return mode, and the upshift stabilizing assembly completes one upshift.

As shown in fig. 8, the downshift stabilization assembly operates: when the rotating speed of the ratchet seat 88 is slightly lower than a certain low one-gear set rotating speed, the elasticity of the torsion spring II49 is larger than the centrifugal force of the transmission block 14, the torsion spring II49 pushes the transmission block 14 to move towards the center of the supporting shaft 51 through the fixed pull rod I53 and the movable pull rod II48, the movable pull rod II pushes the transmission sleeve 29, the sliding plate 76 and other gear shifting mechanisms to move rightwards through the hinged support II44, the gear-reducing stable component torsion spring II79 on the sliding plate 76 is blocked by the torsion spring I81, the thrust of the three torsion springs II49 can overcome the blocking of the three torsion springs I81, the torsion spring II79 is supported by the wall of the limiting hole II21 to push the torsion spring I81 to rotate anticlockwise by a certain angle around the mounting pin, the torsion spring II79 penetrates through the torsion spring I81 to enter a low one-gear area, and the torsion spring I81 is then returned and attached to the wall of the limiting hole I85; before the shift mechanism is about to complete displacement, the torsion spring IV80 is blocked by the torsion spring III83, the torsion spring III83 is supported by the wall of the limiting hole III31, the torsion spring IV80 is pushed to rotate anticlockwise by a certain angle around the mounting pin, the torsion spring IV80 passes through the torsion spring III83 to move a small amount of right, and then the shift mechanism stops, namely, the vector resultant force of the transmission block 14 and the torsion spring II49 in the axial direction reaches balance again, the torsion spring IV80 is attached to the wall of the limiting hole IV41 in a return mode, and the shift-down stabilizing assembly completes one shift down.

In order to reduce the reverse motion resistance of the torsion springs II79 and IV80, the torsion force of each three groups of torsion springs is set to be smaller than the torsion force of the torsion springs I81 and III83, and meanwhile, in order to improve the rigidity of the torsion springs II79 and IV80, steel sheets with larger rigidity can be adopted to be made into the shape identical to that of the torsion springs II79 and IV80, and the torsion springs and the steel sheets are connected into a whole so as to meet the requirements of small torsion force and large rigidity of the torsion springs II79 and IV80, and the torsion springs I81 and III83 are pushed to rotate by means of the walls of the limiting holes II21 and IV 41.

When the rotating speed of the output seat 77 is not greater than the set rotating speed of the first gear, vector resultant force of the transmission block 14 and the torsion spring II49 drives the transmission block 14 to move away from the supporting shaft 51, the transmission block 14 drives the fixed pull rod I53 and the movable pull rod II48 to rotate around the hinged support I54 and the hinged support II44, the hinged support II44 drives the gear shifting mechanisms such as the transmission sleeve 29 to move left, the torsion spring IV80 moves left to a small extent to be in contact with the torsion spring III83, at the moment, the torsion spring IV80 cannot push the torsion spring III83 to rotate, and the ratchet I23 moves left to a small extent to be axially dislocated with the meshing area of a certain gear ratchet II50, so that torque transmission of the ratchet I23 and the ratchet II50 is not influenced; when the rotation speed of the output seat 77 is not lower than the first gear set rotation speed, the vector resultant force of the transmission block 14 and the torsion spring II49 drives the transmission block 14 to move towards the direction of the supporting shaft 51, the transmission block 14 drives the fixed pull rod I53 and the movable pull rod II48 to rotate around the hinged support I54 and the hinged support II44, the hinged support II44 drives the gear shifting mechanisms such as the transmission sleeve 29 to move rightwards, the torsion spring II79 moves rightwards to be in contact with the torsion spring I81, at the moment, the torsion spring II79 cannot push the torsion spring I81 to rotate, the ratchet I23 moves rightwards to be slightly staggered with the meshing area of a certain gear ratchet II50 axially, and torque transmission is not influenced, so that the arrangement of the torsion spring I81, the torsion spring II79, the torsion spring III83 and the torsion spring IV80 can ensure that a reasonable rotation speed range is provided for each gear of a bicycle or a motorcycle, and conditions are created for stable operation of the transmission. Another function of the gear stabilizing assembly is: when the rotating speed of the ratchet seat 88 is slightly higher than the high first gear set rotating speed or slightly lower than the low first gear set rotating speed, the vector resultant force of the three groups of transmission blocks 14 and the torsion spring II49 breaks through the blocking of a certain gear torsion spring III83 or torsion spring I81, and then the rotating sleeve 29 is driven to move leftwards or rightwards rapidly, so that conditions are created for the follow-up effect of the ratchet telescopic mechanism.

And (3) stress and motion analysis of the ratchet telescopic mechanism: when the vector resultant force of the transmission block 14 and the torsion spring II49 drives the transmission sleeve 29 to move leftwards or rightwards rapidly, the ratchet seat 88 cannot move leftwards or rightwards synchronously along the transmission sleeve 29 under the inertia effect, but moves rightwards or leftwards relative to the transmission sleeve 29, the roller 27 on the ratchet seat 88 lifts upwards along the right side or left side inclined plane of the recess 64 of the transmission sleeve 29 and continuously moves rightwards or leftwards along the horizontal section to compress the spring II13 or the spring I28, and when the spring II13 or the spring I28 is compressed to a set limit position, the ratchet seat 88 and the transmission sleeve 29 synchronously move leftwards or rightwards; namely: the relative movement speed of the ratchet seat 88 with respect to the support shaft 51 varies at the same time: in the process that the roller 27 of the ratchet seat 88 lifts along the right side or the left side inclined plane of the recess 64 of the transmission sleeve 29, the horizontal component force generated by the inclined plane affects the ratchet seat 88, the ratchet seat 88 starts to move leftwards or rightwards, or starts to move leftwards or rightwards, when the ratchet seat 88 continues to move rightwards or leftwards along a horizontal track to compress the spring II13 or the spring I28, the movement speed of the ratchet seat 88 rightwards or leftwards relative to the transmission sleeve 29 is gradually reduced to zero by the continuous reaction force of the spring II13 or the spring I28, and meanwhile, the movement of the ratchet seat 88 relative to the support shaft 51 is a uniform acceleration movement process of leftwards or rightwards, namely, the movement speed of the ratchet seat 88 leftwards or rightwards relative to the support shaft 51 is gradually increased from zero, and when the spring II13 or the spring I28 is compressed to a set limit position, the movement speed of the ratchet seat 88 leftwards or rightwards is approximately equal to the transmission sleeve 29. When the vector resultant force of the driving block 14 and the torsion spring II49 drives the torsion spring IV80 or the torsion spring II79 mounted on the sliding plate 76 to push the torsion spring III83 or the torsion spring I81 mounted on the output seat 77, the speed and the kinetic energy are maximum, and before the driving sleeve 29 reaches the next gear, the vector resultant force of the driving block 14 and the torsion spring II49 needs to overcome the reverse thrust required by the torsion spring II79 in the gear-down stabilizing assembly or the torsion spring IV80 in the gear-up stabilizing assembly, when the next gear is reached, the axial speed of the driving sleeve 29 is zero, and the vector resultant force of the driving block 14 and the torsion spring II49 reaches the force balance again. Therefore, in the whole gear shifting process of the transmission sleeve 29, after the vector resultant force of the transmission block 14 and the torsion spring II49 breaks through the blocking of the torsion spring III83 or the torsion spring I81, the whole motion process is a uniform deceleration motion process, the gear stabilizing assembly driven by the transmission sleeve 29 and the sliding plate 76 firstly reaches a preset speed gear, and then the ratchet seat 88 drives the ratchet I23 to enter a preset gear ratchet ring 87 to be matched with the gear ratchet II50 for transmitting power; the roller 27 on the ratchet seat 88 returns to the balance point, and the springs II13 and I28 have proper prestress when the ratchet seat 88 is at the balance point, and meanwhile, the ratchet seat 88 is stable at the balance point to transmit torque due to the blocking and limiting effects of the inclined surface of the concave 64 on the roller 27.

Override downshifting: because the bicycle or motorcycle is required to be braked and decelerated suddenly when running, the centrifugal force of the power block 14 is reduced along with the rotating speed, the energy of the torsion spring II49 is not balanced, the torsion spring II49 drives the fixed pull rod I53 and the movable pull rod II48 to rotate around the hinge support pin shaft through the power block 14, the transmission sleeve 29 is pushed to move right quickly, the transmission sleeve 29 drives the torsion springs on the sliding plate 76 to pass through each gear torsion spring on the output seat 77 in a separated mode due to the fact that the transmission sleeve 29 is relatively longer in the process of gear-down motion, if the ratchet seat 88 drives the roller 27 to return to the depression 64 in the process of gear-down motion of the transmission sleeve 29 in a gear-down mode, the ratchet I23 extends outwards, and the ratchet I23 passes through the ratchet ring 87 after the ratchet I23 extends outwards when meeting a certain gear ratchet II50 big diameter point 92 to be penetrated in the moving process; if the ratchet I23 meets the large diameter point 92 of the non-ratchet II50, the ratchet I23 is blocked by the ratchet II50, the ratchet seat 88 moves leftwards relative to the driving sleeve 29 again, the roller 27 lifts upwards and leftwards along the left inclined plane of the concave 64, the ratchet I23 is retracted into the ratchet seat 88 again, the ratchet seat passes through the ratchet blocking gear ring, when the driving sleeve 29 reaches a certain gear, the movement is stopped, namely the vector resultant force of the driving block 14 and the torsion spring II49 reaches balance again, the ratchet seat 88 returns to the balance point again, and the ratchet I23 is matched with the ratchet blocking II50 to transmit torque.

An automatic transmission embodiment is as follows:

and (3) a gear increasing process:

starting to ride the bicycle, stepping on the pedal drives the input shaft 1 to rotate, the input shaft 1 drives the gear I3 through a spline, the gear I3 is meshed with the gear II6, the gear II6 drives the transmission shaft 69 through a spline, the transmission shaft 69 drives the gear III66 through a spline, the gear III66 is meshed with the gear IV61, the gear IV61 and the driving gear set 11 are integrally arranged on the spline shaft 5, the gear IV61 drives the first-gear driving gear 19, the second-gear driving gear 18, the third-gear driving gear 17, the fourth-gear driving gear 16 and the fifth-gear driving gear 15 to synchronously rotate, and accordingly the first-gear driven gear 40, the second-gear driven gear 39, the third-gear driven gear 38, the fourth-gear driven gear 37 and the fifth-gear driven gear 36 are driven to rotate according to respective transmission ratios; the gear shifting system of the automatic transmission is in a first gear position before working, the ratchet I23 is matched with the ratchet II50 of the first-gear driven gear 40, the ratchet I23 pushes the ratchet seat 88 through the ratchet sleeve 22, the ratchet seat 88 is matched and connected with the transmission sleeve 29 through the ball III33, circumferential synchronous rotation is achieved, the transmission sleeve 29 and the support I65 are positioned through the sliding key 30 and the groove connecting clamping ring, the support I65 drives the ball IV89 arranged on the sliding plate 76 to be matched with the axial groove 62 on the output seat 77 to drive the output seat 77 to synchronously rotate, the output seat 77 is matched with the end cover 60 through the installation of the spline, the end cover 60 is provided with the output shaft 52 to be matched with the rear wheel of a bicycle or a motorcycle, and the first-gear driven gear 40 pushes the gear shifting system to drive the rear wheel to rotate, and one-gear running is achieved.

When the automatic transmission works in first gear and needs to be lifted to second gear, the pedal is quickly stepped to increase the rotating speed of the input shaft 1, the ratchet II50 of the first gear driven gear 40 is matched with the ratchet I23 to enable the rotating speed of a gear shifting system to be slightly higher than the second gear set rotating speed, the vector resultant force of the three groups of transmission blocks 14 and the torsion spring II49 drives the fixed pull rod I53, the movable pull rod II48 to rotate around the hinge support I54 and the hinge support II44, the torsion spring II49 is compressed and simultaneously pulls the transmission sleeve 29 to move left, the sliding plate 76 arranged on the support I65 realizes circumferential synchronous rotation and axial movement through the matching of the ball mounting groove 46 and the ball IV89 with the axial groove 62, the outer end of the torsion spring IV80 is supported and pushed by the wall of the limit hole IV41 to enable the first gear torsion spring III83 to rotate clockwise around the mounting pin by a certain angle, the three groups of torsion springs IV80 penetrate through the first gear three groups of torsion springs III83 to enter the second gear area and continue to move left, when the ratchet I23 is about to be aligned with the second gear ratchet II50, the torsion spring II79 is blocked by the second gear torsion spring I81, the torsion spring I81 is supported by the hole wall of the limiting hole I85, the torsion spring II79 is pushed to rotate clockwise by a certain angle around the mounting pin, the three groups of torsion springs II79 pass through the second gear and three groups of torsion springs I81 to move left by a small amount and stop, the positions of the torsion springs IV80 and the torsion springs II79 formed by the broken lines in the figure 9 and the solid lines in the figure 8 are the positions of the automatic transmission when the automatic transmission works in the second gear, the rotating speed of the output seat 77 before gear shifting is slightly higher than the set rotating speed of the second gear, the vector resultant force of the three groups of the transmission blocks 14 and the three groups of the torsion springs II49 overcomes the resistance of the three groups of torsion springs III83 and the torsion springs II79 to enter the second gear in a time sharing mode, meanwhile, the centrifugal transmission assembly drives the transmission sleeve 29 to move left quickly, because the ratchet seat 88 is connected with the transmission sleeve 29 by adopting the ball III33, when the transmission sleeve 29 moves left quickly, the gear sleeve 29 can not be synchronously and rapidly moved left, but is moved right relative to the gear sleeve 29, a spring II13 arranged on the right side of a ratchet seat 88 is compressed by a bracket II67, a roller 27 continuously moves right after rolling to the highest point of the concave limit 64 from the lowest point of the concave limit 64, the roller 27 pushes a displacement rod 58 and a lever 26 to compress a torsion spring I63, meanwhile, the lever 26 pushes a ratchet I23 and a spring seat 59 to compress a spring III25 through a limiting block 71, the ratchet I23 is fully retracted into the ratchet sleeve 22, the top of the ratchet I23 is flush with the outer circle of the ratchet seat 88, when the ratchet seat 88 compresses the spring II13 to a set limit position, the ratchet seat 88 moves left relative to the gear sleeve 29 under the continuous pushing force of the spring II13, when the roller 27 reaches the top edge of the right inclined plane of the concave limit 64, the ratchet I23 axially enters a second-gear ratchet II50 in a small amount, and the spring II13 continuously pushes the ratchet seat 88 to return to a balance point, namely: the roller 27 returns to the low point of the recess 64, the lever 26 is pushed by the torsion spring I63 to return to the initial position as shown in fig. 3, when the large diameter point 92 of the second gear ratchet II50 is engaged with the ratchet I23, namely: in the matching position of the ratchet II50 where the ratchet I23 is shown in fig. 5, the ratchet I23 smoothly extends out of the ratchet sleeve 22, so that power transmission can be realized; when the small diameter point 91 of the ratchet II50 is matched with the ratchet I23 and limited by the small diameter point 91 of the second-gear ratchet II50, the top of the ratchet I23 is limited by the ratchet II50 after a small amount of extension is pushed by the spring III25, and the extension is stopped; when the rotation speed of the second-gear ratchet ring 87 is greater than that of the ratchet seat 88, the ratchet I23 slides backwards along the inclined plane of the ratchet II50 to enter the large-diameter point 92 of the ratchet II50, and the spring III25 pushes the ratchet I23 to extend outwards to be matched with the large-diameter point 92 of the ratchet II50, so that power transmission can be realized; when the second-gear ratchet ring 87 does not rotate or rotates at a speed lower than that of the ratchet seat 88, the ratchet I23 continuously slides forwards clockwise along the inclined plane of the second-gear ratchet II50, the spring III25 is pushed to compress and return by the ratchet I23 until the speed of the second-gear driven gear 39 is higher than that of the ratchet seat 88, the ratchet I23 and the second-gear ratchet II50 are matched to transmit power, the speed of the input shaft 1 is unchanged, and the output speed of the automatic transmission is the second-gear speed.

When the automatic transmission works in the second gear and needs to be lifted to the third gear, the pedal is quickly stepped to improve the rotating speed of the input shaft 1, the upshift process is similar to the upshift process when the automatic transmission works in the first gear and needs to be lifted to the second gear and the pedal is quickly stepped to improve the rotating speed of the input shaft 1, and finally the speed of the input shaft 1 is unchanged, but the output rotating speed of the automatic transmission is the third gear rotating speed.

When the automatic transmission works in the third gear and needs to be lifted to the fourth gear, the pedal is quickly stepped to improve the rotating speed of the input shaft 1, the upshift process is similar to the upshift process when the automatic transmission works in the first gear and needs to be lifted to the second gear and the pedal is quickly stepped to improve the rotating speed of the input shaft 1, and finally the speed of the input shaft 1 is unchanged, but the output rotating speed of the automatic transmission is the fourth gear rotating speed.

When the automatic transmission works in the fourth gear and needs to be lifted to the fifth gear, the pedal is quickly stepped to improve the rotating speed of the input shaft 1, the upshift process is similar to the upshift process when the automatic transmission works in the first gear and needs to be lifted to the second gear and the pedal is quickly stepped to improve the rotating speed of the input shaft 1, and finally the speed of the input shaft 1 is unchanged, but the output rotating speed of the automatic transmission is the fifth gear rotating speed.

Gear shifting down process

When the automatic transmission runs in five gears and is braked and decelerated under the condition that the rotating speed of a gear shifting system is slightly lower than the set rotating speed of four gears, vector resultant force of the three groups of torsion springs II49 and the transmission block 14 drives the transmission sleeve 29 to push the three groups of torsion springs I81 and IV80 in a time-sharing mode through the fixed pull rod I53 and the movable pull rod II48, the hinged support I54 and the hinged support II48 are supported by the hole wall of the limiting hole II21, the three groups of torsion springs I81 in five gears are pushed to rotate anticlockwise by a certain angle around the mounting pin, the torsion springs II79 penetrate through the torsion springs I81 in five gears to enter a four gears area, meanwhile, the transmission sleeve 29 moves rapidly to the right, the ratchet seat 88 cannot move right synchronously with the transmission sleeve 29 under the inertia effect, but moves leftwards relative to the transmission sleeve 29, the ratchet seat 88 compresses the spring I28, meanwhile, the roller 27 is driven to lift upwards along the left side inclined plane of the concave 64 on the transmission sleeve 29, the connecting rod mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88 to be separated from the meshed five gears 36 ratchet II50, and meanwhile, the ratchet I23 pushes the ratchet seat 59 to compress the spring III25; when the ratchet I23 is about to be aligned with the fourth-gear ratchet II50, the fourth-gear torsion spring III83 arranged on the output seat 77 is supported by the wall of the limit hole III31, the torsion spring IV80 arranged on the sliding plate 76 is pushed to rotate anticlockwise by a certain angle around the mounting pin, and three groups of torsion springs IV80 pass through the fourth-gear three groups of torsion springs III83 to move a small amount to the right and then stop; when the ratchet seat 88 compresses the spring I28 to the set limit position, the ratchet seat 88 is acted by the continuous thrust of the spring I28, the roller 27 moves rightward at the left horizontal section of the recess 64 of the driving sleeve 29, when the roller 27 moves to the left top edge of the recess 64 of the driving sleeve 29, the ratchet I23 has axially slightly entered the engagement area of the fourth-gear ratchet II50, because the roller 27 is still at the left horizontal section of the recess 64 of the driving sleeve 29, the ratchet I23 does not extend outward, when the roller 27 continues to move rightward to reach the center position of the recess 64 of the driving sleeve 29, the link mechanism 2 moves while the ratchet seat 88 drives the ratchet I23 to move rightward, aligned with the axial position of the ratchet II50 of the fourth-gear driven gear 37, and simultaneously the ratchet I23 extends outward under the thrust of the spring III25, when the fourth-gear ratchet II50 large diameter point 92 is matched with the ratchet I23, namely: the ratchet I23 and the ratchet II50 shown in FIG. 5 are matched in position, the ratchet I23 extends outwards smoothly, and power transmission can be realized; if the small diameter point 91 of the ratchet II50 is matched with the ratchet I23 at the moment, the ratchet I23 is limited after a small amount of overhanging; when the rotation speed of the fourth-gear ratchet ring 87 is greater than that of the ratchet seat 88, the ratchet I23 slides backwards along the ratchet inclined plane of the ratchet II50 to the large-diameter point 92, and simultaneously, the ratchet I23 extends outwards under the pushing of the spring III25 to form matched transmission power; if the four-gear ratchet ring 87 does not rotate or the rotation speed is less than the rotation speed of the ratchet seat 88 at this moment, the ratchet I23 moves forwards on the ratchet inclined surface of the ratchet II50 to be pressed, when the ratchet seat 88 continuously rotates, the spring III25 is repeatedly compressed and returns by the ratchet I23 until the pedal is stepped to make the rotation speed of the ratchet ring 87 of the four-gear driven gear 37 greater than the rotation speed of the ratchet seat 88, and the ratchet ring 87 drives the ratchet seat 88 to transmit power; the speed of the input shaft 1 is unchanged, but the automatic transmission output rotation speed is a fourth gear rotation speed.

When the automatic transmission runs in five gears and is braked and decelerated under the condition that the rotating speed of a gear shifting system is slightly less than the set rotating speed of three gears, the three groups of torsion springs II49 push the transmission block 14 to move towards the center of the supporting seat 57 along the guide rod 45, the vector resultant force of the torsion springs II49 and the transmission block 14 drives the fixed pull rod I53 to rotate anticlockwise around the hinged support I54, meanwhile, the guide rod 45 and the supporting seat 57 move rightwards along the shaft, three groups of balls IV89 fixedly installed on the sliding plate 76 move rightwards in the axial grooves 62 on the output seat 77 and synchronously rotate with the output seat 77, and three groups of torsion springs II79 and IV80 installed on the sliding plate 76 synchronously move rightwards: the rotation speed of the output seat 77 is reduced more, and the centrifugal force of the transmission block 14 is reduced more; shift-down stabilizing assembly: the torsion spring II79 pushes three groups of torsion springs I81 of five gears and four gears respectively in a dividing way, the torsion springs I81 of the five gears and the four gears rotate anticlockwise by a certain angle in sequence, and the torsion spring II79 enters a three-gear area; upshift stabilizing component: the torque spring II79 of the shift-reducing stabilizing assembly is staggered to push the torque spring I81, the torque spring IV80 is sequentially pushed to be in contact with the four-gear and three-gear three-group torque springs III83, the torque spring IV80 rotates anticlockwise for a certain angle twice, the torque spring IV80 passes through the four-gear and three-gear three-group springs III83 to move a small amount to the right and then stops, the vector resultant force of the transmission block 14 and the torsion spring II49 drives the transmission sleeve 29 to reach balance again at the three-gear position through the movable pull rod II48 and the hinged support II44, the gear shifting system is kept stable, and the out-of-gear shift-reducing stress analysis and the motion process of other gears are the same. Simultaneously, the transmission sleeve 29 moves rightwards and rapidly under the vector resultant force action of the torsion spring II49 and the transmission block 14, the ratchet seat 88 cannot move rightwards synchronously with the transmission sleeve 29 under the inertia action, but moves leftwards relative to the transmission sleeve 29, the ratchet seat 88 compresses the spring I28, meanwhile, the roller 27 is driven to lift upwards along the left inclined plane of the concave 64 on the transmission sleeve 29 and then move leftwards, the link mechanism 2 moves to drive the ratchet I23 to retract into the ratchet seat 88 to be separated from the meshed five-gear driven gear 36 ratchet II50, meanwhile, the ratchet I23 pushes the spring seat 59 to compress the spring III25, when the ratchet I23 reaches the four-gear position, because the transmission sleeve 29 still moves rightwards, the shifting system moves rightwards at a high speed, the ratchet seat 88 is positioned on the left horizontal section of the concave 64 of the transmission sleeve 29, the spring I28 is in a compressed state, the ratchet I23 is kept in the ratchet seat 88 and does not extend outwards, the ratchet I23 smoothly passes through the four-gear ratchet ring 87, when the transmission sleeve 29 reaches the three-gear position, the vector resultant force of the transmission speed 14 and the torsion spring II49 reaches balance again, the transmission sleeve 29 is stabilized to work at the three-gear position, the ratchet seat 88 is acted by the continuous thrust of the spring I28, the roller 27 moves rightwards at the left horizontal section of the recess 64 of the transmission sleeve 29, when the roller 27 moves to the top edge of the left side of the recess 64 of the transmission sleeve 29, the ratchet I23 axially enters the meshing area of the ratchet II50 a little, because the roller 27 is still at the left horizontal section of the recess 64 of the transmission sleeve 29, the ratchet I23 does not extend outwards, when the ratchet seat 88 drives the roller 27 to move rightwards relative to the transmission sleeve 29 to enter the central position of the recess 64 of the transmission sleeve 29, the ratchet seat 88 drives the ratchet I23 to move rightwards when the link mechanism 2 moves, and aligns with the axial position of the ratchet II50 of the three-gear driven gear 38, and simultaneously the ratchet I23 extends outwards under the thrust of the spring III25, and when the three-gear ratchet II50 big diameter point 92 is matched with the ratchet I23, namely: the matching position of the ratchet I23 and the ratchet II50 shown in fig. 5 is that the ratchet I23 extends outwards smoothly, so that power transmission can be realized; if the small diameter point 91 of the ratchet II50 is matched with the ratchet I23 at the moment, the ratchet I23 is limited after a small amount of overhanging; when the rotation speed of the three-gear ratchet ring 87 is greater than that of the ratchet seat 88, the ratchet I23 slides backwards along the ratchet inclined plane of the ratchet II50 to the large-diameter point 92, and simultaneously, the ratchet I23 extends outwards under the pushing of the spring III25 to form matched transmission power; if the three-gear ratchet ring 87 does not rotate or the rotation speed is less than the rotation speed of the ratchet seat 88 at this time, the ratchet I23 moves forwards on the ratchet inclined surface of the ratchet II50 to be pressed, when the ratchet seat 88 continuously rotates, the spring III25 is repeatedly compressed and returns by the ratchet I23 until the pedal is stepped to make the rotation speed of the ratchet ring 87 of the three-gear driven gear 38 greater than the rotation speed of the ratchet seat 88, and the ratchet ring 87 drives the ratchet seat 88 to transmit torque; the speed of the input shaft 1 is unchanged, but the automatic transmission output rotation speed is a three-speed rotation speed.

When the automatic transmission runs in five gears, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the second gear, the automatic gear shifting process with the out-of-step is similar to the automatic gear shifting process when the automatic transmission runs in five gears, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the third gear, and finally the speed of the input shaft 1 is unchanged, but the output rotating speed of the automatic transmission is the second gear rotating speed.

When the automatic transmission runs in five gears, the braking and decelerating running is carried out under the condition, the rotating speed of the gear shifting system is slightly less than the set rotating speed of the first gear or the rotating speed is zero, and the out-of-order automatic gear shifting process is similar to the out-of-order automatic gear shifting process when the automatic transmission runs in five gears, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the third gear; the final input shaft 1 speed is unchanged, but the automatic transmission output speed is either a first gear speed or stopped.

When the automatic transmission runs in the four gears and runs at a speed reduction under the condition, the speed of the gear shifting system is slightly less than the set speed of the three gears, the automatic gear shifting process is similar to the automatic gear shifting process when the automatic transmission runs in the five gears and runs at a speed reduction under the condition, and the speed of the gear shifting system is slightly less than the set speed of the four gears; the final input shaft 1 speed is unchanged, but the automatic transmission output speed is a three speed.

When the automatic transmission runs in the fourth gear, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the second gear, the automatic gear shifting process with the out-of-step is similar to the automatic gear shifting process with the gear automatic transmission running in the fifth gear, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the third gear; the speed of the input shaft 1 is unchanged, but the automatic transmission output rotation speed is the second gear rotation speed.

When the automatic transmission runs in the four gears, the braking and decelerating running is carried out under the condition, the rotating speed of the gear shifting system is slightly less than the set rotating speed of the first gear or the rotating speed is zero, and the out-of-order automatic gear shifting process is similar to the out-of-order automatic gear shifting process when the automatic transmission runs in the five gears, the braking and decelerating running is carried out under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the third gear; the final input shaft 1 speed is unchanged, but the automatic transmission output speed is either a first gear speed or stopped.

When the automatic transmission runs in the third gear and runs at a speed reduction under the condition, the rotating speed of a gear shifting system is slightly less than the set rotating speed of the second gear, and the automatic gear shifting process is similar to the automatic gear shifting process when the automatic transmission runs in the fifth gear and runs at a speed reduction under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the fourth gear; the final input shaft 1 is unchanged in speed, but the automatic transmission output speed is in second gear.

When the automatic transmission runs in three gears, the speed is reduced by braking under the condition, the rotating speed of a gear shifting system is slightly less than the set rotating speed of a first gear or the rotating speed is zero, the automatic gear shifting process is similar to the automatic gear shifting process when the automatic transmission runs in five gears, the speed is reduced by braking under the condition, and the rotating speed of the gear shifting system is slightly less than the set rotating speed of the third gear; the final input shaft 1 speed is unchanged, but the automatic transmission output speed is either a first gear speed or stopped.

When the automatic transmission runs in the second gear, the speed of the gear shifting system is slightly lower than the set speed of the first gear or the speed is zero, the automatic gear shifting process is similar to the automatic gear shifting process when the automatic transmission runs in the fifth gear, the speed of the gear shifting system is slightly lower than the set speed of the fourth gear; the final input shaft 1 speed is unchanged, but the automatic transmission output speed is either a first gear speed or stopped.

When the bicycle runs in each gear and is parked in the case of meeting the condition, the torsion spring II49 pushes the shifting system to move in the process of reducing each gear into one gear, and as the shifting system stops rotating, the ratchet I23 enters the first-gear ratchet II50, and then the ratchet I23 stays at any position of the ratchet ring 87 and is in a matched state, so that preparation is made for running in the next time.

While the foregoing is directed to embodiments of the present utility model, other and further embodiments of the utility model may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.

Claims

1. The centrifugal transmission mechanism of the shaftless automatic transmission comprises a supporting shaft (51) and a transmission sleeve (29) arranged at one end of the supporting shaft (51) and in clearance fit with the supporting shaft (51), and is characterized in that the other end of the supporting shaft (51) is rotationally connected with an output shaft (52), a supporting seat (57) is further arranged on the supporting shaft (51) between the output shaft (52) and the transmission sleeve (29), and the supporting seat (57) is in clearance fit with the supporting shaft (51); a centrifugal component is arranged on the supporting seat (57), and comprises a guide rod (45) fixed on the supporting seat (57) and a transmission block (14) in sliding connection with the guide rod (45);

the centrifugal assembly further comprises a fixed pull rod I (53) and a movable pull rod II (48), wherein one end of the fixed pull rod I (53) is hinged with the transmission block (14), and the other end of the fixed pull rod I is hinged with an end cover (60) on the output shaft (52); one end of the movable pull rod II (48) is hinged with the transmission block (14), and the other end is hinged with the transmission sleeve (29);

The device also comprises an elastic connecting piece, wherein two ends of the elastic connecting piece are respectively fixed at the middle parts of the fixed pull rod I (53) and the movable pull rod II (48), and the middle part of the elastic connecting piece is hinged with the transmission block (14).

2. The centrifugal transmission mechanism of a shaftless automatic transmission according to claim 1, wherein the number of centrifugal components is two or more; more than two groups of balls I (56) are arranged between the supporting seat (57) and the supporting shaft (51), each group of balls I (56) is more than one, and each group of balls I (56) corresponds to one group of centrifugal components in position.

3. The centrifugal drive mechanism of a shaftless automatic transmission according to claim 1 or 2, wherein,

an opening is arranged in the contact area of the transmission block (14) and the supporting seat (57), a pin shaft is arranged in the opening, and a pin hole matched with the pin shaft is arranged at one end of the fixed pull rod I (53) connected with the transmission block (14); the end cover (60) is fixed with a hinged support I (54), and the fixed pull rod I (53) is hinged with the end cover (60) through the hinged support I (54);

one end of the movable pull rod II (48) connected with the transmission block (14) is provided with a pin hole matched with a pin shaft in an opening of the transmission block (14); the transmission sleeve (29) is fixedly provided with a hinged support II (44), and the movable pull rod II (48) is hinged with the transmission sleeve (29) through the hinged support II (44).

4. A centrifugal transmission mechanism of a shaftless automatic transmission according to claim 3, wherein the elastic connecting member is a torsion spring II (49), one end of the torsion spring II (49) is fixedly connected with a fixed tie rod I (53), and the other end is fixedly connected with a movable tie rod II (48); the middle part of the torsion spring II (49) is hinged with a pin shaft in the opening of the transmission block (14).

5. The shaftless automatic speed change device is characterized by comprising an input end (4) and an output end, wherein the output end comprises a supporting shaft (51) and a ratchet telescopic mechanism arranged at one end of the supporting shaft (51), and a driven gear set (12) is arranged outside the ratchet telescopic mechanism; the other end of the supporting shaft (51) is rotationally connected with the output shaft (52); a centrifugal transmission mechanism of the shaftless automatic transmission device according to any one of claims 1 to 4 is further arranged between the ratchet telescopic mechanism and the output shaft (52);

the output end also comprises an output seat (77) and an end cover (60), the end cover (60) is fixedly connected with the output shaft (52), and the output seat (77) is matched with the end cover (60) through a spline;

the input end (4) comprises a transmission mechanism with an input shaft (1) and a spline shaft (5), the input shaft (1) and the spline shaft (5) are arranged in parallel with the support shaft (51), and the input shaft (1) and the spline shaft (5) are rotationally connected through a transmission shaft (69); the spline shaft (5) is provided with a driving gear set (11) matched with the driven gear set (12).

6. The shaftless automatic transmission according to claim 5, characterized in that both ends of the transmission shaft (69) are respectively spline-fixed with a gear II (6) and a gear III (66), wherein the gear II (6) is fitted with the input shaft (1), and the gear III (66) is fitted with the spline shaft (5);

the input shaft (1) is fixedly provided with a gear I (3) meshed with a gear II (6) through a spline, the driving gear set (11) is integrated with a gear IV (61) meshed with a gear III (66), and the driving gear set (11) and the gear IV (61) are integrated into a whole.

7. The shaftless automatic transmission according to claim 5 or 6, characterized in that the ratchet telescoping mechanism comprises a ratchet seat (88), a ratchet mechanism and a transmission sleeve (29) penetrating the ratchet seat (88) and having a sliding key (30) and a recess (64) on a side surface; the ratchet mechanism comprises a connecting rod mechanism (2), ratchet teeth I (23) and a roller (27) which are respectively fixed at two ends of the connecting rod mechanism (2), the connecting rod mechanism (2) is movably arranged in a ratchet seat (88), the ratchet teeth I (23) correspond to ratchet teeth rings (87) of a driven gear set (12) of the transmission, and the roller (27) correspond to the concave (64); a bracket I (65) and a bracket II (67) are respectively fixed at two ends of the transmission sleeve (29), a spring I (28) is arranged between the bracket I (65) and the ratchet seat (88), a spring II (13) is arranged between the bracket II (67) and the ratchet seat (88), and the spring I (28) and the spring II (13) are respectively fixedly connected with the ratchet seat (88); the lower end of the ratchet I (23) is provided with a spring III (25).

8. The shaftless automatic transmission according to claim 7, characterized in that an outer circular slide plate (76) with a ball mounting groove (46) is provided on the bracket I (65), and a ball IV (89) is placed in the ball mounting groove (46); the output seat (77) is provided with an axial groove (62) matched with the ball IV (89).

9. The shaftless automatic transmission device according to claim 8, wherein both sides of the ball mounting groove (46) are provided with shift stabilizing assemblies, each group of shift stabilizing assemblies including a shift down stabilizing assembly and a shift up stabilizing assembly; the gear-reducing stabilizing assembly comprises a torsion spring I (81), a torsion spring II (79), a positioning seat I (82), a positioning seat II (78), a limiting hole II (21) and more than two limiting holes I (85) formed in an output seat (77), wherein the limiting holes II (21) are formed in a sliding plate (76), the torsion spring I (81) is fixed on the positioning seat I (82) and corresponds to the limiting holes I (85), the torsion spring II (79) is fixed on the positioning seat II (78) and corresponds to the limiting holes II (21), the positioning seat I (82) is fixed on the output seat (77), and the positioning seat II (78) is fixed on the sliding plate (76); the upshift stabilizing assembly comprises a torsion spring III (83), a torsion spring IV (80), a positioning seat III (84), a positioning seat IV (42), a limit Kong (41) and more than two limit holes III (31) formed in an output seat (77), wherein the limit Kong (41) is formed in a sliding plate (76), the torsion spring III (83) is fixed on the positioning seat III (84) and corresponds to the limit holes III (31), the torsion spring IV (80) is fixed on the positioning seat IV (42) and corresponds to the limit Kong (41), the positioning seat III (84) is fixed on the output seat (77), and the positioning seat IV (42) is fixed on the sliding plate (76); the installation direction of the torsion spring I (81) is opposite to that of the torsion spring III (83), and the installation direction of the torsion spring II (79) is opposite to that of the torsion spring IV (80); the torsion spring I (81) is partially contacted with the torsion spring II (79); torsion spring III (83) is in partial contact with torsion spring IV (80).

10. The shaftless automatic transmission according to claim 5, 6, 8 or 9, characterized in that the number of ratchet telescopic mechanisms is two or more, two or more sets of balls ii (32) are provided between the transmission sleeve (29) and the support shaft (51), and each set of balls ii (32) corresponds to one set of ratchet telescopic mechanism in position.