CN219406793U - Elastic clutch speed change mechanism - Google Patents

Abstract

The utility model provides an elastic clutch speed change mechanism, which comprises an axle center; a gear lever, a gear ring, one end of the gear ring is provided with a guide joint surface; at least one gear clutch device is respectively provided with at least one pawl, and one end of each pawl is provided with an elastic element; at least one gear tooth set provided with a ratchet wheel; when the gear is shifted, the gear shifting device drives the gear shifting rod, so that the gear shifting ring moves to the gear clutch device corresponding to the gear, the guide contact surface correspondingly abuts against the elastic element, the pawl is elastically expanded and is in one-way transmission connection with the ratchet wheel corresponding to the gear tooth group to carry out gear shifting, the ratchet wheel is not in transmission connection with the gear tooth group, the gear clutch device not corresponding to the gear does not interfere with the gear tooth group, the gear shifting device also comprises an abutting part or a bearing part, the sequential adjacent gear tooth groups are connected in a friction mode, and additional power assistance is generated during gear shifting operation; therefore, the utility model can achieve the effect of quick gear shifting and labor saving.

Description

Elastic clutch speed change mechanism

Technical Field

The utility model provides an elastic clutch speed change mechanism, in particular to a speed change mechanism which is used for switching gears through an axial transmission speed change ring and can be suitable for switching gears of a speed changer in a bicycle.

Background

Nowadays, society is rising to environmental protection, body building and other consciousness, and all countries in the world implement energy-saving and carbon-reducing policies, and the energy demand and pollution problem are reduced, so that the bicycle is popularized as one of solutions and can be used for riding instead of walk or sports and leisure and other purposes; various speed changing devices have been developed to enhance the comfort, handleability and practicality of bicycles to address the needs of various road conditions while riding.

In order to adapt to the development of electric auxiliary bicycles, automation and intellectualization of riding operation are important to research, however, an external speed change system must complete gear shifting when traveling, and cannot directly span multiple gear shifting and has the operating characteristics of chain dropping risk and the like, so that an automatic gear shifting control strategy is greatly limited.

Therefore, many people further research an internal transmission, and most internal transmission devices adopt a planetary gear train speed change mechanism and control a plurality of pawl groups to carry out clutch control, so that the target transmission part is meshed with an axle center to be fixed and not rotatable.

In view of this, the inventors of the present application have intensively studied the clutch type transmission mechanism and have made researches and improvements, and have expected a preferred utility model to solve the above-mentioned problems, and have made the utility model after continuous experiments and modifications.

Disclosure of Invention

The present utility model has been made to solve the above problems, and an object of the present utility model is to provide a transmission device which is simple in mechanism, excellent in reliability, easy to process and assemble, and easy to perform one-way clutch control while reducing resistance at the time of gear shift, and to achieve the above objects, the present inventors have provided an elastic clutch transmission mechanism comprising: an axle center; the gear lever is axially connected and driven to a gear ring, the gear ring is correspondingly sleeved and axially slides on the axle center, and a guide joint surface is arranged at one axial end of the gear ring; the gear clutch device is respectively provided with at least one pawl, and one end of the pawl is provided with an elastic element corresponding to the guide joint surface; and at least one gear tooth set provided with a ratchet wheel corresponding to the pawl; when the ratchet wheel is in a non-transmission state, the guide joint surface is not abutted against the elastic element, and the pawl is in non-transmission joint with the ratchet wheel; and in a transmission state, the guide contact surface is correspondingly abutted against the elastic element of at least one gear clutch device, so that the corresponding pawl is elastically expanded and connected with the ratchet wheel in a one-way transmission manner.

The elastic clutch speed change mechanism is characterized in that one end of the pawl is provided with a clamping part; the elastic element is provided with a first elastic arm and a second elastic arm, the first elastic arm and the second elastic arm are connected and arranged on an elastic connection part, the first elastic arm is connected to one end of the pawl away from the clamping connection part, and the second elastic arm is used for enabling the guide connection part to correspondingly abut against when in a transmission state, so that the pawl expands outwards and is connected with the ratchet wheel in a unidirectional transmission mode.

The gear clutch device is provided with an elastic ring body respectively, and is connected to one end of the corresponding pawl corresponding to the elastic element, and when the gear clutch device is used in the non-transmission state, the elastic ring body elastically contracts inwards to press against the pawl, so that the pawl is connected with the ratchet wheel in a non-transmission mode.

The elastic clutch speed change mechanism is characterized in that the pawl is provided with a fixing groove, the elastic connection part is provided with a clamping groove, and the elastic ring body is correspondingly and elastically abutted to the fixing groove and the clamping groove.

The elastic clutch speed change mechanism further comprises a driving shaft, the gear tooth group is correspondingly sleeved on the outer edge of the driving shaft, and the speed change ring is axially displaced at the inner edge of the driving shaft; the driving shaft is further axially cut with a through groove corresponding to the gear clutch device and the speed changing ring, and the second elastic arm penetrates through the through groove to extend into the driving shaft, so that the guide joint surface can correspondingly abut against the second elastic arm when the driving shaft is in the transmission state.

The elastic clutch speed change mechanism further comprises an abutting part sleeved at one end of the driving shaft and correspondingly abutting against at least one gear tooth group axially.

The elastic clutch speed change mechanism is characterized in that at least one sliding block corresponding to the guide joint surface is further arranged between the adjacent gear tooth groups, a bearing part is arranged at one end of the sliding block opposite to the guide joint surface, at least one connecting part is arranged on the bearing part, the gear tooth groups are respectively provided with a connecting part corresponding to the connecting part, and when the guide joint surface abuts against the sliding block, the sliding block correspondingly pushes against the bearing part, so that the corresponding connecting part is connected with the corresponding connecting part.

The elastic clutch speed change mechanism is characterized in that the gear teeth are respectively provided with a sun gear and at least one planetary gear corresponding to the sun gear, and the inner edge of the sun gear is provided with the ratchet wheel.

The elastic clutch speed change mechanism is characterized in that a limit groove is concavely formed in the axis in a radial direction, and the speed change ring is correspondingly arranged in an axial sliding mode and is limited in the limit groove.

The elastic clutch speed change mechanism is characterized in that a spiral part is arranged on the outer edge of the speed change rod, and the speed change rod rotates to enable the spiral part to axially drive the speed change ring.

The elastic clutch speed change mechanism further comprises a gear change device correspondingly connected and driven to the speed change rod, so that the speed change ring axially moves; the gear shifting device is driven by electricity automatically or manually; when the gear shifting device is electrically and automatically driven, the gear shifting device can be a direct current motor or a stepping motor; when the gear shifting device is manually operated by manpower, the gear shifting device is a corresponding speed changing line.

From the above description and the arrangement, it is apparent that the present utility model has the following advantages and effects, and is described in detail as follows:

1. when shifting gears, the gear shifting device drives the gear shifting rod, so that the gear shifting ring can correspondingly move to the gear clutch device of the corresponding gear, the guide joint surface of the gear shifting ring can correspondingly abut against the elastic element of the gear clutch device of the corresponding gear, the corresponding pawl is elastically expanded and is in one-way drive connection with the ratchet wheel of the corresponding gear tooth group to switch gears, but not the gear clutch device of the corresponding gear, the ratchet wheel is not in drive connection with the gear tooth group, and the gear clutch device of the non-corresponding gear does not interfere with the gear tooth group; the gear shifting mode of the utility model adopts the simplest gear transmission principle, thereby remarkably reducing the number and the interrelation of transmission parts, further achieving the advantages of lighter weight, high transmission efficiency and easy assembly and processing, and the sequential configuration makes gear shifting control easier, does not need to control a plurality of groups of clutch devices at the same time, avoids generating excessive resistance when the collecting claws are separated, thus achieving the effects of quick gear shifting and labor saving, simplifying the number and the complexity of part configuration, and further greatly reducing the manufacturing and assembly cost.

2. According to the utility model, through the arrangement of the abutting part or the bearing part, the rotating speed difference during the running of the gears can be utilized, and the adjacent gear tooth groups are connected in a friction manner through the abutting part or the bearing part, so that the gear tooth groups generate the assistance of additional gear shifting, and the advantage of miniaturization of the gear shifting device is facilitated.

Drawings

FIG. 1 is a schematic cross-sectional view of the present utility model.

Fig. 2 is an exploded perspective view of the present utility model.

Fig. 3 is a perspective exploded and enlarged schematic view of the gear clutch of the present utility model.

FIG. 4 is a schematic cross-sectional and operational view of the shift ring in a driven state with pawls engaged during shifting in accordance with the present utility model.

FIG. 5 is a schematic cross-sectional and operational view of the ratchet with the pawl disengaged during shifting of the present utility model.

FIG. 6 is a schematic cross-sectional and operational view of the shift ring in a non-transmitting state with the pawl disengaged by the elastic ring body in accordance with the present utility model.

Fig. 7 is a schematic cross-sectional view of a slider and a receiving member according to another embodiment of the present utility model.

FIG. 8 is a schematic cross-sectional and operational view of the present utility model based on FIG. 7, with friction assist in disengaging the high pawl during a downshift.

Fig. 9 is a schematic view of the gear ring according to the utility model in a sectional view and in use in a driving state, based on fig. 7.

Reference numerals:

1, an axle center;

11, a limit groove;

2, a gear lever;

a speed-changing ring;

211, a guide joint surface;

212, limiting pins;

a screw member 22;

3, a gear clutch device;

31, pawl;

311, a clamping part;

312, fixing grooves;

an elastic element 32;

321, a first elastic arm;

322 a second resilient arm;

323, spring connection part;

324, clamping grooves;

33, an elastic ring body;

34, driving a shaft;

341, through groove;

342, a containing groove;

343 a fixedly connected groove;

344 an abutment member;

345, sliding block;

346 a receiving member;

347 a connecting portion;

4, a gear tooth group;

a ratchet wheel 41;

42. 42a, 42b, 42c, 42 d;

421, a joint;

43. 43a, 43b, 43c, 43 d;

431 planetary shaft;

5, a power input device;

and 6, a planet carrier.

Detailed Description

In relation to the technical means of the present inventors, several preferred embodiments are described in detail below with reference to the drawings to further understand and identify the present utility model.

Referring to fig. 1, the present utility model is an elastic clutch transmission mechanism, comprising:

an axle center 1; the bicycle frame is used for being fixedly arranged at a proper position of the bicycle frame and can also be arranged on the shell so as to prevent rotation or movement;

a gear lever 2 axially connected to and driven by a gear shift ring 21, where a guide joint surface 211 is disposed at one axial end of the gear shift ring 21, and the gear shift ring 21 is correspondingly sleeved and axially slid on the axle center 1, in an embodiment, in order to limit the axial movement distance of the gear shift ring 21, a limit groove 11 is radially recessed in the axle center 1, and the gear shift ring 21 is correspondingly axially slid and limited in the limit groove 11, in a specific embodiment, the gear shift ring 21 may be used by itself, or by providing a limit pin 212, for example: pins or flat keys to positively locate the shift ring 21 in the limit groove 11 and axially slide, but this is only illustrative and not limiting;

at least one gear clutch 3, there is at least one pawl 31 separately, one end of the pawl 31 has an elastic element 32 corresponding to the said guide joint surface 211, the said guide joint surface 211 can be configured as inclined plane or conical surface, in order to facilitate the said speed change ring 21 to push the elastic element 32 correspondingly when moving axially; and

at least one set of gear teeth 4 provided with a ratchet 41 corresponding to said pawl 31;

therefore, when in the non-transmission state, the guide surface 211 is not abutted against the elastic element 32, and the pawl 31 is non-transmission connected to the ratchet 41; and when in a transmission state, the guide joint surface 211 is correspondingly abutted against the elastic element 32 of at least one gear clutch device 3, so that the corresponding pawl 31 is elastically expanded and is connected with the ratchet wheel 41 in a one-way transmission manner, and the gear shifting effect is achieved through the gear tooth set 4.

First, in the transmission mode of the shift lever 2 to the shift ring 21 in the axial direction, the shift lever 2 is driven by disposing a gear shift device (not shown), in this embodiment, a spiral member 22 is provided on the outer edge of the shift lever 2, and the shift lever 2 is rotated to drive the spiral member 22 to the shift ring 21 in the axial direction, so that the shift ring 21 can be moved back and forth in the axial direction by rotating the shift lever 2 by the gear shift device; in other embodiments, the gear shift device may operate the gear shift lever 2 by a linear driving method to directly longitudinally move the shift ring 21, and the linear driving method may not provide the screw member 22 on the gear shift lever 2.

For the driving mode of the gear shifting device, the gear shifting device can be driven automatically by electricity or manually by manpower; when the gear shifting device is electrically and automatically driven, the gear shifting device can be a direct current motor or a stepping motor; when the gear shifting device is manually operated by manpower, the gear shifting device is a corresponding speed change line; in addition, the gear shifting device is driven by receiving a gear shifting instruction in a wired or wireless mode, can be configured as a direct current motor or a stepping motor, and can comprise a potentiometer, a Hall sensor, an encoder or an eddy current sensor when the direct current motor is adopted, so as to ensure the control of the angle or the distance and ensure the control stroke of a speed changing ring; therefore, the user can manually or automatically select the gear, so that the gear shifting device can control the axial position of the gear shifting ring 21 on the axle center 1 to complete the gear shifting control.

Regarding the configuration of the pawl 31, when the axial movement of the shift ring 21 corresponds to the transmission state, the pawl 31 can be expanded outwards and is in transmission connection with the ratchet 41, in an embodiment, one end of the pawl 31 is provided with a clamping part 311 corresponding to the ratchet 41, because the pawl 31 and the ratchet 41 are in unidirectional transmission, the ratchet 41 is provided with ratchets in unidirectional configuration, and the clamping part 311 is in clamping configuration capable of being in unidirectional transmission with the ratchets, thereby when the pawl 31 is driven to rotate in one transmission direction, the pawl 41 can be correspondingly transmitted to rotate, otherwise, when the pawl 31 rotates in the other direction, the pawl 31 is pressed by the ratchets, so that the pawl 31 idles and cannot be transmitted to the ratchet 41, and the specific configuration is not repeated herein; the elastic element 32 is provided with a first elastic arm 321 and a second elastic arm 322, the first elastic arm 321 and the second elastic arm 322 are connected and arranged on the spring connection portion 323, the first elastic arm 321 is connected to one end of the pawl 31 away from the clamping portion 311, and the second elastic arm 322 is used for enabling the guide connection surface 211 to correspondingly abut when in the transmission state, so that the pawl 31 is ejected out through the spring connection portion 323 and the first elastic arm 321 to be connected to the ratchet 41 in a outwards-expanding unidirectional transmission manner.

In the non-transmission state, the pawl 31 can be reset and not expanded, so as to prevent interference to the rotation of the gear clutch device 3 or the gear tooth set 4, in an embodiment, the gear clutch device 3 is respectively provided with an elastic ring body 33, which is connected to one end of the corresponding pawl 31 opposite to the elastic element 32, when the gear clutch device is used in the non-transmission state, the elastic ring body 33 elastically contracts to press the pawl 31, so that the pawl 31 is not in transmission connection with the ratchet 41, and in the specific elastic configuration, the elastic ring body 33 needs to elastically contract the pawl 31 in the non-transmission state, the elastic force needs to be slightly larger than the sliding friction force when the elastic element 32 is not in contact with the guide contact surface 211, in addition, when the transmission state, the guide contact surface 211 is in contact with the elastic element 32, the elastic element 32 can be received to elastically push the pawl 31 outwards, and the elastic force of the elastic element 32 which is stressed and deformed at the moment must be larger than the elastic force of the elastic ring body 33 in the inward direction, so as to ensure that the elastic element 32 can be elastically contracted and firmly connected with the ratchet 41 in the transmission state.

In order to facilitate the arrangement of the elastic ring 33, in a preferred embodiment, the pawl 31 is provided with a fixing slot 312, the spring connection portion 323 is provided with a clamping slot 324, and the elastic ring 33 is correspondingly elastically abutted in the fixing slot 312 and the clamping slot 324, so that the elastic ring 33 can be firmly buckled and exert elastic force on the pawl 31.

In the power transmission configuration of the present utility model, in a specific embodiment, by providing a driving shaft 34, the gear teeth set 4 is correspondingly and movably sleeved on the outer edge of the driving shaft 34, and the gear teeth set 4 and the driving shaft 34 do not mutually transmit, and the speed-changing ring 21 is axially displaced at the inner edge of the driving shaft 34; the driving shaft 34 is further axially cut with a through groove 341 corresponding to the gear clutch 3 and the gear shifting ring 21, and the second elastic arm 322 extends through the through groove 341 inside the driving shaft 34, so that the guide contact surface 211 can correspondingly abut against the second elastic arm 322 when in the transmission state; therefore, the driving shaft 34 can be used for driving and correspondingly configured to the power input device 5, so that the power input device 5 can drive the driving shaft 34 and correspondingly drive the pawl 31 to rotate through the through groove 341, and as mentioned above, the pawl 31 is pushed by the guiding surface 211 to be assembled with the ratchet wheel 41 in the driving state, thereby achieving the gear shifting effect through the gear ratio of the gear tooth set 4.

In order to facilitate positioning of the pawl 31 in the non-transmission state, in the embodiment, the outer ring surface of the driving shaft 34 is concavely provided with a receiving groove 342 and a fixing groove 343 at two sides of the through groove 341, the pawl 31 is disposed in the receiving groove 342 at one end opposite to the clamping portion 311, and the spring portion 323 is correspondingly disposed in the fixing groove 343, so as to facilitate positioning and assembling.

In addition, regarding the configuration of the gear set 4, in the preferred embodiment, the gear set 4 is respectively provided with a sun gear 42 and at least one planetary gear 43 corresponding to the sun gear 42, and the ratchet wheel 41 is arranged at the inner edge of the sun gear 42, so that the gear transmission effect can be achieved through the number and the gear ratio configuration of the sun gear 42 and the planetary gear 43; for the positioning of the whole of the present utility model, a planet carrier 6 is configured to be correspondingly disposed on the axle center 1 and correspondingly shielded from the gear teeth set 4 and the gear clutch device 3 of the present utility model, so as to limit the center distance of rotation of the planetary gears 43, and the planetary gears 43 corresponding to the different gear teeth sets 4 are pivoted by a planetary shaft 431; the number of the gear teeth 4 and the gear clutch 3 may be correspondingly set according to the number of gears, and in the present embodiment, four sets of the gear teeth 4 and the gear clutch 3 are set, but this is merely an exemplary description and not a limitation.

In the present embodiment, the gear teeth sets 4 are arranged in an increasing or decreasing manner by corresponding gears, so that the sun gears 42a to 42d are axially sequentially arranged from the first gear to the fourth gear, and respectively correspond to the planetary gears 43a to 43d, and the sun gears 42a to 42d respectively correspond to the pawls 31 of the corresponding gear clutch device 3; thus, as shown in fig. 1 and 2, when shifting the gear to the fourth gear, the gear lever 2 drives the gear ring 21 to the pawl 31 of the gear clutch device 3 corresponding to the sun gear 42d, thereby, as shown in fig. 4, the guide surface 211 correspondingly contacts the second elastic arm 322, so that the pawl 31 is radially pushed out of the driving shaft 34 by the elasticity between the first elastic arm 321, the second elastic arm 322 and the elastic contact portion 323, the pawl 31 can be in driving connection with the ratchet wheel 41 of the sun gear 42d, and further, the driving shaft 34 can transmit power to the sun gear 42d and the corresponding planetary gear 43d through the pawl 31, and the planetary gear 43 transmits power to the planetary shaft 431 corresponding to the sun gear 42d due to the non-circular arrangement of the planetary shaft 431, and the rest of the planetary gears 43 correspondingly contact the rest of the planetary gears 43, and simultaneously, the planetary gears 43a to 43c rotate at the same time, so that the gears 43a to 42c corresponding to the sun gears 42a to 42c in the first to the third gear are not in the fourth gear, and the first to 31 are not in interference with the fourth gear, and the power is not in driving connection with the ratchet wheel 42a to any other gears 42; the foregoing gear and number arrangements are merely illustrative and not limiting.

In the gear shifting operation, as shown in fig. 1 and 4, when the shift ring 21 is moved from the third gear to the fourth gear or from the fourth gear to the third gear, the shift ring 21 contacts the elastic element 32 pushing the target gear to push out the corresponding pawl 31 before being separated from the lower gear, and the sun gear 42 and the engaged planetary gear 43 of each gear are different in tooth number although the pawls 31 of the lower gear and the pawls 31 of the target gear are simultaneously pushed out, the planetary gear 43 rotates at constant speed by the planetary shaft 431, the gear ratio of the planetary gear 43 with the lower gear transmitted to the sun gear 42 is larger than the gear ratio with the higher gear ratio, the driving shaft 34 is faster than the driving shaft 34 by the pawls 31 and the sun gear 42 with the higher gear ratio, so that the ratchet wheel 41 will push the compression elastic element 32 to separate the pawls, the gears 31 are pushed into gear while realizing the gear shifting operation, idle or the transmission lock is not generated by the elastic clutch ensuring process, and the gear shifting time is not required to be controlled by the elastic clutch lock, and the gear shifting time is shortened.

With continued reference to fig. 4 to 6, in the foregoing shift process, when the shift ring 21 pushes the elastic element 32 to push the pawls 31 out of the open elastic ring 33 and engage the ratchet 41 of the sun gear 42 of the fourth gear, the drive shaft 34 will drive the sun gear 42d of the fourth gear to rotate synchronously clockwise, as shown in fig. 4, and in the shift process, the shift ring 21 also pushes the elastic element 32 in the shift stroke, so that the pawls 31 push out of the open elastic ring 33; since the sun gear 42c of the third gear also rotates clockwise and rotates faster than the driving shaft 34, the ratchet wheel 41 of the sun gear 42c will push the corresponding pawl 31 to compress and deform the corresponding elastic element 32 to separate as shown in fig. 5; instead of the gear teeth set 4 and the gear clutch 3 for gear change, the elastic element 32 is not pushed by the shift ring 21, and the corresponding pawls 31 are retracted into the driving shaft 34 by the elastic ring 33, so that the sun gears 42a and 42b are separated from the driving shaft 34, as shown in fig. 6, when the gear is shifted to a specific gear, only the corresponding gear teeth set 4 and the gear clutch 3 can mutually drive, and the sun gears 42 of the other gears idle on the driving shaft 34 without interfering with power transmission.

In a preferred embodiment, in order to facilitate the smooth traction of the sun gear 42 of the rest gear under the set gear operation, an abutment member 344, which may be a wave spring or a belleville spring in the embodiment, is sleeved on one end of the driving shaft 34 and abuts against at least one gear tooth set 4 correspondingly to make the sun gear 42 on the driving shaft 34 mutually adhere and increase the contact friction force thereof, so that the sun gear 42 can traction the adjacent gears when rotating, thereby providing additional assistance for shifting and collecting pawls during transmission.

In another embodiment, instead of providing the abutment member 344 on the driving shaft 34, at least one slider 345 corresponding to the guide contact surface 211 is provided between the adjacent gear tooth groups 4, the slider 345 is provided with a receiving member 346 at one end opposite to the guide contact surface 211, the receiving member 346 may be provided with an elastic ring, the receiving member 346 is provided with at least one connecting portion 347, the gear tooth groups 4 are provided with connecting portions 421 corresponding to the connecting portions 347, in an embodiment, the connecting portions 421 are provided on the sun gear 42, and when the guide contact surface 211 abuts against the slider 345, the slider 345 correspondingly pushes the receiving member 346 to connect the corresponding connecting portions 347 to the corresponding connecting portions 421; therefore, as shown in fig. 7, when the gear shift control is performed, the moving process of the shift ring 21 pushes the sliding block 345 to radially and outwardly open the receiving member 346, so that the connecting portion 347 of the receiving member 346 and the connecting portions 421 of the adjacent two sun gears 42 are mutually assembled to be in friction contact, by virtue of the faster rotation speed of the sun gear 42 with a lower gear, the higher gear sun gear 42 provides additional friction assistance, the pawl 31 corresponding to the higher gear sun gear 42 is easier to retract, when the gear shift is completed, the shift ring 21 moves to the sun gear 42 with a corresponding target gear, so that the sliding block 345 is not pushed out by the shift ring 21, the opened receiving member 346 retracts inwards into the driving shaft 34 by virtue of the self-elastic shrinkage, so that the connecting portion 347 of the receiving member 346 is separated from the sun gears 42 with two adjacent sides, the friction contact connection is released, and the arrangement of the gear group 4 and the gear clutch 3 is not affected, and the lower gear 42 can push the corresponding pawl 31 with a higher rotation speed to compress the corresponding pawl 31 to compress the corresponding pawl to deform the required power to be assisted by virtue of the elastic force.

In addition, as described above, during the shift down, the shift ring 21 moves from the fourth gear to the third gear, the slider 345 is pushed out to open the receiving member 346, the connecting portions 347 on both sides of the receiving member 346 are in frictional contact with the connecting portions 421 of the adjacent sun gears 42, the shift ring 21 continues to move and push the spring plate of the third gear to push the corresponding pawl 31 open the corresponding elastic ring 33, the sun gear 42c of the third gear corresponding to the pawl 31 is ready to engage the ratchet 41 to enter the gear, as shown in fig. 8 and 9, radial sectional views of the third gear and the fourth gear in the shift assist operation state are further referred to, when the transmission is performed, as shown in fig. 9, the driving shaft 34 transmits power to the sun gear 42d of the fourth gear through the pawl 31, the planetary gear 43d of the corresponding engaged fourth gear rotates in the reverse direction, by means of the non-circular structure, the planetary gears 43 arranged on the planetary shafts 431 rotate at constant speed through the rotation of the planetary shafts 431 and the contact transmission with the non-circular structure of the planetary shafts 431, so that the power is transmitted to the sun gear 42c of the third gear through the meshing of the planetary gears 43c of the third gear, as shown in fig. 8, the number of teeth of the planetary gears 43c of the third gear is more than that of the planetary gears 43d of the fourth gear, the number of teeth of the sun gear 42c of the third gear is less than that of the sun gear 42d of the fourth gear, the rotation speed of the sun gear 42c of the third gear is faster than that of the sun gear 42d of the fourth gear, the power of the third gear is transmitted to the sun gear 42d of the fourth gear through the bearing member 346 to generate additional power when the gear is shifted, thereby assisting the sun gear 42d of the fourth gear to increase the rotation speed, and the corresponding pawl 31 is separated from the ratchet wheel 41, and after the speed-changing ring 21 ejects the pawl 31 of the third gear, the downshift process continues to operate the shift ring 21 to move toward the third gear, so that the elastic element 32 in the fourth gear is released, the elastic ring 33 in the fourth gear is contracted to simultaneously act with the auxiliary force of the receiving member 346 to retract the pawl 31 into the driving shaft 34, thereby overcoming the self-locking characteristic of the pawl 31, then the shift ring 21 moves to release the slider 345, so that the receiving member 346 is contracted to retract the slider 345 into the driving shaft 34, and when the shift ring 21 moves to correspond to the third gear, the sun gear 42c in the third gear is meshed with the pawl 31 corresponding to the sun gear, thereby completing the downshift operation.

In summary, the technical means disclosed in the present utility model can effectively solve the common problems and achieve the expected purposes and effects, and the technical means disclosed in the present utility model is not disclosed in publications before application, has long-term advancement, and is true of the patent patents called by the honest patent laws, so that the present utility model is applied by law, and the present utility model is clawed and issued to the patent patents for double-sense and happy.

The foregoing description is only illustrative of the present utility model and is not to be construed as limiting the scope of the utility model, which is defined by the appended claims and their equivalents and modifications.

Claims (10)

1. An elastic clutch transmission mechanism, comprising:

an axle center;

the gear lever is axially connected and driven to the gear ring, the gear ring is correspondingly sleeved and axially slides on the axle center, and a guide joint surface is arranged at one axial end of the gear ring;

the gear clutch device is respectively provided with at least one pawl, and one end of the pawl is provided with an elastic element corresponding to the guide joint surface;

at least one gear tooth group provided with a ratchet wheel corresponding to the pawl; and

the elastic ring body is connected to one end of the corresponding pawl, which is opposite to the elastic element, and is used for elastically shrinking inwards to press the pawl when in a non-transmission state, the guide joint surface is not connected with the elastic element, and the pawl is connected to the ratchet wheel in a non-transmission mode; when in a transmission state, the guide contact surface is correspondingly abutted against the elastic element of at least one gear clutch device, and the corresponding pawl is elastically expanded and connected with the ratchet wheel in a one-way transmission way.

2. The elastic clutch transmission mechanism according to claim 1, wherein said pawl is provided with a click-on portion at one end; the elastic element is provided with a first elastic arm and a second elastic arm, the first elastic arm and the second elastic arm are connected and arranged on the elastic connection part, the first elastic arm is connected to one end of the pawl away from the clamping connection part, and the second elastic arm is used for enabling the guide connection part to correspondingly abut against when in a transmission state, so that the pawl expands outwards and is connected with the ratchet wheel in a unidirectional transmission mode.

3. The elastic clutch transmission according to claim 2, wherein the pawl is provided with a fixing groove, the spring connection part is provided with a clamping groove, and the elastic ring body is correspondingly elastically abutted in the fixing groove and the clamping groove.

4. The elastic clutch transmission mechanism according to claim 2, comprising a drive shaft, said set of gear teeth being correspondingly sleeved on an outer edge of said drive shaft, said shift ring being axially displaced at an inner edge of said drive shaft; the driving shaft is further axially cut with a through groove corresponding to the gear clutch device and the speed changing ring, and the second elastic arm penetrates through the through groove to extend into the driving shaft, so that the guide joint surface can correspondingly abut against the second elastic arm when the driving shaft is in the transmission state.

5. The elastic clutch transmission mechanism according to claim 4, comprising an abutment member sleeved on one end of the driving shaft and correspondingly axially abutting at least one of the gear tooth sets.

6. The elastic clutch transmission according to claim 4, wherein at least one slider corresponding to the guide contact surface is further provided between the adjacent gear tooth groups, the slider is provided with a receiving member at one end opposite to the guide contact surface, the receiving member is provided with at least one connecting portion, the gear tooth groups are respectively provided with a connecting portion corresponding to the connecting portion, and when the guide contact surface abuts against the slider, the slider correspondingly pushes against the receiving member, so that the corresponding connecting portion is connected with the corresponding connecting portion.

7. The elastic clutch transmission according to any one of claims 1 to 6, wherein each of the shift gears is provided with a sun gear and at least one planetary gear corresponding to the sun gear, and the ratchet wheel is provided at an inner edge of the sun gear.

8. The elastic clutch transmission according to any one of claims 1 to 6, wherein the shaft center is further radially recessed with a limiting groove, and the transmission ring is disposed corresponding to the axial sliding and is limited in the limiting groove.

9. The elastic clutch transmission according to any one of claims 1 to 6, wherein a spiral member is provided at an outer edge of the shift lever, and the shift lever is rotated such that the spiral member axially drives the shift ring.

10. The elastic clutch transmission according to any one of claims 1 to 6, comprising a gear shift device correspondingly coupled to and driven by said shift lever so that said shift ring moves axially; the gear shifting device is driven by electricity automatically or manually; when the gear shifting device is electrically and automatically driven, the gear shifting device can be a direct current motor or a stepping motor; when the gear shifting device is manually operated by manpower, the gear shifting device is a corresponding speed changing line.