Elastic clutch transmission mechanism

Abstract

The present invention provides an elastic clutch speed change mechanism, comprising: an axis; a speed change rod axially connected to and transmitting to a speed change ring, and a guide surface provided at one end of the speed change ring; at least one gear clutch device, each provided with at least one pawl, and one end of the pawl is provided with an elastic element corresponding to the guide surface; at least one gear tooth group, provided with a ratchet corresponding to the pawl; thereby, when a speed change is performed, the speed change ring can be moved to the gear clutch device of the corresponding gear position through the gear change device, so that the guide surface abuts against the elastic element of the gear clutch device of the corresponding gear position. The gear clutch device of the non-corresponding gear will not be transmitted to the gear tooth group, so that the gear clutch device of the non-corresponding gear will not interfere with the gear tooth group. In addition, it also includes the setting of abutment components or receiving components, which can utilize the speed difference of the gears during operation and connect the sequentially adjacent gear tooth groups by friction, so that additional assistance is generated during the gear shifting operation; therefore, the configuration of the present invention can achieve the effect of fast gear shifting and labor saving.

Description

Technical Field

[0001] The present invention provides an elastic clutch speed change mechanism, in particular a mechanism for switching gears through an axial transmission speed change ring, which can be adapted to the gear switching of a transmission in a bicycle. Background Art

[0002] With the rise of environmental awareness and fitness in society, countries around the world are implementing energy-saving and carbon-reduction policies to reduce energy demand and pollution. Therefore, the promotion of bicycles has become one of the solutions, and they can be used for transportation, sports and leisure. To enhance the comfort, maneuverability and practicality of bicycles, various speed change devices have been developed to meet the needs of various road conditions when riding.

[0003] To adapt to the development of electric-assisted bicycles, automated and intelligent riding controls have become a research focus. However, the external transmission system requires shifting while driving, cannot directly shift across multiple gears, and has the risk of chain drop, which greatly limits the control strategy of automatic shifting.

[0004] Therefore, many people have conducted relevant research on internal transmissions, and the vast majority of internal transmission devices use a planetary gear system transmission mechanism and simultaneously control multiple pawl groups for clutch control, so that the target transmission parts are engaged and fixed with the axis and cannot rotate. Although this method has more speed changes, it has complex mechanisms, a large number of parts, high processing precision requirements and higher costs. In addition, the pawl has a certain self-locking ability when engaged to prevent disengagement and slippage during transmission. However, this characteristic makes the resistance of the shift pawl greater, which is not conducive to the operation of the electronic shift device, especially for the shifting when pedaling, which causes the pawl to load more. It is even more severe when multiple pawl groups are operated at the same time. How to further innovate technology to achieve a more streamlined structure to reduce costs and lighter shift resistance to make it suitable for electronic shifting operation is a goal that the industry urgently needs to break through.

[0005] In view of this, we, the inventors, have devoted ourselves to further research on the clutch type transmission mechanism and have embarked on research and development and improvement, hoping to solve the above problems with a better invention. After continuous testing and modification, the present invention was produced. Summary of the Invention

[0006] The object of the present invention is to solve the above-mentioned problems and provide a speed change device with simple structure, good reliability, easy processing and assembly, and easy one-way clutch control, while reducing the resistance during gear shifting. To achieve the above objects, the inventors provide an elastic clutch speed change mechanism, comprising: an axis; a shift rod axially connected to and transmitted to a speed change ring, the speed change ring correspondingly sleeved and axially sliding on the axis, the speed change ring provided with a guide surface at one axial end; at least one gear clutch device, each provided with at least one pawl, one end of the pawl provided with an elastic element corresponding to the guide surface; and at least one gear tooth set, provided with a ratchet corresponding to the pawl; whereby in a non-transmission state, the guide surface does not abut against the elastic element, and the pawl is non-transmission-connected to the ratchet; and in a transmission state, the guide surface correspondingly abuts against the elastic element of at least one of the gear clutch devices, so that the corresponding pawl elastically expands outward and is unidirectionally transmission-connected to the ratchet.

[0007] The elastic clutch transmission mechanism, wherein one end of the pawl is provided with a clamping portion; 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 at an elastic connection portion, the first elastic arm is connected to the end of the pawl away from the clamping portion, and the second elastic arm is used to make the guiding surfaces correspondingly abut in the transmission state, so that the pawl expands outward and is connected to the ratchet wheel in a one-way transmission.

[0008] The elastic clutch transmission mechanism, wherein the gear clutch device is respectively provided with an elastic ring body, which is connected to the end of the corresponding pawl opposite to the elastic element. When in the non-transmission state, the elastic ring body elastically shrinks inward to press against the pawl, so that the pawl is non-transmission-connected to the ratchet.

[0009] The elastic clutch transmission mechanism, wherein the pawl is provided with a fixing groove, the elastic connection portion is provided with a clamping groove, and the elastic ring body elastically abuts against the fixing groove and the clamping groove accordingly.

[0010] The elastic clutch speed change mechanism further includes a drive shaft, the gear gear group is correspondingly sleeved on the outer edge of the drive shaft, and the speed change ring is axially displaced at the inner edge of the drive shaft; the drive shaft is further axially cut with a through groove corresponding to the gear clutch device and the speed change ring, and the second elastic arm extends through the interior of the drive shaft through the through groove, so that the guide surface can correspondingly abut the second elastic arm when in the transmission state.

[0011] The elastic clutch transmission mechanism further includes an abutment component sleeved on one end of the drive shaft and correspondingly abutting against at least one of the gear gear sets in the axial direction.

[0012] The elastic clutch speed change mechanism, wherein at least one slider corresponding to the guide surface is respectively provided between adjacent gear tooth groups, the slider is provided with a receiving component at one end opposite to the guide surface, the receiving component 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 surface abuts against the slider, the slider pushes against the receiving component accordingly, so that the corresponding connecting portion is connected to the corresponding connecting portion.

[0013] The elastic clutch transmission mechanism, wherein the gear gear sets are respectively provided with a sun gear and at least one planetary gear corresponding to the sun gear, and the ratchet is provided at the inner edge of the sun gear.

[0014] The elastic clutch speed change mechanism, wherein the shaft center is further radially recessed with a limiting groove, and the speed change ring is arranged corresponding to the axial sliding and is limited in the limiting groove.

[0015] The elastic clutch speed change mechanism, wherein the speed change lever is provided with a spiral component on the outer edge, and the speed change lever is rotated so that the spiral component axially transmits the speed change ring.

[0016] The elastic clutch speed change mechanism further includes a shifting device, which is correspondingly connected and transmitted to the shift lever, so that the shift ring moves axially; the shifting device is driven automatically by electricity or manually; when the shifting device is driven automatically by electricity, the shifting device can be a DC motor or a stepping motor; when the shifting device is driven manually, it is a corresponding shift cable.

[0017] From the above description and configuration, it is obvious that the present invention mainly has the following advantages and effects, which are described in detail as follows:

[0018] 1. During a gear shift, the shift lever is driven by the shifting device, causing the shift ring to move to the corresponding gear clutch. The guide surface of the shift ring abuts against the elastic element of the corresponding gear clutch, causing the corresponding pawl to elastically expand outward and unidirectionally transmit power to the ratchet connected to the corresponding gear tooth set to shift the gear. The ratchet connected to the gear clutch of the non-corresponding gear will not transmit power to the gear tooth set, so that the gear clutch of the non-corresponding gear will not interfere with the gear tooth set. The shifting method of the present invention adopts the simplest gear transmission principle, which can significantly reduce the number of transmission parts and their relationships, thereby achieving the advantages of light weight, high transmission efficiency, and easy assembly and processing. The sequential configuration makes shifting control easier, eliminating the need to control multiple clutch devices simultaneously, avoiding excessive resistance when the pawls are disengaged, thereby achieving fast shifting and labor-saving effects. The number and complexity of the component configuration can also be simplified, thereby significantly reducing manufacturing and assembly costs.

[0019] 2. The present invention utilizes the speed difference of the gears during operation by providing the abutment component or the receiving component, and connects the adjacent gear tooth groups by means of friction through the abutment component or the receiving component, thereby generating additional gear shifting assistance and helping to achieve the advantage of minimizing the gear shifting device. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is a cross-sectional schematic diagram of the present invention.

[0021] Figure 2 It is a three-dimensional exploded schematic diagram of the present invention.

[0022] Figure 3 It is a schematic diagram of a three-dimensional exploded and enlarged view of the gear clutch device of the present invention.

[0023] Figure 4 This is a cross-sectional view and a schematic diagram of the use state of the present invention when the speed change ring is in the transmission state and the pawl is engaged during gear shifting.

[0024] Figure 5 This is a cross-sectional view and a schematic diagram of the use state of the present invention when the ratchet wheel separates the pawl during gear shifting.

[0025] Figure 6 This is a cross-sectional view and a schematic diagram of the use state of the present invention when the speed change ring is in a non-transmission state and the elastic ring body separates the pawls during gear shifting.

[0026] Figure 7 It is a cross-sectional schematic diagram of the configuration of a slider and a receiving component in another embodiment of the present invention.

[0027] Figure 8 FIG7 is a cross-sectional view and a schematic diagram of the use state of the present invention, which is based on FIG7 and assists the separation of the high-speed pawl by friction during downshifting.

[0028] Figure 9 FIG7 is a cross-sectional view of the speed change ring in the transmission state and a schematic diagram of the use state of the present invention based on FIG.

[0029] Reference numerals:

[0030] 1: axis;

[0031] 11: limit slot;

[0032] 2: gear lever;

[0033] 21: speed change ring;

[0034] 211: guide surface;

[0035] 212: limit pin;

[0036] 22: spiral component;

[0037] 3: Gear clutch device;

[0038] 31: pawl;

[0039] 311: clamping portion;

[0040] 312: fixing slot;

[0041] 32: elastic element;

[0042] 321: first elastic arm;

[0043] 322: second elastic arm;

[0044] 323: elastic connection part;

[0045] 324: card slot;

[0046] 33: elastic ring body;

[0047] 34: drive shaft;

[0048] 341: through slot;

[0049] 342: receiving tank;

[0050] 343: fixing groove;

[0051] 344: abutting component;

[0052] 345: slider;

[0053] 346: receiving component;

[0054] 347: connecting portion;

[0055] 4: gear gear group;

[0056] 41: ratchet;

[0057] 42, 42a, 42b, 42c, 42d: sun gear;

[0058] 421: junction;

[0059] 43, 43a, 43b, 43c, 43d: planetary gears;

[0060] 431: planetary axis;

[0061] 5: Power input device;

[0062] 6: Planet carrier. DETAILED DESCRIPTION

[0063] Regarding the technical means of our inventors, several preferred embodiments are now described in detail below with reference to the drawings to facilitate a deeper understanding and recognition of the present invention.

[0064] Please see first Figure 1 As shown, the present invention is an elastic clutch transmission mechanism, comprising:

[0065] An axis 1; used to be fixed to a suitable position on the bicycle frame, and can also be configured on the shell so that it cannot rotate or move;

[0066] A shift rod 2 is axially connected to and transmits to a shift ring 21. The shift ring 21 is provided with a guide surface 211 at one axial end. The shift ring 21 is correspondingly sleeved and axially slides on the shaft 1. In an embodiment, in order to limit the axial movement distance of the shift ring 21, the shaft 1 is further radially recessed with a limit groove 11. The shift ring 21 is provided with an axial sliding arrangement and is limited in the limit groove 11. In a specific embodiment, the shift ring 21 can be positioned in the limit groove 11 and axially slided by the shift ring 21 itself or by providing a limit pin 212, such as a latch or a flat key. However, this is for example only and is not intended to be limiting.

[0067] At least one gear clutch device 3 is provided with at least one pawl 31. One end of the pawl 31 is provided with an elastic element 32 corresponding to the guide surface 211. The guide surface 211 can be configured as an inclined surface or a conical surface, so as to facilitate the corresponding pushing of the elastic element 32 when the speed change ring 21 moves axially; and

[0068] At least one gear tooth set 4 is provided with a ratchet 41 corresponding to the pawl 31;

[0069] In this way, when in the non-transmission state, the guide surface 211 does not abut against the elastic element 32, and the pawl 31 is non-transmission-connected to the ratchet 41; and when in the transmission state, the guide surface 211 correspondingly abuts against the elastic element 32 of at least one of the gear clutch devices 3, so that the corresponding pawl 31 elastically expands outward and is unidirectionally connected to the ratchet 41, so that the gear shifting effect is achieved through the gear tooth group 4.

[0070] First, with regard to the axial transmission method of the shift lever 2 to the shift ring 21, the shift lever 2 is transmitted by configuring a shift device (not shown). In this embodiment, a spiral component 22 is provided on the outer edge of the shift lever 2. The shift lever 2 rotates to cause the spiral component 22 to axially transmit the shift ring 21. Therefore, by rotating the shift lever 2 through the shift device, the shift ring 21 can be moved back and forth in the axial direction. In other embodiments, the shift device can also control the shift lever 2 by a linear drive method to directly move the shift ring 21 longitudinally. In the linear drive method, the spiral component 22 may not be provided on the shift lever 2.

[0071] As for the driving mode of the gear shifting device, the gear shifting device can be driven electrically automatically or manually; when the gear shifting device is electrically automatically driven, the gear shifting device can be a DC motor or a stepper motor; when the gear shifting device is manually driven, it is a corresponding gear shift cable; in addition, the gear shifting device is driven by receiving gear shifting instructions in a wired or wireless manner, and can be configured as a DC motor or a stepper motor, and when a DC motor is used, it can include a potentiometer, a Hall sensor, an encoder or an eddy current sensor to ensure the control of the angle or distance, so as to ensure the control stroke of the speed ring; therefore, the user can select the gear manually or automatically, so that the gear shifting device can control the axial position of the speed ring 21 on the shaft 1 to complete the gear shifting control.

[0072] As for the configuration of the pawl 31, when the axial movement of the speed change ring 21 corresponds to the transmission state, the pawl 31 can expand outward and be transmission-connected to the ratchet 41. In the embodiment, one end of the pawl 31 is provided with a clamping portion 311 corresponding to the ratchet 41. Since the pawl 31 and the ratchet 41 are unidirectionally transmitted, the ratchet 41 has ratchet teeth that are unidirectionally configured, and the clamping portion 311 is a clamping configuration that can be unidirectionally transmitted to the ratchet teeth. When the pawl 31 is driven and rotated in one transmission direction, the ratchet 41 can be correspondingly driven to rotate. Conversely, when the pawl 31 rotates in the other direction, the pawl 31 is pressed by the ratchet teeth, so that the pawl 31 is empty. The elastic element 32 is provided with a first elastic arm 321 and a second elastic arm 322, and the first elastic arm 321 and the second elastic arm 322 are connected at a spring-connecting portion 323. The first elastic arm 321 is connected to the end of the pawl 31 away from the clamping portion 311, and the second elastic arm 322 is used to enable the guiding surface 211 to correspondingly abut when in the transmission state, so as to push the pawl 31 out through the spring-connecting portion 323 and the first elastic arm 321 and expand the one-way transmission connection to the ratchet 41.

[0073] When in the non-transmission state, the pawl 31 can be reset without expanding outward to prevent interference with the rotation of the gear clutch device 3 or the gear gear group 4. In the embodiment, an elastic ring body 33 can be provided in the gear clutch device 3, which is connected to the end of the corresponding pawl 31 relative to the elastic element 32. When in the non-transmission state, the elastic ring body 33 elastically shrinks to press against the pawl 31, so that the pawl 31 is non-transmission-connected to the ratchet 41. As far as its specific elastic configuration is concerned, since the elastic ring body 33 needs to be in In the non-transmission state, the pawl 31 is elastically retracted, and the elastic force must be slightly greater than the sliding friction force of the elastic element 32 when it is not in contact with the guide surface 211. In addition, when in the transmission state, in order to make the guide surface 211 contact the elastic element 32, the elastic element 32 can be pushed so that it can elastically push the pawl 31 radially outward. At this time, the elastic force of the elastic element 32 that is deformed by the force must be greater than the elastic force of the elastic ring body 33 in the retraction direction, so as to ensure that the elastic element 32 can be assembled and transmit power to the ratchet 41 in the transmission state.

[0074] To facilitate the configuration of the elastic ring 33, in a preferred embodiment, a fixing groove 312 is provided in the pawl 31, and a clamping groove 324 is provided in the elastic connection portion 323. The elastic ring 33 elastically abuts against the fixing groove 312 and the clamping groove 324, so that the elastic ring 33 can be securely buckled and apply elastic force to the pawl 31.

[0075] As for the power transmission configuration of the present invention, in a specific embodiment, a drive shaft 34 is provided, the gear gear set 4 is correspondingly and movably sleeved on the outer edge of the drive shaft 34, and the gear gear set 4 and the drive shaft 34 do not transmit each other, and the speed change ring 21 is axially displaced at the inner edge of the drive shaft 34; the drive shaft 34 is further axially cut with a through groove 341 corresponding to the gear clutch device 3 and the speed change ring 21, and the second elastic arm 322 is extended through the through groove 341 to extend through the drive shaft 34. The interior of the driving shaft 34 is used to enable the guiding surface 211 to correspondingly abut the second elastic arm 322 when in the transmission state; thereby, the driving shaft 34 can be used for transmission and correspondingly configured on 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 will be pushed by the guiding surface 211 and assembled with the ratchet 41 in the transmission state, thereby achieving the gear shifting effect through the gear ratio of the gear tooth group 4.

[0076] As for the transmission configuration between the drive shaft 34 and the pawl 31, in order to facilitate the positioning of the pawl 31 in the non-transmission state, in the embodiment, the outer ring surface of the drive shaft 34 is respectively provided with a receiving groove 342 and a fixing groove 343 on both sides of the through groove 341. The pawl 31 is placed in the receiving groove 342 at one end relative to the clamping portion 311, and the elastic connection portion 323 is correspondingly located in the fixing groove 343, so as to facilitate the positioning and assembly configuration.

[0077] As for the configuration of the gear gear set 4, in a preferred embodiment, the gear 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 41 is provided at the inner edge of the sun gear 42, thereby achieving the gear transmission effect by configuring the number and gear ratio of the sun gear 42 and the planetary gear 43; and for the overall positioning of the present invention, a planetary carrier 6 can be configured to correspond to the axis 1, and to correspond to the gear gear set 4 and the gear clutch device 3 of the present invention, and to limit the center distance of the rotation of the planetary gear 43, and the planetary gears 43 corresponding to different gear gear sets 4 are pivotally connected through a planetary shaft 431; the number of gear gear sets 4 and the gear clutch device 3 can be configured according to the number of gears. In this embodiment, four groups of gear gear sets 4 and gear clutch devices 3 are configured, but this is only an exemplary description and is not intended to be limiting.

[0078] In this embodiment, the arrangement of the gear teeth group 4 can be arranged in an increasing or decreasing manner according to the corresponding gears. Therefore, the sun gears 42a to 42d are arranged in axial order from the first gear to the fourth gear, and they are respectively configured with the planetary gears 43a to 43d. In addition, the sun gears 42a to 42d respectively correspond to the pawls 31 of the corresponding gear clutch device 3; thereby, as shown in FIG. Figure 1 and Figure 2 As shown, when the gear is changed to the fourth gear, the gear lever 2 will transmit the speed ring 21 to the pawl 31 of the gear clutch device 3 corresponding to the sun gear 42d, so as to Figure 4As shown, the guide surface 211 will correspond to the second elastic arm 322, so that the elasticity between the first elastic arm 321, the second elastic arm 322 and the elastic connection portion 323 can push the pawl 31 radially out of the drive shaft 34, so that the pawl 31 can be connected to the ratchet 41 of the sun gear 42d for transmission. Then, the power can be transmitted to the sun gear 42d and its corresponding planetary gear 43d through the pawl 31 through the drive shaft 34. Since the planetary shaft 431 is non-circular, the planetary gear 43 transmits its power to the planetary shaft 431 and makes the other corresponding matching The remaining planetary gears 43 on the planetary shaft 431 rotate at the same speed at the same time, and the planetary gears 43a to 43c will also be correspondingly transmitted to the sun gears 42a to 42c located in the first to third gears. Because the gear is in the fourth gear at this time, the pawl 31 of the first to third gears is in a non-transmission state. Therefore, the pawl 31 is not connected to the ratchet 41 for mutual transmission. The sun gears 42a to 42c only rotate arbitrarily on the drive shaft 34 and do not interfere with the power of the fourth gear; the aforementioned gear and quantity configuration is only for illustration and is not intended to be limiting.

[0079] During the gear shifting operation, refer to Figure 1 and Figure 4 As shown, when the speed change ring 21 moves from the third gear to the fourth gear, or from the fourth gear to the third gear, the speed change ring 21 will first contact the elastic element 32 of the target gear before leaving the current gear, so that the corresponding pawl 31 is ejected. Although the pawls 31 of the current gear and the target gear are ejected at the same time, the number of teeth of the sun gear 42 and the meshing planetary gear 43 of each gear are different. The planetary gear 43 rotates at a constant speed by the planetary shaft 431, and the planetary gear 43 of the lower gear rotates at a constant speed. The gear ratio transmitted to the sun gear 42 is greater than the gear ratio of the higher gear. The drive shaft 34 engages with the higher gear sun gear 42 via the pawl 31. The sun gear 42 of the lower gear rotates faster than the drive shaft 34. Therefore, the ratchet 41 pushes the pawl 31 to compress the elastic element 32 to separate it, achieving simultaneous shifting and shifting. The elastic clutch ensures that the shifting process will not cause transmission idling or transmission lockup, and eliminates the need for multiple clutch control gaps, thereby shortening the shift response time.

[0080] Please continue to see Figures 4 to 6 As shown in the radial cross-sectional view of the clutch actuation state of each gear during the aforementioned shifting process, when the speed change ring 21 pushes and rotates the elastic element 32 to cause the pawl 31 to push out and open the elastic ring body 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 in the clockwise direction, as shown in FIG. Figure 4As shown, during the speed change process, the speed change ring 21 will also push the elastic element 32 in the moving stroke, so that the pawl 31 pushes out and opens the elastic ring body 33; since the sun gear 42c of the third gear also rotates clockwise and its speed is faster than the drive shaft 34, the ratchet 41 of the sun gear 42c will push the corresponding pawl 31, so that the corresponding elastic element 32 is compressed and deformed to separate, as shown in FIG. Figure 5 As shown; instead of the gear shift gear set 4 and the gear clutch device 3, since the elastic element 32 is not pushed by the speed ring 21, the elastic ring body 33 will retract the corresponding pawl 31 into the drive shaft 34, so that the sun gear 42a and 42b and the drive shaft 34 are separated, as shown Figure 6 As shown, when shifting to a specific gear, only the corresponding gear gear set 4 and the gear clutch device 3 can transmit to each other, and the sun gears 42 of the other gears will all idle on the drive shaft 34 without interfering with power transmission.

[0081] In a preferred embodiment, in order to facilitate the smooth pulling of the sun gears 42 of the other gears when running in the set gear, an abutment component 344 can be provided, which can be a wave spring or a disc spring in the embodiment, which is sleeved on one end of the drive shaft 34 and elastically abuts against at least one of the gear tooth groups 4 in the corresponding axial direction, so that the sun gears 42 on the drive shaft 34 fit together and increase their contact friction, so that the sun gear 42 can pull the adjacent gears when rotating, thereby providing additional assistance to the shift claw during transmission.

[0082] In another specific embodiment, the abutment component 344 may not be provided on the drive shaft 34, and at least one slider 345 corresponding to the guide surface 211 may be provided between adjacent gear tooth groups 4. The slider 345 is provided with a receiving component 346 at one end opposite to the guide surface 211. The receiving component 346 may also be provided in the form of an elastic ring. The receiving component 346 is provided with at least one connecting portion 347, and the gear tooth groups 4 are respectively provided with a coupling portion 421 corresponding to the connecting portion 347. In the embodiment, the coupling portion 421 is provided on the sun gear 42, and when the guide surface 211 abuts against the slider 345, the slider 345 pushes against the receiving component 346, so that the corresponding connecting portion 347 is connected to the corresponding coupling portion 421. In this way, Figure 7As shown, when the gear shift control is performed, the movement process of the speed change ring 21 pushes the slider 345 to radially and outwardly expand the receiving part 346, so that the connecting part 347 of the receiving part 346 and the connecting part 421 of the two adjacent sun gears 42 are mutually connected to form friction contact. By virtue of the faster rotation speed of the sun gear 42 at the lower gear, the sun gear 42 at the higher gear is provided with additional friction assistance, making it easier for the ratchet 31 corresponding to the sun gear 42 at the higher gear to retract during gear shifting. When the gear shifting action is completed, the speed change ring 21 moves to the sun gear 42 corresponding to the target gear, so that The slider 345 is not pushed out by the speed ring 21. The stretched receiving part 346 retracts the slider 345 inward into the drive shaft 34 through its own elastic contraction, so that the connecting part 347 of the receiving part 346 disengages from the sun gears 42 on both adjacent sides, and releases the friction contact connection. Its configuration does not affect the transmission connection between the aforementioned gear tooth group 4 and the gear clutch device 3. The faster rotation speed of the sun gear 42 of the lower gear can push the corresponding pawl 31 to compress the corresponding elastic element 32 to produce deformation and separate it, thereby guiding the transmission power to assist the power required for shifting and retracting the pawl.

[0083] As mentioned above, when downshifting, the speed change ring 21 moves from the fourth gear to the third gear by first pushing out the slider 345 to open the receiving member 346, so that the connecting parts 347 on both sides of the receiving member 346 are in frictional contact with the joint part 421 of the adjacent sun gear 42. The speed change ring 21 continues to move and pushes the spring piece of the third gear to open the corresponding elastic ring body 33, so that the sun gear 42c of the third gear corresponding to the pawl 31 is ready to engage the ratchet wheel 41 to enter the gear. Please refer to the following for details. Figure 8 and Figure 9 As shown, it is a radial cross-sectional view of the third and fourth gears in the gear-shift assist actuation state. When the transmission is in progress, as shown in FIG. Figure 9 As shown, the drive shaft 34 transmits power to the sun gear 42d corresponding to the fourth gear through the pawl 31. The planetary gear 43d corresponding to the fourth gear rotates in the opposite direction of the transmission direction. The non-circular structure allows it to rotate along the planetary shaft 431 and contact the non-circular structure of the planetary shaft 431 for transmission, so that all the planetary gears 43 configured on the planetary shaft 431 rotate at the same speed. Therefore, the power is transmitted to the sun gear 42c of the third gear through the engagement of the planetary gear 43c of the third gear. Figure 8As shown, the number of teeth of the planetary gear 43c in the third gear is greater than that of the planetary gear 43d in the fourth gear, and the number of teeth of the sun gear 42c in the third gear is less than that of the sun gear 42d in the fourth gear. Therefore, the rotation speed of the sun gear 42c in the third gear is faster than that of the sun gear 42d in the fourth gear. The faster rotation speed power of the sun gear 42c in the third gear is transmitted to the sun gear 42d in the fourth gear by the receiving component 346, thereby assisting the sun gear 42d in the fourth gear to increase the rotation speed and disengage the corresponding pawl 31 from the ratchet 41. After the speed change ring 21 pushes out the pawl 31 in the third gear, The downshifting process will continue to manipulate the speed change ring 21 to move toward the third gear, so that it first releases the elastic element 32 of the fourth gear, causing the elastic ring body 33 of the fourth gear to contract and simultaneously act with the auxiliary force of the receiving component 346 to retract the pawl 31 into the drive shaft 34, thereby overcoming the self-locking characteristics of the pawl 31. Then the speed change ring 21 moves and releases the slider 345, causing the receiving component 346 to contract and retract the slider 345 into the drive shaft 34. When the speed change ring 21 moves to the corresponding third gear, the sun gear 42c of the third gear engages with its corresponding pawl 31 to enter the gear, thus completing the downshifting operation.

[0084] In summary, the technical means disclosed in the present invention can indeed effectively solve common problems and achieve the expected purpose and effect. It has not been publicly used in publications before the application and has long-term progressiveness. It is indeed an invention as defined in the Patent Law. Therefore, I have filed an application in accordance with the law and sincerely hope that you will review it in detail and grant me the invention patent. I am very pleased.

[0085] The above descriptions are merely several preferred embodiments of the present invention and are not intended to limit the scope of the present invention. In other words, any equivalent changes and modifications made within the scope of the present invention and the contents of the invention specification shall still fall within the scope of the present invention.

Claims

1. An elastic clutch transmission mechanism, characterized in that: Include: One axis; a shift rod, the shift rod being axially connected to and transmitting to a shift ring, the shift ring being correspondingly sleeved and axially sliding on the axis, the shift ring being provided with a guide surface at one axial end, and the axial movement distance of the shift ring being limited; At least one 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 surface; at least one gear tooth set, provided with a ratchet corresponding to the pawl; and At least one elastic ring body is connected to one end of the corresponding pawl opposite to the elastic element. When in a non-transmission state, the elastic ring body elastically contracts to press against the pawl, and the guiding surface does not abut against the elastic element. The pawl is non-transmission-connected to the ratchet; when in a transmission state, the guiding surface correspondingly abuts against the elastic element of at least one of the gear clutch devices, and the corresponding pawl elastically expands outward and is unidirectionally connected to the ratchet.

2. The elastic clutch transmission mechanism according to claim 1, wherein: The pawl is provided with a clamping 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 at the elastic connection portion, the first elastic arm is connected to the end of the pawl away from the clamping portion, and the second elastic arm is used to make the guiding surfaces correspondingly abut in the transmission state, so that the pawl expands outward and is connected to the ratchet wheel in a one-way transmission.

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

4. The elastic clutch transmission mechanism according to claim 2, wherein: It comprises a driving shaft, the gear gear set 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 change ring, and the second elastic arm extends through the interior of the driving shaft through the through groove, so that the guide surface can correspondingly abut the second elastic arm when in the transmission state.

5. The elastic clutch transmission mechanism according to claim 4, characterized in that: The invention comprises an abutting component which is sleeved on one end of the driving shaft and abuts against at least one of the gear teeth in the axial direction.

6. The elastic clutch transmission mechanism according to claim 4, characterized in that: Between adjacent gear tooth groups, there is respectively provided at least one slider corresponding to the guide surface, and the slider is provided with a receiving component at one end opposite to the guide surface, and the receiving component is provided with at least one connecting portion, and the gear tooth groups are respectively provided with a connecting portion corresponding to the connecting portion. When the guide surface abuts against the slider, the slider pushes against the receiving component, so that the corresponding connecting portion is connected to the corresponding connecting portion.

7. The elastic clutch transmission mechanism according to any one of claims 1 to 6, characterized in that: The shift gear sets are respectively provided with a sun gear and at least one planetary gear corresponding to the sun gear, and the ratchet is provided at the inner edge of the sun gear.

8. The elastic clutch transmission mechanism according to any one of claims 1 to 6, characterized in that: The shaft center is further radially recessed with a limiting groove, and the speed change ring is arranged to slide in the axial direction and is limited in the limiting groove.

9. The elastic clutch transmission mechanism according to any one of claims 1 to 6, characterized in that: A spiral component is provided on the outer edge of the shift lever, and the shift lever is rotated so that the spiral component axially transmits the shift ring.

10. The elastic clutch transmission mechanism according to any one of claims 1 to 6, characterized in that: It includes a shifting device, which is correspondingly connected and transmitted to the shifting rod, so that the shifting ring moves axially; the shifting device is driven automatically by electricity or manually; when the shifting device is driven automatically by electricity, the shifting device can be a DC motor or a stepping motor; when the shifting device is driven manually, it is a corresponding shifting cable.

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