TWI795237B - Flexible clutch transmission mechanism - Google Patents

Abstract

The present invention provides a flexible clutch transmission mechanism, comprising an axle, a gear shifting lever, at least a clutch and at least a cluster gear. The gear shifting lever connects and drives a shift ring in axial direction. At one end of the shift ring sets a lead surface. Each clutch sets at least a pawl which has a flexible element corresponding to the lead surface on its one end. The cluster gear sets a ratchet corresponding to the pawl. Therefore, the gear shifting lever can be driven by a gear shifting device to make the shift ring correspondingly move to the corresponding-gear clutch when gears are shifted to change speed. It makes the lead surface correspondingly abut the flexible element of corresponding-gear clutch to let the said corresponding pawl flexibly expand and unidirectionally drive the ratchet of corresponding cluster gear for conducting gear shifting. As for non-corresponding-gear clutch, the ratchet will not drive the said cluster gear so that the non-corresponding-gear clutch will not interfere the said cluster gear. In addition, the invention can include an abutting component or bearing component to utilize the difference of rotational speed of gear rotating and friction force to connect cluster gear in sequential interdependence, which generates extra support force when gear shifting. Hence, it is obvious that the configuration of the present invention can achieve the efficacy of rapid gear shifting and effort saving.

Description

Elastic clutch transmission mechanism

The present invention provides an elastic clutch speed change mechanism, especially a gear shifting mechanism through an axial transmission speed change ring, which can also be adapted to the gear shifting of a bicycle internal speed changer.

According to the rising awareness of environmental protection and fitness in today's society, countries around the world are implementing energy-saving and carbon-reducing policies to reduce energy demand and pollution problems. Therefore, the promotion of bicycles is one of the solutions, and can be used for transportation or sports and leisure purposes; for 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.

In order to cope with the development of electric assisted bicycles, the automation and intelligence of riding controls are more research focus. However, the external transmission system can only complete the gear change when driving, and it cannot directly change multiple gears and there is a risk of chain loss, etc. Maneuvering characteristics, resulting in the automatic shift control strategy is greatly limited.

Therefore, many people have conducted related research on internal transmissions, and the vast majority of internal transmissions use a planetary gear train transmission mechanism, and simultaneously control multiple pawl sets for clutch control, so that the target transmission parts and the shaft cannot be fixed. Rotation, although this method has more changes in the speed range, but its mechanism is complicated, the number of parts is large, the processing precision is high, and the cost is higher. In addition, the pawl has a certain self-locking ability when it is engaged to prevent decoupling during transmission. It causes slippage, but this feature makes the resistance of the gear shifting and retracting claws relatively large, which is not conducive to the operation of the electronic shifting device, especially the load on the claws caused by the gear shifting during pedaling is even more serious, and it is even more severe when operating multiple pawl groups at the same time For this, how to make further technical innovations to achieve a more streamlined structure, lower costs and lighter shift resistance to adapt to the subject of electronic shift manipulation is an urgent goal for the industry to break through.

In view of this, our inventors are concentrating on further research on the clutch-type transmission mechanism, and proceed to research and development and improvement, hoping to solve the above problems with a better invention, and after continuous testing and modification, the present invention comes out .

Yes, the purpose of the present invention is to solve the aforementioned problems, expect to provide a transmission device with simple mechanism, good reliability, and easy processing and assembly, and can easily perform one-way clutch control, while reducing the time required for gear shifting. resistance, in order to achieve the above purpose, our inventors provide an elastic clutch speed change mechanism, which includes: a shaft; and axially slide on the axis, and the speed change ring is provided with a guide surface at one end in the axial direction; at least one gear clutch device is provided with at least one pawl respectively, and the pawl is provided at one end There is an elastic element corresponding to the guide surface; and at least one gear tooth set, which is provided with a ratchet corresponding to the pawl; whereby in a non-transmission state, the guide surface is not in contact with the said guide surface. The elastic element, and the non-transmission of the pawl is connected to the ratchet wheel; and in a transmission state, the guide surface is correspondingly abutted against the elastic element of at least one of the gear clutch devices, so that the corresponding The ratchet is elastically expanded and connected to the ratchet in one-way transmission.

According to the above-mentioned elastic clutch transmission mechanism, wherein, the pawl is further provided with a locking part at one end; and the elastic element is provided with a first elastic arm and a second elastic arm, and the first elastic The arm and the second elastic arm are connected to an elastic connection part, and the first elastic arm is connected to the end of the pawl away from the engaging part, and the second elastic arm is used to In the transmission state, the guide surfaces are correspondingly abutted against, so that the pawl is expanded outwards and connected to the ratchet wheel through one-way transmission.

According to the above-mentioned elastic clutch transmission mechanism, wherein, the gear clutch device is further provided with an elastic ring, which is connected to the end of the corresponding pawl opposite to the elastic element, for use in the non-transmission state. At this time, the elastic ring system is elastically retracted to press against the ratchet, so that the ratchet is non-transitively connected to the ratchet.

According to the above-mentioned elastic clutch transmission mechanism, wherein, the pawl is further provided with a fixing groove, and the elastic connection part is provided with a card groove, and the elastic ring system is correspondingly elastically abutted against the fixing groove and the Those in the card slot.

According to the above-mentioned elastic clutch speed change mechanism, it further includes a drive shaft, the gear gear set 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 provided with a through slot corresponding to the gear clutch device and the speed change ring, and the second elastic arm is passed through the inside of the drive shaft through the through slot, It is used to make the guiding surface abut against the second elastic arm correspondingly in the transmission state.

According to the above-mentioned elastic clutch speed change mechanism, it further includes an abutting part, which is sleeved on one end of the drive shaft, and correspondingly axially resists at least one of the gear tooth sets.

According to the above-mentioned elastic clutch transmission mechanism, wherein, at least one slider corresponding to the guide surface is provided between the adjacent gear tooth groups, and the slider is opposite to the guide surface. One end is provided with a receiving part, and the receiving part is provided with at least one connecting part, and the gear tooth sets are respectively provided with a connecting part corresponding to the connecting part, and when the guiding surface abuts against the slider , the slider is correspondingly pushed against the receiving part, so that the corresponding connecting part is combined with the corresponding connecting part.

According to the above-mentioned elastic clutch transmission mechanism, wherein, the gear tooth sets 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.

According to the above-mentioned elastic clutch speed change mechanism, wherein, the shaft center is further radially recessed with a limit groove, and the speed change ring is set corresponding to axial sliding and is limited in the limit groove.

According to the above-mentioned elastic clutch transmission mechanism, wherein, the gear lever is further provided with a helical part on its outer edge, and the gear lever is rotated so that the helical part drives the transmission ring axially.

According to the above-mentioned elastic clutch transmission mechanism, it further includes a shifting device, which is correspondingly connected and transmitted to the shift lever, so that the shifting ring can move axially; and the shifting device is carried out automatically or manually Drive; and when the shifting device is electric automatic drive, the shifting device can be a DC motor or a stepping motor; and when the shifting device is manual, it is the corresponding shifting cable.

By the above description and setting, it is obvious that the present invention mainly has the following advantages and effects, which are detailed as follows one by one:

1. In the present invention, when shifting is required, the shift lever is driven through the shift device, so that the shift ring can be moved to the gear clutch device corresponding to the corresponding gear, so that the guide surface of the shift ring can be correspondingly abutted against the corresponding gear. The elastic element of the gear clutch device of the gear position makes the corresponding pawl expand elastically and unidirectionally drive the ratchet wheel connected to the corresponding gear tooth set to switch gears, not the gears of the corresponding gears In the clutch device, the ratchet wheel will not be connected to the gear tooth set without transmission, so that the gear clutch device of the non-corresponding gear will not interfere with the gear tooth set; the shifting method of the present invention is the most convenient one. The principle of gear transmission can significantly reduce the number of transmission parts and the relationship between them, so as to achieve the advantages of light weight, high transmission efficiency, and easy assembly and processing, and its sequential configuration makes shifting control easier, and it is not necessary to control multiple groups at the same time. The clutch device avoids excessive resistance when the claws are separated, so it can achieve quick shifting and labor-saving effects, and can simplify the number and complexity of parts configuration, thereby greatly reducing its manufacturing and assembly costs.

2. Through the setting of the abutment part or the receiving part, the present invention can utilize the difference in speed when the gear is running, and connect the adjacent gear tooth groups in the form of friction through the abutting part or the receiving part, making it The power to generate additional shifting helps to realize the advantage of miniaturization of the shifting device.

Regarding the technical means of our inventors, several preferred embodiments will be described in detail below in conjunction with the drawings, so as to provide an in-depth understanding and recognition of the present invention.

Please refer to Fig. 1 first, the present invention is an elastic clutch speed change mechanism, which includes:

An axis 1; it is used to be fixed at a suitable place on the frame of a bicycle, and it can also be arranged on a shell so that it cannot rotate or move;

A speed change rod 2, which is axially connected and transmitted to a speed change ring 21, the speed change ring 21 is provided with a guide surface 211 at one end of the axial direction, and the speed change ring 21 is correspondingly sleeved and axially slid on the The axis 1, in one embodiment, is to limit the axial movement distance of the transmission ring 21, so the axis 1 is further recessed with a limit groove 11 in the radial direction, and the transmission ring 21 is correspondingly axially slipped Set and limited in the limit groove 11, and in a specific embodiment, the speed change ring 21 can be fixed through the speed change ring 21 itself, or by setting a limit pin 212, such as: a bolt or a flat key. Locate in the limit groove 11 and slide it axially, but it is only for illustration and not as a limitation;

At least one gear clutch device 3, which is respectively provided with at least one ratchet 31, and said ratchet 31 is provided with an elastic element 32 corresponding to the guide surface 211 at one end, and as far as the guide surface 211 is concerned, its It can be configured as an inclined surface or a conical surface, so as to facilitate the axial movement of the speed change ring 21, and push the elastic element 32 correspondingly; and

At least one gear tooth set 4, which is provided with a ratchet 41 corresponding to the pawl 31;

Thereby, in a non-transmission state, the guide surface 211 is not in contact with the elastic member 32, and the ratchet 31 is non-transmission connected to the ratchet wheel 41; and in a transmission state, the The guide surface 211 is correspondingly abutted against the elastic member 32 of at least one of the gear clutch devices 3, so that the corresponding pawl 31 is elastically expanded and connected to the ratchet wheel 41 in one-way transmission, so that through The gear gear group 4 is to achieve the effect of gear shifting.

First of all, as far as the gear lever 2 is concerned with the axial transmission mode of the gear shift ring 21, a gear shift device (not shown in the figure) is configured to transmit the gear lever 2. In this embodiment, A helical part 22 is provided on its outer edge through the shift lever 2, and the shift lever 2 is rotated so that the helical part 22 axially drives the shift ring 21, so the shift lever 2 is rotated by the shifting device, that is It can make the transmission ring 21 move back and forth in the axial direction; and in other embodiments, the transmission device can also control the transmission lever 2 through a linear drive method to directly move the transmission ring 21 longitudinally, while its linear drive method can not A screw member 22 is provided on the shift lever 2 .

As for the driving method of the shifting device, the shifting device can be driven automatically or manually; and when the shifting device is automatically driven by electricity, the shifting device can be a DC motor or a stepper motor; and when the shifting device is manually operated, it is the corresponding shifting line; in addition, the shifting device is driven by receiving shift commands by wired or wireless means, and it can be configured as a DC motor or a stepper Motor, and when a DC motor is used, it may contain potentiometers, Hall sensors, encoders or eddy current sensors to ensure the control of its angle or distance, so that it can ensure the control travel of the speed change ring; Therefore, the user can select a gear manually or automatically, so that the shifting device can control the position of the shifting ring 21 in the axial direction of the shaft center 1 to complete the shifting control.

As far as the configuration of the ratchet 31 is concerned, in order to make the axial movement of the speed change ring 21 correspond to the transmission state, the ratchet 31 can be expanded and connected to the ratchet 41 in transmission, so in one embodiment, the One end of the ratchet 31 is further provided with a locking portion 311 corresponding to the ratchet 41, and since the ratchet 31 and the ratchet 41 are in one-way transmission, it can be seen that the ratchet 41 has ratchets arranged in one direction. And the clamping portion 311 is a clamping configuration that can be driven in one direction on the ratchet, so that when the pawl 31 is driven to rotate in one transmission direction, it will be able to rotate the ratchet wheel 41 correspondingly. When the direction rotates, the ratchet 31 will be pressed against by the ratchet teeth, so that the ratchet 31 will run idle and cannot be transmitted to the ratchet 41. Its specific configuration is a known technology, so it will not be described in detail here; There is 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 to an elastic joint 323, and the first elastic arm 321 is connected to It is located at the end of the ratchet 31 away from the engaging portion 311 , and the second elastic arm 322 is used to make the guiding surface 211 abut against it in the transmission state, so as to pass through the engaging portion 323 and the first elastic arm 321 to push out the ratchet 31 and expand outward to connect to the ratchet wheel 41 in a one-way transmission.

And in order to make in non-transmission state, ratchet 31 can reset and does not expand outwards, to prevent the rotation of gear clutch device 3 or gear gear 4 from causing interference, so in one embodiment, it can be used in all gears. The gear clutch device 3 is respectively provided with an elastic ring body 33, which is connected to the corresponding end of the pawl 31 opposite to the elastic element 32, so that the elastic ring body 33 is elastic in the non-transmission state. shrink to press against the ratchet 31, so that the ratchet 31 is connected to the ratchet 41 in a non-transmission manner. As far as its specific elastic configuration is concerned, since the elastic ring body 33 needs to be in a non-transmission state, the ratchet will 31 is elastically retracted because its elastic force system needs to be slightly greater than the sliding friction force of the elastic element 32 when it is not abutted by the guiding surface 211. In addition, in the transmission state, in order to make the guiding surface 211 abut the elastic element 32 At this time, the elastic element 32 can be pushed by it so that it can elastically push the pawl 31 radially outward, so the elastic force of the elastic element 32 deformed by force must be greater than the elasticity of the elastic ring body 33 in the direction of retraction. force to ensure that the elastic element 32 can be assembled and transmitted to the ratchet wheel 41 in the transmission state.

In order to facilitate the configuration of the elastic ring body 33, in a preferred embodiment, a fixing groove 312 is provided on the pawl 31, and a locking groove 324 is provided on the elastic joint portion 323, and the elastic ring The body 33 is elastically abutted against the fixing groove 312 and the locking groove 324 , so that the elastic ring body 33 can be firmly engaged and apply elastic force to the ratchet 31 .

As far as the power transmission configuration of the present invention is concerned, in a specific embodiment, a drive shaft 34 is provided, and the gear tooth set 4 is correspondingly movably sleeved on the outer edge of the drive shaft 34, and the gear The gear set 4 and the drive shaft 34 are not mutually transmitted, and the transmission ring 21 is axially displaced at the inner edge of the drive shaft 34; The through groove 341 of the position clutch device 3 and the transmission ring 21, and the second elastic arm 322 is passed through the through groove 341 to pass through the inside of the drive shaft 34, and is used to make the drive shaft 34 in the transmission state. The guiding surface 211 can correspond to abut against the second elastic arm 322; thereby, the drive shaft 34 can be used for transmission and is correspondingly arranged on a power input device 5, so that the power input device 5 can drive the drive shaft 34 accordingly. Correspondingly, the ratchet 31 is driven to rotate through the through groove 341, and as mentioned above, the ratchet 31 will be pushed by the guide surface 211 and assembled with the ratchet 41 in the transmission state, so as to pass through the gear teeth. 4 gear ratio to achieve the effect of gear change.

As far as the transmission arrangement between the drive shaft 34 and the ratchet 31 is concerned, in order to facilitate the positioning of the ratchet 31 in the non-transmission state, in one embodiment, the outer ring surface of the drive shaft 34 is in the through groove. The two sides of 341 are respectively recessed with an accommodating groove 342 and a fixed groove 343, and the pawl 31 is placed in the accommodating groove 342 at the end opposite to the clamping portion 311, and the elastic joint portion 323 is correspondingly located in the fixed groove. In the slot 343, it is convenient for its positioning and assembly configuration.

Also regarding 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 sun gear 42 The inner edge is provided with the ratchet 41, whereby the effect of gear transmission can be achieved through the number and gear ratio configuration of the sun gear 42 and the planetary gear 43; and for the overall positioning of the present invention, Therefore, a planetary carrier 6 can be configured to correspond to the shaft center 1, and to cover the gear teeth set 4 and the gear clutch device 3 of the present invention, and thereby limit the center distance of the rotation of the planetary gear 43, And between the planetary gears 43 corresponding to each other of the different gear tooth groups 4, the transmission pivot is carried out through a planetary shaft 431; It can be configured according to the number of gears, and in this embodiment, four sets of gear teeth 4 and gear clutches 3 are configured, but it is only an exemplary description and is not intended as a limitation.

In the present embodiment, the arrangement of the gear tooth sets 4 can be arranged in an increasing or decreasing manner through the corresponding gears, so the sun gears 42a to 42d will be arranged axially according to the first gear to the fourth gear. sequence, and it is respectively corresponding to the planetary gears 43a to 43d, and the sun gears 42a to 42d are respectively corresponding to the pawls 31 of the gear clutch device 3; thereby, as shown in Fig. 1 And as shown in Figure 2, when the gear position is changed to the fourth gear position, the shift lever 2 will transmit the speed change ring 21 to the pawl 31 of the gear clutch device 3 corresponding to the sun gear 42d, so as to As shown in the figure, the guide surface 211 will be able to abut against the second elastic arm 322 correspondingly, so that through the elasticity between the first elastic arm 321, the second elastic arm 322 and the elastic connection part 323, the pawl 31 can be radially Eject the drive shaft 34, so that the ratchet 31 can be connected with the ratchet 41 of the sun gear 42d, and then the power can be transmitted to the sun gear 42d and its corresponding planetary gear 43d through the drive shaft 34 through the ratchet 31, and Because the planetary shaft 431 is non-circular, the planetary gear 43 is the planetary shaft 431 that transmits its power, and the other planetary gears 43 corresponding to the planetary shaft 431 are all rotated at the same speed at the same time. Therefore, The planetary gears 43a to c will also be correspondingly transmitted to the sun gears 42a to 42c located in the first to third gears, but the gears at this time are located in the fourth gears, so the pawls 31 of the first to third gears It is in the non-transmission state, therefore, its ratchet 31 is not connected with the ratchet wheel 41. Therefore, the sun gears 42a to c are only arbitrarily rotating on the drive shaft 34, and do not interfere with the power of the fourth gear; and The aforementioned stalls and quantity configurations are examples only, and are not intended to be limiting.

And during the operation process of shifting, please refer to those shown in Fig. 1 and Fig. 4, if the speed change ring 21 rises to the fourth gear in the third gear, or drops from the fourth gear to the third gear When moving, before the shifting ring 21 leaves the current gear, it will first contact the elastic element 32 that pushes the target gear to push the corresponding pawl 31 out, and the pawl 31 of the current gear and the target gear pushes out at the same time However, the number of teeth of the sun gear 42 and the meshing planetary gear 43 of each gear is different, and the planetary gear 43 is rotated at a constant speed by the planetary shaft 431, and the planetary gear 43 with a lower gear is transmitted to the sun gear 42 The gear ratio of the higher gear is greater than the gear ratio of the higher gear, so the drive shaft 34 engages with the sun gear 42 of the higher gear through the ratchet 31, and the sun gear 42 of the lower gear rotates faster than the drive shaft 34, so the ratchet gear 41 will push the pawl 31 and compress the elastic element 32 to make it separate, so as to realize the gear shifting operation at the same time, and the elastic clutch ensures that the shifting process will not cause the transmission idling or the transmission lockup, and it does not need much The gap between the group clutch control can shorten the shift response time.

Please refer to Figures 4 to 6, which are the radial cross-sectional views of the clutch actuation state of each gear during the aforementioned shifting process. When the speed change ring 21 pushes the elastic element 32, the ratchet 31 is ejected and stretched. When the elastic ring body 33 engages the ratchet wheel 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 clockwise synchronously, as shown in Figure 4, and the speed change In the process of gear shifting, the speed change ring 21 also pushes and rotates the elastic element 32 in the moving stroke, so that the ratchet 31 pushes out and stretches the elastic ring body 33; but because the sun gear 42c of the third gear also rotates clockwise and the speed Faster than the drive shaft 34, therefore, 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 make it separate, as shown in Figure 5; instead of gear shifting The gear teeth group 4 and the gear clutch device 3, because the elastic element 32 is not pushed by the speed change ring 21, the elastic ring body 33 will make the corresponding ratchet 31 retract in the drive shaft 34, so that the sun gear 42a and 42b are separated from the drive shaft 34, as shown in the sixth diagram; therefore, when shifting to a specific gear position, only the corresponding gear tooth set 4 and the gear clutch device 3 can transmit each other, and the rest The sun gears 42 of the gear positions will all idle on the drive shaft 34 without interfering with power transmission.

In a preferred embodiment, in order to facilitate the operation of the set gear, the sun gear 42 of the remaining gears can be smoothly pulled, so a contact member 344 can be set, which can be used in one embodiment. It is a wave spring or disc spring, which is sleeved on one end of the drive shaft 34, and resists at least one of the gear tooth sets 4 corresponding to the axial elasticity, so that the sun gear on the drive shaft 34 42 fit each other and increase its contact friction, so that the adjacent gears can be pulled when the sun gear 42 rotates, so as to provide extra power for shifting and retracting claws during transmission.

In another specific embodiment, the abutment member 344 may not be provided on the drive shaft 34, but between the adjacent gear tooth sets 4, at least one corresponding to the guide surface 211 is further provided. The slider 345, and the slider 345 is provided with a receiving part 346 at one end opposite to the guide surface 211, the receiving part 346 can also be arranged as an elastic ring, and the receiving part 346 is provided with at least one connecting part 347, and The gear tooth set 4 is respectively provided with a coupling portion 421 corresponding to the coupling portion 347. In one embodiment, the coupling portion 421 is provided on the sun gear 42 and abuts against the guide surface 211. When pushing against the slider 345, the slider 345 is correspondingly pushed against the receiving part 346, so that the corresponding connecting portion 347 is combined with the corresponding connecting portion 421; thereby, as shown in Fig. 7 As shown, when the shifting control is carried out, the moving process of the speed change ring 21 will push the slider 345 to make it radially and outwardly stretch the receiving part 346, so that the connecting part 347 of the receiving part 346 is connected to the adjacent two sun gears. The joints 421 of 42 are combined with each other to be in frictional contact. By the faster rotating speed of the sun gear 42 of the lower gear, the extra frictional boost of the sun gear 42 of the higher gear is provided, so that the sun gear of the higher gear can be shifted when shifting gears. It is easier for the pawl 31 corresponding to the gear 42 to retract the pawl. When the shift action is completed, the speed change ring 21 moves to the sun gear 42 corresponding to the target gear, so that the speed change ring 21 that the slider 345 is unaffected is ejected, and the spread The receiving part 346 makes the sliding block 345 retract inwardly in the drive shaft 34 through the contraction of its own elasticity, so that the connecting part 347 of the receiving part 346 is separated from the sun gear 42 on the adjacent two sides, and the connection of the frictional contact is released, and its configuration It does not affect the transmission connection between the above-mentioned gear tooth set 4 and the gear clutch device 3, but can push the corresponding pawl 31 to make the corresponding elastic member 32 through the faster speed of the lower gear sun gear 42 Compression generates deformation to separate them, so as to guide the power of transmission to assist the power required for gear shift and claw retraction.

And as mentioned above, when downshifting, the process of shifting ring 21 moving from the fourth gear to the third gear will first push out the slider 345 to make it stretch the receiving part 346, so that the connection between the receiving part 346 both sides The part 347 is in frictional contact with the joint part 421 of the adjacent sun gear 42, and the transmission ring 21 continues to move and then pushes the shrapnel of the third gear so that the corresponding pawl 31 stretches the corresponding elastic ring body 33, so that the pawl 31 The sun gear 42c of the corresponding third gear is ready to engage the ratchet wheel 41 to enter the gear. Please refer to Figure 8 and Figure 9 for further reference. It is the third gear and the fourth gear in the state of gear shift assist activation. In the cross-sectional view, when the transmission is performed, as shown in Figure 9, the drive shaft 34 transmits the power to the sun gear 42d corresponding to the fourth gear through the pawl 31, and the planetary gear 43d corresponding to the fourth gear meshes with the transmission The direction is reverse rotation, and through the non-circular structure, it can 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 arranged on the planetary shaft 431 rotate at a constant speed, so the power The planetary gear 43c of the third gear meshes and transmits to the sun gear 42c of the third gear, as shown in Figure 8, wherein the planetary gear 43c of the third gear has more teeth than the planetary gear 43d of the fourth gear , and 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, so 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. Make the sun gear 42c of the third gear transmit the faster speed power to the sun gear 42d of the fourth gear to generate extra power when shifting gears, thereby assisting the sun gear 42d of the fourth gear to increase the speed and make it corresponding After the ratchet 31 disengages from the ratchet wheel 41, and the shifting ring 21 pushes out the ratchet 31 of the third gear, the downshifting process will continue to manipulate the shifting ring 21 to move to the third gear, so that it releases the elasticity of the fourth gear first. The element 32 shrinks the elastic ring body 33 of the fourth gear and acts simultaneously with the auxiliary force of the receiving part 346 to retract the ratchet 31 into the drive shaft 34, so as to overcome the self-locking characteristic of the ratchet 31, and then the speed change ring 21. Move and release the slider 345 to shrink the receiving part 346 and retract the slider 345 into the drive shaft 34. When the transmission ring 21 moves to the third gear, the sun gear 42c of the third gear corresponds to it The ratchet 31 bites into gear, promptly finishes the action of downshift manipulation.

To sum up, the technical means disclosed in the present invention can effectively solve the problems of conventional knowledge and achieve the expected purpose and effect, and it has not been published in publications before application, has not been publicly used, and has long-term progress. The invention mentioned in the patent law is correct. I file an application according to the law. I sincerely pray that Junshang Hui will give you a detailed review and grant the invention patent. I am very grateful to Dexin.

However, the above are only several preferred embodiments of the present invention, and should not limit the scope of the present invention, that is, all equivalent changes and modifications made according to the patent scope of the present invention and the content of the description of the invention are all Should still belong to the scope covered by the patent of the present invention.

1: axis 11: limit slot 2: gear lever 21: Speed change ring 211: Lead surface 212: limit pin 22: Spiral parts 3: gear clutch device 31: pawl 311:Clamping part 312: fixed slot 32: elastic element 321: the first elastic arm 322: second elastic arm 323: spring joint 324: card slot 33: elastic ring body 34: drive shaft 341: Through groove 342: storage tank 343: fixed groove 344: abutment parts 345:Slider 346: Undertake parts 347: link 4: Gear gear group 41: Ratchet 42, 42a, 42b, 42c, 42d: sun gear 421: junction 43, 43a, 43b, 43c, 43d: planetary gears 431: planet shaft 5: Power input device 6:Planet carrier

Fig. 1 is a schematic cross-sectional view of the present invention. Fig. 2 is a three-dimensional exploded schematic view of the present invention. Fig. 3 is a three-dimensional exploded and enlarged schematic diagram of the gear clutch device of the present invention. Fig. 4 is a sectional view and a schematic diagram of the use state of the pawls engaged when the speed change ring is in the transmission state when shifting gears according to the present invention. Fig. 5 is a sectional view and a schematic diagram of the use state of the ratchet wheel separating the ratchet pawls when shifting gears according to the present invention. Fig. 6 is a sectional view and a schematic diagram of the use state of the pawl separated by the elastic ring body when the speed change ring is in a non-transmission state when shifting gears according to the present invention. Fig. 7 is a schematic cross-sectional view of the configuration of the slider and the receiving parts in another embodiment of the present invention. Fig. 8 is the sectional view and schematic view of the use state of the present invention based on Fig. 7, when downshifting by assisting the separation of the high gear pawl by friction. Fig. 9 is the sectional view of the present invention based on Fig. 7, the transmission ring in the transmission state and the schematic diagram of the use state.

1: axis

11: limit slot

2: gear lever

21: Speed change ring

211: Lead surface

212: limit pin

22: Spiral parts

3: gear clutch device

31: pawl

32: elastic element

33: elastic ring body

34: drive shaft

341: Through groove

342: storage tank

344: abutment parts

4: Gear gear group

41: Ratchet

42, 42a, 42b, 42c, 42d: sun gear

43, 43a, 43b, 43c, 43d: planetary gears

431: planet shaft

6:Planet carrier

Claims (10)

An elastic clutch transmission mechanism, which includes: an axis; a transmission lever, which is axially connected and transmitted to a transmission ring, and the transmission ring is correspondingly sleeved and axially slid on the axis, and the transmission ring A guide surface is provided at one end in the axial direction; at least one gear clutch device is provided with at least one pawl respectively, and one end of the pawl is provided with an elastic element corresponding to the guide surface; at least one gear A tooth set, which is provided with a ratchet wheel corresponding to the pawl; and at least one elastic ring body, which is connected to the end of the corresponding pawl opposite the elastic element, for in a non-transmission state, The elastic ring system is elastically retracted to press against the pawl, and the guide surface is not in contact with the elastic element, so that the pawl is non-transmittingly connected to the ratchet wheel; and in a transmission state The guide surface is correspondingly abutted against the elastic element of at least one of the gear clutch devices, so that the corresponding pawl is elastically expanded and connected to the ratchet wheel in one-way transmission. The elastic clutch speed change mechanism according to claim 1, wherein, the pawl is further provided with a locking part at one end; and the elastic element is provided with a first elastic arm and a second elastic arm, and the first An elastic arm and the second elastic arm are connected to an elastic connection part, and the first elastic arm is connected to the end of the pawl away from the engaging part, and the second elastic arm is In the transmission state, the guide surface is correspondingly abutted to make the pawl expand outward and be connected to the ratchet in one-way transmission. The elastic clutch speed change mechanism according to claim 2, wherein, the pawl is further provided with a fixing groove, and the elastic joint is provided with a locking groove, and the elastic ring system elastically abuts against the fixing groove correspondingly and those inside the card slot. The elastic clutch speed change mechanism as described in Claim 2 further includes a drive shaft, the gear gear set is correspondingly sleeved on the outer edge of the drive shaft, and the speed change ring is axially displaced within the drive shaft edge; 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 is passed through the through groove to pass through the drive shaft The inside is used to make the guiding surface abut against the second elastic arm correspondingly in the transmission state. The elastic clutch speed change mechanism as described in Claim 4 further includes an abutment member, which is sleeved on one end of the drive shaft and is correspondingly axially abutted against at least one of the gear teeth sets. The elastic clutch transmission mechanism as described in claim 4, wherein, between the adjacent gear tooth groups, at least one slider corresponding to the guide surface is further provided, and the slider is opposite to the guide surface. One end of the connecting surface is provided with a receiving part, and the receiving part is provided with at least one connecting part, and the gear tooth sets are respectively provided with a connecting part corresponding to the connecting part, and abut against the sliding part on the guiding surface. When block, the slider is correspondingly pushed against the receiving part, so that the corresponding connecting part is combined with the corresponding connecting part. The elastic clutch transmission mechanism according to any one of claim 1 to claim 6, wherein, the gear teeth sets are further provided with a sun gear and at least one planetary gear corresponding to the sun gear, and the sun gear The ratchet is arranged at the inner edge of the gear. The elastic clutch speed change mechanism according to any one of claim 1 to claim 6, wherein, the shaft center is more radially recessed with a limit groove, and the speed change ring is set corresponding to the axial sliding and limited in the Those in the limit slot. The elastic clutch speed change mechanism as described in any one of claim 1 to claim 6, wherein, the gear lever is further provided with a helical part on its outer edge, and the gear lever is rotated to drive the helical part axially The gear shifter. The elastic clutch transmission mechanism as described in any one of claim 1 to claim 6 further includes a shifting device, which is correspondingly connected and transmitted to the shift lever to move the shift ring axially; and the shifter The shifting device is driven by electric automatic or manual; and when the shifting device is electric automatic, the shifting device can be a DC motor or a stepping motor; and when the shifting device is manual, it is Corresponding to the transmission line.

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