gear shift mechanism

Abstract

The present application comprises parallel transmission shaft and shift cam shaft, and connected composite planetary gear set, two synchronization assemblies, clutch set and two clutch actuating assemblies. The two synchronization assemblies are combined with the shift cam shaft and can be controlled by the shift cam shaft to move along the shift cam shaft, thereby controlling the connection of the transmission shaft and the composite planetary gear set. The clutch set is provided with two clutch assemblies, and the two clutch actuating assemblies are combined with the shift cam shaft and the clutch set, and can be controlled by the shift cam shaft to move along the transmission shaft, thereby controlling the composite planetary gear set. The present application controls the shift along the parallel transmission shaft and shift cam shaft, can reduce the size of the transmission mechanism, solve the problem of large size of the existing transmission device, and provide a transmission mechanism with simple and compact structure, small size and energy saving.

Description

TECHNICAL FIELD

[0001] The present invention relates to a transmission device, in particular to a transmission device with small volume, simple structure and low energy consumption. BACKGROUND

[0002] During the driving of a vehicle, different power is required to cope with different road conditions. For example, when the vehicle is climbing a slope, a low speed gear with low rotation speed is required. When the vehicle is driving on a flat road, a high speed gear with high rotation speed is required. Therefore, in order to obtain different power, the vehicle needs to be equipped with a transmission device to cooperate with a driving device to change different gears.

[0003] A conventional transmission device includes an input shaft, an output shaft, an intermediate shaft, and a plurality of range shafts connected to a range lever. The number of range shafts is determined according to the number of gears. The input shaft, the output shaft, and the intermediate shaft are provided with a plurality of gears engaged with each other. Each range shaft is provided with a synchronizer sleeved on the output shaft. The user operates the range lever to select the range shaft corresponding to different gears, and connects the output shaft and the intermediate shaft by the synchronizer provided on the range shaft, thereby outputting different power.

[0004] However, the conventional transmission device needs to set the range shafts according to the number of gears in addition to the input shaft, the output shaft, and the intermediate shaft. Therefore, the conventional transmission device has a relatively loose structure and a large volume, which is not suitable for vehicles with small installation space. In addition, the conventional automatic transmission device usually uses an electronic hydraulic control system to switch gears. In order to maintain the normal operation of the electronic hydraulic control system, energy needs to be continuously consumed to maintain a certain hydraulic pressure. Therefore, the conventional transmission device has room for improvement in structure. SUMMARY

[0005] In order to solve the problem of the large volume of the conventional transmission device which is not suitable for small vehicles, the present invention provides a transmission device with simple and compact structure and electronic cooperation mechanism to control gear shifting without continuous hydraulic pressure, so that energy is only consumed during gear shifting, thereby achieving the purposes of reducing volume and energy consumption.

[0006] The transmission device provided by the present invention to solve the technical problem comprises:

[0007] a transmission shaft driven to rotate;

[0008] a gear shifting cam shaft parallel to the transmission shaft and driven to rotate, the gear shifting cam shaft comprising a shaft body and two synchronizer cam grooves, each of the synchronizer cam grooves being annularly arranged on the shaft body, and the two synchronizer cam grooves being spaced apart;

[0009] A compound planetary gear set, which is connectable to and drivable by the transmission shaft;

[0010] Two synchronization assemblies, which are connectable to the compound planetary gear set and respectively combined with the two synchronization cam grooves, and are respectively driven by the two synchronization cam grooves to reciprocate along the shift cam shaft;

[0011] A clutch set, which includes a central guide seat and two clutch assemblies;

[0012] The central guide seat is used to be fixed to a clutch hub and includes a sleeve portion and two clutch cam segments;

[0013] The sleeve portion is in a tubular shape and includes an axial direction and two ends located at opposite positions in the axial direction of the sleeve portion, and the sleeve portion is coaxially sleeved on the transmission shaft;

[0014] Each of the clutch cam segments is annularly arranged on the outer circumferential surface of the sleeve portion and includes a pushing curved surface, and the pushing curved surfaces of the two clutch cam segments respectively face the two ends of the sleeve portion;

[0015] Each of the clutch assemblies includes a plurality of clutch members, each of which is coaxially arranged with the sleeve portion, reciprocable along the axial direction of the sleeve portion, and connected to the compound planetary gear set; and

[0016] Two clutch actuating sets, each of which includes a drive gear and an actuating member;

[0017] The drive gear is combined with the shift cam shaft and rotatable along with the shift cam shaft;

[0018] The actuating member is annular and rotatably sleeved on the sleeve portion, and includes an actuating ring gear engaged with the drive gear, and a plurality of actuating abutting portions annularly arranged on the side surface of the actuating ring gear at intervals;

[0019] The two actuating ring gears of the two actuating members of the two clutch actuating sets respectively abut on the two clutch cam segments with the actuating abutting portions arranged thereon, and the two actuating ring gears are pushed by the two clutch cam segments to make the two actuating members move along the sleeve portion and push the two clutch assemblies.

[0020] The shift mechanism, wherein the pushing curved surface of each of the clutch cam segments is provided with a plurality of clutch actuating regions at intervals, and each of the clutch actuating regions includes a plurality of actuating protrusions.

[0021] The shift mechanism, wherein each of the clutch actuating regions includes two actuating protrusions and a limiting recess located between the two actuating protrusions.

[0022] The variable speed mechanism, wherein each of the actuating members comprises a contact ring and a plurality of buffer elastic members; the contact ring is coaxially combined with the actuating ring gear of the actuating member by a plurality of positioning members; a plurality of the buffer elastic members are between the actuating ring gear and the contact ring and are respectively sleeved on a plurality of the positioning members, and two ends of each of the buffer elastic members are respectively in contact with the actuating ring gear and the contact ring.

[0023] The variable speed mechanism, wherein the central guide seat comprises two auxiliary guide grooves, the two auxiliary guide grooves are respectively close to two ends of the sleeve part of the central guide seat, each of the auxiliary guide grooves is concave on the outer circumferential surface of the sleeve part and undulates around the sleeve part; the actuating ring gear of each of the actuating members is spaced apart and annularly arranged on the inner circumferential edge, and the two actuating ring gears of the two actuating members are respectively inserted into the two auxiliary guide grooves of the sleeve part by the guide protrusions.

[0024] The variable speed mechanism, wherein each of the clutch members comprises a clamping ring and a friction ring arranged coaxially; the two planes of the friction ring are rough, and the outer diameter of the friction ring is smaller than the outer diameter of the clamping ring.

[0025] The variable speed mechanism, wherein each of the clutch members comprises a wave spring; the wave spring of the clutch member is coaxially arranged with the clamping ring and the friction ring of the clutch member; the plurality of clutch members of each of the clutch assemblies are in contact with each other by the wave springs.

[0026] The variable speed mechanism, wherein the parking group comprises a parking cam and a parking claw; the parking cam is combined with the shaft body of the shift cam shaft and can push the parking claw, so that the parking claw is clamped with the parking clamping port of the output ring gear provided by the compound planetary gear set.

[0027] The variable speed mechanism comprises a driving group, the driving group comprises a motor, a worm, a worm wheel and a driving gear; the worm is combined with the motor shaft of the motor and can be driven by the motor; the worm wheel and the driving gear are coaxially arranged and can synchronously rotate, the worm wheel is engaged with the worm; the shift cam shaft comprises a driven gear coaxially arranged on the shaft body, and the driving gear is engaged with the driven gear.

[0028] The technical means of the application can obtain the following effects:

[0029] 1. The present application is provided with parallel transmission shaft and shift camshaft, two synchronization components are combined with shift camshaft, and can be controlled by shift camshaft, moving along shift camshaft, and then controlling transmission shaft and compound planetary gear set whether to be connected. Two clutch actuating components are combined with shift camshaft and clutch set, and can be controlled by shift camshaft, moving two clutch components along transmission shaft, and then controlling compound planetary gear set. The present application controls shift along parallel transmission shaft and shift camshaft, can reduce volume and does not need to consume energy to maintain hydraulic pressure, so that the structure of the present application is more simple, more compact and more energy-saving.

[0030] 2. The present application is provided with multiple buffer elastic components between actuating ring gear of each actuating component and abutting ring, which can provide buffer and pre-press when actuating component pushes against clutch set, ensuring that abutting ring abuts against multiple clutch components to provide a pre-press clamping function, avoiding slip of clamping ring and friction ring of multiple clutch components.

[0031] 3. The present application is provided with guide convex part of actuating ring gear of each actuating component, and the guide convex part is inserted into auxiliary guide groove of sleeve part, so that each actuating component can stably and smoothly rotate and move relative to sleeve part of central guide seat, and clutch actuating set can accurately drive clutch set to reciprocate.

[0032] 4. The present application is provided with wave spring of each clutch component of clutch set; when clutch set is not moving, multiple clutch components of clutch set abut against each other by wave spring. The wave spring of each clutch component forces clamping ring and friction ring of adjacent two clutch components to separate, and can avoid unexpected movement of clutch set.

[0033] 5. The present application is driven by motor driving worm, and then driving worm wheel, drive gear and driven gear to rotate, which can use self-locking characteristics between worm and worm wheel to achieve locking function without consuming energy in different gears. BRIEF DESCRIPTION OF DRAWINGS

[0034] The drawings described herein are for illustrative purposes only and are not intended to limit the scope of the present application in any way. In addition, the shape and scale of each component in the drawings are only illustrative, which helps to understand the present application, and is not a specific limitation on the shape and scale of each component of the present application. Those skilled in the art can select various possible shapes and scales according to specific circumstances to implement the present application under the guidance of the present application.

[0035] Figure 1 It is a perspective view of the preferred embodiment of the present application.

[0036] Figure 2 It is a partial sectional perspective view of the preferred embodiment of the present application.

[0037] Figure 3 Partial sectional perspective view of another aspect of a preferred embodiment of the present application.

[0038] Figure 4 Partial assembly exploded view of a preferred embodiment of the present application.

[0039] Figure 5 Exploded partial sectional perspective view of a preferred embodiment of the present application.

[0040] Figure 6 Exploded partial sectional perspective view of a preferred embodiment of the present application.

[0041] Figure 7 Perspective view of the shift cam shaft of the present application.

[0042] Figure 8 Partial sectional side view of a preferred embodiment of the present application in N range.

[0043] Figure 9 Assembly exploded view of the compound planetary gear set of a preferred embodiment of the present application.

[0044] Figure 10 Perspective view of the central guide seat of a preferred embodiment of the present application.

[0045] Figure 11 Perspective view of the clutch member of a preferred embodiment of the present application.

[0046] Figure 12 Perspective view of the actuation member of a preferred embodiment of the present application.

[0047] Figure 13 Plan view of the park group of a preferred embodiment of the present application.

[0048] Figure 14 Partial sectional side view of a preferred embodiment of the present application in P range.

[0049] Figure 15 Partial sectional side view of a preferred embodiment of the present application in R range.

[0050] Figure 16 Partial sectional side view of a preferred embodiment of the present application in Dl range.

[0051] Figure 17 Partial sectional side view of a preferred embodiment of the present application in D2 range.

[0052] Figure 18 Partial sectional side view of a preferred embodiment of the present application in D3 range.

[0053] Figure 19This is a partial cross-sectional view of the side view in D4 mode, a preferred embodiment of the present invention. Detailed Implementation

[0054] The details of the present invention can be more clearly understood by referring to the accompanying drawings and the description of specific embodiments. However, the specific embodiments of the present invention described herein are for illustrative purposes only and should not be construed as limiting the invention in any way. Under the teachings of this invention, those skilled in the art can conceive of any possible modifications based on the invention, and these should all be considered to fall within the scope of the invention.

[0055] To gain a detailed understanding of the technical features and practical effects of the present invention, and to enable its implementation according to the invention, the preferred embodiments shown in the figures are further described in detail below:

[0056] like Figures 1 to 3 As shown, a preferred embodiment of the transmission mechanism of the present invention includes a drive shaft 10, a shift camshaft 20, a compound planetary gear set 30, a first synchronization assembly 40A, a second synchronization assembly 40B, a clutch assembly 50, a first clutch actuation assembly 60A, a second clutch actuation assembly 60B, and a parking assembly 70. Further, as... Figure 1 , Figure 3 and Figure 5 As shown, the improved transmission mechanism of the present invention further includes a drive group 80 connected to the shift camshaft 20, the drive group 80 being used to drive the shift camshaft 20 to rotate.

[0057] like Figures 1 to 3 As shown, the drive shaft 10 and the shift camshaft 20 are arranged parallel to each other and spaced apart. The two synchronizing components 40A and 40B are connected to the drive shaft 10 and the shift camshaft 20, enabling the compound planetary gear set 30 to be connected to both the drive shaft 10 and the shift camshaft 20. The two synchronizing components 40A and 40B can reciprocate along the shift camshaft 20, allowing the shift camshaft 20 to control whether the drive shaft 10 is connected to the compound planetary gear set 30 via the two synchronizing components 40A and 40B. The compound planetary gear set 30 is driven by the drive shaft 10; the clutch assembly 50 is connected to the compound planetary gear set 30, and the two clutch actuation assemblies 60A and 60B are connected to the drive shaft 10 and the shift camshaft 20, enabling the compound planetary gear set 30 to be connected to the drive shaft 10 and the shift camshaft 20; when the drive assembly 80 drives the shift camshaft 20 to rotate, the shift camshaft 20 can control the output of the compound planetary gear set 30 via the two clutch actuation assemblies 60A and 60B. With the above configuration, the present invention can shift gears along the parallel drive shaft 10 and the shift camshaft 20.

[0058] like Figures 3 to 6,as well as Figure 8 As shown, the drive shaft 10 includes an axially oriented input component 11, a planetary carrier drive component 12, a small sun gear drive component 13, a connector 14, a one-way clutch 15, a large sun gear drive component 16, and a connecting component 17, all coaxially arranged. The input component 11 has an input end 111 connected to a power source (not shown). The planetary carrier drive component 12 is coaxially inserted through the input component 11 and can rotate relative to it. The planetary carrier drive component 12 includes a locking gear portion 121 and a planetary carrier locking section 122. The locking gear portion 121 is located at one end of the planetary carrier drive component 12, and the planetary carrier locking section 122 is located at the other end. Figure 4 As shown, the small sun gear transmission component 13 is sleeved on the planetary carrier transmission component 12 and is tubular, including a small sun gear locking section 131. The connecting component 14 is annular and sleeved on the small sun gear transmission component 13, and the connecting component 14 includes a locking tooth portion 141 and a receiving groove 142 with opposite positions; the one-way clutch 15 is sleeved on the small sun gear transmission component 13 and received in the receiving groove 142.

[0059] like Figure 5 , Figure 6 and Figure 8 As shown, the large sun gear transmission component 16 is dome-shaped and fitted onto the small sun gear transmission component 13. The large sun gear transmission component 16 includes a large sun gear engagement portion 161, a locking portion 162, and multiple clutch locking grooves 163. The large sun gear engagement portion 161 is located at the front end of the large sun gear transmission component 16, the locking portion 162 is located inside the large sun gear transmission component 16, and the multiple clutch locking grooves 163 are arranged around the outer circumferential surface of the large sun gear transmission component 16, with each clutch locking groove 163 parallel to the axial direction of the transmission shaft 10. Figure 6 and Figure 8 As shown, the connecting member 17 is coaxially disposed inside the large sun gear transmission member 16 and connected to the input member 11.

[0060] like Figures 6 to 8 As shown, the shift camshaft 20 includes a shaft 21, a first synchronous cam groove 22A, a second synchronous cam groove 22B, a driven gear 23, and a gear retaining section 24. The first synchronous cam groove 22A and the second synchronous cam groove 22B are arranged in a wave-like pattern around the shaft 21 and are spaced apart. The gear retaining section 24 is located in the middle section of the shaft 21. The driven gear 23 is coaxially arranged with the shaft 21. The first synchronous cam groove 22A, the second synchronous cam groove 22B, and the driven gear 23 are located at one end of the shaft 21 and close to the input end 111 of the input component 11.

[0061] As Figure 3 , Figure 9 , Figure 14 and Figure 15 shown, the composite planetary gear set 30 is annularly arranged on the transmission shaft 10 and away from the input end 111 of the input member 11, and comprises a planet carrier 31, a large sun gear 32, a small sun gear 33, three short-shaft planetary gears 34, three long-shaft planetary gears 35, and an output ring gear 36. The large sun gear 32, the small sun gear 33, each short-shaft planetary gear 34, and each long-shaft planetary gear 35 are arranged in the planet carrier 31. The planet carrier 31 comprises a transmission member clamping portion 311 and a clamping tooth portion 312. The transmission member clamping portion 311 is tubular, and the planet carrier 31 is sleeved on the planet carrier transmission member 12 as shown in Figure 4 , with the transmission member clamping portion 311 clamped with the planet carrier clamping segment 122 of the planet carrier transmission member 12; the clamping tooth portion 312 is arranged on the outer circumferential surface of the planet carrier 31. The large sun gear 32 is rotatably sleeved on the planet carrier transmission member 12, and comprises a transmission member clamping portion 321 clamped with the large sun gear clamping portion 161 of the large sun gear transmission member 16. The small sun gear 33 has an outer diameter smaller than that of the large sun gear 32 and an inner circumferential surface annularly arranged with a plurality of teeth, and is sleeved on the small sun gear transmission member 13 as shown in Figure 4 , and clamped with the small sun gear clamping segment 131.

[0062] As shown in Figure 3 , Figure 9 and Figure 14 , the three short-shaft planetary gears 34 surround the small sun gear 33, and each short-shaft planetary gear 34 is engaged with the small sun gear 33. Each long-shaft planetary gear 35 has a length greater than that of each short-shaft planetary gear 34, and the three long-shaft planetary gears 35 surround the large sun gear 32 and the three short-shaft planetary gears 34; each long-shaft planetary gear 35 is engaged with the large sun gear 32, and the three long-shaft planetary gears 35 are respectively engaged with the three short-shaft planetary gears 34. The output ring gear 36 is in the shape of a circular cover and is sleeved on the three long-shaft planetary gears 35 and engaged with the three long-shaft planetary gears 35, and the outer circumferential surface of the output ring gear 36 is annularly arranged with a plurality of parking clamping openings 361.

[0063] As shown in Figure 1 , Figure 5 and Figure 6As shown, each of the synchronization assemblies 40A / 40B includes a driven shaft sleeve 41, a sleeve ring 42A / 42B, and a connecting arm 43A / 43B. The driven shaft sleeve 41 is sleeved on the shift cam shaft 20 and can reciprocate along the shift cam shaft 20. The driven shaft sleeve 41 includes a guide member 411 for being inserted into one of the synchronization cam grooves 22A / 22B of the shift cam shaft 20, and the guide member 411 can move along the wavy synchronization cam groove 22A / 22B. The sleeve ring 42A / 42B is sleeved on the input member 11 and can reciprocate along the axial direction of the drive shaft 10. The sleeve ring 42A / 42B has a clamping groove 421 arranged on the outer periphery. The connecting arm 43A / 43B has two opposite ends. One end of the connecting arm 43A / 43B is fixed to the driven shaft sleeve 41, and the other end of the connecting arm 43A / 43B is embedded in the clamping groove 421 of the sleeve ring 42A / 42B, so that the sleeve ring 42A / 42B can rotate relative to the connecting arm 43A / 43B. When the shift cam shaft 20 rotates, the guide member 411 moves along the synchronization cam groove 22A / 22B, and the driven shaft sleeve 41 drives the sleeve ring 42A / 42B through the connecting arm 43A / 43B, so that the sleeve ring 42A / 42B reciprocates along the axial direction of the drive shaft 10.

[0064] As shown in Figure 2 , Figure 3 and Figure 5 , the first synchronization assembly 40A further includes a first transmission member 44 in the form of a ring. The sleeve ring 42A of the first synchronization assembly 40A and the first transmission member 44 are connected by a plurality of connecting rods. The first transmission member 44 is coaxially arranged inside the input member 11 and coaxially sleeved on the planetary carrier transmission member 12, and can reciprocate along the axial direction of the drive shaft 10. The outer periphery of the first transmission member 44 is clamped with the inner periphery of the input member 11. The inner periphery of the first transmission member 44 can be clamped with the clamping gear portion 121 of the planetary carrier transmission member 12. Further, the inner periphery of the first transmission member 44 can also be clamped with the clamping tooth portion 141 of the connecting member 14.

[0065] As shown in Figure 2 , Figure 3 , Figure 5 and Figure 6As shown, the second synchronization assembly 40B further includes a second transmission member 45 in the form of a ring, the collar 42B of the second synchronization assembly 40B is connected with the second transmission member 45 by a plurality of connecting rods, the second transmission member 45 is coaxially arranged inside the big sun gear transmission member 16, coaxially arranged on the connecting member 17, clamped with the connecting member 17 and coaxially surrounds the small sun gear transmission member 13, and the second transmission member 45 can reciprocate along the axial direction of the transmission shaft 10; the inner circumferential surface of the second transmission member 45 is annularly provided with a plurality of teeth, and the plurality of teeth provided on the inner circumferential surface of the second transmission member 45 can be clamped with the clamping portion 162 of the big sun gear transmission member 16.

[0066] As shown in Figure 1 , Figure 3 , Figure 10 and Figure 14 , the clutch set 50 includes a central guide seat 51, a first clutch assembly 52A and a second clutch assembly 52B. The central guide seat 51 includes a sleeve portion 511, a flange portion 512, a first auxiliary guide groove 513A, a second auxiliary guide groove 513B, a first clutch cam segment 514A and a second clutch cam segment 514B. As shown in Figure 10 , the sleeve portion 511 is in the form of a circular tube and includes an axial direction and two ends located at opposite positions in the axial direction of the sleeve portion 511, and the sleeve portion 511 is coaxially arranged on the transmission shaft 10. The flange portion 512 is annularly arranged on the outer circumferential surface of the sleeve portion 511 and located at the middle section of the sleeve portion 511, and the central guide seat 51 is combined with a clutch hub by the flange portion 512. The two auxiliary guide grooves 513A, 513B are respectively close to the two ends of the sleeve portion 511, and the two auxiliary guide grooves 513A, 513B are concavely arranged on the outer circumferential surface of the sleeve portion 511 and undulate around the sleeve portion 511 in different forms. The two clutch cam segments 514A, 514B are annularly arranged on the outer circumferential surface of the sleeve portion 511 in different forms, and each clutch cam segment 514A / 514B includes a wave-shaped push surface, and the push surface of each clutch cam segment 514A / 514B is spaced apart from a plurality of clutch actuating areas 515, and each clutch actuating area 515 includes two actuating convex portions 516 and a limiting concave portion 517 located between the two actuating convex portions 516; the two clutch cam segments 514A, 514B are located between the two auxiliary guide grooves 513A, 513B and separated by the flange portion 512, and the push surfaces of the two clutch cam segments 514A, 514B are respectively directed towards the two ends of the sleeve portion 511.

[0067] As shown in Figure 1 , Figure 3 , Figure 9 , Figure 11 and Figure 14As shown, each of the clutch assemblies 52A / 52B includes a plurality of clutch members 521. As shown in Figure 11 As shown, each of the clutch members 521 includes a clamping ring 522, a friction ring 523 and a wave spring 524 coaxially arranged. The clamping ring 522 has a plurality of clamping protrusions 522a spacedly arranged on the outer periphery thereof. The friction ring 523 has two rough surfaces and a plurality of clamping protrusions 525 spacedly arranged on the inner periphery thereof. The outer diameter of the friction ring 523 is smaller than that of the clamping ring 522. The wave spring 524 is arranged around the friction ring 523. The plurality of clutch members 521 are coaxially arranged with the sleeve portion 511 and are reciprocally movable along the axial direction of the sleeve portion 511. When each of the clutch assemblies 52A / 52B is not moved, the wave springs 524 of the plurality of clutch members 521 abut against each other. When each of the clutch assemblies 52A / 52B is moved, the wave springs 524 of the plurality of clutch members 521 are compressed and abut against the friction rings 523.

[0068] As shown in Figure 3 , Figure 6 , Figure 11 and Figure 14 As shown, each of the clutch members 521 of the first clutch assembly 52A has the friction ring 523 arranged on the inner periphery thereof and abuts against the plurality of clutching grooves 163 of the large sun gear member 16 via the plurality of clamping protrusions 525 on the inner periphery thereof, so that the first clutch assembly 52A is connected to the large sun gear 32 of the compound planetary gear set 30 via the large sun gear member 16 and can control whether the large sun gear 32 can rotate. Each of the clutch members 521 of the second clutch assembly 52B also has the friction ring 523 arranged on the inner periphery thereof and abuts against the clamping teeth 312 of the carrier 31 of the compound planetary gear set 30 via the plurality of clamping protrusions 525 on the inner periphery thereof, so as to be connected to the compound planetary gear set 30 and can control whether the carrier 31 of the compound planetary gear set 30 can rotate.

[0069] As shown in Figure 3 , Figure 12 and Figure 14 As shown, each of the clutch actuating assemblies 60A / 60B includes a drive gear 61 and an actuating member 62. Figure 3 , Figure 7 and Figure 14 As shown, the drive gear 61 is annular and has a plurality of teeth arranged on the inner periphery thereof. The drive gear 61 is sleeved on the gear clamping section 24 of the shift cam shaft 20 and the plurality of teeth arranged on the inner periphery of the drive gear 61 abut against the gear clamping section 24. In the preferred embodiment of the present application, the drive gears 61 of the two clutch actuating assemblies 60A, 60B are coaxially fixed and abut against the gear clamping section 24 together.

[0070] As shown in Figure 3 ,Figure 10 , Figure 12 and Figure 14 As shown, each actuator 62 is annular and rotatably fitted onto the sleeve portion 511. Each actuator 62 includes a rotating ring gear 621, a stop ring 622, and a plurality of buffer elastic members 623. The rotating ring gear 621 is annular, with three actuating stops 624 spaced around its side and three guide protrusions 625 spaced around its inner periphery. Each guide protrusion 625 protrudes radially from the inner periphery of the rotating ring gear 621. The stop ring 622 is coaxially coupled to the rotating ring gear 621. The plurality of buffer elastic members 623 are located between the rotating ring gear 621 and the stop ring 622. In a preferred embodiment of the present invention, each buffer elastic member 623 is a compression spring, and both ends of each buffer elastic member 623 abut against the rotating ring gear 621 and the stop ring 622, respectively. The buffer elastic elements 623 of the present invention are not limited to compression springs. Any buffer elastic element 623 that can elastically support the actuating ring gear 621 and the abutment ring 622 is the target of the present invention. In a preferred embodiment of the present invention, the actuating ring gear 621 and the abutment ring 622 of each actuator 62 are combined by a plurality of positioning elements 626. The plurality of buffer elastic elements 623 are respectively fitted onto the plurality of positioning elements 626. Each buffer elastic element 623 simultaneously abuts against the actuating ring gear 621 and the abutment ring 622, maintaining the distance between the actuating ring gear 621 and the abutment ring 622, and generating a preload effect on the corresponding clutch assembly 52A / 52B. Furthermore, the plurality of buffer elastic elements 623, guided by the plurality of positioning elements 626, can stably abut against the actuating ring gear 621 and the abutment ring 622.

[0071] like Figure 3 , Figure 10 , Figure 12 and Figure 14 As shown, the two actuators 62 of the two clutch actuator assemblies 60A and 60B are rotatably fitted onto the sleeve portion 511 and can reciprocate along the sleeve portion 511. The two actuator ring gears 621 of the two actuators 62 mesh with the two drive gears 61 fixed to the shift camshaft 20. The two actuators 62 abut against the central guide seat 51 fixed to the clutch hub with their actuator ring gears 621. Specifically, the two actuator ring gears 621 abut against the two pushing curved surfaces of the two clutch cam sections 514A and 514B of the central guide seat 51 with their actuating abutments 624 respectively; and the two actuator ring gears 621 are inserted into the two auxiliary guide grooves 513A and 513B of the sleeve portion 511 with their guide protrusions 625 respectively.

[0072] When the shift cam shaft 20 rotates, it drives the two drive gears 61 of the two clutch actuation sets 60A, 60B to rotate. The two actuation members 62 of the two clutch actuation sets 60A, 60B, whose two actuation ring gears 621 engaged with the two drive gears 61, are further driven to rotate relative to the sleeve portion 511. The two actuation ring gears 621 of the two actuation members 62, which rotate, can be pushed by the pushing curved surfaces of the two clutch cam segments 514A, 514B to move along the sleeve portion 511 (i.e. the axial direction of the transmission shaft 10), so that the two actuation members 62 can move towards the two ends of the sleeve portion 511 respectively. The guide protrusions 625 of the two actuation ring gears 621 can move along the two auxiliary guide grooves 513A, 513B respectively, so that the two actuation members 62 can reciprocate along the sleeve portion 511, helping the two actuation ring gears 621 to rotate smoothly relative to the sleeve portion 511.

[0073] As shown in Figure 2 , Figure 3 , Figure 13 and Figure 14 , the parking set 70 includes a parking cam 71 and a parking claw 72. The parking cam 71 is combined with the shaft body 21 of the shift cam shaft 20 away from the two synchronization assemblies 40A, 40B and includes a pushing portion 711. The parking claw 72 can be pivoted and includes a clamping hook 721 that can be clamped in any parking clamping port 361 of the output ring gear 36.

[0074] As shown in Figure 1 , Figure 3 and Figure 5 , the drive set 80 includes a motor 81, a worm 82, a worm gear 83 and a drive gear 84; the worm 82 is combined with the motor shaft of the motor 81 and can be driven by the motor 81; the worm gear 83 and the drive gear 84 are coaxially arranged and can rotate synchronously, the worm gear 83 is engaged with the worm 82; the drive gear 84 is engaged with the driven gear 23 of the shift cam shaft 20. The present application drives the worm 82 by the motor 81, thereby driving the worm gear 83, the drive gear 84 and the driven gear 23 to rotate, which can utilize the self-locking characteristics between the worm 82 and the worm gear 83 to achieve the locking function without consuming energy in different gears.

[0075] The motion and configuration of the N, P, R, D1, D2, D3 and D4 files of the present application are introduced below.

[0076]

[0077] Black dot: motion

[0078] Black line segment: no motion

[0079] N Range:

[0080] Please refer to Figure 8 the N-file configuration shown, in conjunction with Figure 4 , Figure 6 and Figure 9 , the large sun gear driving member 16 of the transmission shaft 10 is engaged with the driving member engaging portion 321 of the large sun gear 32 of the compound planetary gear set 30, and the large sun gear driving member 16 is connected with the large sun gear 32; both the synchronization assemblies 40A, 40B, both the clutch assemblies 52A, 52B, both the clutch actuating assemblies 60A, 60B, and the parking assembly 70 are not in motion. The first driving member 44 of the first synchronization assembly 40A is interposed between the pawl gear portion 121 of the carrier driving member 12 and the pawl portion 141 of the connecting member 14; therefore, the first driving member 44 is only engaged with the input member 11, and is not engaged with the pawl gear portion 121 or the pawl portion 141; the second driving member 45 of the second synchronization assembly 40B is also not engaged with the pawl portion 162 of the large sun gear driving member 16.

[0081] Although the large sun gear driving member 16 is connected with the large sun gear 32, because both the synchronization assemblies 40A / 40B are not in motion, the transmission shaft 10 is not connected with the compound planetary gear set 30, and therefore the power of the transmission shaft 10 cannot be transmitted to the compound planetary gear set 30 and cannot be outputted.

[0082] Please refer to Figure 8 , Figure 10 and Figure 12 , the actuating member 62 of each of the clutch actuating assemblies 60A / 60B, with the actuating ring gear 621 abutting against the central guide seat 51 fixed to the clutch hub; the actuating member 62 of each of the clutch actuating assemblies 60A / 60B, with the actuating abutting portion 624 abutting against the push abutting curved surface of the corresponding clutch cam segment 514A / 514B. When in the N range, the actuating abutting portion 624 of the actuating ring gear 621 abuts against the recessed portion of the push abutting curved surface, and not against the clutch actuating area 515 of the push abutting curved surface. The two actuating members 62 of the two clutch actuating assemblies 60A, 60B abut against the fixed central guide seat 51, and do not respectively push against the two clutch assemblies 52A, 52B. The clutch members 521 of the two clutch assemblies 52A, 52B are not pressed by the two actuating members 62 and are not in motion; therefore, the large sun gear 32 linked with the first clutch assembly 52A, and the carrier 31 linked with the second clutch assembly 52B are not locked by the two clutch assemblies 52A, 52B.

[0083] P Range:

[0084] Please refer to asFigure 14 The P file configuration shown, along with reference to... Figure 3 and Figure 13 The P-gear configuration of this invention is similar to the N-gear configuration; the large sun gear transmission 16 is connected to the large sun gear 32, and the two synchronization components 40A and 40B and the two clutch components 52A and 52B are not moving. The difference between the P-gear configuration and the N-gear configuration of this invention is that in P gear, the shift camshaft 20 is driven to rotate, and the parking cam 71 connected to the shift camshaft 20 pushes the parking pawl 72 with the provided push portion 711, so that the parking pawl 72 is locked with the provided locking hook 721 into one of the parking locking ports 361 of the output ring gear 36 of the compound planetary gear set 30, so that the output ring gear 36 cannot rotate. Compared with N gear, the P-gear configuration of this invention, in addition to the fact that the power of the drive shaft 10 cannot be transmitted to the compound planetary gear set 30 and cannot be output, the parking assembly 70 further moves and locks the output ring gear 36.

[0085] R gear:

[0086] like Figure 15 As shown in the R file configuration, the large sun gear transmission 16 is connected to the large sun gear 32. When the shift camshaft 20 rotates, the parking assembly 70 does not move, and the first transmission 44 of the first synchronization assembly 40A is not engaged with the locking gear portion 121 or the locking tooth portion 141.

[0087] like Figure 5 , Figure 6 and Figure 15 As shown, the second synchronizing cam groove 22B of the shift camshaft 20 drives the second synchronizing assembly 40B toward... Figure 15 When the right side moves, the second transmission member 45 of the second synchronization component 40B engages with the locking part 162 of the large sun gear transmission member 16, so that the second synchronization component 40B is connected to the large sun gear 32 of the compound planetary gear set 30.

[0088] like Figure 3 , Figure 10 , Figure 12 and Figure 15 As shown, the drive gears 61 and actuators 62 of the two clutch actuation assemblies 60A and 60B are driven to rotate by the file-changing camshaft 20; wherein, the actuator 62 of the first clutch actuation assembly 60A abuts against the recessed portion of the pushing surface of the first clutch cam segment 514A, but does not drive the first clutch assembly 52A to move. The actuator 62 of the second clutch actuation assembly 60B is pushed by the clutch actuation area 515 of the pushing surface of the second clutch cam segment 514B, and the actuator 62 of the second clutch actuation assembly 60B faces towards Figure 15The right side of the second clutch assembly 52B is pushed and pressed by the clutch 521, the second clutch assembly 52B moves and clamps the planet carrier 31 of the compound planetary gear set 30, so that the planet carrier 31 cannot rotate.

[0089] As shown in Figure 3 , Figure 9 and Figure 15 , because the large sun gear transmission 16 is connected with the large sun gear 32, the second transmission 45 of the second synchronization assembly 40B is connected with the large sun gear transmission 16 of the compound planetary gear set 30, and the second clutch assembly 52B moves, so that the planet carrier 31 cannot rotate; when the input 11 of the transmission shaft 10 rotates clockwise, the large sun gear 32 rotates clockwise, the long shaft planetary gear 35 rotates counterclockwise and drives the output ring gear 36 to rotate counterclockwise, so that the vehicle provided with the application can reverse.

[0090] D1 gear:

[0091] As shown in Figure 16 , the D1 file configuration of the application, the large sun gear transmission 16 is connected with the large sun gear 32.

[0092] As shown in Figure 5 , Figure 6 and Figure 16 , when the shift camshaft 20 rotates, the parking group 70 does not move, the output ring gear 36 can output, the second transmission 45 of the second synchronization assembly 40B is not clamped with the clamping part 162 of the large sun gear transmission 16, and the second synchronization assembly 40B is not connected with the compound planetary gear set 30. The first synchronization assembly 40A moves to the right of Figure 16 , the first transmission 44 of the first synchronization assembly 40A is clamped with the connecting piece 14. The first clutch assembly 52A does not move; and the second clutch assembly 52B moves, and the planet carrier 31 connected with the second clutch assembly 52B is locked.

[0093] As shown in Figure 3 , Figure 9 and Figure 16 , when the input 11 of the transmission shaft 10 rotates clockwise, the power provided by the transmission shaft 10 is transmitted to the small sun gear 33 through the first transmission 44 of the first synchronization assembly 40A, the connecting piece 14, the one-way clutch 15, the small sun gear transmission 13, drives the small sun gear 33 to rotate clockwise, so that the vehicle provided with the application can move forward.

[0094] As shown in Figure 3 , Figure 9 and Figure 16As shown, the small sun gear 33 drives the three short-axis planetary gears 34 to rotate counterclockwise, the three long-axis planetary gears 35 to rotate clockwise, and the output ring gear 36 to rotate clockwise. Similarly, when the drive shaft 10 decelerates, the rotational speed of the small sun gear 33 is greater than that of the input component 11 of the drive shaft 10, and the one-way clutch 15 disengages the small sun gear drive component 13, achieving the effect of engine braking.

[0095] D2 gear:

[0096] like Figure 17 The configuration shown in document D2 of the present invention involves the large sun gear transmission 16 being connected to the large sun gear 32. When the shift camshaft 20 rotates, the parking assembly 70 remains stationary, allowing the output ring gear 36 to rotate and output power.

[0097] like Figure 10 , Figure 12 and Figure 17 As shown, the drive gears 61 and actuators 62 of the two clutch actuation assemblies 60A and 60B are driven to rotate by the file-changing camshaft 20. The actuator 62 of the first clutch actuation assembly 60A moves against the clutch actuation area 515 of the pushing surface of the first clutch cam segment 514A, thereby driving the first clutch assembly 52A to engage the large sun gear transmission member 16 and lock the large sun gear 32. The actuator 62 of the second clutch actuation assembly 60B is not driven to move by the recessed area of ​​the pushing surface of the second clutch cam segment 514B, allowing the planetary carrier 31 to rotate.

[0098] like Figure 5 , Figure 6 and Figure 17 As shown, the first synchronizing cam groove 22A of the shift camshaft 20 drives the first synchronizing assembly 40A toward... Figure 17 The right side moves, and the first transmission member 44 of the first synchronization component 40A is engaged with the connecting member 14.

[0099] like Figure 5 , Figure 6 and Figure 17 As shown, the second synchronizing cam groove 22B of the shift camshaft 20 drives the second synchronizing assembly 40B toward... Figure 17 When the left side moves, the second transmission member 45 of the second synchronization component 40B disengages from the large sun gear transmission member 16.

[0100] like Figure 3 , Figure 9 and Figure 17As shown, the compound planetary gear set 30 is linked with the first synchronization assembly 40A, when the input member 11 of the drive shaft 10 rotates clockwise, the first driving member 44 of the first synchronization assembly 40A drives the connecting member 14 to rotate clockwise, the one-way clutch 15 in the accommodating groove 142 of the connecting member 14 clamps the small sun gear driving member 13 and drives the small sun gear driving member 13 to rotate clockwise, the small sun gear driving member 13 drives the small sun gear 33 to rotate clockwise.

[0101] As shown in Figure 3 , Figure 9 and Figure 17 , the small sun gear 33 drives the three short shaft planetary gears 34 to rotate counterclockwise, the three long shaft planetary gears 35 to rotate clockwise, and the output ring gear 36 to rotate clockwise, so that the vehicle equipped with the present application can move forward.

[0102] When the drive shaft 10 is decelerated, since the rotation speed of the small sun gear 33 is greater than that of the input member 11 of the drive shaft 10, the one-way clutch 15 releases the small sun gear driving member 13, achieving the effect of engine brake.

[0103] D3 gear:

[0104] As shown in the D3 file configuration of the present application, the large sun gear driving member 16 is connected to the large sun gear 32. Figure 18 As shown in

[0105] , Figure 5 , Figure 6 and Figure 18 , the shift cam shaft 20 rotates, the parking assembly 70 does not move, and the output ring gear 36 can output; the two synchronization assemblies 40A, 40B move towards the right side of Figure 18 , the first driving member 44 of the first synchronization assembly 40A is clamped with the connecting member 14, the first synchronization assembly 40A is connected with the small sun gear 33 of the compound planetary gear set 30, and the second driving member 45 of the second synchronization assembly 40B is connected with the large sun gear 32 of the compound planetary gear set 30.

[0106] As shown in Figure 10 , Figure 12 and Figure 18 , the actuating members 62 of the two clutch actuating assemblies 60A, 60B respectively abut the recessed parts of the push surfaces of the two clutch cam segments 514A, 514B, without driving the two clutch assemblies 52A, 52B to move, so that the large sun gear 32 and the planetary carrier 31 are not locked and can rotate.

[0107] As shown in Figure 3 , Figure 9 and Figure 18As shown, the input member 11 of the drive shaft 10 rotates clockwise. The power provided by the drive shaft 10 is transmitted to the small sun gear 33 via the first transmission member 44 of the first synchronization assembly 40A, the connecting member 14, the one-way clutch 15, and the small sun gear transmission member 13, causing the small sun gear 33 to rotate clockwise. The power provided by the drive shaft 10 is also transmitted to the large sun gear 32 via the second transmission member 45 of the second synchronization assembly 40B and the large sun gear transmission member 16, causing the large sun gear 32 to rotate clockwise.

[0108] like Figure 3 , Figure 9 and Figure 18 As shown, the clockwise rotating small sun gear 33 and the clockwise rotating large sun gear 32 respectively drive the output ring gear 36 and the planet carrier 31 to rotate clockwise via the short-axis planetary gear 34 and the long-axis planetary gear 35. During deceleration, the power provided by the drive shaft 10 achieves an engine braking effect by rotating the large sun gear 32 clockwise.

[0109] D4 mode:

[0110] like Figure 19 Please refer to the D4 file configuration shown in the figure. Figure 5 and Figure 6 The large sun gear transmission component 16 is connected to the large sun gear 32. When the shift camshaft 20 rotates, the parking assembly 70 remains stationary, and the output ring gear 36 can output power; the two synchronization components 40A and 40B face... Figure 19 When the left side moves, the first transmission member 44 of the first synchronization assembly 40A engages with the locking gear portion 121 of the planetary carrier transmission member 12; the second transmission member 45 of the second synchronization assembly 40B disengages from the large sun gear transmission member 16 and is not connected to the large sun gear 32. The first clutch assembly 52A moves, locking the large sun gear 32.

[0111] like Figure 3 , Figure 9 and Figure 19 As shown, when the input component 11 of the drive shaft 10 rotates clockwise, the first transmission component 44 drives the planetary carrier transmission component 12 to rotate clockwise. The planetary carrier 31 is engaged with and driven by the planetary carrier transmission component 12 to rotate clockwise. The three long-shaft planetary gears 35 rotate clockwise around the large sun gear 32, and the output ring gear 36 rotates clockwise. When the drive shaft 10 decelerates, the planetary carrier 31 decelerates accordingly, achieving an engine braking effect.

[0112] The above detailed description of the embodiments is only intended to explain the present application, so that the present application can be better understood, but these descriptions cannot be interpreted as limiting the present application in any way, and in particular, the features described in different embodiments can be arbitrarily combined with each other to form other embodiments, and these features should be understood as being applicable to any one embodiment, and not limited to the described embodiments, except for the explicitly opposite description.

Claims

1. A speed change mechanism characterized by comprising: The variable speed mechanism comprises: a transmission shaft driven to rotate; a shift camshaft parallel to the transmission shaft and driven to rotate, the shift camshaft comprising a shaft body and two synchronous cam grooves, each of the synchronous cam grooves being annularly arranged on the shaft body, and the two synchronous cam grooves being spaced apart; a compound planetary gear set connected to the transmission shaft and driven to move by the transmission shaft; two synchronous assemblies connected to the compound planetary gear set and respectively combined with the two synchronous cam grooves, the two synchronous assemblies being driven to reciprocate along the shift camshaft by the two synchronous cam grooves; a clutch set comprising a central guide seat and two clutch assemblies; the central guide seat is used to be fixed to a clutch hub and comprises a sleeve part and two clutch cam segments; the sleeve part is in the shape of a circular tube and comprises an axial direction and two ends located opposite to each other in the axial direction of the sleeve part, and the sleeve part is coaxially sleeved on the transmission shaft; each of the clutch cam segments is annularly arranged on the outer circumferential surface of the sleeve part and comprises a pushing curved surface, and the pushing curved surfaces of the two clutch cam segments respectively face the two ends of the sleeve part; each of the clutch assemblies comprises a plurality of clutch members, each of the clutch members is coaxially arranged on the sleeve part, can reciprocate along the axial direction of the sleeve part, and is connected to the compound planetary gear set; and two clutch actuating groups, each of the clutch actuating groups comprises a drive gear and an actuating member; the drive gear is combined with the shift camshaft and can rotate with the shift camshaft; the actuating member is annular and is rotatably sleeved on the sleeve part, and the actuating member comprises an actuating ring gear engaged with the drive gear, and the side surface of the actuating ring gear is annularly spaced apart and provided with a plurality of actuating abutting portions; the two actuating ring gears of the two actuating members of the two clutch actuating groups respectively abut on the two clutch cam segments by the provided actuating abutting portions, and the two actuating ring gears are pushed by the two clutch cam segments to make the two actuating members reciprocate along the sleeve part and push the two clutch assemblies. The pushing curved surface of each of the clutch cam segments is spaced apart and provided with a plurality of clutch actuating regions, and each of the clutch actuating regions comprises a plurality of actuating protrusions.

2. The transmission mechanism according to claim 1, wherein Each of the clutch actuating regions comprises two actuating protrusions and a limiting recess located between the two actuating protrusions.

3. The gear shift mechanism according to claim 2, wherein Each of the actuating members comprises an abutting ring and a plurality of buffer elastic members; the abutting ring is coaxially combined with the actuating ring gear of the actuating member by a plurality of positioning members; the plurality of buffer elastic members are between the actuating ring gear and the abutting ring and are respectively sleeved on the plurality of positioning members, and the two ends of each of the buffer elastic members respectively abut on the actuating ring gear and the abutting ring.

4. The gear shift mechanism according to claim 2, wherein The central guide seat comprises two auxiliary guide grooves, the two auxiliary guide grooves are respectively close to the two ends of the sleeve part of the central guide seat, each of the auxiliary guide grooves is concavely arranged on the outer circumferential surface of the sleeve part and undulates around the sleeve part; the actuating ring gear of each of the actuating members is spaced apart and provided with a plurality of guide protrusions on the inner circumferential edge, and the two actuating ring gears of the two actuating members are respectively inserted into the two auxiliary guide grooves of the sleeve part by the provided guide protrusions.

5. The gear shift mechanism according to claim 4, wherein ​ 6. The transmission mechanism according to claim 1, wherein Each of the actuating members comprises a contact ring and a plurality of buffer elastic members; the contact ring is coaxially combined with the actuating ring gear of the actuating member; the plurality of buffer elastic members are between the actuating ring gear and the contact ring, and two ends of each of the buffer elastic members are respectively in contact with the actuating ring gear and the contact ring.

7. The gear shift mechanism according to any one of claims 2, 4 or 6, wherein Each of the clutch members comprises a clamping ring and a friction ring coaxially arranged; the friction ring has two rough surfaces, and the outer diameter of the friction ring is smaller than the outer diameter of the clamping ring.

8. The gear shift mechanism according to claim 7, wherein Each of the clutch members comprises a wave spring; the wave spring of the clutch member is coaxially arranged with the clamping ring and the friction ring of the clutch member; the plurality of clutch members of each of the clutch assemblies are in contact with the wave springs.

9. The transmission mechanism according to claim 1, wherein The transmission mechanism further comprises a parking group, and the parking group comprises a parking cam and a parking claw; the parking cam is combined with the shaft body of the shift cam shaft and can push the parking claw, so that the parking claw is clamped with the composite planetary gear set.

10. The transmission mechanism according to claim 1, wherein The transmission mechanism comprises a driving group, and the driving group comprises a motor, a worm, a worm wheel and a driving gear; the worm is combined with the motor shaft of the motor and can be driven by the motor; the worm wheel and the driving gear are coaxially arranged and can synchronously rotate, the worm wheel is engaged with the worm; the shift cam shaft comprises a driven gear coaxially arranged in the shaft body, and the driving gear is engaged with the driven gear.

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