Speed changer capable of preventing back-up locking, electric drive assembly, motorcycle and agricultural crawler

Abstract

The utility model discloses a reverse locking prevention transmission, an electric drive assembly, a motorcycle and an agricultural crawler, an input shaft of the reverse locking prevention transmission is sleeved with an outer centrifugal disc, an inner centrifugal disc and a high-speed transmission sleeve, the outer centrifugal disc and the inner centrifugal disc synchronously rotate with the input shaft, and the high-speed transmission sleeve can rotate relative to the input shaft. The inner centrifugal disc can axially slide between the outer centrifugal disc and the high-speed transmission sleeve, an elastic element for driving the inner centrifugal disc to have a tendency to be separated from the high-speed transmission sleeve is arranged between the inner centrifugal disc and the high-speed transmission sleeve, and when the rotating speed of the output shaft is low, the centrifugal force generated by each rolling element due to rotation is not enough to overcome the elastic force of the elastic element; therefore, when a low-speed gear and the output shaft rotate reversely at a low speed, a high-speed transmission path is always in an interrupted state, the problem that the output shaft is pinned when rotating reversely at the low speed is thoroughly avoided, and the universality and the reliability of the two-gear transmission are improved.

Description

Technical Field

[0001] The utility model relates to the technical field of electric drive devices, and in particular to a transmission with anti-backward locking function, an electric drive assembly, a motorcycle and an agricultural crawler vehicle. Background Art

[0002] In the existing technology, there is a two-speed transmission, which is based on the cooperation of a planetary gear train and an overrunning clutch. It does not require the control of actuators such as shift forks, and can achieve high and low speed shifting only through the forward and reverse rotation of the motor shaft. It is not only cleverly designed and extremely compact in structure, it takes up little space, and has a small gear shifting impact.

[0003] However, the above-mentioned two-speed transmission has a serious problem: the output shaft cannot be reversed. Once reversed by external force, a deadlock problem will occur at the intersection of the high-speed transmission path and the low-speed transmission path (usually at one of the overrunning clutches), resulting in it being unable to be applied to some widely used products such as electric motorcycles (users cannot pedal to reverse) and agricultural crawler vehicles (users cannot push the vehicle backwards).

[0004] Solving the above problems has become a top priority. Utility Model Content

[0005] In order to solve the technical problem that the output shaft of the existing two-speed transmission based on a planetary gear train and an overrunning clutch will cause the internal devices to lock with each other when the output shaft is reversed by an external force, the utility model provides a transmission, an electric drive assembly, a motorcycle and an agricultural crawler vehicle with anti-reverse lock.

[0006] The technical solution is as follows:

[0007] A first aspect of the present application relates to a transmission with an anti-backward lock, comprising a gearbox and an input shaft and an output shaft coaxially arranged in the gearbox, wherein the input shaft is capable of driving a low-speed transmission sleeve to rotate through a planetary gear train, and an output transmission sleeve is connected to an end of the output shaft close to the input shaft and rotates synchronously therewith, and a first overrunning clutch is installed by interference pressure between the output transmission sleeve and the low-speed transmission sleeve, characterized in that: an outer centrifugal disk and an inner centrifugal disk are sleeved on the input shaft and rotate synchronously therewith, and a high-speed transmission sleeve that can rotate relative thereto, the inner centrifugal disk can slide axially between the outer centrifugal disk and the high-speed transmission sleeve, an elastic element is provided between the inner centrifugal disk and the high-speed transmission sleeve for driving the inner centrifugal disk to have a tendency to separate from the high-speed transmission sleeve, a second overrunning clutch is installed by interference pressure between the high-speed transmission sleeve and the output transmission sleeve, at least three rolling grooves are formed between the outer centrifugal disk and the inner centrifugal disk and distributed along the circumference of the input shaft, the depth of each rolling groove gradually decreases radially outwardly along the input shaft, and a rolling element that can move along the rolling groove is provided in each rolling groove;

[0008] When the input shaft rotates in one direction, the first overrunning clutch is in the engaged state, and the second overrunning clutch is in the overrunning state, and the power input by the input shaft is transmitted to the output shaft through the planetary gear train, the low-speed transmission sleeve, the first overrunning clutch and the output transmission sleeve in sequence; when the input shaft rotates in the other direction, the first overrunning clutch is in the overrunning state, and the second overrunning clutch is in the engaged state, and each rolling element moves to the outer end of the corresponding rolling groove to make the inner centrifugal disc and the high-speed transmission sleeve engage and rotate synchronously. At this time, the power input by the input shaft is transmitted to the output shaft through the outer centrifugal disc, the inner centrifugal disc, the high-speed transmission sleeve, the second overrunning clutch and the output transmission sleeve in sequence.

[0009] With the above-mentioned transmission with anti-reverse lock, when the output shaft rotates at a low speed, the centrifugal force generated by the rotation of each rolling element is insufficient to overcome the elastic force of the elastic element, thereby causing the inner centrifugal disk and the high-speed transmission sleeve to be in a separated state. Therefore, in low-speed gear and low-speed reverse rotation of the output shaft (low-speed reverse gear), the high-speed transmission path is always in an interrupted state, completely avoiding the problem of lock when the output shaft reverses at low speed. Therefore, the two-speed transmission can be applied to some widely used products such as electric motorcycles (users cannot pedal to reverse) and agricultural crawler vehicles (users cannot push the vehicle backward), thereby improving the versatility and reliability of the two-speed transmission.

[0010] In some embodiments, a circle of first one-way ratchet teeth is protruding from the disk surface of the inner centrifugal disk close to the high-speed transmission sleeve, and a circle of second one-way ratchet teeth that are compatible with the first one-way ratchet teeth are formed on the end surface of the high-speed transmission sleeve close to the inner centrifugal disk; when the first one-way ratchet teeth are combined with the second one-way ratchet teeth, the inner centrifugal disk can drive the high-speed transmission sleeve to rotate synchronously with it in one direction; when the first one-way ratchet teeth are separated from the second one-way ratchet teeth, the high-speed transmission sleeve can rotate relative to the inner centrifugal disk.

[0011] In some embodiments, the inner centrifugal disk is spline-matched with the outer circumference of the input shaft through a first spline connection seat, the high-speed transmission sleeve is installed on the input shaft through a first needle roller bearing, and the second overrunning clutch is interference-pressed between the inner circumference of the output transmission sleeve and the outer circumference of the high-speed transmission sleeve. The first needle roller bearing is provided with a retaining spring at one end close to the high-speed transmission sleeve, and a retaining ring that can rotate relative to the input shaft is provided on the side of the retaining spring away from the first needle roller bearing, and the elastic element is a reset compression spring, one end of the reset compression spring is elastically supported on the retaining ring, and the other end is elastically supported on the end surface of the first spline connection seat close to the inner centrifugal disk.

[0012] In some embodiments, the low-speed transmission sleeve includes a mounting sleeve portion with a cylindrical structure and a mounting disk portion extending radially outward from the mounting sleeve portion near one end of the planetary gear train. The mounting sleeve portion is rotatably mounted on the input shaft through a second needle roller bearing. The first overrunning clutch is interference-pressed between the inner circumferential surface of the output transmission sleeve and the outer circumferential surface of the mounting sleeve portion. The mounting disk portion is fixedly connected to the output end of the planetary gear train.

[0013] In some embodiments, the planetary gear train includes at least three planetary gears rotatably mounted on a gearbox and an inner ring gear simultaneously meshed with each of the planetary gears. The input shaft is provided with a sun gear that rotates synchronously therewith. The planetary gears are circumferentially distributed around the sun gear and meshed with the sun gear. The inner ring gear is connected to the low-speed transmission sleeve in a synchronously rotatable manner at one end close to the output shaft.

[0014] In some embodiments, the planetary gear system further includes a planet carrier, which is fixedly mounted on the gearbox via a plurality of second fastening bolts, and both ends of each planetary wheel are rotatably mounted on the planet carrier and the gearbox via corresponding planetary wheel bearings.

[0015] In some embodiments, the rolling element is a roller with a cylindrical structure, and the rolling groove is a wedge-shaped groove adapted to the roller.

[0016] A second aspect of the present application relates to an electric drive assembly, comprising a drive motor and the above-mentioned anti-reverse lock transmission, wherein the motor shaft of the drive motor rotates synchronously with the input shaft.

[0017] The above electric drive assembly has all the advantages of the above anti-reverse lock transmission.

[0018] A third aspect of the present application relates to a motorcycle using the above-mentioned electric drive assembly, wherein the electric drive assembly is mounted on a motorcycle frame and can drive the rear wheel to rotate through a rear wheel transmission assembly.

[0019] The above motorcycle has all the advantages of the above-mentioned anti-reverse lock transmission and can avoid the problem of the transmission being locked when the pedal is used to reverse.

[0020] The fourth aspect of the present application relates to an agricultural tracked vehicle using the above-mentioned electric drive assembly, wherein two sets of electric drive assemblies are both installed on the tracked vehicle frame and can drive the active track wheels of the corresponding tracks to rotate through the corresponding track wheel transmission components.

[0021] The above agricultural crawler vehicle has all the advantages of the above-mentioned anti-reverse lock transmission, which can avoid the problem of the transmission being locked when the user pushes the vehicle back by hand. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 It is a structural diagram of the electric drive assembly when the inner centrifugal disc and the high-speed transmission sleeve are in a separated state;

[0023] Figure 2 It is a structural diagram of the electric drive assembly when the inner centrifugal disc and the high-speed transmission sleeve are in a combined state;

[0024] Figure 3 Schematic diagram of the matching relationship between the outer centrifugal disc, the inner centrifugal disc and the high-speed transmission sleeve;

[0025] Figure 4 It is a structural diagram of the high-speed transmission sleeve;

[0026] Figure 5 Schematic diagram of the structure of the inner centrifugal disk;

[0027] Figure 6 Schematic diagram of the structure of the outer centrifugal disk;

[0028] Figure 7 is a schematic diagram of the structure of a motorcycle;

[0029] Figure 8 This is a structural diagram of an agricultural tracked vehicle. DETAILED DESCRIPTION

[0030] The present invention will be further described below with reference to the embodiments and accompanying drawings.

[0031] Example 1:

[0032] like Figures 1-6 As shown, a transmission with anti-reverse locking mainly includes a gearbox 1 and a centrifugal thrust reverse anti-lock structure, a planetary gear train, an input shaft 2 and an output shaft 3, all of which are arranged in the gearbox 1.

[0033] Among them, the input shaft 2 and the output shaft 3 are coaxially arranged, and the ends of the input shaft 2 and the output shaft 3 that are away from each other both pass out of the gearbox 1. The input shaft 2 is used for power input, and the output shaft 3 is used for power output. The end of the output shaft 3 that passes through the gearbox 1 can directly drive the wheel, or can be equipped with a gear or sprocket 20 that rotates synchronously with it.

[0034] In this embodiment, the input shaft 2 can not only drive the low-speed transmission sleeve 6 through the planetary gear system, but also transmit power to the centrifugal thrust reverse anti-lock mechanism. The output shaft 3 is connected to the output transmission sleeve 7 at one end near the input shaft 2, which rotates synchronously with it.

[0035] Specifically, the end of the output shaft 3 close to the input shaft 2 extends radially outward to form a connecting disk 3a. The output transmission sleeve 7 is a cylindrical structure. The end face of the output transmission sleeve 7 away from the planetary gear system is fixedly connected to the connecting disk 3a.

[0036] At the same time, the low-speed transmission sleeve 6 includes a mounting sleeve portion 6a with a cylindrical structure and a mounting disc portion 6b extending radially outward from the mounting sleeve portion 6a close to one end of the planetary gear train. The mounting sleeve portion 6a is rotatably mounted on the input shaft 2 through a second needle roller bearing 19, and the mounting disc portion 6b is fixedly connected to the output end of the planetary gear train, that is, the power output by the planetary gear train drives the mounting disc portion 6b to rotate.

[0037] Therefore, the output transmission sleeve 7 surrounds the centrifugal thrust reverse anti-lock structure and the outside of the mounting sleeve 6a. At the same time, the first overrunning clutch 8 is interference-pressed between the inner circumference of the output transmission sleeve 7 and the outer circumference of the mounting sleeve 6a.

[0038] In this embodiment, the centrifugal thrust reverse anti-lock structure includes an outer centrifugal disc 9, an inner centrifugal disc 10 and a high-speed transmission sleeve 11, all of which are mounted on the input shaft 2, wherein the outer centrifugal disc 9 and the inner centrifugal disc 10 rotate synchronously with the input shaft 2, and the high-speed transmission sleeve 11 can rotate relative to the input shaft 2. In addition, the inner centrifugal disc 10 is located between the outer centrifugal disc 9 and the high-speed transmission sleeve 11 and can slide axially between the outer centrifugal disc 9 and the high-speed transmission sleeve 11. An elastic element 15 is provided between the inner centrifugal disc 10 and the high-speed transmission sleeve 11 to drive the inner centrifugal disc 10 to have a tendency to separate from the high-speed transmission sleeve 11. At the same time, a second overrunning clutch 14 is interference-pressed between the high-speed transmission sleeve 11 and the output transmission sleeve 7. At least three rolling grooves 12 are formed between the outer centrifugal disc 9 and the inner centrifugal disc 10 and are distributed along the circumference of the input shaft 2. The depth of each rolling groove 12 gradually decreases radially outward from the input shaft 2, and each rolling groove 12 is provided with a spring that can move along the spring. rolling elements 13, that is, when the outer centrifugal disc 9 and the inner centrifugal disc 10 do not rotate or the rotation speed is extremely low, each rolling element 13 is located at the inner end of the corresponding rolling groove 12 when the centrifugal force is insufficient to overcome the thrust of the elastic element 15 on the inner centrifugal disc 10, pushing the inner centrifugal disc 10 and the high-speed transmission sleeve 11 into a separated state. When the outer centrifugal disc 9 and the inner centrifugal disc 10 rotate faster and faster, each rolling element 13 moves toward the outer end of the corresponding rolling groove 12 under the action of centrifugal force, and at the same time pushes the inner centrifugal disc 10 to move toward the direction close to the high-speed transmission sleeve 11, and finally the inner centrifugal disc 10 and the high-speed transmission sleeve 11 are in a combined state.

[0039] The specific working principle is as follows:

[0040] When input shaft 2 rotates in one direction, first overrunning clutch 8 is engaged and second overrunning clutch 14 is in overrunning mode. The low-speed gear transmission path is connected, while the high-speed gear transmission path is disconnected. The power input from input shaft 2 is transmitted to output shaft 3 in sequence through the planetary gear train, low-speed transmission sleeve 6, first overrunning clutch 8, and output transmission sleeve 7.

[0041] When input shaft 2 rotates in the other direction, first overrunning clutch 8 is in the overrunning state, and second overrunning clutch 14 is in the engaged state. Each rolling element 13 moves to the outer end of the corresponding rolling groove 12, causing the inner centrifugal disc 10 and the high-speed transmission sleeve 11 to engage and rotate synchronously. At this time, the low-speed transmission line is disconnected, and the high-speed transmission line is connected. Therefore, the power input from input shaft 2 is transmitted to output shaft 3 through outer centrifugal disc 9, inner centrifugal disc 10, high-speed transmission sleeve 11, second overrunning clutch 14, and output transmission sleeve 7 in sequence.

[0042] In the above two gears, the output shaft 3 rotates in the same direction, which is forward rotation.

[0043] When the output shaft 3 is reversed at low speed under the action of external force (for example, pedaling or pushing the bicycle backward), the first overrunning clutch 8 and the second overrunning clutch 14 are both in the engaged state, and the power input by the output shaft 3 drives the input shaft 2 to rotate at low speed through the low-speed gear transmission route. At this time, since the rotation speed of the input shaft 2 is very low, the centrifugal force of each rolling element 13 is not enough to overcome the thrust of the elastic element 15 on the inner centrifugal disc 10, pushing the inner centrifugal disc 10 and the high-speed transmission sleeve 11 into a separated state, so that the high-speed gear transmission route is interrupted, and the second overrunning clutch 14 will not have a deadlock problem.

[0044] See Figure 1-Figure 5 A circle of first one-way ratchet teeth 10a is protruded on the disk surface of the inner centrifugal disk 10 close to the high-speed transmission sleeve 11, and a circle of second one-way ratchet teeth 11a that are adapted to the first one-way ratchet teeth 10a is formed on the end surface of the high-speed transmission sleeve 11 close to the inner centrifugal disk 10; when the first one-way ratchet teeth 10a and the second one-way ratchet teeth 11a are combined, the inner centrifugal disk 10 can drive the high-speed transmission sleeve 11 to rotate synchronously with it in one direction; when the first one-way ratchet teeth 10a and the second one-way ratchet teeth 11a are separated, the high-speed transmission sleeve 11 can rotate relative to the inner centrifugal disk 10.

[0045] Furthermore, the high-speed transmission sleeve 11 includes a transmission sleeve mounting seat 11b. A second one-way ratchet 11a is integrally formed at the end of the transmission sleeve mounting seat 11b near the inner centrifugal disc 10. The transmission sleeve mounting seat 11b is mounted on the input shaft 2 via a first needle roller bearing 16, ensuring smooth rotation of the high-speed transmission sleeve 11 relative to the input shaft 2. At the same time, a second overrunning clutch 14 is interference-pressed between the inner circumference of the output transmission sleeve 7 and the outer circumference of the transmission sleeve mounting seat 11b, ensuring reliable installation of the second overrunning clutch 14.

[0046] The inner centrifugal disc 10 is spline-coupled with the outer circumference of the input shaft 2 via the first spline connection seat 10b. Similarly, the outer centrifugal disc 9 is spline-coupled with the outer circumference of the input shaft 2 via the second spline connection seat 9b, thereby enabling the input shaft 2 to reliably drive the inner centrifugal disc 10 and the outer centrifugal disc 9 to rotate synchronously therewith.

[0047] In order to prevent the high-speed transmission sleeve 11 from moving axially, a retaining spring 17 is provided at one end of the first needle roller bearing 16 close to the high-speed transmission sleeve 11, and a retaining ring 18 that can rotate relative to the input shaft 2 is provided on the side of the retaining spring 17 away from the first needle roller bearing 16. The retaining ring 18 can rotate relative to the input shaft 2. The elastic element 15 is a return spring, one end of which is elastically supported on the retaining ring 18, and the other end is elastically supported on the end face of the first spline connection seat 10b close to the inner centrifugal disk 10. The above installation method can avoid the problem of twisting of the return spring.

[0048] See Figure 5 and Figure 6 In this embodiment, the rolling element 13 is preferably a roller with a cylindrical structure, and the rolling groove 12 is a wedge-shaped groove adapted to the roller for ease of processing and assembly.

[0049] Furthermore, the outer centrifugal disk 9 is recessed on one side of the disk surface close to the inner centrifugal disk 10 to form grooves 9a that are respectively adapted to each roller. The depth of each groove 9a gradually decreases from the inside to the outside along the radial direction of the outer centrifugal disk 9. At the same time, the inner centrifugal disk 10 has a mating surface 10c with a conical surface structure on one side of the disk surface close to the outer centrifugal disk 9. The mating surface 10c is simultaneously covered on each groove 9a, thereby forming each rolling groove 12 together with each groove 9a, which is convenient for the installation of each roller and the processing and assembly of the outer centrifugal disk 9 and the inner centrifugal disk 10.

[0050] See Figure 1 and Figure 2 The planetary gear train includes at least three planetary gears 4 rotatably mounted on the gearbox 1 and an inner ring gear 5 meshing with each of the planetary gears 4. The input shaft 2 is provided with a sun gear 2a that rotates synchronously therewith. The planetary gears 4 are circumferentially distributed around the sun gear 2a and mesh with the sun gear 2a. The end of the inner ring gear 5 close to the output shaft 3 is connected to a mounting plate portion 6b for synchronous rotation. Therefore, the sun gear 2a drives the inner ring gear 5 to rotate through the planetary gears 4, and the inner ring gear 5 drives the mounting plate portion 6b to rotate.

[0051] The outer edge of the mounting plate portion 6b is fixedly connected to the inner gear ring 5 by at least three first fastening bolts distributed along the circumferential direction, and has high reliability.

[0052] To improve the reliability of the installation of each planetary gear 4, the planetary gear system also includes a planetary carrier 21, which is fixed to the transmission case 1 via a plurality of second fastening bolts 22. Each planetary gear 4 is rotatably mounted on the planetary carrier 21 and the transmission case 1 at both ends via corresponding planetary bearings 23. At the same time, an internal gear bearing 26 is press-fitted between the internal gear 5 and the transmission case 1, ensuring the reliable installation of the internal gear 5.

[0053] Example 2:

[0054] See Figure 1 and Figure 2 , an electric drive assembly, including a drive motor 24 and an anti-reverse lock transmission of Example 1, wherein the motor shaft 24b of the drive motor 24 rotates synchronously with the input shaft 2, forming a complete electric drive system.

[0055] In this embodiment, a spline groove is formed on the end surface of the input shaft 2 away from the output shaft 3. The outer end of the motor shaft 24b is embedded in the spline groove and matched with the spline, which is simple and reliable.

[0056] Furthermore, the transmission 1 includes a housing 1a and a cover 1b that covers the housing 1a. The housing 1a and cover 1b are securely connected via a plurality of fourth fastening bolts, providing a simple and reliable connection. The ring gear 5 is mounted on the housing 1a via a ring gear bearing 26, and the ends of the planetary gears 4 facing away from the planet carrier 21 are mounted on the cover 1b via corresponding planetary gear bearings 23, ensuring convenient assembly of the planetary gear train.

[0057] Furthermore, in order to ensure the reliability of the overall installation, the motor housing 24 a of the drive motor 24 is fixedly connected to the box cover 1 b through a plurality of third fastening bolts 25 .

[0058] Example 3:

[0059] See Figure 7 A motorcycle adopts the electric drive assembly of Example 2, which is installed on the motorcycle frame 27. The electric drive assembly can drive the rear wheel 28 to rotate through the rear wheel transmission component. The electric drive assembly can achieve high and low speed shifting by driving the motor shaft 24b of the motor 24 in the forward and reverse directions. At the same time, the transmission will not be stuck when the pedal is used to reverse.

[0060] Example 4:

[0061] See Figure 8 An agricultural crawler vehicle adopts two sets of electric drive assemblies of Example 2. Both sets of electric drive assemblies are installed on the crawler vehicle frame 29. The two sets of electric drive assemblies can drive the active track wheels 30a of the corresponding crawlers 30 to rotate through the corresponding track wheel transmission components. Among them, the electric drive assembly can realize high and low speed shifting by the forward and reverse rotation of the motor shaft 24b of the drive motor 24. At the same time, the transmission will not be stuck when the vehicle is pushed back manually.

[0062] Among them, an articulated robot 31 is also installed on the tracked vehicle frame 29, and an electric gripper 32 is installed at the outer end of the articulated robot 31. When the depth camera recognizes and locates the position of the target to be removed (such as tobacco leaves) of the plant to be operated (such as tobacco plants), the articulated robot 31 drives the electric gripper 32 to the target to be removed. The electric gripper 32 clamps the target close to the stem, and the articulated robot 31 rotates the electric gripper 32 to simulate the action of human picking, and removes the target to be removed from the plant to be operated.

[0063] Finally, it should be noted that the above description is only a preferred embodiment of the present invention. Under the guidance of the present invention, ordinary technicians in this field can make various similar expressions without violating the purpose and claims of the present invention. Such changes fall within the scope of protection of the present invention.

Claims

1. A transmission with an anti-backward lock function, comprising a gearbox and an input shaft and an output shaft coaxially disposed within the gearbox, wherein the input shaft is capable of driving a low-speed transmission sleeve for rotation via a planetary gear train, and wherein an output transmission sleeve is connected to an end of the output shaft proximate the input shaft and rotates synchronously therewith, and a first overrunning clutch is interlocked between the output transmission sleeve and the low-speed transmission sleeve, characterized in that: The input shaft is provided with an outer centrifugal disc and an inner centrifugal disc which rotate synchronously therewith, and a high-speed transmission sleeve which can rotate relative thereto; the inner centrifugal disc can slide axially between the outer centrifugal disc and the high-speed transmission sleeve; an elastic element is provided between the inner centrifugal disc and the high-speed transmission sleeve to drive the inner centrifugal disc to have a tendency to separate from the high-speed transmission sleeve; a second overrunning clutch is press-fitted between the high-speed transmission sleeve and the output transmission sleeve; at least three rolling grooves are formed between the outer centrifugal disc and the inner centrifugal disc, distributed along the circumference of the input shaft; the depth of each rolling groove gradually decreases radially outwardly along the input shaft, and a rolling element which can move along the rolling groove is provided in each rolling groove; When the input shaft rotates in one direction, the first overrunning clutch is in the engaged state, and the second overrunning clutch is in the overrunning state, and the power input by the input shaft is transmitted to the output shaft through the planetary gear train, the low-speed transmission sleeve, the first overrunning clutch and the output transmission sleeve in sequence; when the input shaft rotates in the other direction, the first overrunning clutch is in the overrunning state, and the second overrunning clutch is in the engaged state, and each rolling element moves to the outer end of the corresponding rolling groove to make the inner centrifugal disc and the high-speed transmission sleeve engage and rotate synchronously. At this time, the power input by the input shaft is transmitted to the output shaft through the outer centrifugal disc, the inner centrifugal disc, the high-speed transmission sleeve, the second overrunning clutch and the output transmission sleeve in sequence.

2. The anti-backward lock transmission according to claim 1, characterized in that: A circle of first one-way ratchet teeth is protruded from the disk surface of the inner centrifugal disk close to the high-speed transmission sleeve, and a circle of second one-way ratchet teeth that are adapted to the first one-way ratchet teeth are formed on the end surface of the high-speed transmission sleeve close to the inner centrifugal disk; when the first one-way ratchet teeth are combined with the second one-way ratchet teeth, the inner centrifugal disk can drive the high-speed transmission sleeve to rotate synchronously with it in one direction; when the first one-way ratchet teeth are separated from the second one-way ratchet teeth, the high-speed transmission sleeve can rotate relative to the inner centrifugal disk.

3. The anti-backward lock transmission according to claim 1 or 2, characterized in that: The inner centrifugal disk is spline-matched with the outer circumference of the input shaft through a first spline connection seat, the high-speed transmission sleeve is installed on the input shaft through a first needle roller bearing, and the second overrunning clutch is interference-pressed between the inner circumference of the output transmission sleeve and the outer circumference of the high-speed transmission sleeve. A retaining spring is provided at one end of the first needle roller bearing close to the high-speed transmission sleeve, and a retaining ring that can rotate relative to the input shaft is provided on the side of the retaining spring away from the first needle roller bearing. The elastic element is a return compression spring, one end of which is elastically supported on the retaining ring, and the other end is elastically supported on an end surface of the first spline connection seat close to the inner centrifugal disk.

4. The anti-backward lock transmission according to claim 3, characterized in that: The low-speed transmission sleeve includes a mounting sleeve portion with a cylindrical structure and a mounting disc portion extending radially outward from the mounting sleeve portion close to one end of the planetary gear train. The mounting sleeve portion is rotatably mounted on the input shaft through a second needle roller bearing. The first overrunning clutch is interference-pressed between the inner circumferential surface of the output transmission sleeve and the outer circumferential surface of the mounting sleeve portion. The mounting disc portion is fixedly connected to the output end of the planetary gear train.

5. The anti-backward lock transmission according to claim 1, characterized in that: The planetary gear system includes at least three planetary gears rotatably mounted on the gearbox and an inner ring gear meshed with each of the planetary gears. The input shaft is provided with a sun gear that rotates synchronously with the input shaft. The planetary gears are circumferentially distributed around the sun gear and meshed with the sun gear. The inner ring gear is connected to the low-speed transmission sleeve in a synchronously rotatable manner at one end close to the output shaft.

6. The anti-backward lock transmission according to claim 5, characterized in that: The planetary gear system further includes a planet carrier, which is fixedly mounted on the gearbox via a plurality of second fastening bolts. Both ends of each planetary gear are rotatably mounted on the planet carrier and the gearbox via corresponding planetary gear bearings.

7. The anti-backward lock transmission according to claim 1, characterized in that: The rolling element is a roller with a cylindrical structure, and the rolling groove is a wedge-shaped groove adapted to the roller.

8. An electric drive assembly, characterized in that: The invention comprises a drive motor and an anti-backward lock transmission according to any one of claims 1 to 7, wherein the motor shaft of the drive motor rotates synchronously with the input shaft.

9. A motorcycle using the electric drive assembly according to claim 8, characterized in that: The electric drive assembly is mounted on the motorcycle frame and can drive the rear wheel to rotate through the rear wheel transmission component.

10. An agricultural crawler vehicle using the electric drive assembly according to claim 8, characterized in that: The two electric drive assemblies are both installed on the crawler vehicle frame and can drive the active track wheels of the corresponding tracks to rotate through the corresponding track wheel transmission components.

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