A differential

Abstract

The application discloses a differential mechanism, aiming at solving the problem that the application of the automobile differential mechanism structure to the power tool vehicle greatly increases the production cost of the whole machine and greatly reduces the overall structural rigidity of the output shaft in the prior art. The technical scheme is as follows: the differential mechanism comprises a machine body, a transmission shaft and a differential assembly, the differential assembly comprises a driving part, an output shaft, a maintaining sleeve, a first tooth disc, a second tooth disc and a transmission gear, the driving part is coaxially arranged on the transmission shaft and rotates synchronously with the transmission shaft, the output shaft is coaxially arranged on the transmission shaft and rotates with the transmission shaft, the output shaft is provided with a driven part, the maintaining sleeve is coaxially arranged on the transmission shaft and rotates with the transmission shaft, the maintaining sleeve is provided with a maintaining frame, a plurality of positioning grooves are formed in the maintaining frame, rollers are arranged in the positioning grooves in a rolling mode, and the transmission gear is meshed with the first tooth disc and the second tooth disc.

Description

Technical Field

[0001] The present invention relates to a transmission device, and more specifically, to a differential. Background Technology

[0002] Power tool vehicles are commonly used mobile work equipment in landscaping, municipal, and agricultural operations, offering advantages such as flexibility, maneuverability, and adaptability to complex terrain. Currently, most small and medium-sized power tool vehicles adopt a coaxial dual-wheel synchronous drive structure, where the left and right drive wheels share the same power output shaft, ensuring that the two wheels maintain completely identical rotational speeds during operation.

[0003] When a vehicle turns, the turning radius of the outer wheel is larger than that of the inner wheel, causing the outer wheel to travel a significantly greater distance per unit time than the inner wheel. Since the coaxially connected wheels cannot adapt to this speed difference, relative sliding friction occurs between the inner and outer wheels and the ground. This not only accelerates tire wear and shortens tire lifespan but also causes steering jerking, reduced driving stability, and long-term impacts on the overall operational performance of the equipment.

[0004] To address these issues, existing technologies often borrow from automotive differential structures for power utility vehicles. This differential mechanism enables adaptive adjustment of the two wheel speeds, eliminating steering slippage and wear. However, this structure requires the separation of the integrated power take-off shaft, significantly increasing component and assembly costs, raising the overall production cost, and drastically reducing the overall structural rigidity of the output shaft. The significantly reduced load-bearing capacity of the split output shaft leads to a decline in the overall load-bearing capacity and deformation resistance of the utility vehicle, making it unsuitable for heavy-duty operations and severely limiting its applicability and reliability. Summary of the Invention

[0005] This invention provides a differential; it solves the problem in the prior art that applying the automotive differential structure to power vehicles would significantly increase the overall production cost of the machine and significantly reduce the overall structural rigidity of the output shaft.

[0006] The above-mentioned technical objective of the present invention is achieved through the following technical solution: a differential, including a body and a drive shaft rotatably mounted on the body, the two ends of the drive shaft extending from both sides of the body, and two sets of differential components are also provided on both sides of the body, the differential component including: a driving member, which is coaxially mounted on the drive shaft and rotates synchronously with it; An output shaft is coaxially rotatably mounted on the transmission shaft. The output shaft is provided with a driven member corresponding to the driving member. The driven member rotates synchronously with the output shaft. A transmission cylinder surrounding the driving member is connected to the driven member. The transmission cylinder is a cylindrical structure coaxial with the output shaft. An annular clutch groove is formed between the driving member and the transmission cylinder. The surface of the driving member facing the clutch groove is provided with several protrusions. The surface of the transmission cylinder facing the clutch groove is an annular surface. A retaining sleeve is coaxially rotatably mounted on the drive shaft. The retaining sleeve is provided with a retaining frame that extends into the clutch groove. The retaining frame is formed with a plurality of positioning grooves, and rollers are rolled in the positioning grooves. The first gear disc is coaxially rotatably mounted on the transmission shaft and forms a frictional transmission with the retaining sleeve. The second gear plate rotates synchronously with the output shaft and is coaxial with the transmission shaft. The transmission gear is rotatably mounted on the machine body and simultaneously meshes with the first gear disk and the second gear disk, causing the two gear disks to rotate in opposite directions.

[0007] The drive shaft in this invention can be connected to any existing power output device, such as an electric motor or an internal combustion engine. Therefore, the drive shaft is the power input shaft of the differential, and the driving component rotates synchronously with the drive shaft. The output shaft is the power output component of the differential, which is generally used to connect the wheel set. The driven component and the second gear plate both rotate synchronously with the output shaft. The second gear plate is connected to the first gear plate through a transmission gear, so that the first gear plate and the second gear plate rotate in opposite directions.

[0008] When the differential is engaged, it can transmit torque normally. Specifically, during the starting phase, the drive shaft rotates while the output shaft does not. The driven member, the first gear, and the second gear are all fixed. The maintaining sleeve and the first gear are connected by friction, so the maintaining frame is also temporarily fixed. The position of the roller is fixed. As the driving member rotates, the protrusion moves closer to the roller until the roller simultaneously contacts the annular surface on the driving member and the drive cylinder. At this point, the roller begins to drive, and the driving member and the driven member begin to rotate synchronously. This is when the running phase begins. The first gear and the second gear start to rotate synchronously and in opposite directions. Therefore, the maintaining frame rotates in the opposite direction relative to the driving member, pushing the roller to move towards the protrusion. This keeps the driving member, the roller, and the drive cylinder in a state of transmission engagement, and the output shaft and the drive shaft achieve a transmission state. When the differential is in differential mode, the output shaft cannot transmit torque to the drive shaft. Specifically, when the actual speed of the output shaft tends to be higher than the speed of the drive shaft, the speed of the driven member and the transmission cylinder begins to be higher than that of the driving member. Furthermore, the friction force generated by the transmission cylinder on the roller pushes the roller away from the protrusion. Therefore, the roller cannot be stably engaged, and thus cannot produce a transmission effect. That is, the roller tends to disengage under the action of the friction force of the transmission cylinder, so that the driving member, the roller, and the transmission cylinder cannot maintain transmission engagement, and the output shaft and the drive shaft achieve a differential state.

[0009] In summary, under normal conditions, the retainer can keep the rollers in the transmission engagement state, and the driving component can transmit torque to the driven component through the rollers; conversely, when the driven component rotates faster than the driving component, the transmission cylinder cannot transmit torque to the driving component through the rollers, so the driven component can rotate freely and will not transmit torque to the transmission shaft.

[0010] Furthermore, when the driving member, roller, and transmission cylinder are in clockwise engagement, the power output of the transmission shaft stops, and then the output shaft rotates in the opposite direction, driving the transmission cylinder to rotate counterclockwise. At this time, the transmission cylinder applies frictional force to the roller to continue engagement, and the driving member, roller, and transmission cylinder still have a high probability of remaining engaged, thus causing "jamming". To prevent this problem, the transmission structure between the driven member 90 and the transmission cylinder 110 is intentionally designed with a free stroke. When the output shaft rotates in the opposite direction, the two gear discs will rotate synchronously in the opposite direction, driving the retainer to rotate in the opposite direction, thereby pushing the roller out of the engagement position. Due to the free stroke, transmission between the transmission cylinder and the driven member will only occur after the roller is out of the engagement position. Therefore, this invention is less prone to "jamming" during forward and reverse rotation.

[0011] Furthermore, the driving component has a polygonal outline and correspondingly forms several meshing sides. These meshing sides are planar or irregular surfaces, and each meshing side forms a clutch cavity with its corresponding annular surface. The width of each clutch cavity is wider in the middle and narrower at both ends. Several clutch cavities are connected end-to-end to form a clutch groove. The rollers are cylindrical, with at most one roller in each clutch cavity. The cylindrical shape provides better compressive strength, thus allowing for the transmission of greater torque.

[0012] Furthermore, the machine body is provided with a bushing that rotatably engages with the drive shaft, and a bearing is connected between the bushing and the drive shaft; a first limiting plate is provided on one side of the bushing, an outer sleeve is drivenly connected to the driven member, and a retaining sleeve is provided on the machine body that axially engages and limits the outer sleeve, so that the retaining sleeve, the driving member, and the drive cylinder are constrained between the first limiting plate and the driven member, and the second gear is located on the inner wall of the outer sleeve. Through the above technical solution, the retaining sleeve and the driving member are fixed in the axial direction.

[0013] Furthermore, the outer side of the retaining sleeve has a cylindrical surface coaxial with the drive shaft, the first gear disc is rotatably sleeved on the cylindrical surface, and a rubber ring is clamped between the two. The rubber ring can provide significant frictional force, thereby enabling frictional transmission between the retaining sleeve and the first gear disc.

[0014] Furthermore, the two ends of the drive shaft extend from both sides of the machine body, and the differential assembly is provided in two sets, respectively located on both sides of the machine body.

[0015] In summary, the present invention has the following beneficial effects: 1. This invention can realize differential function, and the drive shaft is integrated, which has obvious advantages over the existing solution in the assembly and production stage. It is conducive to reducing the production cost of the whole machine, and will also greatly improve the overall structural rigidity of the output shaft and increase the load-bearing limit. 2. The differential assembly has a compact overall structure and relatively flexible placement. 3. Due to the idle distance, transmission will only occur between the transmission cylinder and the driven part after the rollers disengage from the meshing position. Therefore, the present invention is less likely to "jam" during forward and reverse rotation. Attached Figure Description

[0016] Figure 1 This is a partial cross-sectional view of the present invention; Figure 2 This is the front view of the present invention; Figure 3 This is a schematic diagram of the differential assembly. Figure 4 This is an axial sectional view of the differential assembly; Figure 5 for Figure 4 Sectional view along axis AA; Figure 6 A cross-sectional view showing the driving, rolling, and driven components maintaining the transmission engagement state; Figure 7 This is an exploded view of the differential assembly; Figure 8 This is a schematic diagram of the driven component. Figure 9 This is a schematic diagram of the outer sleeve structure; Figure 10 This is an assembly drawing showing the connection between the transmission cylinder and the driven component. Figure 11 This is a schematic diagram of the clutch groove.

[0017] Explanation of reference numerals in the attached figures: 10. Body; 20. Drive shaft; 21. Anti-disengagement component; 30. Driving component; 31. Key; 32. Meshing side; 33. Protrusion; 40. Output shaft; 41. First slot; 50. Holding sleeve; 51. Holding bracket; 52. Positioning groove; 53. Roller; 54. Cylindrical surface; 55. Rubber ring; 60. First gear plate; 70. Second gear plate; 80. Transmission gear; 90. Driven component; 91. First locking block; 92. Second locking block; 93. Third locking block ; 94, shaft hole; 95, oil groove; 96, limiting step; 100, clutch groove; 101, clutch cavity; 110, transmission cylinder; 111, annular surface; 112, second slot; 113, assembly clearance; 120, wheel set; 130, bushing; 131, bearing; 132, first limiting piece; 140, outer sleeve; 141, inner flange; 142, third slot; 150, ferrule; 160, mounting base; 170, metal sheet; 180, snap ring. Detailed Implementation

[0018] To enable those skilled in the art to better understand the technical solutions of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of this application can be combined with each other.

[0019] In the description of this invention, it should be noted that the terms "upper", "lower", "inner", "outer", "top / bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0020] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," "set up / connected," "connected," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0021] The present invention will now be described in detail with reference to the accompanying drawings.

[0022] Example: See Figure 1 and Figure 2A differential includes a body 10 and a single drive shaft 20 rotatably mounted on the body 10. Both ends of the drive shaft 20 extend from both sides of the body 10. Two sets of differential components are provided between the body 10 and the drive shaft 20. The differential components include: a driving element 30, an output shaft 40, a retaining sleeve 50, a first gear 60, a second gear 70, and a transmission gear 80.

[0023] Active component 30, see Figure 5 It is coaxially mounted on the transmission shaft 20 and rotates synchronously with it. A key 31 is provided between the driving member 30 and the transmission shaft 20. The outline of the driving member 30 is approximately hexagonal and has 6 meshing side surfaces 32.

[0024] Output shaft 40, see Figure 1 and Figure 3 The drive member 30 is coaxially mounted on the drive shaft 20. The output shaft 40 is provided with a driven member 90 corresponding to the drive member 30. The driven member 90 rotates synchronously with the output shaft 40. An annular clutch groove 100 is formed between the drive member 30 and the driven member 90. The drive member 30 has 6 protrusions 33 on the side facing the clutch groove 100. The corners of the regular polygons constitute the protrusions 33. The driven member 90 is provided with a drive cylinder 110 surrounding the drive member 30. The drive cylinder 110 is a cylindrical structure coaxial with the output shaft 40. The clutch groove 100 is formed between the inner circumference of the drive cylinder 110 and the 6 meshing side surfaces 32. The side of the drive cylinder 110 facing the clutch groove 100 is an annular surface 111. A wheel set 120 is coaxially fixed on the output shaft 40.

[0025] Maintain a 50% hold, see below. Figure 5 and Figure 7 It is coaxially mounted on the transmission shaft 20. The retaining sleeve 50 is provided with a retaining bracket 51 extending into the clutch groove 100. Six positioning grooves 52 are formed on the retaining bracket 51, and rollers 53, which are cylindrical, roll within the positioning grooves 52. (See...) Figure 11 The meshing side surface 32 is a planar or irregular surface. Each meshing side surface 32 forms a clutch cavity 101 with the corresponding annular surface 111. The width of the clutch cavity 101 is set to be wider in the middle and narrower at both ends. The six clutch cavities 101 are connected end to end to form a clutch groove 100. In order to improve the meshing effect, the closer the meshing side surface 32 is to the protrusion 33, the smaller the angle between it and the annular surface 111. Under the same torque, the smaller the angle, the more stable the meshing effect of the meshing side surface 32, the annular surface 111 and the roller.

[0026] First gear 60, see [reference] Figure 4 and Figure 7 It is coaxially mounted on the transmission shaft 20 and forms a friction transmission with the retaining sleeve 50; Second gear 70, see [reference] Figure 4It rotates synchronously with the output shaft 40 and is coaxial with the transmission shaft 20; Transmission gear 80, see Figure 4 It is rotatably mounted on the body 10 and simultaneously meshes with the first gear 60 and the second gear 70, causing the two gears to rotate in opposite directions.

[0027] In this embodiment, the drive shaft 20 can be connected to any existing power output device, such as an electric motor or an internal combustion engine. Therefore, the drive shaft 20 is the power input shaft of the differential, and the driving member 30 rotates synchronously with the drive shaft 20. The output shaft 40 is the power output member of the differential, used to connect the wheel set 120. The driven member 90 and the second gear 70 both rotate synchronously with the output shaft 40. The second gear 70 is connected to the first gear 60 through the transmission gear 80, so that the first gear 60 and the second gear 70 rotate in opposite directions.

[0028] When the differential is engaged, it can transmit torque normally. Specifically, during the starting phase, the drive shaft 20 rotates while the output shaft 40 does not. The driven member 90, the first gear 60, and the second gear 70 are all fixed. The retaining sleeve 50 and the first gear 60 are connected by friction transmission. This friction transmission effect is greater than the friction between the retaining sleeve 50 and the drive shaft 20. Therefore, the retaining bracket 51 is also temporarily fixed, and the position of the roller 53 is fixed. As the driving member 30 rotates, the protrusion 33 moves closer to the roller 53 until the roller 53 is aligned with the drive shaft 20. When the roller 53 comes into contact with the annular surface 111 on the driving member 30 and the transmission cylinder 110, the roller 53 begins to drive, and the driving member 30 and the driven member 90 begin to rotate synchronously. At this time, the running stage begins. The first toothed disc 60 and the second toothed disc 70 begin to rotate synchronously and in opposite directions. Therefore, the retainer 51 rotates in the opposite direction relative to the driving member 30, pushing the roller 53 to move towards the protrusion 33 side, so that the driving member 30, the roller 53 and the transmission cylinder 110 maintain the transmission meshing state, and the output shaft 40 and the transmission shaft 20 achieve the transmission state. When the differential is in differential mode, the output shaft cannot transmit torque to the drive shaft. Specifically, when the actual speed of the output shaft 40 tends to be higher than the speed of the drive shaft 20, the speed of the driven member 90 and the transmission cylinder 110 begins to be higher than that of the driving member 30. Furthermore, the friction force generated by the transmission cylinder 110 on the roller 53 pushes the roller 53 away from the protrusion 33. Therefore, the roller 53 cannot be stably engaged, and thus cannot produce a transmission effect. That is, the roller 53 tends to disengage under the action of the friction force of the transmission cylinder 110, so that the driving member 30, the roller 53, and the transmission cylinder 110 cannot maintain transmission engagement, and the output shaft 40 and the drive shaft 20 achieve a differential state.

[0029] In summary, under normal conditions, the retainer 51 can keep the roller 53 in the transmission engagement state, and the driving member 30 can transmit torque to the driven member 90 through the roller 53; conversely, when the speed of the driven member 90 is higher than that of the driving member 30, the driven member 90 cannot transmit torque to the driving member 30 through the roller 53, so the driven member 90 can rotate freely and will not interfere with the normal rotation of the driving member 30.

[0030] Specifically, the transmission structure between the driven member 90 and the transmission cylinder 110 has a free travel. When the output shaft 40 rotates in the opposite direction, the two gear discs will rotate in the opposite direction synchronously, driving the retainer 51 to rotate in the opposite direction, thereby pushing the roller 53 out of the meshing position. Due to the free travel, the transmission between the transmission cylinder 110 and the driven member 90 will only occur after the roller 53 is out of the meshing position. Therefore, this embodiment is less prone to "jamming" during forward and reverse rotation.

[0031] See Figure 4 The machine body 10 is provided with a bushing 130 that rotatably engages with the drive shaft 20, and a bearing 131 is connected between the bushing 130 and the drive shaft 20. A first limiting piece 132 is provided on one side of the bushing 130, and an outer sleeve 140 is drivenly connected to the driven member 90. The machine body 10 is provided with a retaining sleeve 150 that axially engages and limits the outer sleeve 140, so that the retaining sleeve 50, the driving member 30, and the drive cylinder 110 are constrained between the first limiting piece 132 and the driven member 90, and the second gear 70 is located on the inner wall of the outer sleeve 140. Through the above technical solution, the retaining sleeve 50 and the driving member 30 are fixed in the axial direction.

[0032] See Figure 4 and Figure 7 The bushing 130 is also integrally provided with a mounting base 160 that is fixed to the machine body 10. The ferrule 150 is fixed on the mounting base 160. Two transmission gears 80 are provided and are rotatably mounted on the mounting base 160. A metal plate 170 is also sleeved on the transmission shaft 20. The metal plate 170 is located between the driving member 30 and the driven member 90 to avoid direct contact between the two and thus prevent wear.

[0033] For details, see Figure 4 and Figure 7 The outer side of the retaining sleeve 50 has a cylindrical surface 54 coaxial with the drive shaft 20. The first gear disc 60 is rotatably sleeved on the cylindrical surface 54, and a rubber ring 55 is clamped between the two. The rubber ring 55 can provide significant friction, thereby enabling frictional transmission between the retaining sleeve 50 and the first gear disc 60.

[0034] For details, see Figure 8The output shaft 40 is a circular tube structure and is coaxially rotatably sleeved on the transmission shaft 20. The driven member 90 is rotatably sleeved on the transmission shaft 20. The driven member 90 has a number of first locking blocks 91 arranged in a circular array at one end near the output shaft 40. The output shaft 40 has a number of first locking slots 41 that engage with the first locking blocks 91. The outer end of the transmission shaft 20 is fixed with an anti-detachment member 21. The output shaft 40 is constrained between the anti-detachment member 21 and the driven member 90, so that the first locking blocks 91 and the first locking slots 41 remain engaged.

[0035] For details, see Figure 8 and Figure 10 The driven member 90 is also provided with a number of second locking blocks 92 and third locking blocks 93 arranged in a circumferential array. The transmission cylinder 110 is provided with a number of second locking grooves 112 that engage with the second locking blocks 92, and an assembly gap 113 is formed between the second locking grooves 112 and the second locking blocks 92. The assembly gap 113 causes idle stroke. The outer sleeve 140 is provided with an inner flange 141 sleeved on the driven member 90. The inner flange 141 is provided with a number of third locking grooves 142 that engage with the third locking blocks 93.

[0036] To simplify production, this embodiment manufactures the follower 90, output shaft 40, transmission cylinder 110, and outer sleeve 140 separately. The shaft transmission connection is achieved by interlocking three types of locking blocks and three types of locking slots, resulting in simple assembly and reliable transmission.

[0037] Specifically, the driven member 90 has a shaft hole 94 for accommodating the drive shaft 20, and the side wall of the shaft hole 94 is provided with several oil grooves 95.

[0038] Specifically, the driven member 90 is provided with a limiting step 96 that engages and limits with the inner wall of the inner flange 141, and a retaining spring 180 that engages and limits with the outer wall of the inner flange 141.

[0039] The above description is merely a preferred embodiment of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principles of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. A differential, comprising a body (10) and a drive shaft (20) rotatably mounted on the body (10), characterized in that, The two ends of the drive shaft (20) extend from both sides of the body (10). The two sides of the body (10) are also provided with two sets of differential components. The differential components include: a driving component (30), which is coaxially mounted on the drive shaft (20) and rotates synchronously with it. An output shaft (40) is coaxially rotatably mounted on the transmission shaft (20). The output shaft (40) is provided with a driven member (90) corresponding to the driving member (30). The driven member (90) rotates synchronously with the output shaft (40). A transmission cylinder (110) surrounding the driving member (30) is connected to the driven member (90). The transmission cylinder (110) is a cylindrical structure coaxial with the output shaft (40). An annular clutch groove (100) is formed between the driving member (30) and the transmission cylinder (110). A plurality of protrusions (33) are provided on the surface of the driving member (30) facing the clutch groove (100). The surface of the transmission cylinder (110) facing the clutch groove (100) is an annular surface (111). A retaining sleeve (50) is coaxially rotatably mounted on the transmission shaft (20). The retaining sleeve (50) is provided with a retaining bracket (51) extending into the clutch groove (100). A plurality of positioning grooves (52) are formed on the retaining bracket (51), and rollers (53) are rolled in the positioning grooves (52). The first gear disc (60) is coaxially rotatably mounted on the transmission shaft (20) and forms a friction transmission with the retaining sleeve (50); The second gear (70) rotates synchronously with the output shaft (40) and is coaxial with the transmission shaft (20); The transmission gear (80) is rotatably mounted on the machine body (10) and simultaneously meshes with the first gear disc (60) and the second gear disc (70), causing the two gear discs to rotate in opposite directions; When the differential is engaged, the retainer (51) rotates in the opposite direction to the drive member (30), and the drive member (30), roller (53), and transmission cylinder (110) are engaged in transmission, and the output shaft (40) and the transmission shaft (20) are in a transmission state. When the differential is in differential state, the roller (53) tends to disengage under the friction of the transmission cylinder (110), so that the driving component (30), roller (53) and transmission cylinder (110) cannot maintain transmission engagement, and the output shaft (40) and transmission shaft (20) achieve differential state.

2. The differential according to claim 1, characterized in that: The transmission structure between the driven member (90) and the transmission cylinder (110) has a free stroke.

3. The differential according to claim 2, characterized in that: The active component (30) has a polygonal outline and is provided with several meshing side surfaces (32). The meshing side surfaces (32) are planar or irregular surfaces. Each meshing side surface (32) is connected to a corresponding annular surface (111) to form a clutch cavity (101). The width of the clutch cavity (101) is set to be wider in the middle and narrower at both ends. Several clutch cavities (101) are connected end to end to form a clutch groove (100). The roller (53) is a cylindrical structure. At most one roller (53) is provided in each clutch cavity (101).

4. The differential according to claim 3, characterized in that: The machine body (10) is provided with a bushing (130) that rotates with the drive shaft (20), and a bearing (131) is connected between the bushing (130) and the drive shaft (20); a first limiting piece (132) is provided on one side of the bushing (130), and an outer sleeve (140) is connected to the driven member (90) for transmission. The machine body (10) is provided with a retaining sleeve (150) that engages and limits the outer sleeve (140) axially, so that the retaining sleeve (50), the driving member (30) and the drive cylinder (110) are constrained between the first limiting piece (132) and the driven member (90), and the second gear plate (70) is located on the inner wall of the outer sleeve (140).

5. The differential according to claim 4, characterized in that: The outer side of the retaining sleeve (50) has a cylindrical surface (54) coaxial with the drive shaft (20), the first gear plate (60) is rotatably sleeved on the cylindrical surface (54), and a rubber ring (55) is clamped between the two.

6. The differential according to claim 4, characterized in that: The output shaft (40) is a cylindrical structure and is coaxially rotatably mounted on the transmission shaft (20). The driven member (90) is coaxially rotatably mounted on the transmission shaft (20). The driven member (90) has several first locking blocks (91) arranged in a circular array at one end near the output shaft (40). The output shaft (40) has several first slots (41) that engage with the first locking blocks (91). The outer end of the transmission shaft (20) is fixed with an anti-detachment member (21). The output shaft (40) is constrained between the anti-detachment member (21) and the driven member (90), so that the first locking blocks (91) and the first slots (41) remain engaged.

7. The differential according to claim 4, characterized in that: The driven member (90) is also provided with a plurality of second locking blocks (92) and third locking blocks (93) arranged in a circular array. The transmission cylinder (110) is provided with a plurality of second locking grooves (112) that engage with the second locking blocks (92) in transmission. An assembly gap (113) is formed between the second locking grooves (112) and the second locking blocks (92). The assembly gap (113) causes idle stroke. The outer sleeve (140) is provided with an inner flange (141) sleeved on the driven member (90). The inner flange (141) is provided with a plurality of third locking grooves (142) that engage with the third locking blocks (93) in transmission.

8. The differential according to claim 7, characterized in that: The driven member (90) has a shaft hole (94) for accommodating the drive shaft (20), and the side wall of the shaft hole (94) is provided with a plurality of grooves (95).

9. The differential according to claim 1, characterized in that: A wheel assembly (120) is coaxially fixed on the output shaft (40).

Images