Speed reducer assembly with differential mechanism and vehicle

Abstract

The invention discloses a speed reducer assembly with a differential mechanism and a vehicle, the speed reducer assembly comprises a driven gear and the differential mechanism, a center hole is formed in the driven gear, and a containing groove extending in the radial direction is formed in the driven gear; the differential mechanism comprises a differential mechanism shell and a planetary gear shaft, the differential mechanism shell is arranged in the center hole in a penetrating mode and fixedly connected with the driven gear, a shaft hole is further formed in the differential mechanism shell, and the planetary gear shaft is in clearance fit with the shaft hole and arranged in the differential mechanism shell in a penetrating mode through the shaft hole. The two ends of the planetary gear shaft are exposed out of the differential mechanism shell and arranged in the containing groove. The end of the planetary gear shaft is provided with a first plane, the first plane and the side wall of the containing groove are oppositely arranged, and when the driven gear rotates, the side wall abuts against the first plane so as to drive the planetary gear shaft and the driven gear to coaxially rotate. Through the scheme, the weight of the differential mechanism can be reduced, and the economical efficiency of a vehicle is improved.

Description

Technical Field

[0001] This application relates to the field of automotive technology, and in particular to a reducer assembly with a differential and a vehicle. Background Technology

[0002] As a crucial component of the electric drive transmission system, the differential ensures the transmission of power torque and the speed difference between the inner and outer wheels during cornering, preventing tire slippage and directly impacting the vehicle's performance, reliability, and comfort.

[0003] Current market users have increasingly higher requirements for lightweight electric drives. However, existing differentials are large in size and heavy in weight, which increases the weight of the reduction gear assembly and makes the car less fuel-efficient. Summary of the Invention

[0004] The main technical problem this application addresses is to provide a reducer assembly with a differential and a vehicle that can reduce the weight of the differential and improve the vehicle's fuel economy.

[0005] To solve the above-mentioned technical problems, one technical solution adopted in this application is: providing a reducer assembly with a differential, including a driven gear and a differential. The driven gear has a central hole and a radially extending receiving groove. The differential includes a differential housing and a planetary gear shaft. The differential housing passes through the central hole and is fixedly connected to the driven gear. The differential housing also has a shaft hole. The planetary gear shaft is clearance-fitted with the shaft hole and passes through the shaft hole in the differential housing. Both ends of the planetary gear shaft protrude outside the differential housing and are disposed in the receiving groove. The end of the planetary gear shaft has a first plane. The first plane is disposed opposite to the side wall of the receiving groove. When the driven gear rotates, the side wall abuts against the first plane to drive the planetary gear shaft to rotate coaxially with the driven gear.

[0006] The differential housing is externally connected to a fixing part, which is fixedly connected to the driven gear and fits against the end face of the driven gear. This technical solution achieves the connection between the differential and the driven gear by setting a fixing part, allowing the fixing part to support the driven gear axially. Furthermore, the fixing part increases the contact area between the differential housing and the driven gear, dispersing the stress between them and preventing stress concentration.

[0007] The fixing part has a through hole extending axially along the driven gear, and the driven gear has a threaded hole corresponding to the through hole. The fixing part has a fixing bolt, which passes through the through hole and is threadedly connected to the threaded hole. In this technical solution, the fixing bolt passes through the through hole and is threadedly connected to the threaded hole, so that the fixing part abuts against the first end face of the driven gear, thereby fixing the differential housing and the driven gear relatively and axially supporting the driven gear to prevent offset or deflection, ensuring accurate gear meshing, and resulting in better NVH levels in the reducer. Simultaneously, the connection between the differential housing and the driven gear via the fixing bolt is simple and has a low technical threshold. Specifically, in this embodiment, there are four fixing parts and four fixing bolts. Since this application removes the differential housing from the torque transmission path, it simplifies the connection structure between the differential housing and the driven gear, and achieves fixation with fewer fixing bolts, thus achieving vehicle weight reduction. Meanwhile, since the differential housing and driven gear are detachably connected by fixing bolts, the differential can be supplied separately from the driven gear, and is easy to install and remove.

[0008] The receiving groove includes two opposing and parallel sidewalls; each end of the planetary gear shaft is provided with two first planes, which are arranged in parallel. In this technical solution, the two sidewalls limit the planetary gear shaft from both sides, improving the stability of the planetary gear shaft within the driven gear and enabling it to stably transmit torque.

[0009] In this design, one end of the receiving groove communicates with the central hole and forms an opening on the wall of the central hole. The other end of the receiving groove extends away from the central hole and forms a bottom wall on the driven gear. The bottom wall is disposed opposite to the end face of the planetary gear shaft and is clearance-fitted. In this technical solution, the length of the receiving groove of the planetary gear shaft is greater than the length of the planetary gear shaft. The axial limiting of the planetary gear shaft in the driven gear can be achieved by the differential housing. For example, the limiting in this direction can be achieved by setting the shaft hole of the planetary gear shaft and the differential housing to be tightly fitted.

[0010] The planetary gear shaft and the differential housing are respectively provided with a first positioning hole and a second positioning hole. The differential also includes a positioning pin, which is inserted into the first positioning hole and the second positioning hole. This technical solution achieves the positioning of the differential and the planetary gear shaft by inserting the positioning pin into the first positioning hole and the second positioning hole, which facilitates the transportation of the differential and the planetary gear shaft in a fixed form. The differential can be supplied separately from other structures of the reducer assembly, such as the driven gear.

[0011] The differential housing has a mounting cavity containing two planetary gears and two half-shaft gears. The planetary gears are mounted on the planetary gear shaft and rotatably connected to it. The half-shaft gears mesh with the planetary gears and are rotatably connected to the differential housing.

[0012] The reducer assembly further includes a reducer housing and a tapered bearing. The driven gear is disposed within the reducer housing, and the tapered bearing is connected between the reducer housing and the differential housing, so that the differential housing is rotatably connected within the reducer housing.

[0013] The differential housing is made of either cast iron or stainless steel. Cast iron differential housings are less expensive and easier to manufacture. Because they retain the traditional cast iron differential housing design, they provide better support for the driven gear compared to thin-walled welded cover plates, keeping the meshing misalignment of the driven gear at a lower level and resulting in better NVH (noise, vibration, and harshness) levels.

[0014] Another technical solution adopted in this application is to provide a vehicle including a reducer assembly with a differential as described in any of the above embodiments.

[0015] The beneficial effects of this application are as follows: Unlike existing technologies, this application decouples the planetary gear shaft of the differential from the differential housing, and achieves torque transmission between the planetary gear shaft and the driven gear through a receiving groove and a first plane. Unlike related technologies, the torque transmission route in this application is that the driven gear directly transmits the torque to the planetary gear shaft, separating the differential housing from the torque transmission route. Therefore, the differential housing does not need to bear torque; it only needs to support the driven gear. Thus, this application eliminates the need for a heavy connecting structure between the differential housing and the driven gear and reduces the number of connecting parts, thereby reducing the weight of the differential and reduction gear assembly, achieving the goal of vehicle lightweighting, and improving vehicle economy. Attached Figure Description

[0016] Figure 1 This is a perspective schematic diagram of an embodiment of the reducer assembly with differential of this application; Figure 2 This application is Figure 1 A sectional view; Figure 3 This is a perspective schematic diagram of an embodiment of the driven gear of this application; Figure 4 This is a perspective view of an embodiment of the differential of this application; Figure 5 This is a perspective view of an embodiment of the planetary gear shaft of this application; Figure 6This is a cross-sectional schematic diagram of another embodiment of the reducer assembly of this application.

[0017] Reference numerals in the attached figures: 100, reducer assembly; 10, differential; 11, differential housing; 111, shaft hole; 112, fixing part; 113, mounting cavity; 114, mounting hole; 115, oil inlet; 116, second positioning hole; 12, planetary gear shaft; 121, first plane; 122, second end face; 123, flat groove; 124, first positioning hole; 13, planetary gear; 131, planetary gear washer; 14, half-shaft gear; 141, half-shaft gear washer; 15, fixing bolt; 20, driven gear; 21, center hole; 22, receiving groove; 221, side wall; 222, bottom wall; 23, first end face; 24, screw hole. Detailed Implementation

[0018] To make the objectives, technical solutions, and effects of this application clearer and more explicit, the following detailed description is provided with reference to the accompanying drawings and embodiments. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0019] For ease of understanding, the attached diagram shows the mutually orthogonal X-axis, Y-axis, and Z-axis. The direction along the X-axis is called the X-direction, which is the front-rear direction of the vehicle body structure; the direction along the Y-axis is called the Y-direction, which is the width direction of the vehicle body structure; and the direction along the Z-axis is called the Z-direction, which is the height direction of the vehicle body structure.

[0020] See Figure 1 and Figure 2 , Figure 1 This is a perspective schematic diagram of an embodiment of the reducer assembly with differential according to this application. Figure 2 This application is Figure 1 A cross-sectional view. The reducer assembly 100 includes a differential 10 and a driven gear 20. The differential 10 includes a differential housing 11 and a planetary gear shaft 12.

[0021] See Figure 3 , Figure 3 This is a perspective view of an embodiment of the driven gear of this application. The driven gear 20 has a central hole 21 and a radially extending receiving groove 22. It should be noted that the driven gear 20 is the last stage driven gear 20 in the gear set of the main reducer in the reducer assembly 100. Figure 1 and Figure 2Only the driven gear 20 of the main reducer is shown; other structures of the main reducer are omitted. The center hole 21, which is the inner hole of the driven gear 20, extends through the driven gear 20 along its axial direction (shown by the Y-axis in the figure). The center hole 21 is used to accommodate the differential 10. A receiving groove 22 extends radially (shown by the X-axis in the figure) within the driven gear 20 and is used to accommodate the planetary gear shaft 12 of the differential 10. The radial length of the receiving groove 22 can be less than or greater than the diameter of the center hole 21. The receiving groove 22 can extend through the driven gear 20 in the Y-direction or be a groove structure that does not extend through the driven gear 20. In this embodiment, in the axial direction of the driven gear 20, the first end face 23 inside the driven gear 20 is concave relative to the edge, that is, the thickness inside the driven gear 20 in the Y direction is less than the thickness of the edge. While ensuring that the driven gear 20 meshes with other gears of the main reducer, the thickness of the driven gear 20 can be reduced, thereby reducing the weight of the driven gear 20 and thus achieving the weight reduction of the reducer assembly 100.

[0022] See Figure 1 and combined Figure 4 , Figure 4 This is a perspective view of an embodiment of the differential according to this application. The differential housing 11 passes through the central hole 21 and is fixedly connected to the driven gear 20. The differential housing 11 is also provided with a shaft hole 111. The planetary gear shaft 12 passes through the shaft hole 111 and passes through the differential housing 11. The two ends of the planetary gear shaft 12 are exposed outside the differential housing 11 and are disposed in the receiving groove 22. Specifically, the differential housing 11 is an integral structure. The material of the differential housing 11 can be ductile iron or stainless steel, etc. The differential housing 11 made of cast iron has a lower cost, and because it retains the traditional cast iron differential housing 11, it provides better support for the driven gear 20 compared with the thin-walled part of the welded cover plate, which can keep the meshing misalignment of the driven gear 20 at a low level and has a better NVH (Noise, Vibration, Harshness) level. Along the axial direction Y of the driven gear 20, the differential housing 11 protrudes beyond the first end face 23 of the driven gear 20. The differential housing 11 is provided with two shaft holes 111, which are distributed on both sides of the differential housing 11 along the radial direction X of the driven gear 20. The shaft holes 111 are clearance-fitted with the planetary gear shaft 12, so that the planetary gear shaft 12 can pass radially through the differential housing 11 and engage with the receiving groove 22 of the driven gear 20.

[0023] See Figure 2 and combined Figure 5 , Figure 5This is a perspective view of an embodiment of the planetary gear shaft of this application. The end of the planetary gear shaft 12 has a first plane 121, which is disposed opposite to the side wall 221 of the receiving groove 22. When the driven gear 20 rotates, the side wall 221 abuts against the first plane 121 to drive the planetary gear shaft 12 and the driven gear 20 to rotate coaxially. Specifically, the planetary gear shaft 12 is cylindrical in shape. The first plane 121 is parallel to the axial direction of the planetary gear shaft 12 and parallel to the axial direction of the driven gear 20. The first plane 121 can be formed by partially cutting the side of the end of the planetary gear shaft 12. In this embodiment, the first plane 121 is rectangular. The side wall 221 of the receiving groove 22 is an inner wall in a plane parallel to the first plane 121. In this embodiment, the side wall 221 can also be rectangular. The vehicle's power is transmitted from the drive unit to the driven gear 20, which rotates around its own axis. When the driven gear 20 rotates, the side wall 221 of the receiving groove 22 comes into contact with the first plane 121 of the planetary gear shaft 12 and applies force to the planetary gear shaft 12, causing the planetary gear shaft 12 and the driven gear 20 to rotate coaxially. The contact between the first plane 121 and the side wall 221 results in a large contact area, which ensures torque transmission while reducing stress concentration.

[0024] In related technologies, the torque transmission route of the reducer assembly 100 is sequentially the driven gear 20, the differential housing 11, and the planetary gear shaft 12. The differential housing 11 needs to bear the torque and support both the driven gear 20 and the planetary gear shaft 12, which means that the differential housing 11 needs to achieve a stable connection with the driven gear 20 through a heavy connection structure (such as a flange) and a large number of connecting parts (such as bolts).

[0025] This application decouples the planetary gear shaft 12 of the differential 10 from the differential housing 11, and achieves torque transmission between the planetary gear shaft 12 and the driven gear 20 through the receiving groove 22 and the first plane 121. The direction of this torque is the direction of rotation around the Y-axis. Unlike related technologies, the torque transmission route in this application is that the driven gear 20 directly transmits the torque to the planetary gear shaft 12, separating the differential housing 11 from the torque transmission route. This allows the differential housing 11 to not bear torque, but only to support the driven gear 20. Therefore, this application can eliminate the heavy connecting structure between the differential housing 11 and the driven gear 20 and reduce the number of connecting parts, thereby reducing the weight of the differential 10 and the reduction gear assembly 100, achieving the goal of vehicle lightweighting, and improving vehicle economy.

[0026] Continue reading Figure 1 and Figure 4In some embodiments, a fixing part 112 is externally connected to the differential housing 11. The fixing part 112 is fixedly connected to the driven gear 20, and the fixing part 112 is in contact with the end face of the driven gear 20. Specifically, the fixing part 112 protrudes radially from the differential housing 11 and is integrally formed with the differential housing 11. There are multiple fixing parts 112, which are evenly distributed circumferentially outside the differential housing 11. The fixing part 112 can be detachably connected to the driven gear 20 by a fastener, or the fixing part 112 can be welded to the first end face 23 of the driven gear 20. In this embodiment, the connection between the differential 10 and the driven gear 20 is achieved by setting the fixing part 112, so that the fixing part 112 can support the driven gear 20 axially, and the fixing part 112 can increase the contact area between the differential housing 11 and the driven gear 20, disperse the stress between them, and avoid the problem of stress concentration.

[0027] Continue reading Figure 1 and Figure 3 In some embodiments, the fixing part 112 is detachably connected to the driven gear 20 via a fixing member, which includes a fixing bolt 15. The fixing part 112 has a through hole (not shown) extending axially along the driven gear 20, and the driven gear 20 has a threaded hole 24 corresponding to the through hole. The fixing bolt 15 passes through the through hole and is threadedly connected to the threaded hole 24, so that the fixing part 112 abuts against the first end face 23 of the driven gear 20, thereby fixing the differential housing 11 relative to the driven gear 20 and supporting the driven gear 20 axially to prevent it from shifting or deflecting, ensuring accurate gear meshing, and giving the reducer a better NVH level. At the same time, the connection between the differential housing 11 and the driven gear 20 via the fixing bolt 15 is simple and has a low technical threshold. Specifically, in this embodiment, there are four fixing parts 112 and four fixing bolts 15. Since this application removes the differential housing 11 from the torque transmission path, the connection structure between the differential housing 11 and the driven gear 20 can be simplified, and the two can be fixed with fewer fixing bolts 15, thus achieving vehicle weight reduction. At the same time, since the differential housing 11 and the driven gear 20 are detachably connected by fixing bolts 15, the differential 10 can be supplied separately from the driven gear 20, which facilitates installation and disassembly.

[0028] Continue reading Figure 3 and Figure 5The receiving groove 22 includes two opposing and parallel sidewalls 221. Each end of the planetary gear shaft 12 is provided with two first planes 121, which are arranged in parallel. The two sidewalls 221 are the inner walls on both sides of the receiving groove 22, corresponding to the two first planes 121 of the planetary gear shaft 12. The two sidewalls 221 limit the planetary gear shaft 12 on both sides, improving the stability of the planetary gear shaft 12 within the driven gear 20, so that it can stably transmit torque.

[0029] In some embodiments, one end of the receiving groove 22 communicates with the central hole 21 and forms an opening on the wall of the central hole 21. Specifically, in this embodiment, the receiving groove 22 is located between the central hole 21 and the tooth surface of the driven gear 20, that is, the receiving groove 22 is recessed radially from the inner wall of the central hole 21 to the edge. This structure can further reduce the volume and weight of the driven gear 20. In other embodiments, a boss may also be provided inwardly on the inner wall of the central hole 21, and the receiving groove 22 is disposed on the boss, with its opening located on the side of the boss facing the central hole 21. The other end of the receiving groove 22 extends away from the central hole 21 and forms a bottom wall 222 on the driven gear 20. The bottom wall 222 is disposed opposite to the second end face 122 of the planetary gear shaft 12 and is clearance-fitted. When the length of the receiving groove 22 in the planetary gear shaft 12 is greater than the length of the planetary gear shaft 12, the limiting of the planetary gear shaft 12 in the axial direction of the driven gear 20 can be achieved by the differential housing 11. For example, the limiting in this direction can be achieved by setting the planetary gear shaft 12 and the shaft hole 111 of the differential housing 11 to be tightly fitted.

[0030] In other embodiments, the receiving groove 22 is interference-fitted with the planetary gear shaft 12 in the axial direction of the planetary gear shaft 12, limiting the axial direction X of the planetary gear shaft 12. Simultaneously, the bottom wall 222 abuts against the second end face 122, also limiting the planetary gear shaft 12 in the Y direction. In this case, the limiting of the planetary gear shaft 12 in all directions is provided by the driven gear 20, and no additional fixing structure is required. This further decouples the limiting effect of the differential housing 11 on the planetary gear shaft 12. For example, the diameter of the shaft hole 111 can be set to be larger than the diameter of the planetary gear shaft 12. The shaft hole 111 is only used to allow the planetary gear shaft 12 to pass through the differential housing 11 and connect with the driven gear 20; the shaft hole 111 no longer provides a limiting function for the planetary gear shaft 12. The above-mentioned configuration increases the size of the shaft hole 111, which can further reduce the weight of the differential housing 11. Of course, in other embodiments, the shaft hole 111 and the receiving groove 22 can be simultaneously fitted to the planetary gear shaft 12; or the driven gear 20 can be limited in all directions by other fixing methods.

[0031] Optionally, see Figure 6 , Figure 6This is a cross-sectional schematic diagram of another embodiment of the reducer assembly of this application. In some embodiments, the planetary gear shaft 12 and the differential housing 11 are respectively provided with a first positioning hole 124 and a second positioning hole 116. The differential 10 also includes a positioning pin (not shown), which is inserted into the first positioning hole 124 and the second positioning hole 116. Specifically, the first positioning hole 124 and the second positioning hole 116 both extend along the Y direction. The first positioning hole 124 passes through the planetary gear shaft 12. By inserting the positioning pin into the first positioning hole 124 and the second positioning hole 116, the positioning of the differential 10 and the planetary gear shaft 12 is achieved, which facilitates the transport of the differential 10 and the planetary gear shaft 12 in a fixed form. The differential 10 can be supplied separately from other structures of the reducer assembly 100, such as the driven gear 20. In other embodiments, the positioning pin may not be provided to further reduce the weight of the differential 10, but it is not likely to affect the torque transmission of the reducer assembly 100.

[0032] Continue reading Figure 2 and combined Figure 4 The differential housing 11 has a mounting cavity 113, which encloses the differential housing 11 to form an internally hollow structure. The mounting cavity 113 is provided with two planetary gears 13 and two half-shaft gears 14. Both the planetary gears 13 and the half-shaft gears 14 are bevel gears, and the axes of the two planetary gears 13 are perpendicular to the axes of the two half-shaft gears 14.

[0033] Two planetary gears 13 are mounted on the planetary gear shaft 12 and rotatably connected to it. Optionally, the planetary gear shaft 12 has flat slots 123 corresponding to the planetary gears 13. Each planetary gear 13 may have two flat slots 123, for a total of four flat slots 123. The two flat slots 123 corresponding to each planetary gear 13 are distributed along the Y direction on both sides of the planetary gear shaft 12. The flat slots 123 are used to accommodate lubricating oil, ensuring sufficient lubrication between the planetary gears 13 and the planetary gear shaft 12. In other embodiments, the number of flat slots 123 may be increased or no flat slots 123 may be provided. The two planetary gears 13 are distributed along the axial direction of the planetary gear shaft 12, and the teeth of the two planetary gears 13 are arranged opposite each other. The side of the planetary gear 13 facing the differential housing 11 is spherical. A planetary gear washer 131 is provided between this spherical surface and the inner wall of the differential housing 11. The planetary gear washer 131 is partially spherical, with its concave surface fitting against the planetary gear 13 and its convex surface fitting against the spherical recessed inner wall of the differential housing 11. In this embodiment, one planetary gear washer 131 is provided for each planetary gear 13.

[0034] Half-shaft gears 14 mesh with planetary gears 13. Two half-shaft gears 14 are distributed along the Y-direction, and each half-shaft gear 14 meshes with two planetary gears 13. The two half-shaft gears 14 are respectively fitted onto the left and right half-shafts (not shown). The half-shaft gears 14 and half-shafts are splined together, allowing the half-shaft gears 14 and half-shafts to rotate synchronously. The half-shaft gears 14 and the left and right half-shafts can rotate relative to the differential housing 11 around the Y-axis. Half-shaft gear washers 141 are provided between the half-shaft gears 14 and the inner wall of the differential housing 11. In this embodiment, one half-shaft gear washer 141 is provided for each half-shaft gear 14, and the half-shaft gear washer 141 has a flat plate shape. In other embodiments, the half-shaft gear washer 141 can conform to the differential housing 11 and be shaped as a conical surface, etc., which, while limiting the movement of the half-shaft gears 14 by the differential housing 11, further reduces the stress between the differential housing 11 and the half-shaft gears 14.

[0035] The following is a simple description of the basic principle of differential 10.

[0036] The power output from the vehicle's drive motor or engine is first transmitted to the driven gear 20. The rotation of the driven gear 20 drives the planetary gear shaft 12, which is fixed to it, to rotate. At the same time, it drives the differential housing 11 to rotate synchronously. The power is directly transmitted from the planetary gear shaft 12 through the planetary gear 13 and the half-shaft gear 14 to the left and right half-shafts.

[0037] When the vehicle is traveling in a straight line, the resistance experienced by the left and right wheels is roughly the same. While the planetary gear 13 revolves around the Y-axis following the planetary gear shaft 12, it does not rotate relative to the planetary gear shaft 13.

[0038] When the vehicle turns, the left and right wheels travel different distances and experience different resistances. The planetary gear 13 inside the differential housing 11 rotates relative to the planetary gear shaft 13 while revolving around the Y-axis, so as to transmit more torque to the half-shaft gear 14 on the side of the wheel that has traveled a greater distance. Due to the revolution of the planetary gear 13 plus its own rotation, the left and right half-shaft gears 14 rotate at different speeds relative to the differential housing 11, thus making the vehicle turn smoothly.

[0039] The differential housing 11 is also provided with mounting holes 114, which connect to the mounting cavity 113. The size of the mounting holes 114 is configured so that the planetary gear 13 and the half-shaft gear 14 can be inserted into the mounting cavity 113 through the mounting holes 114. There can be two mounting holes 114, which are symmetrically arranged along the Z-direction of vehicle height.

[0040] Optionally, the differential housing 11 is further provided with an oil inlet 115, which connects to the mounting cavity 113. In the Y direction, the oil inlet 115 and the fixing part 112 can be distributed on the same side of the driven gear 20. There can be two oil inlets 115, which are symmetrically distributed along the X direction, for introducing lubricating oil from the outside into the interior of the differential housing 11, for example, into the flat groove 123.

[0041] The reducer assembly 100 also includes a reducer housing and a tapered bearing (not shown in the figure). The driven gear 20 is disposed inside the reducer housing. The tapered bearing is connected between the reducer housing and the differential housing 11. Specifically, there are two tapered bearings. The two tapered bearings are respectively sleeved on both ends of the differential housing 11 along the Y direction. The inner ring of the tapered bearing is connected to the differential housing 11, and the outer ring of the tapered bearing is connected to the reducer housing, so that the differential housing 11 is rotatably connected inside the reducer housing.

[0042] This application also provides a vehicle including the reducer assembly 100 of any of the above embodiments. The vehicle provided in this application can be a pure gasoline vehicle, a hybrid electric vehicle, or a pure electric vehicle, and its drive system can be a drive motor or an engine. The vehicle can also be any type of vehicle, such as a sports utility vehicle (SUV), off-road vehicle, MPV, etc. The vehicle provided in this application decouples the planetary gear shaft 12 of the differential 10 from the differential housing 11, and realizes the torque transmission between the planetary gear shaft 12 and the driven gear 20 through the receiving groove 22 and the first plane 121. The torque direction is the direction of rotation around the Y-axis. Unlike related technologies, the torque transmission route of this application is that the driven gear 20 directly transmits the torque to the planetary gear shaft 12, separating the differential housing 11 from the torque transmission route, so that the differential housing 11 does not need to bear the torque, but only needs to support the driven gear 20. Therefore, this application can eliminate the heavy connecting structure between the differential housing 11 and the driven gear 20 and reduce the number of connecting parts, thereby reducing the weight of the differential 10 and the reducer assembly 100, achieving the goal of vehicle lightweighting and improving vehicle economy.

[0043] The above are merely embodiments of this application and do not limit the scope of this patent application. Any equivalent structural or procedural changes made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the scope of patent protection of this application.

Claims

1. A reducer assembly with a differential, characterized in that, include: Driven gear, the driven gear has a central hole and a radially extending receiving groove; A differential includes a differential housing and a planetary gear shaft. The differential housing passes through the central hole and is fixedly connected to the driven gear. The differential housing is also provided with a shaft hole. The planetary gear shaft is clearance-fitted with the shaft hole and passes through the shaft hole in the differential housing. Both ends of the planetary gear shaft protrude outside the differential housing and are disposed in the receiving groove. The end of the planetary gear shaft has a first plane, which is disposed opposite to the side wall of the receiving groove. When the driven gear rotates, the side wall abuts against the first plane to drive the planetary gear shaft and the driven gear to rotate coaxially.

2. The reducer assembly with differential according to claim 1, characterized in that, The differential housing is externally connected to a fixing part, which is fixedly connected to the driven gear and the fixing part is in contact with the end face of the driven gear.

3. The reducer assembly with differential according to claim 2, characterized in that, The fixing part is provided with a through hole extending along the axial direction of the driven gear, the driven gear is provided with a threaded hole corresponding to the through hole, and the fixing part is provided with a fixing bolt, which passes through the through hole and is threadedly connected to the threaded hole.

4. The reducer assembly with differential according to claim 1, characterized in that, The receiving groove includes two opposite and parallel sidewalls; each end of the planetary gear shaft is provided with two first planes, which are arranged in parallel.

5. The reducer assembly with differential according to claim 1, characterized in that, One end of the receiving groove is connected to the central hole and forms an opening on the wall of the central hole. The other end of the receiving groove extends away from the central hole and forms a bottom wall on the driven gear. The bottom wall is disposed opposite to the end face of the planetary gear shaft and is clearance-fitted.

6. The reducer assembly with differential according to claim 1, characterized in that, The planetary gear shaft and the differential housing are respectively provided with a first positioning hole and a second positioning hole. The differential also includes a positioning pin, which is inserted into the first positioning hole and the second positioning hole.

7. The reducer assembly with differential according to claim 1, characterized in that, The differential housing has a mounting cavity, and the mounting cavity is provided with two planetary gears and two half-shaft gears; The planetary gear is sleeved on the planetary gear shaft and rotatably connected to the planetary gear shaft. The half-shaft gear meshes with the planetary gear and is rotatably connected to the differential housing.

8. The reducer assembly with differential according to claim 1, characterized in that, The reducer assembly also includes a reducer housing and a tapered bearing. The driven gear is disposed within the reducer housing, and the tapered bearing is connected between the reducer housing and the differential housing, such that the differential housing is rotatably connected within the reducer housing.

9. The reducer assembly with differential according to claim 1, characterized in that, The differential housing is made of either cast iron or stainless steel.

10. A vehicle, characterized in that, Includes a reduction gear assembly with a differential as described in any one of claims 1-9.

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