Active power-splitting differential and automobile

Abstract

An active power-splitting differential and an automobile. The active power-splitting differential comprises a differential assembly (1), an active power-splitting assembly (2), and a reverse transmission device (3). By applying the reverse speed comparison of output shafts on two sides of the differential and controlling the speed differential value obtained by comparison, power splitting of differential output is adjusted, thereby achieving active differential output of the differential. When the active power-splitting assembly (2) is not in operation, the differential is in a normal differential state, and when the active power-splitting assembly (2) is in operation, the differential is in an active power-splitting state, thereby achieving active differential output of the differential, so as to meet the requirements of active steering, anti-slip, turning radius reduction, and turning trajectory control of the automobile. When the active power-splitting differential is applied to the front and rear axles of a four-wheel-drive vehicle, zero-radius turn of the automobile can be achieved.

Description

Active split differential and automobile

[0001] Cross-reference to related applications

[0002] The present application claims priority to the Chinese patent application No. 2024109886740, filed on July 23, 2024, and entitled "Active split differential and automobile", the content of which is incorporated herein by reference in its entirety. TECHNICAL FIELD

[0003] The present application relates to the technical field of differential, more particularly, to an active split differential and automobile. BACKGROUND

[0004] Differential is an important component to ensure the driving of automobile, and plays an important role in the safe driving and direction control of automobile. With the improvement of the requirements for driving safety and steering control, the requirements for active differential control are further improved, and the progress of automatic auxiliary driving technology puts forward higher requirements for active differential control; the differential is usually composed of a planetary carrier, a planetary gear, an output gear and a half shaft, and the meshing of the planetary gear and the output gear can realize the differential function of the left and right wheel ends of the automobile, and thus the normal driving of the automobile can be realized.

[0005] However, the existing differential can only realize the differential function of the automobile, but cannot realize the active differential function of the automobile wheels, and cannot meet the requirements of the automobile in the working conditions such as anti-skid, traction control, reduction of turning radius, better tracking performance on curves and U-turn.

[0006] Therefore, it is an urgent problem for those skilled in the art to provide an active split differential and automobile. SUMMARY

[0007] Therefore, the present application provides an active split differential and automobile, which can realize the active differential output of the differential to meet the requirements of the automobile in the working conditions such as active steering, anti-skid, reduction of turning radius, turning trajectory control and U-turn.

[0008] In order to achieve the above-mentioned purpose, the present application adopts the following technical solutions:

[0009] An active split differential, comprising:

[0010] a differential assembly, the differential assembly comprising a first planetary gear assembly and a first half shaft and a second half shaft connected to two output ends of the first planetary gear assembly;

[0011] an active split assembly, the active split assembly comprising a second planetary gear assembly and a third half shaft and a fourth half shaft connected to two output ends of the second planetary gear assembly;

[0012] A reverse transmission device, comprising a reverse transmission assembly and a co-directional transmission assembly, wherein the first half-shaft and the third half-shaft located on the same side are respectively connected by the reverse transmission assembly, and the second half-shaft and the fourth half-shaft located on the same side are respectively connected by the co-directional transmission assembly.

[0013] A first power drive device and a second power drive device, wherein the first power drive device is connected to the first planetary gear assembly, and the second power drive device is connected to the second planetary gear assembly.

[0014] By adopting the above technical solutions, the beneficial effects of this application are as follows:

[0015] When the active power splitter is not working, the differential is in a differential state. When the active power splitter is working, the differential is in an active power split state, thereby realizing the active differential output of the differential to meet the needs of the vehicle in active steering, anti-skid, reducing turning radius and turning trajectory control.

[0016] Furthermore, the first planetary gear assembly includes a first driving gear, a first driven gear, a first planetary carrier, a first planetary gear, a first output gear, and a second output gear. The first driven gear meshes with the first driving gear for transmission. The driving gear on the output shaft of the first power drive device meshes with the first input driven gear for transmission. The first input driven gear shares the same axis of rotation with the first driving gear and is connected as a single unit. The first driven gear is bolted to the first planetary carrier. Multiple first planetary gears are mounted on the first planetary carrier via a first planetary gear shaft and rotate around the first planetary gear shaft. The first output gear is mounted on the first half-shaft along the same axis of rotation and connected by a spline. The second output gear is mounted on the second half-shaft along the same axis of rotation and connected by a spline. The first output gear and the second output gear mesh with the first planetary gear for transmission.

[0017] Further, the second planetary gear assembly comprises a second driving gear, a second driven gear, a second planetary carrier shell, a second planetary gear, a third output gear and a fourth output gear, the second driven gear is in meshing transmission connection with the second driving gear, the driving driving gear on the second power driving device output shaft is in meshing transmission connection with the second input driven gear, the second input driven gear is in the same rotation axis with the second driving gear and is connected as a whole; the second driven gear is fixed on the second planetary carrier shell by bolts; a plurality of the second planetary gears are installed on the second planetary carrier shell through the second planetary gear shaft and rotate around the second planetary gear shaft; the third output gear is installed on the same rotation axis of the third half shaft and is connected through the spline, the fourth output gear is installed on the same rotation axis of the fourth half shaft and is connected through the spline; the third output gear and the fourth output gear are respectively in meshing transmission with the second planetary gear.

[0018] Further, the reverse transmission assembly comprises a first reverse transmission gear and a second reverse transmission gear, the first reverse transmission gear is installed on the journal of the first planetary carrier shell and is connected with the outer spline of the first half shaft through the inner spline of the first fixed plate, and the rotation axis of the first reverse transmission gear coincides with the rotation axis of the first half shaft, the second reverse transmission gear is installed on the journal of the second planetary carrier shell and is connected with the outer spline of the third half shaft through the inner spline of the second fixed plate, and the rotation axis of the second reverse transmission gear coincides with the rotation axis of the third half shaft, the first reverse transmission gear is in meshing transmission with the second reverse transmission gear and has the same outer diameter and tooth number; the first fixed plate is fixedly connected with the first reverse transmission gear through bolts, the second fixed plate is fixedly connected with the second reverse transmission gear through bolts, the second fixed plate inner spline hole is provided with a snap spring slot, a snap spring is installed in the snap spring slot, and the axial movement of the third half shaft is limited.

[0019] Further, the same direction transmission assembly comprises a first same direction transmission gear, a second same direction transmission gear, an intermediate shaft and an intermediate gear, the first same direction transmission gear is installed on the shaft journal of the first planetary carrier shell and connected with the outer spline of the second half shaft through the inner spline of the third fixed plate, and the rotation axis of the first same direction transmission gear coincides with the rotation axis of the second half shaft; the second same direction transmission gear is installed on the shaft journal of the second planetary carrier shell and connected with the outer spline of the fourth half shaft through the inner spline of the fourth fixed plate, and the rotation axis of the second same direction transmission gear coincides with the rotation axis of the fourth half shaft; the third fixed plate is fixedly connected with the first same direction transmission gear through bolts, the fourth fixed plate is fixedly connected with the second same direction transmission gear through bolts, the inner spline hole of the fourth fixed plate is provided with a snap spring groove, and a snap spring is installed in the snap spring groove to limit the axial movement of the fourth half shaft; the intermediate shaft is rotatably installed on the automobile body through a bearing seat, the intermediate shaft is located between the second half shaft and the fourth half shaft, and the intermediate shaft, the second half shaft and the fourth half shaft are parallel and arranged in a triangular shape; the intermediate gear is rotatably installed on the intermediate shaft and positioned by a snap spring; the first same direction transmission gear and the second same direction transmission gear have the same outer diameter and the same number of teeth and are respectively meshed with the intermediate gear.

[0020] Further, the first fixed plate is connected with the first half shaft through spline, the second fixed plate is connected with the third half shaft through spline, the third fixed plate is connected with the second half shaft through spline, and the fourth fixed plate is connected with the fourth half shaft through spline.

[0021] Further, the shaft journal of the intermediate shaft, the right shaft journal of the first planetary carrier shell and the right shaft journal of the second planetary carrier shell are connected together through a first bearing seat provided with two mounting semicircular holes and one shaft hole, the shaft journal of the intermediate shaft, the left shaft journal of the first planetary carrier shell and the left shaft journal of the second planetary carrier shell are connected together through a second bearing seat provided with two mounting semicircular holes and one shaft hole; the first input driven gear and the first driving gear which are integrated, and the second input driven gear and the second driving gear which are integrated, are installed on the intermediate shaft and arranged on the same rotation axis and between the two bearing seats.

[0022] Further, the length of the right shaft journal of the first planetary carrier shell is greater than the sum of the mounting hole width of the first bearing seat and the width of the first same direction transmission gear; the length of the right shaft journal of the second planetary carrier shell is greater than the sum of the mounting hole width of the first bearing seat and the width of the second same direction transmission gear; the length of the left shaft journal of the first planetary carrier shell is greater than the sum of the mounting hole width of the second bearing seat and the width of the first reverse transmission gear; and the length of the left shaft journal of the second planetary carrier shell is greater than the sum of the mounting hole width of the second bearing seat and the width of the second reverse transmission gear.

[0023] Further, a snap spring groove is formed between the two sides of the first reverse transmission gear and the journal of the first planetary carrier shell, between the second reverse transmission gear and the journal of the second planetary carrier shell, between the two sides of the first same direction transmission gear and the journal of the first planetary carrier shell, and between the two sides of the second same direction transmission gear and the journal of the second planetary carrier shell, and a snap spring is installed in the snap spring groove; the first input driven gear and the first driving gear are integrated, and the second input driven gear and the second driving gear are integrated, and a snap spring groove is formed in the middle shaft on which the first input driven gear and the first driving gear are installed and on which the second input driven gear and the second driving gear are installed, and a snap spring is installed in the snap spring groove.

[0024] An automobile comprises the active split-flow differential mentioned above.

[0025] By adopting the above technical scheme, the application has the following beneficial effects:

[0026] The automobile can realize the function of active differential while realizing the function of normal differential driving, and the off-road performance, the trajectory adjustment of the vehicle body, the steering performance, the passing ability and the fuel economy of the automobile are improved.

[0027] According to the technical solution, the application provides an active split differential and a vehicle. Compared with the prior art, under the action of driving force, the first planetary gear assembly of the differential assembly drives the first half shaft and the second half shaft of the vehicle to realize the function of normal differential driving of the vehicle. The first half shaft drives the third half shaft of the active split assembly to rotate reversely at the same speed through the reverse transmission assembly, and the second half shaft drives the fourth half shaft to rotate in the same direction at the same speed through the same direction transmission assembly. In this way, when the vehicle travels in a straight line, the first output gear and the second output gear of the differential assembly rotate in the same direction at the same speed, the third output gear and the fourth output gear of the active split assembly rotate reversely at the same speed through the driving of the reverse transmission assembly, at this time, the second planetary gear of the active split assembly only rotates around its own axis without revolving around the sun gear, the planetary gear is connected to the planet carrier shell through the planetary gear shaft, the revolving speed of the planetary gear is the rotating speed of the planet carrier shell, the rotating speed of the second planet carrier shell is zero, and the active split assembly is in a zero motion state. When the vehicle turns, the first output gear and the second output gear of the differential assembly rotate in the same direction at different speeds, the third output gear and the fourth output gear of the active split assembly rotate reversely at different speeds through the driving of the reverse transmission assembly, at this time, the second planetary gear of the active split assembly rotates around its own axis and revolves around the sun gear, the planetary gear is connected to the planet carrier shell through the planetary gear shaft, the revolving speed of the planetary gear is the rotating speed of the planet carrier shell, the rotating speed of the second planet carrier shell is not zero, and the active split assembly is in a follow-up state. The rotating speed of the second planet carrier shell is the difference between the rotating speeds of the first output gear and the second output gear of the differential assembly, and the rotating speed of the second planet carrier shell is positively correlated with the turning direction and the turning angle of the vehicle. The greater the turning angle of the vehicle, the greater the rotating speed of the second planet carrier shell.

[0028] On this basis, when the active split differential is used for front and rear drive of a four-wheel drive vehicle, or for single front drive or single rear drive, the rotating speed of the second planet carrier shell is zero when the vehicle travels in a straight line, and the active split assembly is in a zero motion state, thereby reducing the resistance and drag torque of the vehicle and improving the fuel economy of the vehicle. The active split differential does not use a mechanical or hydraulic friction plate clutch as an execution element to operate and control, thereby reducing the manufacturing and maintenance costs of the vehicle and improving the economy and service life of the vehicle. When the vehicle wheels are trapped, slip or in a state of adjusting the movement track of the vehicle body, or the vehicle is in a state of small turning radius or parking difficulty, the active split differential can be in an active differential state. At this time, the active split assembly drives the rotating speeds of the first half shaft and the second half shaft to be in an active differential state through the reverse transmission assembly. In this way, on the one hand, the ability of the vehicle to escape or adjust the movement track of the vehicle body is improved, and on the other hand, a special rear wheel deflection mechanism is avoided to solve the problem of small turning radius or parking difficulty of the vehicle.

[0029] When the active split differential is used for front and rear drive of the automobile, the driving of the differential assembly is in the non-working state or in the working state, and under the driving of the active split assembly, the third half shaft and the fourth half shaft are in the mutual same speed rotating state, the first half shaft and the second half shaft are driven by the reverse transmission assembly to be in the mutual active differential or even the mutual reverse rotating state, so as to realize the function of the automobile turning around at the original place, thus improving the steering and passing capacity of the automobile; the steering direction and the steering angle of the automobile are positively correlated with the speed difference (i.e. the second planetary carrier shell) at the same time, which also lays a structural foundation for the intelligent differential and the line-controlled chassis, and the steering function of the automobile can be realized through four-wheel active differential control. On the one hand, the risk of limping caused by single drive failure of the distributed four-wheel electric drive is avoided, and on the other hand, the high cost and complex electro-hydraulic control device of the mechanical four-wheel drive vehicle and the high cost and complex differential mechanical control of the front and rear axle connection mechanical transmission shaft are also avoided. BRIEF DESCRIPTION OF DRAWINGS

[0030] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed to be used in the embodiments or the prior art description will be briefly introduced. Obviously, the drawings in the following description are only a part of the embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor on the basis of the provided drawings.

[0031] Fig. 1 is a schematic diagram of the overall structure of an active split differential provided by the present application;

[0032] Fig. 2 is an exploded view of an active split differential provided by the present application;

[0033] Fig. 3 is a schematic diagram of the working principle of an active split differential provided by the present application. DETAILED DESCRIPTION

[0034] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the present application.

[0035] As shown in FIGS. 1-3, the embodiment of the present application discloses an active split differential, which comprises a differential assembly 1, an active split assembly 2, a reverse transmission device 3, and a first power driving device and a second power driving device. The differential assembly 1 comprises a first planetary gear assembly 11 and a first half shaft 12 and a second half shaft 13 connected to the two output ends of the first planetary gear assembly 11. The active split assembly 2 comprises a second planetary gear assembly 21 and a third half shaft 22 and a fourth half shaft 23 connected to the two output ends of the second planetary gear assembly 21. The reverse transmission device 3 comprises a reverse transmission assembly 31 and a same direction transmission assembly 32. The first half shaft 12 and the third half shaft 22 located on the same side are drivingly connected through the reverse transmission assembly 31. The second half shaft 13 and the fourth half shaft 23 located on the same side are drivingly connected through the same direction transmission assembly 32. The first power driving device is drivingly connected with the first planetary gear assembly 11, and the second power driving device is drivingly connected with the second planetary gear assembly 21. In the embodiment, the first power driving device is a motor or an engine, and the second power driving device is a motor. When the active split assembly 2 does not work, the differential is in a differential state. When the active split assembly 2 works, the differential is in an active power split state, so as to realize the active differential output of the differential, so as to meet the requirements of active steering, anti-skid, reducing the turning radius and turning trajectory control of the automobile.

[0036] Specifically, the first planetary gear assembly 11 comprises a first driving gear 111, a first driven gear 112, a first planetary carrier shell 113, a plurality of first planetary gears 114, a first output gear 115 and a second output gear 116. The first driven gear 112 is drivingly connected with the first driving gear 111. The driving driving gear on the output shaft of the first power driving device is drivingly connected with a first input driven gear 118. The first input driven gear 118 is connected with the first driving gear 111 on the same rotation axis and is integrated, so as to realize two-stage speed reduction transmission, avoid the use of a large gear, and avoid interference with the active split assembly. At the same time, the volume is reduced, the weight is reduced, and the cost is reduced. The first driven gear 112 is fixed on the first planetary carrier shell 113. The plurality of first planetary gears 114 are installed on the first planetary carrier shell 113 through a first planetary gear shaft 117 and rotate around the first planetary gear shaft 117. The first output gear 115 is installed on the first half shaft 12 on the same rotation axis and is connected through a spline. The second output gear 116 is installed on the second half shaft 13 on the same rotation axis and is connected through a spline. The first output gear 115 and the second output gear 116 are respectively drivingly connected with the first planetary gears 114. In work, under the driving of the first power driving device, the first half shaft 12 and the second half shaft 13 of the automobile are driven by the first planetary gear assembly 11. The first half shaft 12 and the second half shaft 13 are connected with the wheels (front wheels or rear wheels) of the automobile at the outer ends, so as to realize the normal differential driving function of the automobile.

[0037] Specifically, the second planetary gear assembly 21 includes a second driving gear 211, a second driven gear 212, a second planetary carrier housing 213, a second planetary gear 214, a third output gear 215, and a fourth output gear 216. The second driven gear 212 is meshed with the second driving gear 211 for transmission. The driving gear on the output shaft of the second power drive device is meshed with the second input driven gear 218 for transmission. The second input driven gear 218 is connected to the second driving gear 211 as a single unit, thereby achieving a two-stage reduction transmission. This avoids the use of large gears and reduces the overall size. While increasing volume, the weight is reduced and the cost is decreased; the second driven gear 212 is fixed on the second planetary carrier housing 213; multiple second planetary gears 214 are mounted on the second planetary carrier housing 213 via the second planetary gear shaft 217 and rotate around the second planetary gear shaft 217; the third output gear 215 is mounted on the third half-shaft 22 on the same axis of rotation and connected by a spline, and the fourth output gear 216 is mounted on the fourth half-shaft 23 on the same axis of rotation and connected by a spline; the third output gear 215 and the fourth output gear 216 are respectively meshed with the second planetary gears 214 for transmission.

[0038] It should be noted that the second planetary gear assembly 21 includes, but is not limited to, the above structure. It can also be other similar planetary gear mechanism assemblies that realize differential function, such as spur gear planetary gear differential mechanism, stepped planetary gear differential mechanism, etc., which can realize differential function and are all within the protection scope of this application.

[0039] Specifically, the reverse transmission assembly 31 includes a first reverse transmission gear 311 and a second reverse transmission gear 312. The first reverse transmission gear 311 is mounted on the journal of the first planetary carrier housing 113 and connected to the external spline on the first half-shaft 12 via an internal spline on the first fixed plate. The rotation axis of the first reverse transmission gear 311 coincides with the rotation axis of the first half-shaft 12. The second reverse transmission gear 312 is mounted on the journal of the second planetary carrier housing 213 and connected to the external spline on the third half-shaft 22 via an internal spline on the second fixed plate. The rotation axis of the second reverse transmission gear 312 coincides with the rotation axis of the first half-shaft 12. The rotation axes of the three half-shafts 22 coincide. The first reverse transmission gear 311 and the second reverse transmission gear 312 mesh and transmit power, and have the same outer diameter and number of teeth. Thus, when the first reverse transmission gear 311 and the second reverse transmission gear 312 mesh and transmit power, the first half-shaft 12 and the third half-shaft 22 rotate in opposite directions at the same speed. The first fixed plate is fixedly connected to the first reverse transmission gear 311 by bolts, and the second fixed plate is fixedly connected to the second reverse transmission gear 312 by bolts. A snap ring groove is opened in the spline hole of the second fixed plate, and a snap ring is installed in the snap ring groove to restrict the axial movement of the third half-shaft 22. The above is only one type of reverse transmission; other reverse transmission types are also included within the scope of the principle of this application.

[0040] Specifically, the co-rotating transmission assembly 32 includes a first co-rotating transmission gear 321, a second co-rotating transmission gear 322, an intermediate shaft 323, and an intermediate gear 324. The first co-rotating transmission gear 321 is mounted on the journal of the first planetary carrier housing 113 and connected to the external spline of the second half-shaft 13 via the internal spline of the third fixing plate, and the rotation axis of the first co-rotating transmission gear 321 coincides with the rotation axis of the second half-shaft 13. The second co-rotating transmission gear 322 is mounted on the journal of the second planetary carrier housing 213 and connected to the external spline of the fourth half-shaft 23 via the internal spline of the fourth fixing plate, and the rotation axis of the second co-rotating transmission gear 322 coincides with the rotation axis of the fourth half-shaft 23. The third fixing plate is fixedly connected to the first co-rotating transmission gear 321 by bolts, and the fourth fixing plate is fixedly connected to the second co-rotating transmission gear 322 by bolts. A retaining ring groove is provided in the spline hole of the fixed plate, and a retaining ring is installed in the retaining ring groove to restrict the axial movement of the fourth half-shaft 23. The intermediate shaft 323 is rotatably mounted on the vehicle body through the two bearing seats. The intermediate shaft 323 is located between the second half-shaft 13 and the fourth half-shaft 23, and the intermediate shaft 323, the second half-shaft 13, and the fourth half-shaft 23 are parallel and arranged in a triangular pattern. The intermediate gear 324 is mounted on the intermediate shaft 323. The first co-rotating transmission gear 321 and the second co-rotating transmission gear 322 have the same outer diameter and number of teeth and mesh with the intermediate gear 324 respectively. In this way, the second half-shaft 13 and the fourth half-shaft 23 rotate at the same speed and in the same direction. The mechanism including the intermediate shaft 323 is beneficial to the two-stage reduction arrangement of power transmission, avoids the design of a large transmission gear in a single-stage reduction, reduces the weight of the active splitter differential, and is conducive to the lightweight design of the vehicle. The above is only one type of co-rotating transmission, and other co-rotating transmission types are also included within the scope of the principle of this application.

[0041] Specifically, the first fixing plate and the first half-shaft 12, the second fixing plate and the third half-shaft 22, the third fixing plate and the second half-shaft 13, and the fourth fixing plate and the fourth half-shaft 23 are all connected by splines.

[0042] Specifically, the journal of the intermediate shaft 323, the right journal of the first planetary carrier housing 113, and the right journal of the second planetary carrier housing 213 are connected together by a first bearing seat 4 with two mounting semicircular holes and one shaft hole. The journal of the intermediate shaft 323, the left journal of the first planetary carrier housing 113, and the left journal of the second planetary carrier housing 213 are connected together by a second bearing seat 5 with two mounting semicircular holes and one shaft hole. Both the first bearing seat 4 and the second bearing seat 5 are fixedly connected to the vehicle body by bolts, which simplifies the installation and improves the quietness of the vehicle. The first input driven gear 118 and the first driving gear 111, which are integrated as one unit, and the second input driven gear 218 and the second driving gear 211, which are integrated as one unit, are mounted on the intermediate shaft 232 and are on the same axis of rotation and arranged between the two bearing seats.

[0043] Specifically, the length of the right journal of the first planetary carrier housing 113 is greater than the sum of the width of the mounting hole of the first bearing housing 4 and the width of the first co-directional transmission gear 321; the length of the right journal of the second planetary carrier housing 213 is greater than the sum of the width of the mounting hole of the first bearing housing 4 and the width of the second co-directional transmission gear 322; the length of the left journal of the first planetary carrier housing 113 is greater than the sum of the width of the mounting hole of the second bearing housing 5 and the width of the first reverse transmission gear 311; and the length of the left journal of the second planetary carrier housing 213 is greater than the sum of the width of the mounting hole of the second bearing housing 5 and the width of the second reverse transmission gear 312.

[0044] Specifically, snap ring grooves are provided on both sides of the first reverse transmission gear 311 between the journals of the first planetary carrier housing 113, between the second reverse transmission gear 312 and the journals of the second planetary carrier housing 213, between both sides of the first co-directional transmission gear 321 and the journals of the first planetary carrier housing 113, and between both sides of the second co-directional transmission gear 322 and the journals of the second planetary carrier housing 213, and snap rings are installed in each snap ring groove; the first input driven gear 118 and the first driving gear 111, which are connected as one unit, and the second input driven gear 218 and the second driving gear 211, which are connected as one unit, have snap ring grooves on both sides of the intermediate shaft 323 on which they are mounted, and snap rings are installed in each snap ring groove.

[0045] This application also discloses a vehicle including the active differential described above. This application, while enabling normal differential driving, also achieves active differential functionality, improving the vehicle's ability to get out of trouble, adjust its vehicle trajectory, steering and maneuverability, and fuel economy.

[0046] The specific working status of this application is as follows:

[0047] When a normal differential command is received, the external driving force drives the first planetary carrier housing 113 and its first planetary gear 114 to revolve via the first driven gear 112. Under the action of the first output gear 115 and the second output gear 116, the first planetary gear 114 rotates on its own axis, thereby driving the first half-shaft 12 and the second half-shaft 13 of the vehicle, achieving the normal differential driving function of the vehicle. It can be understood that the differential command can be an automatically triggered command based on vehicle driving information (including vehicle speed, direction, acceleration, etc.) confirming that the vehicle is in a normal driving state.

[0048] When the active splitter assembly 2 is not in operation, the first planetary gear 114 is driven to rotate by the differential assembly 1 under the action of external driving force, thereby realizing the normal differential driving function of the car. At this time, the active splitter assembly 2 is in a zero-movement or follow-up state under the drive of the reverse transmission device 3, achieving the purpose of splitting and differential being related yet independent, extending the service life of the active splitter transmission, and taking advantage of the existing differential structure and manufacturing advantages, with mature parts and low production and manufacturing costs.

[0049] The first half-shaft 12, connected to the differential assembly 1, drives the third half-shaft 22, connected to the active splitter assembly 2, to rotate in the opposite direction via the reverse transmission assembly 31; the second half-shaft 13, connected to the differential assembly 1, drives the fourth half-shaft 23, connected to the active splitter assembly 2, to rotate in the same direction via the same transmission assembly 32; thus, when the car is traveling straight, the third output gear 215 and the fourth output gear 216 of the active splitter assembly 2 rotate in the opposite direction at the same speed. At this time, the second planetary gear 214 of the active splitter assembly 2 only rotates on its own axis and does not revolve around the sun. Understandably, the second planetary gear shaft 217 inside the central hole of the second planetary gear 214 in the active flow splitter assembly 2 rotates at zero speed because it does not revolve. The second planetary carrier housing 213 connected to the second planetary gear shaft 217 also rotates at zero speed, remaining in a zero-motion state. When the vehicle turns or engages differential, the third output gear 215 and the fourth output gear 216 rotate in opposite directions at differential speeds. At this time, the second planetary gear 214 both rotates on its own axis and revolves around the central axis, while the second planetary carrier housing 213, driven by the revolving second planetary gear shaft 217, rotates at a non-zero speed, remaining in a follower state. Therefore, this active flow splitter differential reduces the vehicle's drag and trailing torque, improving fuel economy.

[0050] When the vehicle wheels are stuck, slipping, or the vehicle's trajectory is being adjusted, the active differential can be put into active differential mode. At this time, the active shunt assembly 2, through the reverse transmission device 3, causes the rotational speed of the first half-shaft 12 and the second half-shaft 13 of the differential assembly 1 to be in active differential mode. This improves the vehicle's ability to get out of trouble and adjust its trajectory, gives the vehicle better tracking in curves, and improves the vehicle's steering ability. At the same time, active centralized differential control is more conducive to the realization of precise controllable differential and automatic driver assistance technology.

[0051] When the active split differential is used in the front and rear drive of a car, the differential component 1 is either in a non-working state or in a working state. Driven by the active split component 2, it drives the first half-shaft 12 and the second half-shaft 13 to be in a mutually reversible state, thereby realizing the function of turning the car in place. This improves the car's steering and passability, and also lays the structural foundation for intelligent differential and drive-by-wire chassis.

[0052] The following example illustrates the power transmission relationship between differential component 1 and active splitter component 2:

[0053] Let N, T, and P represent the speed, torque, and power of differential assembly 1, and NDIF, TDIF, and PDIF represent the speed, torque, and power of active splitter assembly 2; let N1OUT, T1OUT, and P1OUT represent the speed, torque, and power of the first half-shaft 12, and N2OUT, T2OUT, and P2OUT represent the speed, torque, and power of the second half-shaft 13; assume that the torque directions of differential assembly 1 and active splitter assembly 2 are consistent:

[0054] When the active differential is in normal differential mode: 2N = N1OUT + N2OUT; T = T1OUT + T2OUT; P = P1OUT + P2OUT;

[0055] When the active split differential is in active split mode: 2N = N1OUT + N2OUT; T = T1OUT + T2OUT; P = P1OUT + P2OUT; 2NDIF = N2OUT - N1OUT; TDIF = T2OUT - T1OUT; PDIF = P2OUT - P1OUT.

[0056] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to the method section.

[0057] The above description of the disclosed embodiments enables those skilled in the art to make or use this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. An active split differential characterized in that, The differential assembly comprises a first planetary gear assembly, a first half shaft and a second half shaft connected to the two output ends of the first planetary gear assembly; The active split assembly comprises a second planetary gear assembly, a third half shaft and a fourth half shaft connected to the two output ends of the second planetary gear assembly; The reverse transmission device comprises a reverse transmission assembly and a same-direction transmission assembly, the first half shaft and the third half shaft on the same side are drivingly connected through the reverse transmission assembly, and the second half shaft and the fourth half shaft on the same side are drivingly connected through the same-direction transmission assembly; The first power driving device is drivingly connected with the first planetary gear assembly, and the second power driving device is drivingly connected with the second planetary gear assembly. The first planetary gear assembly comprises a first driving gear, a first driven gear, a first planetary carrier shell, a first planetary gear, a first output gear and a second output gear, the first driven gear is drivingly connected with the first driving gear, a driving driving gear on an output shaft of the first power driving device is drivingly connected with a first input driven gear, the first input driven gear is connected with the first driving gear on the same rotation axis and is integrated, the first driven gear is fixed on the first planetary carrier shell by bolts, a plurality of the first planetary gears are installed on the first planetary carrier shell and rotate around the first planetary gear shaft, the first output gear is installed on the first half shaft on the same rotation axis and is connected through a spline, the second output gear is installed on the second half shaft on the same rotation axis and is connected through a spline, and the first output gear and the second output gear are respectively drivingly connected with the first planetary gear.

2. An active split differential according to claim 1, wherein, The second planetary gear assembly comprises a second driving gear, a second driven gear, a second planetary carrier shell, a second planetary gear, a third output gear and a fourth output gear, the second driven gear is drivingly connected with the second driving gear, a driving driving gear on an output shaft of the second power driving device is drivingly connected with a second input driven gear, the second input driven gear is connected with the second driving gear on the same rotation axis and is integrated, the second driven gear is fixed on the second planetary carrier shell by bolts, a plurality of the second planetary gears are installed on the second planetary carrier shell and rotate around the second planetary gear shaft, the third output gear is installed on the third half shaft on the same rotation axis and is connected through a spline, the fourth output gear is installed on the fourth half shaft on the same rotation axis and is connected through a spline, and the third output gear and the fourth output gear are respectively drivingly connected with the second planetary gear.

3. An active split differential according to claim 2, wherein, ​ 4. An active split differential according to claim 3, wherein, The reverse transmission assembly comprises a first reverse transmission gear and a second reverse transmission gear, the first reverse transmission gear is mounted on the journal of the first planetary carrier shell and connected with the outer spline of the first half shaft through the inner spline of the first fixed plate, and the rotation axis of the first reverse transmission gear coincides with the rotation axis of the first half shaft, the second reverse transmission gear is mounted on the journal of the second planetary carrier shell and connected with the outer spline of the third half shaft through the inner spline of the second fixed plate, and the rotation axis of the second reverse transmission gear coincides with the rotation axis of the third half shaft, the first reverse transmission gear and the second reverse transmission gear are in meshing transmission and have the same outer diameter and the same number of teeth; the first fixed plate is fixedly connected with the first reverse transmission gear through bolts, the second fixed plate is fixedly connected with the second reverse transmission gear through bolts, the inner spline hole of the second fixed plate is provided with a snap spring groove, and a snap spring is mounted in the snap spring groove to limit the axial movement of the third half shaft.

5. An active split differential according to claim 4, wherein, The same direction transmission assembly comprises a first same direction transmission gear, a second same direction transmission gear, an intermediate shaft and an intermediate gear, the first same direction transmission gear is mounted on the journal of the first planetary carrier shell and connected with the outer spline of the second half shaft through the inner spline of the third fixed plate, and the rotation axis of the first same direction transmission gear coincides with the rotation axis of the second half shaft; The second same direction transmission gear is mounted on the journal of the second planetary carrier shell and connected with the outer spline of the fourth half shaft through the inner spline of the fourth fixed plate, and the rotation axis of the second same direction transmission gear coincides with the rotation axis of the fourth half shaft; the third fixed plate is fixedly connected with the first same direction transmission gear through bolts, the fourth fixed plate is fixedly connected with the second same direction transmission gear through bolts, the inner spline hole of the fourth fixed plate is provided with a snap spring groove, and a snap spring is mounted in the snap spring groove to limit the axial movement of the fourth half shaft; the intermediate shaft is rotatably mounted on the automobile body through a bearing seat, the intermediate shaft is located between the second half shaft and the fourth half shaft, and the intermediate shaft, the second half shaft and the fourth half shaft are parallel and arranged in a triangular shape; the intermediate gear is rotatably mounted on the intermediate shaft and positioned by a snap spring; the first same direction transmission gear and the second same direction transmission gear have the same outer diameter and the same number of teeth and are respectively in meshing transmission with the intermediate gear.

6. An active split differential according to claim 5, wherein, The first fixed plate is spline-connected with the first half shaft, the second fixed plate is spline-connected with the third half shaft, the third fixed plate is spline-connected with the second half shaft, and the fourth fixed plate is spline-connected with the fourth half shaft.

7. An active split differential according to claim 6, wherein, The shaft journal of the intermediate shaft, the right shaft journal of the first planetary carrier shell and the right shaft journal of the second planetary carrier shell are connected together by the first bearing seat with two mounting semicircular holes and one shaft hole; the shaft journal of the intermediate shaft, the left shaft journal of the first planetary carrier shell and the left shaft journal of the second planetary carrier shell are connected together by the second bearing seat with two mounting semicircular holes and one shaft hole; the first input driven gear and the first driving gear connected as a whole, and the second input driven gear and the second driving gear connected as a whole, are installed on the intermediate shaft and have the same rotation axis and are arranged between the two bearing seats.

8. An active split differential according to claim 7, wherein, The length of the right shaft journal of the first planetary carrier shell is greater than the sum of the mounting hole width of the first bearing seat and the width of the first same-direction transmission gear; the length of the right shaft journal of the second planetary carrier shell is greater than the sum of the mounting hole width of the first bearing seat and the width of the second same-direction transmission gear; the length of the left shaft journal of the first planetary carrier shell is greater than the sum of the mounting hole width of the second bearing seat and the width of the first reverse transmission gear; the length of the left shaft journal of the second planetary carrier shell is greater than the sum of the mounting hole width of the second bearing seat and the width of the second reverse transmission gear.

9. An active split differential according to claim 8, wherein, Spring clips are installed in the spring clip grooves between the two sides of the first reverse transmission gear and the shaft journals of the first planetary carrier shell, between the second reverse transmission gear and the shaft journals of the second planetary carrier shell, between the two sides of the first same-direction transmission gear and the shaft journals of the first planetary carrier shell, and between the two sides of the second same-direction transmission gear and the shaft journals of the second planetary carrier shell; spring clips are also installed in the spring clip grooves on the intermediate shaft on which the first input driven gear and the first driving gear connected as a whole, and the second input driven gear and the second driving gear connected as a whole, are installed.

10. An automobile characterized by comprising: A driving split differential including any one of claims 1-9.

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