Differential assembly and vehicle

Abstract

The invention provides a differential mechanism assembly. The differential mechanism assembly comprises a differential mechanism shell, a transmission clutch assembly arranged on the right side of the differential mechanism shell and a differential clutch assembly arranged on the left side of the differential mechanism shell. The state of the differential mechanism assembly can be switched by controlling the states of the transmission electromagnetic actuator and the differential electromagnetic actuator, so that the differential mechanism assembly is switched among a differential state, a power disconnection state and a differential locking state according to needs, the phenomenon of power reverse dragging during high-speed running of a vehicle is avoided, and the service life of the vehicle is prolonged. The escape capability of the vehicle when the vehicle runs on an uneven road surface is improved; besides, in the differential locking state, the power transmission route of the differential assembly is optimized, it is guaranteed that power of a differential shell can only be transmitted to a left half axle gear through a planetary gear sleeve and a differential clutch ring in sequence, the stress uniformity of the planetary gear sleeve and the differential clutch ring is effectively guaranteed, and the service life of the differential assembly is prolonged. Torsional deformation caused by uneven stress of the planetary gear sleeve and the differential clutch ring is avoided, and the service life of the planetary gear sleeve and the differential clutch ring is prolonged.

Description

Technical Field

[0001] The invention belongs to the field of automobile transmission, and in particular relates to a differential assembly and a vehicle. Background Art

[0002] The differential assembly is an important part of the car. When the car turns, it can adjust the left and right wheels to roll at different speeds to ensure the smooth operation of the car. However, the current differential assembly has limited functions and cannot meet customer requirements. For example, when the car is driving at high speed, since the power source is still connected to the differential assembly, power back-drag will occur, increasing energy consumption. For another example, when the car is driving on muddy roads or icy roads, the differential assembly adaptively adjusts the speed of the wheels on both sides, so one side of the wheel will not move on the bad road, while the other side of the wheel will slip on the good road, resulting in the problem that the car is restricted and cannot drive.

[0003] In order to solve the above technical problems, the invention patent with application number 202211387362.1 discloses a differential assembly with disconnection and locking functions, in which a differential clutch assembly and a transmission clutch assembly are respectively arranged on the left and right sides of the differential housing, and the power transmission and disconnection between the planetary gear carrier and the differential housing are realized through the transmission clutch assembly, and the power transmission and disconnection between the left half-shaft gear and the differential housing are realized through the differential clutch assembly; however, when the differential assembly needs to work in the differential locking mode, since the transmission clutch assembly and the differential clutch assembly are both in a power connection state, the torque of the differential housing will be transmitted to the planetary gear carrier through two different paths. Gear carrier, wherein the first transmission path is: the torque of the differential case can be transmitted to the right side of the planetary gear carrier through the transmission clutch assembly; the second transmission path is: the torque of the differential case is transmitted to the left half-shaft gear through the differential clutch assembly, and then transmitted to the planetary gear carrier; since there are transmission losses (such as friction losses) in both transmission paths, and it is difficult to ensure the consistency of the transmission losses of the two, the two positions of the planetary gear carrier (i.e., the right end and the gear shaft position) are subjected to two torques of the same direction but different magnitudes. This unbalanced torque distribution can easily cause the planetary gear carrier to torsional deformation, which not only reduces the service life of the planetary gear carrier, but also affects the normal operation of the differential assembly. Summary of the invention

[0004] In view of the above shortcomings of the prior art, the purpose of the present invention is to provide a differential assembly and a vehicle, which have the functions of power disconnection, differential and differential locking, and ensure that the power of the differential case can only be transmitted to the left half-shaft gear through the planetary gear sleeve under the differential locking function, so as to solve the problem in the prior art that different cross sections of the planetary gear sleeve are prone to torsional deformation when they are respectively subjected to the power transmitted from the differential case and the left half-shaft, thereby improving the service life of the planetary gear sleeve.

[0005] To achieve the above-mentioned purpose and other related purposes, the differential assembly provided by the present invention includes a differential case, a ring gear driving the differential case to rotate, a transmission clutch assembly arranged on the right side of the differential case, and a differential clutch assembly arranged on the left side of the differential case; the differential case is provided with a planetary gear sleeve, planetary gears, and left and right half-shaft gears meshing with the planetary gears; the planetary gears are installed in the planetary gear sleeve through the planetary gear shaft; the transmission clutch assembly includes a transmission electromagnetic actuator, a first return spring, and a transmission clutch ring; the transmission clutch ring is fixed to the circumferential direction of the differential case The first reset spring drives the transmission clutch ring to move axially in the direction away from the planetary gear sleeve, and finally disconnects from the planetary gear sleeve; the differential clutch assembly includes a differential electromagnetic actuator, a second reset spring and a differential clutch ring; the differential clutch ring is circumferentially fixed to the planetary gear sleeve and can move axially relative to the planetary gear sleeve; the second ... ring is circumferentially fixed to the planetary gear sleeve and can move axially relative to the planetary gear sleeve; the second reset spring drives the transmission clutch ring to move axially in the direction away from the planetary gear sleeve, and finally disconnects from the planetary gear sleeve; the differential clutch ring is circumferentially fixed to the planetary gear sleeve and can move axially relative to the planetary gear sleeve; the second reset spring drives the transmission clutch ring to move axially in the direction away from the planetary gear sleeve The spring is located between the differential clutch ring and the left half-shaft gear; when the differential electromagnetic actuator is energized, the differential electromagnetic actuator drives the differential clutch ring to move axially toward the left half-shaft gear, and finally forms a circumferential fixation with the left half-shaft gear; when the differential electromagnetic actuator is de-energized, the second return spring drives the differential clutch ring to move axially away from the left half-shaft gear, and finally disconnects from the left half-shaft gear; when the transmission electromagnetic actuator is energized and the differential electromagnetic actuator is de-energized, the power of the differential housing is transmitted to the planetary gear sleeve, so that the differential assembly has a differential function; when the transmission electromagnetic actuator is de-energized, the differential housing is de-energized, and the differential assembly has a differential function. When the transmission electromagnetic actuator is powered on and the differential electromagnetic actuator is powered on, the power transmission between the differential case and the planetary gear sleeve is disconnected to solve the problem of power back-drag; when the transmission electromagnetic actuator is powered on and the differential electromagnetic actuator is powered on, the differential case, the planetary gear sleeve, the half-shaft gears and the planetary gears rotate synchronously to achieve the differential locking function. In this state, the power of the differential case can only be transmitted to the left half-shaft gear through the planetary gear sleeve, effectively ensuring the uniformity of the force on the planetary gear sleeve, avoiding torsional deformation of the planetary gear sleeve due to uneven force, and improving the service life of the planetary gear sleeve.

[0006] Preferably, an intermediate plate is provided between the differential electromagnetic actuator and the differential clutch ring, and the intermediate plate is located outside the differential housing; at least one second transmission axial component is provided on the side of the intermediate plate facing the differential clutch ring, and a second through hole for the second transmission axial component to pass through is provided on the differential housing; the differential electromagnetic actuator pushes the differential clutch ring to move axially in the direction close to the left half-shaft gear through the intermediate plate to ensure the stability of the push.

[0007] Preferably, at least one differential axial boss is provided on the outer periphery of the differential clutch ring, and a driving groove is provided in the planetary gear sleeve for the differential axial boss to enter and exit; when the differential axial boss enters the driving groove, the driving groove drives the differential clutch ring to rotate through the differential axial boss; the differential clutch ring is provided with differential connecting teeth on the side facing the left half-shaft gear, and the left half-shaft gear is provided with differential combining teeth that cooperate with the differential connecting teeth; the differential clutch ring and the planetary gear sleeve are controlled to enter and exit the driving groove to achieve circumferential linkage or circumferential linkage release.

[0008] Preferably, the differential connecting teeth are dog teeth to facilitate the transmission of high torque.

[0009] Preferably, the differential axial boss has a driven surface, and the driving groove has a driving surface that fits the driven surface; when the driving surface pushes the driven surface to rotate, the differential clutch ring moves axially in a direction close to the left half-shaft gear to achieve the combination stability of the differential clutch ring and the left half-shaft gear.

[0010] The driven surface is an inclined surface extending outward from left to right. When the driving groove rotates until the driving surface is in contact with the corresponding driven surface, if the driving groove continues to rotate, the driving surface will apply a thrust perpendicular to the driven surface to the driven surface, and the thrust can be decomposed into.

[0011] Preferably, the driven surface is an inclined surface extending outward from left to right, and the driven surface is inclined outward at an angle of 3° to 5°.

[0012] Preferably, a side of the transmission clutch ring close to the planetary gear sleeve is provided with transmission connecting teeth, and a side of the planetary gear sleeve close to the transmission clutch ring is provided with transmission combining teeth meshing with the transmission connecting teeth.

[0013] Preferably, at least one first transmission axial component is provided on a side of the transmission clutch ring close to the transmission electromagnetic actuator, and a first through hole for the first transmission axial component to pass through is provided on the differential housing.

[0014] Preferably, a chuck facing the planetary gear sleeve is provided between the transmission clutch ring and the transmission electromagnetic actuator; the chuck is located outside the differential housing, and the chuck is detachably fixedly connected to the second transmission axial member; the first return spring is limited between the chuck and the differential housing, so as to facilitate the stable transmission of the power of the transmission electromagnetic actuator to the transmission clutch ring through the chuck.

[0015] The present invention also provides a vehicle, comprising the above-mentioned differential assembly.

[0016] As described above, the differential assembly and vehicle provided by the present invention have the following beneficial effects:

[0017] The differential assembly of the present invention can switch the state of the differential assembly by controlling the states of the transmission electromagnetic actuator and the differential electromagnetic actuator, so that the differential assembly can be switched between the differential state, the power disconnection state and the differential locking state as needed, so as to avoid the phenomenon of power back-drag when the vehicle is running at high speed, and improve the vehicle's ability to get out of trouble when driving on uneven roads; in addition, in the differential locking state, since the power of the differential housing can only be transmitted to the left half-shaft gear through the planetary gear sleeve and the differential clutch ring in sequence, the uniformity of the force on the planetary gear sleeve and the differential clutch ring is effectively guaranteed, and the torsional deformation of the planetary gear sleeve and the differential clutch ring due to uneven force is avoided, thereby improving the service life of the planetary gear sleeve and the differential clutch ring; in addition, when the driven surface on the differential axial boss and the driving surface in the driving groove of the planetary gear sleeve cooperate in the present application, the axial position of the differential clutch ring can be locked, thereby ensuring the stability of the differential clutch ring when combined with the left half-shaft gear. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is an axial cross-sectional view of the differential assembly of the present invention.

[0019] Figure 2 for Figure 1 Isometric half-section view of the planetary gear sleeve.

[0020] Figure 3 It is an exploded view of the transmission clutch assembly, the planetary gear sleeve, and the differential housing in the present invention.

[0021] Figure 4 for Figure 3 Exploded diagram of the fit between the intermediate transmission clutch ring and the planetary gear sleeve.

[0022] Figure 5 for Figure 3 Exploded diagram of the fit between the intermediate transmission clutch ring and the differential housing.

[0023] Figure 6 It is an exploded view of the differential clutch assembly, the planetary gear sleeve, and the differential housing in the present invention.

[0024] Figure 7 for Figure 6 Exploded view of the center differential clutch ring, left half-shaft gear, and planetary gear sleeve from the first perspective.

[0025] Figure 8 for Figure 6 Exploded view of the center differential clutch ring, left half-shaft gear, and planetary gear sleeve from the second perspective.

[0026] Fig. 9 It is a three-dimensional diagram of the differential clutch ring.

[0027] Fig.10 It is the right view of the differential axial boss on the differential clutch ring.

[0028] Fig.11 It is a top view of the differential axial boss on the differential clutch ring.

[0029] Fig.12 Schematic diagram of the drive groove in the planetary gear sleeve.

[0030] Fig.13 This is a schematic diagram of the driven surface on the differential axial boss being subjected to force.

[0031] Fig.14 This is an exploded diagram of the fit between the intermediate plate and the differential housing.

[0032] Description of Reference Numerals

[0033] Left housing 1a, right housing 1b, first through hole 1-1, second through hole 1-2, ring gear 2, planetary gear sleeve 3, spherical mounting cavity 3a, cylindrical mounting cavity 3b, transmission coupling tooth 3-1, driving groove 3-2, driving surface 3-21, planetary gear 4, left half-shaft gear 5, differential coupling tooth 5-1, right half-shaft gear 6, transmission electromagnetic actuator 7, transmission clutch ring 8, transmission connecting tooth 8-1, first transmission axial member 8-2, first return spring 9a, second return spring 9b, third return spring 9c, chuck 10, differential electromagnetic actuator 11, differential clutch ring 12, differential axial boss 12-1, driven surface 12-11, differential connecting tooth 12-2, intermediate disk 13, second transmission axial member 13-1, thrust washer 14. DETAILED DESCRIPTION

[0034] The following is a description of the implementation of the present invention by means of specific embodiments. Those skilled in the art can easily understand other advantages and effects of the present invention from the contents disclosed in this specification.

[0035] See also Figures 1 to 14 . It should be noted that the structures, proportions, sizes, etc. illustrated in the drawings in this specification are only used to match the contents disclosed in the specification for people familiar with this technology to understand and read, and are not used to limit the limiting conditions for the implementation of the present invention, so they have no substantial technical significance. Any modification of the structure, change in the proportional relationship, or adjustment of the size should still fall within the scope of the technical content disclosed by the present invention without affecting the effects and purposes that can be achieved by the present invention. At the same time, the terms such as "upper", "lower", "left", "right", "middle" and "one" quoted in this specification are only for the convenience of description, and are not used to limit the scope of the implementation of the present invention. Changes or adjustments in their relative relationships should also be regarded as the scope of the implementation of the present invention without substantially changing the technical content.

[0036] The differential assembly involved in the present invention is installed on a car, and has a differential state, a differential locking state and a power disconnection state, so as to avoid the problems of power back-drag and wheel slippage during the operation of the car; at the same time, the power transmission route in the differential locking state is optimized to solve the defect that the planetary gear sleeve 3 and the differential clutch ring 12 are easily deformed and damaged when the existing differential assembly is in the differential locking state, thereby improving the service life of the differential assembly.

[0037] See also Figure 1 , Figure 2 As shown, the differential assembly involved in the present invention includes a differential housing, a ring gear 2 driving the differential housing to rotate, a transmission clutch assembly arranged on the right side of the differential housing, and a differential clutch assembly arranged on the left side of the differential housing.

[0038] in,

[0039] The differential case is composed of a left case 1a and a right case 1b that are detachably connected; the ring gear 2 is a split structure fixed on the right case 1b or the ring gear and the right case 1b are integrally formed, and the ring gear 2 is used to engage with the power gear of the gearbox to transmit the driving force of the power source (motor or engine) to the differential case.

[0040] A planetary gear sleeve 3, planetary gears 4, and a left half-shaft gear 5 and a right half-shaft gear 6 meshing with the planetary gear 4 are provided in the differential housing; the planetary gear 4 is installed in the planetary gear sleeve 3 through a planetary gear shaft; specifically, the planetary gear sleeve 3 is rotatably installed in the differential housing, and the planetary gear sleeve 3 has a spherical mounting cavity 3a and a cylindrical mounting cavity 3b which are connected and arranged; a spherical surface which fits the inner surface of the spherical mounting cavity 3a is provided on the planetary gear 4. Since the planetary gear 4 is always in spherical contact with the spherical mounting cavity 3a, when the left housing 1a and the right housing 1b cooperate to limit the axial position of the left half-shaft gear 5, the planetary gear 4, and the right half-shaft gear 6, the planetary gear sleeve 3 which is in spherical contact with the planetary gear 4 will also be restricted in axial position, so that the planetary gear sleeve 3 can be rotatably installed in the differential housing but cannot be axially moved.

[0041] The transmission clutch assembly includes a transmission electromagnetic actuator 7, a first return spring 9a and a transmission clutch ring 8; the transmission clutch ring 8 is circumferentially fixed to the differential housing and can move axially relative to the differential housing; when the transmission electromagnetic actuator 7 is energized, the transmission electromagnetic actuator 7 drives the transmission clutch ring 8 to move axially toward the direction approaching the planetary gear sleeve 3, and finally connects with the planetary gear sleeve 3 to form a circumferential fixation; when the transmission electromagnetic actuator 7 is de-energized, the first return spring 9a drives the transmission clutch ring 8 to move axially away from the planetary gear sleeve 3, and finally disconnects from the planetary gear sleeve 3.

[0042] The differential clutch assembly includes a differential electromagnetic actuator 11, a second return spring 9b and a differential clutch ring 12; the differential clutch ring 12 is circumferentially fixed to the planetary gear sleeve 3 and can move axially relative to the planetary gear sleeve 3; the second return spring 9a is located between the differential clutch ring 12 and the left half-shaft gear 5; when the differential electromagnetic actuator 11 is energized, the differential electromagnetic actuator 11 drives the differential clutch ring 12 to move axially toward the left half-shaft gear 5, and finally forms a circumferential fixation with the left half-shaft gear 5; when the differential electromagnetic actuator 11 is de-energized, the second return spring 9b drives the differential clutch ring 12 to move axially away from the left half-shaft gear 5, and finally disconnects from the left half-shaft gear 5.

[0043] Since the transmission electromagnetic actuator 7 and the differential electromagnetic actuator 11 are prior art, their structures will not be described in detail.

[0044] Furthermore, if Figures 3 to 5 As shown, the transmission clutch ring 8 is provided with a first transmission axial member 8-2 on the side facing the transmission electromagnetic actuator 7, and a first through hole 1-1 is provided on the right housing 1b for the first transmission axial member 8-2 to pass through, thereby making the transmission clutch ring 8 circumferentially fixed on the differential housing and movable axially relative to the differential housing; the transmission clutch ring 8 is also provided with a transmission connecting tooth 8-1 on the side facing the planetary gear sleeve 3, and the planetary gear sleeve 3 is correspondingly provided with a transmission combining tooth 3-1 that can mesh with the transmission connecting tooth 8-1 on the side facing the transmission clutch ring 8, and the transmission connecting tooth 8-1 is meshed with the transmission combining tooth 3-1 to realize the circumferential fixation of the transmission clutch ring 8 and the planetary gear sleeve 3 through the meshing connection between the transmission connecting tooth 8-1 and the transmission combining tooth 3-1; in the present embodiment, the transmission connecting tooth 8-1 is preferably a dog tooth to reduce the loss during torque transmission between the planetary gear sleeve 3 and the transmission clutch ring 8 and improve the transmission efficiency.

[0045] It can be understood that there are multiple first transmission axial components 8-2 on the transmission clutch ring 8, and the multiple first transmission axial components 8-2 are preferably arranged at intervals along the circumference of the transmission clutch ring 10; in this embodiment, the multiple first transmission axial components 8-2 are evenly distributed along the circumference of the transmission clutch ring 10.

[0046] In a preferred embodiment, if Figure 1 and Figure 3 As shown, a chuck 10 facing the planetary gear sleeve 3 is provided between the transmission clutch ring 8 and the transmission electromagnetic actuator 7; the chuck 10 is located outside the differential housing, and the chuck 10 is detachably fixedly connected to the second transmission axial member 8-1 to achieve relative fixation of the chuck 10 and the transmission clutch ring 8; the first return spring 9a is limited between the chuck 10 and the differential housing. In this way, when the chuck 10 moves axially, it can drive the transmission clutch ring 8 to move along with it.

[0047] Optionally, the differential assembly further includes a sensor for detecting the position of the chuck 10 , so that the user can accurately identify the moving position of the chuck 10 .

[0048] Further, see Figure 1 , Figures 6 to 8 A differential axial boss 12-1 is provided on the outer periphery of the differential clutch ring 12, and a driving groove 3-2 for the axial entry and exit of the differential axial boss 12-1 is provided in the planetary gear sleeve 3, thereby enabling the differential clutch ring 12 and the planetary gear sleeve 3 to achieve circumferential linkage or circumferential linkage release; a differential clutch ring 12 is also provided with a differential connecting tooth 12-2 on the side facing the left half-shaft gear 5, and a differential combining tooth 5-1 that can mesh with the differential connecting tooth 12-2 is correspondingly provided on the side facing the differential clutch ring 12, and the differential connecting tooth 12-2 is meshed with the differential combining tooth 5-1, and the circumferential fixation of the differential clutch ring 12 and the left half-shaft gear 5 is achieved through the meshing connection between the differential connecting tooth 12-2 and the differential combining tooth 5-1; in this embodiment, the driving groove 3-2 is opened on the inner wall of the cylindrical mounting cavity 3b to avoid interference between the differential clutch ring 12 and the planetary gear 4.

[0049] It can be understood that the differential axial boss 12-1 can only slide axially in the driving groove 3-2, or the differential axial boss 12-1 can both slide axially and rotate circumferentially in the driving groove 3-2. There is no limitation on this, as long as the differential axial boss 12-1 has a driven surface 12-11 and the driving groove 3-2 has a driving surface 3-21 that fits the driven surface 12-11 (such as Figures 10 to 12 shown).

[0050] In order to ensure the stability of the combination of the differential clutch ring 12 and the left half shaft gear 5, Figures 9 to 13 As shown, the driven surface 12-11 is an inclined surface extending outward from left to right (i.e., extending in the direction away from the differential axial boss 12-1); when the driving surface 3-21 pushes the driven surface 12-11 to rotate, the pressure F exerted by the driving surface 3-21 on the driven surface 12-11 can be decomposed into an axial pressure F1 toward the left half-shaft gear 5 and a tangential component force F2 that rotates the differential clutch ring 12. Under the action of the axial pressure F1, the differential clutch ring 12 is tightly combined with the left half-shaft gear 5 to avoid the problem of unstable combination caused by insufficient driving force of the differential electromagnetic actuator 11.

[0051] It should be noted that the outward extension angle of the driven surface 12 - 11 can be determined according to actual conditions and is not limited thereto. In the present embodiment, the outward inclination angle of the driven surface 12 - 11 is preferably 3° to 5°.

[0052] It is understandable that there are multiple differential axial bosses 12 - 1, and the multiple differential axial bosses 12 - 1 are preferably arranged at intervals along the circumference of the differential clutch ring 12; in this embodiment, the multiple differential axial bosses 12 - 1 are evenly distributed along the outer circumference of the differential clutch ring 12.

[0053] In a preferred embodiment, the differential connecting teeth 12 - 2 are dog teeth to reduce the loss during torque transmission between the planetary gear sleeve 3 and the differential clutch ring 12 and improve the transmission efficiency.

[0054] Furthermore, if Figure 1 , Figure 6 and Fig.14 As shown, an intermediate plate 13 is provided between the differential electromagnetic actuator 11 and the differential clutch ring 12, and the intermediate plate 13 is located outside the differential housing; a second transmission axial member 13-1 is provided on the side of the intermediate plate 13 facing the differential clutch ring 12, and a second through hole 1-2 is provided on the differential housing for the second transmission axial member 13-1 to pass through, thereby making the intermediate plate 13 circumferentially fixed on the differential housing and axially move relative to the differential housing; a third return spring 9c can be optionally provided between the intermediate plate 13 and the differential housing; since there is no power transmission in the circumferential direction between the intermediate plate 13 and the differential clutch ring 12, when the differential electromagnetic actuator 11 pushes the differential clutch ring 12 to move axially toward the direction close to the left half-shaft gear 5 through the intermediate plate 13, the intermediate plate 13 and the differential clutch ring 12 can rotate separately without interfering with each other.

[0055] Furthermore, if Figure 1 As shown, a thrust gasket 14 is provided between the differential electromagnetic actuator 11 and the intermediate disk 13, and a thrust gasket 14 is provided between the transmission electromagnetic actuator 7 and the chuck 10, so as to utilize the thrust gasket 14 to transmit the thrust of the electromagnetic actuator; the thrust gasket 14 is preferably made of friction material.

[0056] Optionally, the differential assembly further includes a sensor for detecting the position of the intermediate disk 13 , so that the user can accurately identify the moving position of the intermediate disk 13 .

[0057] The present invention also provides a vehicle, which comprises the above-mentioned differential assembly.

[0058] During actual driving, the user can control the state of the transmission electromagnetic actuator 7 and the differential electromagnetic actuator 11 as needed to switch the differential assembly between the differential state, the power disconnection state and the differential locking state. When the transmission electromagnetic actuator 7 is powered on and the differential electromagnetic actuator 11 is powered off, the powered transmission electromagnetic actuator 7 will drive the transmission clutch ring 10 to approach the planetary gear sleeve 3 until the transmission connection teeth 8-1 of the transmission clutch ring 10 are connected with the transmission combination teeth 3-1 of the planetary gear sleeve 3 to form a circumferential fixation. During this process, the first reset spring 9a is gradually compressed; when the transmission clutch ring 10 is circumferentially fixed to the planetary gear sleeve 3, since the transmission clutch ring 10 itself is circumferentially fixed to the differential housing, the differential housing and the planetary gear sleeve 3 are in a power connection state; at this time, the differential assembly is in a differential state, which can automatically adjust the rotation speed of the left and right wheels when the car turns, to ensure the steering stability of the car;

[0059] When the transmission electromagnetic actuator 7 and the differential electromagnetic actuator 11 are powered off, the compressed first return spring 9a will push the transmission clutch ring 10 to move axially in the direction away from the planetary gear sleeve 3 until the transmission connecting tooth 8-1 of the transmission clutch ring 10 is separated from the transmission combining tooth 3-1 of the planetary gear sleeve 3. At this time, the differential assembly is in a power disconnected state, and there is no power transmission between the differential housing and the half-shaft gears, which prevents the power of the wheel rotation from being transmitted to the differential housing, causing the problem of power back-drag.

[0060] When the transmission electromagnetic actuator 7 is energized and the differential electromagnetic actuator 11 is energized, the energized transmission electromagnetic actuator 7 will drive the transmission clutch ring 10 to approach the planetary gear sleeve 3 until the transmission connecting teeth 8-1 of the transmission clutch ring 10 are connected with the transmission combining teeth 3-1 of the planetary gear sleeve 3 to form a circumferential fixation; at the same time, the energized differential transmission electromagnetic actuator 11 will push the differential clutch ring 12 to approach the left half-shaft gear 5 through the intermediate plate 13 until the differential connecting teeth 12-2 of the differential clutch ring 12 are connected with the differential combining teeth 5-1 of the left half-shaft gear 5 to form a circumferential fixation; in this way, the power of the power source can be transmitted to the planetary gear sleeve 3 through the differential case, and transmitted to the differential clutch ring 12 through the planetary gear sleeve 3, and then transmitted to the left half-shaft gear 5. At this time, the differential assembly is in a differential locking state. In this state, the differential The differential case, planetary gear sleeve 3, planetary gear 4 and each half-shaft gear rotate synchronously, so that the differential adjustment of the wheels on both sides is limited, which effectively solves the problem of wheel slippage when the car is driving on bad roads and improves the vehicle's ability to get out of trouble; in addition, in the differential locking state, the present application optimizes the power transmission route of the entire differential assembly, and optimizes the original dual-route power transmission (i.e., differential case → planetary gear sleeve 3 → planetary gear 4 → left half-shaft gear 5 → differential clutch ring 12 and differential case → differential clutch ring 12 → left half-shaft gear 5) to a single-route power transmission (i.e., differential case → planetary gear sleeve 3 → differential clutch ring 12 → left half-shaft gear 5), thereby avoiding torsional deformation of the planetary gear sleeve 3 and the differential clutch ring 12 due to uneven force and improving the service life of the planetary gear sleeve 3 and the differential clutch ring 12.

[0061] In summary, the present invention optimizes the structure of the differential transmission component to optimize the power transmission route of the differential assembly in the differential locking state, ensuring that the power of the differential housing can only be transmitted to the left half-shaft gear 5 through the planetary gear sleeve 3 and the differential clutch ring 12, avoiding torsional deformation of the planetary gear sleeve 3 and the differential clutch ring 12 due to uneven force in the differential locking state, and improving the service life of the planetary gear sleeve 3 and the differential clutch ring 12.

[0062] The above embodiments are merely illustrative of the principles and effects of the present invention, and are not intended to limit the present invention. Anyone familiar with the art may modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by a person of ordinary skill in the art without departing from the spirit and technical concept disclosed by the present invention shall still be covered by the claims of the present invention.

Claims

1. A differential assembly, comprising a differential housing, a ring gear (2) for driving the differential housing to rotate, a transmission clutch assembly arranged on the right side of the differential housing, and a differential clutch assembly arranged on the left side of the differential housing; the differential housing is provided with a planetary gear sleeve (3), a planetary gear (4), and a left half-shaft gear (5) and a right half-shaft gear (6) meshing with the planetary gear (4); the planetary gear (4) is installed in the planetary gear sleeve (3) through a planetary gear shaft; the transmission clutch assembly comprises a transmission electromagnetic actuator (7), a first return spring (9a) and a transmission clutch ring (8); the transmission clutch ring (8) is connected to the differential The transmission housing is circumferentially fixed and can move axially relative to the differential housing; when the transmission electromagnetic actuator (7) is powered on, the transmission clutch ring (8) is driven to move axially in a direction close to the planetary gear sleeve (3), and finally connected with the planetary gear sleeve (3) to form a circumferential fixation; when the transmission electromagnetic actuator (7) is powered off, the first return spring (9a) drives the transmission clutch ring (8) to move axially in a direction away from the planetary gear sleeve (3), and finally disconnects from the planetary gear sleeve (3); the differential clutch assembly comprises a differential electromagnetic actuator (11), a second return spring (9b) and a differential clutch ring (12); characterized in that, The differential clutch ring (12) is circumferentially fixed to the planetary gear sleeve (3) and can move axially relative to the planetary gear sleeve (3); the second return spring (9a) is located between the differential clutch ring (12) and the left half-shaft gear (5); when the differential electromagnetic actuator (11) is powered on, the differential electromagnetic actuator (11) drives the differential clutch ring (12) to move axially in a direction close to the left half-shaft gear (5), and finally forms a circumferential fixation with the left half-shaft gear (5); when the differential electromagnetic actuator (11) is powered off, the second return spring (9b) drives the differential clutch ring (12) to move axially in a direction away from the left half-shaft gear (5), and finally disconnects from the left half-shaft gear (5).

2. A differential assembly according to claim 1, characterized in that: An intermediate disk (13) is provided between the differential electromagnetic actuator (11) and the differential clutch ring (12), and the intermediate disk (13) is located outside the differential housing; at least one second transmission axial component (13-1) is provided on the side of the intermediate disk (13) facing the differential clutch ring (12), and a second through hole (1-2) for the second transmission axial component (13-1) to pass through is provided on the differential housing; the differential electromagnetic actuator (11) pushes the differential clutch ring (12) to move axially in a direction close to the left half-shaft gear (5) through the intermediate disk (13).

3. A differential assembly according to claim 2, characterized in that: At least one differential axial boss (12-1) is provided on the outer periphery of the differential clutch ring (12), and a driving groove (3-2) for the differential axial boss (12-1) to enter and exit is provided in the planetary gear sleeve (3); when the differential axial boss (12-1) enters the driving groove (3-2), the driving groove (3-2) drives the differential clutch ring (12) to rotate via the differential axial boss (12-1); a differential connecting tooth (3-1) is provided on the side of the differential clutch ring (12) facing the left half-shaft gear (5), and a differential coupling tooth (5-1) cooperating with the differential connecting tooth (3-1) is provided on the left half-shaft gear (5).

4. A differential assembly according to claim 3, characterized in that: The differential connecting teeth (12-2) are dog teeth.

5. A differential assembly according to claim 3, characterized in that: The differential axial boss (12-1) has a driven surface (12-11), and the driving groove (3-2) has a driving surface (3-21) that fits the driven surface (12-11); when the driving surface (3-21) pushes the driven surface (12-11) to rotate, the differential clutch ring (12) moves axially in a direction close to the left half-shaft gear (5).

6. A differential assembly according to claim 5, characterized in that: The driven surface (12-11) is an inclined surface extending outward from left to right, and the driven surface (12-11) is inclined outward at an angle of 3° to 5°.

7. A differential assembly according to claim 6, characterized in that: A transmission connection tooth (8-1) is provided on one side of the transmission clutch ring (8) close to the planetary gear sleeve (3), and a transmission coupling tooth (3-2) meshing with the transmission connection tooth (8-1) is provided on one side of the planetary gear sleeve (3) close to the transmission clutch ring (8).

8. A differential assembly according to claim 7, characterized in that: At least one first transmission axial component (8-1) is provided on a side of the transmission clutch ring (8) close to the transmission electromagnetic actuator (7), and a first through hole (1-1) for the second transmission axial component (8-1) to pass through is provided on the differential housing.

9. A differential assembly according to claim 8, characterized in that: A chuck (10) facing the planetary gear sleeve (3) is provided between the transmission clutch ring (8) and the transmission electromagnetic actuator (7); the chuck (10) is located outside the differential housing, and the chuck (10) is detachably fixedly connected to the second transmission axial member (8-1); and the first return spring (9a) is limited between the chuck (10) and the differential housing.

10. A vehicle, characterized in that: Comprising the differential assembly as claimed in any one of claims 1 to 9.

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