Differential assembly

Abstract

The invention relates to a differential assembly for a drive axle of a vehicle, comprising a drive housing and a planetary gear mechanism (2) arranged within the drive housing, which is capable of distributing the torque of the drive housing to the respective half shafts, wherein the differential assembly further comprises a disconnect sleeve (3), wherein the disconnect sleeve (3) is arranged radially between the drive housing and the planetary gear mechanism (2), wherein the disconnect sleeve (3) is torsionally connected with the drive housing, wherein the disconnect sleeve (3) is axially movable between an engaged position and a disengaged position, in which the disconnect sleeve (3) is torsionally connected with the planet carrier of the planetary gear mechanism (2) in the engaged position and in which the disconnect sleeve (3) is disconnected from the planetary gear mechanism (2) in the disengaged position.

Description

TECHNICAL FIELD

[0001] The present invention relates to the field of vehicle technology, in particular to a differential assembly for a drive axle of a vehicle, comprising a disconnect mechanism. BACKGROUND

[0002] Differentials generally split or distribute the input power introduced from a power input end via planetary gearings in the differential to two drive shafts. Differentials can be used in particular for drive axles of vehicles. In this case, the drive power provided by the drive equipment of the vehicle can be distributed by the differential to the half shafts connected to the drive wheels. In the case of straight-ahead driving of the vehicle, the drive wheels rotate at the same speed; in the case of cornering of the vehicle, the drive wheels rotate at different speeds. The differential enables the speed difference, but the average of the rotational speeds of the two drive wheels remains unchanged.

[0003] A common differential is the so-called bevel gear differential, which, however, is relatively wide and requires a large amount of space, which is disadvantageous for the arrangement in a vehicle. In addition to the bevel gear differential, the differential can also be designed as a so-called spur gear differential, which significantly reduces the required arrangement space. In the spur gear differential, the gear wheels as power outputs are coupled to one another by means of a planetary gearing pair which can be rotated in opposite directions by two mutually engaging planetary gears, which are designed as spur gears. A differential drive is disclosed, for example, in patent application DE 10 2007 040 478 A1, in which the drive gear wheel of the differential drive as input is distributed to two outputs by means of a gear wheel pair consisting of one of the first planetary gears and one of the second planetary gears, wherein the two planetary gears of the gear wheel pair are connected to one another so as to be opposite and acting such that the two planetary gears of the gear wheel pair each engage with two driven gear wheels as outputs, wherein the drive gear wheel is designed as an axially symmetrical spur gear and comprises a first and a second support manufactured by cold rolling, on which the planetary gears are supported. Furthermore, a differential drive is disclosed in patent application WO 201 1 003747 A2, in which the planetary gears are designed as spur gears.

[0004] However, in drive vehicles in which the drive power can be transmitted to both the front wheels and the rear wheels, it is sometimes necessary to disconnect a set of wheels from the drive device of the vehicle in order to improve fuel efficiency and vehicle performance. For example, a bevel gear differential assembly is disclosed in patent document CN106246860 B, which comprises a differential housing, a differential case, a differential bevel gear set, a ring gear and a disconnecting member configured as a friction clutch, wherein the disconnecting member selectively disconnects or connects the ring gear and the differential case. The disadvantage of this solution is that the axial dimension of the bevel gear differential assembly is further expanded on the basis of the large dimension of the differential bevel gear set due to the size and arrangement of the disconnecting member, thereby making it difficult to arrange the bevel gear differential assembly. In addition, the disconnecting member relies on an actuator to maintain its position, and especially when the bevel gear differential needs to be kept in a disconnected state, the disconnected state is unstable. SUMMARY

[0005] Therefore, the technical problem to be solved by the present application is to provide a differential assembly for a drive axle of a vehicle, which itself comprises a mechanism capable of disconnecting and connecting the drive wheels from the drive device, and which has a very compact axial dimension while being able to maintain a stable disconnected state.

[0006] The technical problem is solved by a differential assembly which can be used in a drive axle of a vehicle, in particular for an electric drive axle of a purely electric vehicle or a hybrid vehicle. The differential assembly comprises a drive housing and a planetary gear transmission arranged in the drive housing, wherein the planetary gear transmission is capable of distributing the torque of the drive housing to the respective half shafts of the drive axle, and the planetary gear transmission comprises a planet carrier which can be driven by the drive housing.

[0007] In this case, the drive housing is capable of introducing the drive torque generated by, for example, an internal combustion engine and / or an electric motor into the differential assembly. The drive housing forms a cavity on its radially inner side to accommodate the planetary gear transmission. The axial position of the planetary gear transmission relative to the drive housing is preferably kept constant. The planetary gear transmission can be designed as a bevel gear differential transmission or as a cylindrical gear differential transmission.

[0008] According to the application, the differential assembly further comprises a disconnecting mechanism designed as a disconnecting sleeve, wherein the disconnecting sleeve is arranged radially between the drive housing and the planetary gear transmission, wherein the disconnecting sleeve is torsionally connected to the drive housing, wherein the disconnecting sleeve is axially movable, in particular by means of an actuator, between an engagement position and a disengagement position, the disconnecting sleeve in the engagement position achieving a torsional connection between the drive housing and the planet carrier, the disconnecting sleeve in the disengagement position disconnecting the torsional connection between the drive housing and the planetary gear transmission.

[0009] The decoupling sleeve has a main structure, for example, in the form of a thin-walled ring, which can be arranged in the radial space between the drive housing and the planetary gear mechanism if necessary. The decoupling sleeve is torsionally connected to the drive housing, while the decoupling sleeve remains axially movable relative to the drive housing. For example, the connection of the decoupling sleeve to the drive housing is positively locking in the circumferential direction and has a certain freedom of movement in the axial direction. The movement of the decoupling sleeve between the engaged position and the decoupled position can be carried out by the driver or automatically by the vehicle control system. The decoupling sleeve has a first engagement part, and the carrier has a second engagement part for torsionally connecting to the first engagement part. Here, the engagement parts of the decoupling sleeve and the carrier can be arranged radially and / or axially outside the planetary gear mechanism. The torsional connection of the decoupling sleeve and the carrier can be a form-fit connection or a frictional engagement. When the decoupling sleeve is in the engaged position, the first engagement part and the second engagement part are in torsional connection, so that the drive housing can transmit torque to the carrier, thereby further distributing torque to the two sun gears. When the decoupling sleeve is in the decoupled position, the first engagement part and the second engagement part are disconnected, thereby interrupting the torque transmission between the drive housing and the planetary gear mechanism, in particular the carrier.

[0010] In a preferred embodiment, the planetary gear mechanism further comprises: a first sun gear and a second sun gear for transmitting torque to respective half-shafts of the drive axle; and at least one planetary gear pair composed of first and second planetary gears meshing with each other, wherein the first and second planetary gears are respectively supported on the carrier, the first planetary gears mesh with the first sun gear, and the second planetary gears mesh with the second sun gear. That is, the planetary gears are each configured as a cylindrical gear. Therefore, the planetary gear pair is configured as a cylindrical gear pair. In the planetary gear mechanism, two or more planetary gear pairs composed of first and second planetary gears can be arranged, preferably three, four, or five such planetary gear pairs. Here, all first planetary gears mesh with the first sun gear, and all second planetary gears mesh with the second sun gear. In the planetary gear mechanism, all planetary gear pairs are preferably evenly distributed on the carrier in the circumferential direction based on the revolution axis of the planetary gears. Such an arrangement can enhance the stability of torque transmission and reduce the force to be borne by each planetary gear pair, slow down wear, and enhance the service life. The two sun gears can be directly or indirectly torsionally connected to the half-shafts to further transmit the torque distributed to the two sun gears to the respective half-shafts. Thus, by designing as a cylindrical gear differential mechanism, the planetary gear mechanism not only can distribute the torque of the drive housing to the respective half-shafts, but also has a very small axial dimension, which is particularly suitable for the electric drive axle of a hybrid vehicle or an all-electric vehicle.

[0011] Preferably, the rotational axis of the drive housing, the rotational axis of the decoupling sleeve and the revolution axis of the planetary gear mechanism lie on one straight line. The revolution axis of the planetary gear mechanism is the common revolution axis of the individual planetary gears of the planetary gear mechanism. In this case, it can be advantageously provided that the decoupling sleeve has a first engagement portion on the radially inner side and the planet carrier has a second engagement portion on the radially outer side for a torque-proof connection with the first engagement portion. Thereby, the axial dimension of the differential assembly can be minimized, meeting the design requirements of an electric drive axle of an electric or hybrid vehicle, in particular. Here, advantageously, the first engagement portion and the second engagement portion can be configured as spline portions. Thereby, a torque-proof and axially movable connection of the decoupling sleeve with the drive housing is realized in a simple manner, and this connection enables a high torque transfer. Alternatively, the first engagement portion and the second engagement portion can also be configured as keyway connections.

[0012] Here, advantageously, the planet carrier comprises a planet carrier support and a planet carrier end disk which are fixedly connected to each other, wherein the first planetary gear and the second planetary gear are each supported on both axial sides on the planet carrier support and the planet carrier end disk. Thereby, a stable support of the individual planetary gears is enabled.

[0013] Here, the planet carrier end disk can be configured as an annular disk, and the planet carrier support can comprise an annular base plate and axial connection portions for the connection with the planet carrier end disk. Here, the annular base plate of the planet carrier support and the planet carrier end disk are preferably arranged parallel to each other. The axial connection portions can here be designed as a continuous connection sleeve in the circumferential direction or as connection beams which are spaced apart in the circumferential direction. The free ends of the axial connection portions are fixedly connected, preferably welded, to the planet carrier end disk, and can alternatively also be connected by further connecting elements. Advantageously, the second engagement portion is configured on the planet carrier end disk, which is advantageous in terms of manufacturing.

[0014] In a preferred embodiment, the differential assembly further comprises a return spring which is clamped between the drive housing and the decoupling sleeve. The return spring is for example a disc spring or a cylindrical spring or the like. In an advantageous embodiment, when the actuator acts on the decoupling sleeve and overcomes the spring force of the return spring, the decoupling sleeve is moved from the decoupling position to the engagement position; when the actuator withdraws the force from the decoupling sleeve, the decoupling sleeve is moved from the engagement position to the decoupling position by means of the spring force of the return spring. Thereby, a stable and reliable disconnection state is ensured.

[0015] Preferably, the drive housing comprises a drive gear and a drive end cap which are fixedly connected to one another, wherein the decoupling sleeve and the planetary gear mechanism are arranged axially between the drive gear and the drive end cap. The drive gear is configured with a toothing on the radially outer side in a conventional manner, which toothing is able to engage with a gear upstream of the drive axle in order to introduce the torque of the drive axle upstream into the differential assembly. Advantageously, the drive gear is formed with a cavity on the radially inner side for accommodating the decoupling sleeve and the planetary gear mechanism. The drive gear and the drive end cap are fixedly connected to one another, preferably by welding, but can alternatively also be connected by means of further connecting elements. The drive gear and the drive end cap have a central bore for the passage of a shaft sleeve of the sun gear or of the half shafts. If necessary, the drive gear and / or the drive end cap have an axially extending shaft sleeve for support. Advantageously, the drive end cap has an axial through-hole which is arranged offset from the axis thereof and the decoupling sleeve has an axial protrusion, wherein the axial protrusion extends into the axial through-hole, thereby achieving a torque-proof and axially relatively movable connection between the decoupling sleeve and the drive end cap and thus between the drive housing. Preferably, at least three sets of corresponding axial through-holes and axial protrusions are provided. The at least three sets of axial through-holes and axial protrusions are preferably uniformly distributed in the circumferential direction.

[0016] Here, advantageously, the return spring is, at one end, abutted against an axial end face of the drive end cap which faces away from the drive gear, and, at the other end, is abutted against a projecting section of the axial protrusion which extends out of the axial through-hole. This arrangement is advantageous in terms of assembly. In particular in the case of a fixed connection of the drive gear and the drive end cap to one another by means of welding, this arrangement is very advantageous in terms of the ease of replacement of the return spring.

[0017] Advantageously, a holding portion for holding the return spring is configured on the projecting section. The holding portion preferably matches an end portion structure of the return spring which abuts against the projecting section. For example, in the case of a return spring which is designed as a dished spring which is slotted on the radially outer side, a catch slot can be configured on the projecting section which matches a spring finger on the dished spring which is formed by the slot, thereby enabling the dished spring to be held.

[0018] Advantageously, the decoupling sleeve has an axial positioning portion which can be abutted against an axial end face of the drive end cap which faces towards the drive gear. The axial positioning portion is in particular configured in a region of an axial end face of the decoupling sleeve which faces towards the drive end cap and which is free of the axial protrusion.

[0019] Advantageously, an end portion of the axial protrusion at its projecting section is configured with a planar region which extends perpendicular to the rotational axis of the decoupling sleeve, thereby facilitating the abutment of the actuator against the decoupling sleeve, whereby a force, in particular an axial force, is applied to the decoupling sleeve in a smooth manner. BRIEF DESCRIPTION OF DRAWINGS

[0020] The preferred embodiments of the application are schematically set out below with reference to the accompanying drawings. The drawings are:

[0021] Figure 1 is an exploded view of a differential assembly according to a preferred embodiment,

[0022] Figure 2 is a perspective view of a split sleeve in a differential assembly according to Figure 1

[0023] Figure 3 is an exploded view of a planetary gear mechanism in a differential assembly according to Figure 1

[0024] Figure 4 is a side view of a planetary gear mechanism according to Figure 3

[0025] Figure 5 is a half sectional view of a differential assembly according to Figure 1

[0026] Figure 6 is a half sectional view of a differential assembly according to Figure 1 DETAILED DESCRIPTION

[0027] Figure 1 An exploded view of a differential assembly according to a preferred embodiment is shown. The differential assembly comprises a drive housing and a planetary gear mechanism 2 arranged inside the drive housing, the differential assembly further comprises a split sleeve 3 and a return spring 4.

[0028] In Figure 1 , the components of the differential assembly are shown in order from left to right, i.e. the return spring 4, the drive end cover 5, the split sleeve 3, the planetary gear mechanism 2 and the drive gear 1. In the present embodiment, the rotational axis of the return spring 4, the rotational axis of the drive end cover 5, the rotational axis of the split sleeve 3 and the axis of revolution of the planetary gear mechanism 2 as well as the rotational axis of the drive gear 1 are arranged on the same straight line.

[0029] ​​​​​The drive housing is composed of an axially distributed drive gear 1 and a drive end cap 5. The drive gear 1 and the drive end cap 5 are welded to each other, whereby a small radial dimension is achieved. The drive gear 1 is configured with a toothing on the radially outer side in a conventional manner, for engaging with a gear (not shown) upstream of the drive axle, in order to introduce the torque upstream of the drive axle into the differential assembly. The drive gear 1 is formed with a cavity on the radially inner side and is closed with the drive end cap 5. The split sleeve 3 and the planetary gear mechanism 2 can be accommodated in the cavity. The drive gear 1 and the drive end cap 5 each have a central bore for the two half shafts of the drive axle to extend through, respectively. An axially extending bearing bushing is formed on the outer periphery of the respective central bore of the drive gear 1 and the drive end cap 5. The drive end cap 5 has an axial through hole 51 which is arranged offset to the rotational axis thereof.

[0030] Figure 3 and Figure 4 respectively show an exploded view and a side view of the planetary gear mechanism 2 in a differential assembly according to Figure 1 The planetary gear mechanism 2 is designed here as a module as a whole, in order to achieve the differential function. As shown in Figure 3 and Figure 4 The planetary gear mechanism 2 comprises a carrier, two sun gears and three planetary gear pairs 23. The two sun gears are a first sun gear 22 on the drive gear 1 side and a second sun gear 24 on the drive end cap 5 side, respectively. Each planetary gear pair 23 comprises a first planetary gear 232 and a second planetary gear 231 which mesh with each other. At least two planetary gear pairs 23 can be provided. In the present embodiment, three planetary gear pairs 23 are provided which are arranged uniformly in the circumferential direction. All first planetary gears 232 mesh with the first sun gear 22. All second planetary gears 231 mesh with the second sun gear 24.

[0031] The carrier is composed of a carrier support 25 and a carrier end disk 21 which are arranged coaxially. The carrier end disk 21 is in the form of an annular disk. The carrier support 25 has an annular base plate which extends in a plane perpendicular to the rotational axis of the carrier and connecting beams which extend from the outer periphery of the annular base plate in the direction of the rotational axis of the carrier. As shown in Figure 3 The connecting beams are designed in the present embodiment as three. The carrier end disk 21 and the annular base plate of the carrier support 25 are arranged in parallel. The carrier end disk 21 and the free ends of the connecting beams of the carrier support 25 are welded to each other. Here, all planetary gears 232, 231 are supported on the carrier end disk 21 on the drive gear 1 side and on the carrier support 25 on the drive end cap 5 side, in order to achieve a stable support. The carrier end disk 21 and the carrier support 25 each have a central bore for the shaft bushing of the first sun gear 22 and the second sun gear 24 to pass through, respectively. Furthermore, the carrier end disk 21 is provided with an external spline 211 on the outer periphery. The spline teeth of the external spline 211 are preferably provided with a chamfer.

[0032] Figure 2 A perspective view of a partial section of a split sleeve in a differential assembly according to Figure 1 is shown. In conjunction with Figure 1 and Figure 2 it can be seen that the split sleeve 3 has a main body structure which is essentially a thin-walled ring, so as to be able to be arranged in the radial space between the drive pinion 1 and the planetary gear mechanism 2.

[0033] The split sleeve 3 is provided with an inner spline portion 32 at the axial end side facing away from the drive end cap 5, which matches an outer spline portion 211 of the planet carrier end disk 21. The spline teeth of the inner spline portion 32 are likewise preferably provided with a chamfer, so as to reduce the collision during meshing. In the present embodiment, the inner spline 32 is produced by stamping.

[0034] The split sleeve 3 is provided with axially protruding portions 31 at the axial end side facing towards the drive end cap 5, which are distributed uniformly in the circumferential direction. In the present embodiment, there are six axially protruding portions 31, but other numbers of axially protruding portions 31 can also be provided in other embodiments. The axially protruding portions 31 preferably match the number and position of the axial through-holes 51 on the drive end cap 5. Advantageously, the axially protruding portions 31 are configured as thin-walled bent portions, such that the axially protruding portions 31 comprise three successively connected sections, namely a first axial section which extends from the main body structure of the split sleeve 3 through the corresponding axial through-hole 51 on the drive end cap 5; a radial planar section 312 which extends radially inwards from the end of the first axial section; and a second axial section which extends axially back towards the main body structure from the radially inner side of the radial planar section 312. Thereby, the anti-torsional connection between the split sleeve 3 and the drive housing is achieved by the axial through-holes 51 of the drive end cap 5 and the axially protruding portions 31 of the split sleeve 3, which can be passed into the axial through-holes 51 and moved axially, and at the same time the axial movability of the split sleeve 3 relative to the drive housing is ensured.

[0035] The split sleeve 3 has an axial positioning portion 33 for abutment on the axial end face of the drive end cap 5 facing towards the drive pinion 1. The axial positioning portion 33 is in particular configured in the axial end face region between the axially protruding portions 31 of the split sleeve 3, and has a profile which matches the axial end face of the drive end cap 5 facing towards the drive pinion 1, for example can be configured as a flat surface.

[0036] As Figure 1As shown, the return spring 4 is configured as a disc spring, in particular a slotted disc spring, in the present embodiment. The return spring 4 abuts at one end against an axial end face of the drive end cap 5 facing away from the drive gear wheel 1 and at the other end against the protruding section of the axial protrusion 3 extending through the axial through-hole 51. The disc spring 4 forms spring fingers pointing radially outwards by means of the slots on the radially outer side. The number of spring fingers is preferably matched to the number of axial protrusions 31 of the decoupling sleeve 3. Matching spring fingers can be provided on the second axial section of the axial protrusions 31 in order to hold the disc spring 4.

[0037] Figure 5 and Figure 6 respectively show a half-section view of a differential assembly according to Figure 1 in the engaged state and in the decoupled state. By means of an actuator not shown, the decoupling sleeve 3 can be switched by the driver or automatically by a vehicle control system between different axial positions, namely the engaged position shown in Figure 5 and the decoupled position shown in Figure 6 .

[0038] In the case shown in Figure 5 , the actuator not shown exerts an axial force on the radially planar section 312 of the decoupling sleeve 3 so that the decoupling sleeve 3 is held against the spring force of the disc spring 4 in the engaged position as shown in Figure 5 . At this time, the inner spline 32 on the decoupling sleeve 3 is in engagement with the outer spline 211 on the planet carrier 21 so that the drive torque transmitted from the drive gear wheel 1 can be distributed to the two half shafts not shown by means of the planetary gear mechanism 2.

[0039] In the case shown in Figure 6 , the actuator not shown does not exert a force on the decoupling sleeve 3. The decoupling sleeve 3 is held by the spring force of the disc spring 4 in the decoupled position as shown in Figure 6 . At this time, the inner spline 32 on the decoupling sleeve 3 is not in engagement with the outer spline 211 on the planet carrier 21 so that the drive gear wheel 1 is disconnected from the planetary gear mechanism 2. At this time, the vehicle can be switched from a four-wheel drive state to a two-wheel drive state, for example. It can also be seen in Figure 6 that the axial positioning portion 33 is at this time abutting against the axial end face of the drive end cap 5 facing towards the drive gear wheel 1 so that the disconnected state is very stable.

[0040] It can be seen in particular in connection with Figure 5 and Figure 6 that the decoupling sleeve 3 is arranged radially in the radial space between the drive housing and the planetary gear mechanism 2 so that the differential assembly has a very compact axial dimension. Furthermore, the decoupling sleeve 3 can be held in the decoupled position by means of the disc spring so that the disconnected state of the differential from the drive device can be held even more reliably and stably.

[0041] While the above description illustrates possible embodiments, it is understood that there exist numerous variations of the embodiments by all known and otherwise conceivable technical characteristics and implementation forms. It is further understood that the exemplary embodiments are merely examples and that the embodiments in no way limit the scope of protection, application and construction of the present application in any form. The foregoing description is intended more as a specific example of the technical guidance which would be provided to a person of skill in the art by the present application, and thus various changes to the embodiments described herein can be made without departing from the scope of the present application as defined by the appended claims, particularly considering the teachings of the specification as a whole.

[0042] List of reference signs

[0043] 1 drive gear

[0044] 2 planetary gear mechanism

[0045] 21 planet carrier end disk

[0046] 211 second engagement portion, external spline portion

[0047] 22 first sun gear

[0048] 23 planetary gear pair

[0049] 231 second planetary gear

[0050] 232 first planetary gear

[0051] 24 second sun gear

[0052] 25 planet carrier support

[0053] 3 separation sleeve

[0054] 31 axial protrusion

[0055] 311 clamping slot

[0056] 312 radial planar section

[0057] 32 first engagement portion, internal spline portion

[0058] 33 axial positioning portion

[0059] 4 return spring, disc spring

[0060] 5 drive end cap

[0061] 51 axial through hole

Claims

1. Differential assembly for a drive axle of a vehicle, comprising: - a drive housing; - a planetary gear mechanism (2) arranged within the drive housing and capable of distributing the torque of the drive housing to respective half shafts of the drive axle, wherein the planetary gear mechanism (2) comprises a planet carrier capable of being driven by the drive housing; characterized in that the differential assembly further comprises a decoupling sleeve (3), wherein the decoupling sleeve (3) is arranged radially between the drive housing and the planetary gear mechanism (2), wherein the decoupling sleeve (3) is torsionally connected with the drive housing, wherein the decoupling sleeve (3) is axially movable between an engagement position, in which the decoupling sleeve (3) effects a torsional connection between the drive housing and the planet carrier, and a decoupling position, in which the decoupling sleeve (3) interrupts the torsional connection between the drive housing and the planetary gear mechanism (2).

2. The differential assembly of claim 1, wherein, the planetary gear mechanism (2) further comprises: - a first sun gear (22) and a second sun gear (24) for respectively transmitting torque to the respective half shafts; - at least one planetary gear pair, which is composed of a first planetary gear (232) and a second planetary gear (231) that mesh with each other, wherein the first planetary gear (232) and the second planetary gear (231) are respectively supported on the planet carrier, the first planetary gear (232) meshes with the first sun gear (22), and the second planetary gear (231) meshes with the second sun gear (24).

3. The differential assembly of claim 2, wherein, the rotational axis of the drive housing, the rotational axis of the decoupling sleeve (3), and the axis of revolution of the planetary gear mechanism (2) are on the same straight line, wherein the decoupling sleeve (3) has a first engagement portion (32) on the radially inner side, and the planet carrier has a second engagement portion (211) on the radially outer side for torsionally connecting with the first engagement portion (32).

4. The differential assembly of claim 3, wherein, the planet carrier comprises a planet carrier support (25) and a planet carrier end disk (21) that are fixedly connected with each other, wherein the first planetary gear (232) and the second planetary gear (231) are respectively supported on both axial sides of the planet carrier support (25) and the planet carrier end disk (21).

5. The differential assembly of claim 4, wherein, the planet carrier end disk (21) is in the shape of a ring disk, the planet carrier support (25) comprises a ring-shaped base plate and an axial connection portion for connecting with the planet carrier end disk (21), and the second engagement portion is configured on the planet carrier end disk (21).

6. The differential assembly according to claim 1, further comprising a return spring (4) clamped between the drive housing and the decoupling sleeve (3).

7. The differential assembly of claim 6, wherein, the drive housing comprises a drive gear (1) and a drive end cover (5) that are fixedly connected with each other, wherein the decoupling sleeve (3) and the planetary gear mechanism (2) are arranged axially between the drive gear (1) and the drive end cover (5), The drive end cap (5) has an axial through-hole (51) arranged offset from its central axis and the decoupling sleeve (3) has an axial protrusion (31), wherein the axial protrusion (31) extends through the axial through-hole (51).

8. The differential assembly of claim 7, wherein, The return spring (4) rests at one end on an axial end face of the drive end cap (5) facing away from the drive gear (1) and at the other end on a protruding section of the axial protrusion (31) extending out of the axial through-hole (51).

9. The differential assembly of claim 8, wherein, A holding portion (311) for holding the return spring (4) is configured on the protruding section.

10. The differential assembly of claim 7, wherein, The decoupling sleeve (3) has an axial positioning portion (33) which can rest on an axial end face of the drive end cap (5) facing towards the drive gear (1).

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