Differential and vehicle transmission

Abstract

A differential is provided comprising: a ring gear (1); a housing comprising a first section (21) and a second section (22) of identical construction, wherein the first section (21) and the second section (22) are arranged coaxially with the ring gear (1), the first section (21) and the second section (22) are detachably mounted together with the ring gear (1), the first section (21) and the second section (22) are each splined to the ring gear (1) to implement a power transmission connection, and the first section (21) and the second section (22) define a mounting space (2s); and a bevel gear assembly (3) housed and mounted in the mounting space (2s). Therefore, the housing can be obtained with sufficient precision without additional final machining, and the housing can achieve dynamic equilibrium in the operation of the differential.In addition, the differential's design facilitates disassembly and assembly, torque transmission, and simplifies manufacturing and assembly processes. Furthermore, a vehicle transmission that incorporates the differential is provided.

Description

Technical field

[0001] The present application relates to the field of wheel differentials for vehicles and in particular a differential and a vehicle transmission comprising the differential. background

[0002] In the prior art, a differential in a vehicle's transmission mechanism is typically used to transmit torque from the vehicle's transmission to the wheels and to allow the wheels to rotate at different speeds when cornering. A bevel gear differential is a typical differential used in a vehicle's transmission mechanism.

[0003] In a prior art bevel gear differential, an integrated housing is used. In this case, the design of the integrated housing is complex, leading to complex designs of the manufacturing tools for casting and the like, as well as a cumbersome casting process. Furthermore, in one aspect of the manufacturing process for such an integrated housing, a blank is typically first produced by sand casting and then machined to obtain the integrated housing. Since the precision of sand casting is low, the blank is prone to defects such as shrinkage porosity and voids, making it necessary to subject the cast blank (especially the parts intended to be fitted with other components) to final machining.To ensure the dynamic equilibrium of such an integrated housing in the differential's machining process, special tools are also typically required to perform the final machining of the blank.

[0004] In another prior art bevel gear differential, a split housing is used. In this case, the split housing is permanently attached to the ring gear, which serves as the input element of the differential, by means such as welding, which leads to damage to the differential when it is disassembled. Brief description

[0005] The present application was developed with regard to the aforementioned shortcomings of the prior art. One objective of the present application is to provide a differential that has a relatively simple design and can be assembled and disassembled non-destructively. Furthermore, a housing for such a differential can be manufactured with sufficient precision without additional final machining, and the housing can achieve dynamic equilibrium during the differential's operation. Another objective of the present application is to provide a vehicle transmission comprising the differential.

[0006] To solve the aforementioned problems, the following technical solutions are used in this application.

[0007] The present application provides a differential comprising: a bevel gear; a housing comprising a first section and a second section having the same construction, wherein the first section and the second section are arranged coaxially with the ring gear, the first section and the second section are detachably mounted together with the ring gear, the first section and the second section are each in splined connection with the ring gear to implement a power transmission connection, and the first section and the second section define a mounting space; and a bevel gear assembly which is housed and mounted in the assembly space, wherein the bevel gear assembly comprises a transmission shaft, a first pair of bevel gears and a second pair of bevel gears, wherein the transmission shaft extends along a radial direction of the ring gear and is in power transmission connection with the ring gear, the two bevel gears of the first pair of bevel gears are mounted on the transmission shaft and are rotatable about the transmission shaft, and each bevel gear of the second pair of bevel gears meshes with a corresponding bevel gear of the first pair of bevel gears.

[0008] In an alternative solution, the ring gear is designed with at least one annular groove, the differential includes at least one retaining ring, and the at least one retaining ring is mounted on the at least one annular groove to axially limit the first section and the second section.

[0009] In another alternative solution, the ring gear is designed with two mounting grooves and two axial ends of the transmission shaft are each inserted into the two mounting grooves, thus enabling the ring gear to directly drive the transmission shaft to rotation.

[0010] In another alternative solution, the ring gear has a ring-shaped form, is provided on an inner circumferential surface of the ring gear with a first internal spline and a second internal spline, and the first internal spline and the second internal spline are arranged next to each other and spaced apart in an axial direction of the ring gear. If the first section is provided with a first external spline, the first external spline and the first internal spline mesh; if the second section is provided with a second external spline, the second external spline and the second internal spline mesh.

[0011] In another alternative solution, the ring gear has a central projection, and the central projection is located axially between the first internal spline and the second internal spline. The ring gear is formed with a first annular groove, the differential further includes a first retaining ring, the first retaining ring is mounted in the first annular groove, and the first retaining ring and the central projection for axially limiting the first external spline are located on two axial sides of the first external spline. If the ring gear is designed with a second annular groove, the differential further includes a second retaining ring, the second retaining ring is mounted in the second annular groove, and the second retaining ring and the central projection for axially limiting the second external spline are located on two axial sides of the second external spline.

[0012] In another alternative solution, the central projection is designed with two mounting grooves, two end sections of the transmission shaft form mounting sections corresponding to the mounting grooves, and the mounting sections are inserted into the corresponding mounting grooves.

[0013] In another alternative solution, the mounting groove is a U-shaped groove, the mounting groove comprises two planar side walls that are parallel to each other, the mounting section is formed with an adjacent section that is positively connected to and in contact with the two side walls, and the side walls interact with the adjacent section to establish a force transmission connection.

[0014] In another alternative solution, a plane of symmetry is present that is perpendicular to the axial direction of the ring gear, and the differential as a whole has a construction that is symmetrical with respect to the plane of symmetry.

[0015] In another alternative solution, the first section and the second section are machined using the same fine blanking device.

[0016] The present application further provides a vehicle transmission comprising the differential according to one of the aforementioned technical solutions.

[0017] By utilizing the aforementioned technical solutions, the present application provides a differential comprising a ring gear, a housing, and a bevel gear assembly. Typically, the ring gear can receive torque from outside the differential, and the bevel gear assembly can transmit torque to the outside of the differential. The housing comprises a first section and a second section of identical construction, and the first and second sections are arranged coaxially with the ring gear. The first and second sections are detachably mounted together with the ring gear, and each section engages with the ring gear in a splined connection, thereby achieving a power transmission connection between the housing and the ring gear.Additionally, the first and second sections define an assembly space, and the bevel gear assembly is housed and mounted within this assembly space. The bevel gear assembly comprises two meshing pairs of bevel gears. Bevel gears of one pair are mounted on the transmission shaft such that they are rotatable with the transmission shaft about the central axis of the ring gear, and the bevel gears of this pair are rotatable about the transmission shaft. The other pair of bevel gears meshes with the first pair to transmit torque, for example, via a half-shaft to the wheels of a vehicle. The present application further provides a vehicle transmission comprising the aforementioned differential.

[0018] Since the differential housing of the present application uses a split design and the two housing sections have the same construction, the two sections can be formed using a fine blanking process. Thus, the housing can be obtained with sufficient precision without additional final machining, and the mass distribution of the two housing sections can be symmetrical and uniform without additional final machining, thereby enabling the housing to achieve dynamic equilibrium during the differential's operation.Furthermore, the housing and the ring gear are detachably connected, and the two parts are engaged with the ring gear by a splined connection in such a way that the differential can be disassembled without damaging the housing and ring gear structure. Compared to cases where welding, bolted connections, and the like are used, a higher torque can be transmitted. Moreover, the design of the differential in the present application is relatively simple, which facilitates the simplification of the manufacturing and assembly processes. Additionally, the vehicle transmission incorporating the aforementioned differential exhibits the same advantageous effects. Brief description of the drawings Fig. Figure 1 is a schematic cross-sectional view showing a differential according to an embodiment of the present application, with section lines omitted. Fig. 2 is a schematic exploded view showing the differential in Fig. 1 shows. Fig. Figure 3 is a schematic perspective view showing the differential in Fig. 1 shows. Fig. Figure 4 is a schematic perspective view of a first retaining ring of the differential in Fig. 1. Detailed description

[0019] Specific embodiments of the present application are described in detail below with reference to the accompanying drawings of the description. It is understood that these specific descriptions are intended only to teach those skilled in the art how the present application can be implemented, and are neither intended to exhaustively present all possible implementations of the present application nor to limit the scope of protection of the present application.

[0020] In the present application, ‘power transmission connection’ refers to a connection between two components that is capable of transmitting torque, including a direct connection and an indirect connection.

[0021] Unless otherwise specified, in this application “axial”, “radial” and “circumferential direction” refer to the axial, radial and circumferential directions of the ring gear respectively.

[0022] The construction of a differential according to an embodiment of the present application is described below with reference to the accompanying drawings of the description.

[0023] As in Fig. 1 and Fig. As shown in Figure 2, a differential according to an embodiment of the present application comprises a ring gear 1, a housing (a first section 21 and a second section 22), a bevel gear assembly 3, two retaining rings 41, 42 and two bearings 51, 52, all assembled. Fig. As shown in Figure 1, the differential as a whole has a construction which, with respect to a plane of symmetry P (in Fig. 1 (marked with a single dashed line) is symmetrical, and the plane of symmetry P is perpendicular to an axial direction A. Symmetry here means that the entire constructive design of the differential is essentially symmetrical, but not necessarily completely and precisely symmetrical. For example, in this embodiment, the outer teeth of the ring gear 1 may have a shape that is asymmetrical with respect to the plane of symmetry P. As an example, the one in Fig. 2 shown ring gear 1 a helical gear.

[0024] In this embodiment, the ring gear 1 can, for example, be in power transmission connection with an output gear of an output shaft of a vehicle transmission in such a way that torque from outside the differential can be transmitted to the ring gear 1. Here, the ring gear 1 can, for example, be an outer ring gear. As in Fig. As shown in Figure 1, the ring gear 1 has a ring-shaped form and the ring gear 1 is arranged coaxially to the housing and a second pair of bevel gears 33a, 33b of the bevel gear group 3.

[0025] As in Fig. As shown in Figures 1-3, the ring gear 1 is provided with a first internal spline 11, a second internal spline 12, and a central projection 13 on its inner circumferential surface. The first internal spline 11, the second internal spline 12, and the central projection 13 are arranged side by side in the axial direction A. The central projection 13 is located in the axial direction A between the first internal spline 11 and the second internal spline 12 such that the first internal spline 11 and the second internal spline 12 are spaced apart in the axial direction A by the central projection 13.

[0026] As in Fig. As shown in Figures 1-3, the ring gear 1 is further formed with a first annular groove 1c1 and a second annular groove 1c2. With respect to the first internal spline 11, the first annular groove 1c1 is located on a side opposite the side on which the central projection 13 is located (the left side of the Fig. 1), and the first annular groove 1c1 is configured for inserting and mounting the first retaining ring 41. With respect to the second internal spline 12, the second annular groove 1c2 is located on one side opposite the side on which the central projection 13 is located (the right side of Fig. 1), and the second ring groove 1 c2 is used for inserting and mounting the second retaining ring 42.

[0027] As in Fig. 2 and Fig. As shown in Figure 3, the central projection 13 is formed with two mounting grooves 13c, which correspond to the mounting sections 31p of a gear shaft 31 of the bevel gear assembly 3. The two mounting grooves 13c are spaced apart by a central angle of 180 degrees and have the same shape. As shown in Fig. As shown in Figure 3, each mounting groove 13c is a U-shaped groove and its cross-section has a square shape, corresponding to the mounting section 31p of the transmission shaft 31. The circumferential sidewall surfaces of the mounting groove 13c are designed as mutually parallel planes in order to bear against and interact with the mounting section 31p of the transmission shaft 31.

[0028] In this embodiment, the housing is as shown in Fig. 1 and Fig. Figure 2 shows a rotating body with a central axis. The cross-sectional shape of the rotating body at each axial position is annular, and the housing as a whole is rotatable about the central axis. In particular, the housing comprises the first section 21 and the second section 22, which have the same construction. The first section 21 and the second section 22 are arranged coaxially with the ring gear 1 and symmetrically with respect to the plane of symmetry P. The first section 21 and the second section 22 are detachably mounted together with the ring gear 1 such that the housing is in power transmission connection with the ring gear 1. Furthermore, the first section 21 and the second section 22 define a mounting space 2s.

[0029] As in Fig. 1 and Fig. As shown in Figure 2, the first section 21 comprises a first external spline 211, a first conical section 212, and a first bearing seat 213, all formed in one piece. The first external spline 211 meshes with the first internal spline 11 of the ring gear 1. A large-diameter end of the first conical section 212 is connected to a root of the first external spline 211, and a small-diameter end of the first conical section 212 is connected to the first bearing seat 213. The second section 22 comprises a second external spline 221, a second conical section 222, and a second bearing seat 223, all formed in one piece. The second external spline 221 meshes with the second internal spline 12 of the ring gear 1.A large-diameter end of the second conical section 222 is connected to a root of the second external spline 221, and a small-diameter end of the second conical section 222 is connected to the second bearing seat 223. Furthermore, the first conical section 212 is formed with a plurality of first weight-reducing holes 212h, distributed circumferentially and spaced apart from one another, and the second conical section 222 is formed with a plurality of second weight-reducing holes 222h, also distributed circumferentially and spaced apart from one another, to reduce the weight of the housing. Since the first section 21 and the second section 22 have the same construction, they can be fine-blanked using the same fine-blanking device.Furthermore, the housing can be obtained with sufficient precision without the need for additional final machining of the first section 21 and the second section 22, and it is made possible for the housing to achieve a dynamic equilibrium in the working process of the differential.

[0030] In this embodiment, the bevel gear group 3 is as shown in Fig. 1 and Fig. 2 shown, housed and mounted in the assembly space 2s, which is defined by the first section 21 and the second section 22. The bevel gear group 3 comprises the transmission shaft 31, a first pair of bevel gears (a first bevel gear 32a and a second bevel gear 32b) and a second pair of bevel gears (a third bevel gear 33a and a fourth bevel gear 33b).

[0031] As in Fig. As shown in Figure 1, the transmission shaft 31 extends along a radial direction R of the ring gear 1 and is in power transmission connection with the ring gear 1. Specifically, the transmission shaft 31 is detachably inserted into the mounting grooves 13c of the central projection 13 of the ring gear 1 along the radial direction R. The transmission shaft 31 is configured for mounting the first pair of bevel gears such that the first bevel gear 32a and the second bevel gear 32b of the first pair of bevel gears can rotate together with the transmission shaft 31 and the housing as a whole, and simultaneously, the first bevel gear 32a and the second bevel gear 32b can also rotate independently of each other around the transmission shaft 31. Furthermore, two end sections of the transmission shaft 31 form the mounting sections 31p corresponding to the mounting grooves 13c, and the mounting sections 31p are inserted into the corresponding mounting grooves 13c.The mounting section 31p can be designed with an adjacent section that is positively connected to and in contact with the two circumferential sidewall surfaces of the mounting groove 13c. The two circumferential sidewall surfaces interact with the adjacent section to implement a power transmission connection between the ring gear 2 and the transmission shaft 31. To allow the transmission shaft 31 and the ring gear 1 to rotate together without this resulting in relative rotation with respect to the ring gear 1 during the interaction between the mounting sections 31p and the mounting grooves 13c, the cross-section of the mounting section 31p can be square.By utilizing the interaction between the mounting grooves 13c of the ring gear 1 and the mounting sections 31p, on the one hand a contact area between the transmission shaft 31 and the ring gear 1 is large enough to facilitate the transmission of a larger torque; on the other hand, relative rotation between the transmission shaft 31 and the ring gear 1 is prevented.

[0032] As in Fig. 1 and Fig. As shown in Figure 2, the first bevel gear 32a and the second bevel gear 32b of the first pair of bevel gears are mounted on the transmission shaft 31 and are rotatable around the transmission shaft 31. The third bevel gear 33a of the second pair of bevel gears meshes with both the first bevel gear 32a and the second bevel gear 32b of the first pair of bevel gears, and the fourth bevel gear 33b of the second pair of bevel gears meshes with both the first bevel gear 32a and the second bevel gear 32b of the first pair of bevel gears. The third bevel gear 33a and the fourth bevel gear 33b are both designed with an internal spline that engages with an external spline of a half-shaft in such a way that the differential can transmit a torque to the half-shaft via the bevel gear assembly 3.

[0033] In this embodiment, the first retaining ring 41 and the second retaining ring 42, as shown in Fig. 1, Fig. 2 and Fig. Figure 4 shows the same construction, and both are C-shaped. The first retaining ring 41 is mounted in the first annular groove 1c1 and projects radially inward relative to the first annular groove 1c1. The first retaining ring 41 and the central projection 13 are located on two axial sides of the first external spline 211 to axially limit its engagement. The second retaining ring 42 is mounted in the second annular groove 1c2 and projects radially inward relative to the second annular groove 1c2. The second retaining ring 42 and the central projection 13 are located on two axial sides of the second external spline 221 to axially limit its engagement.

[0034] In this embodiment, the first bearing 51 and the second bearing 52 can be, as in Fig. 1 and Fig.Figure 2 shows both bearings as single-row tapered roller bearings. An inner ring of the first bearing 51 is slid onto the first bearing seat 213, and an inner ring of the second bearing 52 is slid onto the second bearing seat 223. The two bearings 51 and 52 are mounted on the housing such that their respective inner rings are attached to an axial end section of the housing. The two bearings 51 and 52 are configured to support the differential housing so that the differential can rotate and operate properly.

[0035] The specific technical solutions of the present application have been described in detail above; however, the present application is not limited to the technical solutions mentioned above, and supplementary explanations follow below. i. The aforementioned split housing has a relatively simple design and can be formed not only by a fine blanking device but also by processes such as precision forging, thereby improving the machining accuracy of the housing and the strength of the components. Since the first section 21 and the second section 22 have the same design and are arranged symmetrically, the housing composed of the first section 21 and the second section 22 can achieve dynamic equilibrium in the gearbox's operation even without additional machining. Furthermore, if a fine blanking device is used for machining, the first section 21 and the second section 22 can be machined using the same fine blanking device, thus significantly reducing manufacturing costs. ii. Since the housing and the ring gear 1 are connected via splined connections in the aforementioned embodiments, and the interaction between the design of the ring gear 1 itself (the central projection 13) and the retaining rings 41, 42 is used to axially limit the first section 21 and the second section 22, the design of the differential is not only relatively simple, but also allows for disassembly and assembly of the differential without damaging its structure, thereby reducing the maintenance costs of the differential, etc.

[0036] It is understood that, in an alternative solution, the internal spline of the ring gear 1 can extend continuously along the axial direction A of the ring gear 1 (instead of forming a discontinuous design as described in the embodiments mentioned above), and the central projection 13 of the ring gear 1 can be omitted. In this case, the first section 21 and the second section 22 of the housing can abut each other in the axial direction A, and the interaction with the retaining rings 41, 42 is used to axially limit the first section 21 and the second section 22, thereby achieving the same effects as in the embodiments mentioned above.

[0037] It is understood that in another alternative solution, the internal spline of the ring gear 1 can extend continuously along the axial direction A of the ring gear 1 (instead of forming a discontinuous design as described in the embodiments mentioned above), and the central projection 13 of the ring gear 1 can be omitted. Furthermore, one of the retaining rings 41, 42 can be formed integrally with the ring gear 1. That is, the ring gear 1 is formed with a limiting projection for axial limitation. This limiting projection interacts with the other retaining ring 41, 42 to axially limit the first section 21 and the second section 22, thereby achieving the same effects as in the embodiments mentioned above.

[0038] iii. It is understood that, compared to the case where sections of the split housing are joined by multiple bolts, the use of multiple bolts can be eliminated, resulting in fewer parts and faster assembly. The radial space required for mounting bolts to the housing can be reduced or eliminated to provide a more compact size for the differential and reduce material costs, thus facilitating a reduction in the differential's weight and simplifying its installation and use in applications such as a gearbox. Compared to bolted or welded connections, a splined connection offers greater strength, which is advantageous for the differential to meet requirements for transmitting higher torque.

[0039] iv. Due to the alignment between the mounting sections 31p of the transmission shaft 31 and the mounting grooves 13c of the ring gear 1, the transmission shaft 31 and the ring gear 1 are in direct power transmission connection without the need for a connection via the housing. This results in a very low load on the housing, thus reducing the requirements for its strength. In this way, the differential housing serves only as a support and can therefore have a thinner wall thickness to reduce its volume and weight.

[0040] v. It is understood that the first section 21 and the second section 22, after all components of the differential have been installed in their place, are able to provide axial limits for the transmission shaft 31.

[0041] vi. The present application also provides a vehicle transmission which may include the differential described in the specific embodiments mentioned above, and a power source of the vehicle may transmit torque to the wheels via the differential. LIST OF REFERENCE MARKS 1 ring gear; 1c1 first ring groove; 1 c2 second ring groove; 11 first internal spline; 12 second internal spline teeth; 13 central lead; 13c Mounting groove; 21 first section; 211 first external spline toothing; 212 first conical section; 212h first weight-reducing hole; 213 first warehouse location; 22 second section; 221 second external spline toothing; 222 second conical section; 222h second weight-reducing hole; 223 second warehouse location; 2s assembly room; 3 bevel gear group; 31 Gear shaft; 31p assembly section; 32a first bevel gear; 32b second bevel gear; 33a third bevel gear; 33b fourth bevel gear; 41 first retaining ring; 42 second retaining ring; 51 first camp; 52 second camp; P symmetry plane; A axial direction; R radial direction.

Claims

[1] Differential, encompassing: a bevel gear (1); a housing comprising a first section (21) and a second section (22) having the same construction, wherein the first section (21) and the second section (22) are arranged coaxially with the ring gear (1), the first section (21) and the second section (22) are detachably mounted together with the ring gear (1), the first section (21) and the second section (22) are each in splined connection with the ring gear (1) for the purpose of implementing a power transmission connection, and the first section (21) and the second section (22) define a mounting space (2s); and a bevel gear assembly (3) which is housed and mounted in the assembly space (2s), wherein the bevel gear assembly (3) comprises a transmission shaft (31), a first pair of bevel gears (32a, 32b) and a second pair of bevel gears (33a, 33b), wherein the transmission shaft (31) extends along a radial direction (R) of the ring gear (1) and is in power transmission connection with the ring gear (1), the two bevel gears of the first pair of bevel gears (32a, 32b) are mounted on the transmission shaft (31) and are rotatable about the transmission shaft (31), and each bevel gear of the second pair of bevel gears (33a, 33b) meshes with a corresponding bevel gear of the first pair of bevel gears (32a, 32b). [2] Differential according to claim 1, wherein the ring gear (1) is formed with at least one annular groove, the differential comprises at least one retaining ring and the at least one retaining ring is mounted on the at least one annular groove for axially limiting the first section (21) and the second section (22). [3] Differential according to claim 1 or 2, wherein the ring gear (1) is formed with two mounting grooves (13c) and two axial ends of the transmission shaft (31) are each inserted into the two mounting grooves (13c), thereby enabling the ring gear (1) to directly drive the transmission shaft (31) to rotation. [4] Differential according to one of claims 1 to 3, wherein the ring gear (1) has an annular shape, the ring gear (1) is provided on an inner circumferential surface thereof with a first internal spline (11) and a second internal spline (12), and the first internal spline (11) and the second internal spline (12) are arranged next to each other and spaced apart in an axial direction (A) of the ring gear (1), the first section (21) is provided with a first external spline (211), the first external spline (211) and the first internal spline (11) mesh, the second section (22) is provided with a second external spline (221), and the second external spline (221) and the second internal spline (12) mesh. [5] Differential according to claim 4, wherein the ring gear (1) has a central projection (13) and the central projection (13) is located in the axial direction (A) between the first internal spline (11) and the second internal spline (12), the ring gear (1) is formed with a first annular groove (1c1), the differential further comprises a first retaining ring (41), the retaining ring (41) is mounted in the first annular groove (1c1) and the first retaining ring (41) and the central projection (13) are located on two axial sides of the first external spline (211) for axially limiting the first external spline (211), and the ring gear (1) is further formed with a second annular groove (1c2), the differential further comprises a second retaining ring (42),the retaining ring (42) is mounted in the second annular groove (1c2) and the second retaining ring (42) and the central projection (13) for axially limiting the second external spline (221) are located on two axial sides of the second external spline (221). [6] Differential according to claim 5, wherein the central projection (13) is formed with two mounting grooves (13c), two end sections of the transmission shaft (31) form mounting sections (31p) corresponding to the mounting grooves (13c) and the mounting sections (31p) are inserted into corresponding mounting grooves (13c). [7] Differential according to claim 6, wherein the mounting groove (13c) is a U-shaped groove, the mounting groove (13c) comprises two planar side walls that are parallel to each other, the mounting section (31p) is formed with an adjacent section that is positively connected to and in contact with the two side walls, and the side walls interact with the adjacent section to establish a force transmission connection. [8] Differential according to any one of claims 1 to 7, wherein a plane of symmetry (P) is provided which is perpendicular to the axial direction (A) of the ring gear (1) and the differential as a whole has a construction which is symmetrical with respect to the plane of symmetry (P). [9] Differential according to any one of claims 1 to 8, wherein the first part (21) and the second part (22) are formed using the same fine blanking device for machining. [10] Vehicle transmission comprising the differential according to any one of claims 1 to 9.

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