Lockable differential gear

Abstract

A differential gear (1) for transmitting torque to axles (2) of a motor vehicle (3), comprising a differential basket (4), two output shafts (5, 6) having a common axis of rotation (7), and a multi-plate clutch (8) having at least one inner plate (9) and at least one outer plate (10) for switchably connecting a first output shaft (5) to the differential basket (4).

Description

[Technical Field]

[0001] The present invention relates to a lockable differential for transmitting torque to the axles of a motor vehicle. [Background technology]

[0002] Typically, torque is transmitted from the drive unit via an input shaft (e.g., a longitudinal shaft) to two output shafts via a differential gear. In the differential gear, the introduced torque is transmitted from a differential basket to gear wheels rotatably arranged in the differential basket and interconnected via gear teeth. The gear wheels are connected to the output shafts. At least one output shaft may be connected to the differential basket via a clutch. On the one hand, the differential gear may be used to compensate for differences in the speed of the wheels connected to the output shafts. On the other hand, the clutch may be used to distribute torque differentially to the wheels, if necessary.

[0003] When the clutch is disengaged, both wheels are driven by the same torque through the differential, even if they are rotating at different speeds, such as when negotiating a curve. When rotating at the same speed, the wheels connected to the differential's output shafts do not move relative to each other, resulting in no power loss or wastage. When one wheel comes to a complete stop and the clutch is disengaged, the other wheel rotates at twice the speed of the differential basket. This can occur, for example, when setting off, when one of the two wheels loses traction with the ground, such as on mud or snow. This wheel then "spins," and both wheels no longer transmit forward drive torque. Even when negotiating a curve at high speed, the inside wheel can become so unloaded that it spins.

[0004] A lockable differential can prevent this: the balancing effect is either prevented by rigidly connecting the two output shafts (full lock) or reduced by friction applied via a clutch. In the latter case, part of the power is transferred to the drive wheels, and the rest is converted into heat in the differential or clutch. When the lock is engaged (full lock), the wheels rotate at the same speed and torque is distributed between them according to grip. If full lock is used on roads or other good surfaces, the driveline can be distorted and damaged, as the different path lengths of the wheels in curves can only be absorbed by tire slippage.

[0005] A differential gear with a shiftable clutch is known from US Pat. No. 5,098,360.

[0006] A differential gear with a multi-plate clutch and a dog clutch is known from US Patent Application Publication No. 2020 / 0292045. The multi-plate clutch can be actuated by an actuation device having a ramp device. A bevel gear connected to an output shaft is designed as an internal plate carrier. The bevel gear is radially supported by the output shaft. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] U.S. Patent No. 5,098,360 [Patent Document 2] US Patent Application Publication No. 2020 / 0292045 Summary of the Invention [Problem to be solved by the invention]

[0008] There is a constant need to improve motor vehicle components. In particular, these components should be lighter, smaller, and as inexpensive to manufacture as possible. Additionally, compact designs should provide long component life.

[0009] The object of the present invention is to at least partially solve the problems cited with reference to the prior art, in particular to present a differential gear with a further reduced weight and size. [Means for solving the problem]

[0010] A differential gear having the features according to claim 1 contributes to solving these problems. Further advantageous developments are the subject of the dependent claims. The features individually recited in the claims can be combined with one another in a technically useful manner and can be supplemented by explanations from the description and / or details from the drawings, which lead to further variant designs of the invention.

[0011] A (lockable) differential gear for transmitting torque to the axles of a motor vehicle is presented. The differential gear comprises at least one differential basket, two output shafts with a common rotation axis, and a multi-plate clutch with at least one inner plate and at least one outer plate for switchably connecting a first output shaft to the differential basket. The first output shaft extends along the rotation axis and forms a positive connection with a bevel gear at least in the circumferential direction via a first outer peripheral surface of the first output shaft and an inner peripheral surface of the bevel gear. A portion of the second outer peripheral surface of the bevel gear is designed as an inner plate carrier, and the differential basket is designed as an outer plate carrier. The bevel gear is supported at least in the radial direction by a contact surface of the differential basket.

[0012] Reference is made to the description of the known differential gears mentioned at the beginning. Typically, the bevel gear is arranged on the output shaft and is radially supported via the output shaft and then via a (roller) bearing of the output shaft, for example by a housing or other component of the differential. If this support is not feasible from a design point of view, the bevel gear and also the output shaft must be radially supported elsewhere.

[0013] The differential gear presented here is particularly advantageous due to the characteristic support of the bevel gear by the differential basket, for which purpose contact surfaces are provided, via which the bevel gear is supported by the differential basket at least in the radial direction.

[0014] The support is provided by a special design of the contact surfaces or of the support elements contacting the contact surfaces. The support elements are, for example, arranged between the bevel gears and the differential cage and provide the radial support. The bevel gears thus contact the contact surfaces of the differential cage or the support elements via an opposing surface. The support elements contact the contact surfaces of the differential cage via an opposing surface. The support elements may also form (additional) contact surfaces for the bevel gears.

[0015] The contact via the contact surfaces (arranged on the differential basket and / or on the support elements) allows for an (at least largely) frictionless connection between the differential basket and the bevel gear, which is in particular rotatable, i.e. rotatable in the circumferential direction, so that during operation of the differential gear, the bevel gear can rotate as damage-free as possible between the differential basket and the bevel gear.

[0016] The support between the differential basket and the bevel gear is provided in particular by contact with cylindrical surfaces that enable the rotatable connection and the support in the radial direction, in particular that extend parallel to the axis of rotation, in particular that are arranged on at least the bevel gear and the differential basket, and possibly on the additional support element.

[0017] The contact surfaces on the differential basket and / or the support elements are preferably at least 100 N / mm 2 , preferably 150N / mm 2 Designed for surface pressure (fatigue resistant).

[0018] The contact surfaces on the differential basket and / or on the support elements and / or the counter surfaces on the bevel gears or the support elements that contact the respective contact surfaces can be designed, for example, with a sliding coating. The support elements can be designed, for example, as sliding rings. In this way, the contact surfaces and / or the respective counter surfaces can be formed, for example, with a coating having special sliding properties.

[0019] The contact surfaces and the counter surfaces on the differential basket, bevel gears, and, if applicable, support elements form a rotatable connection in the radial direction, in particular for at least one component of the differential basket and the bevel gears, preferably for both components. In each case, the bevel gears are rotatable relative to the differential basket. If necessary, the support elements may rotate relative to the bevel gears and / or the differential basket.

[0020] In particular, the support element is arranged in contact with the differential basket in a rotationally fixed manner by press-fitting, so that relative rotation of the support element with respect to the differential basket is not possible, and thus relative rotation occurs between the contact surface on the support element and the counter surface on the bevel gear.

[0021] The support element is instead designed as a multi-part element, such as a roller bearing.

[0022] In particular, a multi-plate clutch has a plurality of output plates and a plurality of inner plates. However, the clutch can also be designed as a friction clutch with a pressure plate, a clutch disc, and a counter plate. The pressure plate and the counter plate are connected in a rotationally fixed manner, for example, to the bevel gear (as an inner plate) or to the differential basket (as an outer plate). The pressure plate is arranged displaceably along the axial direction, so that the clutch disc is arranged between the pressure plate and the counter plate. The clutch is not limited to a specific embodiment. However, preferably, a partial torque transmission from the input shaft to the output shaft via the clutch should be performed. The following description applies in particular to the multi-plate clutch, but also to other (friction) clutches as well.

[0023] The multi-plate clutch can be actuated in particular by a (known) actuation device that can be assigned to the differential gear, via which the plates can be displaced along the rotation axis and form an adjustable frictional connection with one another.

[0024] For example, EP 0 414 086 A1 describes an actuation device with two expansion discs supported in the axial direction by balls. Circumferential rotation of the expansion discs relative to one another leads to axial displacement of one of the expansion discs because the balls are arranged on ramps. Both expansion discs are arranged in contact with a first output shaft, and actuation forces are absorbed in the axial direction on one side by one disc fixed to the first output shaft and on the other side by the differential basket.

[0025] In particular, the output shafts each extend towards the differential basket and are positively connected to a bevel gear at least in the circumferential direction thereat, and the output shafts are arranged coaxially with one another such that the differential basket and the output shafts have a common axis of rotation.

[0026] The bevel gears are rotatably arranged relative to the output shafts within the differential basket, where the output shafts or their bevel gears are further interconnected via gear wheels.

[0027] The first output shaft extends along the rotation axis and forms a positive connection with the bevel gear at least in the circumferential direction via a first outer circumferential surface of the first output shaft and an inner circumferential surface of the bevel gear, for example by a spline connection. A portion of a second outer circumferential surface of the bevel gear is designed as an inner plate carrier, and the differential basket is designed as an outer plate carrier. At least one inner plate is positively connected to the inner plate carrier in the circumferential direction. At least one outer plate is positively connected to the outer plate carrier in the circumferential direction. The inner and outer plates are alternately arranged along the axial direction (extending along the rotation axis). By displacing the plates along the axial direction, a frictional connection can be formed between the plates so that the first output shaft can be adjustably coupled to the differential basket.

[0028] In particular, the contact surface is located along the axis of rotation between the bevel teeth of the bevel gear and the portion.

[0029] In particular, the bevel gears are supported by the contact surfaces via support elements. In this case, the plates are supported by the differential basket via the support elements in an axial direction extending along the rotation axis. In particular, the contact surfaces of the support elements and the differential basket provide support in the axial direction and are designed so that relative rotation between these surfaces along the circumferential direction is as friction- and damage-free as possible. Alternatively, the support elements can also be designed to rotate (almost) exclusively relative to the bevel gears. In particular, the support elements are thus arranged in contact with the differential basket by an interference / press fit and are connected to the differential basket in a rotationally fixed manner. The bevel gears are then arranged to rotate relative to the support elements.

[0030] In particular, the bevel gear is supported by the contact surface of the differential cage via the support element, in which case the bevel gear is supported in the radial direction by the support element (or by the contact surface of the support element) together with the cylindrically designed support surface (the opposing surface) of the second outer circumferential surface of the bevel gear.

[0031] In particular, the portion of the bevel gear (formed as an internal plate carrier) is arranged along the rotation axis between the bevel teeth and the contact surface. In particular, the actuating device actuates the plate through the support element. For this purpose, for example, an axially extending opening can be provided in the support element, through which an actuating element of the actuating device extends.

[0032] In particular, the contact surfaces of the differential basket and / or the support element are cylindrical.

[0033] In particular, the contact surfaces of the differential cages are arranged radially outside the maximum extensions of the bevel gears, which are the longest extensions of the bevel gears in the radial direction, so that the bevel gears can be inserted into the differential baskets along the axial direction for assembly of the differential gears.

[0034] In particular, the first outer peripheral surface and the inner peripheral surface of the bevel gear form an overlap region along the rotation axis having two overlap region portions arranged adjacent to each other along the rotation axis, and at least one channel is formed in the bevel gear in the first overlap region portion extending from the inner peripheral surface to the portion of the second outer peripheral surface. In particular, a plurality of channels are arranged in the first overlap region portion, and these channels are arranged offset from each other along the axial direction and / or the circumferential direction.

[0035] At least one channel serves in particular to supply fluid to said clutch, said fluid being used in particular to cool said clutch.

[0036] In particular, the positive connection, such as a spline connection, between the first output shaft and the bevel gear is arranged only in the second overlapping region.

[0037] In particular, the first overlapping area portion has a larger diameter than the second overlapping area portion.

[0038] In particular, the first overlapping area is used to guide the fluid along the first output shaft to the at least one channel. For this purpose, a clearance area is required between the output shaft and the inner circumferential surface of the bevel gear. However, this clearance area reduces the area required to support the bevel gear in the radial direction. In particular, support is provided by the contact surface of the differential basket to compensate for this reduction in support in the area of ​​the first overlapping area.

[0039] In particular, only the first of the output shafts can be connected to the differential basket via a clutch, and in particular, the second output shaft with the bevel gear connected thereto is arranged in the differential basket without a clutch, i.e., without a clutch, so that the second output shaft cannot be locked to the differential basket itself.

[0040] In particular, the differential gear has two output shafts, whereby only one output shaft can be connected to the differential basket in a torque-transmitting manner via a clutch. The differential gear thus has only one clutch, whereby the two output shafts are interconnected via the bevel gears of the differential gear. The differential basket forms a drive shaft, via which the differential gear is connected to a drive unit.

[0041] There is further provided a drive mechanism for a motor vehicle, comprising at least a drive unit and the above-mentioned differential gear, which is provided to transmit torque from the drive unit to two wheels of an axle, and the torque of the drive unit can be introduced into the differential gear via the differential basket and transmitted to the respective wheels via respective output shafts.

[0042] In particular, the differential basket of the differential gear is designed as a drive shaft, via which the differential gear can be or is connected to a drive unit.

[0043] The above description regarding the differential gear applies equally to the drive mechanism, and vice versa.

[0044] Also provided is a motor vehicle having at least one of the above-described drive mechanisms and a plurality of wheels, the differential gear preferably being disposed on the rear axle of the motor vehicle.

[0045] The use of indefinite articles ("a", "an"), particularly in the claims and the specification containing them, is to be interpreted literally and not as a numeral, and thus a term or element introduced therein is to be understood as being present in at least one quantity, but particularly as possibly being present in plural.

[0046] It should be noted that the numerical values ​​used herein (such as "first," "second," etc.) primarily (or exclusively) serve to distinguish between multiple similar objects, dimensions, or steps, i.e., do not necessarily specify a dependency and / or sequence of these objects, variables, or steps relative to one another. Where a dependency and / or sequence is required, this will be explicitly stated herein or will become apparent to one skilled in the art upon review of the specifically described embodiment. To the extent that there is a plurality (at least one) of elements, a description of one of these elements may, but is not required to, apply to all or many of these elements as well.

[0047] The present invention and technical environment will be described in more detail below with reference to the accompanying drawings. It should be noted that the present invention is not limited by the illustrated design examples. In particular, unless explicitly indicated otherwise, partial aspects of the matters illustrated in the drawings may be extracted and combined with other facts and findings from this specification. In particular, it should be noted that the illustrated drawings and, in particular, the size relationships are shown only diagrammatically. [Brief explanation of the drawings]

[0048] [Figure 1] 1 is a motor vehicle having a drive mechanism and actuation gear shown in a side cross-sectional view. [Figure 2] 2 is an exploded perspective view of the differential gear portion of FIG. 1. [Figure 3] 1 is a plan view of a motor vehicle having a drive mechanism.

[0049] Figure 1 shows a cross-sectional side view of a motor vehicle 3 having a drive mechanism 31 and a differential gear 1. Figure 2 shows an exploded perspective view of a portion of the differential gear 1 of Figure 1. Figures 1 to 3 are both described below.

[0050] The motor vehicle 3 has a drive mechanism 31 and a plurality of wheels 33. The drive mechanism 31 includes a drive unit 32 and a differential gear 1. The differential gear 1 is provided to transmit torque from the drive unit 32 to two wheels 33 on an axle 2. The torque of the drive unit 32 can be introduced into the differential gear 1 via a drive shaft 34 and a differential basket 4, and can be transferred to the respective wheels 33 via output shafts 5 and 6. The differential gear 1 is disposed adjacent to the rear axle 2 of the motor vehicle 3.

[0051] The differential 1 has two output shafts 5, 6, whereby only the first output shaft 5 can be connected to the differential basket 4 via a multi-plate clutch 8 for torque transmission. The differential 1 thus has only one multi-plate clutch 8, and the two output shafts 5, 6 are interconnected via the bevel gear differential 1. The differential basket 4 forms or is connected to a drive shaft 34, via which (further) drive shaft 34 the differential 1 is connected to a drive unit 32.

[0052] The differential gear 1 comprises a differential basket 4, two output shafts 5, 6 having a common rotation axis 7, and a multi-plate clutch 8 having a plurality of inner plates 9 and a plurality of outer plates 10 for switchably connecting the first output shaft 5 to the differential basket 4. The first output shaft 5 extends along the rotation axis 7 and forms a positive connection 15 with a bevel gear 13 via a first outer peripheral surface 11 of the first output shaft 5 and an inner peripheral surface 12 of the bevel gear 13 at least in a circumferential direction 14. A portion 16 of a second outer peripheral surface 17 of the bevel gear 13 is designed as an inner plate carrier 18, and the differential basket 4 is designed as an outer plate carrier 19. The bevel gear 13 is supported by the differential basket 4 via a contact surface 20 of the differential basket 4 at least in a radial direction 21.

[0053] Support is provided by a support element 23 in contact with the contact surface 20. The support element 23 is arranged between the bevel gear 13 and the differential cage 4 in the radial direction 21. The bevel gear 13 contacts the contact surface 20 with the support element 23 via an opposing surface. The support element 23 contacts the contact surface 20 with the differential cage 4 via an opposing surface. The support element 23 is connected to the differential cage 4 in a rotationally fixed manner by an interference / press fit.

[0054] The contact via the contact surfaces 20 (which contact the differential cage 4 and the support elements 23) allows for a connection between the differential cage 4 and the bevel gear 13 which is (at least largely) rotatable without friction in the circumferential direction 14. This means that the bevel gear 13 can rotate relative to the differential cage 4 substantially without damage during operation of the differential gear 1.

[0055] Support between the differential cage 4 and the bevel gear 13 is provided by cylindrical contact surfaces 20, 25, which together allow a rotatable connection and support in the radial direction 21. The cylindrical surfaces 20, 25 extend parallel to the axis of rotation 7. The cylindrical surfaces 20, 25 are arranged in contact with the bevel gear 13 and the differential cage 4 as well as with an additional support element 23.

[0056] The multi-plate clutch 8 can be actuated by a (known) actuating device 35. The actuating device 35 is arranged along the rotation axis 7 adjacent to the multi-plate clutch 8, tangentially to the first output shaft 5, so that the multi-plate clutch 8 is arranged between the actuating device 35 and the bevel gear 13. Via the actuating device 35, the plates 9, 10 can be displaced along the rotation axis 7 and form an adjustable frictional connection with one another.

[0057] The actuation device 35 comprises two expansion discs supported in the axial direction 24 via balls. Rotation of the expansion discs relative to one another in the circumferential direction 14 leads to a displacement of one of the expansion discs in the axial direction 24, as the balls are arranged on ramps. Both expansion discs are arranged in contact with the first output shaft 5, and the actuation forces are absorbed on one side by one disc fixed to the first output shaft 5 in the axial direction 24, and on the other side by the differential basket 4.

[0058] The output shafts 5, 6 each extend towards the differential basket 4, where they are each positively connected to a bevel gear 13 at least in the circumferential direction 14. The output shafts 5, 6 are arranged coaxially with one another so that the differential basket 4 and the output shafts 5, 6 have a common axis of rotation 7. The bevel gear 13 is rotatably arranged together with the output shafts 5, 6 in the differential basket 4. Within the differential basket 4, the output shafts 5, 6 or their bevel gears 13 are interconnected via further gears or bevel gears 13.

[0059] The first output shaft 5 extends along the rotation axis 7 and forms a positive connection 15 with the bevel gear 13 at least in the circumferential direction 14 by a spline connection via a first outer peripheral surface 11 of the first output shaft 5 and an inner peripheral surface 12 of the bevel gear 13. A portion 16 of a second outer peripheral surface 17 of the bevel gear 13 is designed as an inner plate carrier 18, and the differential basket 4 is designed as an outer plate carrier 19. The inner plate 9 is positively connected to the inner plate carrier 18 in the circumferential direction 14. The outer plate 10 is positively connected to the outer plate carrier 19 in the circumferential direction 14. The inner and outer plates 9 and 10 are alternately arranged along an axial direction 24 (extending along the rotation axis 7). By displacing the plates 9, 10 along the axial direction 24, a friction connection can be formed between the plates 9, 10 so that the first output shaft 5 can be adjustably coupled to the differential basket 4.

[0060] The contact surface 20 of the differential basket 4 and the contact surface 20 of the support element 23 are arranged along the rotation axis 7 between the bevel teeth 22 of the bevel gear 13 and the portion 16 .

[0061] The bevel gear 13 is supported by the contact surface 20 via a support element 23. In this case, the plates 9, 10 are supported by the differential cage 4 via the support element 23 in an axial direction 24 extending along the rotation axis 7. The support element 23 is connected to the differential cage 4 in a rotationally fixed manner by means of an interference fit / press fit. Therefore, there is no relative rotation between the output plate 10 and the support element 23. The bevel gear 13 is supported by the support element 23 (or by the contact surface 20 of the support element 23) in the radial direction 21 together with a cylindrically designed support surface 25 (opposite surface) of the second outer peripheral surface 17 of the bevel gear 13.

[0062] The contact surface 20 of the differential cage 4 is arranged outside the maximum extension 26 of the bevel gear 13 in the radial direction 21, which is the longest extension 26 of the bevel gear 13 in the radial direction 21, so that the bevel gear 13 can be inserted into the differential basket 4 along the axial direction 24 for assembly of the differential gear 1. This arrangement of the bevel gear 13 forms a press fit between the support member 23 and the differential cage 4.

[0063] The first outer peripheral surface 11 of the output shaft 5 and the inner peripheral surface 12 of the bevel gear 13 form an overlap region 27 along the rotation axis 27, having two overlap region portions 28, 29 arranged adjacent to each other along the rotation axis 7, and in the first overlap region portion 28, a plurality of channels 30 are formed in the bevel gear 13, and the channels 30 extend from the inner peripheral surface 12 to the portion 16 of the second outer peripheral surface 17. In the first overlap region portion 28, the plurality of channels 30 are arranged, each offset along the axial direction 24 and along the circumferential direction 14.

[0064] The channel 30 serves to supply fluid to the multi-plate clutch 8. The positive connection 15 between the first output shaft 5 and the bevel gear 13, which in this case is a spline connection, is arranged only in the second overlap area 29. The first overlap area 28 has a diameter 36 that is appreciably larger than the second overlap area 29.

[0065] The first overlap area 28 is used to direct fluid into the channel 30 along the first output shaft 5. This requires an open area / gap between the first output shaft 5 and the inner peripheral surface 12 of the bevel gear 13. However, this open area reduces the area required to support the bevel gear 13 in the radial direction 21. To compensate for this reduced support in the area of ​​the first overlap area 28, support is provided by the contact surface 20 of the differential basket 4. [Explanation of symbols]

[0066] 1 differential gear 2 axles 3 Motor vehicles 4 Differential basket 5 First output shaft 6 Second output shaft 7 Rotation Axis 8 Multi-plate clutch 9 Inner Plate 10 outer plate 11 first outer peripheral surface 12 Inner surface 13 Bevel gear 14 Circumferential direction 15 Connections 16 parts 17 Second outer surface 18 Internal Plate Carrier 19 External Plate Carrier 20 Contact surface 21 Radial 22 bevel teeth 23 Supporting Elements 24 axial direction 25 Support surface 26 Extension 27 Overlapping area 28 First overlapping area 29 Second overlapping area 30 channels 31 Drive Assembly 32 Drive unit 33 Wheels 34 Drive shaft 35 Actuator 36 diameter

Claims

1. A differential gear (1) for transmitting torque to an axle (2) of a motor vehicle (3), comprising: a differential basket (4); two output shafts (5, 6) having a common rotation axis (7); a multi-plate clutch (8) having at least one inner plate (9) and at least one outer plate (10) for switchably connecting a first output shaft (5) to the differential basket (4); Equipped with the first output shaft (5) extends along the rotation axis (7) and forms a form connection (15) with a bevel gear (13) at least in a circumferential direction (14) via a first outer peripheral surface (11) of the first output shaft (5) and an inner peripheral surface (12) of the bevel gear (13); a portion (16) of the second outer peripheral surface (17) of the bevel gear (13) is designed as an inner plate carrier (18), and the differential basket (4) is designed as an outer plate carrier (19); The bevel gear (13) is supported at least in the radial direction (21) by a contact surface (20) of the differential basket (4), the first outer peripheral surface (11) and the inner peripheral surface (12) form an overlapping region (27) along the rotation axis (7) having two overlapping region portions (28, 29) arranged adjacent to each other along the rotation axis (7); At least one channel (30) is formed in the bevel gear (13) in the first overlap region (28); the channel (30) extends from the inner circumferential surface (12) to the portion (16) of the second outer circumferential surface (17); A differential gear (1) in which a plurality of channels are arranged in the first overlapping region, and these channels are arranged offset from one another along an axial direction (24) extending along the rotation axis (7).

2. 2. The differential gear (1) according to claim 1, wherein the contact surface (20) is disposed along the rotation axis (7) between the bevel teeth (22) of the bevel gear (13) and the portion (16).

3. The bevel gear (13) is supported by the contact surface (20) via a support element (23), 3. The differential gear (1) according to claim 2, wherein the plates (9, 10) are supported by the differential basket (4) via the support elements (23) in an axial direction (24) extending along the rotation axis (7).

4. 4. The differential gear (1) according to claim 3, wherein the support element (23) is arranged in contact with the differential basket (4) in a rotationally fixed manner by press-fitting.

5. The bevel gear (13) is supported by the contact surface (20) via a support element (23), 5. The differential gear (1) according to claim 1, wherein the bevel gear (13) is supported in the radial direction (21) by the support element (23) via a cylindrically formed support surface (25) of the second outer peripheral surface (17).

6. 2. The differential gear (1) according to claim 1, wherein the portion (16) is disposed along the rotation axis (7) between the bevel teeth (22) of the bevel gear (13) and the contact surface (20).

7. The differential gear (1) according to any one of claims 1 to 6, wherein the contact surface (20) is cylindrical.

8. the contact surface (20) is located radially (21) outside the maximum extension (26) of the bevel gear (13); 8. The differential gear (1) according to any one of claims 1 to 7, wherein the maximum extension (26) is the longest extension (26) of the bevel gear (13) in the radial direction (21).

9. 2. The differential gear (1) according to claim 1, wherein the positive connection (15) between the first output shaft (5) and the bevel gear (13) is arranged only in the second overlapping region (29).

10. 10. The differential gear (1) according to any one of claims 1 to 9, wherein only the first output shaft (5) of the output shafts (5, 6) can be connected to the differential basket (4) via a multi-plate clutch (8).

11. A differential gear (1) comprising at least a drive unit (32) and the differential gear (1) according to any one of claims 1 to 10, The differential gear (1) is provided to transmit torque from the drive unit to two wheels (33) of the axle (2), A drive mechanism (31) for an automobile vehicle (3) in which the torque of the drive unit (32) can be introduced into the differential gear (1) via the differential basket (4) and transferred to each wheel (33) via each output shaft (5, 6).

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