Bearing assembly for drive assembly of vehicle

Abstract

The present disclosure relates to a bearing assembly for a drive assembly of a vehicle. The bearing assembly includes a transfer case having a plurality of wheelset elements for torque transmission and an output shaft. Wherein one of the wheel set elements is connected to the output shaft for introducing an axial force. The bearing assembly also includes a stationary member and a first support section for transferring an axial force in a first axial direction from the one wheelset element to the stationary member. The bearing assembly also includes a second support section for transferring an axial force in a second axial direction opposite the first axial direction from the one wheelset element to the stationary component. The first support section and the second support section are arranged on different axial sides of the one wheelset element. The invention further relates to a vehicle with the bearing assembly.

Description

Technical Field

[0001] This disclosure relates to a bearing assembly for a drive assembly in a vehicle. Furthermore, this disclosure also relates to a vehicle having a drive assembly including such a bearing assembly. Background Technology

[0002] Transfer cases are known for compensating for relative rotation between two driven shafts. In some configurations, elements of the transfer case (e.g., planetary gear set elements) can be connected to one of the driven shafts in a rotationally resistant manner to transmit torque. It is also known that all axial forces acting on such elements are transmitted to a stationary component via this single driven shaft by means of one or more axial locking mechanisms. Summary of the Invention

[0003] This disclosure relates, in its first aspect, to a bearing assembly for a drive system of a vehicle. The vehicle may be, for example, a passenger car, a bus, or a work machinery. In the case of work machinery, it may be, for example, agricultural machinery, construction machinery, or a commercial vehicle. An example of agricultural machinery is a tractor. An example of construction machinery is a wheel loader. Examples of commercial vehicles are municipal vehicles, dump trucks, and concrete mixer trucks. Furthermore, the vehicle may be a driven trailer coupled to a tractor during operation. The vehicle has a transfer case. The transfer case has multiple wheel elements for torque transmission and an output shaft. The wheel elements for torque transmission can be configured to provide a mechanical action connection between the different elements of the transfer case.

[0004] If two elements are mechanically coupled, they are directly or indirectly coupled to each other, such that the movement of one element causes a reaction in the other. Mechanical coupling can be established, for example, through frictional engagement or form-fitting. Mechanical coupling can correspond to the tooth engagement between corresponding gears of the two elements. Additional elements, such as one or more spur gear stages, may exist between the elements. A permanently anti-rotational coupling is a connection in which two elements are rigidly coupled to each other. These elements can be constructed as independent, anti-rotational coupling components or as a single unit. Anti-rotational coupling between two elements can also be established by switching elements (e.g., clutches or brakes). Anti-rotational coupling is established when the switching element is actuated. The anti-rotational coupling is disengaged when the switching element is no longer actuated.

[0005] One of the gear set elements is connected to the output shaft to introduce axial force. This gear set element can be, for example, a planetary gear set element, such as a sun gear, planet carrier, or ring gear. This gear set element can be connected to the output shaft to introduce axial force. This gear set element can be anti-rotatably connected to the output shaft to transmit torque to the output shaft. The anti-rotatable connection can be constructed in a releasable manner. The anti-rotatable connection can be configured to allow the output shaft to move in at least one axial direction. The anti-rotatable connection can be, for example, constructed as a form-locking connection or a friction-locking connection.

[0006] In one design, the output shaft can be configured to drive a first driving element of the vehicle. The transfer case may also have an additional output shaft. This additional output shaft can be configured to drive a second driving element of the vehicle, opposite to the first driving element. For example, the first driving element may be the right-hand wheel of the vehicle, and the second driving element may be the left-hand wheel of the vehicle. Both opposing first and second driving elements of the vehicle can be driven simultaneously via the output shaft.

[0007] A transfer case can be configured to transmit driving torque from a vehicle's drive source to two output shafts. For example, the two output shafts can be the two drive shafts of a driven axle of the vehicle. The drive source can be a traction engine (e.g., an electric motor), or alternatively, an internal combustion engine. The transfer case can have an input shaft to receive the driving torque from the drive source. The transfer case can also be configured to compensate for relative rotation or speed differences between the two output shafts, rather than driving the two output shafts.

[0008] The bearing assembly includes a stationary component. This stationary component can be, for example, a housing in which the transfer case, wheel assembly elements, and / or output shaft are wholly or partially housed. The stationary component can have multiple housing sections. For example, the stationary component can have two housing halves in the axial direction.

[0009] The bearing assembly has a first support section for transmitting axial force in a first axial direction from this wheelset element to a stationary component. The first support section can be configured to transmit axial force only in the first axial direction. The first support section can be configured not to transmit axial force in a second axial direction opposite to the first axial direction. The first support section can be configured to limit relative movement of this wheelset element relative to the stationary component in the first axial direction. The first support section can be configured to allow relative movement of this wheelset element relative to the stationary component in the second axial direction.

[0010] The first support section can be integrally constructed with the stationary component, or it can be disposed and mounted on the stationary component independently of it. Examples of an integral design for the first support section include stops, steps, or contact surfaces respectively constructed on the output shaft-facing surface of the stationary component. For example, the first support section itself can be a housing section fixedly or detachably mounted on a housing. Examples of an independent design for the first support section include retaining rings, retaining discs, locking rings, and locating rings. The first support section can here be configured as a separate component that contacts the stationary component on one axial side and a portion of the output shaft on another axial side to transmit axial force in the first axial direction. The first support section constructed as a retaining ring can, for example, be inserted into a groove in the output shaft-facing surface of the stationary component. The first support section can be constructed as a component located between the stationary component and a portion of the output shaft in the first axial direction. The first support section constructed in this way can, for example, be an annular component. The annular component can, for example, contact a support surface at the output shaft on one axial side and another support surface at the stationary component on the other axial side.

[0011] The bearing assembly includes a second support section for transmitting axial force in a second axial direction, opposite to the first axial direction, from one wheelset element to a stationary component. The second support section can be configured to transmit axial force only in the second axial direction. The second support section can be configured not to transmit axial force in the first axial direction. The second support section can be configured to restrict relative movement of the wheelset element relative to the stationary component in the second axial direction. The second support section can be configured to allow free relative movement of the wheelset element relative to the stationary component in the second axial direction. For example, the second support section can bring the axial face of the wheelset element or a component connected thereto abut against the axial face of the stationary component to transmit axial force in the second axial direction. This abutment can be direct or indirect. As an example of direct abutment, the axial face of the wheelset element or a component connected thereto can slidably contact the axial face of the stationary component. As an example of indirect abutment, the axial face of the wheelset element or a component connected thereto can contact the axial face of another component (e.g., another wheelset element). Then, another component (e.g., its other axial face) can come into contact with the axial face of the stationary component. The second support section can be integrally constructed with the stationary component, or it can be constructed independently of the stationary component and mounted thereon. For example, the second support section can be an annular stepped section integrally constructed on the inner circumferential surface of the stationary component.

[0012] The design of the first support section described above also applies to the second support section. The relationships described for the design of the first support section with respect to the first axial direction can be similarly transferred to the design of the second support section with respect to the second axial direction. The second support section may be designed the same as or differently from the first support section. For example, one support section may be constructed as a retaining ring that contacts a thrust bearing. Another support section may, for example, be constructed as a housing section that accommodates another thrust bearing.

[0013] The first support section and the second support section are arranged on different axial sides of this wheelset element. The first support section may be spaced apart from this wheelset element, for example, in a first axial direction. The second support section may be spaced apart from this wheelset element, for example, in a second axial direction.

[0014] According to a first aspect of this disclosure, a bearing assembly is provided in which the axial force of a wheelset element is supported by either a first support section or a second support section, depending on the force direction. In an assembly where a single support section supports the axial force of a wheelset element from both sides, the vibration excitation from both sides is introduced into a stationary member. The unilateral axial support for each support section according to the first aspect allows movement of the wheelset element in one axial direction. Here, the stationary member bears the axial force in the first axial direction on one axial side and the axial force in the second axial direction on the other axial side. Thus, two different, direction-dependent paths for supporting the axial force are provided, which improves the vibration damping characteristics of the transfer case. Furthermore, the transfer case can be designed such that at least one tooth of the wheelset element intervenes in the path of the axial force in at least one axial direction. For example, the wheelset element can mesh with and transmit the axial force via helical teeth to another wheelset element supported in at least one axial direction. Thus, a portion of the axial force of the wheelset element can be supported via the helical teeth and the other wheelset element. The helical teeth can act as vibration dampers due to their frictional effect. This will further improve the vibration damping characteristics of the transfer case. Additionally, any thrust bearing that does not support axial force or only supports axial force on one side can be configured with a transition fit or clearance fit instead of a press fit. This facilitates the installation of the transfer case.

[0015] In one embodiment, the output shaft has a thrust bearing for introducing axial forces in a first axial direction into a first support section. The thrust bearing is movable relative to the first support section in a second axial direction. For example, the thrust bearing can be accommodated in a stationary component with a clearance fit and supported only on one side. This effectively decouples vibration excitation in the first axial direction from vibration excitation in the second axial direction. The thrust bearing can be configured to bear axial forces only on one side in the axial direction. The thrust bearing can also be configured to bear radial forces or be configured as a purely unilateral thrust bearing. Examples of such thrust bearings include axially fixed ball bearings, skew ball bearings, tapered ball bearings, single-row cylindrical roller bearings, tapered ball bearings, axial rolling bearings, and axial sliding bearings. In another design, the thrust bearing itself can bear axial forces in both axial directions. Examples of such thrust bearings include deep groove ball bearings and double-row cylindrical roller bearings. In this case, the thrust bearing and the first support section are configured to still allow the thrust bearing to move in the second axial direction, for example by not providing support on the second axial side.

[0016] In one embodiment, the bearing assembly has a preload element for preloading the thrust bearing in a first axial direction, thereby suppressing bearing creep and extending bearing life. The preload element can be configured to preload a radially outer section of the thrust bearing. This allows it to bear support forces over a larger diameter, thus reducing bearing load. In one embodiment, the preload element is configured as a wave spring. In another embodiment, the preload element is configured as a disc spring. In both cases, the preload effect is provided in a particularly simple and effective manner.

[0017] In one embodiment, the transfer case has a coupling section for coupling one wheelset element to the output shaft. A bearing assembly has a thrust bearing for transmitting axial force in a second axial direction from the coupling section to another wheelset element. A second support section can be configured to directly or indirectly contact another wheelset element to transmit axial force in the second axial direction. The coupling section can extend at least partially in the radial direction and overlap with one wheelset element. Another wheelset element can intervene in the force flow between the second support section and the coupling section.

[0018] In one embodiment, the bearing assembly has an additional thrust bearing for transmitting axial forces in the second axial direction from the additional wheelset element to the second support section. The additional wheelset element may, for example, be configured to contact the coupling section in the first axial direction and the second support section in the second axial direction. This integrates the additional wheelset element into the force flow from the wheelset element to the stationary component, improving vibration damping characteristics.

[0019] In one embodiment, the transfer case has a first planetary gear set and a second planetary gear set. Each planetary gear set has a first element, a second element, and a third element. Torque can be introduced into the transfer case via the first element of the first planetary gear set. The third element of the first planetary gear set is permanently anti-rotationally connected to the first element of the second planetary gear set. The second element of the second planetary gear set is permanently anti-rotationally fixed to a stationary component. One output shaft is permanently anti-rotationally connected to the second element of the first planetary gear set. The other output shaft is permanently anti-rotationally connected to the third element of the second planetary gear set. For example, one output shaft may be the other output shaft described above, and the other output shaft may be the output shaft described above. The third element of the second planetary gear set then corresponds to one gear set element that supports its axial force in a direction-dependent manner via a bearing assembly, and the second element of the first planetary gear set corresponds to the other gear set element. Furthermore, the aforementioned coupling section can mechanically couple the third element of the second planetary gear set to the output shaft.

[0020] The first, second, and third elements can be, for example, the sun gear, planet carrier, or ring gear of their respective planetary gear sets. Each planetary gear set can be a positive or negative planetary gear set. Each planetary gear set can have planet gears rotatably supported on their respective planet carriers. The planet gears can mesh with both the sun gear and the ring gear of their respective planetary gear sets. In this transfer case connection, the two planetary gear sets can be arranged at the same axial height or sequentially in the axial direction of the bearing assembly. This provides a compact transfer case in either the axial or radial direction.

[0021] In one embodiment, the first element of each of the two planetary gear sets is configured as a sun gear, the second element of each of the two planetary gear sets is configured as a planet carrier, and the third element of each of the two planetary gear sets is configured as a ring gear. Furthermore, a coupling shaft can be provided, which forms both the ring gear of the first planetary gear set and the sun gear of the second planetary gear set. This design results in the transfer case possessing the aforementioned advantages, thereby reducing complexity. In an alternative embodiment, the first element of each of the two planetary gear sets is configured as a sun gear, the second element is configured as a ring gear, and the third element is configured as a planet carrier.

[0022] In one embodiment, a second element of the first planetary gear set is rotatably connected to another output shaft. A third element of the second planetary gear set is mechanically coupled to the output shaft. The third element of the second planetary gear set may be coupled to the output shaft, for example, via the aforementioned coupling section. The second element of the first planetary gear set may have a torque transmission section for transmitting torque to the other output shaft. The torque transmission section may, for example, be configured as a hub. The coupling section may, for example, be configured as a radially extending component that radially connects the third element of the second planetary gear set to the output shaft in a rotatable manner.

[0023] The second aspect of this disclosure relates to a vehicle with a bearing assembly according to the first aspect. Various advantages and other features are described in the first aspect, wherein the design of the first aspect also constitutes the design of the second aspect, and vice versa. Attached Figure Description

[0024] Figure 1 A vehicle with a transfer case and bearing assembly according to an embodiment of the present disclosure is shown;

[0025] Figure 2 Schematic illustration Figure 1 The diagram shows the connection of the transfer case of the vehicle shown.

[0026] Figure 3 Schematic illustration based on Figure 2 The connecting transfer case and the bearing assembly according to an embodiment of this disclosure. Detailed Implementation

[0027] Figure 1 Vehicle 100 is shown. Vehicle 100 is provided with a drive assembly 1. Drive assembly 1 has a transfer case 12, which has the following reference... Figure 3 The first output shaft 16 and the second output shaft 18 are described in detail. Currently, the first output shaft 16 and the second output shaft 18 are used to drive the left or right wheel of the vehicle 100. The drive assembly 1 also includes a traction engine (not shown) for driving the vehicle 100 by introducing torque into the transfer case 12.

[0028] Figure 2 It shows Figure 3 The general connection concept of the transfer case 12 used in the illustrated embodiment (described in detail below). The transfer case 12 is a transfer case with two planetary gear sets. From Figure 2As can be seen, the transfer case 12 includes a first planetary gear set 121 with a first element 121.1, a second element 121.2, and a third element 121.3. Furthermore, the transfer case 12 includes a second planetary gear set 122 with a first element 122.1, a second element 122.2, and a third element 122.3. Torque from a traction engine (not shown) can be introduced into the transfer case 12 via the first element 121.1 of the planetary gear set 121. For this purpose, the input shaft 14 is mechanically connected to the first element 121.1 of the planetary gear set 121 (currently permanently anti-rotationally connected). The third element 121.3 of the planetary gear set 121 is permanently anti-rotationally connected to the first element 122.1 of the second planetary gear set 122 (currently via a coupling shaft). The second element 122.2 of the second planetary gear set 122 is permanently fixed to a stationary component (currently housing 20) against relative rotation. The first output shaft 16 is mechanically connected to the second element 121.2 of the planetary gear set 121 (currently a permanent anti-relative rotation connection). The second output shaft 18 is mechanically connected to the third element 122.3 of the second planetary gear set 122 (currently a permanent anti-relative rotation connection).

[0029] Figure 3 Schematic illustration with according to Figure 2 The bearing assembly of the drive assembly 1 of the connected transfer case 12. For clarity, only half of the cross-sectional view of the transfer case 12 along its centerline is shown. Figure 3 In this embodiment, the first elements 121.1 and 122.1 of the first planetary gear set 121 and the second planetary gear set 122 are both configured as sun gears. The second elements 121.2 and 122.2 of the first planetary gear set 121 and the second planetary gear set 122 are both configured as planet carriers. The third elements 121.3 and 122.3 of the first planetary gear set 121 and the second planetary gear set 122 are both configured as ring gears. Figure 3 In this embodiment, the first planetary gear set 121 and the second planetary gear set 122 are radially nested. This means that the first planetary gear set 121 is radially completely arranged within the second planetary gear set 122. The third element 121.3 of the first planetary gear set 121 is integrally constructed with the first element 122.1 of the second planetary gear set 122 (in the current construction, a sun gear ring). Figure 3 In one embodiment, the ring gear 122.3 of the second planetary gear set 122 forms a gear set element, while the planet carrier 121.2 of the first planetary gear set 121 forms another gear set element.

[0030] Transfer case 12, first output shaft 16, and second output shaft 18 are housed within housing 20. Second output shaft 18 extends away from planetary gear sets 121, 122 in a first axial direction 50. First output shaft 16 extends away from planetary gear sets 121, 122 in a second axial direction 60. Currently, second output shaft 18 constitutes one output shaft, while first output shaft 16 constitutes another. In another embodiment, first output shaft 16 constitutes one output shaft, while second output shaft 18 constitutes another.

[0031] The planet carrier 121.2 of the first planetary gear set 121 is rotatably supported on the first housing section 21 by means of the first thrust bearing 23. The first housing section 21 is a detachable section of the housing 20 and is currently fastened to the housing 20 via a flange. The first housing section 21 is arranged on the first side of the housing 20 and the transfer case 12.

[0032] The second output shaft 18 is rotatably supported in the second housing section 22 by a second thrust bearing 24. The second thrust bearing 24 is constructed as a ball bearing and is fixed not only to the second output shaft 18 but also to the second housing section 22 in the first axial direction 50. The second housing section 22 is a removable section of the housing 20 and is currently fastened to the housing 20 via a flange. The second housing section 22 is arranged on the second side of the housing 20 and the transfer case 12. Currently, the second thrust bearing 24 is supported on the second output shaft 18 only by its radially inward portion in the second axial direction 60. The radially outward portion of the second thrust bearing 24 is fixed in the first axial direction 50 by a first support section 32 as described below. The radially outward portion of the second thrust bearing 24 is supported in a movable manner in the second axial direction 60 by a preload element 33. The preload element 33 preloads the second thrust bearing 24 in the direction of the first axial direction 50. This allows the bearing to withstand the supporting force over a large diameter, thereby reducing the bearing load. Currently, the preload element 33 is configured as a wave spring ( Figure 3 (Shown only schematically). In another embodiment, the preload element is configured as a disc spring.

[0033] The transfer case 12 also has an input shaft 14 for introducing torque into the transfer case 12. Currently, the input shaft 14 is constructed as a hollow shaft through which the first output shaft 16 passes. The transfer case 12 also includes a radial bearing 26 that rotatably supports the first output shaft 16 in a second output shaft 18 via a planetary carrier hub 30. The transfer case 12 has an additional radial bearing 27 that rotatably supports the second output shaft 18 in a second housing section 22. The radial bearings 26 and 27 are configured as sliding bearings capable of transmitting radial forces and allowing axial movement.

[0034] The planet carrier 121.2 of the first planetary gear set 121 is connected to the first output shaft 16 in a rotationally inert manner via a planet carrier hub 30 (currently used as a torque transmission section). The planet carrier hub 30 has a tooth profile 34 for introducing torque into the first output shaft 16. The tooth profile 34 is the torque transmission section and forms a rotationally inert connection between the planet carrier 121.2 and the first output shaft 16.

[0035] The ring gear 122.3 of the second planetary gear set 122 is permanently anti-rotationally connected to the second output shaft 18 via a coupling section 38. The coupling section 38 is also configured to transmit axial force from the ring gear 122.3 to the second output shaft. Currently, the coupling section 38 has a cap-like construction and extends radially outward from the second output shaft 18 to the ring gear 122.3 of the second planetary gear set 122. A section of the coupling section 38 also extends in the axial direction and partially surrounds the first output shaft 16 and the planet carrier hub 30. Currently, the coupling section 38 is rotatably supported on the planet carrier 121.2 of the first planetary gear set 121 by a third thrust bearing 25. The third thrust bearing 25 is currently configured as a needle roller bearing. The third thrust bearing 25 is configured to transmit axial force in the second axial direction 60.

[0036] Currently, the first support section 32 is configured as a retaining ring. The first support section 32 is placed in a groove 31. The groove 31 is constructed on the radially inward surface of the housing 20 (currently the second housing section 22). The first support section 32 is axially fixed in the groove 31 relative to the housing 20. The surface of the first support section 32 pointing towards the second axial direction 60 faces the second thrust bearing 24. The first support section 32 is configured to withstand the axial force of the second thrust bearing 24 in the first axial direction 50.

[0037] When an axial force is applied to the ring gear 122.3 of the second planetary gear set 122 in the first axial direction 50, this axial force is transmitted to the housing 20 via the coupling section 38, the second output shaft 18, the second thrust bearing 24, and the first support section 32. Therefore, for the axial force in the first axial direction 50, a force flow is provided from the ring gear 122.3 of the second planetary gear set 122 to the housing 20. When an axial force is applied to the ring gear 122.3 of the second planetary gear set 122 in the second axial direction 60, the second thrust bearing 24 can be lifted from the first support section 32, allowing the ring gear 122.3 to move in the first axial direction 50. Therefore, the aforementioned force flow is not provided in the second axial direction 60, and the ring gear 122.3 can move freely in the second axial direction 60 with respect to the first support section 32.

[0038] The second support section 36 is constructed as an annular section integral with the first housing section 21 of the housing 20. Currently, the second support section 36 is in contact with the first thrust bearing 23 to withstand its axial force in the second axial direction 60 and transmit this axial force to the first housing section 21 and thus to the housing 20. When the ring gear 122.3 of the second planetary gear set 122 is subjected to an axial force in the second axial direction 60, this axial force is transmitted to the housing 20 via the coupling section 38, the third thrust bearing 25, the planet carrier 121.2 of the first planetary gear set 121, the second thrust bearing 23, and the second support section 36. Therefore, for an axial force in the second axial direction 60, a force flow is provided from the ring gear 122.3 of the second planetary gear set 122 to the housing 20. When the ring gear 122.3 is subjected to an axial force in the first axial direction 50, the third thrust bearing 25 can be lifted from the coupling section 38 or the planet carrier 121.2. Alternatively or additionally, the first thrust bearing 23 can be lifted from the planetary carrier 121.2 or the second support section 36. In any case, the gear ring 122.3 can move in the first axial direction 50. Therefore, the aforementioned force flow is not provided in the first axial direction 50, and the gear ring 122.3 can move freely in the first axial direction 50 with respect to the second support section 36. Therefore, the gear ring 122.3 is axially supported in the manner described above via the first support section 32 and the second support section 36, depending on the direction. Thus, two different, direction-dependent paths are provided to support the axial force, and these two paths are guided through different axial sides of the gear ring 122.3. Therefore, the vibration damping characteristics of the gear ring 122.3 and the transfer case 12 are improved.

[0039] List of reference numerals

[0040] 1 driver components

[0041] 12-way drive

[0042] 14 input axes

[0043] 16 and 18 output shafts

[0044] 20 stationary parts

[0045] Shell sections 21 and 22

[0046] 23, 24, 25 thrust bearings

[0047] 26 and 27 radial bearings

[0048] 30 planetary carrier hub

[0049] 31 slots

[0050] 32 First Support Section

[0051] 33 Preload Components

[0052] 34 tooth profile

[0053] 36 Second Support Section

[0054] 38 Coupled Sections

[0055] 100 vehicles

[0056] 121 First Planetary Gear Set

[0057] 122 Second Planetary Gear Set

[0058] 121.1, 122.1 First Component

[0059] 121.2, 122.2 Second Components

[0060] 121.3, 122.3 Third Component

[0061] 50 First axial direction

[0062] 60 Second Axial Direction

Claims

1. Bearing assembly for a drive assembly (1) of a vehicle (100), the drive assembly having a transfer case (12) with a plurality of wheel set elements (121.1, 121.2, 121.3, 122.1, 122.2, 122.3) for torque transmission and an output shaft (18), wherein, one of the wheelset elements (122.3) is connected to the output shaft (18) for introduction of an axial force; a stationary component (20, 21, 22); a first support section (32) for transmitting an axial force in a first axial direction (50) from this one wheelset element (122.3) to the stationary component (20, 21, 22); and a second support section (36) for transmitting an axial force in a second axial direction (60) opposite the first axial direction (50) from this one wheelset element (122.3) to the stationary component (20, 21, 22), wherein the first support section (32) and the second support section (36) are arranged on different axial sides of this one wheelset element (122.3).

2. The bearing assembly of claim 1, wherein, The output shaft (18) has a thrust bearing (24) for introduction of an axial force in the first axial direction (50) into the first support section (32), and wherein the thrust bearing (24) is movable relative to the first support section (32) in the second axial direction (60).

3. The bearing assembly of claim 1 or 2, wherein, The bearing assembly has a pretensioning element (33) for pretensioning the thrust bearing (24) in the first axial direction (50).

4. A bearing assembly according to claim 2 or 3, wherein, The pretensioning element (33) is configured as a wave spring.

5. A bearing assembly according to any one of the preceding claims, characterised in that, The transfer (12) has a coupling section (38) for coupling this one wheelset element (122.3) to the output shaft (18), wherein the bearing assembly comprises a thrust bearing (25) for transmitting an axial force in the second axial direction (60) from the coupling section (38) to a further wheelset element (121.2) thereof.

6. The bearing assembly of claim 5, wherein, The bearing assembly has a further thrust bearing (23) for transmitting an axial force in the second axial direction (60) from the further wheelset element (121.2) to the second support section (36). The bearing assembly has a pretensioning element (33) for pretensioning the thrust bearing (24) in the first axial direction (50). The pretensioning element (33) is configured as a wave spring. The transfer (12) has a coupling section (38) for coupling this one wheelset element (122.3) to the output shaft (18), wherein the bearing assembly comprises a thrust bearing (25) for transmitting an axial force in the second axial direction (60) from the coupling section (38) to a further wheelset element (121.2) thereof. The bearing assembly has a further thrust bearing (23) for transmitting an axial force in the second axial direction (60) from the further wheelset element (121.2) to the second support section (36).

7. A bearing assembly according to any one of the preceding claims, characterised in that, The transfer (12) has the output shaft (18), a further output shaft (16), a first planetary gear set (121) and a second planetary gear set (122), wherein both planetary gear sets (121, 122) have a first element (121.1, 122.1), a second element (121.2, 122.2) and a third element (121.3, 122.3), wherein torque can be introduced into the transfer (12) via the first element (121.1) of the first planetary gear set (121), the third element of the first planetary gear set (121) is permanently rotationally fixed connected with the first element (122.1) of the second planetary gear set (122), the second element (122.2) of the second planetary gear set (122) is permanently rotationally fixed arranged on the stationary part (20), wherein one output shaft (16; 18) is permanently rotationally fixed connected with the second element (121.2) of the first planetary gear set (121) and wherein the other output shaft (18; 16) is permanently rotationally fixed connected with the third element (122.3) of the second planetary gear set (122).

8. The bearing assembly of claim 7, wherein, The first elements (121.1, 122.1) of both planetary gear sets (121, 122) are configured as sun gears, the second elements (121.2, 122.2) of both planetary gear sets (121, 122) are configured as planet carriers and the third elements (121.3, 122.3) of both planetary gear sets (121, 122) are configured as ring gears.

9. The bearing assembly of claim 8, wherein, The second element (121.2) of the first planetary gear set (121) is rotationally fixed connected with the further output shaft (16) and the third element (122.3) of the second planetary gear set (122) is mechanically coupled with the output shaft (18).

10. Vehicle (100) having a bearing assembly according to any one of the preceding claims.

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