TORQUE TRANSMISSION ASSEMBLY FOR A MOTOR VEHICLE

Abstract

The present invention relates to a torque transmission assembly for a motor vehicle comprising a two-stage spur gear, having an input shaft for introducing the torque of a drive unit and an output shaft arranged parallel to the input shaft, and comprising a dual clutch following the spur gear in the torque flow for selectively transmitting the torque from a first and second stage of the spur gear to an output-side torque transmission member of the torque transmission assembly, wherein the dual clutch has a clutch output hub, on which the torque transmission member is arranged in a rotationally fixed manner, and the clutch output hub and the output shaft are supported against one another via at least one radial bearing.

Claims

1. A torque transmission assembly for a motor vehicle comprising a two-stage spur gear, having an input shaft for introducing the torque of a drive unit and an output shaft arranged parallel to the input shaft, and comprising a dual clutch following the spur gear in the torque flow for selectively transmitting the torque from a first and second stage of the spur gear to an output-side torque transmission member of the torque transmission assembly, wherein the dual clutch has a clutch output hub, on which the torque transmission member is arranged in a rotationally fixed manner, and the clutch output hub and the output shaft are supported against one another via at least one radial bearing.

2. The torque transmission assembly as claimed in claim 1, wherein a fixed housing is provided, wherein the clutch output hub is preferably supported on the housing via a clutch-side fixed bearing, optionally a rolling bearing, and the clutch-side fixed bearing is particularly preferably arranged nested with the at least one radial bearing, optionally completely, in the radial direction.

3. The torque transmission assembly as claimed in claim 1, wherein the torque transmission member is supported on the clutch output hub in the mutually opposite axial directions, wherein the torque transmission member is preferably supported on the clutch output hub in an axial direction via the clutch-side fixed bearing, particularly preferably on a retaining ring for supporting the clutch-side fixed bearing on the clutch output hub, and is optionally supported directly on the clutch-side fixed bearing.

4. The torque transmission assembly as claimed in claim 2, wherein a transmission-side fixed bearing, optionally a rolling bearing, is provided, via which the output shaft is supported on the housing, wherein the first stage, the second stage and the dual clutch, preferably also the torque transmission member, are arranged particularly preferably in the axial direction between the clutch-side fixed bearing and the transmission-side fixed bearing.

5. The torque transmission assembly as claimed in claim 1, wherein the torque transmission member is arranged coaxially with the clutch output hub or/and is plugged onto the clutch output hub in the axial direction or/and is arranged with a form-fit, preferably via a spline, on the clutch output hub in a rotationally fixed manner or/and is formed by a gear, preferably helically toothed or/and externally toothed gear, or/and is arranged nested with the at least one radial bearing in the radial direction, or/and the clutch output hub has an opening, which is preferably continuous in the axial direction for receiving the output shaft, in which the at least one radial bearing is arranged.

6. The torque transmission assembly as claimed in claim 1, wherein the dual clutch is a wet-running or/and hydraulically actuatable dual clutch, wherein between a fixed housing portion and the clutch output hub there is preferably a rotary feedthrough via which the dual clutch can be supplied with a cooling or/and lubricating fluid or/and a hydraulic fluid, and the rotary feedthrough 1 is preferably arranged nested with the at least one radial bearing in a radial direction, wherein particularly preferably a first radial bearing, which is arranged nested with the clutch-side fixed bearing or/and the torque transmission member in the radial direction, and a second radial bearing, which is arranged nested with the rotary feedthrough in the radial direction, are provided, wherein the rotary feedthrough or/and the housing portion is optionally arranged in the axial direction between the torque transmission member and the components of the dual clutch to be supplied with the cooling or/and lubricating fluid or/and the hydraulic fluid.

7. The torque transmission assembly as claimed in claim 1, wherein the first stage has a first output gear which is rotatably mounted on the output shaft and which is connected to a first input side of a first clutch of the dual clutch in a rotationally fixed manner, and the second stage has a second output gear which is arranged rotationally fixed on or to the output shaft and which is connected via the output shaft to a second input side of a second clutch of the dual clutch in a rotationally driving manner, wherein preferably, the first input side is connected, optionally directly, to the first output gear in a rotationally fixed manner spaced apart from a wheel hub of the first output gear in the radial direction, or/and the second input side is connected, optionally directly, to the output shaft in a rotationally driving manner, and particularly preferably, the second input side, the first output gear and the second output gear are supported, optionally with the interposition of axial bearings, on the output shaft in an axial direction via a common retaining ring, or/and on the output shaft or/and on the housing in the opposite axial direction via the transmission-side fixed bearing.

8. The torque transmission assembly as claimed in claim 7, wherein the wheel hub of the first output gear is tubular and extends substantially in the axial direction wherein the first output gear preferably further has a radial portion extending substantially in the radial direction and to which the first input side is connected in a rotationally fixed manner and on which an external toothing or/and helical toothing is particularly preferably provided.

9. The torque transmission assembly as claimed in claim 1, wherein the dual clutch is a concentric dual clutch or/and multi-disk dual clutch, wherein preferably the first clutch is a radially outer multi-disk clutch with the first input side in the form of an outer disk carrier and the second clutch is a radially inner multi-disk clutch with the second input side in the form of an inner disk carrier and particularly preferably a multi-disk carrier connected to the clutch output hub in a rotationally fixed manner is provided to form the output side of the outer and inner multi-disk clutch, which multi-disk carrier optionally comprises a single or/and one-piece, tubular multi-disk carrier portion with an outer rotary drive contour for inner disks of the outer multi-disk clutch and an inner rotary drive contour for outer disks of the inner multi-disk clutch arranged nested in the radial direction with the outer rotary drive contour.

10. The torque transmission assembly as claimed in claim 1, wherein a drive unit is provided with an output drive shaft which is connected to the input shaft in a rotationally driving manner, wherein the output drive shaft is preferably formed as a single piece with the input shaft and the drive unit is particularly preferably formed by an electric motor or an electric machine, which optionally comprises a rotor connected to the output drive shaft in a rotationally fixed or/and direct manner.

Description

[0033] The invention is explained in more detail below using an exemplary embodiment with reference to the single FIGURE. The single FIGURE shows a side view of an embodiment of the torque transmission assembly according to the invention in sectional illustration.

[0034] The FIGURE shows a torque transmission assembly 2 for a motor vehicle or the drive train of a motor vehicle. The torque transmission assembly 2 is substantially made up of a drive unit 4, a two-stage spur gear 6, a dual clutch 8 and a output-side torque transmission member 10, which are arranged one after the other starting from the the drive unit 4 in the said sequence in the torque flow starting from the drive unit 4. Moreover, the said components are arranged within a fixed housing 12, which in the embodiment shown is substantially formed by the housing portions 14, 16, 18, 20, 22, 24 which are preferably each formed in one piece or/and releasably attached to one another. The mutually opposing axial directions 26, 28, the mutually opposing radial directions 30, 32 and the mutually opposing circumferential directions 34, 36 are indicated in the FIGURE by corresponding arrows.

[0035] The drive unit 4 is formed by an electric motor. To more precise, the drive unit 4 is formed by an electric machine which can be operated both as a motor and as a generator. In this case, the drive unit 4, which is substantially arranged within the housing portions 14, 16, has a stator 38 fixed to the housing and a rotor 40 arranged in the radial direction 32 within the annular stator 38. The rotor 40 is connected in a rotationally fixed manner to an output drive shaft 42 of the drive unit 4 which is rotatable about a rotation axis 44 extending in the axial directions 26, 28. The rotor 40 is also directly connected to the output drive shaft 42 in a rotationally fixed manner.

[0036] The output drive shaft 42 of the drive unit 4 is in rotary drive connection with an input shaft 46 of the spur gear 6 in the axial direction 26, wherein the rotary drive connection between the output drive shaft 42 and the input shaft 46 can be direct or indirect. In the embodiment illustrated, the output drive shaft 42 of the drive unit 4 is designed in one piece with the input shaft 46 of the spur gear 6, in order to be directly connected to the input shaft 46 in a rotationally fixed manner, whereby a rotation axis 48 the input shaft 46 consequently coincides with the rotation axis 44 of the output drive shaft 42 and likewise extends in the axial directions 26, 28. The output drive shaft 42 designed in one piece with the input shaft 46 extends in the axial direction 26 through an opening in the housing portion 16 into a chamber which is substantially surrounded by the housing portions 16, 18 and 20.

[0037] The spur gear 6 is arranged in this chamber. In addition to the aforementioned input shaft 46 for introducing the torque of the drive unit 4, the spur gear 6 has an output shaft 50 which is arranged parallel to the input shaft 46 and is rotatable about a rotation axis 52, wherein the rotation axis 52 in turn extends in the axial directions 26, 28 and is arranged parallel to the rotation axis 48 and thereby offset in the radial direction 32 or 30 with respect to the rotation axis 48. The spur gear 6 has two gear stages or stages, namely a first stage 54 and a second stage 56. Both stages 54, 56 each have an externally toothed or/and helically toothed input gear 58, 60 which is connected to the input shaft 46 in a rotationally fixed manner. Moreover, the first stage 54 has a first output gear 62 which is indirectly or directly, here directly, in rotary drive engagement with the input gear 58. The second stage 56 has a second output gear 64 which is indirectly or directly, here directly, in rotary drive engagement with the input gear 60. For this purpose, both output gears 62, 64 each have an external toothing 66, 68, which is preferably designed as a helical toothing.

[0038] Both output gears 62, 64 are furthermore arranged on the output shaft 50 and can rotate about the latter or with the latter about the rotation axis 52, wherein the first output gear 62 is arranged behind the second output gear 64 in the axial direction 26 and thus follows the second output gear 64 in the said axial direction 26.

[0039] The first output gear 62 of the first stage 54 is rotatably mounted on the output shaft 50 by means of a bearing 70. The second output gear 64 of the second stage 56 on the other hand is arranged rotationally fixed on or to the output shaft 50, wherein the rotationally fixed arrangement is achieved here by a positive fit, specifically by a toothing or spline 72. Therefore, the second output gear 64 rotates together with the output shaft 50 about the rotation axis 52.

[0040] In the embodiment illustrated, the first output gear 62 is designed in one piece and is made up substantially of a tubular wheel hub 74, which extends substantially in the axial direction 26, 28, so that the output shaft 50 can be guided through the wheel hub 74 in the axial direction 26, as shown in the FIGURE, and of a radial portion 76 which extends outwards from the tubular wheel hub 74 in the radial direction 30, on the side of which pointing outwards in the radial direction 30 the aforementioned external toothing 66 is provided in the form of a helical toothing. The bearing 70 is arranged in the radial direction 30, 32 between the inner output shaft 50 and the tubular wheel hub 74.

[0041] The dual clutch 8 is arranged substantially in the axial direction 26 next to the first output gear 62 and within the chamber delimited by the housing portions 16, 18 and 20. The dual clutch 8 is used to selectively transmit the torque from the first stage 54 and the second stage 56 of the spur gear 6 to the output-side torque transmission member 10. The dual clutch 8 is a hydraulically actuatable dual clutch 8. In addition, the dual clutch 8 is a wet-running dual clutch 8, so that it rotates in a cooling or/and lubricating fluid. To be more precise, the dual clutch 8 is a dual-disk clutch, the disks of which are arranged inside the cooling or/and lubricating fluid, i.e. in a wet chamber.

[0042] The dual clutch 8 has a first clutch 78 and a second clutch 80 which are consequently each designed as multi-disk clutches with a multi-disk pack 82 or 84 respectively. The dual clutch 8 is also a concentric dual clutch 8, wherein the first clutch 78 is a radially outer multi-disk clutch and the second clutch 80 is a radially inner multi-disk clutch. Because this is a concentric dual clutch 8, the multi-disk packs 82, 84 are arranged nested in the radial direction 30, 32, so that the multi-disk pack 82 surrounds the multi-disk pack 84 in the radial direction 30 on the outside, wherein this does not necessarily have to be the case entirely, as is shown in the FIGURE, in which the two multi-disk packs 82, 84 have only a partial axial region of overlap.

[0043] The first clutch 78 has a first input side 86 in the form of an outer multi-disk carrier, while the second clutch 80 has a second input side 88 in the form of an inner multi-disk carrier. The output side 90 of both the first clutch 78 and the second clutch 80 is substantially formed by a clutch output hub 92 on which a further multi-disk carrier 94 is attached in a rotationally fixed manner. The multi-disk carrier 94 forming a portion of the output side 90 has a tubular disk carrier portion 96 which extends in the axial direction 28 between the multi-disk packs 82, 84 of the two clutches 78, 80 arranged nested in the radial direction 30, 32. The disk carrier portion 96 has an outer rotary drive contour, pointing outward in the radial direction 30, for inner disks of the first clutch 78 in the form of the outer multi-disk clutch and an inner rotary drive contour, pointing inward in the radial direction 32 and arranged nested with the outer rotary drive contour in the radial direction 30, 32, for outer disks of the second clutch 80 in the form of the inner multi-disk clutch. In this case, the disk carrier portion 96 is preferably designed as single or/and one-piece disk carrier portion 96 in order to form a common disk carrier portion 96 for both the first and the second clutches 78, 80. It is preferred here if the multi-disk carrier 94 or, optionally, only the disk carrier portion 96 is a sheet-metal part in which the generation of the outer or inner rotary drive contour likewise brings about the generation of the inner or outer rotary drive contour, resulting in a multi-disk carrier 94 or disk carrier portion 96 which is particularly easy to manufacture and moreover ensures a space-saving arrangement of the two multi-disk packs 82, 84 relative to one another.

[0044] The second input side 88 in the form of the inner multi-disk carrier is arranged on axial side of the first output gear 62 facing away from the second output gear 64, i.e. next to the first output gear 62 in the axial direction 26. Irrespective of this, the second input side 88 is in rotary drive connection with the second output gear 64 via the output shaft 50 which extends through the tubular wheel hub 74 of the first output gear 62, wherein, for this purpose, the inner multi-disk carrier forming the second input side 88 is positively attached in a rotationally fixed manner to the output shaft 50, here by means of a toothing 98. Consequently, in the embodiment illustrated, the second input side 88 is indirectly in rotary drive connection with the output shaft 50.

[0045] The first input side 86 in the form of the outer multi-disk carrier is, by contrast, connected to the first output gear 62 in a rotationally fixed manner. In this case, however, the first input side 86 in the form of the outer multi-disk carrier is connected in a rotationally fixed manner or attached not to the wheel hub 74 of the first output gear 62, but rather to the first output gear 62 in the radial direction 30 outwardly spaced apart from the wheel hub 74 of the first output gear 62, more precisely on the radial portion 76 of the first output gear 62, on which the aforementioned external toothing 66 in the form of the helical toothing is provided on the outside in the radial direction 30. In this case, the outer multi-disk carrier forming the first input side 86 is attached in a rotationally fixed manner to the first output gear 62 or the radial portion 76 of the first output gear 62. As evident from the FIGURE, the outer multi-disk carrier forming the first input side 86 can thus be substantially reduced to a tubular disk carrier portion for the outer disks of the multi-disk pack 82, while the support of the thus reduced outer multi-disk carrier in the radial direction 30, 32 can be provided via the radial portion 76, the wheel hub 74 and the bearing 70 on the output shaft 50, resulting in a significantly more simple and compact design, which dispenses with an additional radial support portion on the outer multi-disk carrier. Moreover, the path for transmitting the torque between the first stage 54 or the first output gear 62 and the outer multi-disk carrier forming the first input side 86 is significantly shorter.

[0046] As evident from the FIGURE, the second output gear 64, the first output gear 62 and the second input side 88 in the form of the inner multi-disk carrier are arranged on the an the output shaft 50 one after the other in the axial direction 26. In order to support the said components in the axial direction 26 on the output shaft 50, a common retaining ring 100 is arranged on the output shaft 50, on which the second input side 88 in the form of the inner multi-disk carrier can be or is supported in the axial direction 26, while the first output gear 62 can be or is supported indirectly on the common retaining ring 100 via the second input side 88 and the second output gear 64 via the first output gear 62 and the second input side 88. In this case, the said components can be supported against one another indirectly, however it is preferred if an axial bearing 102, preferably an axial needle roller bearing, is arranged between the first output gear 62 and the second input side 88 or/and between the second output gear 64 and the first output gear 62.

[0047] In the opposite axial direction 28, however, the second input side 88, the first output gear 62 and the second output gear 64 are supported on the output shaft 50 or/and the housing 12 via a transmission-side fixed bearing 104, with the transmission-side fixed bearing 104 which is preferably designed as a rolling bearing being discussed again in more detail later on.

[0048] The clutch output hub 92 extends starting from the multi-disk carrier 94 in the axial direction 26 through an opening in the housing portion 20 into a chamber which is substantially surrounded by the housing portion 20 and the housing portions 22 and 24. The torque transmission member 10 which is arranged on the clutch output hub 92 in a rotationally fixed manner is also provided in this chamber. The clutch output hub 92 is supported on the housing 12, to be more precise on the two housing portions 22, 24 of the housing 12 via a clutch-side fixed bearing 106, whichas shown in the FIGUREis preferably designed as a rolling bearing. This clutch-side fixed bearing 106 is arranged in the axial direction 26 next to the torque transmission member 10, i.e. on the side of the torque transmission member 10 facing away from the dual clutch 8. In this case, the clutch-side fixed bearing 106 is supported indirectly on the clutch output hub 92 via a retaining ring 108 in the axial direction 26. Moreover, the clutch-side fixed bearing 106 is supported in both axial directions 26, 28 on the housing 12, to be more precise in the axial direction 6 on the housing portion 24 and in the axial direction 28 on the housing portion 22.

[0049] The torque transmission member 10 is arranged coaxially with the clutch output hub 92, so that the latter can rotate together with the clutch output hub 92 about the rotation axis 52. The torque transmission member 10, which in the embodiment illustrated is designed as a helically toothed or/and externally toothed gear, is plugged onto the clutch output hub 92 in the axial direction 28 to achieve a form-fit, rotationally fixed connection with the clutch output hub 92, wherein for this purpose, a spline 110 is preferably formed between the torque transmission member 10 and the clutch output hub 92.

[0050] The torque transmission member 10 is supported on the clutch output hub 92 in the mutually opposite axial directions 26, 28. In the axial direction 26, the support is provided via the clutch-side fixed bearing 106 and the retaining ring 108 on the clutch output hub 92. The torque transmission member 10 is directly supported on the clutch-side fixed bearing 106 in the axial direction 26. In the opposite axial direction 28, the torque transmission member 10 is, by contrast, directly supported on the clutch output hub 92, which, for this purposeas evident from the FIGUREpreferably has a corresponding stage on which the support in the axial direction 28 can be effected. Due to the arrangement of the torque transmission member 10 adjacent to the clutch-side fixed bearing 106, an advantageous support of the forcesacting on the torque transmission member 10 via the external or helical toothingon the housing 12 is already achieved, wherein the support of the said forces in torque transmission assembly 2 shown is again considerably improved by the further features of the torque transmission assembly 2 that are described below.

[0051] The clutch output hub 92 is substantially tubular, so that this has an opening 112 located on the inside in the radial direction 32, which opening is preferably continuous in the axial direction 26, 28. The opening 112 serves to receive the output shaft 50 of the spur gear 6, which extends in the axial direction 26 into the said opening 112, in order to be arranged substantially coaxially with the tubular clutch output hub 92, wherein the output shaft 50 extends so far in axial direction 26 into the opening 112 that this is also arranged nested with the clutch-side fixed bearing 106 and the torque transmission member 10, and the rotary feedthrough described in more detail later on. The clutch output hub 92 and the output shaft 50 are supported against one another via at least one radial bearing 114, 116 within the opening 112.

[0052] In the embodiment illustrated, a first radial bearing 114 and a second radial bearing 116 are advantageously arranged between the output shaft 50 and the side of the clutch output hub 92 pointing inward in the radial direction 32, which are spaced apart from one another in the axial direction 26, 28 or/and are formed by rolling bearings, preferably needle roller bearings. The first radial bearing 114 is positioned in the axial direction 26, 28 such that it is arranged nested with the clutch-side fixed bearing 106 in the radial direction 30, 32. Thus, the clutch-side fixed bearing 106 in the embodiment illustrated is even arranged fully nested with the first radial bearing 114 in the radial direction 30, 32. The first radial bearing 114 is also arranged such it is also arranged at least partially nested with the torque transmission member 10 in the radial direction 30, 32, as is evident from the FIGURE, in which the first radial bearing 114 and the torque transmission member 10 are arranged overlapping one another in at least one axial region.

[0053] The second radial bearing 116 is, by contrast, arranged in the axial direction 28 spaced apart from the first radial bearing 114 between the output shaft 50 and the side of the clutch output hub 92 pointing inward in the radial direction 32.

[0054] Due to the two radial bearings 114, 116 in connection with the clutch-side fixed bearing 106 and the transmission-side fixed bearing 104, the radial and axial forces introduced via the torque transmission member 10 and via the output gears 62, 64 can be supported particularly reliably within the torque transmission assembly 2, without the output gears 62, 64, the torque transmission member 10, the clutch output hub 92 and the output shaft 50 performing undesirable movements, such as for example a wobble, thereby creating a particularly robust and also compact torque transmission assembly 2 with very smooth running and little wear. The aforementioned transmission-side fixed bearing 104 ensures that the output shaft 50 is supported in the axial directions 26, 28 on the housing 12, to be more precise the housing portion 16 of the housing 12. The robust design of the torque transmission assembly 2 to prevent undesirable movements is further supported by the fact that the first stage 54, the second stage 56, the dual clutch 8 and the torque transmission member 10 are arranged in the axial direction 26, 28 between the clutch-side fixed bearing 106 and the transmission-side fixed bearing 104.

[0055] As already indicated above, the dual clutch 8 is a wet-running and hydraulically actuatable dual clutch 8. To ensure the supply of such a dual clutch 8 with a cooling or/and lubricating fluid and a hydraulic fluid, the rotary feedthrough 118 indicated above is formed between a fixed housing portion of the housing 12, here the housing portion 20, and the clutch output hub 92. Specifically, the rotary feedthrough 118 is formed in the radial direction 30, 32 between the side of the opening in the housing portion 20 pointing radially inward in the radial direction 32 and a side of the clutch output hub 92 pointing outward in the radial direction 30. In principle, only the supply of hydraulic fluid to actuate the dual clutch 8 or only the supply of cooling or/and lubricating fluid to the dual clutch 8 ca be effected via the said rotary feedthrough 118, wherein both options are described together below by way of example with reference to the FIGURE. Thus, at least one hydraulic fluid line not shown in detail is formed in the housing portion 20, which line is fluidically connected via the rotary feedthrough 118 with at least one hydraulic fluid line that is formed within the tubular clutch output hub 92. Moreover, at least one cooling or/and lubricating fluid line is formed in the housing portion 20, which line is fluidically connected via the rotary feedthrough 118 with at least one cooling or/and lubricating fluid line within the tubular clutch output hub 92.

[0056] As evident from the FIGURE, the rotary feedthrough 118 and the housing portion 20 are advantageously arranged in the axial direction 26, 28 between the componentsto be supplied with cooling or/and lubricating fluid and hydraulic fluidof the dual clutch 8 on one side and the torque transmission member 10 on the other side. Moreover, the aforementioned second radial bearing 116 is arranged nested with the rotary feedthrough 118 and the housing portion 20 to support the clutch output hub 92 and the output shaft 50 against each other in the radial direction. As a result, a wobbling of the clutch output hub 92 in the axial region of the rotary feedthrough 118 is prevented particularly effectively so that a leakage in the region of the rotary feedthrough 118 can be countered particularly effectively.

LIST OF REFERENCE NUMERALS

[0057] 2 torque transmission assembly [0058] 4 drive unit [0059] 6 two-stage spur gear [0060] 8 dual clutch [0061] 10 output-side torque transmission member [0062] 12 fixed housing [0063] 14 housing portion [0064] 16 housing portion [0065] 18 housing portion [0066] 20 housing portion [0067] 22 housing portion [0068] 24 housing portion [0069] 26 axial direction [0070] 28 axial direction [0071] 30 radial direction [0072] 32 radial direction [0073] 34 circumferential direction [0074] 36 circumferential direction [0075] 38 stator [0076] 40 rotor [0077] 42 output drive shaft [0078] 44 rotation axis [0079] 46 input shaft [0080] 48 rotation axis [0081] 50 output shaft [0082] 52 rotation axis [0083] 54 first stage [0084] 56 second stage [0085] 58 input gear [0086] 60 input gear [0087] 62 first output gear [0088] 64 second output gear [0089] 66 external gearing [0090] 68 external gearing [0091] 70 bearing [0092] 72 gearing [0093] 74 wheel hub [0094] 76 radial portion [0095] 78 first clutch [0096] 80 second clutch [0097] 82 multi-disk pack [0098] 84 multi-disk pack [0099] 86 first input side/outer disk carrier [0100] 88 second input side/inner disk carrier [0101] 90 output side [0102] 92 clutch output hub [0103] 94 multi-disk carrier [0104] 96 multi-disk carrier portion [0105] 98 toothing [0106] 100 common retaining ring [0107] 102 axial bearing [0108] 104 transmission-side fixed bearing [0109] 106 clutch-side fixed bearing [0110] 108 retaining ring [0111] 110 spline [0112] 112 opening [0113] 114 first radial bearing [0114] 116 second radial bearing [0115] 118 rotary feedthrough