CN105485309B

CN105485309B - Torque transmitting device and driveline

Info

Publication number: CN105485309B
Application number: CN201510600768.7A
Authority: CN
Inventors: D·梅耶尔
Original assignee: BorgWarner Inc
Current assignee: BorgWarner Inc
Priority date: 2014-10-02
Filing date: 2015-09-18
Publication date: 2020-03-17
Anticipated expiration: 2035-09-18
Also published as: CN105485309A; DE102014014669A1

Abstract

The invention relates to a torque transmission device having an input side, an output side, a clutch device for selective torque transmission between the input side and the output side and an electric machine having a rotor which is rotatable relative to a stator and which is rotationally fixed at the output side and is radially supportable or supported, wherein the output side is supportable or supported at a housing part by means of at least one radial bearing and at least one first supply channel is provided in the housing part, which is in flow connection with a second supply channel in the output side by means of a rotary channel, which is used for supplying a coolant or lubricant or/and hydraulic fluid to the clutch device. The housing part separates the wet chamber from the dry chamber, the clutch device being arranged in the wet chamber and the rotor and, where appropriate, the stator being arranged in the dry chamber. The invention further relates to a drivetrain having such a torque transmission device.

Description

Torque transmitting device and driveline

Technical Field

The invention relates to a torque transmission device having an input side, an output side, a clutch device for selective torque transmission between the input side and the output side, and an electric machine having a rotor which is rotatable relative to a stator and which is fastened against rotation at the output side and is radially supportable or supported, wherein the output side is supportable or supported at a housing part by means of at least one radial bearing. The invention also relates to a drive train for a motor vehicle, which has a torque transmission device of this type between a drive unit and a transmission.

Background

In the drive train of a conventional motor vehicle, the drive unit (mostly an internal combustion engine) is in rotationally synchronous connection with the transmission of the motor vehicle, where appropriate with the intermediary of a torsional vibration damper and a clutch device. In contrast, in the drive train of a motor vehicle formed as a hybrid vehicle, which can thus be driven selectively via the transmission unit or an electric machine, an additional separating clutch must be provided in addition to the electric machine itself for separating the transmission unit from the transmission. It has proven to be costly in terms of manufacturing technology to couple the additional separating clutch and the electric machine into the drive train. Furthermore, the integration of these two components into the drive train results in a higher installation space requirement. It must also be ensured that the rotor of the electrical machine is reliably supported.

Against this background, DE 102012002290 a1 proposes a torque transmission device which is formed as a module, wherein the module as an assembled unit is to be insertable or insertable into the drive train between the drive unit and the transmission, in order to be able to achieve a space-saving construction and a simple insertion into the drive train and a simple production of the drive train of the motor vehicle. In the known torque transmission device, a housing is provided which is assembled from a first pot-shaped housing part and a second cover-shaped housing part. A receiving space is formed inside the housing for receiving the separating clutch and the electric machine together with the stator and the rotor. The input side of the torque transmitting device is supported at the first housing part by a first radial bearing, while the output side is supported at the second housing part by a second radial bearing. Feed channels are also formed in the pot-shaped first housing part, which feed channels are in flow connection with supply channels in the feed side via a rotary channel. The separating clutch is supplied with hydraulic oil for hydraulic operation of the separating clutch and cooling oil for cooling through the feed and supply passages in the input side. The receiving space is divided by means of a separating wall formed as a sheet metal part inside the housing into a wet chamber (in which the separating clutch is arranged) and a dry chamber (in which the electric machine together with the stator and the rotor are arranged).

Disclosure of Invention

Starting from this known torque transmission device, the present invention is based on the object of specifying a torque transmission device which has a compact and space-saving construction, can be produced and installed in a simple manner and/or ensures a reliable support of the rotor. The present invention is also based on the object of specifying a drive train for a motor vehicle, which has an advantageous torque transmission device of this type, in particular with a low installation space requirement.

This object is achieved by a torque transmitting device and a driveline according to the present invention. Wherein the housing portion separates a wet chamber from a dry chamber, the clutch device being arranged in the wet chamber, the rotor being arranged in the dry chamber; said torque transmission device is arranged between the transmission unit and the transmission for selective torque transmission from the transmission unit to the transmission, wherein a second wet chamber is arranged nested with the dry chamber, in which second wet chamber a second clutch device connected upstream of the transmission is arranged, in which dry chamber the rotor is arranged.

The torque transmission device according to the invention has an input side, for example an input hub, which is connectable to a transmission unit, and an output side, for example an output hub, which is connectable to a downstream component in the drive train, for example a second clutch or a transmission. The torque transmission device also has a clutch device for the selective transmission of torque between the input side and the output side. The clutch device is preferably a plate clutch device, particularly preferably formed as a simple clutch. Also, when referring to a clutch device in this context, the clutch device may also be referred to as a disconnect clutch or start-up clutch, by means of which the input side and the output side are selectively connectable or disconnectable. The torque transmission device also has an electric machine, wherein the electric machine has a stator and a rotor that is rotatable relative to the stator. The stator and the rotor of the electrical machine are preferably embodied here such that: the rotor rotating relative to the stator generates a current in the stator (generator mode), while the excitation of the stator (bestromng) causes a relative rotation of the rotor with respect to the stator (engine mode). The rotor, which is rotatable relative to the stator, is fastened against rotation at the output side of the torque transmission device and can be supported or supported in the radial direction at the output side. The output side is supportable or supported at a housing part by at least one radial bearing, wherein the at least one radial bearing is preferably a rolling bearing. In the housing part, i.e. for example in a wall of the housing part, at least one first supply channel is provided. The first supply channel is in flow connection via a rotary channel with a second supply channel in the output side for supplying coolant or lubricant or/and hydraulic fluid to the first clutch device. The clutch device used according to the invention can thus be, for example, a wet clutch device or/and a hydraulically actuated clutch device, wherein, for example, oil can be considered as a coolant or lubricant or/and hydraulic fluid. The housing part separates a wet chamber, in which the clutch device is arranged, from a dry chamber, in which the rotor is arranged, by means of the at least one first supply channel. It is preferred here that the rotor and (at least partially) the stator are arranged in the dry chamber. As with the torque transmission device known from DE 102012022290 a1, the arrangement of the rotor and, where appropriate, the stator in the dry chamber also functions in isolation from the wet chamber receiving the clutch device, so that a co-action between stator and rotor which is not influenced by coolant or lubricant is possible, while the clutch device is cooled or lubricated in an advantageous manner. In contrast to the known solution, however, the additional separating wall is omitted between the wet chamber of the clutch device and the dry chamber of the rotor, in particular this function is already assumed by the housing part in which on the one hand at least one first supply channel is provided and on the other hand the output side of the torque transmission device is supportable or supported by the at least one radial bearing. A simplified and space-saving construction of the torque transmission device is thereby achieved.

In order to provide a torque transmission device which is compact in terms of axial constructional length while using a housing part with the at least one first supply channel to separate the wet chamber from the dry chamber, the housing part is arranged between the wet chamber and the dry chamber with the wet chamber and the dry chamber at least partially nested radially. In this case, it is preferred that the dry chamber at least partially, i.e., for example in an axial section, radially outwardly surrounds the wet chamber. In this way, the housing part can, for example, bulge or protrude in the direction of the dry chamber in a radially inner region to achieve radial nesting of the wet chamber with the dry chamber. In this embodiment, it is also preferred that the electric machine or at least part of the electric machine, for example the stator or/and the rotor, is arranged in the dry chamber in such a way that the electric machine, the stator or/and the rotor are arranged radially nested with at least one component of the clutch device in order to use the space in the dry chamber effectively while achieving a small axial construction length.

In principle, the housing part can be any housing part. However, it has proven advantageous in terms of production if the housing part is formed as a housing cover of a housing, as is also the case in another preferred embodiment of the torque transmission device according to the invention. The housing preferably closes an end-side opening of the housing. The housing part formed as a housing cover is preferably formed so as to be removable in order to further simplify the production and in particular to enable a quick mounting and dismounting of the torque transmission device. The housing is preferably the transmission housing or a transmission housing of a drive train.

In an advantageous embodiment of the torque transfer device according to the invention, the housing part directly separates the wet chamber from the dry chamber. In other words, the housing part is formed in such a way that the wet chamber and the dry chamber directly adjoin the housing part in at least sections of the housing part. In this way, an additional separating wall between the wet chamber and the dry chamber is dispensed with, in order to achieve a particularly compact construction, in particular a small axial construction length.

In a particularly advantageous embodiment of the torque transmission device according to the invention, the output side is supportable or supported at the housing part by two radial bearings. As a result, the rotor, which is supported radially on the output side, can be supported or supported particularly reliably via the output side and the two radial bearings at the housing part, wherein in particular an increased tilting protection of the rotor relative to the stator is ensured. Due to the improved support reliability of the rotor, the gap formed between the rotor and the stator also remains largely constant during operation of the torque transmission device, so that unaffected operation of the electric machine is possible. In this embodiment, it is preferred that the two radial bearings mentioned are spaced apart from one another in the axial direction in order to further enhance the advantages mentioned.

In a further advantageous embodiment of the torque transmission device according to the invention, the two radial bearings for supporting the output side at the housing part are spaced apart from one another in such a way that the rotation path is arranged axially between the two radial bearings. It has been shown that with such an arrangement of the rotary channel, a largely constant rotary channel gap can also be achieved during operation, so that leakage losses (lockageverute) can be avoided on the one hand and increased wear on the other hand in the rotary channel region.

In order to simplify and make more flexible the assembly (wherein the production of the components is also to be simplified), in a further preferred embodiment of the torque transmission device according to the invention the output side is formed in at least two parts. The output side is therefore assembled at least in two parts from a first output assigned to the rotor and a second output fastened to the first output in a rotationally fixed manner. In this embodiment, the rotor is thereby fastened indirectly or directly against rotation at the first output of the output side and can be supported or supported in the radial direction. The second output of the output side associated with the clutch device is, on the contrary, preferably formed as an output hub of the clutch device. The anti-rotation fastening of the first output side at the second output can be performed in any way, i.e., for example by force, form or material fit, but it has proven advantageous if the first output is fastened releasably at the second output, wherein a connection formed as a plug-in toothing between the first and second outputs has proven advantageous here.

In principle, the output side, which is assembled from the first and second output, can be supported or supported at the housing part by the first or second output and the at least one radial bearing. In a further preferred embodiment of the torque transmission device according to the invention, however, the first output (at which the rotor is fastened rotationally fast and radially supportable or supported) is supportable or supported at the housing part by the at least one radial bearing, preferably by the two radial bearings, to ensure a particularly reliable support of the rotor and thus a stable arrangement of the rotor relative to the stator of the electric machine.

According to a further advantageous embodiment of the torque transmission device according to the present invention, the rotational path is provided between the housing part and the first output part of the two-part output side.

In order to achieve a particularly compact construction in terms of the axial construction length and a simple, rotation-proof fastening between the first output and the second output, in a further preferred embodiment of the torque transmission device according to the invention the first output is arranged radially nested with the second output.

According to a further advantageous embodiment of the torque transmission device according to the invention, the second supply channel in the output side is formed by a first channel section in the first output and a second channel section in the second output, which is connected in flow communication with the first channel section. The advantage of this is that the channel sections of the second supply channel can be produced independently of one another in the outputs, wherein the channel sections can have a relatively simple shape in the axial direction or/and radial direction, i.e. for example a circumferential groove or hole, as is also further preferred. In this embodiment, it is also preferred that the first channel section and the second channel section are sealed in a transition region between the first channel section and the second channel section by means of at least one seal. It is therefore particularly preferred that the respective second supply channel in the outlet side is sealed on the one hand in an axial direction by a first seal and on the other hand in the opposite axial direction by a second seal, wherein the seals are preferably sealing rings.

In a particularly preferred embodiment of the torque transmission device according to the invention, the first output preferably forms a first module together with a rotor carrier or/and the rotor, which first module is transferable as an assembled unit or into a defined position relative to the housing part in order to simplify mounting and dismounting. In this connection, an assembled unit is understood here and in the following to mean that the mentioned components are arranged in the assembled unit in a manner secured against loosening relative to one another.

Alternatively or in addition to the above-described embodiments, in a further particularly preferred embodiment of the torque transmission device according to the invention, the second output preferably forms, together with the clutch device and the input side, and if appropriate also a torsional vibration damper, a second module between the input side and a clutch input side of the clutch device, which second module can be transferred or is transferred as an assembled unit into a defined position relative to the housing part, in order to simplify the mounting and dismounting of the torque transmission device.

In a further particularly advantageous embodiment of the torque transmission device according to the invention, the first module is displaceable or transferred in one axial direction and the second module in the opposite axial direction into the respective nominal position relative to the housing part if the first module mentioned above and the second module mentioned above are provided. Expediently, the first module can thus be transferred in the one axial direction into the nominal position relative to the housing part, while the further module can be transferred in the opposite axial direction into the nominal position relative to the housing part, thereby simplifying the manufacture and installation of the torque transmission device and the drive train. In this case, it is preferred that the rotation-proof connection to the further module, which has already been transferred into the nominal position relative to the housing part, is effected automatically by the transfer of the one module into the nominal position relative to the housing part. Furthermore, it is preferred in this embodiment that the first module is displaceable or transferred into the respective nominal position relative to the housing part exclusively in the one axial direction and the second module is displaceable or transferred exclusively in the opposite axial direction.

In a further advantageous embodiment of the torque transmission device according to the invention, the rotor of the electric machine is arranged at least partially radially nested with the rotational path to achieve a very small axial constructional length.

According to a further advantageous embodiment of the torque transmission device according to the invention, the rotor of the electric machine and the at least one radial bearing, preferably two radial bearings (for supporting the output side, preferably the first output section of the output side) are arranged radially nested at the housing part to achieve a small axial constructional length of the torque transmission device.

In a further particularly advantageous embodiment of the torque transmission device according to the invention, the rotor of the electric machine is arranged at least partially radially nested with the clutch device, for example with a clutch plate carrier of the clutch device embodied as a plate clutch, in order to achieve a small axial overall length.

As described above with reference to a preferred embodiment, the first module may have a rotor support. In a further preferred embodiment of the torque transmission device according to the invention, the rotor is therefore fastened at the output side, where appropriate the first output, by means of a rotor support, thereby enabling the rotor to be arranged significantly further radially outwards than the output side. In this embodiment, it is also preferred that the rotor support has a first radial section assigned to or fastened at the output side and a second radial section fastened releasably to the first radial section, at which second radial section the rotor is arranged. This embodiment has the advantage that the rotor can first be fastened at the second radial section, which is fastened at the first radial section of the rotor support. This configuration is also possible in that the rotor can be exchanged particularly simply by another, suitably differently dimensioned rotor, without the output side or the first output of the output side also having to be exchanged. For a different size of the replacement rotor, only a correspondingly adapted second radial section may be provided, so that the second radial section is fastened together with the rotor at the first radial section.

In a further preferred embodiment of the torque transmission device according to the invention, a torsional vibration damper is also proposed for rotationally elastically connecting the input side of the torque transmission device with a clutch input side of the clutch device in order to attenuate or balance a torque shock (drehmostistöβ e) from a drive unit.

In order to achieve a particularly compact, lightweight and space-saving construction of the torque transmission device, in a further preferred embodiment of the torque transmission device according to the invention the input side is fixed or supported at the output side, where appropriate at the second output of the output side, radially and axially by means of a separate radial and axial bearing, which is preferably formed as a roller bearing, this can be achieved, for example, by means of a support stage (St ü tzstufen) or/and a safety ring at the input side and the output side, since the separate radial and axial bearing for fixing or supporting in both radial and axial directions between the input side and the output side, a further radial bearing, axial bearing or/and radial and axial bearing can be omitted between the input side and the output side, whereby a significantly simplified construction is achieved.

As already explained above, in an advantageous embodiment of the torque transmission device according to the invention the clutch means is a disconnect clutch, a starting clutch, a hydraulically operable clutch or/and a wet clutch.

In a further advantageous embodiment of the torque transmission device according to the invention, the clutch device is a plate clutch. In contrast to a single-disk friction clutch, this disk clutch has a relatively compact design with equally good heat dissipation, in particular if the disk clutch is a wet disk clutch. The plate clutch preferably has an outer clutch plate carrier which is connected to the output side, if appropriate to the second output of the output side, in a rotationally fixed manner. It is preferred here that the outer clutch plate carrier has a radial support section adjoining a clutch plate retaining section of the outer clutch plate carrier in the direction of the housing part, by means of which radial support section the outer clutch plate carrier is fastened at the output side, if appropriate at the first output of the output side, so that a relatively sealed arrangement and thus a compact construction of the outer clutch plate carrier at the housing part separating the wet chamber from the dry chamber is possible. Furthermore, in the embodiment, it is preferred that the radial support section of the outer clutch plate carrier at least partially delimits a pressure chamber for the hydraulic actuation of the clutch device. In this way, the radial support section not only obtains the second function, i.e. to confine the pressure chamber, but the pressure chamber can also be arranged relatively close to the rotation passage between the housing part and the output side to ensure a short transmission path for the hydraulic fluid, even if the second supply channel extends through the first and the second output of the output side.

The drive train according to the invention for a motor vehicle, in particular a hybrid vehicle, has a drive unit, preferably an internal combustion engine, and a transmission, preferably a dual clutch transmission. According to the invention, a torque-transmitting device of the type according to the invention is arranged between the transmission unit and the transmission (where appropriate a second clutch device arranged upstream of the transmission) for selectively transmitting torque from the transmission unit to the transmission or to the second clutch device. In respect of the advantages of one such drive train, reference is made to the advantages of the inventive torque transmitting device described above, which are applicable in a corresponding manner to the drive train.

In a preferred embodiment of the drive train according to the invention, a second wet chamber (in which the second clutch device is arranged) is arranged at least partially radially nested with the dry chamber (in which the rotor is arranged) to reduce the axial constructional length of the drive train. In this case, it is preferred that the dry chamber at least partially surrounds the second wet chamber radially on the outside. Thus, a radially inner section of a separating wall can be formed, for example, to bulge or protrude axially into the dry chamber between the dry chamber and the second wet chamber for the second clutch device, in order to achieve radial nesting of the dry chamber with the second wet chamber. The electric machine, i.e. the stator or/and the rotor, is here preferably arranged in the dry chamber in such a way that at least one component of the electric machine, for example the rotor or/and the stator, is arranged radially nested radially with a component of the second clutch device, in order to effectively utilize the radial nesting of the dry chamber with the second wet chamber in such a way that the axial constructional length is shortened.

In a further preferred embodiment of the drive train according to the invention, the second clutch device is formed as a double clutch device for the selective torque transmission between the output side of the torque transfer arrangement and a first transmission input shaft and for the selective torque transmission between the torque transfer arrangement and a second transmission input shaft. In this respect, it has proven to be advantageous in terms of shortening the axial construction length of the drive train if the double clutch is formed as a concentric double clutch, as is further preferred. The double clutch device is furthermore preferably hydraulically operable. The two mentioned transmission input shafts are also preferably arranged concentrically, so that one of the transmission input shafts extends coaxially through the other transmission input shaft, which is formed as a hollow shaft.

Drawings

The invention will be explained in detail below with the aid of a number of exemplary embodiments and with reference to the drawings. In the drawings:

FIG. 1 shows a side view of a drive train with a first embodiment of a torque transmitting device according to the invention shown in cross section, an

Fig. 2 shows a side view of a drive train with a second embodiment of the torque transmitting device according to the invention shown in a cross-sectional view.

Detailed Description

Fig. 1 shows a drive train 2 for a motor vehicle, more precisely for a hybrid vehicle. The mutually opposite axial directions 4, 6, the mutually opposite radial directions 8, 10 and the mutually opposite circumferential directions 12, 14 of the drive train 2 and of a torque transmission device 16 described in detail below are illustrated by means of corresponding arrows. A rotary shaft 18 of the drive train 2 or of the torque transmission device 16 is likewise illustrated in fig. 1.

The drive train 2 has a drive unit 20 formed as an internal combustion engine, which is illustrated schematically in fig. 1. The drive shaft, not shown in detail, of the drive unit 20 is in rotationally synchronous connection with an input side 22 of the torque transmission device 16. The torque transmitting device 16 also has a clutch device 24, an electric machine 26, and an output side 28, wherein the clutch device 24 is used for selective torque transmission between the input side 22 and the output side 28. A second clutch device 30 connected upstream of a transmission 32 follows the output side 28 in the axial direction 4, wherein the torque transmission device 16 serves for the selective torque transmission from the transmission unit 20 to the transmission 32 or the second clutch device 30 connected upstream of the transmission 32.

The transmission 32 is formed as a dual clutch transmission and has a first transmission input shaft 34 and a second transmission input shaft 36, wherein the

transmission input shafts

34, 36 are arranged concentrically and the second transmission input shaft 36 is formed tubular, while the first transmission input shaft 34 extends through the tubular second transmission input shaft 36. The second clutch device 30 is a dual clutch device for selective torque transfer between the output side 28 and the first transmission input shaft 34, and for selective torque transfer between the output side 28 and the second transmission input shaft 36. The second clutch device 30 is formed here as a concentric and hydraulically operable dual clutch device, wherein the two

clutches

38, 40 of the second clutch device 30 are respectively formed as wet-running plate clutches.

The clutch device 24 is formed as a plate clutch with a clutch disk pack 42 of outer and inner clutch disks which follow one another alternately in the axial direction 4, 6. The clutch device 24 therefore has an inner clutch plate carrier 44, which is connected to the input side 22 in a rotationally fixed manner, and an outer clutch plate carrier 46, which is connected to the output side 28 in a rotationally fixed manner. As will also be explained in more detail below, the output side 28 is assembled in two parts from a first output 48 and a second output 50 which is secured in a rotationally fixed and releasable manner to the first output 48, wherein the outer clutch plate carrier 46 is connected in a rotationally fixed manner to the second output 50. The outer clutch plate carrier 46 is assembled from a clutch plate retaining section 52, which is substantially tubular and extends in the axial direction 4, 6, and a radial support section 54, which adjoins the clutch plate retaining section 52 in the axial direction 4, the latter extending from the clutch plate retaining section 52 radially inward 10 in order to be connected in a rotationally fixed manner to the second output 50 of the output side 28. The inner clutch plate carrier 44 also has a clutch plate retaining section 56 which is substantially tubular and extends in the axial direction 4, 6, a radial support section 58 adjoining the clutch plate retaining section in the axial direction 6, which radial support section extends inward in the radial direction 10 toward the input side 22 in order to be connected rotationally fixedly to the input side.

The clutch device 24 is hydraulically operable. As can be seen from fig. 1, the clutch plate set 42 of the clutch device 24 is therefore assigned an actuating piston 60 which can be displaced in the axial direction 4, 6, the actuating piston 60 being arranged axially behind the clutch plate set 42 in the axial direction 4. The actuating piston 60 is associated with a pressure chamber 62 that can be acted upon by a hydraulic fluid or hydraulic pressure, wherein the pressure chamber 62 is delimited in the axial direction 4, here also in the radial direction 8, by the radial support section 54 of the outer clutch plate carrier 46. Conversely, the pressure chamber 62 is delimited in the axial direction 6 by the actuator piston 60 itself, while the pressure chamber 62 is delimited in the radial direction 10 inwardly by the output side 28 or the second output 50 of the output side 28. The actuating piston 60 is pretensioned in the axial direction 4 on its side facing away from the pressure chamber 62 by means of at least one restoring spring 64. The return spring 64 is supported in the axial direction 6 at a support 66, which is fastened in the axial direction 6 at the output side 28, to be precise at the second output 50 of the output side 28. The support 66 also serves to delimit a pressure compensation chamber 68 on the side of the actuating piston 60 facing away from the pressure chamber 62, wherein the pressure compensation chamber serves to at least partially centrifuge the oil balance.

As can be seen from fig. 1, the clutch device 24 is a normally open clutch device 24. The clutch device 24 can also be referred to as a separating clutch or starting clutch, wherein the clutch device 24 is arranged in a wet chamber 70, so that it can also be referred to as a wet-running clutch.

The electric machine 26 has a stationary stator 72 and a rotor 74 arranged radially 10 within the stator 72, thereby radially nested with the stator 72. The rotor 74, which is rotatable relative to the stator 72 about the axis of rotation 18, is fastened in a rotationally fixed manner on the output side 28, to be precise on the first output 48 of the output side 28, and can be supported or supported in the radial direction 8, 10. As can be seen from fig. 1, however, the anti-rotation fastening and bracing of the rotor 74 at the first output 48 is not straightforward. Instead, the rotor 74 is fastened at the first output 48 of the output side 28 by a rotor bracket 76.

The rotor carrier 76 has a first radial section 78 which is fastened at the first output 48 and is assigned to the output side 28, and which is formed by a section of the rotor carrier 76 which is disposed in the radial direction 10. The rotor support 76 furthermore has a second radial section 80 following the first radial section 78 outwards in radial direction 8, at which the rotor 74 is arranged or fastened. The second radial section 80 is releasably fastened to the first radial section 78 by means of a fastening means, not shown in detail, which may be formed, for example, by a screw. Thereby, the second radial segment 80 can be released from the first radial segment 78 together with the rotor 74 arranged or fastened at the second radial segment, in order to, for example, enable a replacement of the rotor 74 and, where appropriate, also the second radial segment 80. Thus, the distance a provided in the radial direction 8, 10 between the stator 72 and the rotor 74, which likewise forms the height of the circumferential gap 82 formed between the stator 72 and the rotor 74, can be adjusted exactly by using differently dimensioned rotors 74 or/and second radial segments 80 in the radial direction 8, 10. The rotor 74, here also the stator 72, is arranged in a dry chamber 84, so that the common gap between stator and

rotor

72, 74 is not influenced by coolant or/and lubricant (in particular in the region of the encircling gap 82).

As already explained above, the output side 28 of the torque transmission device 16 is assembled in two parts from the first output 48 assigned to the rotor 74 and the second output 50, which is assigned to the clutch device 24, which is secured against rotation and releasably to the first output 48. In this case, the two

outputs

48, 50 are arranged nested in an axial section b in the radial direction 8, 10. Specifically, the first output 48 surrounds the second output 50 in the axial section b from the outside in the radial direction 8, wherein the first output 48 is formed tubular at least in the axial section b. For reasons of weight, it has proven effective here to form the first and

second outlet

48, 50 in each case substantially tubular. The anti-rotation connection between the first and

second outputs

48, 50 can be made in any manner, but as already explained above, a releasable fastening is preferred here. In the embodiment shown, this is achieved by a plug-in toothing 85, wherein an external toothing at the second output 50 is inserted in the axial direction 4 into an internal toothing at the first output 48.

The output side 28 can be supported or supported in the radial direction 8, 10 at the housing part 86. The housing part 86 is a housing cover of a housing, not shown in detail, wherein the housing is preferably a transmission housing of the transmission 32 or a transmission housing of the transmission unit 20. The housing part 86 is detachably fastened to the respective housing in the form of a housing cover. The housing part 86, which is preferably formed as a casting, has an outer section 88 in the radial direction 8, a middle section 90 which follows the outer section 88 in the radial direction 10 and an inner section 92 which follows the middle section 90 in the radial direction 10, wherein the housing part 86 separates the wet chamber 70, in which the clutch device 24 is arranged, from the dry chamber 84, in which the rotor 74, here also the stator 72, is arranged. Here, the housing portion 86 directly separates (at least partially) the wet chamber 70 from the dry chamber 84. In other words, the housing portion 86 has sections in which the wet chamber 70 receiving the clutch device 24 and the dry chamber 84 receiving the electric machine 26 directly adjoin the housing portion 86. The housing part 86 is also arranged or formed in such a way that the wet chamber 70 and the dry chamber 84 are arranged radially nested with one another in at least one axial section c. In other words, the dry chamber 84 surrounds the wet chamber 70 from the outside in the axial section c in the radial direction 8. This is achieved in the illustrated embodiment as follows: the middle section 90 of the housing part 86 is formed so as to project in the axial direction 4 relative to the outer section 88 and thus in the direction of the dry chamber 84 in such a way that the housing part 86 has, for example, a convex curvature in the axial direction 4. In contrast, an opening 94 is formed in the inner section 92 (which preferably has a greater extent in the axial direction 4, 6 than in the case of the outer and inner sections 88, 90), through which the outlet side 28 extends from the wet chamber 70 in the axial direction 4 to the dry chamber 84.

As already explained above, the output side 28 extending through the opening 94 can be supported or supported at the housing part 86 by means of at least one radial bearing. The output side 28 is supported in the radial direction 8, 10 on the housing part 86 by two

radial bearings

96, 98, which are preferably formed as roller bearings. Two

radial bearings

96, 98 are arranged here in each case between the side of the inner section 92 directed inward in the radial direction 10 (i.e. similar to the opening edge of the opening 94) on the one hand and the side of the outlet side 28 extending into the opening 94 and directed outward in the radial direction 8 of the first outlet 48 on the other hand. As is shown in fig. 1 by means of this distance d, the two

radial bearings

96, 98 are spaced apart from one another in the axial direction 4, 6. The first output 48 is thus supported or supported on the housing part 86 in the radial direction 8, 10 by the two

radial bearings

96, 98.

A seal 100 is also arranged between the inner section 92 of the housing part 86 and the first output 48 of the output side 28 in order to seal the dry chamber 84 relative to the wet chamber 70, wherein the seal 100 follows a rotary path, which is explained in more detail below, from the wet chamber 70 in the gap between the inner section 92 of the housing part 86 and the first output 48 of the output side 28, here also the two

radial bearings

96, 98, in order to seal the dry chamber 84 not only relative to the wet chamber 70 but also to reliably ensure the sealing of the dry chamber 84 in the region of the rotary path in the event of any leakage losses. Furthermore, the coolant or/and lubricant supplied to the

radial bearings

96, 98 is thereby blocked by the seal 100 to avoid the coolant or/and coolant from penetrating into the dry chamber 84.

The output side 28 is supported at the housing part 86 by means of the two

radial bearings

96, 98, while the input side 22 (which in the embodiment shown can also be referred to as clutch input side or clutch input hub) is fastened or supported at the output side 28, to be precise at the two outputs 50 of the output side 28, on the two radial directions 8, 10 and the two axial directions 4, 6 by means of a separate radial and axial bearing 102. In the embodiment shown, the radial and axial bearing 102, which is preferably formed as a rolling bearing, is fastened in the axial direction 4, 6 at the respective component part at the input side 22 and at the first output 48 of the output side 28 by means of a step element (abstufang) and a securing ring, respectively.

However, the housing part 86 in the form of a housing cover serves not only to separate the wet chamber 70 from the dry chamber 84, but also to support the output side 28 by means of the

radial bearings

96, 98. Instead, two

first supply channels

104, 106 are provided in the housing part 86, which supply channels are connected in flow communication with a respective

second supply channel

110, 112 in the outlet side 28 via a rotary channel 108. The first supply channel 104 is in this case connected to the second supply channel 110 for supplying a hydraulic fluid, i.e. for example a hydraulic oil, to the clutch device 24 or the pressure chamber 62. Conversely, the first supply channel 106 is connected to the second supply channel 112 for supplying the clutch device 24, in particular the clutch plate set 42, with a coolant or lubricant, i.e. for example a cooling oil or lubricating oil, with which the aforementioned wet space 70 can be filled. It is mentioned here that the coolant or wetting agent supplied via the first supply channel 106 and the second supply channel 112 can likewise reach the pressure compensation chamber 68 in order to act here on the already mentioned (at least partially) centrifugal oil compensation.

As already explained, the rotary channel 108 is arranged between the side of the housing part 86, specifically the inner section 92 of the housing part 86, which is directed inward in the radial direction 10 on the one hand, and the side of the output side 28, specifically the first output 48 of the output side 28, which is directed outward in the radial direction 8 on the other hand, wherein the rotary channel 108 is also arranged between the two

radial bearings

96, 98 spaced apart from one another in the axial direction 4, 6 in order to obtain a rotary channel play which is as constant as possible during operation of the torque transmission device 16 or the drive train 2. The

second supply channels

110, 112 are formed by a first channel section in the first outlet 48 and a second channel section in the second outlet 50, which is in flow connection with the first channel section. In the embodiment shown, the first channel section in the first outlet 48 comprises a circumferential groove 12, 14 at the side of the first outlet 48 pointing outward in the radial direction 8 and at least one radial opening adjoining the circumferential groove in the radial direction 10. Conversely, the second radial section in the second outlet 50 has a groove in the side of the second outlet 50 pointing outward in the radial direction 8 and one or more axial or radial bores, respectively, which surrounds in the circumferential direction 12, 14, wherein the radial openings in the first outlet 48 are in flow connection with the grooves surrounding in the second outlet 50 in the circumferential direction 12, 14 in a transition region. Due to the two-part embodiment of the outlet side 28, the

second supply channels

110, 112 can thus be produced in a relatively simple manner. In the mentioned transition region between the first channel section and the second channel section of the

second supply channels

110, 112, there are also arranged seals 114, which are preferably sealing rings encircling in the circumferential direction 12, 14.

As already explained above, the dry chamber 84 and the wet chamber 70 are arranged radially nested in the axial section c. This makes possible a space-saving arrangement of the electric machine 26 or the rotor 74 or/and the stator 72 within the dry chamber 84, which facilitates a reduced axial length of the torque transmission device 16 and thus also of the drive train 2. The rotor 74 of the electric machine 26, here also the stator 72, is therefore arranged nested in the radial direction 8, 10 with a rotary channel 108 and the two

radial bearings

96, 98, i.e. the rotor 74 surrounds the mentioned parts from the outside in the radial direction 8. Furthermore, the rotor 74 of the electric machine 26, in this case also the stator 72, is arranged nested radially 8, 10 at least partially with the clutch device 24, in this case the outer clutch plate carrier 46, the actuating piston 60 and the pressure chamber 62, radially 8, 10, so that the rotor 74 and the stator 72 of the electric machine 26 surround the mentioned parts from the outside in radial direction 8.

By suitable arrangement of the electric machine 26, i.e. the rotor 74 or/and the stator 72 of the electric machine 26, within the dry chamber 84, a reduction of the axial length is also achieved in the direction of the second clutch device 30. The second clutch device 30 is therefore likewise formed as a wet-running clutch device 30 which is arranged in a second wet space 116. The second wet chamber 116 is separated with respect to the dry chamber 84 (in which the electric machine 26 is arranged with the rotor 74 and the stator 72) by means of a plate-shaped separating wall 118, wherein the separation takes place directly, as described above with reference to the housing part 86. The separating wall 118, which is preferably formed as a sheet metal part or/and has a smaller built-in supply channel, is also formed and arranged in such a way that the second wet chamber 116 is arranged nested with the dry chamber 84 at least partially in radial directions 8, 10. In the embodiment shown, the dry chamber 84 surrounds the second wet chamber 116 in an axial section e on the outside in the radial direction 8. Here too, the rotor 74 and/or the stator 72 should be arranged in the dry chamber 84 in such a way that they are arranged at least partially radially nested with a component of the second clutch device 30, as is explained in the embodiment according to fig. 1, for example, by means of the stator 72, which surrounds a rotating synchronization disk 120 of the second clutch device 30 at least partially on the outside in the radial direction 8. Although not shown, this should also apply to the rotor 74 in order to use the dry chamber 84 efficiently and space-effectively with a reduced axial length of the torque-transmitting device 16.

Independently of the advantages already mentioned above, the illustrated torque transmission device 16 also has a particularly advantageous modular construction which can be produced, installed and, if appropriate, removed in a significantly simplified manner. The first output 48 of the output side 28 thus forms, together with the rotor holder 76 and the rotor 74, but at least with the first radial section 78 of the rotor holder 76, a first module which can be transferred or is transferred as an assembled unit into its nominal position shown in fig. 1 relative to the housing part 86. Conversely, the second output 50 forms, together with the clutch device 24 and the input side 22, a second module which can be transferred as an assembled unit or into its nominal position shown in fig. 1. In particular, the second module has a second output 50, an outer clutch plate carrier 46, an actuating piston 60, a support 66, a return spring 64, a clutch plate pack 42, an inner clutch plate carrier 44, the input side 22 and radial and axial bearings 102, wherein the mentioned parts are arranged in a manner secured to one another and can thus be simply mounted or dismounted as an assembled unit. It can also be seen from the formation of the first and second modules that the first module is transferable (here exclusively) in the axial direction 6 and the second module (here again exclusively) in the opposite axial direction 4 or into the additional positions shown in fig. 1. During installation, the first module can initially be transferred in the axial direction 6 into the nominal position shown in fig. 1 relative to the housing part 86, so that the first output 48 is supported at the housing part 86 by the

radial bearings

96, 98 and the rotary passage 108 is produced. Subsequently, the second module can be transferred in the axial direction 4 into the nominal position according to fig. 1 relative to the housing part 86, wherein this results in the first output 48 being connected to the second output 50 in a rotationally fixed manner via the plug-in toothing 85 and in a flow connection between the first channel sections in the first output 48 on the one hand and the second channel sections in the second output 50 on the other hand.

Fig. 2 shows a second embodiment of the drive train 2 with a torque transmission device 16, wherein the second embodiment substantially corresponds to the first embodiment according to fig. 1, so that only the differences will be discussed below, identical or similar parts being provided with the same reference numerals and correspondingly applying to the previous description, even if some constituent parts of the drive train 2 according to the first embodiment are not re-illustrated in the second embodiment according to fig. 2.

In the second embodiment according to fig. 2, a torsional vibration damper 122 is provided for rotationally elastically connecting the input side 22 with a clutch input side 124 of the clutch device 24. The torsional vibration damper 122 has a damper input 126 which is connected to the input side 22 in a rotationally fixed manner and a damper output 128 which is connected to the clutch input side 124 in a rotationally fixed manner. The damper input 126 and the damper output 128 extend from the input 22 or the clutch input side 124 in the radial direction 8 to be coupled to one another there in a rotationally elastic manner relative to the circumferential direction 12, 14 by means of at least one spring element 130. The torsional vibration damper 122 is arranged at least partially nested in the radial direction 8, 10 with the clutch device 24, so that the torsional vibration damper 122, in particular the torsional vibration damper of the at least one spring element 130, at least partially surrounds the clutch device 24 on the outside in the radial direction 8. The torsional vibration damper 122 is also arranged in a space-saving manner in the wet space 70, in which the clutch device 24 is already arranged. As in the first embodiment according to fig. 1, in the second embodiment according to fig. 2, the input side 22 (which is now decoupled from the clutch input side 124) is also fastened or supported at the second output 50 of the output side 28 only by the individual radial and axial bearings 102 in the two axial directions 4, 6 and the two radial directions 8, 10. Between the clutch input side 124 and the second output 50 of the output side 28, however, a further radial bearing 132, preferably a rolling bearing, is provided, while between the clutch input side 124 and the input side 22 an axial bearing 134 is arranged.

It can be seen from the above description of the second embodiment according to fig. 2 that the second module, which has been mentioned above with reference to the first embodiment, also comprises in the second embodiment the clutch input side 124, the radial bearing 132, the axial bearing 134 and the torsional damper 122, together with the damper input side 126, the damper output side 128 and the at least one spring element 130.

List of reference numerals

2 drive train

4 axial direction

6 axial direction

8 radial direction

10 radial direction

12 in the circumferential direction

14 circumferential direction of the shaft

16 Torque transmitting device

18 axis of rotation

20 drive unit

22 input side

24 clutch device

26 electric machine

28 output side

30 second clutch device

32 speed variator

34 first Transmission input shaft

36 second transmission input shaft

38 clutch

40 clutch

42 clutch plate set

44 inner clutch plate support

46 outer clutch plate support

48 first output part

50 second output part

52 Clutch plate retaining segment

54 radial support section

56 Clutch plate retaining segment

58 radial support section

60 actuating piston

62 pressure chamber

64 return spring

66 support part

68 pressure balance chamber

70 wet chamber

72 stator

74 rotor

76 rotor support

78 first radial segment

80 second radial segment

82 surrounding gap

84 Dry chamber

85 inserting tooth part

86 housing portion

88 outer section

90 middle section

92 inner section

94 opening

96 radial bearing

98 radial bearing

100 seal

102 radial and axial bearing

104 first supply channel

106 first supply channel

108 rotary channel

110 second supply channel

112 second supply channel

114 seal

116 second wet chamber

118 separating wall

120 rotating synchronizer disc

122 torsional vibration damper

124 clutch input side

126 damper input

128 damper output

130 spring element

132 radial bearing

134 axial bearing

a distance

b axial segment

c axial segment

d distance

e an axial section.

Claims

1. Torque-transmitting device (16) having an input side (22), an output side (28), a clutch device (24) for the selective torque transmission between the input side (22) and the output side (28), and an electric machine (26) having a rotor (74) which is rotatable relative to a stator (72) and which is fastened in a rotationally fixed manner at the output side (28) and is supportable or supported in the radial direction (8, 10), wherein the output side (28) is supportable or supported at a housing part (86) by means of at least one radial bearing (96; 98) and at least one first supply channel (104; 106) is provided in the housing part (86) which is in flow connection with a second supply channel (110; 112) in the output side (28) by means of a rotary channel (108), the second supply channel is used for supplying coolant or lubricant or/and hydraulic fluid to the clutch device (24), characterized in that the housing part (86) separates a wet chamber (70) in which the clutch device (24) is arranged from a dry chamber (84) in which the rotor (74) is arranged.

2. The torque transmitting device (16) according to claim 1, characterized in that the housing portion (86) is arranged between the wet chamber (70) and the dry chamber (84) with the wet chamber (70) and the dry chamber (84) at least partially radially nested, the housing portion being a housing cover of a housing, or/and the housing portion directly separates the wet chamber (70) from the dry chamber (84).

3. The torque transmitting device (16) according to claim 1 or 2, characterized in that the output side (28) is supportable or supported at the housing part (86) by two radial bearings (96, 98), wherein the rotational passage (108) is arranged between the two radial bearings (96, 98).

4. The torque-transmitting device (16) as claimed in claim 1, characterized in that the output side (28) is assembled at least in two parts from a first output (48) assigned to the rotor (74) and a second output (50) which is fastened in a rotationally fixed manner at the first output (48) and which is assigned to the clutch arrangement (24), wherein the rotary channel (108) is provided between the housing part (86) and the first output (48) or/and the first output (48) and the second output (50) are arranged radially nested.

5. The torque transmitting device (16) according to claim 4, characterized in that the first output (48) forms a first module together with a rotor carrier (76) or/and the rotor (74), which first module is transferable or transferred as an assembled unit into a nominal position relative to the housing part (86), or/and the second output (50) forms a second module together with the clutch arrangement (24) and the input side (22), which second module is transferable or transferred as an assembled unit into a nominal position relative to the housing part (86).

6. The torque transmitting apparatus (16) according to claim 1, characterized in that the rotor (74) is arranged at least partially radially nested with the rotational passage (108), with the at least one radial bearing (96; 98), or/and with the clutch device (24).

7. The torque transmitting device (16) according to claim 4, characterized in that the rotor (74) is fastened at the output side (28) by a rotor bracket (76).

8. The torque transmission device (16) as claimed in claim 1, characterized in that a torsional damper (122) is also provided for the rotationally elastic connection of the input side (22) to a clutch input side (124) of the clutch arrangement (24).

9. The torque transmitting device (16) according to claim 4, characterized in that the input side (22) is fixed or supported at the output side (28) in radial (8, 10) and axial (4, 6) directions by means of a single radial and axial bearing (102).

10. The torque transmitting device (16) of claim 1, characterized in that the clutch means (24) is a disconnect clutch.

11. The torque transmitting device (16) of claim 4, characterized in that the clutch means (24) is a plate clutch.

12. The torque transmitting device (16) according to claim 1, characterized in that the stator (72) is also arranged in the dry chamber (84).

13. The torque transmitting device (16) of claim 2, wherein said housing cover is removable.

14. The torque transmitting device (16) of claim 2, wherein said housing is a transmission housing or a transmission housing.

15. The torque transmitting device (16) according to claim 3, characterized in that the two radial bearings (96, 98) are spaced apart from each other in the axial direction (4, 6).

16. The torque transmitting device (16) according to claim 3, characterized in that the rotational passage (108) is arranged in axial direction (4, 6) between the two radial bearings (96, 98).

17. The torque transmitting device (16) of claim 4, characterized in that the second output (50) is releasably secured at the first output (48).

18. Torque transmitting device (16) according to claim 4, characterized in that the first output (48) is supportable or supported at the housing part (86) by the at least one radial bearing (96; 98).

19. The torque transmitting device (16) as claimed in claim 4, characterized in that the second supply channel (110; 112) is formed by a first channel section in the first output (48) and a second channel section in the second output (50) which is connected in flow communication with the first channel section, the first channel section and the second channel section being sealed in a transition region.

20. The torque transmitting device (16) according to claim 19, characterized in that the first channel section and the second channel section are sealed in said transition area by means of at least one seal (114).

21. The torque transmitting device (16) according to claim 5, characterized in that the second output (50) forms said second module together with the clutch device (24) and the input side (22), also together with a torsional damper (122), between the input side (22) and a clutch input side (124).

22. The torque transmitting device (16) according to claim 5, characterized in that the first module is displaceable or shifted in the axial direction (4; 6) and the second module in the opposite axial direction (6; 4) into a respective nominal position relative to the housing part (86).

23. The torque transmitting device (16) according to claim 22, characterized in that the first module is displaceable or shifted into a respective nominal position relative to the housing portion (86) exclusively in an axial direction (4; 6) and the second module is displaceable or shifted into a respective nominal position exclusively in an opposite axial direction (6; 4).

24. The torque transmitting device (16) according to claim 6, characterized in that two radial bearings (96, 98) are provided, wherein the rotor (74) is arranged at least partially radially nested with the two radial bearings (96, 98).

25. The torque transmitting device (16) according to claim 7, characterized in that the rotor (74) is fastened at the first output (48).

26. The torque transmitting device (16) as claimed in claim 7, characterized in that the rotor support (76) has a first radial section (78) assigned to the output side (28) and a second radial section (80) which is releasably fastened at the first radial section (78), at which second radial section the rotor (74) is arranged.

27. The torque transmitting device (16) according to claim 8, characterized in that the torsional damper (122) is arranged in the wet chamber (70).

28. The torque transmitting device (16) as set forth in claim 9 wherein said separate radial and axial bearings (102) are rolling bearings.

29. The torque transmitting device (16) according to claim 9, characterized in that the input side (22) is fixed or supported at a second output (50) of the output side (28).

30. The torque-transmitting device (16) according to claim 11, characterized in that the plate clutch has an outer clutch plate carrier (46) which is connected to the output side (28) in a rotationally fixed manner.

31. The torque transmitting device (16) according to claim 30, wherein the outer clutch plate carrier (46) is connected to the second output (50) in a rotationally fixed manner.

32. The torque transmitting device (16) according to claim 30, characterized in that the outer clutch plate carrier (46) has a radial support section (54) which adjoins a clutch plate retaining section (52) of the outer clutch plate carrier (46) in the direction of the housing portion (86).

33. The torque transmitting apparatus (16) according to claim 32, characterized in that the support section (54) circumscribes a pressure chamber (62) for hydraulically operating the clutch device (24).

34. The torque transmitting device (16) of claim 1, characterized in that the clutch means (24) is a starting clutch.

35. The torque transmitting device (16) of claim 1, characterized in that the clutch means (24) is a hydraulically operable clutch.

36. The torque transmitting device (16) of claim 1, characterized in that the clutch means (24) is a wet clutch.

37. Drive train (2) for a motor vehicle with a drive unit (20) and a transmission (32), characterized in that a torque transmission device (16) according to one of claims 1 to 36 is arranged between the drive unit (20) and the transmission (32) for selective torque transmission from the drive unit (20) to the transmission (32), wherein a second wet chamber (116) is arranged nested with the dry chamber (84), in which second wet chamber the second clutch device (30) connected upstream of the transmission (32) is arranged, in which dry chamber the rotor (74) is arranged.

38. Drive train (2) according to claim 37, characterized in that said torque transfer arrangement (16) is arranged between the transmission unit (20) and said second clutch device (30) for selective torque transfer from the transmission unit (20) to the second clutch device (30).

39. Drive train (2) according to claim 37, characterized in that the second wet chamber (116) is at least partially arranged nested with the dry chamber (84) in a radial direction (8, 10).

40. Drive train (2) according to claim 37, characterized in that the second clutch device (30) is formed as a double clutch device for selective torque transmission between the output side (28) and a first transmission input shaft (34) and for selective torque transmission between the output side (28) and a second transmission input shaft (36).

41. Drive train (2) according to claim 40, characterized in that the dual clutch device is concentric or/and hydraulically operable.