Actuating device with centered release bearing, clutch assembly and drive module with the actuating device

Abstract

Clutch arrangement (1) for a vehicle, with a clutch device (3), with an input shaft (5) and with an output shaft (34), wherein the input shaft (5) and the output shaft (34) are connected and / or connectable to one another in a rotationally fixed manner via the clutch device (3), with an actuating device (2) for actuating the clutch device (3), - with a concentric slave cylinder (4) which has an annular piston (8) and an annular housing (9), wherein the annular piston (8) is axially movably received in an annular space (10) of the annular housing (9) which surrounds the main axis (100) and delimits the annular space (10) axially with respect to the main axis (100), so that a pressure chamber (11) which can be filled with an operating medium is formed between the annular piston (8) and the annular housing (9), - with a release bearing (6) which has an inner ring (20) and an outer ring (21), wherein the outer ring (21) is supported at least axially with respect to the main axis (100) on the annular piston (8), - with a pressure pot (7), wherein the inner ring (20) is supported at least axially with respect to the main axis (100) on the pressure pot (7), so that an actuating force (101) can be transmitted from the annular piston (8) via the release bearing (6) to the pressure pot (7), wherein the clutch device (3) is designed as a multi-disk clutch, wherein the clutch device (3) has an outer disk carrier (30) which is connected in a rotationally fixed manner to the input or output shaft (5, 34), on which outer disk carrier the pressure pot (7) is supported in a radial direction (104) with respect to the main axis (100), characterized in that the inner ring (20) or the pressure pot (7) has a centering section (27) for centering the release bearing (6) on the pressure pot (7).

Description

[0001] The invention relates to a clutch arrangement with an actuating device and a drive module with the actuating device and / or the clutch arrangement.

[0002] Concentric slave cylinders (CSC) are typically used in both hybrid and purely electric vehicle drive systems. These serve, for example, to separate the electric motor from the combustion engine or to change gears. Such slave cylinders essentially consist of an annular housing and an annular piston that can be axially displaced within the annular housing. When a master cylinder is actuated, the annular piston acts on a clutch-side release bearing, thus actuating, in particular engaging, the clutch.

[0003] The document DE 10 2020 109 989 A1 discloses a clutch device for a motor vehicle, comprising a shaft, the shaft extending axially, a clutch portion, the clutch portion being arranged coaxially to the shaft and rotating with the shaft, axial and radial forces acting on the shaft and / or the clutch portion upon rotation of the shaft, at least the radial forces being able to cause a radial offset of the clutch portion and / or a misalignment of the clutch portion and / or the shaft, and a release bearing, the release bearing being axially movable to transmit an actuating force to the clutch portion, the release bearing being guided through the shaft and / or on the shaft in the radial direction to compensate for the axial offset and / or the misalignment. Further prior art is cited in DE 10 2019 100 871 A1.

[0004] It is an object of the present invention to propose a clutch arrangement which is characterized by high operational reliability, in particular at high speeds.

[0005] This object is achieved by a clutch arrangement having the features of claim 1 and a drive module having the features of claim 10. Preferred or advantageous embodiments of the invention emerge from the subclaims, the following description and the attached figures.

[0006] The subject matter of the invention is an actuating device designed and / or suitable for actuating a clutch device. In particular, the actuating device serves to transmit an actuating force to the clutch device in order to open or close the clutch device. The clutch device is preferably designed as a friction clutch, preferably a friction-disk clutch. Particularly preferably, the actuating device is hydraulically actuated.

[0007] For this purpose, the actuating device has a concentric slave cylinder, also known as a “concentric slave cylinder (CSC),” which essentially comprises an annular piston and an annular housing. In particular, the concentric slave cylinder is designed as a central release cylinder. The annular piston and the annular housing are preferably arranged coaxially and / or concentrically to one another with respect to the main axis. The annular housing preferably has a central through-opening, in particular a bore, through which at least one shaft can be passed when the actuating cylinder is installed. The main axis is preferably defined by a rotational axis of the shaft. The annular piston is preferably rotationally symmetrical with respect to the main axis.

[0008] The annular housing has an annular space surrounding the main axis, wherein the annular piston is accommodated in the annular space of the annular housing so as to be axially movable with respect to the main axis. The annular space is delimited axially with respect to the main axis by the annular piston, so that a pressure chamber that can be filled with an operating medium is formed between the annular piston and the annular housing. In particular, the annular space is open on one side in the axial direction delimited by the annular piston and closed in an axially opposite direction. When the slave cylinder is actuated, the pressure on the operating medium is increased, wherein the actuating force is generated due to the rising pressure in the pressure chamber and is transmitted to the annular piston, so that the latter is disengaged axially. In particular, the operating medium is a hydraulic fluid, specifically hydraulic oil.

[0009] The actuating device comprises a release bearing, wherein the release bearing has an inner ring and an outer ring. In particular, the inner ring and / or the outer ring are arranged coaxially and / or concentrically to the main axis. Preferably, the release bearing is designed as a rolling bearing, wherein at least one row of rolling elements is arranged in a rolling manner between the inner ring and the outer ring. Specifically, in one installation situation of the release bearing, the at least one shaft is guided through the inner ring, wherein the inner ring is arranged radially spaced and / or unguided from the shaft.

[0010] Furthermore, the actuating device has a pressure pot, wherein the inner ring is supported at least axially with respect to the main axis on an inner diameter of the pressure pot, such that an actuating force can be transmitted from the annular piston via the release bearing to the pressure pot. In particular, the actuating force is to be understood as a pressure force directed axially with respect to a main axis. In other words, the release bearing is supported in the axial direction with the inner ring on the pressure pot and in the axially opposite direction with the outer ring on the annular piston. Preferably, the pressure pot is arranged coaxially and / or concentrically to the main axis. Particularly preferably, the release bearing and / or the pressure pot are arranged radially within the slave cylinder, in particular the annular housing.

[0011] Within the scope of the invention, it is proposed that the inner ring has a centering section which is designed and / or suitable for centering the release bearing on the pressure pot. Alternatively, the pressure pot has a centering section which is designed and / or suitable for centering the release bearing on the pressure pot. In particular, the centering section has the function of centering the release bearing, in particular the inner ring, on the pressure pot and of preventing decentering due to centrifugal force. Preferably, the inner ring and the pressure pot are additionally supported on one another via the centering section in the radial direction with respect to the main axis, so that the inner ring is supported on the pressure pot during operation due to the increasing centrifugal forces. Put simply, the centrifugal forces occurring on the release bearing during operation are diverted via the inner ring directly into the pressure pot.

[0012] The invention is based on the finding that with increasing speed, the centrifugal forces acting on the release bearing increase, causing the release bearing to become decentered with respect to its main axis. This decentering leads to increased imbalance, which in turn can cause damage and failure of the system. Particularly in combination with an electric machine, which typically reaches speeds of > 10,000 rpm, the centering of the release bearing during operation must be ensured. By arranging the centering section on the inner ring or on the pressure pot, the centering of the release bearing on the pressure pot can be ensured in a simple and cost-effective manner, and decentering caused by centrifugal force can be prevented.Another advantage is that only the existing release bearing needs to be slightly modified, while the remaining components, especially the slave cylinder, remain unchanged. Thus, an actuating device is proposed that is characterized by high operational reliability at high speeds.

[0013] In a specific embodiment, it is provided that the inner ring is supported on the pressure pot via the centering section in a radial direction, in particular a radially outward direction, and / or is centered coaxially with respect to the main axis on the pressure pot. In particular, the pressure pot has a central opening, wherein the centering section engages at least partially in the opening, so that the inner ring is supported on the pressure pot via the centering section in the radial direction. Particularly preferably, the pressure pot is in turn supported and / or centered on the coupling device radially or coaxially with the main axis.

[0014] Alternatively, it is provided that the pressure pot is supported on the inner ring via the centering section in a radially opposite direction, in particular a radially inward direction, and / or is centered coaxially with respect to the main axis. In particular, the inner ring has a central bore, wherein the centering section engages at least partially in the central bore, so that the inner ring is supported on the centering section of the pressure pot in the radially opposite direction. Particularly preferably, the pressure pot is in turn supported and / or centered on the coupling device radially or coaxially with the main axis.

[0015] Thus, the pressure pot serves to center the release bearing, in particular the inner ring, relative to the clutch device, so that the clutch device and the release bearing remain essentially axially centered to one another during operation.

[0016] In a further specific implementation, it is provided that the inner ring with the centering section is supported on an inner diameter of the pressure pot, in particular the central opening, in a form-fitting manner and / or without play in the radial direction. In particular, “free from play” is to be understood to mean that the centering section is received in the central opening of the pressure pot either with a precise fit or with a slight radial play. Preferably, a form-fitting connection between the pressure pot and the centering section of the inner ring is formed by inserting or pushing the inner ring with the centering section into the opening of the pressure pot coaxially to the main axis. Optionally, the centering section can be connected to the pressure pot in a force-fitting manner in the radial direction and / or in the circumferential direction with respect to the main axis, e.g. via a press fit.

[0017] Alternatively, it is provided that the pressure pot is supported with the centering section in the radially opposite direction on an inner diameter of the inner ring in a form-fitting manner and / or without play. In particular, “free from play” is to be understood to mean that the centering section is accommodated in the central bore of the inner ring either with a precise fit or with a slight radial play. Preferably, a form-fitting connection between the inner ring and the centering section of the pressure pot is formed by the inner ring with the bore being pushed or placed coaxially to the main axis onto the centering section of the pressure pot. Optionally, the centering section can be connected to the inner ring in a force-fitting manner in the radial direction and / or in the circumferential direction with respect to the main axis, e.g. via a press fit.

[0018] A simple centering of the release bearing is thus proposed, whereby the release bearing can be supported particularly securely on the pressure pot via the centering section if the centrifugal forces increase and the release bearing tends to decenter.

[0019] In a specific embodiment, the centering section is formed by a centering shoulder which runs around the main axis and is formed on an axial end face of the inner ring. In particular, the centering shoulder provides a radial centering surface for the pressure pot, which is preferably formed by an outer peripheral surface of the centering shoulder. For this purpose, the centering shoulder can penetrate the opening in the pressure pot, so that the pressure pot contacts the centering shoulder at the centering surface or rests against it. In particular, the centering shoulder is formed by a cylindrical projection which extends in the axial direction on the end face of the inner ring. Preferably, the centering shoulder forms a step or an annular shoulder which simultaneously forms an axial support surface for the pressure pot. Particularly preferably, the centering shoulder is arranged on an inner diameter of the inner ring.

[0020] Alternatively, it is provided that the centering section is formed by a centering shoulder which runs around the main axis and is formed on an axial end face of the pressure vessel. In particular, the centering shoulder provides a radial centering surface for the inner ring, which is preferably formed by an outer peripheral surface of the centering shoulder. For this purpose, the centering shoulder can penetrate the bore of the inner ring, so that the inner ring contacts the centering shoulder on the centering surface or rests on it. In particular, the centering shoulder is formed by a cylindrical extension which extends in the axial direction on the end face of the pressure vessel. Preferably, the centering shoulder forms a step or an annular shoulder which simultaneously forms an axial support surface for the inner ring. Particularly preferably, the centering shoulder is arranged on an inner diameter of the pressure vessel.Specifically, the inner ring has a centering contour that interacts with the centering section of the pressure vessel. For example, the centering contour can be formed by a radial shoulder, in particular a step or annular shoulder, which is formed circumferentially around the main axis on the inner circumference of the inner ring.

[0021] A centering section is thus proposed which can be produced particularly easily and cost-effectively, e.g. by means of a forming or separating manufacturing process, on the pressure pot or the inner ring.

[0022] In a further development, the inner ring is formed from a solid material and the outer ring from a sheet metal material. In particular, the inner ring is manufactured from a solid metallic material, in particular steel or aluminum, using a material-removing manufacturing process, preferably by machining. In particular, the outer ring is manufactured from a metal sheet, in particular steel or aluminum, using a forming manufacturing process. Thus, a release bearing is proposed that is characterized by cost-effective production and, at the same time, by a robust design of the inner ring.

[0023] In a further specification, it is provided that the outer ring has a radially outwardly directed outer ring flange and the annular piston has a support contour running around the main axis, wherein the outer ring is supported on the support contour via the outer ring flange at least axially with respect to the main axis. In particular, the outer ring flange serves to bridge a radial distance between the annular piston and the release bearing. Preferably, at least the outer ring is arranged radially and / or concentrically within the annular piston, wherein the outer ring flange is supported on a radial inner side of the annular piston via the support contour. In particular, the support contour is formed by a circumferential radial offset extending along an inner circumference of the annular piston. Preferably, the support contour forms a step or an annular shoulder, which simultaneously forms an axial support surface for the pressure pot.In principle, the outer ring flange can be supported directly on the axial support surface. Alternatively, the outer ring flange is supported on the support surface via at least one intermediate disk, preferably a shim disk. Thus, an actuating device is proposed that is characterized by a particularly compact and cost-effective design.

[0024] Another subject of the invention relates to a clutch assembly for a drive train of a vehicle. The drive train can be a purely electric or hybrid drive train. The clutch assembly has an input shaft and an output shaft. In particular, the input and output shafts are arranged coaxially and / or concentrically with respect to the main axis.

[0025] Furthermore, the clutch arrangement has at least one clutch device and the actuating device, as already described above, wherein the input shaft and the output shaft can be and / or are connected to one another in a rotationally fixed manner via the clutch device. For this purpose, the annular piston is operatively connected to the clutch device via the release bearing and the pressure pot for transmitting the actuating force. Preferably, the annular piston is moved out of the annular housing in the axial direction by a pressure build-up in the pressure chamber, such that the actuating force is transmitted to the pressure pot via the release bearing. Preferably, the clutch device is open in the unactuated state, such that the clutch device is closed when the annular piston is disengaged. Alternatively, however, the clutch device can also be closed in the unactuated state, such that the clutch device is opened when the annular piston is disengaged.Preferably, the input shaft and the output shaft are connected to one another in a rotationally fixed manner when the clutch device is in the closed state.

[0026] In a specific implementation, it is provided that the clutch device is designed as a multi-plate clutch, wherein the clutch device has an outer plate carrier connected in a rotationally fixed manner to one shaft and an inner plate carrier connected in a rotationally fixed manner to the other shaft, wherein the pressure pot is supported radially with respect to the main axis on the outer plate carrier. In particular, the outer plate carrier carries a plurality, preferably at least two, outer plates and the inner plate carrier carries a plurality, preferably at least two, inner plates, which are in frictional engagement with one another when the clutch device is in the closed state. In this case, the pressure pot can be supported axially with respect to the main axis on one of the inner or outer plates to transmit the actuating force. Particularly preferably, the pressure pot is guided on the outer plate carrier so as to be at least axially movable relative to the outer plate carrier.For this purpose, the pressure pot is supported radially and optionally circumferentially on the outer diameter of the outer plate carrier, preferably via a clearance fit. The radial support of the pressure pot in the outer plate carrier ensures particularly reliable and stable support of the release bearing under increasing centrifugal forces.

[0027] In a further specific embodiment, the clutch device is designed as a separating clutch, also referred to as a KO clutch. In particular, the separating clutch serves to interrupt the drive torque between the internal combustion engine and the electric motor in the hybrid drive train or to change gears in the electric drive train. The separating clutch is preferably designed as an automated separating clutch.

[0028] A further subject matter of the invention relates to a drive module with at least or exactly one electric machine and with the actuating device and / or the clutch arrangement, as already described above. In particular, the drive module is connected to a transmission device, wherein a torque path between the electric machine and the transmission module is influenced upon actuation of the actuating device. Optionally, the drive module is connected to an internal combustion engine, wherein a torque path between the internal combustion engine and the electric machine is influenced upon actuation of the actuating device. In simple terms, the clutch arrangement serves optionally to couple the electric machine to the transmission device or to the internal combustion engine. The transmission device can be a stepped automatic transmission, a dual-clutch transmission or a continuously variable transmission, e.g.CVT transmission. Particularly preferably, either the input or output shaft is drive-connected to the electric motor, with the outer disk carrier in turn being connected to the input shaft in a rotationally fixed manner. Due to the high speeds of the electric motor, the centrifugal forces acting on the release bearing can thus be reliably supported. Thus, a drive module with a high degree of functional reliability is proposed.

[0029] Further features, advantages, and effects of the invention will become apparent from the following description of preferred embodiments of the invention. These show: Fig. 1 is a sectional view of a clutch arrangement for a drive train of a vehicle as an embodiment of the invention; Fig. 2 a schematic representation of a drive train with the clutch arrangement; Fig. 3 a schematic sectional view of an actuating device for clutch arrangement from Fig. 1 in an alternative version.

[0030] Fig. Figure 1 shows a clutch assembly 1 for a hybrid or electric drive train of a vehicle in a schematic sectional view as an exemplary embodiment of the invention. The clutch assembly 1 is essentially composed of an actuating device 2 and a clutch device 3, which are arranged coaxially with respect to a main axis 100.

[0031] The actuating device 2 has a concentric slave cylinder 4, abbreviated to CSC, which is arranged coaxially and / or concentrically with an input shaft 5 of the clutch assembly 1. The main axis 100 is defined, for example, by a rotational axis of the input shaft 5. The slave cylinder 4 serves to generate an actuating force 101, which is transmitted to the clutch device 3 via a release bearing 6 and a pressure pot 7 in order to actuate the clutch device 3.

[0032] The slave cylinder 4 has an annular piston 8 and an annular housing 9, which are arranged coaxially and concentrically with respect to the main axis 100. The annular housing 9 has an annular space 10 open in an axial direction 102, wherein the annular piston 8 is accommodated in the annular space 10 so as to be axially displaceable with respect to the main axis 100.

[0033] The annular piston 8 rests radially against the annular housing 9 within the annular space 10, so that a pressure chamber 11 is delimited or sealed in the axial direction 102 by the annular piston 8. For example, the slave cylinder 4 is hydraulically actuated, wherein the pressure chamber 11 is filled with a hydraulic operating medium, e.g., hydraulic oil, in an operating state.

[0034] To seal the pressure chamber 11, the slave cylinder 4 has an outer and an inner sealing ring 12, 13, wherein the annular piston 8 bears sealingly against the annular housing 9 in a radial direction via the outer sealing ring 12 in a radial direction 104 and via the inner sealing ring 13 in a radially opposite direction 105 within the annular chamber 10. The two sealing rings 12, 13 are each designed as an elastomer seal, in particular as grooved sealing rings, which are captively attached to the annular piston 8. For this purpose, the slave cylinder 4 has a retaining ring 14, which is designed to secure the two sealing rings 12, 13 in an axially opposite direction 103 with respect to the main axis 100 against loss and / or slipping on the annular piston 8.

[0035] The annular housing 9 has a fluid opening 15 on a radial outer side, via which the pressure chamber 11 is or can be fluidly connected to a master cylinder (not shown). The annular housing 9 is accommodated in a housing 16 of the clutch assembly 1, wherein an intermediate space 17 is formed radially between the annular housing 9 and the housing 16, which space 17 surrounds the main axis 100 and is or can be fluidly connected to the master cylinder via a hydraulic path. The fluid opening 15 connects the pressure chamber 11 to the intermediate space 17. For example, the housing 16 is designed as a transmission housing or transmission housing section of a hybrid transmission (DHT).

[0036] The slave cylinder 4 has a first and a second sealing ring 18, 19, which seal the intermediate space 17 in a fluid-tight manner. For this purpose, the two sealing rings 18, 19 are fixed to the radial outer side of the ring housing 9, wherein the first sealing ring 18 bears against the housing 16 in the radial direction 104 in order to seal the intermediate space 17 in the axial direction 102, and the second sealing ring 19 bears against the housing 16 in the radial direction 104 in order to seal the intermediate space 17 in the opposite axial direction 103, wherein the fluid opening 15 is arranged axially between the two sealing rings 18, 19 and opens into the intermediate space 17.

[0037] When the master cylinder is actuated, a hydraulic column is displaced toward the slave cylinder 4, with the operating medium flowing into the pressure chamber 11 via the fluid opening 15, thereby increasing the fluid pressure in the pressure chamber and applying the actuating force 101 to the annular piston 8. The annular piston 9 is moved in the axial direction 102, and the actuating force 101 is transmitted to the clutch device 3 via the release bearing 6 and the pressure pot 7.

[0038] The release bearing 6 has an inner ring 20 and an outer ring 21, with a plurality of rolling elements 22 arranged in a rolling manner between the inner and outer rings 20, 21. For example, the release bearing 6 is designed as an angular contact ball bearing, which is designed and / or suitable for absorbing radial and axial forces with respect to the main axis 100.

[0039] The release bearing 6 is arranged radially inside the annular piston 8 or concentrically to the annular piston 8, wherein the inner ring 20 is supported on the pressure pot 7 in the axial direction 102 and the outer ring 21 is supported on the annular piston 8 in the opposite axial direction 103 via an intermediate disk 26, e.g. a shim disk. For this purpose, the outer ring 21 has an outer ring flange 23 which extends essentially in a radial plane of the main axis 100 in order to bridge a radial distance between the annular piston 8 and the release bearing 6. For example, the outer ring flange 23 is designed as an annular flange surrounding the main axis 100.

[0040] The annular piston 8 accordingly has a support contour 24 on its inner circumference, via which the outer ring flange 23 is supported on the annular piston 8 in the axially opposite direction 103. The support contour 24 is formed by a radial shoulder, in particular a step or annular shoulder, which is formed circumferentially to the main axis 100. The support contour 24 thus has an axial support surface 25, on which the outer ring flange 23 is supported via the intermediate disk 26 in the axially opposite direction 103. The support surface 25 is to be understood as an annular surface which extends in a radial plane of the main axis 100.

[0041] Since in reality the rotational axes of the release bearing 6 and the clutch assembly are not ideally centered relative to each other, an axial offset between the rotational axes can occur during operation. At speeds above 10,000 rpm, as typically occurs in electric drive trains, this effect is further amplified by the centrifugal forces acting on the release bearing 6. The resulting decentering of the release bearing 20 leads to increased imbalance, which can lead to the failure of the clutch assembly 1.

[0042] As from the Fig. 1, the inner ring 20 has a centering section 27 on its inner diameter, which serves to center the inner ring 20 on the pressure pot 7. The centering section 27 is formed as a centering shoulder which runs around the main axis 100 and is formed or molded onto an axial end face of the inner ring 20. The centering section 27 thus forms a step or an annular shoulder which provides an axial support surface 28 and a radial centering surface 29 for the pressure pot 7. The further support surface 28 is to be understood as an annular surface which extends in a further radial plane of the main axis 100. The radial centering surface 29 is to be understood as an outer peripheral surface of the centering section 27 which extends essentially around the main axis 100 or parallel to the main axis 100.

[0043] The centering section 27 engages in a central opening in the pressure pot 7, so that the inner ring 20 can be supported via the centering section 27 in the radial direction 104 on the inner diameter of the pressure pot 7 if the centrifugal forces predominate and the release bearing 6 tends to become decentered. This ensures radial centering of the release bearing 6, in particular of the rotating inner ring 20, relative to the clutch device 3 or coaxially to the main axis 100, thereby preventing imbalance at increasing speeds and the associated damage to the clutch assembly 1.

[0044] The clutch device 3 has an outer disk carrier 30 and an inner disk carrier 31, wherein the outer disk carrier 30 carries a plurality of outer disks 32 formed as steel disks, and the inner disk carrier 31 carries a plurality of inner disks 33 formed as friction disks, which are arranged alternately one behind the other. The outer disk carrier 30 is rotationally fixedly connected to the input shaft 5, and the inner disk carrier 31 is rotationally fixedly connected to an output shaft 34. The input shaft 5 and the output shaft 34 are arranged coaxially and / or concentrically with respect to the main axis 100, wherein the input shaft 5 is formed as a hollow shaft and the output shaft 34 is formed as a solid shaft guided through the hollow shaft.

[0045] When the actuating device 2 is actuated, the actuating force 101 is transmitted via the pressure pot 7 to the outer and inner plates 32, 33, respectively, whereby the inner and outer plates 32, 33 are frictionally pressed together to close the clutch device 3. For this purpose, the pressure pot 7 is supported in the axial direction 102 on one of the outer plates 32, wherein the pressure pot 7 is simultaneously supported in the radial direction 104 and optionally in the circumferential direction with respect to the main axis 100 on the outer plate carrier 30. For example, the pressure pot 7 is thus positively supported radially between the inner ring 20 and the outer plate carrier 30, so that the inner ring 20 is supported in the radial direction without play or with only a slight radial play.

[0046] Fig. 2 shows a drive train 35 for a vehicle, wherein the drive train 35 comprises a drive module 36 with the clutch assembly 1. In the exemplary embodiment shown, the drive module 36 is designed as a so-called hybrid module, wherein the drive module 36 for this purpose comprises an electric machine 37, which is drive-coupled and / or can be coupled to an internal combustion engine 38 via the clutch assembly 1.

[0047] For example, the input shaft 5 can be defined by a crankshaft of the internal combustion engine 38, and the output shaft 34 by a rotor shaft of the electric machine 36, wherein the clutch device 3 is designed as a separating clutch, also called a KO clutch, for interrupting a drive torque between the internal combustion engine 38 and the electric machine 38. For example, the clutch assembly 1 and the electric machine 37 together form the drive module 36.

[0048] The drive train 35 also has a transmission device 39, which is connected on the input side to the drive module 36 and on the output side to a differential 40. A torque generated by the internal combustion engine 38 and / or the electric motor 37 is transmitted or translated via the transmission device 39 to the differential 40 and thus to the driven wheels 41 of the vehicle. For example, the transmission device 39 can be designed as a dual-clutch transmission.

[0049] Fig.3 shows an alternative embodiment of the actuating device 2, wherein the pressure pot 7, instead of the inner ring 20, has the centering section 27 on its inner diameter, which serves to center the inner ring 20 on the pressure pot 7. The centering section 27 is formed as a centering shoulder which surrounds the main axis 100 and is formed or molded onto an axial end face of the pressure pot 7. The centering section 27 thus forms a step or an annular shoulder which provides an axial support surface 28 and a radial centering surface 29 for the inner ring 20. The further support surface 28 is to be understood as an annular surface which extends in a further radial plane of the main axis 100. The radial centering surface 29 is to be understood as an outer peripheral surface of the centering section 27, which extends essentially around the main axis 100 or parallel to the main axis 100.

[0050] The centering section 27 engages in a central bore of the inner ring 20, so that the inner ring 20 can be supported on the centering section 27 of the pressure pot 7 at the inner diameter in the radially opposite direction 105 if the centrifugal forces predominate and the release bearing 6 tends to become decentered. This ensures radial centering of the release bearing 6, in particular of the rotating inner ring 20, relative to the clutch device 3 or coaxially to the main axis 100, thereby preventing imbalance at increasing speeds and the associated damage to the clutch assembly 1.

[0051] The inner ring 20 also has a centering contour 42, which interacts with the centering section 27. For example, the centering contour 42 is formed by a radial shoulder, in particular a step or annular shoulder, which is formed circumferentially relative to the main axis 100. Thus, the centering contour 42 serves to accommodate the centering section 27 radially offset and / or flush with the inner diameter of the inner ring 20. List of reference symbols 1 Coupling arrangement 2 Actuating device 3 Coupling device 4 slave cylinders 5 Input shaft 6 release bearings 7 Pressure cooker 8 ring pistons 9 ring housing 10 Annular space 11 Printing room 12 outer sealing ring 13 inner sealing ring 14 Retaining ring 15 Fluid opening 16 Gearbox housing 17 gap 18 first sealing ring 19 second sealing ring 20 inner ring 21 Outer ring 22 rolling elements 23 Outer ring flange 24 Support contour 25 support surface 26 Intermediate disc 27 Centering section 28 additional support areas 29 Centering surface 30 outer disc carriers 31 inner disc carrier 32 outer slats 33 inner slats 34 Output shaft 35 Powertrain 36 drive module 37 electric machine 38 internal combustion engine 39 Gear device 40 Differential 41 wheels 42 Centering contour 100 Main axis 101 operating force 102 axial direction 103 axial opposite direction 104 radial direction 105 radial opposite direction

Claims

[1] Clutch arrangement (1) for a vehicle, with a clutch device (3), with an input shaft (5) and with an output shaft (34), wherein the input shaft (5) and the output shaft (34) are connected and / or connectable to one another in a rotationally fixed manner via the clutch device (3), with an actuating device (2) for actuating the clutch device (3), - with a concentric slave cylinder (4) which has an annular piston (8) and an annular housing (9), wherein the annular piston (8) is axially movably received in an annular space (10) of the annular housing (9) which surrounds the main axis (100) and delimits the annular space (10) axially with respect to the main axis (100), so that a pressure chamber (11) which can be filled with an operating medium is formed between the annular piston (8) and the annular housing (9), - with a release bearing (6) which has an inner ring (20) and an outer ring (21), wherein the outer ring (21) is supported at least axially with respect to the main axis (100) on the annular piston (8), - with a pressure pot (7), wherein the inner ring (20) is supported at least axially with respect to the main axis (100) on the pressure pot (7), so that an actuating force (101) can be transmitted from the annular piston (8) via the release bearing (6) to the pressure pot (7), wherein the clutch device (3) is designed as a multi-disk clutch, wherein the clutch device (3) has an outer disk carrier (30) which is connected in a rotationally fixed manner to the input or output shaft (5, 34), on which outer disk carrier the pressure pot (7) is supported in a radial direction (104) with respect to the main axis (100), characterized by that the inner ring (20) or the pressure pot (7) has a centering section (27) for centering the release bearing (6) on the pressure pot (7). [2] Coupling arrangement (1) according to claim 1, characterized by that the coupling device (3) is designed as a separating clutch, also referred to as a KO clutch. [3] Coupling arrangement (1) according to claim 1 or 2, characterized by that the inner ring (20) is supported on the pressure pot (7) via the centering section (27) in a radial direction (104) with respect to the main axis (100) and / or is coaxially centered, or that the pressure pot (7) is supported on the inner ring (20) via the centering section (27) in a radially opposite direction (105) with respect to the main axis (100) and / or is coaxially centered. [4] Coupling arrangement (1) according to claim 1, 2 or 3, characterized bythat the inner ring (20) with the centering section (27) is supported in a form-fitting manner and / or without play on an inner diameter of the pressure pot (7) in a radial direction (104) with respect to the main axis (100), or that the pressure pot (7) with the centering section (27) is supported in a form-fitting manner and / or without play on an inner diameter of the inner ring (20) in a radial opposite direction (105) with respect to the main axis (100). [5] Coupling arrangement (1) according to one of the preceding claims, characterized by that the centering section (27) is formed by a centering shoulder which runs around the main axis (100) and is formed on an axial end face of the inner ring (20) or the pressure pot (7). [6] Coupling arrangement (1) according to one of the preceding claims, characterized by that the inner ring (20) is made of a solid material and the outer ring (21) is made of a sheet material. [7] Coupling arrangement (1) according to one of the preceding claims, characterized by that the outer ring (21) has a radially outwardly directed outer ring flange (7) and the annular piston (10) has a support contour (24) surrounding the main axis, wherein the outer ring (21) is supported on the support contour (24) via the outer ring flange (7) at least axially with respect to the main axis (100). [8] Drive module (36) for a vehicle, with at least one electric machine (37), characterized by a coupling arrangement (1) according to one of claims 1 to 7.

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