Abstract:
A dual clutch for coupling an engine-side input shaft with a first transmission-side and/or a second transmission-side output shaft. A first clutch has a first pressure plate, which is axially mobile relative to a first counter plate, for coupling with a first clutch disk connected to the first output shaft. A second clutch has a second pressure plate, which is axially mobile relative to a second counter plate, for coupling with a clutch disk connected to the second output shaft. A clutch cover is connected to the first and second counter plates. An actuator displaces the first and/or the second pressure plate. The actuator is radially supported on the input side on the input shaft by the clutch cover and a torsional vibration damper, which is connected to the clutch cover and is radially mounted on the output side on one of the output shafts and/or on a transmission housing.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation application of PCT/DE/000266 filed Mar. 15, 2011, which in turn claims the priority DE 10 2010 012 862.7 filed Mar. 25, 2010, the priority of these applications is hereby claimed and these applications are incorporated by reference herein. 
    
    
     BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The invention relates to a dual clutch for coupling a motor-side input shaft substantially without an interruption in tractive force to two transmission-side output shafts which are arranged coaxially with respect to one another. 
     2. Description of the Prior Art 
     EP 1 524 446 A1 discloses a dual clutch for coupling a motor-side input shaft to two different output shafts which are arranged coaxially with respect to one another. The dual clutch has a first clutch and a second clutch, wherein the respective clutch has a pressure plate which can move axially relative to an opposing plate and has the purpose of coupling the respective clutch to the associated output shaft. In addition, a co-rotating clutch cover is provided which is screwed to the second opposing plate of the second clutch, which is in turn screwed to the first opposing plate of the first clutch. In addition, a secured activation device for moving the first pressure plate and/or the second pressure plate is provided. The activation device is screwed in the axial direction to a secured transmission housing, wherein, in order to absorb the forces occurring at the activation device, a multiplicity of attachment means which extend axially are provided. 
     There is a constant need for the design of dual clutches to be simplified and, in particular, for forces which occur to be dissipated easily. 
     SUMMARY OF THE INVENTION 
     An object of the invention is to provide a dual clutch which permits a simplified design which makes it possible, in particular, for forces which occur to be dissipated in a simplified fashion. 
     The dual clutch according to the invention for coupling a motor-side input shaft to a first transmission-side output shaft and/or to a second transmission-side output shaft has a first clutch which has a first pressure plate which can be moved axially relative to a first opposing plate and has the purpose of coupling a first clutch plate which is connected to the first output shaft. In addition, a second clutch is provided which has a second pressure plate which can move axially relative to a second opposing plate and has the purpose of coupling a second clutch plate which is connected to the second output shaft. A co-rotating clutch cover is connected to the first opposing plate and to the second opposing plate. In addition, an activation device for moving the first pressure plate and/or the second pressure plate is provided, wherein according to the invention the activation device is supported on the input shaft on the input side via the clutch cover and a drive plate or flex plate which is indirectly or directly connected to the clutch cover, and said activation device is mounted radially on the output side on one of the output shafts and/or on a transmission housing. 
     Since the activation device is supported on the input side, that is to say at the location where the force flux is applied to the dual clutch from the input shaft, and on the output side, that is to say at the location where the force flux leaves the dual clutch via the respective output shaft, the activation device&#39;s own weight and drag torques occurring at the activation device are, in particular, transferred radially. In particular, it is not necessary to transfer forces occurring in the radial direction via axially extending attachment means, with the result that large shearing forces which occur at the axial attachment means are avoided. Axial forces occurring during the axial displacement of the respective pressure plate can, in particular, be particularly easily transferred by virtue of the fact that at its axial end the activation device abuts against the transmission housing. In order to transfer the forces occurring in the radial direction, a fixed bearing or sliding bearing of simple design is sufficient in order to support the activation device radially, in particular on the output side. At the same time, the activation device is mounted on the output side with the result that it is still possible for a relative movement of the activation device to occur in the circumferential direction and/or in the axial direction with respect to the output shaft, or transmission housing, which is used as a support. In addition, the activation device is supported radially on the input side via components which are present in any case, with the result that the forces which occur can be distributed in the radial direction between at least two supporting locations. This leads to a simplified design of the dual clutch and simplified dissipation of forces occurring at the activation device. In addition, the component loading at the supporting points may be comparatively small, with the result that the corresponding components can be produced and mounted in a correspondingly simple and cost-effective fashion. 
     The respective pressure plate can be connected via a toothing to the respective output shaft in a rotationally fixed but axially movable fashion. The first opposing plate or the second opposing plate can protrude radially inward, as a separate component, from a radially outer transmission housing wall and/or from the clutch cover. It is also possible for the first opposing plate or the second opposing plate to be formed in one piece with the transmission housing wall and/or with the clutch cover. For example, one of the opposing plates can be formed by a flywheel which is connected to the motor-side input shaft, or an output flange of a two-mass flywheel. The respective clutch plate can have in each case one friction lining on, in particular, axial end faces pointing away from one another, which friction lining can enter into frictionally locking contact with a friction lining which is provided, if appropriate, on the associated opposing plate and/or pressure plate, in order to close the respective clutch. The respective clutch plate can be connected in a rotationally fixed but axially movable fashion via a toothing to the respective output shaft. The respective pressure plates and opposing plates are configured, in particular, as separate, functionally separated components, with the result that what is referred to as a “four-plate design” is possible for the dual clutch without significantly increasing the installation space. The dual clutch can be connected directly or indirectly, in particular, to a vibration damper, in particular two-mass flywheel and/or centrifugal force pendulum and/or mass pendulum, which is mounted upstream on the motor side and/or downstream on the transmission side. In addition, the respective clutch disk can, in particular, be damped using a two-mass flywheel and/or centrifugal force pendulum and/or mass pendulum. The drive plate and/or the flex plate can be embodied by means of a rigid plate (drive plate) or bendable and/or flexible plate (flex plate), wherein the plate can transmit torques in order to be able to apply the torque of the input shaft to the dual clutch. As a result of the flexible configuration of the plate, vibrations which occur can be damped or attenuated entirely or partially. 
     In particular, the activation device is supported on one of the output shafts by means of a bearing, in particular a radial needle bearing. The bearing can have, in particular in the axial direction, a sufficiently large extent with the result that the forces applied by the activation device can be distributed over a correspondingly large surface. The component loading of the bearing can therefore be correspondingly low. In particular, if the bearing is configured as a needle bearing, the bearing consequently has only a small extent in the radial direction, with the result that the installation space is not substantially increased in the radial direction. In particular, a gap can be provided between the activation device and the outer output shaft, by means of which gap the activation device is arranged spaced apart from the outer output shaft. The gap can, in particular, be bridged exclusively by means of the bearing, with the result that further supports of the activation device on the corresponding output shaft, for example via an additional sliding bearing, are not necessary. 
     The bearing is preferably arranged at an input-side and/or output-side axial end of the activation device. The bearing can, as a result, be inserted into the activation device at the input end and/or output end. As a result, the mounting of the bearing is simplified. It is not necessary to insert the bearing into the activation device, for example centrally with respect to the activation device, using a tool up to a point which is comparatively difficult to access. In particular, it is possible to press the bearing into the activation device, and it is therefore not necessary to secure the bearing axially using securing rings. 
     The activation device particularly preferably has a radially outwardly protruding bearing block, in particular running around in an annular shape, in order to bear against a radially inwardly pointing bearing face of the transmission housing, wherein, in particular, the curvature of the bearing block is selected such that a theoretical center point of the curvature of the bearing block lies substantially on a rotational axis of the first output shaft and of the second output shaft. As a result of the bearing block, tilting torques acting on the activation device can be compensated and at the same time forces occurring in the radial direction can be transferred to the transmission housing. The curvature of the bearing block provides line-shaped contact between the activation device and the transmission housing, with the result that tilting of the activation device in the transmission housing is avoided. 
     In particular, a cover bearing is provided between the activation device and the clutch cover, where, in particular, the activation device is mounted on the output side in the axial direction at least partially at the height of the cover bearing. As a result of the cover bearing, forces occurring at the activation device can be transferred to the clutch cover. At the same time it is ensured that the co-rotating clutch cover can carry out a relative movement with respect to the activation device. In particular if the bearing of the activation device is not provided in an axially offset fashion with respect to the cover bearing, forces occurring in the activation device can be transferred radially outwardly via the cover bearing or radially inwardly via the bearing arrangement without unnecessarily large tilting torques and bending torques being produced. 
     The activation device is particularly preferably connected to the first pressure plate via a first activation pot which has a substantially radially extending first part, and is particularly preferably connected to the second pressure plate via a second activation pot which has a substantially radially extending second part, wherein the cover bearing is spaced apart both from the first part of the first activation pot and from the second part of the second activation pot, on the input side or on the output side. If the cover bearing is offset axially on the input side with respect to the first part and with respect to the second part, the forces which occur can be taken up relatively far toward the inside of the dual clutch and can be transferred to the input shaft via the clutch cover. A part of the clutch cover which protrudes in the axial direction is therefore avoided or greatly reduced, with the result that correspondingly small bending torques act on the clutch cover. If the clutch cover is spaced apart on the output side both from the first part and from the second part, the first activation pot and the second activation pot are arranged substantially within the clutch cover. As a result it is not necessary for activation fingers which are connected to the respective pressure plate to be guided through corresponding openings in the clutch cover. The clutch pot can instead engage around both the first activation pot and the second activation pot, without the need to provide openings in the activation pot which can weaken the clutch pot. The clutch pot can as a result be configured in a simpler way and can transmit relatively large forces. 
     In particular, the cover bearing is arranged in the axial direction next to the activation device, wherein the cover bearing is connected by means of an, in particular, tubular sheet-metal securing element which is connected to the activation device. Since the cover bearing does not have to be arranged radially outside the activation device, the installation space can be reduced in an axial direction. Instead, the cover bearing can be arranged in a region where the cover bearing is arranged in the axial direction at the level of another component, for example one of the pressure plates. As a result, the installation space of the dual clutch is not significantly increased in the axial direction. As a result of the sheet-metal securing element, a radially outwardly protruding attachment can be formed in order to accommodate the cover bearing in a captive fashion between the sheet-metal securing element and the activation device. The sheet-metal securing element can, in particular, be connected to the activation device in a captive fashion on the output side, for example using a securing ring. If appropriate, the sheet-metal securing element can bear on the bearing provided between the activation device and one of the output shafts and can be supported in the radial direction. This leads to a simple design with which forces which occur can be particularly easily transferred. 
     In particular, the activation device has a first piston for axially moving the first pressure plate using a first activation pot and a second piston for axially moving the second pressure plate by means of a second activation pot, wherein the activation travel of the first piston corresponds substantially to the displacement travel of the first pressure plate and/or the activation travel of the second piston corresponds substantially to the displacement travel of the second pressure plate. As a result, a directly activated, transmission-free clutch is formed. Pivoting of the respective activation pot does not take place, with the result that the corresponding components for permitting pivoting of the respective activation pot can be eliminated. Assuming an ideally rigid activation pot, the activation travel of the respective piston corresponds precisely to the displacement travel of the associated pressure plate. The displacement travel of the respective pressure plate therefore differs from the activation travel of the associated piston only by the travel distance in the axial direction by which the associated activation pot is bent elastically when the respective clutch is activated. 
     The activation device preferably has a first annular pressure cylinder for moving the first pressure plate, and a second annular pressure cylinder for moving the second pressure plate, wherein the first pressure cylinder and the second pressure cylinder are arranged coaxially with respect to one another. The coaxial arrangement of the pressure cylinders which are configured in an annular shape produces a particularly compact and installation-space-saving design for the activation device. As a result of the compact design of the activation device, the activation device has a comparatively low intrinsic weight, with the result that the activation device&#39;s own weight can be transferred from the clutch cover without difficulties. 
     A first activation pot, which is connected to the first pressure plate, is particularly preferably mounted on the activation device by means of a first pot bearing, and the first pot bearing is arranged at least partially at the level of the first pressure cylinder and/or at the level of the second pressure cylinder radially inwardly with respect to the first pressure cylinder and/or radially inwardly with respect to the second pressure cylinder. Additionally or alternatively, a second activation pot which is connected to the second pressure plate is preferably mounted on the activation device by means of a second pot bearing, and the second pot bearing is arranged at least partially at the level of the first pressure cylinder and/or at the level of the second pressure cylinder radially inwardly with respect to the first pressure cylinder and/or radially inwardly with respect to the second pressure cylinder. The first pot bearing or the second pot bearing can be arranged in the axial direction substantially at least partially at the same axial height with respect to the first pressure cylinder and/or with respect to the second pressure cylinder, with the result that, when viewed in the radial direction, the first pot bearing or the second pot bearing at least partially overlap the first pressure cylinder and/or the second pressure cylinder. The first pressure cylinder and/or the second pressure cylinder can have a correspondingly larger diameter, with the result that the first pot bearing and/or the second pot bearing can be arranged with a correspondingly smaller diameter within the first pressure cylinder and/or within the second pressure cylinder. In particular, the first pot bearing and/or the second pot bearing are guided in a substantially axially extending, preferably annular depressions in the activation device and, in particular, supported both radially inwardly and radially outwardly on the activation device. A first piston which can be activated by the first pressure cylinder does not have to act on the radially inner end of the first activation pot but instead can act on the first activation pot, spaced somewhat apart from the radially inner end of the first activation pot. Correspondingly, a second piston which can be activated by the second pressure cylinder does not have to act on the radially inner end of the second activation pot but rather can act on the second activation pot, spaced somewhat apart from the radially inner end of the second activation pot. As a result of the spaced-apart support of the respective activation pot, forces occurring during the activation of the activation device can also be transferred via the respective pot bearing, with the result that the bending torques which occur in the respective activation pot can be reduced. As a result, a simplified design is made possible, which, in particular, permits simplified dissipation of forces which occur. Since the respective pot bearing does not necessarily have to be arranged axially next to the activation device but instead can be moved into the activation device, the installation space of the dual clutch can be reduced significantly in the axial direction. This permits the output shafts to be correspondingly shortened, with the result that smaller bending torques occur, and/or relatively large loads can be transferred, in the output shafts. A transmission train with such a dual clutch can therefore be made smaller, more compact and at the same time more robust and efficient. 
     The invention also relates to a dual clutch for coupling a motor-side input shaft to a first transmission-side output shaft and/or to a second transmission-side output shaft, comprising a first clutch which has a first pressure plate which can move axially relative to a first opposing plate and has the purpose of coupling a first clutch plate which is connected to the first output shaft. The dual clutch also has a second clutch which has a second pressure plate which can move axially relative to a second opposing plate and has the purpose of coupling a second clutch disk which is connected to the second output shaft. In addition, an activation device is provided for moving the first pressure plate and/or the second pressure plate, wherein the activation device has a first annular pressure cylinder for moving a first activation pot which is connected to the first pressure plate, and a second annular pressure cylinder for moving a second activation pot which is connected to the second pressure plate. The first activation pot is mounted on the activation device via a first pot bearing, and the first pot bearing is arranged at least partially at the level of the first pressure cylinder and/or at the level of the second pressure cylinder, radially inwardly with respect to the first pressure cylinder and/or radially inwardly with respect to the second pressure cylinder. Additionally or alternatively, the second activation pot is mounted on the activation device via a second pot bearing, and the second pot bearing is arranged at least partially at the level of the first pressure cylinder and/or at the level of the second pressure cylinder radially inwardly with respect to the first pressure cylinder and/or radially inwardly with respect to the second pressure cylinder. The dual clutch can, in particular, be embodied and developed as described above. The dual clutch which is embodied in this way is shorter in the axial direction owing to the radial nesting of the bearing and pressure piston. 
     The first activation bearing or the second activation bearing can be arranged in the axial direction essentially at least partially at the same axial height with respect to the first pressure cylinder and/or with respect to the second pressure cylinder, with the result that, when considered in the radial direction, the first activation bearing and the second activation bearing at least partially overlap the first pressure cylinder and/or the second pressure cylinder. The first pressure cylinder and/or the second pressure cylinder can have a correspondingly larger diameter, with the result that the first activation bearing and/or the second activation bearing can be arranged with a correspondingly smaller diameter within the first pressure cylinder and/or within the second pressure cylinder. In particular, the first activation bearing and/or the second activation bearing are guided in a substantially axially extending, preferably annular depressions in the activation device, and in particular supported both radially inwardly and radially outwardly on the activation device. A first piston which can be activated by the first pressure cylinder does not have to act on the radially inner end of the first activation element but instead can act on the first activation element, spaced somewhat apart from the radially inner end of the first activation element. Correspondingly, a second piston which can be activated by the second pressure cylinder does not have to act on the radially inner end of the second activation element but rather can act on the second activation element, spaced somewhat apart from the radially inner end of the second activation element. As a result of the spaced-apart support of the respective activation element, forces which occur during the activation of the activation device can also be transferred via the respective activation bearing, with the result that the bending torques which occur in the respective activation element, such as the activation pot, can be reduced. As a result, a simplified design is made possible which permits, in particular, simplified dissipation of forces which occur. Since the respective activation bearing does not necessarily have to be arranged axially next to the activation device but instead can be moved into the activation device, the installation space of the dual clutch can be reduced significantly in the axial direction. This permits the output shafts to be correspondingly shortened, with the result that smaller bending torques occur, and/or larger loads can be transferred in the output shafts. A transmission train having such a dual clutch can therefore be made smaller, more compact and at the same time more robust and more efficient. 
     The invention also relates to a transmission train for a motor vehicle having a motor-side input shaft, a first transmission-side output shaft, a second transmission-side output shaft and a dual clutch for coupling the input shaft to the first output shaft and/or the second output shaft, wherein the dual clutch can be embodied and developed as described above. As a result of the dual clutch, a simplified design is obtained for the transmission train which permits, in particular, simplified dissipation of forces occurring at the activation device. 
     The invention will be explained below by way of example on the basis of preferred exemplary embodiments and with reference to the appended drawings, in which: 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  shows a schematic, simplified sectional view of a dual clutch according to the invention in a first embodiment, 
         FIG. 2  shows a schematic, simplified sectional view of a dual clutch according to the invention in a second embodiment, 
         FIG. 3  shows a schematic, simplified sectional view of a dual clutch according to the invention in a third embodiment, 
         FIG. 4  shows a schematic, simplified sectional view of a dual clutch according to the invention in a fourth embodiment, 
         FIG. 5  shows a schematic, simplified sectional view of a dual clutch according to the invention in a fifth embodiment, 
         FIG. 6  shows a schematic, simplified sectional view of a dual clutch according to the invention in a sixth embodiment, and 
         FIG. 7  shows a schematic, simplified sectional view of a dual clutch according to the invention in a seventh embodiment. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     In the dual clutch  10  illustrated in  FIG. 1 , an input shaft  12  is connected to a rotational oscillation damper in the form of a flex plate  14 . The flex plate  14  is connected to a first opposing plate  16  of a first clutch  18 . The first opposing plate  16  is also connected to a starter ring  20 . The first clutch  18  also has a first pressure plate  22  which can be moved toward the first opposing plate  16  in order to connect a first clutch disk  24  in a frictionally locking fashion between the first opposing plate  16  and the first pressure plate  22 . The first clutch plate  24  is connected in a rotationally fixed but axially movable fashion to a first output shaft  28  via a toothing  26 . In the illustrated exemplary embodiment, the first clutch plate  24  has a first two-mass flywheel  30  radially on the inside with respect to the first opposing plate  16  and with respect to the first pressure plate  22 . The first opposing plate  16  is also connected to a second opposing plate  32  of a second clutch  34 . The second clutch  34  has a second pressure plate  36  which can be moved toward the second opposing plate  32  in order to couple a second clutch plate  38  in a frictionally locking fashion. The second clutch plate  38  can also be connected in a rotationally fixed but axially movable fashion to a second output shaft  40  via a toothing  26 . In the illustrated exemplary embodiment, the first clutch plate  38  has a second two-mass flywheel  42 . An input-side direction  44  is defined by the side on which the force flux is applied to the dual clutch  10  from the input shaft  12 . Correspondingly, an output-side direction  46  is defined by the side on which the force flux leaves the dual clutch  10  via the output shafts  28 ,  40 . 
     In order to activate the first pressure plate  22  and the second pressure plate  36 , an activation device  48  is provided. The activation device  48  has a first annular pressure cylinder  50 , by means of which a first piston  52  can be disengaged. As a result, a first activation pot  54  can be pushed in a purely axial fashion in order to move the first pressure plate  22  toward the first opposing plate  16  in order to close the first clutch  18 . Correspondingly, the activation device  48  has a second annular pressure cylinder  56 , by means of which a second piston  58  can be disengaged in order to move a second activation pot  60  in a purely axial fashion. The second pressure plate  36  is moved toward the second opposing plate  32  by the second activation pot  60  in order to close the second clutch  34 . The first activation pot  54  is mounted on the activation device  48  by means of a first pot bearing  53  in an annular depression  55  of the activation device  48 . The first pot bearing  53  is arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56  radially on the inside with respect to the first pressure cylinder  50  and radially on the outside with respect to the second pressure cylinder  56 . The second activation pot  60  is supported by means of a second pot bearing  57  which is arranged axially next to the activation device  48 . However, the second pot bearing  57  can also be arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56  radially on the inside with respect to the first pressure cylinder  50  and radially on the inside with respect to the second pressure cylinder  56 . 
     The activation device  48  is radially supported by means of a radial needle bearing  62  on the second output shaft  40  which is arranged coaxially on the outside with respect to the first output shaft  28 . In addition, a cover bearing  66  is connected to the activation device  48  via a sheet-metal securing element  64 . A clutch cover  68  is mounted by means of the cover bearing  66 , wherein the clutch cover  68  is connected to the second opposing plate  32 . The clutch cover  68 , the second opposing plate  32 , the first opposing plate  16  and the flex plate  14  are connected to the input shaft  12  and as a result experience a rotation. The activation device  48  does not rotate and is fixed exactly like a transmission housing  70  of the dual clutch  10 . In the illustrated exemplary embodiment, the first activation pot  54  has a substantially radially extending first part  72 , wherein the second activation pot  60  correspondingly has a substantially radially extending second part  74 . The clutch cover  68  is arranged spaced apart in the axial direction, in the input-side direction  44  both with respect to the first part  72  and with respect to the second part  74 . 
     In the embodiment of the dual clutch  10  illustrated in  FIG. 2 , the needle bearing  62  is arranged at least partially at the level of the cover bearing  66  in the axial direction, in contrast to the embodiment of the dual clutch  10  illustrated in  FIG. 1 . The needle bearing  62  and the cover bearing  66  are as a result arranged at least partially nested radially one in the other. The needle bearing  62  can for this purpose be inserted in the output-side direction  46  into the sheet-metal securing element  64  or into the clutch cover  70 . 
     In the embodiment of the dual clutch  10  illustrated in  FIG. 3 , the needle bearing  62  is in contrast with the dual clutch  10  illustrated in  FIG. 1 , replaced by a bearing block  76  which is formed by the activation device  48 . The bearing block  76  bears against a radially inwardly pointing bearing face  78  of the transmission housing  70 . The bearing block  76  is, in particular, annular and circumferential and has a curvature whose theoretical centre point  80  lies on a rotational axis  82  of the coaxially arranged output shafts  28 ,  40 . In addition, the clutch cover  68  and the cover bearing  66  are moved in the output-side direction  46 , with the result that the substantially radial first part  72  of the first activation pot  54  and the second part  74  of the second activation pot  60  are spaced apart with respect to the clutch pot  68  in the input-side direction  44 . However, it is also possible for the clutch cover  68  and the cover bearing  66  to be configured and arranged as illustrated in  FIG. 1 . 
     In the embodiment of the dual clutch  10  illustrated in  FIG. 4 , the clutch cover  68  is, in contrast to the embodiment of the dual clutch  10  illustrated in  FIG. 1 , connected, as illustrated in  FIG. 3 , to the radial outer side of the activation device  48  via the cover bearing  66 . 
     The invention also relates to a dual clutch  10  which is illustrated in  FIG. 5 . In the embodiment of the dual clutch  10  illustrated in  FIG. 5 , the activation device  48  is only supported radially on the inside by virtue of the fact that the forces which are applied by the activation device  48  are transferred to a flywheel  84  via the cover bearing  66 , the clutch cover  68 , the second cover plate  32  and the first opposing plate  16 , wherein the flywheel  84  is connected to the input shaft  12  in a rotationally fixed fashion. Since the flywheel  84  is of comparatively solid design in order to make available a correspondingly large inert mass, all the forces which occur can be transferred to the input shaft  12  solely via the flywheel  84 . The first opposing plate  16  is also formed at the same time as a result of the flywheel  84 . The first activation pot  54  is mounted on the activation device  48  in an annular depression  55  in the activation device  48  by means of the first pot bearing  53 . The first pot bearing  53  is arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56  radially on the inside with respect to the first pressure cylinder  50  and radially on the outside with respect to the second pressure cylinder  56 . The second activation pot  60  is supported on the second piston  58  radially on the outside with respect to the second piston  58 , by means of a second pot bearing  57  which is arranged axially next to the activation device  48 . The second pot bearing  57  can, however, also be arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56 , radially on the inside with respect to the first pressure cylinder  50  and radially on the inside with respect to the second pressure cylinder  56 . 
     The invention also relates to a dual clutch as illustrated in  FIG. 6 . In the embodiment of the dual clutch  10  illustrated in  FIG. 6 , the needle bearing  62  is, in contrast to the dual clutch  10  illustrated in  FIG. 1 , replaced by a flexible element  86 , wherein the flexible element  86  can be connected radially on the outside to the transmission housing  70 , in particular by screwing or riveting. By means of the flexible element  84 , oscillations can be damped and forces which act both radially and axially can be transferred to the transmission housing  70 . The first pot bearing  53  is arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56 , radially on the inside with respect to the first pressure cylinder  50  and radially on the outside with respect to the second pressure cylinder  56 . The second activation pot  60  is supported on the second piston  58  by means of a second pot bearing  57  which is arranged axially next to the activation device  48 , radially on the outside with respect to the second piston  58 . The second pot bearing  57  can, however, also be arranged at the level of the first pressure cylinder  50  and at the level of the second pressure cylinder  56  radially on the inside with respect to the first pressure cylinder  50  and radially on the inside with respect to the second pressure cylinder  56 . 
     The invention also relates to a dual clutch  10  as illustrated in  FIG. 7 . In the embodiment of the dual clutch  10  illustrated in  FIG. 7 , the clutch cover  68  and the cover bearing  66  are configured and arranged as in  FIG. 3 , in contrast to the embodiment of the dual clutch  10  illustrated in  FIG. 6 . 
     LIST OF REFERENCE NUMBERS 
       10  Dual clutch 
       12  Input shaft 
       14  Hex plate 
       16  First opposing plate 
       18  First clutch 
       20  Starter ring 
       22  First pressure plate 
       24  First clutch plate 
       26  Toothing 
       28  First output shaft 
       30  First two-mass flywheel 
       32  Second opposing plate 
       34  Second clutch 
       36  Second pressure plate 
       38  Second clutch plate 
       40  Second output shaft 
       42  Second two-mass flywheel 
       44  Input-side direction 
       46  Output-side direction 
       48  Activation device 
       50  First pressure cylinder 
       52  First piston 
       53  First pot bearing 
       54  First activation pot 
       55  Depression 
       56  Second pressure cylinder 
       57  Second pot bearing 
       58  Second piston 
       60  Second activation pot 
       62  Needle bearing 
       64  Sheet-metal securing element 
       66  over bearing 
       68  Clutch cover 
       70  Transmission housing 
       72  First part 
       74  Second part 
       76  Bearing block 
       78  Bearing face 
       80  Center point 
       82  Rotational axis 
       84  Flywheel 
       86  Flexible element