Abstract:
A multiple clutch device which includes a drive unit, a downstream transmission connected to a drive shaft of the drive unit and accommodated in a clutch bell that does not co-rotate with the drive shaft, two wet multi-plate clutches, which include a plate support at the input and output end and plates alternating axially, and an actuation mechanism. A housing of the actuation mechanism is supported on the clutch bell, and the plate support at the input end of at least one of the multi-plate clutches is connected to the housing by a supporting metal sheet or a supporting pot and a footstep bearing such that a flow of an actuation force generated by the actuation mechanism is redirected to the housing of the actuation mechanism via the supporting metal sheet or the supporting pot and the footstep bearing, thus creating a closed force flow within the device.

Description:
This application is a continuation of PCT/DE2009/001809 filed Dec. 22, 2009, which in turn claims the priority of DE 10 2009 005 075.2 filed Jan. 19, 2009, and DE 10 2009 012 207.9 filed Mar. 9, 2009. The priority of these applications is hereby claimed and these application are incorporated by reference herein. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to a multiple clutch device for a drive train with a drive unit and with a following transmission, which device is connected to a drive shaft of the drive unit and is received in a bell-shaped clutch casing not corotating with the drive shaft of the drive unit, with two multi-plate clutches which have in each case an input-side and output-side plate carrier and plates alternating in the axial direction, and with an actuating device. 
     BACKGROUND OF THE INVENTION 
     A dual clutch device of this type is known from DE 10 2006 049 731. In this dual clutch, an actuating force generated by the actuating device has to be supported via the input-side plate carrier, a supporting bearing and a clutch cover tied fixedly to the bell-shaped clutch casing. For this purpose, the input-side plate carrier, supporting bearing and clutch cover must have correspondingly high dimensioning, the respective actuating force depending on the torque to be transmitted. With a rising torque, a correspondingly higher actuating force and correspondingly high dimensioning, in particular, of the clutch cover are accordingly necessary. 
     SUMMARY OF THE INVENTION 
     An object of the present invention is to specify a multiple clutch device of the type initially mentioned, with improved support of an actuating force. This object is achieved, according to the invention, by means of a multiple clutch device having the features of patent claim  1 . Preferred exemplary embodiments of this multiple clutch device are the subject matter of the dependent patent claims. 
     At the present time, for energy efficiency reasons, attempts are made to reduce an overall number of cylinders of internal combustion engines, in particular 2-cylinder or 3-cylinder engines being developed. However, with a reduced number of cylinders, there is an increase in unsteady running of the drive units. With an increase in unsteady running of the drive units, the torsional vibration dampers, such as, for example, two-mass flywheels, also have to be redimensioned, thereby increasing the axial construction space requirement of the dual clutch. 
     An object of the present invention is to specify a multiple clutch device with improved support of a actuating force. A further object of the present invention is to specify a multiple clutch device with improved vibration damping, along with a construction space requirement which is not appreciably changed. 
     The objects are achieved by the present invention, which broadly relates to a multiple clutch device for a drive train which has a drive unit with a drive shaft and a following transmission. The device is connectable to the drive shaft of the drive unit. The device comprises a bell-shaped clutch casing, which is not corotatable with the drive shaft of the drive unit. The device is received in the bell-shaped clutch casing. Also, the device comprises an actuating device which has a housing supported radially on the bell-shaped clutch casing, a support sheet or a support pot and a supporting bearing which are arranged so as to connect the input-side plate carrier of at least one of the multi-plate clutches to the housing of the actuating device such that a force flux of an actuating force generated by the actuating device is returned to the housing of the actuating device by the support sheet or the support pot and the supporting bearing, so that the force flux, which is closed within the multiple clutch device, is present. 
     In one embodiment, the multi-plate clutches are arranged radially one above the other, and the input-side plate carrier of the radially outer multi-plate clutch is supported radially rotatably, and axially fixedly, on the housing of the actuating device via the support sheet or the support pot so that the force flux of the actuating force generated by the actuating device is supported on the housing of the actuating device via the axially fixed support of the radially outer input-side plate carrier and a force flux closed within the clutch device is present. 
     In another embodiment, the multi-plate clutches, which include a radially inner multi-clutch plate and a radially outer multi-clutch plate, are arranged radially one above the other and the input-side plate carrier of the radially inner multi-plate clutch is supported on the input-side plate carrier of the radially outer multi-plate clutch via a connection sheet or a connection pot. 
     In a further embodiment, the multi-plate clutches are arranged radially one above the other and the input-side plate carrier of the radially outer multi-plate clutch is connectable rotatably fixedly to an output side of a two-mass flywheel and/or to a torsional vibration absorber. 
     In yet another embodiment, the input-side plate carrier of the radially outer multi-plate clutch is a clutch pot has a clutch hub, on which an output hub of the two-mass flywheel is arranged rotatably fixedly, and the clutch pot is supportable radially on a transmission input shaft. 
     In an even further embodiment, the multiple clutch device includes a clutch cover, which is supported on the bell-shaped clutch casing. The output-side plate carriers of the multi-plate clutches and the input-side plate carrier of the radially outer multi-plate clutch are preloaded against the clutch cover. 
     In another embodiment, the device includes a corrugated spring arranged so as to preload the output-side plate carriers of the multi-plate clutches and the input-side plate carrier of the radially outer multi-plate clutch against the clutch cover. 
     In a further embodiment, the input-side plate carrier of the radially outer multi-plate clutch is a substantially cylindrical toothing sheet which is connectable to an output flange of the two-mass flywheel and to the support sheet or the support pot. 
     In yet another embodiment, the output-side plate carriers of the multi-plate clutches and the input-side plate carrier of the radially outer multi-plate clutch are preloadable against a primary-side sheet of the two-mass flywheel. 
     In an even further embodiment, the device includes a corrugated spring arranged so as to preload the output-side plate carriers of the multi-plate clutches and the input-side plate carrier of the radially outer multi-plate clutch against a primary-side sheet of the two-mass flywheel. 
     In another embodiment, the actuating device for each of the multi-plate clutches has a dedicated actuating unit which comprises an actuating bearing and a force transmission device. The force transmission device comprises a pressure pot, a lever spring and a pressure piece. The pressure pot is operatively connected to the actuating bearing, the pressure piece is operatively connected to the plates of an associated multi-plate clutch, and the lever spring is suspended on an input-side plate carrier of the associated multi-plate clutch and is operatively connected to the pressure pot and the pressure piece. 
     In a further embodiment, the multi-plate clutches are open in a non-actuated state and closed in an actuated state. 
     In an additional embodiment, the actuating unit of the actuating device generates a pressure force as actuating force, which is supported on the housing of the actuating device by the support sheet or the support pot, which acts as a tension pot. 
     In yet another embodiment, the two multi-plate clutches are wet-running multi-plate clutches, and the multiple clutch device further comprises a centrifugal pendulum, which is arrangeable parallel to a two-mass flywheel, on the input-side plate carrier of the at least one of the multi-plate clutches. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present invention is explained in more detail below by means of preferred exemplary embodiments in conjunction with the accompanying figures in which: 
         FIG. 1  shows a half section through a dual clutch according to a first exemplary embodiment, 
         FIG. 2  shows a diagrammatical illustration of the internal force flux of the radially inwardly arranged multi-plate clutch K 2  during its actuation for the dual clutch according to  FIG. 1 , 
         FIG. 3  shows a diagrammatic illustration of the mounting of the dual clutch according to  FIG. 1  and  FIG. 2 , 
         FIG. 4  shows a half section through the dual clutch according to a further exemplary embodiment in a play-free plate carrier, and 
         FIGS. 5 and 6  show diagrammatic illustrations relating to built-up plate carriers. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       FIG. 1  shows a dual clutch  1  composed of two radially nested wet-running multi-plate clutches K 1  and K 2 . Clutch K 1  is in this case arranged radially on the outside and clutch K 2  radially on the inside. The dual clutch  1  is driven by an output hub  2  of a two-mass flywheel (not shown in detail) preceding the clutch  1 . 
     Between this two-mass flywheel and the dual clutch  1  is located a clutch cover  3  which separates a wet space  4  from a dry space  5 . Static sealing  6  of the clutch cover  3  with respect to a transmission housing  7  of a transmission (not shown in detail) following in the drive train takes place preferably via an O-ring  6  or another static sealing element. 
     Sealing with respect to the dual clutch  1  takes place preferably via a radial shaft sealing ring  8  as a dynamic sealing element. 
     The output hub  2  of the two-mass flywheel (also designated below briefly as ZMS) is connected fixedly in terms of rotation to a clutch hub  9  via a toothing. The clutch hub  9  is connected to the input-side plate carrier  10  of the clutch K 1  arranged on the outside in the radial nesting. The input-side plate carrier  10  of the multi-plate clutch K 1  and the clutch hub  9  connected fixedly to said plate carrier are supported radially on the first transmission input shaft  15  (which is designed as a solid shaft) via a radial bearing  16 . The input-side plate carrier  10  comprises toothing regions, on which input-side plates of the plate stack of the multi-plate clutch K 1  are suspended, so that the input-side plates  11  are arranged fixedly in terms of rotation and so as to be axially displaceable. The input-side plates  11  are arranged alternately with output-side plates  12 , and the input-side plates  11  and the alternately arranged output-side plates  12  together forming the plate stack of the clutch K 1 . The output-side plates  12  are connected to an output-side plate carrier  13  of the outer multi-plate clutch K 1  fixedly in terms of rotation and so as to be axially displaceable. The output-side plate carrier  13  of the multi-plate clutch K 1  comprises a hub  14  which is connected to a first transmission input shaft  15  of a dual clutch transmission, not shown in detail. 
     The input-side plate carrier  10  of the outer multi-plate clutch K 1  is connected to the input-side plate carrier  18  of the radially inwardly arranged multi-plate clutch K 2  via the connection sheet  17  which is suspended on the toothing region of the plate carrier  10 . The input-side plates of the radially inwardly arranged multi-plate clutch K 2  are suspended in a toothing region fixedly in terms of rotation and so as to be axially displaceable. The input-side plates of the radially inwardly arranged clutch K 2  are arranged alternately with output-side plates which are arranged on an output-side plate carrier  19  of the multi-plate clutch K 2  fixedly in terms of rotation and so as to be axially displaceable. The output-side plate carrier  19  has a hub region, at which the output-side plate carrier  19  is connected to a second transmission input shaft  20  (which is designed as a hollow shaft). 
     The output-side plate carrier  19  of the radially inwardly arranged multi-plate clutch K 2  is pressed via a corrugated spring  21  (and, if necessary by virtue of construction, also via a connection piece  22 ), with a hearing  23  interposed, against the output-side plate carrier  13  of the radially outwardly arranged multi-plate clutch K 1 . The output-side plate carrier  13  of the radially outwardly arranged multi-plate clutch K 1  is in turn pressed, with the further bearing  24  interposed, against the input-side plate carrier  10  of the radially outwardly arranged multi-plate clutch K 1 . The input-side plate carrier  10  of the radially outwardly arranged multi-plate clutch K 1  is in turn pressed, with a further bearing  25  interposed, against the clutch cover  3  which is supported on the housing  7  of the transmission via the securing element  26 . As can be gathered particularly from  FIG. 1 , the bearings  23 ,  24 ,  25  are preferably designed as axial (needle) bearings. 
     In the present case, the transmission input shafts  15 ,  20  are arranged coaxially and so as to be nested one in the other, the outer transmission input shaft  20  being supported in the housing  7  via a supporting bearing  38 , and the inner transmission input shaft  15  being supported in the outer hollow shaft  20  via a mounting. 
     The dual clutch  1  comprises, furthermore, an actuating device  27  which is designed as a central clutch disengager for both multi-plate clutches K 1  and K 2 , with a housing  28  which is supported on the housing  7  of the transmission via a bearing block  29 . The actuating device  27 , designed in the present case as a double annular piston engager (also designated as a dual CSC, CSC standing for “concentric slave cylinder”), comprises two annular pistons  31 ,  32  arranged concentrically to one another. The variant of the actuating device  27 , as illustrated in  FIGS. 1 to 4 , shows an embodiment in which the two annular pistons  31 ,  32  slide one on the other. The inside diameter of the outer piston  31  of the clutch K 1  therefore at the same time constitutes the sealing surface for the inner piston of the clutch K 2 . Alternatively (but not shown), an embodiment is also conceivable in which the two pistons are separated from one another by an annular web on which the seals can slide. Such an alternative embodiment makes it possible to rule out completely a situation where the pistons  31 ,  32  are influenced mutually by the seal. However, the possible embodiments of the actuating device  27  which were described above are to be understood purely as examples. Thus, instead of an annular piston, another cross-sectional form and/or a plurality of individual pistons, distributed along the circumference, may also be provided. An electrical disengager may likewise be provided instead of the piston/cylinder units. Moreover, mechanical actuating devices, in particular lever-actuated devices, could also be provided. In the present case, the piston seals of the annular pistons  31 ,  32  are designed as elastomeric seals which are connected to the respective pistons via positive connections. What may be considered a positive connection is, for example, a conical groove which is located in the piston and into which a corresponding tongue of the elastomeric seal is fitted. Alternatively, inserted seals made, for example, from PTFE or elastomeric seals injection molded directly onto the pistons may also be envisaged. The annular pistons  31 ,  32  are received by the engagement housing  28 , bores in the engager housing  28 , which are not shown in detail in the figures, serving for actuating the pistons via pressure oil. 
     In addition, the engager housing  28  assumes the radial positioning of the pistons via the bearing block within the bell-shaped clutch casing. 
     Each of the actuating units of the actuating device  27  is connected via an actuating bearing  33 ,  34  to a force transmission device, by means of which the respective actuating force is transmitted to the respective multi-plate clutch K 1 , K 2 . In the present case, each of the force transmission devices comprises a pressure pot  35 A,  35 B which bears against the respective bearing  33 ,  34 . It may be noted in this case that, of course, each pressure pot has an elasticity which leads to a certain spring action. However, as regards the present actuating forces of the dual clutch, the pressure pots may be assumed to be “essentially rigid.” 
     Moreover, each of the force transmission devices comprises a lever spring  36 A,  36 B which bears against the respective pressure pot  35 A,  35 B. The lever springs  36 A,  36 B are in each case suspended on the associated plate carrier of the corresponding multi-plate clutch K 1 , K 2 , this suspension point forming the respective center of rotation for the lever spring. A force step-up of the actuating forces generated by the actuating units takes place via the lever ratio of this lever spring. 
     Moreover, each of the force transmission devices comprises a pressure piece  37 A,  37 B which bears against the associated lever spring  36 A,  36 B and is operatively connected to the plates of the plate stacks of the respective multi-plate clutch K 1 , K 2 . The pressure pieces transmit the actuating forces to the plate stacks of the multi-plate clutches K 1  and K 2 . 
     The pressure pieces  37 A,  37 B are suspended axially displaceably in a radially outer region into the toothing of the respective input-side plate carrier and are centered in the radial direction by the toothing. 
     Arranged on the housing  28  of the actuating device  27 , in an outer surface area region, is a supporting bearing  30  which is connected via a tension pot  55  to the input-side plate carrier  10  of the radially outer multi-plate clutch K 1 . In this case, the inner ring of the supporting bearing is supported, via a collar formed on the housing  28 , on the housing, on the one hand, and the outer ring of the supporting bearing, on the other hand, is supported on the tension pot  55  in such a way that an actuating force returned from the input-side plate carrier  10  of the multi-plate clutch K 1  can be transmitted to the housing  28 . The supporting bearing  30 , which returns the actuating force to the engager housing  28 , together with the tension pot  55 , is preferably connected to the engager housing  28  via a bayonet connection. 
     When pressure acts upon one of the pistons or on both pistons, this moves or these move in the direction of the crankshaft (arranged on the left of the output hub of the ZMS in  FIG. 1 ) and at the same time, via the drive of the associated pressure pot  35 A,  35 B, actuates or actuate the respective lever spring  36 A,  36 B which, in turn, introduces the actuating force into the plate stack via the associated pressure piece  37 A,  37 B. In the case of the radially inwardly arranged clutch K 2 , the actuating force is transmitted via the input plate carrier  18  and the connection piece  17  (also designated as a connection sheet) between input-side plate carriers of the radially inwardly arranged multi-plate clutch K 2  and the input-side plate carrier  10  of the radially outwardly arranged multi-plate clutch K 1 . The input-side plate carrier  10 , in turn, transmits the actuating force to the tension pot  55  which is connected to the engager housing  28  via the supporting bearing  30 . 
     In the case of the radially outwardly arranged clutch K 1 , the introduced actuating force is returned directly via the input plate carrier  10  to the tension pot  55  and consequently via the supporting bearing  30  to the engager housing  28 . 
     The present dual CSC therefore generates a pressure force acting on the pressure pots in the direction of the drive unit, a correspondingly high and oppositely directed counterforce being generated in the housing  28 , and the actuating force being returned again via the tension pot and the supporting bearing in the same amount and with the same direction to the housing, so that the actuating force and the counterforce cancel one another in the housing. Since the supporting bearing  30  transmits the actuating force to the engager housing  28 , the internal force flux within the clutch  1  is therefore closed. This run of the actuating force for actuating the multi-plate clutch K 2  is illustrated diagrammatically in  FIG. 2  by the dashed line L 1 . In the present case, therefore, no external forces are freed for actuating the multi-plate clutches K 1  and K 2 , and therefore the clutch  1  requires no support of the actuating force at the bell-shaped clutch casing or on the engine side. 
     The hydraulic medium (actuating module) is fed to the actuating device via fittings which are connected to the bell-shaped clutch casing. 
     The engager housing  28  has torque support within the bell-shaped clutch casing, so that bearing friction within the supporting bearing  30  cannot lead to rotation of the engager housing  28 . The fittings for the feed of pressure may in this case be used as torque support. Alternatively, separate support via tenon or similar component which engages into the bottom of the bell-shaped clutch casing when the clutch is being mounted may also be provided. 
       FIG. 3  illustrates diagrammatically by arrows P 1  to P 5  the radial and axial mounting of the clutch  1  according to the exemplary embodiment shown in  FIG. 1 . 
     As seen in the radial direction, all the components of the dual clutch  1  which rotate at the rotational speed of the engine are mounted, on the transmission side, on the engager housing  28  and, on the engine side, on the solid shaft  15 . Arrow P 1  in this case represents the support of the input-side plate carrier  10  of the radially outwardly arranged multi-plate clutch K 1  and of the components, connected to this component, on the engager housing  28 . The engager housing  28 , in turn, is supported on the bottom of the bell-shaped clutch casing (on the transmission housing) via the bearing block  29 , as illustrated by the arrow P 2 . The bearing block  29  constitutes the angle compensation between the solid shaft  15  and the transmission-side bearing base. The solid shaft  15  supports on the engine side, via the bearing  16 , the input-side plate carrier  10  of the radially outwardly arranged clutch K 1 , as illustrated by the arrow P 3 . The clutch components  14 ,  19  rotating with the respective transmission input rotational speeds of the solid and the hollow shaft  15 ,  20  are mounted radially via the hubs/hub regions seated on the shafts. 
     The bearing block  29  may be replaced by radial support on the outer transmission input shaft, preferably via a radial needle bearing arranged on the outer transmission input shaft. 
     As seen axially, the clutch  1  is supported on the clutch cover  3 , the supporting force being applied by the corrugated spring  21 . The axial mounting points are indicated by the arrows P 4  and P 5 . In this case, the corrugated spring  21  is supported on a securing ring, attached to the hollow shaft  20 , and the hub of the output-side plate carrier  19  of the multi-plate clutch K 2 . The output-side plate carrier  19  of the multi-plate clutch K 2  conducts this axial force via a spacer disk  22  to an axial needle bearing  23  located on the output-side plate carrier  13  or its hub region  14 . The output-side plate carrier  13  of the multi-plate clutch K 1  is supported, in turn, via an axial needle bearing  24  on the input-side plate carrier  10  of the clutch K 1 , which plate carrier is supported on the clutch cover  3  via a further needle bearing  25 . The clutch system  1  is therefore always aligned on the clutch cover  3 . Axial vibrations and tolerances can be compensated via the corrugated spring  21 . The axial needle bearings  23 ,  24 ,  25  may also be replaced by run-on disks. The above-described type of axial mounting of the present clutch  1  may also be used independently of the internally closed force flux described above, that is to say also in other types of actuating force flux, and constitutes a separately usable solution in general for dual (wet) clutches. 
       FIG. 4  shows a further exemplary embodiment of the present multiple clutch device which corresponds completely in terms of the actuating force flux concept to the exemplary embodiments already explained above. Thus, all the features listed above regarding the actuating device are identical among the exemplary embodiments according to  FIGS. 1 to 3  and according to  FIG. 4 . Furthermore, in the present case, a bearing block is provided once again in order to support the actuating housing  28  radially on the transmission housing  7  and compensate axial offset. 
     The exemplary embodiment according to  FIG. 4  differs from the above exemplary embodiment, however, in the elements, ZMS and/or centrifugal pendulum, used for damping the rotational non-uniformities coming from the internal combustion engine. 
     Thus, in the exemplary embodiment according to  FIG. 4 , both the ZMS  39  and a centrifugal pendulum  40  are arranged in the bell-shaped clutch casing which is delimited with respect to a dry space by a clutch cover  41 . In the present case, the clutch cover  41  is not provided for the axial mounting of the clutch. Instead, it constitutes only the separation between the wet space  4  and dry space  5  via the sealing devices  6  and  8 . 
     The ZMS  39  comprises a primary-side ZMS sheet  42  which in the present case is of pot-like design and comprises, in its radially inner region, a pilot tenon  43  which engages into a recess  44  of the crankshaft  45  and centers the primary-side ZMS sheet. The primary-side ZMS sheet  42  has in its radially outer region pocket-shaped regions in which spring elements are received, the end regions, not in contact with these pockets, of the energy accumulators  46  being operatively connected to a secondary-side ZMS flange  47 . The secondary-side ZMS flange  47  is connected via the rivets  49  to an essentially cylindrical toothing sheet  48 , the toothing sheet  48  serving as the input-side plate carrier of the radially outwardly arranged clutch K 1 . 
     The input-side plate carrier  48  is connected via the connection sheet  50  to the input-side plate carrier  51  of the radially inwardly arranged multi-disk clutch K 2 . Moreover, this connection sheet  50  is connected (in the present case, formed in one piece) with the centrifugal pendulum  40 , so that the ZMS  39  and the centrifugal pendulum  40  are jointly connected to the toothing sheet  48  (preferably via the rivets  49 ) and are correspondingly connected in parallel. 
     The toothing sheet  48  is connected via the tension pot  52  to the supporting bearing  53  which is arranged on the engager housing  28  (as already described above). 
     The output-side plate carrier  54  of the multi-plate clutch K 1  is arranged fixedly in terms of rotation on the hollow shaft  15 . The output-side plate carrier  55  of the multi-plate clutch K 2  is arranged fixedly in terms of rotation on the hollow shaft  20 . The output-side plate carrier  54  of the multi-plate clutch K 2  is preloaded against the output-side plate carrier  54 , with an axial bearing interposed, via the corrugated spring  21  in conjunction with the securing element  21 A and the connection element  22 . The output-side plate carrier  54  of the multi-plate clutch K 1  is loaded against the primary-side ZMS flange  42  (also designated as “ZMS sheet”), with a further axial bearing interposed. A drive plate  56  is arranged fixedly on the primary-side ZMS sheet  42  and is connected to a Flexplate  58  via a screw connection  57 , the Flexplate being connected to the crankshaft  45  via a further screw connection  59 . 
     The actuating device  27  again comprises actuating units which in the present case are designed as piston/cylinder units which in each case act via the force transmission devices, composed of the pressure pot, lever spring and pressure piece, on the respective plate stacks of the multi-plate clutches K 1  and K 2 , as already described above. 
     The clutch  100  according to  FIG. 4  is therefore tied to the internal combustion engine via the Flexplate  58 . The drive plate  56  and the primary-side ZMS sheet are connected to one another directly (preferably so as to be oil-tight) and receive the clutch cover  41 , connected axially between them, with the radial shaft sealing ring  8 . 
     The primary-side components of the ZMS are mounted directly on the crankshaft  45  via a pilot tenon  43 . 
     The secondary-side flange  47  of the ZMS at the same time constitutes the end plate of the multi-plate clutch K 1  in the present case. 
     The input-side plate carrier  48  of the multi-plate clutch K 1  is designed as a riveted variant (as already described). 
     Exemplary embodiments of a riveted plate carrier are illustrated in  FIGS. 5 and 6 . 
       FIG. 5  shows a built-up plate carrier  134  (comparable to the input-side plate carrier of  FIG. 4 ) in detail as a sectional illustration. The plate carrier  134  is formed from the flange part  113   a , the carrier disk  136  and circumferentially distributed connection elements  190  arranged axially between them. In the exemplary embodiment shown, the connection elements  190  are formed from prebent sheet metal parts  191  which have axially extending rivet studs  192 ,  193  which are led through corresponding orifices  194 ,  195  in the flange part  113   a  or carrier disk  136  and are riveted against this from outside. The circumferentially pointing ends of the sheet metal parts  191  are chamfered or bent radially inward to form tooth flanks  196 , so as to form, in the cross section of the sheet metal parts  191 , a tooth flank profile on which the plates  138  are suspended, the latter having for this purpose a complementary outer profile  197 , so that the plates  138  are centered on the plate carrier  134  and the torque prevailing at the plate carrier  134  is transmitted to the plates  138 . The plates  138  are layered alternately with the friction plates  140  which are suspended in the output-side plate carrier  142  fixedly in terms of rotation and so as to be displaceable axially to a limited extent. 
       FIG. 6  shows a version alternative to the plate carrier described above, in the form of the plate carrier  135   a  in a built-up version. The plate carrier  135   a  has connection elements  198  which are designed comparably to the connection elements  190  of  FIG. 5  and are riveted between the end plate  172   a  and the carrier disk  136 . Further,  FIG. 6  shows a connection element  190   a  with an axially prolonged pin  186 , which connection element replaces the connection element  190  of  FIG. 5 , for example, in a plurality of circumferential positions and thereby enables the plate carrier  134  to engage with the friction device  185 , in that the pins  186  drive the friction ring  187  in the circumferential direction with respect to the housing of the clutch unit and thus control the friction device. 
     In the exemplary embodiment shown in  FIG. 4 , the individual toothing sheets have two different lengths and are distributed alternately over the circumference. The shorter toothing sheets are riveted to the connection sheet  50  of the input-side plate carriers  48  and  51  of the multi-plate clutches K 1  and K 2 . The longer toothing sheets are connected to the tension pot  52  which returns the actuating forces to the engager housing  28 . What is achieved by these stepped toothing sheets is that the centrifugal pendulum is tied, free of rotational play, to the secondary-side flange of the ZMS. Consequently, the tension pot  52  is connected positively and non-positively to the input-side plate carrier  48  of the multi-plate clutch K 1  and can absorb the actuating forces which occur. 
     List Of Reference Symbols 
     
         
           1  Clutch 
           2  Drive Hub 
           3  Clutch Cover 
           4  Wet Space 
           5  Dry Space 
           6  Lug Ring 
           7  Housing 
           8  Radial Shaft Sealing Ring 
           9  Clutch Hub 
           10  Plate Carrier 
           11  Plate 
           12  Plate 
           13  Plate Carrier 
           14  Hub 
           15  Transmission Input Shaft 
           16  Radial Bearing 
           17  Connection Sheet 
           18  Plate Carrier 
           19  Plate Carrier 
           20  Transmission Input Shaft 
           21  Corrugated Spring 
           22  Connection Piece 
           23  Bearing 
           24  Bearing 
           25  Bearing 
           26  Securing Element 
           27  Actuating Device 
           28  Housing 
           29  Bearing Block 
           30  Supporting Bearing 
           31  Piston 
           32  Piston 
           33  Actuating Bearing 
           34  Actuating Bearing 
           35 A Pressure Pot 
           35 B Pressure Pot 
           36 A Lever Spring 
           36 B Lever Spring 
           37 A Pressure Piece 
           37 B Pressure Piece 
           38  Supporting Bearing 
           39  ZMS 
           40  Centrifugal Pendulum 
           41  Clutch Cover 
           42  ZMS Sheet 
           43  Pilot Tenon 
           44  Recess 
           45  Crankshaft 
           46  Energy Accumulator 
           47  ZMS Flange 
           48  Toothing Sheet 
           49  Rivets 
           50  Connection Sheet 
           51  Input-Side Plate Carrier 
           52  Tension Pot 
           53  Supporting Bearing 
           54  Output-Side Plate Carrier 
           55  Tension Pot 
           56  Drive Plate 
           57  Screw Connection 
           58  Flexplate 
           59  Screw Connection 
         K 1  Multi-Plate Clutches 
         K 2  Multi-Plate Clutches