Abstract:
A clutch unit, which has at least one wet clutch that is arranged in a housing, which is driven by a drive unit. The clutch is effectively connected to an input part. To simultaneously associate a torsional vibration damper, e.g. a centrifugal pendulum, with the input part, a support disk of the torsional vibration damper is connected to the input part so that no or only minor vibrations are generated, allowing the frequency of the torsional vibration damper to be sufficiently adjusted. For this purpose, at least one plate support is connected to a single support disk which is fixedly mounted on the clutch hub and is thus made rigid. Preferably, the plate support further reduces vibration tolerance.

Description:
This application is a continuation of PCT/DE2009/001810 filed Dec. 22, 2009, which in turn claims the priority of DE 10 2009 005 075.2 filed Jan. 19, 2009. The priority of both applications is hereby claimed and both applications are incorporated by reference herein. 
    
    
     FIELD OF THE INVENTION 
     The invention relates to a clutch unit with two wet clutches arranged one above the other and with a torsional vibration absorber. 
     BACKGROUND OF THE INVENTION 
     The use of torsional vibration absorbers, for example centrifugal pendulums, in a drive train is known from DE 103 108 31 A1. Furthermore, clutch units with wet clutches are known. For example, DE 10 2005 027 610 A1 discloses a clutch unit with two wet clutches arranged radially one above the other. 
     It is difficult to accommodate a torsional vibration absorber in the wet space of the clutch unit, since sufficient tuning of the resonant range has to be ensured. In particular, torsional backlash of torque-transmitting connecting parts contributes to a disturbance in the resonant range. 
     SUMMARY OF THE INVENTION 
     The object of the invention is the further development of the use of torsional vibration absorbers in the drive train of motor vehicles, particularly in conjunction with wet clutches accommodated in a housing. 
     The invention is achieved by means of a clutch unit for a drive train with a drive unit and with a following transmission having at least one wet clutch arranged in a housing driven by the drive unit, with lamellae and friction lamellae received in an input-side and an output-side lamella carrier and alternating in the axial direction, the input-side lamella carrier being connected fixedly to a carrier disk received fixedly on a clutch hub, and a torsional vibration absorber, for example a centrifugal pendulum, being arranged on the carrier disk. Advantageously, a torsional vibration damper may be connected in parallel to the torsional vibration absorber and may be arranged effectively between the at least one wet clutch and the housing. For example, an input part of the wet clutch can at the same time be the output part of the torsional vibration damper. 
     In this case, a tie-up of the torsional vibration absorber to the input part of the at least one wet clutch via the input-side lamella carrier is provided. In this case, if, for example, deep-drawn lamella carriers produced by means of sheet metal forming methods are used, the situation cannot sufficiently be ruled out where connections to the torque-transmitting connecting components are subject to play because form fits are made insufficiently or can be made only in high outlay manufacturing terms, so that vibration problems may arise particularly during the actuation of the at least one wet clutch. For example, rattling or clattering noises or other vibratory effects may arise, which are uncomfortable and moreover adversely influence the functioning of the torsional vibration absorber, so that it may be possible that a torsional vibration absorber cannot even be used in this position. It has therefore proved especially advantageous if at least one lamella carrier, for example the input-side lamella carrier of the at least one wet clutch, is designed as a built-up lamella carrier which has bearing faces, capable of being produced axially in a planar manner, between the flange part of the input part, on the one hand, and the carrier disk of the torsional vibration absorber, on the other hand. 
     According to an advantageous exemplary embodiment, the built-up lamella carrier is formed from circumferentially distributed connection elements which connect an input part, designed as a flange part of the at least one wet clutch, to the carrier disk in an axially spaced-apart and play-free manner. Owing to the planar bearing faces of the connection elements on the flange part or on the carrier disk, an especially rigid tie-up of the carrier disk to the input part of the wet clutch is achieved, so that the transmission of torque from the input part to the torsional vibration absorber can be defined and can take place without play, and therefore the torsional vibration absorber, for example a centrifugal pendulum, can be rated especially well for the desired resonant frequency or for a narrow resonant range. 
     It has in this case proved to be especially advantageous to connect in parallel to the torsional vibration absorber a torsional vibration damper which is arranged between the housing and the at least one wet clutch and the output part of which is likewise formed by the flange part of the input part of the at least one wet clutch. Furthermore, the at least one wet clutch may be provided, for example, from two wet clutches, arranged radially one above the other, for a dual clutch transmission, in which case one, preferably the radially outer lamella carrier or both input-side lamella carriers of the two wet clutches can be built up. 
     A lamella carrier built up in this way is advantageously equipped with connection elements which are riveted to the flange part and the carrier disk. These connection elements at the same time form the rotary take-up for the lamellae, for example produced from steel, at the same time with axially limited displaceability, so that, in the case of an alternating arrangement of lamellae and of friction lamellae assigned to the output side of the at least one wet clutch and provided with friction linings, the wet clutch can, in a directed manner, be opened, closed and operated with slip, as a function of axial action upon the stack of lamellae thus formed, by a pressure-loadable piston against a fixed end lamella formed, for example, by the flange part. Rotary take-up in this case takes place by means of recesses, complementary with the cross-sectional profiles of the connection elements, of the lamellae, in particular over their outer circumference, so that the input-side lamellae can be suspended in the connection elements with the form fit in the circumferential direction and so as to be axially displaceable to a limited extent. 
     Particularly for reasons of stability, the connection elements may have on the end face in each case two rivet studs adjacent to one another in the circumferential direction and which pass through corresponding orifices in the flange part and in the carrier disk and are subsequently riveted together. In this case, in an advantageous exemplary embodiment with an end lamella formed from the flange part, for assembly reasons lamellae and friction lamellae are threaded onto the connection elements already connected, such as riveted, to the flange part, before the carrier disk is connected, such as riveted, to the connection elements. 
     Furthermore, particularly for reasons of stability of the lamella carrier, it has been shown to be advantageous if the connection elements have, for riveting to the flange part and/or to the carrier disk, rivet studs of polygonal cross section which pass through recesses, provided complementarily thereto, in the flange part and in the carrier disk and are in each case riveted on their sides facing away from the connection elements. In this case, the polygons may already be predetermined by virtue of their manufacture. 
     The connection elements may be formed from stepped bolts produced, for example, by cutting, the lamellae being suspended directly in the stepped bolts preferably of round cross section. In this case, at least three, for example six to thirty six, preferably nine to twenty four stepped bolts may be distributed over the circumference. Alternatively or additionally, the connection elements may be formed, for example, from three to sixteen, preferably twelve sheet metal parts which are angled radially outward at their circumferential ends, so that they have in cross section a tooth flank profile, on which the lamellae can be received fixedly in terms of rotation and displaceably. In this case, the rivet studs of the sheet metal parts may be provided on the flat and/or angled region of the sheet metal parts. 
     At least one, preferably a plurality of connection elements distributed over the circumference may have at least one pin which is widened axially in the direction of the housing and controls a friction device connected in parallel to the torsional vibration damper. In this case, the pins can control a friction disk which is braced with the housing, so that, if there is twisting of the housing with respect to the lamella carrier and therefore between the input and output parts of the torsional vibration damper, a frictional moment is generated which, in order to exhibit dragged friction, may also have torsional backlash, for example when the pins engage into longitudinal slots of the friction disk which are aligned over the circumference. 
     Furthermore, it has been shown to be advantageous if the torsional vibration damper is coupled to an input-side, such as primary, flywheel mass and an output-side, such as secondary, flywheel mass. For this purpose, according to another advantageous embodiment, the housing of the at least one wet clutch may be designed as a primary flywheel mass and the at least one wet clutch as a secondary flywheel mass. 
     The at least one wet clutch may advantageously be used in any form and independently of the configuration of its surroundings. It may be accommodated, for example, in a housing in which a pressure medium is used for cooling and actuating the pistons. In this case, the at least one wet clutch may be accommodated in the rotating wet space formed by the housing. Furthermore, the at least one wet clutch may be accommodated in a housing, the at least one wet clutch not being actuated by a hydraulically actuated piston, but instead, for example, by an electrical actuator, so that merely pressure medium as a coolant has to be metered and, correspondingly, there is no need for a rotating wet space. In particular, a torsional vibration absorber in the form of a centrifugal pendulum may in this case be designed independently of the pressure medium. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention is explained in more detail by means of the exemplary embodiments illustrated in  FIGS. 1 to 15  in which: 
         FIG. 1  shows a part section through a clutch unit according to the invention, 
         FIG. 2  shows the built-up lamella carrier of  FIG. 1  in detail, 
         FIG. 3  shows a detail with two built-up lamella carriers, 
         FIG. 4  shows a view of a cutout of the flange part of  FIG. 1 , 
         FIG. 5  shows a configuration of the rotary take-up of the lamellae, 
         FIG. 6  shows a rotary take-up of the lamellae which is alternative to  FIG. 5 , 
         FIGS. 7 to 9  show a connection element for the lamella carrier in various views, 
         FIGS. 10 to 12  show a connection element, alternative to  FIGS. 7 to 9 , for the lamella carrier in various views, 
         FIG. 13  shows a view of a connection element for the lamella carrier for controlling a friction device, and 
         FIGS. 14 and 15  show a view of a connection element configured as a stepped bolt in an open and a closed state. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       FIG. 1  shows the clutch unit  1  in the assembled state as a part section above the axis of rotation  2 . The clutch unit  1  is arranged between the drive unit, of which only the crank shaft  20  is illustrated, and the transmission, of which only the transmission housing  22  is illustrated. The housing  8  of the clutch unit  1  is received on the crankshaft  20  by means of an axially flexible drive plate  21 , such as a flexplate, compensating axial vibrations and wobbling vibrations of the crankshaft  20  and is driven by said drive plate. Furthermore, the housing  8  is supported rotatably on the transmission housing,  22  by means of the rolling bearing  23 , the toothed ring  25  for the transmission oil pump, which can also circulate the pressure medium of the clutch unit  1 , being arranged by means of a sleeve-shaped extension between the annular axial extension  24  of the housing part  7  and the rolling bearing  23  and being driven by the extension  24 . The pump drive formed from the toothed ring  25  and the rolling bearing  23 , which via the toothed ring  25  also forms a mounting for the housing  8  on the housing wall of the transmission housing  22 , is preferably premounted on the transmission housing  22 , while, during the connection of clutch unit  1  and transmission, the scoop pipe  14  is centered in the feed device, and the guide pins  83  pass through this and are received in the transmission housing  22  axially displaceably and so as to support the scoop pipe  14  fixedly in terms of rotation. A sealing disk  26  made, for example, from sheet metal or plastic and having a seal  27 , such as a radial shaft sealing ring, to the extension  24  is provided on the axial extension  24  for sealing off the housing  8  with respect to the transmission housing  22 . 
     The torsional vibration damper  12  and the two wet clutches  28 ,  29  arranged radially one above the other are received inside the housing  8  at least partially filled with pressure medium. The input part of the torsional vibration damper  12  is in this case formed by the housing which acts in the circumferential direction upon the circumferentially active energy accumulators  11 , which, in the exemplary embodiment shown, are formed from preferably two bow spring groups, arranged over the circumference and in each case with two how springs  30 ,  31  rested radially one in the other, by means of the drivers  17 ,  18  which engage radially into the end faces of the bow springs  30 ,  31 . The drivers  17  are in this case formed from shaped portions of the housing part  6  which are arranged over the circumference and the drivers  18  by stepped-out regions of the annular flange part  16 . After the insertion of the bow springs  30 ,  31 , the annular flange part  16  is laid against the radial shoulder  32  of the housing part  6  and axially fixed, such as, for example, welded, and serves for the captive reception of the bow springs  30 ,  31  before mounting and for the axial guidance of the bow springs  30 ,  31  during operation. Between the bow springs  30  and the radially outer region of the housing part  6 , a wear protection shell  33  is provided, which are arranged in two parts in the circumferential direction between the drivers  17  can be mounted floatingly with respect to the housing  8 . 
     The torsional vibration damper  12  is active in the torque flux upstream of the wet clutches  28 ,  29 , so that the output part of the torsional vibration damper  12  is at the same time the common input part  13  of the wet clutches  28 ,  29 . For this purpose, the input part  13  has a flange part  13   a  with the output-side drivers  19  of the torsional vibration damper  12  which are designed as radially widened arms of the flange part  13   a  and which, in the non-braced state of the bow springs  30 ,  31 , act on the same circumference of the drivers  17 ,  18  upon the end faces of the bow springs  30 ,  31  and consequently cause a bracing of the bow springs  30 ,  31  in the event of relative rotation of the housing  8  with respect to the input part  13  of the wet clutches  28 ,  29 , so that the torque peaks causing such relative rotations are damped, in that the bow springs active as energy accumulators  11  briefly store intermediately the energy of these torque peaks. 
     The torque of the drive unit is introduced into the input part  13  via the torsional vibration damper  12 . The input part  13  distributes the torque to the input-side lamella carriers  34 ,  35  of the wet clutches  28 ,  29  which are centered and mounted by means of a common carrier disk  36  which is fixedly connected, such as welded, to the clutch hub  37 . In this case, the radially outer lamella carrier  34  is produced in the built-up manner, while the radially inner lamella carrier  35  is deep-drawn. For example, as shown, a centrifugal pendulum  51  with centrifugal weights  52  displaceable to a limited extent with respect to the carrier disk  36  in the circumferential direction and the radial direction is arranged radially on the outside, and preferably spaced apart axially, and at radially the same height on the carrier disk  36  of the torsional vibration absorber  50 . In each case, lamellae  38 ,  39  are suspended in the input-side lamella carrier  34 ,  35  which alternate axially with output-side friction lamellae  40 ,  41  and, when acted upon axially, form frictional engagement. The output-side friction lamellae  40 ,  41  are suspended in lamella carriers  42 ,  43  which are in each case connected, such as welded, to a hub  44 ,  45 , to a toothing  46 ,  47 , to the transmission input shaft  48  or to the transmission input shaft  49  arranged around said transmission input shaft and designed as a hollow shaft and are therefore mounted and centered on both transmission input shafts  48 ,  49 . 
     In the non-installed state of the clutch unit  1 , the two wet clutches  28 ,  29  are configured together with the clutch hub  37  as a structural unit. After installation, the clutch hub  37  is floatingly mounted axially on the transmission input shaft  49  by means of the rolling bearings  53 ,  54 . The transmission input shaft  49  is fixedly mounted in the transmission housing  22  axially and radially by means of the rolling bearing  55 . 
     The floating mounting of the clutch hub  37  is limited by the two run-on disks  56 ,  57 . The run-on disk  56  is formed in one part from plastic and contains formed the carrier part  58  introduced into the end face of the clutch hub  37  and the lubricating oil grooves  59 . The hub  45  is attached axially and rotatably with respect to the hub  44  by means of the rolling bearing  60 . The hub  44  is supported rotatably on the housing part  6  axially fixedly by means of the rolling bearing  61 , so that the clutch hub  37  is supported axially via the shim disk  67 , in that, for example, a defined play is set by the latter. The axial prestress necessary for the bearings  60 ,  61  is set by means of the axially active energy accumulator  45   a , for example a corrugated spring, which is supported on the transmission input shaft  49  by means of the securing disk  45   b . The clutch hub  37  is supported in the opposite direction, by means of the sealing plate  62  which is arranged axially fixedly on said clutch hub at the shoulder  63  by means of the securing ring  64 , on the scoop pipe  14 , which, in turn, is supported axially on the housing part  7  by means of the run-on disk  65 , which may be designed as a rolling bearing. Between the sealing plate  62  and the scoop pipe  14  is arranged the axially active run-on disk  57  which allows an axially limited displacement of the clutch hub  37  counter to its action in the direction of the housing part  7 , so that the clutch hub  37  is mounted so as to be displaceable with respect to the housing  8  in both directions to an axially limited extent and therefore in the floating manner. The run-on disk  57  is formed from a carrier disk  66  meshed with the sealing plate  62  and a shim disk  67  which is received fixedly thereon and which comes into contact with a run-on disk  68  meshed with the scoop pipe  14 . 
     The two wet clutches  28 ,  29  are acted upon by pistons  69 ,  70  which are displaceable axially by means of a pressure medium and which press the lamellae  38  or  39  axially together with the friction lamellae  40  or  41  against an end lamella  71 ,  72  and thereby form frictional engagement. For this purpose, the pressure medium is in each case conducted via rotary leadthroughs  73 ,  74  into supply lines  75 ,  76  and metered into the pressure chambers  77 ,  78 , with the result that the pistons  69 ,  70  are displaced counter to the action of the axially active energy accumulators  79 ,  80  and the wet clutches  28 ,  29  are thereby closed, depending on the applied pressure of the pressure medium. When the pressure in the pressure chambers  77 ,  78  is reduced, the wet clutches are opened again automatically as a result of the expansion of the energy accumulators  79 ,  80 . The supply lines  81 ,  82  serve for cooling the wet clutches  28 ,  29 , in particular the friction linings of the friction lamellae  40 ,  41 , which are exposed to special heat stress particularly when the wet clutches  28 ,  29  are under slipping conditions. The pressure medium metered in this way cools the friction lamellae  40 ,  41  and flows radially outward, from where it is scooped up by the scoop pipe  14  connected fixedly to the transmission housing  22  by means of the guide pins  83  and is fed to the transmission sump via the discharge line  84 . 
     A friction device  85  may be provided between the torsional vibration damper  12  and the input part  13  of the wet clutches  28 ,  29 . For this purpose, a friction ring  87  can be acted upon by means of circumferentially distributed axially raised pins  86  of the lamella carrier  34  and is centered by means of the holding ring  88  fastened to the housing part  6  and is braced by means of the axially active energy accumulator  89 , which may, for example, be a cup spring, as shown, with respect to said holding ring. Additionally or alternatively, the friction device  85  may serve as centering for the two wet clutches  28 ,  29  in the housing  8  before final assembly, as long as said friction device is not yet centered on the transmission input shaft  49 . 
       FIG. 2  shows the built-up lamella carrier  34  of  FIG. 1  in detail as a sectional illustration. The lamella carrier  34  is formed from the flange part  13   a , the carrier disk  36  and circumferentially distributed connection elements  90  arranged axially between them. In the exemplary embodiment shown, the connection elements  90  are formed from prebent sheet metal parts  91  having axially extending rivet studs  92 ,  93  which are led through corresponding orifices  94 ,  95  in the flange part  13   a  or carrier disk  36  and are riveted from outside against this. The circumferentially pointing ends of the sheet metal parts  91  are counted or bent radially inward to form tooth flanks  96 , so as to form, in the cross section of the sheet metal parts  91 , a tooth flank profile, on which are suspended the lamellae  38  which, for this purpose, have a complementary outer profile  97 , so that the lamellae  38  are centered on the lamella carrier  34  and the torque prevailing at the lamella carrier  34  is transmitted to the lamellae  38 . The lamellae  38  are layered alternatively with the frictional lamellae  40  which are suspended in the output-side lamella carrier  42  fixedly in terms of rotation and so as to be displaceable axially to a limited extent. 
       FIG. 3  shows a version alternative to the deep-drawn lamella carrier  35  of  FIG. 1 , in the form of the lamella carrier  35   a  in a built-up version. The lamella carrier  35   a  has connection elements  98  which are designed comparably to the connection elements  90  of  FIG. 2  and are riveted between the end lamella  72   a  and the carrier disk  36 . Furthermore,  FIG. 3  shows a connection element  90   a  with an axially prolonged pin  86  which replaces the connection element  90  of  FIG. 2 , for example, in a plurality of circumferential positions and thereby enables the lamella carrier  34  ( FIG. 1 ) to engage with the friction device  85 , in that the pins  86  drive the friction ring  87  in the circumferential direction with respect to the housing  8  ( FIG. 1 ) of the clutch unit and thus control the friction device. 
       FIG. 4  shows a cutout from the flange part  13   a  with the driver  19  for the energy accumulators  11  of the torsional vibration damper  12  ( FIG. 1 ) and the orifices  94  for receiving the connection elements  90  by means of the rivet studs  92  of  FIG. 2 . The cross section of the orifices  94  is polygonal, here square, and complementary to the likewise square cross sections of the rivet studs  92  ( FIG. 1 ). In the exemplary embodiment shown, each connection element  90  ( FIG. 2 ) has two adjacent rivet studs, so that in each case at least two adjacent orifices  94  are provided per connection element. 
       FIG. 5  shows a cutout from a lamella  38   a  which is similar to the lamella  38  of  FIG. 1  and is produced, for example, from steel. In relation to the version of the clutch unit  1  of  FIG. 1 , the lamellae  38   a  are suspended in connection elements  90   b  which are changed with respect to the connection elements  90 ,  90   a  of the lamella carrier  34  of the radially outer wet clutch  28  and/or with respect to the connection elements  98  of the lamella carrier  35  of the radially inner wet clutch  29  and which are formed from stepped bolts  99 . For this purpose, circumferentially distributed recesses  100   a  in the form of segments of a circle are provided at the lamellae  38   a  in a number corresponding to the number of stepped bolts  99 , so that the lamellae  38   a  are centered and driven on the lamella carrier, not shown, via the stepped bolts  99 . Since the bearing surfaces of the stepped bolts  99  on the bearing surfaces of the lamella  38   a  are provided by the recesses  100   a  and are smaller in comparison with the connection elements of  FIGS. 1 to 4 , the number of stepped bolts  99  is increased with respect to the number of these connection elements and amounts in the exemplary embodiment shown to twenty four. 
       FIG. 6  shows a view of a cutout from a lamella  38  of  FIGS. 1 to 4 . Circumferentially distributed recesses  100  complementary to the connection elements  90  are provided in the lamella  38  and have in each case bearing surfaces  101  which run radially outward obliquely and make a form fit in the circumferential direction with the tooth flanks  96  of the sheet metal parts  91 , so that a rotary take-up of the lamella  38  when the connection elements  90  are subjected to rotary action by the lamella carrier, not shown, takes place. For this purpose, the rivet studs  92  or rivet studs  93  ( FIG. 2 ), in a view from the other direction, are riveted to the orifices  94  of the flange part  13   a  or the orifices  95  of the carrier disk  36  ( FIGS. 2 and 4 ). 
       FIGS. 7 to 9  show views of a not-yet-riveted connection element  90  from three directions, and it is illustrated in  FIGS. 1 to 4  in the installed, that is to say riveted state. The connection element  90  formed from the stamped and preformed sheet metal part  91  has, for riveting to the end faces, in each case at least two rivet studs  92 ,  93  which in cross section preferably, and as illustrated, have a square design. In this case, the rivet studs  92 ,  93  are widened axially out of the planar base surface  102  with respect to which the tooth flanks  96  are designed to be angled. 
       FIGS. 10 to 12  show a variant, alternative to the connection element  90  illustrated in  FIGS. 7 to 9 , of a connection element  90   c  in a view from three directions in the riveted state with the rivet heads  103 ,  104  in each case widened with respect to the rivet studs  92   a ,  93   a . In contrast to the connection element  90  of  FIGS. 7 to 9 , the rivet studs  92   a ,  93   a  are arranged on the tooth flanks  96  and therefore are in each case at a greater distance from one another. As a result of this further distance, a greater stability in the fastening of the connection elements  90   c  to the flange part  13   a  or to the carrier disk  36  can be achieved. 
       FIG. 13  shows a view of the connection element  90   a  of  FIGS. 1 and 3  in the riveted state. The pin  86  for acting upon and controlling the friction device  85  of  FIGS. 1 and 3  is widened axially out of the tooth flank  96 . 
       FIGS. 14 and 15  show the stepped bolt  99  of  FIG. 5  in a view in the non-riveted state ( FIG. 14 ) and riveted state with rivet studs  92   b ,  93   b  arranged on both sides and, in the riveted state, with the rivet heads  103   a ,  104   a . The stepped bolts  99  are preferably produced by cutting, so that the rivet studs  92   b ,  93   b  are designed with a round cross section. 
     LIST OF REFERENCE SYMBOLS 
     
         
           1  Clutch Unit 
           2  Axis of Rotation 
           6  Housing Part 
           7  Housing Part 
           8  Housing 
           11  Energy Accumulator 
           12  Torsional Vibration Damper 
           13  Input Part 
           13   a  Flange Part 
           14  Scoop Pipe 
           16  Annular Flange Part 
           17  Driver 
           18  Driver 
           19  Driver 
           20  Crankshaft 
           21  Drive Plate 
           22  Transmission Housing 
           23  Rolling Bearing 
           24  Axial Extension 
           25  Toothed Ring 
           26  Sealing Disk 
           27  Seal 
           28  Wet Clutch 
           29  Wet Clutch 
           30  Bow Spring 
           31  Bow Spring 
           32  Shoulder 
           33  Wear Protection Shell 
           34  Lamella Carrier 
           35  Lamella Carrier 
           35   a  Lamella Carrier 
           36  Carrier Disk 
           37  Clutch Hub 
           38  Lamella 
           38   a  Lamella 
           39  Lamella 
           40  Friction Lamella 
           41  Friction Lamella 
           42  Lamella Carrier 
           43  Lamella Carrier 
           44  Hub 
           45  Hub 
           45   a  Energy Accumulator 
           45   b  Securing Disk 
           46  Toothing 
           47  Toothing 
           48  Transmission Input Shaft 
           49  Transmission Input Shaft 
           50  Torsional Vibration Absorber 
           51  Centrifugal Pendulum 
           52  Centrifugal Weight 
           53  Rolling Bearing 
           54  Rolling Bearing 
           55  Rolling Bearing 
           56  Run-On Disk 
           57  Run-On Disk 
           58  Carrier Part 
           59  Lubricating Oil Groove 
           60  Rolling Bearing 
           61  Rolling Bearing 
           62  Sealing Plate 
           63  Shoulder 
           64  Securing Ring 
           65  Run-On Disk 
           66  Carrier Part 
           67  Shim Disk 
           68  Run-On Disk 
           69  Piston 
           70  Piston 
           71  End Lamella 
           72  End Lamella 
           72   a  End Lamella 
           73  Rotary Leadthrough 
           74  Rotary Leadthrough 
           75  Supply Line 
           76  Supply Line 
           77  Pressure Chamber 
           78  Pressure Chamber 
           79  Energy Accumulator 
           80  Energy Accumulator 
           81  Supply Line 
           82  Supply Line 
           83  Guide Pin 
           84  Discharge Line 
           85  Friction Device 
           86  Pin 
           87  Friction Ring 
           88  Holding Ring 
           89  Energy Accumulator 
           90  Connection Element 
           90   a  Connection Element 
           90   b  Connection Element 
           90   c  Connection Element 
           91  Sheet Metal Part 
           92  Rivet Stud 
           92   a  Rivet Stud 
           92   b  Rivet Stud 
           93  Rivet Stud 
           93   a  Rivet Stud 
           93   b  Rivet Stud 
           94  Orifice 
           95  Orifice 
           96  Tooth Flank 
           97  Outer Profile 
           98  Connection Element 
           99  Stepped Bolt 
           100  Recess 
           100   a  Recess 
           101  Bearing Surface 
           102  Base Surface 
           103  Rivet Head 
           103   a  Rivet Head 
           104  Rivet Head 
           104   a  Rivet Head