Abstract:
A torque-transmitting apparatus, particularly for motor vehicles, with a fluid coupling or a hydrodynamic torque converter and a damping system has an improved design providing the advantages of stress-free mounting of the damper, technical and cost improvements in the manufacture of the apparatus, modular assembly, capability to transmit large torque and attenuate rotational perturbations over a wide RPM range so as to minimize wear to prolong the useful life of the entire unit.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is a division of co-pending application Ser. No. 09/305,504, filed May 5, 1999, and which is hereby incorporated by reference in its entirety. 
    
    
     BACKGROUND OF THE INVENTION 
     The invention relates to a torque-transmitting apparatus with a fluid-operated torque coupler such as, e.g., a fluid coupling or a hydrodynamic torque converter, with at least one housing that can be connected to a driving shaft of a prime mover. The housing contains at least one impeller pump receiving torque from the housing and a turbine that is connected to the input shaft, such as a transmission shaft, of a power train to be driven. Also, if applicable, the housing contains at least one stator arranged between the pump and the turbine. Further, at least one damper is arranged in the power flow between the turbine and a rotary output element of the device. The damper has an input member constrained to rotate together with the turbine and an output member connected to the rotary output element. The input member and the output member are rotatable relative to each other at least against the opposition of a restoring force furnished by energy-storing devices arranged between them. 
     Torque-transmitting apparatuses of this kind have been proposed, e.g., in DE-OS 195 14 411. To allow rotational displacement of the input and output members relative to each other, it is customary for torque-transmitting apparatuses of this kind to be equipped with a hub that has a toothed internal profile establishing a positive engagement with the transmission shaft and also a toothed external profile which mates with a further component, normally a further hub that carries the turbine and has a toothed internal profile, with play between the flanks of the mating teeth. When a lockup clutch is added that is activated by an axial control piston, there needs to be a corresponding axial space to allow for the axial travel of the hub containing the two toothed profiles. The manufacture of hubs of this kind is complex and therefore expensive. Furthermore, due to the required axial dimension, longer transmission shafts will be needed. Added to this is the difficulty of connecting bulky hub components with the filigreed construction of the turbine shell. Also, dampers that extend far in the radial direction have a tendency to wobble. If in an attempt to solve these problems, the damper is axially docked to the turbine along two or more perimeters of different radii, this will cause undesirable stresses and frictional losses in the damper. 
     OBJECTS OF THE INVENTION 
     It is therefore an object of the present invention to improve the design of a torque-transmitting apparatus in a manner that allows a stress-free accommodation of the damper as well as economical and technical improvements in the manufacturing process for torque-transmitting apparatuses of this kind. According to a further object of the invention, the device is to be manufacturable in such a manner that a modular assembly without time-consuming fastening operations can be performed during final assembly. Also required of the torque-transmitting apparatus are the capabilities to transfer torque of high magnitude and to attenuate rotational perturbations over a broad RPM range. Besides, the unit is to meet the objectives that it will minimize wear and prolong the useful life of the overall system of which it is a part. 
     SUMMARY OF THE INVENTION 
     The invention is embodied in a torque-transmitting apparatus of the kind that has a fluid-operated torque coupler such as a hydrodynamic torque converter or a similar device comprising 
     at least one housing that can be connected to a driving shaft of a prime mover, 
     at least one pump that is arranged inside of and driven by the housing, 
     a turbine that is connected to and drives the input shaft of a power train such as a transmission shaft and also, if applicable, 
     at least one stator arranged between the pump and the turbine, and further 
     at least one damper arranged in the torque-flow path between the turbine and a rotary output element of the apparatus, with an input member of the damper being constrained to rotate together with the turbine and an output member of the damper being connected to the rotary output element, the input member and the output member being at least rotatable relative to each other at least against the opposition of the restoring force exerted by energy-storing devices arranged between them. 
     In accordance with one presently preferred embodiment of the improved torque-transmitting apparatus, the damper at its outside perimeter is directly or indirectly connected to the turbine through a positive rotational constraint. This connection may be free of play relative to coaxial rotational displacements but may allow an axial displacement of the turbine and the input member of the damper relative to each other. For example, the connection may be axially displaceable by means of an axial plug-in connection with the damper rigidly attached to a hub. The problem can further be solved through a torque-transmitting apparatus with a damper whose connection to the turbine shell or turbine, or to the hub, is rotationally fixed both along an inside and outside perimeter, while in the axial direction the connection is fixed only along one perimeter, either on the hub or on the turbine shell, so that axial stresses are relieved by an axial displacement at the axially non-restrained connection. 
     In accordance with a further inventive concept, there may also be an axially and rotationally fixed connection at the outside perimeter of the damper in which case, in order to prevent stresses in the damper, the inside perimeter of the damper may be designed to be axially displaceable, e.g., in an arrangement where the damper, by means of a positive circumferential coupling such as a toothed profile, engages a complementary profile on the hub. In addition, the profile on the hub may be axially fixed but rotatable on a complementary profile of the turbine hub on which the turbine is seated, with the amount of rotational play designed to be at least equal to the working range, i.e., the effective angular range, of the damper. The play in the form-fitting engagement between the turbine hub and the hub may also be obtained through additional devices such as window-like openings that are distributed over the circumference of the hub and are engaged with angular play by a corresponding series of axially directed projections on the turbine hub. 
     With particular advantage, the connection between the turbine and the input member of the damper is accomplished through welding processes such as laser welding, impulse welding, or resistance welding, in which case the damper can be centered on the hub by means of a disk-shaped part that holds the energy-storing devices, or on the turbine shell, e.g., by providing the turbine shell with a series of projections that are distributed over the circumference and that may also serve as locating references for the weld. 
     It is advantageous for the torque-transmitting apparatus to be provided with a lockup clutch arranged in the torque-flow path between the driving shaft and the damper, in which case it has proved to be beneficial if the lockup clutch, by means of friction linings or laminar disks, establishes a positive engagement with a housing surface and transfers the torque to be transmitted directly to the input member of the damper. Thus, when the lockup clutch is engaged, the torque converter is bypassed and the torque to be transmitted is introduced directly into the damper and from there to the rotary output element and subsequently to the transmission shaft. When the lockup clutch is disengaged, the turbine will impart the torque that has been converted—in most cases amplified through the effect of the stator—to the input member of the damper from where the torque will follow the same path as has been previously described. 
     The clutch can be engaged and disengaged through an axially moveable control piston that is controlled by an application of pressure. It is advantageous if the control piston defines a plenum chamber which, in the engaged state of the lockup clutch, is essentially sealed tight against the interior space of the housing (except for insignificant flows of pressure medium into the housing that may be provided to cool the friction linings) and is energized by a pressure medium identical to the converter fluid that is admitted through a bore hole, whereby a pressure force is applied to the piston in the axial direction towards the turbine. According to the invention, this axial displacement is compensated by allowing an axial displacement of the axial plug-in connection. Another possibility for controlling the piston is to apply an over pressure to the control piston, in which case the piston will seal off the chamber when the clutch is open; and when the pressure in the chamber is reduced, the piston is pushed to the housing wall by the fluid pressure in the torque converter, thereby causing the lockup clutch to engage. 
     The control piston can be centered on the transmission shaft, on a hub holding the housing of the torque converter, or on another appropriate part of the apparatus and is preferably provided with sealing means at the interface surfaces to these components for the purpose of sealing the plenum chamber in the same manner as the piston can be sealed at its outside perimeter against the housing. 
     A further embodiment comprises a form-fitting engagement between the control piston and the housing by means of complementary profiles extending in the axial direction, in which case the axial profile is formed by alternating ridges and grooves in the shape of ring segments that are distributed over a perimeter where, e.g., the ridges of the control piston may engage the grooves in the housing. An advantage of such configuration is the direct engagement of the piston with the housing so that the piston can transmit torque to the friction linings directly and/or through other pressure-transmitting devices, whereby the use of an enlarged friction surface and/or of a larger number of friction surfaces and thus a greater transmission torque is made possible. 
     For this purpose, there may be one or more carriers of friction linings in the form of annular disks or laminar disks that can carry friction linings in the outer zones of their axially facing surfaces. The friction-lining carriers or laminar disks are axially movable, and the pressure force is applied against a ring-shaped pressure plate that is connected with the housing either directly or indirectly, e.g., welded, riveted or attached to a flange that is, in turn, connected to the housing. For better cooling fluid distribution, the pressure plate can have one or more circles of holes. 
     It is advantageous to center the friction-lining carrier on the housing. For this purpose, the friction-lining carrier can be provided with lugs that protrude axially towards the housing and are inserted in a shoulder extending in the direction away from the friction-lining carrier. 
     A further advantageous embodiment renders it possible to configure the piston itself as the lockup clutch or, more precisely, as the friction-lining carrier. For this, the radially outer part of the control piston surface that faces axially towards the housing carries a ring-shaped friction lining that may be provided with an optimized surface finish to achieve better cooling. The piston surface may be bent in the axial direction towards the turbine, so that the piston may rest in form-fitting contact against the housing, which in the respective surface portion is shaped similar to a cone shell. 
     As already described above, the lockup clutch is connected through one of its components to the input member of the damper. In one embodiment, the connecting part may be the control piston itself in the manner described above, in which case the piston may be connected to lateral parts of the input member by rivets, weld joints or similar means. A further embodiment employs a ring-shaped friction-lining carrier that may form an axial plug-in connection by virtue of an appropriately shaped lateral portion. In case the friction-lining carrier has a form-fitting engagement with the input member of the damper, e.g., by means of internal teeth at its inside perimeter and, e.g., an axially oriented profile on the lateral part of the input member. The advantages of axial plug-in connections in accordance with the invention are that they compensate for axial displacements and facilitate the manufacturing process by virtue of a modular configuration, because systems of this kind can be built by plug-in assembly without further resort to fastening undertakings such as, e.g., welding or riveting, thus allowing the use of work stations that are not equipped with the respective infrastructure. 
     Further advantageous embodiments of axial plug-in connections between components of the damper and components of the turbine will be described hereinafter. An advantageous configuration has two components of the two units to be connected meeting each other approximately at a right angle, i.e., in the form of a radially and an axially extending flange, respectively, with the two parts in a form-fitting engagement. In this, it may be advantageous to provide the radially extending flange with external teeth and the axially extending flange with axially oriented teeth. 
     It may also be advantageous if a radially extending flange-like part has closed cutouts, distributed along a circle of smaller radius than the outside perimeter, that are engaged by axially directed extremities of the axially extending flange-like part. 
     A preferred embodiment may be a radially oriented flange-like part that, starting at its inside perimeter, follows the shape of the turbine shell outwards in the radial direction and is attached in this portion, e.g., welded or riveted. From there, the flange-like part bends into the radial direction and has a toothed profile along its exterior circumference that is engaged by the lateral part of the input member of the damper. For this purpose, the lateral part at its exterior circumference bends into the axial direction and forms the axially directed flange-like part that carries, e.g., the axially oriented toothed profile. 
     A further advantageous embodiment may include a flange-like part in the shape of an annular disk that adjoins along its inside perimeter the turbine shell and conforms to the shape of the turbine shell towards the inside in the radial direction, is attached to the shape-conforming portion as described above and then curves into the axial direction. The profile facing away from the turbine shell in axial direction, e.g., a toothed profile, engages in closed recesses distributed over the circumference of a radially directed lateral part and in this manner forms an axial plug-in connection. To form this plug-in connection, it may be necessary for the axially directed toothed profile to pass through the output member before engaging the input member of the damper, given that the output member is interposed axially between the turbine and the input member. For this purpose, the output member has a circular arrangement of elongated holes matching the number of teeth. The angular width of the holes corresponds to the maximum angular displacement of the input and output members relative to each other so that at the same time the elongated holes in combination with the axially directed teeth of the axially oriented flange-like part that is connected to the turbine form at least one stop for the angular displacement of the damper. 
     In an advantageous arrangement, the axially extending flange-like part can itself be in the form of a hub that carries the turbine, the latter being connected to the hub by, e.g., welding or riveting. The hub carrying the turbine, in turn, can be seated on a further hub that performs the function of the rotary output element and is attached to the transmission shaft. The axially extending flange-like part has a profile established, e.g., by axially oriented teeth that extend into enclosed cutouts corresponding to the number of teeth in the flange whereby an axial plug-in connection is formed. Depending on the configuration of the damper, it may be necessary with this embodiment, too (as described above) , to provide in the output member an appropriate arrangement of elongated holes which, in combination with the axially directed profile of the axially oriented flange for the axial plug-in connection, can function as stops for the relative displacement between the input and output members of the damper. The output member, being a radial extension of the hub that is attached to the transmission shaft, may also be configured as a separate flange-like part, in which case the flange needs to be centered on the hub and attached through a rotationally fixed connection. 
     It can further be advantageous if an annular disk in the form of a radially extending flange-like part with an exterior profile, e.g., an arrangement of external teeth, is centered on the hub that carries the turbine. By attachment means such as, e.g., rivets, the annular disk is rotationally tied to the turbine, and its outward-pointing teeth, mentioned above by way of an example, engage a lateral part that is bent in the axial direction along the interior perimeter and (also by way of example) has a complementary, axially directed toothed profile. In this case, too, a connection is established that constrains rotational but allows translational displacement of the engaged parts relative to each other. The angular displacement of the damper may advantageously be defined by means of a toothed profile with play between the respective tooth flanks of the hub and the annular disk. The outward-facing profile of the hub may also be engaged by the inward-facing profile of the output member, albeit without play at the flanks, in order to secure the output member for rotation with the hub. This has the advantage of saving space in the axial direction of the hub, given that the relative axial displacement occurring between the damper and the turbine as a result of the axial movement of the control piston is already compensated for by the axial plug-in connection. 
     The axial plug-in connection between the damper and the turbine in different practical variations may be arranged, e.g., at a radial distance beyond the energy-storing devices, at an intermediate radius between the storage devices in the case of at least two damper stages, or inside the radial distance of the storage devices. 
     Other embodiments of the invention concern the advantageous design of the damper. The damper may be of the single-stage or multi-stage type. A dual-stage damper may be configured in such a way that the damper stages can function in a serial or parallel mode, with the additional possibility of different limits of rotation so that, e.g., in a serial arrangement of the damper stages the relative rotation of one stage is stopped before the other stage, e.g., for the purpose of achieving particular damping characteristics. 
     In connection with the damper, it is also advantageous to combine different energy-storing devices, e.g., by selecting arc-shaped springs in a radially exterior damper stage, and short, stiff spring elements for use in smaller-diameter areas so that, e.g., a damper characteristic can be achieved that provides a high amount of energy to compensate for both large-amplitude rotational irregularities at low RPM and small-amplitude rotational irregularities at high RPM. In this kind of an arrangement, the arc-shaped springs in the radially exterior area may be pre-bent to their working diameter and are retained radially by a chamber that is formed by at least one lateral part or by other components of the damper or of the torque-transmitting apparatus, e.g., by the wall of the housing. In addition, there may be wear-reducing components such as wear-protection shells interposed between the arc-shaped springs and the chamber, with the characteristic of the arc-shaped spring being determined by all of the aforementioned factors. 
     It can be advantageous to provide the individual damper stages with displacement properties that depend on the direction from which the torque is introduced. Thus, the damper system may be designed to function in two stages in the “pull” mode and in one stage in the “push” mode. In this manner, the damper characteristic may be adapted to the possibility of hard transient peaks in the torque-flow that are introduced from the “push” side, i.e., from the input shaft of the transmission, in which case, e.g., the soft damper stage is bypassed completely and the firm damper stage is effective instantly. The bypass can be accomplished by means of limit stops that block angular displacement against the drive direction in the input and output members of the damper stage that is inactive in the push mode. 
     It is advantageous to accommodate the storage devices in disk-shaped parts that have dimensionally matched recesses into which the storage devices are fitted and which may at their ends have force-introduction elements facing against the direction of the restoring force. The force-introduction elements retain and thereby compress the storage devices when the input and output members are displaced in relation to each other. The disk-shaped parts forming the input and output members may be arranged in such a manner that either the input or output member is formed by two mutually connected lateral parts, while the other of the two members is formed by a corresponding disk-shaped, flange-like part arranged between the two lateral parts. A further embodiment that brings cost advantages has two disk-shaped parts, one representing a lateral part serving as input member and the other representing a lateral part serving as output member. In two-stage dampers, it can further be cost-effective to use a common disk-shaped part working with both damper stages. 
     Further in the interest of optimizing cost, the disk-shaped parts may take or additional functions. For example, as mentioned already, one or more disk-shaped parts may form a chamber for the energy-storing devices, or they may contain the axial plug-in connection between the damper and the turbine, and/or they may perform other functions. 
     It is further advantageous for cost-optimization if disk-shaped parts and different other components are made of one piece. Thus, e.g., the output member of the damper together with the rotary output element (e.g., the hub that is arranged on the transmission shaft), or the output member together with the hub that carries the turbine, may be made of one piece. 
     An advantageous and cost-effective embodiment of means for limiting the extent of angular displacement avoids the need for special stops. For this purpose, a circular arrangement of elongated holes may be provided on at least one disk-shaped part, where the fasteners (e.g., rivets) that are in any case already provided pass through the holes and are held on the opposite side by another disk-shaped part and/or by means of a sheet metal holder. The angular width of the elongated holes is preferably selected so that the extent of relative angular displacement between the input member and the output member is limited by the ends of the elongated holes stopping the shafts of the fasteners. 
     It is advantageous to provide displacement-limiting stops insofar as a damper or either some or all of the damper stages can be bypassed, so that the damper or the damper stages can be protected from wear. This may apply particularly in the case of wear-prone versions with storage devices that, e.g., contain arc-shaped springs, permit large angular displacements, and/or are exposed to strong shock loads. To guard against premature failure, it is advantageous if initially one damper stage is totally bypassed by means of displacement-limiting stops, while the second stage is either not bypassed at all or only at a later point. When a damper or a damper stage reaches its limit stop, the torque that previously entered into the energy-storing device is transmitted through the stop directly to the output member of the bypassed damper or damper stage. It may also be advantageous to provide different angular displacement limits in the damper device and its damper stages depending on the direction off the torque, i.e., whether the torque works in the pull or push direction, respectively. Thus, it may be advantageous, for example, to provide limit stops in such a manner that a damper stage is entirely bypassed in the costing mode. Likewise, there may be advantages to a configuration in which, e.g., one damper stage works only in the coasting direction while the other stage works only in the pull direction. 
     The novel features that are considered as characteristic of the invention are set forth in particular in the appended claims. The improved apparatus itself, however, both as to its construction and its mode of operation, together with additional features and advantages thereof, will be best understood upon perusal of the following detailed description of certain presently preferred specific embodiments with reference to the accompanying drawing. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a fragmentary sectional view of a novel torque-transmitting apparatus with a two-stage damper. 
     FIG. 2 is a fragmentary sectional view of a further embodiment of a torque-transmitting apparatus with an axial plug-in connection located at a radial position between the energy-storing devices of two damper stages. 
     FIG. 3 is a fragmentary sectional view of an embodiment of the invention with axially directed projections formed on the hub. 
     FIG. 4 is a partial view of a disk-shaped part of a damper. 
     FIG. 5 is a fragmentary sectional view of an embodiment of a damper. 
     FIG. 6 represents a fragmentary view of another embodiment of a damper. 
     FIG. 7 is a fragmentary axial sectional view of an embodiment of a torque-transmitting apparatus with a single-stage damper. 
     FIG. 8 is a fragmentary axial sectional view of an embodiment of a torque-transmitting apparatus with a two-stage damper and a two-part hub. 
     FIGS. 9-12 are fragmentary sectional views of further embodiments of two-part turbine dampers. 
     FIG. 13 represents an embodiment with a damper docked fixedly to the turbine shell. 
     FIG. 14 represents a modified version of the damper of the embodiment of FIG.  13 . 
     FIG. 15 represents a detail of an embodiment comprising a damper that is docked fixedly to the turbine shell. 
     FIG. 16 represents an embodiment of a torque-transmitting apparatus comprising a damper that is docked fixedly to the turbine shell. 
     FIG. 17 represents a hub of the embodiment of FIG.  16 . 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The torque-transmitting apparatus  1  shown in FIG. 1 has a housing  2  confining a torque converter  3 . The housing  2  is connected to a driving shaft that can constitute the output shaft of a prime mover such as, e.g., the crankshaft of a combustion engine. As is known, the housing  2  is constrained to rotate with the shaft by a sheet metal disk that is connected at an inner radius with the driving shaft and at an outer radius with the housing. 
     The housing  2  comprises a shell  4  adjoining the driving shaft or the combustion engine and a further shell  5  axially distant from the driving shaft and attached to the housing shell  4  by means of a weld  2   a.  The two housing shells  4  and  5  are connected and sealed at their radially outer portions by a welded connection  6 . In the illustrated embodiment, the housing shell  5  simultaneously serves as the outer shell of the pump  7 . This is accomplished by connecting the vane portions  8  to the housing shell  5  in a manner known as per se. A turbine  10  is interposed axially between the pump  7  and the radially extending wall  9  of the housing shell  4 . A stator  11  is provided between the radially interior portions of the pump  7  and the turbine  10 . 
     Furthermore, the internal space  12  enclosed by the housing shells  4 ,  5  contains a torque-elastic damper  13  that establishes torque-elastic connection between the output hub  14  and a driving part. In the illustrated embodiment, the driving part is formed by the housing shell  4  in the case where the lockup clutch  15  is engaged or operates with slip. When the lockup clutch  15  is disengaged or slipping, the driving part is formed by the turbine  10 . The converter lockup clutch  15  is arranged in series with the damper  13 . 
     The hub  14  representing the rotary output element of the torque-transmitting apparatus  1  can be coupled through an interior toothed profile  16  to an input shaft (not shown) of a transmission. The turbine  10  is rotatable within a limited angular range relative to the rotary output element, i.e., the hub  14 , against the opposition of the damper. In the case of a damper based on the principle of shear flow of a hydraulic medium, while the relative rotation between the turbine  10  and the output element  14  would still be damped, the angle of relative rotation would be unrestricted. 
     The output hub or rotary output element  14  is non-rotatably connected e.g., welded or caulked, to the flange-like output member  17  of the torque-elastic damper  13 . The input member  18  of the torque-elastic damper  13  is at its outer perimeter bent in the axial direction towards the turbine and forms an axially oriented flange-like part  19  with a rim of axially directed teeth  20 . At its interior perimeter the input member  18  is bent in the axial direction towards the housing shell  4  and has a rim of axially directed teeth  21  so that the input member  18  transmits the torque flow through form-locking connections to the lockup clutch  13  and the turbine  10  by means of the toothed rims  20 ,  21 . For this purpose, a radially oriented flange-like part  22  is attached to the turbine  10  by a weld  24  along its inner perimeter to the outside of the turbine shell  23 . The flange-like part  22  along its outside perimeter has a toothed rim  26  and thereby forms an axial plug-in connection  78  to the input member  18  of the damper  13 . 
     Input member  18  and output member  17  in the axial space between them enclose a flange-like intermediate part  27  which simultaneously constitutes the output member of the first damper stage  28   a  and the input member of the second damper stage  28   b.  Input member  18 , output member  17 , and intermediate part  27  are equipped in an essentially known manner with windows for holding the energy-storing devices in the form of coil springs  29 ,  30  for the two damper stages  28   a,    28   b.    
     In the axial direction, input member  18  is connected to an intermediate part  27 , and the intermediate part  27  is connected to the output member  17  by means of fasteners, here in the form of rivets  31 ,  32 . The given range of play by which the parts can rotate relative to each other is limited by the rivets passing through elongated perforations  33 ,  34  that are arranged along a circle on the input member  18  and on the intermediate part  27 , forming stops limiting the extent of travel of the rivets within the holes. As axial retainers for the rivets  31 ,  32 , ring-shaped membranes  35 ,  36  are provided on the side of the perforations  33 ,  34 . The axial spacing of the input member  18  from the intermediate part  27  and of the intermediate part  27  from the output member  17  is provided by energy-storing devices working in the axial direction between the respective parts, represented in this embodiment by plate springs  44 ,  45 . 
     The input member  18  at its interior perimeter has a profile shape designed to accommodate the energy-storing devices  30  so as to make optimum use of the available axial space, then turning into the axial direction to form an axially oriented flange-like part  37  with a rim of axially directed teeth  21 , where the input member  18  meets the exterior toothed rim  39  of a friction-lining carrier  38  in a form-locking engagement. The friction-lining carrier  38  is centered on a shoulder  41  by means of lugs  40  bent into the axial direction towards the control piston  43  and is faced on both sides with friction linings  42  along its outer perimeter. The friction-lining carrier  38  is interposed in the axial direction between the control piston  43  and the annular disk  46 . The latter is attached in a rotation-blocking connection to the housing shell  4 , which in the respective area extends in the radial direction. Fastener means such as the impulse weld  48  of the present example are used for the connection. The annular disk  46  has cut-outs  47  distributed along a circle that serve to promote circulation and cooling of the chamber  49  that is formed between the annular disk  46 , the control piston  43  and the friction-lining carrier  38 . The annular disk is centered on the housing  2  by means of projections  57  arranged in a circle of the housing shell  4 . 
     The axial displacement of the control piston  43  effects the slipping engagement, full engagement and disengagement of the lockup clutch  15 . The control piston is actuated by the pressure differential in the chamber  50  that is located in the axial direction between the control piston  43  and the housing shell  4  and is supplied from a pressure pump (not shown) with a pressure medium entering through a channel  51  from the radially interior direction. To seal off the chamber  50 , the control piston  43  is equipped along its inner and outer perimeter with sealing means  51   a,    52 . Also, in order to improve guidance and to prevent canting and thereby jamming of the control piston, the latter is bent into the axial direction at one perimeter, such as at the interior perimeter in the present embodiment. To avoid slippage at the sealing means of the piston  43 , the latter has a form-locking engagement with the housing  2  through an axially oriented profile  54  which in the present embodiment consists of alternating ring segment-like recesses  53  and projections  55  that are distributed over the circumference and are engaged by the complementary-shaped profile  56  of the housing shell  4 . 
     The embodiment of FIG. 1 illustrates the function of the torque-transmitting apparatus  1  as follows: When the lockup clutch is open, the torque is transmitted by the pump  7  driving the turbine  10 , assisted in known manner by the free-wheeling stator  11 , through the converter medium that fills the interior space  12  to the flange-like part  22  from where the torque is introduced through an axial plug-in connection formed by the engagement of toothed rims  20 ,  26  into the input member  19  of the damper  13 . When the lockup clutch  15  is closed, the torque-flow path runs through the form-locking engagement of the mutually complementary profiles  54 ,  56  as well as through the annular disk  46  that is connected to the housing  2 . Through the friction engagement of the control piston  43  and the annular disk  46  with the friction linings  42 , the torque is introduced into the friction-lining carrier  38  which, by means of the axial plug-in connection with toothed rims  21 ,  40 , transmits the torque to the input member  18 . Continuing from the input member  18 , the torque flow is smoothed in the damper  13  by means of energy-storing devices  29 ,  30 . The angular displacement of both damper stages  28   a,    28   b  is bounded by limit stops  33 ,  34  and matched to the characteristics and properties of the energy-storing devices  29 ,  30 . If a friction component is needed in the damper  13 , i.e., in the damper stages  28   a,    28   b,  the energy-storing devices  44 ,  45  are designed independently of each other in such a manner that a frictional engagement occurs for the first damper stage  28   a  between the securing membranes  31 ,  36  and the input member  17  and/or for the second damper stage  28   b  between the securing membranes  35 ,  36  and the intermediate part  27 . the output member  17  of the damper  13  transmits the torque to the hub  14  representing the rotary output element of the torque-transmitting apparatus  1 , from where the torque is introduced into the transmission shaft. 
     FIG. 2 shows an inventive torque-transmitting apparatus  101  of similar configuration as the torque-transmitting apparatus  1 , but with a modified damper  113 . The pump  107 , stator  111 , turbine  110 , the overall construction, function and arrangement of the lockup clutch  115  are provided in similar manner as has been described in connection with FIG.  1 . 
     The axial plug-in connection  178  in this embodiment is formed by the flange-like part  122 , which is engaged without play in recesses  120  that are distributed over the circumference of the input member  118 . At its interior perimeter, the flange-like part  122  is connected to the shell  123  of the turbine  10 —by a weld  124  in the illustrated example. Subsequently, the flange-like part  122  conforms to the shape of the turbine shell at a radial distance, then turns into the axial direction towards damper  113 , where its rim of axially oriented teeth  126  engages the openings  120  of the input member  118 . The toothed engagement cccurs at a radius inside the first damper stage  128   a  and outside the second damper stage  128   b  where the flange-like part  122  runs in the axial direction and passes through elongated perforations  133 ) formed along a circle on the intermediate part  117  that is provided as output member of the first damper stage  128   a.  Simultaneously, the flange-like part  122  forms the limiting stops for the relative angular displacement between the input member  118  and the intermediate part  117  within the angular range that is delimited by the perforations  133 . Thus, the energy-storing devices  129  are bypassed in the case of large angular displacements and are protected against the possibility of harmful effects from high transient peaks in the torque-flow. In this embodiment, the energy-storing devices of the first, radially exterior damper stage  128   a  are formed in a known manner as arc-shaped springs  129  that are accommodated and retained at their outside radius by a chamber  118   b  formed by the peripheral portion of the input member  118  that is bent into the axial direction towards the turbine  110  and by an additional lateral part  118   a  enclosing the arc-shaped springs on the side facing the turbine  110 . The chamber  118   b  has provisions for applying a force in the longitudinal direction of the springs in the shape of protrusions  118   c  of the input member  118  and the lateral part  118   a,  and wear-protection shells may be interposed between the inside wall at the circumference of the chamber  118   b  and the arc-shaped springs  129 . The intermediate part  127  representing the output member of the first damper stage  128   a  is arranged between the input member  118  and the lateral part  118   a  (relative to the axial direction) and is equipped with a radially arranged extremities  127   a  along its outside perimeter. A further radially extending flange-like part  127   b  is connected to the intermediate part  127  through fasteners such as the rivets  131  shown in the present embodiment. With openings  130   a  formed in a known manner, the flange-like part together with the intermediate part  127  holds the energy-storing devices of the second damper stage  128   b,  in this embodiment represented by short, stiff helix springs  130  distributed evenly along a circle. On the output side, the force introduction into the springs is accomplished with the output member  117  that is interposed in the axial direction between the intermediate part  127  and the flange-like part  127   b  with openings  117   a  corresponding to the dimensions of the helix springs  130  that in the present embodiment consist of sets of helix springs nested inside each other. At its outer perimeter, the output member  117  has extremities  117   b  that are directed outwards in the radial direction and engage openings  127   c  in the flange-like part  127   b  with play, thus allowing the intended range of angular displacement for the second damper stage  128   b  and providing limit stops so that the second damper stage  128   b  will be bypassed when the angular displacement of the extremities  117   b  within the openings  127   c  has reached the limit. 
     By the interposition of energy-storing devices—in this case plate springs  144 ,  145 —the respective input and output members  118 ,  127  of the first damper stage  128   a  and  127 ,  117  of the second damper stage  128   b  are spaced apart from each other, and through appropriate selection of the spring constants of the plate springs  144 ,  145 , it is possible to achieve a desired amount of frictional torque at the friction surfaces  144   a,    145   a.    
     In the present embodiment, the output member  117  and the output element  114  with the interior toothed profile  116  for the torque-transmitting connection to the transmission shaft (not shown) are formed as one integral part. 
     FIG. 3 illustrates an embodiment of a similar torque-transmitting apparatus  201  similar to the torque-transmitting apparatuses  1  and  101  with a housing  202  that also contains a torque converter  203 . The pump  208  and the stator  211  are configured and arranged in the same manner as has been described in the context of FIG.  1 . 
     The turbine  210  is spaced apart from the stator  211  by means of a roller bearing  211   a  and is connected to a hub  210   a  by means of a weld  210   b  made, e.g., by impulse welding. The hub  210   a  is centered on a projection  214   b  of the hub  214  extending axially towards the stator  211 . The hub  214  represents the output element of the torque-transmitting apparatus  201  and has an interior toothed profile  216  for a form-locking engagement with the outward-facing profile of a transmission shaft  272 . For optimum use of space in the axial dimension, the projection  214   b  surrounds the outside of the stationary sleeve  270  that supports the stator  211  through a free-wheeling hub  271 . In the axial direction, the hub  210   a  is held in place on the projection  214   b  by a retaining ring  214   a.  To limit the relative angular displacement between the turbine  210  and the hub  214 , i.e., the working range of the damper  213 , the hub  210   a  has axially directed bolts  273  engaged with the required amount of rotational play in openings  274  of the hub  214 , the latter representing at the same time the output member  217  of the damper  213 . 
     To accommodate the control piston  243  of the lockup clutch  215 , a further hub  275  is slidably supported on the transmission shaft and rotatable relative to the hub  214  by means of a roller bearing  275   a  retaining the hub  275  engaged with the housing  202 . In first axially and then radially outwards directed wall portions  202   a,    202   b  of the housing  202 , axial and radial toothed profiles are, respectively, arranged for a form-locking engagement with complementary toothed profiles  275   b  on the hub  275 . On the axially extending circumference of the hub  275 , a seal  251  is provided for sealing the piston  243 . 
     Located at a farther radius, the piston  243  has ridges  243   a  running in a circle and projecting axially towards the friction-lining carriers  238 . When the piston  243  is displaced in the axial direction, the ridges  243   a  bear against the clutch disks  238   a  and the friction-lining carriers  238  that are faced on both sides with friction linings  242 , resulting in slipping engagement, full engagement, and disengagement of the lockup clutch  215 . The axial displacement of the piston  243  is energized by the application of pressure differentials of a pressure medium entering through a channel (not shown) into the tightly sealed chamber  250  that is formed by the piston  243   a  where the sealing interface between the outer circumference of the piston  243  and the housing  204  is formed by a seal  252 . 
     The clutch disks  238   a  and an additional annular disk  277  that serves as take-up surface against the clutch force are at their exterior circumference engaged by a rotation-blocking toothed profile and secured axially by a retaining ring  276   a  in the exterior disk holder  276  that is welded to the housing  204 . The friction-lining carriers  238  are held at their inside perimeter in the interior disk holder  218   e  by a rotation-blocking toothed profile. Consequently, when there is friction engagement between the clutch disks  238   a  and the friction linings  242 , a torque-locked connection is established between the housing  202  and the interior disk holder  218   e,  whereby the latter imparts the applied torque to the input member  218 . For this purpose, the inner disk holder is shaped as a ring of approximately rectangular cross-sectional profile. The portion of the disk holder that is running in the axial direction towards the housing  204  supports the friction-lining carriers  238 , while the second portion, extending outwards in the radial direction, is attached to a radially directed portion of the input member  218  in a non-rotatable connection by means of fasteners such as the rivets  231  that are arranged along a circle in the illustrated example. 
     As has been described, the input member  218  of the damper  213  takes up the applied torque in the case where the lockup clutch  215  is closed or at least partially engaged. When the lockup clutch  215  is open as well as when it is slipping, the torque (or a portion of the torque when the lockup clutch  215  is slipping) is passed on from the turbine  210  through an axial plug-in connection  278  to the input member  218  in the same manner as was described in the context of FIG. 1, but using the arrangement and functional concept of FIG. 2, where the input member  218  together with the lateral part  218   a  forms a chamber  218   b  to accommodate the arc-shaped springs  229  with the wear-protection shells  218   d  inserted at the contact surfaces. In order to form the axial plug-in connection  278 , the axially directed portion of the input member  218  is extended at the outer circumference towards the turbine in such a manner that its axially directed toothed rim  226  can engage the outward-pointing toothed rim  220  of the radially directed flange-like part  222  that is attached to the turbine. 
     Input member  218  and lateral part  218   a  are connected by means of fasteners represented in the present embodiment by the rivets  231  with spacer bolts  231   a  to hold them at a fixed distance from each other. Arranged in the space extending in the axial direction between input member  218  and lateral part  218   a  is the intermediate part  227  in the shape of a disk-shaped part  227  serving as output member of the first damper stage  228   a  and as input member of the second damper stage  228   b.  The detail configuration of the disk-shaped part  227  is illustrated in a partial view of FIG.  4 . 
     The FIGS. 3 and 4 show a disk-shaped part  227  with radially directed extremities  227   a  arranged at the exterior circumference and serving as force-introduction elements for the arc-shaped springs (FIG.  3 ). Distributed along a circle of smaller radius in the disk-shaped part are elongated openings  233  through which the rivets  231  pass, permitting relative rotation between the input member and the output member of the first damper stage  228   a  within a limited angular range. As soon as the rivets  231  reach the borders of the cutouts  233 , the first damper stage  228   a  is bypassed and the applied torque is transmitted through the contact points between the rivets  231  and the cutouts  233 , whereby the arc-shaped springs are protected against greater amounts of torque and angular displacement. The rest position of the rivets  231  in the illustrated embodiment is not centered within the cutouts  233  (seen in the circumferential direction), meaning that the range of angular displacement is not equal in both directions but is smaller in the “push” direction than in the “pull” direction. In an inventive embodiment not shown in the drawing, the rivets  231  can be in direct contact with the border  233   a  of the elongated openings  233  so that this damper stage is being bypassed immediately in the push direction without an angular displacement, thus providing a damper with one active stage in the push direction and two active stages in the pull direction. Distributed over another yet smaller circle in the disk-shaped part are further openings  227   b  to hold the energy-storing devices in the form of short helix springs  230  nested inside each other (FIG. 3 ). At their radius, the openings  227   b  have flaps  230   a  that are bent towards the lockup clutch  215  to secure the helix springs  230  in the axial direction. By means of the rivets  232  passing through holes  227   c  (FIG. 4) distributed along a circle of intermediate radius between the openings  233 ,  227   b,  the disk-shaped part  227  is connected to a further flange-like part ( 227   b ) that has openings with flaps ( 227   c ) bent axially towards the turbine to accommodate the helix springs  230 . The flange-like part ( 227   c ) is formed into the shape of a cup extending in the axial direction to provide space in the axial dimension between the intermediate part  227  and the flange-like part ( 227   b ) to accommodate the hub  214 . The hub  214  is extended radially into a disk shape to serve as output member  217  of the damper  213  and thus of the second damper stage  228   b.  To provide space for and couple a force to the helix spring  230 , the output member  217  has openings  217   a  distributed along a circle so that the hub  217  is rotatable relative to the intermediate part  227  against the restoring force of the helix springs  230 . This produces the damping effect of the second damper stage  228   b  wherein the range of angular displacement is limited by the play of the bolts  273  in the openings  274 . 
     The input member  218  and the output member  227  of the first damper stage  228   a  as well as the input member  227  and the output member  217  of the second damper stage  228   b  are elastically clamped against each other by the action of the interposed plate springs  244 ,  245 . Thus, with an appropriate selection of the spring characteristic, a friction effect of a desired magnitude can be generated between the respective input and output members  218 ,  227  and  227 ,  217  at the friction surfaces  244   a,    245   a,  where the friction surface  245   a  is provided by a series of projections distributed along a circle on the lateral part  218   a.    
     FIG.5 illustrates an embodiment of a damper  313  in single-stage configuration. The torque to be transmitted is introduced into the damper  313  through the two lateral parts  318   a,    318   b  that form the input member  318 . The contributions to the torque coming from the lockup clutch  315  are introduced into the damper  313  through the toothed rim  321  of the lateral part  318   a  of the input member  318 . The contributions to the torque coming from the turbine  310  are introduced through the inventive plug-in connection  378  into the input member  318 , represented by its lateral part  318   b.  In addition, a disk-shaped part  322  is connected by means of rivets  332  with the turbine  310 , with the hub  314  (that represents the output element and is connected to the transmission shaft  372  through a toothed profile  316 ) and with the output member  317 . The spacer bolts  332   a  are provided to allow an angular displacement of the output member  317  relative to the turbine  310 , hub  314  and lateral part  322  within a range that is delimited by the borders of elongated openings  334 . The disk-shaped part  322  is engaged in a toothed exterior profile  314   a  of the hub  314  without play. At its outer circumference, the disk-shaped part  322  has an exterior toothed rim  326  that forms the play-free plug-in connection  378 . Also engaged in the toothed exterior profile  314   a  of the hub  314  is the output member  317  of the damper  313 , which has a toothed inner perimeter  317   a  with an amount of play between the opposing tooth flanks that determines the range of relative angular displacement between the input member and the output member in opposition to the restoring torque of the energy-storing devices  329 . It should be noted, however, that the openings  334  and the elongated further openings  333  that are located farther out in the radial direction on the output member  317  will permit a larger amount of angular displacement. Nevertheless, it is conceivable in principle that the maximum amount of angular displacement is determined by any one of the three elements  317   a,    333 ,  334 . 
     The energy-storing devices  329  have the shape of arc-shaped springs  329 . The configuration of the chamber  318   c  that accommodates the arc-shaped springs  329  as well as the arrangement and function of the force-introducing elements have been described previously in the context of FIGS. 2 and 3. 
     The lateral parts  318   a,    318   b  are connected in the axial direction by means of rivets  331  and spacer bolts  331   a  and are held at a suitable distance from each other to allow the output member  317  to be arranged within the axial space between them. Interposed between the lateral part  318   a  and the output member  317  is a plate spring whose axial thrust determines the intensity of the frictional engagement between the output member  317  and a circular ridge  318   d  formed on the lateral part  318   b.    
     FIG. 6 illustrates a further embodiment of a two-stage damper  413  of the kind that was described in the context of FIG. 3, except for the following distinguishing features: The turbine  410  is supported in a manner permitting relative rotation directly by the hub  414  that forms the output element; it is centered on a shoulder  414   b  provided for this purpose and secured in the axial direction by a retaining ring. Thus the hub  210   a  shown in FIG. 3 can be omitted. The bolts  473  delimiting the maximum angular displacement between output member  417  and output member  418  are distributed along a circle and configured to protrude directly from the hub  414  into the axial direction, engaging the input member  418  through elongated openings  474  that provide the limiting stops. For the form-locking engagement with the lockup clutch (not shown), a ring  418   e  of rectangular profile is attached to the input member  418  by means of rivets ( 231 ) that are arranged along a circle. The radially directed portion of the ring  418   e  is riveted to the input member  418 , while the axially directed portion provides the form-locking engagement with the lockup clutch by means of an axially directed profile. 
     FIG. 7 illustrates a further inventive embodiment of a torque-transmitting apparatus  501  with a single-stage damper  513  and a modified lockup clutch  515 . 
     The control piston  543  of the lockup clutch  515 , which is axially displaceable, sealed and centered on the transmission shaft  572 , carries a friction lining  542  along its radially exterior peripheral area on the side that is facing the friction surface  504   a  on the housing  504 . When the clutch is closed or slipping, the friction lining  542  is frictionally engaged with the friction surface  504   a  of the housing  504  and thereby introduces the torque to the input member  518  consisting of lateral parts  518   a  and  518   b.    
     At a point between the housing  504  and the piston  543 , converter fluid is suctioned off through an outlet channel (not shown), whereby an under pressure is generated relative to the converter chamber  512 , resulting in an axial displacement of the piston  543 , thus providing the capability of controlling the slipping engagement, closing and opening of the lockup clutch  515 . The friction engagement between the friction surface  504   a  and the friction linings  542  can be controlled so that the lockup clutch  515  slips while the friction linings  542  are being cooled by the passing flow of the converter medium. However, it is also possible to engage the lockup clutch without slippage. The friction surface  504   a  and the control piston  543  are cone-shaped in the vicinity of the friction engagement, so that the closure and friction engagement of the lockup clutch are enhanced by the effect of the centrifugal force. 
     In a circular area of smaller radius than the friction linings  542 , the piston  543  has protuberances  543   a  projecting in the axial direction towards the input member  518  where the piston  543  is connected to the lateral parts  518   a  and  518   b  by means of bolts  543   b  in a manner permitting axial but blocking rotational movement of the piston in relation to the input member  518 . The two lateral parts  518   a,    518   b  are riveted together at their outer circumference (rivets not shown) , while the bolts  543   b  are inserted into cutouts  518   c  on the lateral parts  518   a,    518   b  that are open at the outer perimeter and thereby permit an axial play between the piston  543  and the input member  518 . The purpose is to prevent negative effects on the axial mobility of the piston  543  from stresses that occur during the engagement and disengagement of the lockup clutch between the piston  543  and the already torque-loaded input member  518 . 
     The torque introduction through the turbine  510  occurs by means of a turbine hub  510   a  that is centered on the hub  514  representing the output element. The turbine hub  510   a  is fixedly attached to the turbine  510  and has axially directed projections  573  distributed along its outer perimeter that are engaged without play—in order to avoid a one-sided introduction of torque—in openings of both lateral parts  518   a,    518 , thereby forming the inventive plug-in connection  578  between the turbine  510  and the input member  518 . 
     The disk-shaped output member  517  that is formed out of the hub  514 , together with the input member  518  and the energy-storing devices in the form of nested helix springs  530 , represent an essentially known damper device  513 . A series of openings ( 574 ) is distributed along a circle on the output member  517 . The projections  573  of the turbine hub  510   a  pass through the openings ( 574 ) and stop the relative angular displacement between the input and output members  518 ,  517  against the restoring torque of the energy-storing devices  530  as soon as the projections  573  run against the borders of the openings ( 574 ). 
     FIG. 8 illustrates a further possible configuration of a damper device  613  of the inventive torque-transmitting apparatus. In contrast to the damper devices described above, the hub  614  is composed off two hub components  614   a,    614   b.  The hub component  614   a  is mounted on the transmission shaft  672  in play-free and rotation-blocking connection. The hub component  614   b  is supported and aligned on a shoulder  614   d  arranged axially on the hub component  614   a  on the side towards the transmission. The hub component  614   b  is secured axially by means of a retaining ring  614   c.  The turbine  610  is firmly connected with the hub component  614   b,  e.g., by welding or keying. To form a meshing engagement with play between the first and second hub components  614   a,    614   b,  the second hub component  614   b  has axially directed projections  673  distributed along its circumference, which engage openings  674  of the hub component  614   a.  The dimension of the openings  674  in the circumferential direction is such that the projections  673  in concert with the openings  674  permit a desired amount of relative angular displacement between the turbine  610  and the hub component  614   a,  with the damper  613  being interposed between them. The output member  617  of the damper device  613  is arranged axially between the two hub components  614   a,    614   b,  centered on the hub component  614   a  and rotationally tied to it by means of the eyed connection  614   e.  The output member  617  rests against the hub component  614   a  along a series of projections distributed on a circle or a circular ridge  614   f  protruding in the axial direction. At locations that correspond to the openings  674 , the flange-like output member  617  of the damper device  613  has openings  675  that are engaged by the projections  673  of the hub component  614   b.  It is advantageous if the openings  675  are wider in the circumferential direction than the openings  674 , so that the limits of angular play are determined by the openings  674 . This prevents the torque from entering the hub component  614   a  through the keyed connection  614   e,  so that the latter does not have to be dimensioned for the torque loads that would occur in that case. The function of the further components of the damper device  613  is otherwise comparable with the other damper devices that have been described above. 
     The FIGS. 9-12 show partial sectional views of embodiments of dampers  713   a-d  that are similar to the damper  213  of FIG.  3 . The dampers  713   a-d  differ from the damper  213  and in part among each other in the different configuration of the input member  718   a-d  and the output member  717 . 
     In contrast to the hub  214  and the output member  217  being configured together as one piece as in FIG. 3, the dampers  713   a-d  of FIGS. 9-12 have output members  717  and hubs  714  in a two-piece configuration, in which the output members  717  are sheet metal stampings attached to and centered on the hub  714  in a rotation-blocking connection, e.g., by shrink-fitting. To accommodate the energy-storing devices of the second damper stage, the disk-shaped output members  717  have window-shaped openings  717   a  distributed along a circle. The disk-shaped output members  717  limit the angular displacement of the second damper stage by means of radially directed extremities  717   b  distributed along the circumference, which are engaged with the required amount of angular play in corresponding openings of the disk-shaped part  727   b  that serves as input member of the second damper stage. 
     In the dampers  713   a,    713   c  of the FIGS. 9 and 11, respectively, the input members  718   a,    718   c  of the damper that transmit an applied torque from the converter lockup clutch  715  and/or from the turbine  710  to the damper  713   a,    713   c  are of single-piece configuration, i.e., they have at their inner circumference an axially directed extension  778   a,    778   c  with a profile  780   a,    780   b  for a rotation-blocking engagement of the disks  742   a,    742   b.  The profile  780   a  (FIG. 9) is impressed into the exterior circumference of the extension  778   a,  while the profile  780   c  (FIG. 11) is formed by axially oriented openings distributed over the circumference of the extension  778   c  for a rotation-blocking engagement of the correspondingly profiled disks  742   b.    
     The dampers  713   b,    713   d  of FIGS. 10,  12  have an input member  718   b,    718   d  firmly connected, preferably riveted as shown here, to the flange-like part  778   b,    778   d  of L-shaped cross-section. The flange-like parts  778   b,    778   d  have profiles  780   b,    780   d  corresponding to the extensions  778   a,    778   c  of FIGS. 9,  11  for a rotation-blocking connection with the disks  742   a,    742   b  of the converter lockup clutch  715 . 
     FIG. 13 represents a cross-sectional view of an embodiment of a torque-transmitting apparatus  801 . Its damper  813 , shown here in a two-stage configuration working in serial mode, is at its outer perimeter solidly connected and thereby axially constrained to the turbine  810 . At its inner perimeter, the damper  813  has an axially displaceable but non-rotatable connection to the hub  814 . 
     The damper  813  is attached to the turbine shell  823  by means of a weld seam or spot welds  822   a  using essentially known welding methods such as, e.g., induction welding, laser welding, impulse welding, or other suitable welding methods. It is to be understood that any other fastening method such as riveting, as well as self-locking connections, could also be used advantageously. In the illustrated embodiment, a connector flange  822 —or alternatively an arrangement of connector lugs in the shape of circular segments distributed over a circumference —is attached, e.g., welded, to the turbine shell  823 . The axially directed extension  820  of the input member  819  is slipped over the connector flange  822  or the connector lugs and then attached as described above. It can be advantageous if in the attachment process the connector flange  822  is centered on the turbine and the input member  819  is centered on the connector flange. 
     Additionally or alternatively, it can be of advantage if the second damper stage is centered on the first damper stage in order to prevent displacement of the two damper stages relative to each other. Thus it is possible to accomplish the centering through a configuration in the area  888  where a component  818   a  of the input member of the first damper stage overlaps radially with a component  827   b  of the output member of the first damper stage (which is also the input member of the second damper stage), allowing the two damper stages to be positioned relative to each other. 
     The output member  817  of the damper  813  is connected to the hub  814  through an inward-facing toothed profile that engages an exterior toothed profile of the hub  814 , allowing axial but preventing angular relative displacement, so that stresses between the outer attachment  822   a  and the interior connection of the damper  813  are prevented. 
     The turbine  810  is supported through a turbine hub  873  on an axially projecting shoulder  814   b  of the hub  814 . The turbine hub  873  has limited rotational play relative to the hub  14  and is axially secured by a retaining ring  814   c.  The angular displacement of the turbine  810  relative to the hub  814 , i.e., the working range of the damper  813 , is limited by axially directed projections  873   a  distributed along a circle on the turbine hub  873  that are engaged with angular play in the exterior toothed profile  814   a  of the hub  814 . It is to be understood that the toothed interior rim  817   a  of the output member  817  and the projections  873   a  of the turbine hub  873  do not have to be arranged side by side as shown in FIG. 13 but may instead be one above the other for the benefit of minimizing the overall axial dimensions, in which case it is advantageous if the projections  873   a  are arranged inside the radius of the toothed rim  817   a.    
     FIG. 14 illustrates a damper  913  that has been modified in comparison to the damper  813  of FIG. 3 in that the disk-shaped input member  927   b  of the second damper stage is shaped at its interior periphery in such a manner that by means of an axially directed extension  927   c,  the damper  913  can be centered on the exterior toothed profile  914   a  of the hub  914 . By means of the centering feature  988 , the first damper stage  928   a  can be centered on the second damper stage  928   b.  The axially and rotationally fixed connection of the input member  918  to the turbine shell (not shown) can thus be made with a tighter tolerance, e.g., according to the embodiment of FIG.  15 . 
     An alternative to the solution shown in FIG. 13 for attaching the damper  813  to the turbine shell  823  by means of a connector flange  822  is illustrated in the detail view of FIG.  15 . The rim  920   a  of the axially directed extension  920  of the input member  918  of the damper is adapted to the shape of the turbine shell  923  of the turbine  9 l 0  and attached along a circle by the continuous weld seam or individual spot welds  922   a.    
     FIG. 16 shows a partial section of a further embodiment of a torque-transmitting apparatus device  1001  that is similar to the embodiment of FIG.  13 . Modifications that deviate from the embodiment of FIG. 13 are in the hub area, including a hub  1014  that is also shown in the detail view of FIG.  17 . 
     As may be seen in FIGS. 16 and 17, the two form-locking connections for the transmission of the torque from the damper  1013  through its output member  1017 , and from the turbine  1010  through the turbine hub  1073 , to the hub  1014  and from there through the toothed-profile connection  1016  to the transmission shaft are spatially separated from each other. At its exterior circumference, the hub  1014  has an outward-facing profile, such as the illustrated toothed rim  1014   a,  that meets the complementary interior profile  1017   a  of the output member  1017  in a form-fitting engagement that is preferably free of play and permits axial displacement. Inside of the toothed rim of the hub  1014  are window-shaped openings  1014   b  distributed along a circle, shown here in an arrangement of four, but arrangements of two or six openings may also be advantageous. The axially directed projections  1073   a  of the turbine hub  1073  pass through the window-shaped openings  1014   b  and establish a positive engagement with a maximum play angle a-b (amounting to, e.g., 10° to 70° in the case where four openings are used), between the hub  1014  and the turbine hub  1073  that is rotatable and axially constrained on the hub  1014 , whereby the maximum angular working range a-b of the damper  1013  is being determined in an advantageous manner. For reasons of structural integrity, the openings  1014   b  are widened and rounded in both radial directions in the vicinity  1014   c  of the contact areas for the projections  1073   a.  The toothed rim profile  1014   a  is interrupted in the circumference segments  1014   d  adjacent to the radial enlargements  1014   c.    
     The axial fixation of the damper  1013  is modified slightly in comparison to the embodiment  801  of FIG. 13 in that, unlike the connector flange  822  of FIG. 13, the connector flange  1022  is not fitted to the radial share of the turbine shell  1023  and then continued in an outward radial direction. Rather, the connector flange  1022  has a planar, radially outward-directed shape with a taper  1022   b  at the contact surface to the turbine shell  1023  and is connected to the latter preferably at its inner perimeter through weld seams or a string of evenly distributed spot welds  1022   c,    1022   d.  The connection  1022   a  between the connector flange  1022  and the input member  1018  of the damper  1013  is made in the same manner as in the embodiment  801  shown in FIG.  13 . 
     The function of the damper  1013 , likewise, is similar to the dampers  213 ,  813  of the FIGS. 3 and 13, respectively, where it should be noted that the dampers shown in the illustrated sample embodiments are serially configured two-stage dampers. However, in applying the invention it may also be of advantage to provide a parallel mode of operation for dampers with two or more stages. It may further be beneficial, to provide individual limits for the angular displacement of each damper stage, as in the present case for the damper stages  1013   a,    1013   b,  in addition to the delimitation of the relative angular displacement of the entire damper  1013  by means of the projections  1073   a  in combination with the openings  1014   b.  For this purpose, the first damper stage  1013   a  as well as its output member  1077  have window-shaped openings  1033  distributed along a circle that are engaged with angular play by the rivet bolts  1031  that connect the two input members  1018 ,  1018   a.  In case of a rotation of the input members  1018 ,  1018   a  relative to the output member  1077  of the first damper stage  1013   a,  when the range of play has been used up, the rivet bolts will act as stops and thereby cause the damper stage  1013   a  to be bypassed. 
     In analogous manner, the rivet bolts  1032  connecting the input member  1077  of the second damper stage  1013   b  (which also represents the output member of the first damper stage  1013   a ) with the disk-shaped part  1078  restrict the angular displacement of the second damper stage  1013   b  as they perform the function of rotation-limiting stops for the radially directed extremities  1017   e  on the circumference of the output member  1017 , whereby the range of relative rotation between the input members  1077 ,  1078  and the output member  1017  is determined by the amount of play between the river bolts  1032  and the extremities  1017   e.  Preferably, the ranges between stops for the first and second damper stages  1013   a    1013   b  as well as for the entire damper are coordinated in such a manner that the individual damper stages  1013   a,    1013   b  reach their stops at a point before the limit angle of the entire damper has been attained by the projections  1073   a  reaching the end of their play. For specific applications is may further be advantageous if the first damper stage is stopped before the second stage or vice versa. 
     It must be understood that features and functions described for individual embodiments of the torque-transmitting apparatus can also be advantageously applied in the rest of the embodiments, regardless of whether or not they are being shown, even it these features and functions have not been described in detail in the context of the respective embodiment and that, therefore, such features and functions are considered to be included in the coverage of all embodiments to which they are applicable. 
     Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can, by applying current knowledge, readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic and specific aspects of the aforedescribed contribution to the art and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the appended claims.