Abstract:
A torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle, comprising: a spring support and a force transmission flange configured rotatable relative to the spring support, wherein at least one compression spring is provided between the spring support and the force transmission flange for transferring a mechanical torque, wherein a housing of the spring support is configured so that in a radial direction of the torsion vibration damper, at least one longitudinal end of the compression spring is supported at/in the spring support housing and/or a clearance remains between windings of a center section of the compression spring and a wall of the spring support.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This patent claims priority from German Patent Application No. 10 2011 009 254.4, filed Jan. 24, 2011, which application is incorporated herein by reference in its entirety. 
     FIELD OF THE INVENTION 
     The present invention relates to a torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle. Furthermore the invention relates to a damping device or a torque transmission device, e.g., a torque converter, a clutch, a clutch assembly, a damper, a torsion vibration damper, a turbine damper, a pump damper, a dual mass converter or a dual mass fly wheel or combinations thereof, optionally with a centrifugal force pendulum, wherein the damping device or the torque transmission device includes a torsion vibration damper. 
     BACKGROUND OF THE INVENTION 
     In torsion vibration dampers with straight compression springs the compression springs are radially and axially supported by two side discs configured with lugs (cf. also FIG 1). For supporting centrifugal forces and for transmitting a mechanical torque the side discs have to be axially connected with one another through fasteners, e.g., rivets. In the prior art the connection is radially applied outside the straight compression springs in order to implement a good mechanical connection of the components and sufficient durability. A torsion vibration damper of this type requires large radial space, wherein a damping capacity is reduced due to comparatively small straight compression springs. On the one side the axial connection itself on the other side the necessary edge distances (fabrication, stamping) and clearances require additional radial installation space which either has a disadvantageous effect upon the diameter of the straight compression spring and/or their effective radius which causes a reduced damping rate and thus reduced mechanical vibration insulation. 
     In torsion vibration dampers with arcuate compression springs, so called bow springs, the bow springs are radially and also axially supported by a sheet metal component configured as a spring channel, also designated as a spring retainer. In this spring channel spring stops for introducing mechanical torques are applied or integrally formed. A reaction of the torques to a transmission is performed through a flange component which receives the mechanical torque from the bow springs typically through externally arranged lugs, wherein the bow springs can move relative to the respective lugs in a radial and also in an axial direction. When a configuration of a torsion vibration damper of this type configured as a bow spring damper shall be friction optimized it is necessary to relieve the bow springs between the respective longitudinal ends in the radial and also in the axial direction in order to provide windings without friction. This is achieved through an externally closed flange, wherein at least a double sheet metal thickness (flange) is required for additional radial installation space. When engaging the bow spring with a so-called nose flange end caps are required for correctly supporting the bow springs and for a low wear transfer of the bow springs. 
     BRIEF SUMMARY OF THE INVENTION 
     The invention relates to a torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle, comprising: a spring support and a force transmission flange configured rotatable relative to the spring support, wherein at least one compression spring is provided between the spring support and the force transmission flange for transferring a mechanical torque, wherein a housing of the spring support is configured so that in a radial direction of the torsion vibration damper at least one longitudinal end of the compression spring is supported at/in the spring support housing and/or a clearance remains between windings of a center section of the compression spring and a wall of the spring support. The invention also relates to a torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle, comprising: a spring support and a force transmission flange configured rotatable relative to the spring support, wherein at least one compression spring preferably configured as a bow spring is provided between the spring support and the force transmission flange for transferring a mechanical torque, wherein through a flange hook of the force transmission flange at least one longitudinal end of the compression spring is supported and/or supportable in the spring support housing, so that at least the respective longitudinal end of the compression spring is offset in a radial direction of the torsion vibration damper from the wall of the spring support. 
     Thus, it is an object of the invention to provide an improved torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle. Furthermore, it is an object of the invention to provide an improved damper device and/or an improved torque transmission device with an improved torsion vibration damper, in particular for a drive train of a motor vehicle. Thus, in torsion vibration dampers with straight or arcuate compression springs a radial installation space shall be used in a better manner. Furthermore spring properties of a straight or arcuate compression spring shall be improved over the prior art, in particular mechanical friction between the straight or arcuate compression spring and a spring support shall be improved. Furthermore the torsion vibration damper according to the invention shall have little radial and axial installation space and good mechanical durability. Furthermore it shall be provided for embodiments of the invention to be able to omit end caps at the arcuate compression springs. 
     The object of the invention is achieved through a torsion vibration damper for a drive train of a motor vehicle, in particular a drive train of a hybrid vehicle and through a damping device or torque transmission device like, e.g., a torque converter, a clutch, a clutch assembly, a damper, a torsion vibration damper, a turbine damper, a pump damper, a dual mass converter or a dual mass fly wheel or combinations thereof, optionally with a centrifugal force pendulum. 
     The torsion vibration damper includes a spring support, also designated a retainer, and a force transmission flange rotatably provided relative to the spring support, wherein at least one straight or arcuate compression spring is provided between the spring support and the force transmission flange for transmitting a mechanical torque. A housing of the spring support according to the invention is configured so that at least one longitudinal end of the compression spring is supported in the radial direction of the torsion vibration damper at/in the spring support housing and/or a free space is provided between windings of a center section of the compression spring and a wall of the spring support. Furthermore, a force transmission flange according to the invention includes a flange hook, wherein a longitudinal end of the compression spring is supported or supportable in the spring support housing through the flange hook so that at least the respective longitudinal end of the compression spring is offset from the wall of the spring support in a radial direction of the torsion vibration damper. 
     In embodiments of the invention the respective longitudinal end of the compression spring is partially enveloped by the spring support housing in a circumferential direction, wherein the spring support housing for enveloping the compression spring includes an inward oriented protrusion, in particular an embossing at which the respective longitudinal end of the compression spring contacts or is contactable. The protrusion or the embossing is provided in a radial outer portion of the spring support housing so that it extends inwardly in the spring support housing for which preferably a respective section of the wall of the spring support housing is bent inwardly into the spring support housing. The spring support housing or the compression spring is preferably configured so that the clearance between the windings of the center section of the compression spring and the respective wall of the spring support remote from the protrusion or the embossing is maintained at least for slow speeds of the torsion vibration damper. The spring support or the retainer thus includes a section with increased height in the respective portions of the center sections of the compression springs which leads to a reduction of the friction between the compression spring and the spring support. Furthermore the force transmission flange or its flange hook includes devices which support the respective longitudinal ends of the bow springs in axial and radial directions up to a certain extent. 
     In a first embodiment of the invention the compression spring is a straight compression spring. Thus, the spring support housing includes a u-shaped ring channel in which the straight compression spring is partially received in the radial direction and in the axial direction of the torsion vibration damper. For a support and an actuation of the respective straight compression spring that is caused by the spring support housing an actuation hook is provided in the u-shaped ring channel, wherein a respective longitudinal end of the straight compression spring contacts the actuation hook or is contactable through the actuation hook. The actuation hook is preferably provided at a support device that is configured as a support ring, in particular wherein the support device is fixated in the spring support housing. Thus, the actuation hook of the support device extends into the u-shaped ring channel. Through using a spring channel or the u-shaped ring channel in a spring support or a retainer of a spring damper with straight compression springs it is possible to implement a good spring rate for a small radial and axial installation space. Thus, cost effective straight compression springs can be used which have low friction with the support and furthermore have a stable support in the spring support. Furthermore, the number of components is reduced over the prior art which generates additional cost savings. 
     In embodiments of the invention the actuation hook preferably includes actuation edges or surfaces that are substantially offset parallel from one another, through which the respective longitudinal end of the straight compression spring is supportable and/or actuatable in a radially outer and a radially inner portion in the circumferential direction of the torsion vibration damper. The actuation edges or surfaces of the actuation hook that are offset from one another are preferably arranged relative to one another so that they define a plane which is parallel to a plane which is defined by two actuation edges or surfaces which are directly adjacent to one another and which are associated with a second actuation hook of the spring support housing. Preferably a flange hook of the force transmission flange is actuatable by the straight compression spring, wherein the flange hook is preferably arranged substantially centrally relative to the face of the straight compression spring, wherein for a torsion vibration damper that is not operational the respective flange hook is preferably arranged substantially parallel to an actuation hook. An actuation edge or surface of the respective flange hook that is engageable by the straight compression spring it thus preferably arranged in an identical plane with the engagement edges or surfaces of the engagement hook offset from one another. Furthermore the compression spring can be hooked up through a lug at the flange or at the engagement hook and can thus be radially fixated. 
     Preferably the flange hook of the force transmission flange and a longitudinal end or a longitudinal end section of the compression spring are configured corresponding to one another, so that the flange hook supports the longitudinal end of the compression spring in one radial outward direction. Thus, the longitudinal end of the compression spring that moves away from the respective actuation hook in the circumferential direction is at least prevented from a radial movement in an outward direction so that the longitudinal end does not come in contact with an inner wall of the spring housing and does not create any undesirable mechanical friction. In preferred embodiments of the invention the flange hook engages the compression spring or an end cap of the compression spring through an engagement pinion. Furthermore the engagement hook can radially reach over a protrusion at the compression spring or the end cap of the compression spring at least on the radial outside. This can certainly be also kinematically inverted. 
     In a second embodiment of the invention the torsion vibration damper is configured so that the respective flange hook of the force transmission flange has a configuration in the portion where it is actuated by the compression spring, so that the respective longitudinal end of the compression spring is supported in the radial direction and possibly also in the axial direction towards the outside. For this purpose the flange hook is preferably provided at a support device which is in particular provided as a support ring. The respective flange hook can at least include a catch lug extending there from essentially in circumferential or tangential directions of the force transmission flange, wherein the catch lug reaches over the respective compression spring at least at its longitudinal end. An over reaching of the compression spring through the catch lug is preferably provided axially offset with respect to the center of the cross section of the compression spring. Furthermore, preferably two catch lugs are provided which are arranged offset with respect to the center of the cross section of the compression spring. Thus, two catch lugs that are oriented towards each other of two directly adjacent flange hooks can be connected with one another, e.g., in an integral manner, wherein a connection portion of the two flange lugs is preferably configured so that it is lifted off from the compression spring. 
     The radial and possibly also axial catching or securing of the arcuate compression spring according to the invention is facilitated without or with only very small additional installation space requirement. 
     The raised arcuate compression spring provides a reduction of the mechanical friction in the entire system. According to the invention end caps at the arcuate compression springs can be omitted in this embodiment since the arcuate compression springs are supported or retained at their longitudinal ends at their outer diameter. Through the radial and possibly also axial support of the arcuate springs through catch lugs integrally formed at the force transmission flange according to the invention it is possible to substantially reduce mechanical friction in a spring support or a retainer damper without requiring additional radial installation space or only requiring very little radial installation space. 
     In embodiments of the invention the respective flange hook includes an indentation or a protrusion at a radially outer portion of the flange hook so that an actuation edge or surface of the flange hook is oriented towards a center of a compression spring. The actuation edge or surface of the flange hook for engaging the compression spring is configured so that the actuation edge or the actuation surface preferably partially approximately follows a contour of the compression spring, wherein the actuation edge or surface is substantially u-shaped with a short arm. For a support and/or an actuation of the compression spring that is provided by the spring support housing preferably an actuation hook is provided at which a respective longitudinal edge of the compression spring contacts or is contactable. The actuation hook is preferably provided at a support device in particular configured as a support ring, wherein the support device is fixated in the spring support housing, wherein the actuation hook is provided radially offset relative to the flange hook and preferably engages the flange hook. The respective actuation hook of the spring support housing can be arranged so that it actuates or supports the compression axially on both sides symmetrically and radially outside of a center of the compression spring, wherein the compression spring can include an outer spring and an inner spring thus forms a compression spring assembly. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention is subsequently described in more detail based on embodiments with reference to the appended drawing figures, wherein: 
         FIG. 1  illustrates a radially tall prior art torsion vibration damper with five straight compression springs or compression spring assemblies; 
         FIG. 2  is a partial cross-sectional view of a first variant of the torsion vibration damper according to the invention with straight compression springs; 
         FIG. 3  is a partial cross-sectional view of a first variant of the torsion vibration damper according to the invention with straight compression springs; 
         FIG. 4  is a perspective view of a first variant of the torsion vibration damper according to the invention with straight compression springs; 
         FIG. 5  is a detail of  FIG. 4 ; 
         FIG. 6  is a detail of  FIG. 4  showing the housing, coil spring, support ring, and flange hook in  FIG. 4 ; 
         FIG. 7  is a detail of the hub flange in  FIG. 4 ; 
         FIG. 8  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 9  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 10  is a perspective view of the second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 11  is a perspective view of the second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 12  is an exploded view of the second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 13  is a detail of the hub flange; 
         FIG. 14  is a front view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 15  is a detail of the flange hook, lug, and coil spring of  FIG. 11 ; 
         FIG. 16  is a detail of the hub flange, lug, flange hook, and coil spring of  FIG. 11 ; 
         FIG. 17  is a detail of the hub flange, lug, flange hook, and coil spring of  FIG. 11 ; 
         FIG. 18  is a detail of the end cap of  FIG. 11 ; 
         FIG. 19  is a detail of the coil spring and end cap of  FIG. 11 ; 
         FIG. 20  is a detail of the hub flange, lug, flange hook, and coil spring of  FIG. 11 ; 
         FIG. 21  is a detail of the hub flange, lug, flange hook, and coil spring of  FIG. 11 ; 
         FIG. 22  is a detail of the hub flange of  FIG. 11 ; 
         FIG. 23  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 24  is a detail of  FIG. 23 ; 
         FIG. 25  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 26  is a detail of the hub flange in  FIG. 25 ; 
         FIG. 27  is a detail of the spring retainer, support ring, hub flange, and coil of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 28  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 29  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 30  is a detail of an engagement pin; 
         FIG. 31  is a detail of a coil spring; 
         FIG. 32  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 33  is a detail of an engagement pin; 
         FIG. 34  is a detail of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 35  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 36  is a detail of an additional hook; 
         FIG. 37  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; 
         FIG. 38  is a detail of  FIG. 37 ; 
         FIG. 39  is a detail of a hub flange; 
         FIG. 40  is a partial cross-sectional view of a second variant of the torsion vibration damper according to the invention with arcuate compression springs; and 
         FIG. 41  is a detail of  FIG. 40 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       FIGS. 2 through 7  illustrate the first variant of the invention, wherein the torsion vibration damper  1  according to the invention includes five straight compression spring arrangements  30  which respectively include an outer spring  32  and an inner spring  34 . Certainly also individual springs or parallel springs with a single stage or multiple stages can be used also in other quantities. The compression springs  30  are received in a spring support housing  12  of a spring support  10  or a spring receiver  10  which can also be designated as spring support ring  10  or a spring retainer  10 , wherein the spring support housing  12  includes a ring channel  130  which is approximately u-shaped in sections (see  FIGS. 2 and 3 ). Thus the longitudinal extensions of the compression springs  30  are arranged like in an even polygon and enveloped by the circular ring channel  130  (see in particular  FIG. 4 ) wherein the compression springs  30  are at least partially supported in radial and axial directions. Together with the spring support housing  12  a support device  14  is provided which is, in particular, configured as a support ring  14 , wherein the support device offsets the compression springs  30  from one another through actuation hooks  142 . For this purpose the approximately plate shaped spring support housing  12  (see  FIG. 4 ) is fixated in an inner portion with the approximately star or disc shaped support device  14 , in particular riveted together, wherein the actuation hooks  142  radially extends into the u-shaped ring channel  130  (see  FIG. 2 ). The spring support  10  is mechanically connectable, e.g., with a shaft of clutch (left side in  FIG. 2 ) and a shaft of an electric motor (right side of  FIG. 2 ). Using only one shaft, thus of the clutch or the electric motor or also another configuration is certainly possible. 
     One respective actuation hook  142  of the support device  14  at both its ends respectively supports a longitudinal compression spring  30  in the circumferential direction. For supporting and/or actuating the respective compression spring  30  a respective actuation hook  142  includes a substantially axially extending actuation edge or an actuation surface (see  FIG. 5 ), wherein preferably an individual actuation hook  142  includes two arms per longitudinal end of a compression spring  30 , wherein the arms are preferably integrally connected through a bar which extends essentially in the radial direction. The two arms and the bar are essentially u-shaped in a center cross section, wherein the bar can be arranged in windows of the windows support housing  12  (see  FIG. 2 ) thus the actuation edges or actuation surfaces respectively oriented towards one another of two actuation hooks  142  directly adjacent to one another in the circumferential direction are parallel to one another or the respective actuation edges or actuation surfaces define planes which are arranged parallel to one another. Between these planes the compression springs  30  are arranged. A respective actuation hook  142  is u-shaped in cross section and preferably used for peripherally loading a cross section of a longitudinal end of the compression spring  30  (see  FIG. 2 ); this means the respective cross section of the respective compression spring  30  is force loaded in a radially outer portion and a radially inner portion. 
     In a torsion vibration damper  1  that is idling, a respective flange hook  202  engages the u-shaped engagement hooks  142  wherein the flange hook substantially centrally engages the compression spring  30  in the respective cross section and substantially extends in the axial direction. A respective engagement edge or a respective actuation surface of the flange hook  202  is thus arranged in the plane recited supra. The flange hooks  202  are provided at a force transmission flange  20  or a hub flange  20  preferably integrally provided there within one piece, wherein the hub flange is mountable, e.g., on a hub of a transmission flange or a hub of a transmission shaft through a support device  24  in particular configured as a support ring  24 . Now when the spring support  10  rotates about its rotation axis the actuation hooks  142  transfer the torque of the actuation hooks  142  of the spring support and transfer a centrifugal force through the compression springs  30  to the flange hooks  202  which, in turn, introduce the torque into the force transmission flange  20 . The compression spring  30  is thus received and supported by the respective flange hook  202  in order to minimize mechanical friction in/at the u-shaped ring channel  130  (cf. infra). The compression springs  30  provide an effective vibration insulation between the spring support  10  and the force transmission flange  20 . 
     According to the invention, the spring support housing  12  of the spring support  10 , thus its wall is configured so that in one portion of the respective center sections of the compression springs  30  a sufficient radial clearance  40 , thus a height increase is provided (cf.  FIGS. 3 and 5 ). This reduces a mechanical friction occurring between a radial outside of the compression spring  30  and an inside of a radial outer wall of the spring support housing  12 . In a respective portion of the longitudinal ends of the compression springs  30  the outer wall of the spring support housing  12  is embossed in an inwardly direction, so that the embossing  122  supports the respective longitudinal end of the compression spring  30  and partially envelops it in its circumferential direction. Thus, also, a protrusion  122  can be used. In the circumferential direction inverted from this engagement of the respective longitudinal end of the respective compression spring  30  at the spring support housing  12  the center section of the compression spring joins at least with the radial clearance  40 . It is furthermore preferred that the compression spring  30  essentially in its entire circumferential direction is clear over its center section and this clearance also continues over essentially the entire speed range of the torsion vibration damper  1 . The center sections preferably extend to the longitudinal ends of the respective compression spring  30 . 
     In order for the compression spring  30  during vibration insulation, this means during operation of the torsion vibration damper  1 , not to move in a radially outward direction the compression spring  30  is positively supported in a loaded condition by the respective flange hooks  202  besides its mechanical preload between two actuation hooks  142  of the spring support  10  (cf.  FIGS. 6 and 7 ). This means the respective longitudinal end of the compression spring  30  is at least partially supported by the flange hook  202 . At the opposite longitudinal end the compression spring  30  contacts an actuation hook  142  and at the embossing  122  of the spring support housing  12 . The positive guiding of the longitudinal end of the compression spring  30  moving away from the engagement hook  142  is at least provided in a radially outward direction. Preferably the positive guiding, however, can be established so that the respective longitudinal end of the compression spring  30  can neither move respective to the flange hook  202  in the radial nor in the axial direction of the torsion vibration damper  1 . Thus a degree of freedom can be provided in a radially inverted direction. This means the respective longitudinal end of the compression spring  30  is supported by the flange hook  202  in the circumferential direction. For this purpose the flange hook  202  includes a protrusion  203  in one embodiment, wherein the protrusion can either engage the compression spring  30  (not illustrated in  FIG. 7 , cf  FIGS. 23 and 24  and infra) or it can engage a recess  363  in an end cap of the compression spring  30 . These embodiments can certainly also be used in the subsequently described second variant of the invention. 
     In the first variant of the invention cost effective straight line compression springs  30  can be used which have lower friction or essentially no friction with the inner wall or an inside of an outer wall of the spring support  10 . The torsion vibration damper  1  is easy to assemble, wherein its assembly in sections can also be performed fully automatically. The provided installation space can be fully used in radial and in axial directions. Thus it is possible for the same available installation space to increase the compression spring  30  from a diameter of 23 mm to 32 mm and to increase an effective radius from 60 mm to 76 mm. Thus a total spring rate can be reduced from 60 Nm/° to 30 Nm/° furthermore the configuration of the spring support  10  according to the invention provides good durability for the torsion vibration damper  1 . 
       FIGS. 8 through 17  illustrate a second embodiment of the invention, wherein the torsion vibration damper  1  according to the invention includes three bow compression springs  30  or bow compression spring arrangement  30 , subsequently designated as bow springs  30 , respectively including an outer spring  32  and an inner spring  34 . Certainly, in turn, individual springs or single stage or multi stage parallel springs are useable in a different number. The bow springs  30  are received in a spring support housing  12  of a spring support  10  wherein the spring support housing  12  includes an approximately u-shaped ring channel  130  for this purpose (cf.  FIGS. 8 and 9 ). Thus, the longitudinal extensions of the bow springs  30  are received in the circular ring channel  130 . (cf. in particular  FIG. 14 ) wherein the bow springs  30  are at least partially supported in axial and radial directions. With the spring support housing  12  a support device  14  is provided which is, in particular, configured as a support ring  14  wherein the support device offsets the arch springs  30  from one another through actuation hooks  142 . For this purpose the approximately plate shaped spring support housing  12  is fixated in an internal portion at the approximately star or disc shaped support device  14  (cf.  FIG. 12 ), in particular riveted together, wherein the actuation hooks  142  radially extend into the u-shaped ring channel  130  (cf.  FIG. 8 ). The spring support  10  is, e.g., mechanically connectible with a turbine (on the right side in  FIG. 8  or  9 ). The application of two shafts at the spring support  10  analogous to the variant provided supra, thus, e.g., the variant of a clutch or the variant of a turbine and, e.g., the variant of an electric motor or another configuration are certainly applicable. 
     A respective actuation hook  142  of the support device  14  respectively supports a longitudinal end of a bow spring  30  at both its ends in a circumferential direction. For supporting and/or actuating the respective bow spring  30  a respective actuation hook  142  includes an essentially axially and radially extending engagement edge or an actuation surface (cf.  FIG. 8 ) wherein preferably per longitudinal end of bow spring  30  an individual actuation hook  142  includes an approximately u-shaped configuration with a longer arm. Thus, the cross section of the engagement hook  142  initially extends in the radial direction at a longitudinal end of the bow spring  30  and then curves slightly over a center of the cross section of the bow spring  30  in an axial direction along a cross section of the bow spring  30 . The longer arm of the u-shaped configuration of the cross section of the actuation hook  142  thus extends from an inside of the spring support housing  12  axially in an outward direction. The actuation edges or actuation surfaces respectively oriented towards one another of two actuation hooks  142  directly adjacent to one another in circumferential direction are arranged rotated relative to one another by the amount of angle that is covered by the bow spring in installed condition. 
     The longer arm of the actuation hook  142  engages an approximately u-shaped flange hook  202  for an idling torsion vibration damper  1 , wherein the flange hook is configured to essentially peripherally load the bow spring  30  with a force in the respective cross section, this means for a force loading of the respective bow spring  30  the bow spring engages the respective flange hook  202  with a radially outer and a radially inner portion. The flange hooks  202  are preferably integrally provided in one piece at a force transmission flange  20  or a hub flange  20 , wherein the hub flange is mountable through a support device  24 , in particular, configured as a support ring  24 , e.g., on a hub of a transmission shaft. When the spring support  10  rotates about its rotation axis the actuation hooks  142  of the spring support transfer a force in a circumferential direction through the bow springs  30  onto the flange hooks  202  wherein the flange hooks introduce the torque into the force transmission flange  20 . The bow spring  30  is thus retained and supported by the respective flange hook  202  in order to minimize mechanical friction in/at the u-shaped ring channel  130  (cf. supra). Through the bow spring  30  an effective vibration insulation is provided between the spring support  10  and the force transmission flange  20 . 
     According to the invention the spring support housing  12  of the spring support  10 , thus its wall is configured so that a sufficient radial clearance  40  is provided in a portion of the respective center sections of the bow springs  30 , thus a height increase (cf.  FIGS. 9 ,  15  through  17 ). Thus an occurring mechanical friction between a radial outside of the bow spring  30  and an inside of a radial outer wall of the spring support housing  12  is reduced. In a respective portion of the longitudinal ends of the bow springs  30  the outer wall of the spring house  12  is embossed inward so that the embossing  122  supports the respective longitudinal end of the bow spring  30  or partially envelopes it in a circumferential direction of the bow spring. For this purpose also a protrusion  122  can be used. In a circumferential direction from this engagement of the respective longitudinal end of the respective bow spring  30  on the inside of the spring support housing  12 , the center section of the bow spring is arranged with at least the radial outer clearance  40 . Thus, it is also preferable that the bow spring  30  is clear essentially in its entire circumferential direction over the center section and this clearance also continues essentially over the entire speed range of the torsion vibration damper  1 . The center sections also preferably extend to the longitudinal ends of the respective bow springs  30 . 
     For a respective longitudinal end of the bow spring  30  during vibration insulation, this means during operation of the torsion vibration damper  1 , not to move away in a radially outward direction, the bow spring  30  is positively supported in loaded condition in addition to its mechanical pre-loaded between two actuation hooks  142  between the spring support  10  by respective flange hooks  202  (cf.  FIGS. 16 and 17 ). This means the respective longitudinal end of the bow spring  30  is at least partially supported by the flange hook  202 . At the opposite longitudinal end the bow spring  30  contacts an actuation hook  142  and the embossing  122  of the spring support housing  12 . The positive support of the longitudinal end of the bow spring  30  moving away from the respective actuation hook  142  is at least provided in a radial outward direction. Preferably, the positive support, however, can be established so that the respective longitudinal end of the bow spring  30  is at least partially supported relative to the flange hook  202  also in an axial direction of the torsion vibration damper  1 . Thus, one degree of freedom can be permitted in a radial inner direction. This means the respective longitudinal end of the bow spring  30  is supported by the flange hook  202  in circumferential direction. For this purpose the flange hook  202  in one embodiment includes a catch lug  204  which protrudes from the flange hook in a tangential and/or circumferential direction (cf.  FIG. 16 ). 
     The respective catch lug  204  or the respective catch lugs  204  fixate the respective longitudinal end of the bow spring  30  at least in a radial direction so that the longitudinal end cannot move away in a radial outward direction when the torsion vibration damper  1  rotates, thus, it is preferable that the catch lug  204  reaches over an outer portion of the bow spring  30  wherein the outer portion is remote from a radial outset of the bow spring  30  which furthermore provides a certain amount of axial fixation. Preferably two catch lugs  204  are arranged radially and laterally on the outside at the respective bow spring and fixate the bow spring. Thus two associated catch lugs  204  of two adjacent flange hooks  202  can be connected with one another, in particular integrally made from one piece. Thus, preferably, the connection is raised from an outside of the bow spring  30  (not illustrated in the drawing). In particular, the respective flange hook  202  includes two respective catch lugs  204  at both its circumferential sides (cf.  FIG. 16 ), wherein the catch lugs  204  of a plurality of flange hooks  202  on one side of the force transmission flange  20  are preferably integrally connected to form a ring. Preferably, the respective flange hook  202  includes a formed surface and a protrusion  206  ( FIGS. 8 and 16 ) and a protrusion  206  so that it can contact the cross section of the bow spring  30 , wherein the formed surface  206  or the protrusion  206  preferably reaches up to a longitudinal end of the inner spring  34 . The embodiments can certainly also be implemented for the first variant of the invention describe supra. 
     Thus, the force transmission flange  20  is preferably configured so that it does not provide a radial height increase with respect to the bow spring  30 . This means the flange hooks  202  are arranged so that they do not extend in a radial direction beyond the bow springs  30 . Furthermore, the catch lugs  204  of the flange hooks  202  are arranged laterally offset relative to a center line of the compression springs, so that a radially outer portion is, at the most, at the same height as the radially outer portion of the bow springs  30  ( FIGS. 8 ,  16  and  17 ). By arranging the catch lugs  204  on both sides axially offset relative to the center of the respective bow spring  30  no additional radial installation space is required above the bow springs  30  for the centrifugal force support. By providing the formed surface  206  or the protrusion  206  in/at the flange hook  202 , using end caps  36  can be omitted. The opposite component in the force flow, thus the actuation hook  142  engages the force transmission flange  20  in an axial or a horizontal direction and actuates the outer spring  32  and also the inner spring  34  preferably radially slightly outside the respective spring center. In order to facilitate simple assembly of the bow springs  30  with a large spring rate, it is conceivable to provide the catch lugs  204  only on a tension side, wherein a stiffening of the force transmission flange  20  in the manner recited supra has to be omitted. 
       FIGS. 18 through 20  illustrate the third embodiment like a flange hook  202  of the force transmission flange  20 , the compression spring  30 , thus a straight compression spring  30  (first variant of the invention) or a curved compression spring  30  (bow spring  30 , second variant of the invention, wherein only one bow spring is also illustrated in  FIGS. 21 through 41  and the following also applies to embodiments of the first variant) and an actuation hook  142  of the spring support  10  or of the support device  14  can interact. The flange hook  202  and the actuation hook  142  are configured analogous to  FIG. 1 , wherein the flange hook  202  can horizontally reach over a comparatively broad nose at the end cap  36  of the compression spring  30  which prevents a movement of the respective longitudinal end of the compression spring  30  in a radially outward direction. Thus the flange hook  202  reaches over the nose at the end cap  36  in a radial direction partially in a form locking manner. When the longitudinal end of the compression spring  30  tries to move in a radially outward direction due to a rotation of the torsion rotation damper  1 , the flange hook  202  restricts this movement due to the engagement of the nose at the flange hook  202 . The end cap  36  is thus mounted with a centering flange ( FIG. 18 ) at the inner spring  34  of the compression spring  30  which is preferably used for embodiments with an end cap  36 . Furthermore, the actual end of the compression spring contacts a flat side of the end cap  36  which is opposite to the lug. 
       FIGS. 21 and 22  illustrate a fourth embodiment of the invention which is analogous to the third embodiment, wherein the end cap  36  of the compression spring  30  preferably includes a central conical, cylindrical, or cone shaped protrusion or a lug. Other shapes and positions of the protrusion are certainly also usable. The flange hook  202  of the force transmission flange  20  is configured flat at the respective actuation edge which is configured as a radially folded catch lug, wherein the flange hook  202  starting from this surface includes a recess that is configured corresponding to the protrusion. When the flange hook  202  contacts the end cap  36  of the compression spring  30  the protrusion at the end cap  36  is essentially received in a form locking manner in the blind hole recess of the flange hook  202 . Thus the engagement hook  142  is configured analogous to  FIG. 20 , the flange hook  202  however has a larger actuation surface through which it can contact the end cap  36 . 
     Furthermore,  FIGS. 23 and 24  illustrate the fifth embodiment of the invention wherein the flange hook  202  and the actuation hook  142  are configured analogous to  FIG. 1 . For radially catching the compression spring  30 , the flange hook  202  includes a protrusion  203  extending there from a circumferential and/or tangential direction, or an integrally formed lug which can engage the compression spring  30 , in particular, the inner spring  34 . Thus the shape of the protrusion  203  is partially configured form locking with an inner contour of the inner spring  34 . Lateral edges adjacent to the protrusion  230  when catching the compression spring  30  engage preferably axially opposite portions at the cross section of the outer spring  32  and inner spring  34 . An end cap  36  can be omitted in this embodiment. 
       FIGS. 25 and 26  represent the sixth embodiment of the invention, wherein the flange hook  202  and the actuation hook  142  are configured analogous to  FIGS. 21 and 22 . Contrary to the embodiment illustrated in these figures, the recess of the flange hook  202  is a pass through recess which is, furthermore, open at a radially inner side (slot), so that the protrusion of the end cap  36  of the compression spring  30  has a radial degree of freedom, namely in a radially inverted direction. An actuation surface of the flange hook  202  for the end cap  36  of the compression spring is configured analogous to the fourth embodiment as a folded over catch lug with a flat surface. Thus, a protrusion of the end cap  36  is preferably configured as a short cylindrical pin; other shapes are certainly also usable (cf. supra). 
     Furthermore,  FIGS. 27 and 28  illustrate the seventh embodiment of the invention wherein the flange hook  202  and the actuation hook  142  are configured analogous to  FIG. 2 . And end cap  36  of the compression spring  30  includes a protrusion with a flat free end which can engage the actuation hook  142 . The flange hook  202  when transferring torques from the flange hook  202  to the compression spring  30  reaches over the protrusion of the end cap  30  partially in a form locking manner. Thus, another portion of the flange hook  202  can contact further on the radial inside at the protrusion and also at the end cap  36 . Preferably the protrusion is provided in a radial direction of the torsion vibration damper  1  slightly offset to the outside but otherwise centrally arranged with respect to the longitudinal end of the compression spring  30 . 
       FIGS. 29 and 30  illustrate the eight embodiment of the invention wherein an end cap  36  of the compression spring  30  can be omitted. The flange hook  202  and the actuation hook  142  are, in turn, configured analogous to  FIG. 2 . Furthermore the flange hook  202  includes a so-called engagement pin  22  which is attached through a central protrusion in a recess, in particular a pass through a recess of a horizontal section of the flange hook  202  which can also be designated as “submarine hookup.” When the flange hook  202  transfers a force onto the compression spring  30  a longitudinal end section of the engagement pin  22  protrudes into the compression spring  30 , in particular into the inner spring  34 . Lateral horizontal portions of the flange hook  202  thus preferably contact the outer spring  32  and the inner spring  34 . 
     Furthermore,  FIGS. 31 through 33  illustrate the ninth embodiment of the invention wherein an end cap  36  of the compression spring  30  and an engagement pin  22  are being used. The flange hook  202  and the actuation hook  142  are, in turn, configured analogous to  FIG. 2 . The engagement pin  22  includes a lateral central pass through recess through which the engagement pin is attached on the flange hook  202  which can also be designated as “torpedo engagement”. The end cap  36  includes a pass through recess in which the engagement pin  22  can engage. Preferably, the engagement pin  22  also engages a compression spring  30  or the inner spring  32 . Furthermore, the end cap  36  can have protrusions with flat free ends adjacent to its pass through recess in an axial direction wherein lateral horizontal portions of the flange hook  202  can engage the flat free ends. 
     The tenth embodiment of the invention is illustrated in  FIGS. 34 through 36 , wherein an arrangement of this type is designated as “hinge configuration.” Thus, the flange hook  202  essentially engages an end cap  36  of the compression spring  30  in a vertical or a radial direction wherein the end cap  36  preferably includes a central conical, cylindrical, or cone shaped protrusion or lug. Other forms and positions of the protrusion are certainly also usable. The flange hook  202  is configured at the respective actuation edge as axially folded over catch lug, wherein the actuation edge preferably completely envelopes the protrusion and force is transferred onto the end cap  36 . The actuation hook  142  of the spring support  10  can thus engage a periphery of the end cap  36  in a radial and an axial direction outside of the flange hook  202 . It is furthermore preferred that the spring support housing  12  includes an additional hook  120  which support the end cap  36  at a side opposite to the actuation hook  142 . 
       FIGS. 37 and 38  illustrate the eleventh embodiment of the invention where the actuation hook  142  of the support device  14  is configured analogous to  FIG. 20 , wherein an arrangement of this type can be designate as “hinge configuration” the flange hook  202  of the force transmission flange  20  and the end cap  36  of the compression spring  30  are thus configured analogous to  FIG. 35 , wherein the actuation edge of the flange hook  202  during force transmission onto the end cap  36  only partially envelopes the protrusion. Thus the engagement edge of the flange hook  202  partially envelopes the protrusion on the radial outside thus, in turn, a partial full locking is created. 
     Eventually,  FIGS. 39 through 41  illustrate the twelfth embodiment of the invention which includes a force transmission flange  20  with vertically or radically extending flange hooks  202  wherein the actuation hook  142  is configured analogous to  FIG. 2 . The flange hook  202  includes a protrusion  203  through which the flange hook  202  can engage the end cap  36  of the compression spring  30  wherein the end cap is provided with a recess or a pass through recess. 
     The statements made supra can, respectively, only apply to a circumferential side of the flange hook  202  or of the respective longitudinal end of the compression spring  30  or the bow spring  30 , or also to both circumferential sides of the flange hook  202 , both longitudinal ends of the respective compression spring  30  or the respective bow spring  30 , wherein these can be configured differently as a function of the embodiments of the invention. 
     REFERENCE NUMERALS AND DESIGNATIONS 
     
         
           1  torsion vibration damper 
           10  spring support, spring receiver, spring support ring, spring retainer 
           12  spring support housing 
           14  support device in particular support ring 
           20  force transmission flange, hub flange 
           22  engagement pin 
           24  support device in particular support ring 
           30  compression spring, compression spring assembly, straight compression spring, bow compression spring bow spring, coil spring 
           32  outer compression spring, outer spring, spring 
           34  inner compression spring, inner spring, spring 
           36  end cap, actuation cap 
           40  clearance, clearance between wall of the spring support housing  12  and the compression spring  30 ,  32   
           120  additional hook 
           122  protrusion, embossing 
           130  u-shaped ring channel 
           142  actuation hook 
           202  flange hook 
           203  protrusion 
           204  catch lug, lug 
           206  formed surface, protrusion 
           363  recess, pass through recess