DE102005034049A1 - Torsional vibration damper for vehicles has driving and driven flywheel, between which one or more spiral springs are mounted which are supported by arms with lugs on their outer ends which fit into cups on ends of springs - Google Patents

Abstract

The torsional vibration damper has a driving and a driven flywheel. One or more spiral springs (6a, 6b) are mounted between these. The springs are supported by arms (21) which have lugs (22) on their outer ends. These fit into cups (32) on the ends of the springs.

Description

The The invention relates to a torsional vibration damper with an input part and an output part that opposes the effect of between them effective energy storage to each other are rotatable, wherein the Energy storage at least one substantially in the circumferential direction of the damper arranged compressible coil spring further comprising at least one pivotable in the circumferential direction Lever element is supported by one of the parts, wherein the lever element at least at a relative rotation between the input part and Output part of the coil spring with one of its circumferential ends in such a way support can that it is due to the relative rotation against the this supporting part is pivoted.

Torsionsschwingungsdämpfer the type described above are for example by the DE 4 433 467 A1 and the DE 101 19 878 A1 been proposed. In these applications, state of the art is given, in which the inventive design can be used.

Of the present invention had the object, torsional vibration of the of the type mentioned above the damping properties and to further improve the life of the engine, which in all operating conditions of the internal combustion engine or the motor vehicle better filtration unwanted Torsional vibrations in the drive train and thereby caused disturbing Sounds can be largely avoided. Furthermore, a according to the invention designed torsional vibration damper in a particularly simple and be economical to produce.

According to the invention this is achieved by the fact that the at least one lever element, which cooperates with the end portion of a coil spring, contours having, which provided with at the end of the coil spring mating contours cooperate such that at least one end portion of the coil spring while the circumferential pivoting the lever element against the force acting on this spring section Centrifugal force retained radially or pushed back. So it is the corresponding spring end during the pivoting of the Lever element or due to the pivoting of the lever element radially supported and retained, causing can be avoided that as a result of on the corresponding end section acting centrifugal force creates an undesirable high friction on a radially outer support surface. It is therefore the corresponding spring end or at least areas the end portion of the coil spring against such a support surface retained or lifted radially. This ensures that at least individual End turns of the coil spring virtually without this friction generate over a certain speed range can be deformed.

The Contours of the lever element can be immediate be molded on this or by an additional of this worn Be formed component. Also at the end of a coil spring provided counter contours can be formed directly by the turns of the coil spring or by an additional one Component, which is provided at the corresponding end of the coil spring is considered and, if necessary, in the axial direction of the coil spring, firmly attached to the end. The latter can, for example by a positive connection between the corresponding component and at least one turn of the spring end, as a snap connection can be formed, guaranteed become.

Especially may be appropriate it may be when the lever element by a bending beam like Spring element is formed. Such a bending beam-like spring element can be one piece with another component such as a flange, which to act on the coil spring, be formed.

The Lever element can be pivoted on the input part and / or on the output part of the torsional vibration damper be stored. In such an embodiment, so the Lever element form a separate component. It is useful if an additional one or separate energy storage the pivoting or Verdrehwiderstand for the Apply lever element. The lever element is thus by means of a Energy storage braced so that its support areas for the associated spring end are urged in the direction of this spring end.

In Advantageously, the input part or the output part through a flange-shaped component be formed, which carries the at least one lever element.

By the embodiment of the invention can guaranteed be that the rotation resistance generated by the lever member between input part and output part and between the latter also effective coil spring are operatively connected in series.

The Coil spring can advantageously in the circumferential direction of the torsional vibration damper extend and inside the torsional vibration damper centrifugal force dependent, the Spring action of this coil spring parallel friction generate, whereby the total generated by the coil spring dynamic torsional resistance is speed-dependent. The coil spring or whose turns can itself directly on a helical spring cross-over Support the wall.

But it can also be considered over the length of the coil spring considered individual sliding or Abstützschuhe be provided, which considered the coil spring over its length in places support radially. Regarding the design and arrangement or leadership of such coil springs is on the DE 199 12 970 A1 . DE 199 09 044 A1 . DE 196 03 248 A1 . DE 196 48 342 A1 . DE 102 09 838 A1 and DE 102 41 879 A1 directed.

Especially may be appropriate it should be when the coil spring at least at its with a lever element cooperating end carries an intermediate layer, which the counter contours forms, which cooperate with the contours of the lever element.

Advantageous it may be when the lever member is pivotable such that its retention contours while the pivoting be displaced on a trajectory, the opposite the Rotation axis of the damping device a changing, preferably has decreasing distance. The lever element can be so pivotable or elastically deformable that at a pivoting or deformation of the lever element due a circumferential admission by the helical spring the Abstützkonturen of the lever element be displaced along a trajectory such that their Distance from the axis of rotation of the torsional vibration damper smaller is, whereby the corresponding spring end urged in the direction of the axis of rotation or is pulled. This will ensure that the corresponding end of the coil spring against a radial support surface or supporting wall withdrawn and thus a friction damping is avoided.

The Contours of the lever element can at least by a circumferentially extending nose-shaped Anformung be formed. The counter-contours provided on the associated spring end can through a recess of an intermediate layer provided at this spring end such as B. Beaufschlagungsschuh be formed. It can, however be expedient when the lever member has a corresponding recess or a corresponding Section has and the intermediate layer in a circumferential direction extending Anformung.

Further advantageous structural design features as well as functional Features are explained in more detail in the following description of the figures.

there demonstrate:

1 a section through a vibration damping device,

2 a section according to the line II-II of 1 , wherein some components have not been shown in order to better represent the designed according to the invention spring element,

3 one of the 2 corresponding view, but wherein the spring element or the spring arm is shown in the clamped state,

4 a substantially the 3 corresponding view of an embodiment variant of the invention,

5 a further embodiment variant according to the invention,

6 to 9 a particularly advantageous embodiment of a Beaufschlagungsnapfes or shoe for a coil spring and

10 to 12 a further advantageous embodiment of a Beaufschlagungsnapfes or shoe for a coil spring.

The in the 1 to 3 illustrated vibration damping device 1 includes a torsional vibration damper 2 in the illustrated embodiment between two flywheel elements 3 . 4 is arranged. The two flywheel elements 3 . 4 are about a storage 5 rotatable relative to each other, centrically positioned. The flywheel element 3 For example, is connectable to the output shaft of an internal combustion engine, whereas the flywheel element 4 can be coupled with a transmission input shaft, for example via a on the flywheel element 4 mounted friction clutch.

With regard to the camp training, the basic structure of the individual flywheel elements whose connection with the internal combustion engine and the transmission input shaft and their operation is expressly to DE-OS 39 09 892, DE-OS 41 17 571 and DE-OS 41 17th 579 and the related art cited therein, so that a detailed description in the present application is not required with respect to these points, and thus the related disclosures of the prior art are considered to be integrated into the present application.

The torsional vibration damper 2 includes in the illustrated embodiment, two energy storage formed by coil springs 6 , which are integrally formed here. The energy storage 6 can only be made from a single spring 6a or, as in the 2 and 3 represented by at least one outer spring 6a and at least one in this recorded inner spring 6b consist. Instead of one-piece, circumferentially elongated coil springs 6a . 6b to use, can be used to form energy storage and several series-connected spring elements, as was suggested, for example, by DE-OS 41 28 868 and DE-OS 43 01 311.

When using long coil springs 6a . 6b These may be according to their arrangement in the vibration damping device 1 be pre-curved before installation. How out 1 it can be seen, are the energy storage 6 in an annular or torus-like space 7 taken, which can be filled in an advantageous manner, at least partially with a viscous medium, such as fat. The space 7 is mainly due to two housing parts 8th . 9 formed, which produced in the illustrated embodiment as sheet metal parts and at least with respect to the coil springs 6a are formed shell-like. In the illustrated embodiment, the housing parts 8th . 9 by means of a weld joint extending over the entire circumference 10 tightly connected.

The annular or toroidal space 7 is - viewed in the circumferential direction - divided into individual images in which the energy storage 6 are included. The individual images are - viewed in the circumferential direction - separated from each other by loading areas 11 . 12 , which in the illustrated embodiment by in the formed as sheet metal parts housing parts 8th . 9 introduced formations, for example, pocket-shaped embossments are formed. The with the second flywheel element 4 associated admission areas 13 for the energy storage 6 are of a scheibenbeziehungsweise ring-like component 14 worn here radially inward via riveted joints 15 with the second flywheel element 4 connected is. The admission areas 13 are through on the outer contour of the disc-like component 14 molded radial arm or arms formed. The poor 13 are in not claimed vibration damping device 1 axially between the axially opposed loading areas 11 . 12 of the first flywheel element 3 arranged.

In a relative rotation between the two flywheel elements 3 . 4 in thrust or pulling direction are the energy storage 6 between the areas of activity interacting with them 11 . 12 . 13 at least after a certain angle of rotation from the in 2 shown rest position or neutral position of the torsional vibration damper 2 compressed. At least one energy storage 6 is in train operation at one end by the arms 13 acted upon or supported, wherein the other end of the energy storage 6 through the admission areas 11 . 12 is claimed. Train operation means that the engine outputs a drive torque for the motor vehicle, that is, the motor drives the motor vehicle.

When pushing operation is the end 16 at least one energy storage 6 initially not by an arm 13 acted as between the corresponding end 16 of the energy store 6 and the associated support areas 18 an arm 13 an additional suspension, by a spring element 19 is applied, is provided. The spring action of the spring element 19 is with the spring action of the associated energy storage 6 connected in series.

In the annular space 7 are support shells 17 provided, which, as from the 2 and 3 it can be seen, at least over the length of the energy storage 6 extend. These support shells are preferably to the contour of the turns of äuße Ren coil spring 6a adjusted and serve as wear protection. For this purpose, the support shells 17 made of spring steel or hardened steel.

Preferably, the energy storage 6 and the arms 13 - Regarded over the circumference of the device - arranged at least approximately rotationally symmetrical. In the illustrated embodiment, two energy storage 6 provided, which is approximately over half the circumference of the vibration damping device 1 can extend. The disk-shaped component 14 has two diametrically opposed arms 13 ,

In the in the 2 and 3 illustrated embodiment, the spring element 19 integral with the flange or disc-shaped component 14 educated. This is in the disk-shaped component 14 a slit-shaped neckline 20 introduced, whereby an arm-shaped spring element 19 is formed. The length of the arm thus formed 21 is in relation to the length of the arm 21 considered cross-sectional profile tuned such that such an arm 21 forms a spring acting as a bending beam. As mentioned earlier, that is through such an arm 21 generated spring action connected in series to the spring action of an energy storage device 6 , By appropriate design of the slot 20 will be between the free end 22 an arm 21 and the Abstütz- or loading areas 18 an arm 13 a defined circumferential distance 23 educated. By appropriate dimensioning of this distance 23 can be the effective travel of an arm 21 be determined. After overcoming the distance 23 as a result of the corresponding elastic arm 21 acting torque, this elastic arm is supported 21 in the illustrated embodiment, directly on the arm portions 13a an arm 13 from. The slot 20 is designed radially outward such that preferably at least partially a planar support between the radially outer regions 22 an arm 21 and the Abstütz- or loading areas 18 the corresponding arm 13 he follows. The closed end 20a a slot 20 as well as the transition areas 21a an arm 21 are formed such that they are in relation to the due to the elastic deformation of the corresponding arm 21 occurring stresses a fatigue strength of the component 14 guarantee.

It may be useful if the slots 20 are formed such that due to an elastic deformation of an arm 22 a twist angle 23 in the order of magnitude between 2 ° and 8 ° between the relatively rotatable components, here by the two flywheel elements 3 and 4 are formed, is made possible.

With appropriate application of a resilient arm 21 through the associated energy store 6 , this deviates in the circumferential direction until this arm 21 preferably with its radially outer regions 22 at the Abstütz- or loading areas 18 comes to the plant.

Like from the 2 and 3 it can be seen, own the arms 21 at its radially outer region 22 a molding 24 , which in the illustrated embodiment with the interposition of a spring cup 25 with the correspondingly assigned end 16 an energy store 6 cooperates such that this end 16 can be radially supported against the centrifugal force acting on this.

In the illustrated embodiment, this Anformung 24 by a circumferentially extending pin or by a nose 24 formed, which in a circumferential recess or recess 26 a spring plunger 25 can intervene. The respective nose 24 and the associated recess 26 are formed and arranged with respect to each other such that at least in an elastic deformation of the corresponding arm 21 the energy store 6 opposite the radially outer regions 27 on which are the turns of the coil spring 6a supported under centrifugal force, withheld or lifted. A corresponding lift 28 is out 3 refer to.

As if from a comparison of 2 and 3 can be seen, is located in 3 the elastic arm 21 in a strained state and is supported in the circumferential direction of the contours 18 an arm 13 from. The radial retraction of the end 16 the feather 6a is by appropriate shaping of the arm 21 guaranteed. This deformation takes place in such a way that as a result of the pivoting or bending of the arm taking place 21 a radial displacement of the corresponding nose 24 in the direction of the axis of rotation 29 of the system.

Like among others 2 can be seen forms the radially inner region of a nose 24 a ramp-ramp-like slope 30 that with a support area 31 a spring plunger 25 interacts. By the slope 30 and with this cooperating counter contour 31 will be a perfect threading of the nose 24 into the recess 26 guaranteed.

The contours of a nose 24 and the associated recess 26 may be formed with respect to each other such that already when threading the nose 24 into the recess 26 a certain radial displacement of the corresponding spring end 16 can be done. However, it can also be expedient if the aforementioned contours and counter-contours are coordinated with one another in such a way that initially virtually complete threading of a nose is achieved 24 in the corresponding recess 26 can be done without the corresponding spring end 16 is pulled radially inward. This ensures that a radial retraction of the corresponding spring end 16 merely due to the action of the associated spring arm 21 deformation of this arm 21 takes place.

The aforementioned radial retraction of the spring ends 16 has the advantage that even at higher speeds, at least the end regions, that is, some turns of the energy storage or here the outer coil spring 6a , Be kept outside out of contact with other components or areas, so that these spring coils can spring freely, that means that virtually no friction damping produce.

Furthermore, by the action of the arms 21 or the noses 24 Be sure that even in speed ranges where the normally existing friction between the turns of an outer coil spring 6a and its radial support surface 27 is so large that the end turns can no longer spring, at least one end portion of a coil spring 6a still has an elasticity or suspension. This is particularly advantageous in order to dampen the high frequency oscillations occurring in these speed ranges with a small angular amplitude.

Like from the 2 and 3 it can be seen, the radially inside the outer coil spring 6a arranged inner coil spring 6b also by means of at least one spring cup 25 applied. For this purpose, the respective spring cup 25 a circumferential direction in the end region of the corresponding spring 6a into extending approach 32 which also has a recess 26 limited.

In the illustrated embodiment, the respective spring cup 25 designed such that its approach 32 at its outer areas 22 an arm 21 facing the end of an annular, radial collar 33 has, at which the associated end of a spring 6a is supported in the circumferential direction.

How out 3 can be seen, some of the opposite the outer support or guide surface 27 lifted turns of the outer spring 6a under centrifugal force on the approach 32 the corresponding spring cup 25 radially support, which in turn some friction between these spring coils and the approach 32 arises. By appropriate choice of the axial approach 32 however, the resulting friction damping can be kept smaller than that which by supporting these turns on the surface 27 would arise.

The radial displacement of a spring end according to the invention by means of a pivotable arm can, as already mentioned, advantageously be used for those spring ends which pass through the flange 14 be applied in overrun operation. However, the radial retraction of spring ends according to the invention by means of bendable or pivotable arms can also find application for those spring ends which pass through the flange 14 be applied in train operation. Furthermore, it may be appropriate if both spring ends of a spring 6a in the radial direction by pivotable arms 21 can be pulled radially inward.

In the embodiment according to the 2 and 3 owns an arm 21 a circumferentially directed Anformung 24 which is in a recess 26 a spring plunger 25 enters. However, it may be useful if the spring cup 25 has a molded in the circumferential direction, trained for the purpose trained, which in a recess in the region of an arm 21 engages to ensure the desired radial displacement of the corresponding spring end.

Advantageously, a corresponding resilient arm 21 formed so in terms of its shape and its spring properties that this under centrifugal force not on the surface 27 comes to the plant. To prevent such a system, it may also be desirable to provide additional means to prevent such support. This can be done for example by a stop that with the flange 14 is firmly connected and an inadmissible elastic deformation of the corresponding arm 21 prevented radially outward.

Although in the illustrated embodiment, the illustrated lever arms 21 integral with the the loading areas 13 forming flange 14 are formed, such resilient arms 21 also be formed by an additional component. This can be done in a similar way, as for example in the DE 44 33 467 , in particular in connection with the 1 to 4 or in the DE 101 19 878 , in particular in connection with the 1 to 5 , has been described.

At the in 4 illustrated embodiment, the pivotable lever 121 formed by at least one separate component which is about an axis of rotation 121 is pivotally mounted. In the illustrated embodiment, the lever 121 on the flange-shaped component 114 pivoted. The lever arm 121 can counteract the effect of an energy storage, here by a coil spring 134 is symbolized, to be pivoted. In 4 an operating state is shown, which corresponds to the in 3 represented corresponds.

The energy storage 134 can be at one with the flange 114 connected area 135 support. This area 135 However, it can also be on another component, which rotatably with the flange 114 is to be provided.

Instead of a coil spring 134 could also be at least one leg spring or leaf spring use. The one leg of such a spring can, for example, rotationally fixed in a corresponding opening of the flange 114 one be hanged, whereas the other leg a Verdrehwiderstand the lever 121 opposes. To an inadmissibly large pivoting of the lever 121 To avoid radially outwards, as already mentioned, a corresponding stop, for example on the flange 114 be provided. Such a stop, for example, by an integral with the flange 114 configured nose may be formed, which has an axial region on which the lever 121 can support. Also could be the lever 121 have an axially projecting projection in a trained, the necessary pivoting of the arm 121 ensuring recess engages. Such a nose or recess could, for example, in the axially overlapping areas of the lever 121 and the flange 114 be provided.

The tendency to pivot a lever arm 21 respectively. 121 required force can also be influenced by appropriate mass design of such a lever element.

In a particularly advantageous manner, the one end of an energy store 6 associated spring cup 25 be captive or firmly connected to the corresponding end of the energy storage. This can be done for example by means of a positive connection that can be configured as a snap connection. In this regard, for example, on the DE 196 03 248 A1 directed. Such a connection may be between the corresponding spring cup and the outer coil spring 6a and / or, provided an internal coil spring 6b is present between this spring cup and this inner coil spring 6b to be available.

According to one embodiment of the invention may, as in 5 is shown on an enlarged scale, a certain grid effect or a positive connection after threading a nose 224 in the corresponding spring bowl 225 to be available. In the illustrated embodiment, such a connection by means of a latching connection 236 guaranteed. This is the ramp 233 the nose 224 and with this cooperating counter contour 231 of the spring cup 225 designed according stepped, so that the contours formed thereby - when viewed in the circumferential direction - radially engage behind, creating a certain positive connection. By appropriate design of the present between the gradations transition region necessary for unlocking this connection, circumferential force can be influenced.

Such a force-limited lock between a pivotable arm 221 and the corresponding end of an energy store 206 or a spring cap 225 also allows a stress of the corresponding energy storage or the coil spring forming this 206a on train. The about such a screening 236 transmissible torque is, as already mentioned, dependent on the by such a screening 236 seized, force-related connection between the corresponding components or areas 221 . 225 and 206a ,

Due to the energy storage, the at least from a helical compression spring 206a exists, acting centrifugal force is to solve such a grid connection 236 necessary force also centrifugal force, so speed dependent.

The in the 2 to 5 illustrated embodiments also have the advantage that during the radial retraction of the energy storage end 16 no relative movement between spring cup 25 and the lever arm 21 or the nose 24 takes place, whereby a related wear can be avoided.

The inventive design further allows, by suitable tuning of the mass or mass distribution of a lever 21 . 121 . 221 build a speed-dependent torque between the corresponding lever and the associated energy storage end, which must be overcome by the occurring during the compression of an energy storage peripheral force. So it can be the Abhebeverlauf an energy storage end 16 be controlled as a function of the applied torsional torque or motor torque and associated speed.

The in the 6 to 9 illustrated spring cup 325 differs from the previously described spring cups essentially characterized in that the free space or the recess 326 for receiving a radial support nose 324 radially outwardly at least over a portion of its circumferential extent is radially outwardly open. As in particular from the 6 and 7 it can be seen, is the free space or the recess 326 Slot-shaped or channel-like and in the illustrated embodiment over the entire circumferential extent radially outwardly open. However, embodiments are also conceivable in which, starting from the end collar 333 , the free space 326 only over a portion of the engaging in a spring end approach 332 extends. Also, provided the circumferential extent of the approach 332 is greater than the corresponding extent of the engaging nose in this 324 that's the collar 333 opposite end region of an approach 332 or free space 326 be closed, creating a more stable design of a spring cup 325 is guaranteed.

The collar 333 serves, as has already been described in connection with the other suspension cups, to support a spring end.

Out 8th and 9 it is evident that the nose 324 and to the free space 326 adjacent, radially inner sections 325a a spring plunger 325 Corresponding coordinated ramps or counter ramps 331 . 331a form, which cooperate such that upon compression of the corresponding spring 306a by means of a nose 324 bearing flange 314 the corresponding spring end 316 is pulled radially inward, in a similar manner, as in connection with the 1 to 5 has been described. This should also be a free suspension of the corresponding spring end 316 be guaranteed.

In the in the 8th and 9 illustrated embodiment is the nose 324 rigid with the flange 314 educated. However, such a nose can also in a similar manner, as in connection with the 1 to 5 has been described, on an elastic or pivotable arm 21 . 121 . 221 be formed, which is supported by a corresponding flange or disc-shaped component.

An at least partial opening of the recess or the free space 326 allows a freer design of the nose 324 because at least in the collar 333 adjacent sections of an approach 332 the nose 324 can be made wider in the radial direction and thus, at least in this area, can have a higher bending stiffness. So you get through a corresponding design of a spring bowl 325 additional radial space for a nose 324 which causes longer noses 324 are possible at least the same strength. The inventive design of a spring cup 325 but also allows the radially inner, with a nose 324 cooperating support areas 325a a bowl 325 thicker in terms of material thickness, whereby the strength of the cup against centrifugal forces, which by the spring 306a can be exercised on this, can be improved.

Due to the possibility created, longer supporting noses 324 You can also use spring pens 325 with longer approaches 332 be used. As a result, the radial support of a larger number of spring coils can be ensured. How out 8th can be seen in the relaxed state of the spring 306a at least five spring tails through the bowl 325 be supported.

By appropriate adaptation or design of the with a spring 306a cooperating radial Abstützkonturen a spring cup 325 can also in the Windun conditions of an end portion of a spring 306a be limited to an acceptable level. By appropriate shaping or design of the Abstützkontur a cup 325 So can the radial bending curve under centrifugal force of one end region forming turns of a spring 306a be determined.

As in particular from 9 it can be seen that are radially within a nose 324 existing spring loading areas 324a of the flange 314 and the radially outside of the nose 324 existing spring loading areas 324b in the circumferential direction of the damping device 301 arranged offset from one another. In the illustrated embodiment, this offset is between the loading areas 324a and 324b dimensioned such that these practically at the same time on the one hand on the collar 333 of the spring cup 325 and on the other hand, at the end turn 316a the feather 316 come to the plant.

However, it may be advantageous if the collar 333 also in the area of the radially inner loading area 324a of the flange 314 interrupted or offset back is in the circumferential direction, in such a way that thereby an immediate support of the Endwindung 316a at the area 324a of the flange is ensured. In such an embodiment, then the loading area 324a . 324b of the flange 314 , in the radial direction, be aligned.

That in the 10 to 12 illustrated support element 425 also allows radial support of the end turns of a spring end 416 in a similar way as in connection with the spring cap 325 has been described. How out 12 it can be seen, are in the illustrated embodiment, the effective as ramps and counter ramps surfaces 431 the flange nose 424 and 431a of the support element 425 coordinated so that during the immersion phase of the flange nose 424 in the cross-sectionally U-shaped support element 425 always a surface contact between the two surfaces 431 and 431a is available. As a result, the wear occurring on these surfaces can be substantially reduced. In the illustrated embodiment, the surfaces 431 and 431a arc-shaped and designed in accordance with the axis of rotation of the vibration damping device according to ensure surface contact.

Although it may be useful if the support element 425 is made of a high strength plastic, the illustrated embodiment is suitable for manufacture from sheet material. To appropriate sliding properties, especially in the area of the area 431a to ensure the sheet metal or the support element 425 at least on this surface 431a be coated with a sliding material. Furthermore, it may be particularly useful if the support element 425 at least in the area of the area 431a is cured. The production of elements 425 Sheet metal has the advantage that it can be produced by simple forming, ie without cutting. This allows a cost-effective production of such support elements.

The support element 425 is, as already mentioned, designed in cross-section U-shaped and has two tabs or tongues 434 . 435 that protrude laterally. These tongues 434 . 435 lean on the end turn 436 the corresponding spring, like this 12 can be seen. The areas 434 . 435 simultaneously serve to act on the Federendbereiches 416 ,

To reduce the material stress due to internal stresses caused by the radial support and the application of the corresponding spring end 416 in the element 425 occur, has this support element 425 corresponding free cuts 437 ,

As in connection with the 10 and 11 seen, has a support element 425 projections 438 here through tab-shaped areas 438 are formed, which in relation to the remaining areas of a support element 425 are deformed so that they are in by the U-shaped shape of the support element 425 formed free space 426 protrude. The areas 438 form support surfaces on which the nose 424 of the flange 414 with a mating surface, which may be formed for example by a gradation comes to rest.

As in particular from the 11 and 12 can still be seen, has a support element 425 a molding 439 here's a radially inward nose 439 forms. This formation 439 attacks, like this 12 can be removed between two turns of the spring end 416 a, whereby a captive between the corresponding spring end 416 and the associated support element 425 is guaranteed.

The embodiments are not as a limitation to understand the invention. Rather, in the context of the present Revelation numerous modifications and modifications possible, in particular such variants, elements and combinations and / or materials, which, for example, by combination or modification of individual in Compound with those in the general description and embodiments and the claims described and in the drawings contained features or elements or process steps for the person skilled in the art with regard to the solution of the task are and by combinable features to a new object or to new process steps or process steps to lead, also as far as manufacturing, testing and work procedures.

1

Vibration damping device

2

torsional vibration dampers

3, 4

flywheel elements

5

storage

6

energy storage

6a, 6b

coil springs

7

torusartiger room

8th, 9

housing parts

10

welded joint

11 12, 13, 13a

impingement

14

disk-like component

15

riveted joints

16

The End

17

support shells

18

support areas

19 19a

spring element

20 20a

slot

21 21a

poor

22

free The End

23

angle of twist

24

conformation

25

spring cup

26

recess

27

areas

28

dregs

29

axis of rotation

30

slope

31

support area

32

approach

33

collar

114

component

121

lever

121

axis of rotation

134

coil spring

135

Area

206

energy storage

206a

Helical compression spring

221

pivotable poor

224

nose

225

spring cup

231

mating contour

233

leading ramp

236

grid connection

306a

feather

314

flange

316 316a

spring end

324

support nose

324a, 324b

impingement

325

spring cup

325a

sections

326

recess

331 331a

counter-ramps

332

approach

333

end collar

414

flange

416

spring end

424

Flanschnase

425

supporting

431, 431a

surfaces

434 435

tabs or tongues

436

end turn

437

cutouts

438 439

projections

Claims (12)

Torsional vibration damper having an input part and an output part, which are mutually rotatable against the action of effective energy storage between them, wherein the energy storage at least one arranged substantially in the circumferential direction of the damper, compressible helical spring, further carried at least one pivotable in the circumferential direction lever member of one of the parts is, wherein at least in a relative rotation between the input part and the output part, the coil spring can be supported with one of its circumferential ends such that it is pivoted due to the relative rotation relative to this supporting part, characterized in that the lever element has contours, which with on associated counter-contours provided cooperate end of the coil spring such that at least one end portion of the coil spring during the circumferential pivoting of the lever element against the centrifugal force acting on this spring section is retained radially. Torsional vibration damper according to claim 1, characterized characterized in that the lever element by a bending beam-like formed spring element is formed. Torsional vibration damper according to claim 1, characterized characterized in that the lever element at the input part and / or output part is mounted pivotably and against the action of an additional Energy storage is pivotable about its storage. Torsional vibration damper according to one of claims 1 to 3, characterized in that the input part or output part by a flange-shaped Part is formed, which carries the at least one lever element. Torsional vibration damper according to one of claims 1 to 4, characterized in that against a spring action pivotable lever element and the coil spring between input part and output part operatively connected in series are. Torsional vibration damper according to one of claims 1 to 5, characterized in that the helical spring in the circumferential direction of the torsional vibration damper extends and within the torsional vibration damper, a centrifugal force-dependent, the Spring action of the coil spring produces parallel friction, whereby the total generated by the coil spring, dynamic Verdrehwiderstand dependent on speed is. Torsional vibration damper according to one of claims 1 to 6, characterized in that the output part or input part a the coil spring axially overlapping Has wall at which the coil spring either directly by means their turns or indirectly over intermediate support parts supported at least under centrifugal force. Torsional vibration damper according to one of claims 1 to 7, characterized in that the coil spring at least at its cooperating with a lever element end an intermediate layer wearing, which forms the counter-contours, with the contours of the lever element interact. Torsional vibration damper according to one of claims 1 to 8, characterized in that the lever element is pivotable in such a way is that its retention contours while the pivoting be displaced on a trajectory, the across from the axis of rotation of the damping device a changing one Distance has. Torsional vibration damper according to claim 1 to 9, characterized in that the lever element is pivotable in such a way is that, in a pivoting of the lever element due to a circumferential loading by the helical spring, the supporting contours of the lever element be displaced along a trajectory such that their Distance from the axis of rotation of the torsional vibration damper becomes smaller, whereby the corresponding spring end in the direction of the axis of rotation packed becomes. Torsional vibration damper according to one of claims 1 to 10, characterized in that the contours of the lever element at least by a circumferentially extending, nose-shaped Anformung is formed. Torsional vibration damper according to one of claims 1 to 11, characterized in that the at the corresponding spring end provided counter-contours by a recess one at the corresponding Spring end provided intermediate layer is formed.