DE102014207961A1 - Tail vibration damper and method of providing a Tilgerschwingungsdämpfers - Google Patents

Abstract

A Tilgerschwingungsdämpfer (110), for example for a drive train of a motor vehicle, for damping a vibration component of a rotary movement comprises at least one absorber mass (112) which is designed to perform in response to the rotational movement to dampen the vibration component thereof. Further, the Tilgerschwingungsdämpfer (110) comprises at least one guide structure (114) against which the absorber mass (112) is arranged to be movable. The Tilgerschwingungsdämpfer (110) also includes at least one rolling body (142) having a mating surface (302) which is adapted to at least partially axially guide the rolling body (142) together with a guide surface (304), wherein the guide surface (304) the absorber mass (112) and / or the guide structure (114) is arranged, wherein the guide surface (304) an exemption (306, 406) connects and / or the guide surface (304) comprises an exemption (306, 406).

Description

Embodiments relate to a Tilgerschwingungsdämpfer and a damper assembly, which can be used for example in the context of a drive train of a motor vehicle, such as a motor vehicle with an internal combustion engine, and a method for providing a Tilgerschwingungsdämpfers.

In the field of motor vehicle construction, but also in other areas of mechanical and plant engineering damper assemblies are used, which are used for damping at least one vibration component of a rotational movement and optionally for transmitting a torque of the rotational movement. Thus, corresponding damper arrangements are used for example in the field of vehicle construction in the context of powertrains of motor vehicles, in which it may come to deviations from a uniform or uniform rotational movement, for example, conceptually.

In the case of a powertrain of a motor vehicle, corresponding deviations from a uniform or uniform rotational movement can be caused, for example, by an unfolding characteristic of the torque of an internal combustion engine. In order to decouple, but at least attenuate, these components, for example a transmission, a differential or other corresponding components of a drive train, damper arrangements are used there.

Such torsional vibration dampers are for example in the DE 10 2010 054 297 A1 described. These relate to a compensation device for torsional vibrations for a drive train of a motor vehicle with an internal combustion engine and a transmission with a centrifugal pendulum, which has distributed over the circumference absorber masses. These are accommodated on both sides on a flange part and can be pivoted radially and in the circumferential direction.

In the area of corresponding damping arrangements, the fundamental challenge of realizing an attenuation of at least one oscillation component of a rotary movement is often accompanied by a multiplicity of further boundary conditions with regard to construction, function and other parameters. For example, there is a need to improve a trade-off between packaging space, friction encountered, ease of manufacture, and other parameters of a damper assembly.

This need is taken into account by a damper vibration damper according to claim 1 and a method for providing a damper vibration damper according to claim 12.

A Tilgerschwingungsdämpfer according to an embodiment, for example, for a drive train of a motor vehicle, for damping a vibration component of a rotary motion, comprising at least one absorber mass, which is designed to perform in response to the rotational movement to a vibration to dampen the vibration component thereof. Further, the Tilgerschwingungsdämpfer comprises at least one guide structure against which the absorber mass is movably arranged and at least one rolling body having a counter-guide surface which is adapted to at least partially guide the rolling element together with a guide surface axially. Here, the guide surface is arranged on the absorber mass and / or the guide structure, wherein the guide surface is followed by an exemption and / or the guide surface comprises an exemption.

Because an exemption adjoins the guide surface and / or the guide surface comprises an exemption, in some embodiments a friction between the rolling body and the absorber mass and / or the rolling body and the guide structure can be at least reduced if they touch in the axial direction.

In some embodiments, the exemption directly adjoins the guide surface. This could possibly be achieved that the mating surface of the rolling body has no contact with the exemption. In some embodiments, such a friction in this area can be avoided because the guide structure and / or the absorber mass with the rolling body in the region of the exemption do not touch.

Additionally or alternatively, the exemption can be arranged circumferentially to a running surface for the rolling elements. In some embodiments, thus, the reduction of friction in all possible operating states, regardless of a deflection of the absorber mass or a degree of deflection of the absorber mass can be effected. The running surface for the rolling body can be arranged, for example, in or on the absorber mass and / or in or on the guide structure. For example, the absorber mass and / or the guide structure for this purpose may have a recess on which the tread is located. The recess may be, for example, a passage opening or else an opening which is open in only one axial direction.

In some embodiments, the exemption is formed chamfered. For example, the exemption may have a deviating from a hollow cone shape. Under certain circumstances, a tangent on a surface of the release may change its direction at any point of release, and not just in a region where the release joins either the tread for the roller or the guide surface.

Additionally or alternatively, the release in some embodiments comprises a punching device. In some embodiments, the release can be made in a simple manner. For example, the release can be produced as part of a punching and / or a manufacturing of the tread. Under certain circumstances, the exemption, which includes the punching indentation, can be reworked in further processing steps. As a result, in some embodiments, it may be possible to modify and / or improve a form of the release. Optionally, in some embodiments, the release may include only the punch. As a result, in some embodiments, further manufacturing steps for generating the exemption can be omitted.

In addition or as an alternative, in some embodiments the release is at least partially produced by embossing. In some embodiments, the exemption can receive such a defined shape. For example, the release may also be made exclusively by embossing.

Additionally or alternatively, the exemption may include a radius. In some embodiments, it is thus possible to avoid an edge and / or line contact being formed between the guide surface of the release and / or the release and the counter guide surface. As a result, an increased surface pressure and / or increased wear of the rolling body and / or the guide surface or the release could possibly be reduced and / or even avoided.

In addition or as an alternative, in some embodiments, the clearance is smaller in a functional region in which the rolling element has a rolling contact in a deflected state of the absorber mass than outside the functional region. In some embodiments, it may thus be possible for the rolling element to be able to receive an axial guidance either at the clearance or the guide surface near a rolling contact. Outside of the functional area in which the rolling element does not have rolling contact in these deflected states, in some embodiments it is possible, because the clearance is greater than in the functional area, that the rolling elements in this area also have no axial guidance and thus no frictional contact in the axial direction Direction with the absorber mass or the management structure receives. A deflected state of the absorber mass may be present, for example, when the absorber vibration damper rotates. In a deflected state, the absorber mass can be in contact with its essentially radially outwardly directed running surface at a substantially radially inwardly directed rolling surface of the rolling element. For example, in some embodiments, the functional region may be in an angular range of 120 °, which extends from a kidney tip over a tread surface opposite the kidney tip in a kidney-shaped tread. A rolling contact or rolling contact region may be, for example, the region in which the rolling element and the absorber mass or the rolling elements and the guide structure make contact in the radial direction of the rolling element.

Additionally or alternatively, in some embodiments, the clearance in the axial direction of the guide surface from a depth of at least a value of 0.2 mm. Additionally or alternatively, in some embodiments, the clearance from a tread to the guide surface, as viewed from a center of the recess comprising the tread, is at least 0.1 mm in the direction of the component. In some embodiments, the release may be of sufficient size to either prevent abutment of the mating surface in the axial direction in that region and / or to avoid line contact.

Additionally or alternatively, the at least one absorber mass is movably arranged in some embodiments between two guide structures which are opposite one another in the axial direction.

Additionally or alternatively, the counter-guide surface of the rolling element is formed conically, at least in some embodiments, in some embodiments. In some embodiments, such a friction surface or a frictional contact between the rolling body and the guide surface or for exemption can be reduced in its size or its surface or its extent. In some embodiments, the rolling element with its counter-guide surface at the clearance and / or the guide surface viewed from a cross-section to an axial direction, have a line-shaped contact region. As a result, under certain circumstances, a band-shaped frictional contact or Reibkontaktbereich between the Guide surface and / or the exemption with the mating surface arise. In contrast to a line contact, over which a flat contact has a lower surface pressure, in some embodiments, the wear between the two components can be reduced.

In some other embodiments, the rolling element additionally or alternatively on at least two rolling surfaces with different diameters. In some embodiments, the counter guide surface can thus result in the axial direction and between the two rolling surfaces. For example, the rolling elements may be formed as a stepped roller. The step roller may be formed symmetrically, for example, and have a largest diameter range in a central region. This can not serve as a rolling surface, for example. For example, two rolling surfaces, each with the same rolling surface diameters, can connect in an axial direction to the largest diameter range. These can serve, for example, as rolling surfaces of the rolling element in running surfaces, which are covered by the absorber mass. After axially outside, two further rolling surfaces with smaller diameters can connect to these rolling surfaces. These rolling surfaces can roll, for example, in running surfaces of the guide structures.

Additionally or alternatively, in other embodiments, a distance in the radial direction between a Wälzkontaktbereich in which touch the rolling elements and the absorber mass or the rolling elements and the guide structure in the radial direction and a Reibkontaktbereich in which the rolling elements and the absorber mass or the rolling elements and touch the guide structures in the axial direction, maximum 1 mm. Characterized in that a distance between the Wälzkontaktbereich and a Reibkontaktbereich in the radial direction is as small as possible, it may be possible in some embodiments that the Reibkontaktbereich receives the smallest possible diameter and thus also the smallest possible area. As a result, the friction between the rolling body and the absorber mass and / or the rolling body and the guide structure can be reduced. The radial direction may relate, for example, to a radial direction of the rolling body. Depending on the position of the rolling element, this may coincide with a radial direction of the Tilgerschwingungsdämpfers under certain circumstances.

Embodiments relate to a method for providing a vibration damper, for example for a drive train of a motor vehicle for damping a vibration component of a rotary movement. In the method, at least one absorber mass, which is designed to perform a vibration in response to the rotational movement, in order to damp the oscillation portion thereof, is movably arranged on at least one guide structure. For this purpose, at least one rolling element, which has a counter-guide surface, is used. The counter-guide surface is designed to at least partially guide the rolling element axially together with a guide surface. Furthermore, an exemption is produced in a further process, so that the release adjoins the guide surface or the guide surface comprises the release, wherein the guide surface is arranged on the absorber mass and / or the guide structure.

By creating an exemption which adjoins the guide surface and / or is at least partially part of the guide surface, friction between the rolling body and the absorber mass and / or the rolling body and the guide structure can be at least reduced in some embodiments.

The individual processes of the method, that is, arranging and / or manufacturing, can be carried out simultaneously, in a different order and / or partially overlapping.

In some embodiments, when the tread is manufactured, a tread is produced by a punching process, so that the punch is the release or comprises it. As a result, the release can be introduced completely or at least partially in a simple manner in one method step. For example, the tread can be punched into the absorber mass or the guide structure. Under certain circumstances, the production of the exemption can take place at the same time or substantially simultaneously with the production of the tread. In some embodiments, the release, which includes the stamping indentation, may be reworked in later operations or machining processes.

Optionally, the production of the exemption can be done by means of a stamping process. In some embodiments, such a geometry of the exemption can be determined very accurately and defined. Additionally or alternatively, the embossing of the release can be done before and / or after introducing a tread for the rolling elements in the absorber mass and / or the guide structure. For example, embossing may in some embodiments take the form of a pre-stamping prior to punching or in a subsequent calibration process of the tread.

Further advantageous embodiments will be described below with reference to exemplary embodiments illustrated in the drawings Embodiments are not limited, described in more detail.

1a shows a schematic representation of a partial elevation of an overview of a vibration damper unit according to an embodiment;

1b shows a schematic cross-sectional view through the in 1a shown vibration damper unit along a sectional plane AA;

2a shows a schematic representation of a plan view of a Tilgerschwingungsdämpfers the vibration damper according to the embodiment of the 1a and 1b ;

2 B shows a schematic cross-sectional view through the in 2a shown Tilgerschwingungsdämpfer the vibration damper unit along a cutting plane RR;

2c shows a schematic cross-sectional view through the in 2a shown Tilgerschwingungsdämpfer the Schwingungsdämpfereinheit along a sectional plane CC;

2d shows a schematic cross-sectional view through the in 2a shown Tilgerschwingungsdämpfer the Schwingungsdämpfereinheit along a sectional plane AA;

2e shows a schematic representation of a perspective view of the Tilgerschwingungsdämpfers the vibration damper unit according to the embodiment of the 2a to 2d ;

3 shows a schematic cross-sectional view of a Schwindungsdämpfereinheit with a Tilgerschwingungsdämpfer;

4 shows a schematic section of the 3 ;

5a shows a schematic cross-sectional view through a Tilger mass of a Tilgerschwingungsdämpfers according to an embodiment;

5b to 5d show enlarged sections of the 5a ;

6a shows a schematic representation of a plan view of an absorber mass for a Tilgerschwingungsdämpfer according to another embodiment;

6b shows an enlarged section of the 6a ;

6c shows a schematic cross-sectional view through the in 6a shown absorber mass along a sectional plane AA;

6d and 6e show enlarged sections of the 6c ;

6f shows a perspective view of the absorber mass of 6a ;

7a shows a schematic representation of a plan view of a guide structure of the Tilgerschwingungsdämpfer according to another embodiment;

7b shows an enlarged section of the 7a ;

7c shows a schematic cross-sectional view through the in 7a shown guide structure along a section line BB;

7d shows a schematic cross-sectional view through the in 7a shown guide structure along a sectional plane AA;

7e shows a schematic, perspective view of the in 7a shown leadership structure;

8a shows a schematic representation of a plan view of a guide structure according to another embodiment;

8b shows an enlarged section of the 8a ;

8c shows a schematic cross-sectional view through the in 8a shown guide structure along a sectional plane BB;

8d shows a schematic cross-sectional view through the in 8a shown guide structure along a section line AA;

8e shows a schematic perspective view of the guide structure according to 8a ;

9a shows a schematic cross-sectional view of a Tilgerschwingungsdämpfers according to another embodiment;

9b shows an enlarged section of the 9a ;

10 shows a schematic representation of a method for providing a Tilgerschwingungsdämpfers;

11 shows a schematic cross-sectional view of an absorber mass;

12a shows a schematic representation of a plan view of an absorber mass;

12b shows a schematic cross-sectional view of the absorber mass of 12a ;

12c shows a further schematic cross-sectional view of the absorber mass of 12b and 12a ;

13 shows a schematic representation of a partial elevation of a rolling body;

14a shows a schematic cross-sectional view of a vibration damper unit;

14b and 14c show schematic sections of the 14a ;

15 shows a schematic cross-sectional view of another vibration damper unit;

16a shows a schematic representation of a plan view of another vibration damper unit;

16b shows an enlarged section of the 16a ;

16c shows a schematic perspective view of another vibration damper unit;

16d shows a schematic cross-sectional view of a support ring of the vibration damper units of 16a to 16c ;

16e shows a schematic representation of a plan view of another support ring;

16f shows a schematic cross-sectional view of another support ring;

16g shows an enlarged section of the 16f ;

17a shows a schematic representation of a plan view of another vibration damper unit;

17b shows an enlarged section of the 17a ;

17c shows a schematic cross-sectional view through the vibration damper unit of 17a ;

18a shows a schematic cross-sectional view of another vibration damper unit;

18b shows a schematic perspective view of a dowel pin of the vibration damper unit according to the 18a ;

18c shows a section of a perspective view of the vibration damper unit of 18a ;

18d shows a schematic perspective view of another vibration damper unit;

18e shows an enlarged section of the 18d ;

18f shows a schematic perspective view of another vibration damper unit;

19a shows a schematic perspective view of an absorber mass;

19b shows a schematic perspective view of a vibration damper unit;

19c shows a schematic cross-sectional view of an absorber mass of the vibration damper unit of 19b ;

19d shows a perspective view of a vibration damper unit;

19e shows a schematic cross-sectional view of an absorber mass of the vibration damper unit of 19d ,

In the following description of the accompanying drawings, like reference characters designate like or similar components. Further, summary reference numbers are used for components and objects that occur multiple times in one embodiment or in one representation, but are described together in terms of one or more features. Components or objects which are described by the same or by the same reference numerals may be the same, but possibly also with regard to individual, several or all features, for example their dimensions be executed differently, unless something else explicitly or implicitly results from the description.

The 1a and 1b shows different views of a vibration damper unit 100 , For example, for a drive train, not shown, of a motor vehicle. This includes a torsion damper 102 , the at least one primary page 104 and at least one secondary side 106 between the at least one spring element 108 is coupled so that a torque transmission from the primary side 104 to the secondary side 106 over the at least one spring element 108 he follows.

Furthermore, the vibration damper unit comprises 100 a damper vibration damper 110 , the at least one absorber mass 112 and at least one leadership structure 114 includes, wherein the management structure 114 is formed around the at least one absorber mass 112 movable to dampen a vibration component of a rotary motion. At the absorber vibration damper 110 Thus, the vibration is damped by the at least one damper mass as damper element, which does not transmit any torque.

Furthermore, the vibration damper unit comprises 100 , which may also be referred to as a flywheel with a torsion damper, also a Taumelentkopplungsstruktur 116 , which is formed around the at least one absorber mass 112 in the axial direction M movable and rotationally fixed and / or torsion angleunlimited with an output side 118 , which in the embodiment of the 1a to 2e as output hub 120 is formed, the vibration damper unit 100 connect to. The absorber mass 112 For example, it may comprise a plurality of individual sealing masses arranged adjacent to each other in the axial direction M. These can each have at least one absorber mass attachment structure 113 which may be, for example, a rivet or other fastening means, connected to each other. In further, not shown embodiments, the absorber mass can also be formed in other ways, for example in one piece. In the embodiment, the Tilgerschwingungsdämpfer includes 110 six absorber masses 112 , In some other, not shown Tilgerschwingungsdämpfern also a different number of absorber masses can be used.

At the vibration damper unit 100 is a torque over a sprocket 122 in one by the arrow 123 specified direction of rotation on the primary side 104 of the torsion damper 102 directed. This is the sprocket 122 with a cover component 124 of the torsion damper 102 rotatably connected. The cover component 124 is with a housing shell 126 of the torsion damper 102 connected and limited with a radially outer region of the housing shell 126 a feather area 128 for receiving the spring element 108 , In the feather area 128 is like in the 1a recognizable, in the circumferential direction a plurality of spring elements 108 arranged. About the primary page 104 becomes a spring element driving shoe 130 driven in the spring area 128 received and a torque on the at least one spring element 108 transfers. About the spring element 108 the torque is applied to a Federansteuersteg 132 the secondary side 106 transfer. The secondary side 106 is over at least one attachment structure 134 , which may be formed, for example, as a rivet, spacer sleeve, Distanzniet, spacers or the like, wobble with the Tilgerschwingungsdämpfer 110 or its management structure 114 connected. The secondary side 106 has a passage opening through which the attachment structure 134 is guided. Concentric with the passage opening is a reduction 136 in which a head of the attachment structure 134 sunk. In the circumferential direction is the secondary side 106 over a plurality of such attachment structures 134 with the absorber vibration damper 110 connected. For example, in the 1a and 1b further attachment structures 136-a to 136-c recognizable.

From the management structure 114 the torque is transmitted via the tumble decoupling structure 116 on the output hub 120 transfer. The output hub 120 has an internal toothing. This is a straight toothing. About the output hub 120 the torque is transmitted to an output shaft, not shown. Both the tumble coupling structure 116 , as well as the Tilgerschwingungsdämpfer 110 , are based on the 2a to 2e described in more detail.

The sprocket 122 has an inner diameter d smaller than an inner diameter D of a fixing portion extending in an axial direction 137 of the cover component 124 , The attachment section 137 This limits an envelope space in a radial direction, in which the at least one absorber mass 112 can move in a deflected state. The absorber mass 112 In a deflected state, therefore, it assumes a larger diameter D than an inner diameter of the toothed rim 122 , For mounting through the sprocket 122 can the at least one absorber mass 112 radially inward in the Tilgerschwingungsdämpfer 110 be sunk.

The 2a to 2e show different schematic representations of the Tilgerschwingungsdämpfers 110 , which can also be referred to as absorber or speed-adaptive absorber. The management structure 114 , which may be formed, for example, as a track plate is via a mounting structure 138 , which may be formed in some embodiments as a support pin, rivet, Distanzniet or the like, with a second guide structure 140 connected in the axial direction opposite to the first guide structure 114 is arranged. Also the second management structure 140 may be formed, for example, as a railway sheet. In the axial direction between the first guide structure 114 and 140 is the at least one absorber mass 112 , which can also be referred to as energy storage or flyweight, via a rolling element 142 guided. As in 2a recognizable, is the absorber mass 112 over two rolling elements 142-a and 142-b between the two management structures 114 and 140 guided.

In the rolling element 142 Embodiments 2a to 2e is a so-called step roller, the rolling surfaces 144 and 146 having different diameters. The rolling surface 146 has a smaller diameter than the rolling surface 144 on. The absorber mass 112 has at least one tread 148 on, in the rolling element 142 with the rolling surface 144 rolls. The management structures are similarly similar 114 and 140 one tread each 150 on, in the rolling element 142 with the rolling surface 146 rolls. In the area of treads 148 and 150 are exemptions shown in dashed lines 306 , which leads to a reduction in friction between the rolling elements 124 with the absorber mass 112 and the leadership structures 114 and 140 serve. The exemptions 306 will be even more accurate on the basis of 5a to 9b described.

At the management structure 114 is also a support body 154 attached. The support body 154 may be formed in some embodiments as a plastic ring. The supporting body 154 is arranged concentrically to a central axis M and has a plurality of radially outwardly directed fastening eyes 156 on. These are C-shaped and engage from radially inward to one of the attachment structures 138 , The leadership structures 114 and 140 wise, as in 1a at the second management structure 140 recognizable, an embossed structure 160 on, against which the support body 154 with his attachment eye 156 can support. The supporting body 154 has a plurality of support sections 158 on. There are two support sections in each case 158-a and 158-b , as in 1a Recognizable, arranged so that they are with an absorber mass 112 For example, the absorber mass 112-a can come into contact. The support sections 158-a and 158-b are symmetrical to an imaginary line of symmetry, which is located centrally between them, arranged and formed.

In the following, the support section will be representative 158-a described. The support section 185-a has a substantially trapezoidal shape. This is one of the parallel legs 159 , namely the longer, on one of the absorber mass 112 opposite side of the support section 185-a and integrally connects to a main body of the support body 154 on or is in this. Opposite is a shorter parallel leg 161 , the absorber mass 112 is facing. The thigh 161 is with the main body of the support body 154 over another leg 165 connected. This is the thigh 165 on a support section 158-b facing side. The thigh 165 closes over a radius to the main body of the support body 154 at. In the circumferential direction opposite are the legs 159 and 161 with another leg 157 connected. This is designed substantially as a straight line and without radius or with a smaller radius than the leg 165 with the main body of the support body 154 connected. In some embodiments, the legs extend 159 and 161 not parallel to each other.

In some other embodiments, not shown, the support body may also be omitted or formed in other ways.

The tumble decoupling structure 116 is in the axial direction only with the guide structure 114 and not with the leadership structure 140 in contact and includes a first Teilentkopplungsbauteil 162 and a second partial decoupling component 164 , The two partial decoupling components 162 and 164 are on an output hub flange 166 the output hub 120 attached. The output hub flange 166 points at the vibration damper unit 100 a plurality of wings 168 on. At the vibration damper unit 100 are four wings 168-a to 168-d , each offset by an angle of 90 ° to each other, arranged. The wings 168-a to 168-d have a greater extent radially outward than areas 170-a to 170-d , each between two wings 168-a to 168-d lie. The output hub flange 166 or its wings 168-a to 168-d have in the axial direction, such as in the 2 B and 2c recognizable, in a radially outer region, a smaller extent in an axial direction, as the output hub flange 166 in a radially inner area.

In some other embodiments, not shown, the output hub flange over its entire extent, even in the region of the wings, have a uniform extension in an axial direction. The areas of lesser extent in an axial direction may be, for example, a diameter range in which at least one of the Supply decoupling components 162 and 164 with the output hub flange 166 connected is.

The partial decoupling components 162 and 164 are at the vibration damper unit 100 identical construction. In some embodiments, the partial decoupling components 162 and 164 be formed for example as a spring plate or axial leaf spring. In some other embodiments, not shown, the tumble coupling structure may also comprise only a partial decoupling component or an axial leaf spring or a spring plate or another spring element. Optionally, the partial decoupling components may have different shapes, materials and / or properties.

Because the partial decoupling components 162 and 164 are designed to be identical, is representative of the shape of the partial decoupling component 162 described. As in 2a recognizable, has the partial decoupling component 162 a symmetrical shape. Symmetry line is the section line CC.

Starting from a leadership structure lead 174-a that attach to the guide structure 114 the partial decoupling component is used 162 described in a clockwise direction. The partial decoupling component 162 has four such guiding structure protrusions 174-a to 174-d on. At the management structure lead 174-a closes further in the circumferential direction a concave radially inwardly curved portion 176-a ,

To the concave inward curved section 176 closes again to radially outwardly extending wing projection 178-a attached to the wing 168-a or the output hub flange 166 serves. Continue clockwise to close the wing ledge 178-a another concave inward curved section 176-b to the next guide structure protrusion 174-b , At the management structure lead 174-b closes a driven attachment receiving section 172-b at. The output attachment receiving section 172-b has in the region of the symmetry line on a concave inwardly curved recess. To the output attachment receiving section 172-b closes again a leadership structure lead 174-c at. Left of the symmetry line in the 2a is the partial decoupling component 162 formed analog. Radially inwardly, the partial decoupling component 162 a passage opening 163 on, with the part of the decoupling component 162 is arranged concentrically to the rotation axis M. The passage opening 163 has a larger radius than the output hub 120 on.

The partial decoupling component 162 is via a plurality of output attachment structures 180 on the output hub 120 or the output hub flange 166 attached. The partial decoupling component 162 is with two output attachment structures 180-a and 180-b , which may be formed, for example, as a rivet or standoffs or other fastening means, with its wing projection 178-a on the wing 168-a attached. Substantially opposite in the radial direction is the partial decoupling component 162 with his wing overhang 178-b on the wing 168-c with the output attachment structures 180-d and 180 c attached. In some other embodiments, not shown, only one output attachment structure per wing can be arranged.

With its leadership structure tabs 174-a to 174-d is the partial decoupling component 162 each at the management structure 114 and thereby also on the Tilgerschwingungsdämpfer 110 attached. The management structure 114 has four tumble decoupling attachment projections 182-a to 182-d on. The tumble decoupling attachment tabs 182-a to 182-d continue to project radially inward than an average radially inward surface of the guide structure 114 , The guide structure protrusions 174-a to 174-d are each with one of the tumble decoupling attachment protrusions 182-a to 182-d via a fastening structure 188 connected. The attachment structure 188 may be formed, for example, as a rivet. In such cases, the management structure 114 with the second partial decoupling component 162 riveted.

The second partial decoupling component 164 is rotated by 90 ° to the first Teilentkopplungsbauteil 162 arranged and fixed, wherein the two partial decoupling components 162 and 164 the output hub flange 166 take up in the axial direction between themselves. The second partial decoupling component 164 is so with his wing projections 178-e and 178-f on the wing 168-d and the wing opposite this 168-b attached. For this purpose, as with the Teilentkopplungsbauteil 162 Output attachment structures 180 used. On the wing 168-b are the output attachment structures 180-e and 180-f recognizable with which the partial decoupling component 164 Being on a the part decoupling component 162 opposite side of the output hub flange 166 is arranged. The partial decoupling component 162 has in its output attachment receiving portions 172-a and 172-b two output attachment mounts each 184 on. In the driven attachment receiving section 172-b these are with the reference numbers 184-e and 184-f characterized. The output attachment mounts 184 take part of the power take-off structure 180 , So for example, a rivet head, in the axial direction.

At the vibration damper unit 100 are the output mounts 184 each formed as through holes, through which the head or a part of the driven attachment structure 180 can protrude through. In this case, the output attachment shots have 184 a larger extent than the output attachment structure 180 so that the partial decoupling component 162 not via the output attachment structures 180 with which the partial decoupling component 164 on the output hub flange 166 is fastened, comes into contact or is fixed by this. In some embodiments, such a space can be reduced in the axial direction. Similarly, the output attachment structures also pierce 180-a and 180-b such as 180 c and 180-d corresponding through holes or output attachment receptacles in the partial decoupling component 164 ,

In some other embodiments, not shown, the partial decoupling components may also be attached to the output hub with a different number of output attachment structures. Analogously, the partial decoupling component can then have a corresponding number of output attachment mounts. In some further embodiments, the partial decoupling component may also have no output attachment mount. Optionally, a different number of guide structure protrusions or attachment structures may be provided.

The partial decoupling component 164 is also with the leadership structure 114 connected. Because the leadership structure 114 in the axial direction, a smaller extent than the output hub flange 166 is at the leadership structure 114 a spacer 186 arranged. The spacer 186 may be formed, for example, as a plastic ring. The spacer 186 is essentially analogous to the management structure 114 a plurality of tumble decoupling attachment protrusions 182-e to 182-h on. At these is the partial decoupling component 162 with its leadership structure tabs 174 established. For example, at the tumble decoupling attachment protrusion 182-h of the spacer 186 the leadership structure lead 174-e riveted. This is a fixing structure 188 used, which may be formed for example as a rivet or riveted joint.

One of the attachment structures 188 is for example in the sectional view of 2d recognizable. The spacer 186 is about the attachment structure 134 with which also the management structure 114 or the absorber 110 tumbling with the secondary side 106 of the torsion damper 102 connected to the management structure 114 attached. At the vibration damper unit 110 are circumferentially eight of the mounting structures 134 intended. These may be, for example, a rivet, a spacer bolt or another fastening means. In some other embodiments, not shown, a different number of attachment structures may be provided.

The 5a to 5d show different magnified representations of the absorber vibration damper 110 which describes the individual components in detail. For the sake of clarity, some of the reference numbers relating to details are not transferred to other figures. The absorber vibration damper 110 For example, for a drive train of a motor vehicle for damping a vibration component of a rotational movement, the at least one absorber mass 112 , which is designed to perform a vibration in response to the rotational movement in order to dampen the vibration component thereof. Furthermore, the Tilgerschwingungsdämpfer includes 110 the at least one management structure 114 , opposite to the absorber mass 112 is movably arranged. The absorber vibration damper 110 also includes the at least one rolling element 142 with a mating surface 302 that is designed to work together with a guide surface 304 at least partially the rolling elements 142 to lead, with the guide surface 304 at the absorber mass 112 and / or the leadership structure 114 is arranged, being attached to the guide surface 304 an exemption 306 connects and / or the guide surface 304 an exemption 306 includes. At the time of release 306 This may be, for example, a material removed from the original component in a region of the guide surface 304 or act on it afterwards. For example, the release may be a fillet of an edge or the like.

The absorber mass 112 includes three single-piece masses 307 . 308 and 309 , These are in the axial direction over the example in 2a recognizable absorber mass attachment structure 113 connected with each other. The tread 148 extends over a passage opening 312 in the single-piece masses 307 to 309 , In this case, the passage opening 312 in the axial direction centrally arranged Einzeletilgermasse 308 a larger radius than in the axial direction of the individual Einzeletilgermassen 307 and 309 , The passage opening 312 points in the individual epilogue mass 308 no tread on. The single-piece mass 308 is not in rolling contact with the rolling element 142 ,

The passage opening of the single-piece sealing compound 307 includes the tread 148-a and the through hole in the single-piece sealing compound 309 includes the tread 148-b , These have the same diameter. The absorber mass 112 is like already described, in the axial direction between the two guide structures 114 and 140 , where the management structure 114 the tread 150-b and the leadership structure 140 the tread 150-a includes. The treads 150-a and 150-b also have the same diameter, which is smaller than a diameter of the treads 148-a and 148-b ,

The rolling surface 144 of the rolling element 142 is, analogous to the tread 148 , in two parts 144-a and 144-b divided. These are through a middle area 314 of the rolling element 142 , with a largest diameter of the rolling element 142 , spaced from each other. Analog is also the Wälzfläche 146 of the rolling element 142 into the rolling surfaces 146-a and 146-b divided, which have a smaller diameter than the Wälzfläche 144 and at axially outer ends of the rolling element 142 are located. The rolling element 142 is with its rolling surfaces 144-a and 144-b at the corresponding treads 148-a and 148-b guided. Analog is the rolling element 142 with its rolling surfaces 146-a and 146-b on the treads 150-a and 150-b guided. The rolling element 142 can also be referred to as a step roller having stages between Wälzflächen with different diameters. Furthermore, the rolling element 142 at an outermost end face in an axial direction 316 , a recess 318 on.

Because of the rolling elements 142 , the absorber mass 112 and the leadership structures 114 and 140 are formed substantially symmetrically, is based on the enlarged view of 5b only one side of the rolling element 142 and the corresponding parts of the absorber mass 112 and the leadership structure 114 described. In each case between the rolling surface 146-b and the rolling surface 144-b of the rolling element 142 results from a difference in diameter of the two rolling surfaces 146-b and 144-b , a counterpart surface 302-a , Analog results between the Wälzfläche 144-b and the middle area 314 a mating surface 302-b , The mating surfaces 302-b and 302-a are substantially similar, but are at different diameters of the rolling element 142 arranged and therefore have even different diameters. Based on the enlarged view of 5c and 5d become the mating surfaces 302-b and 302-a described in more detail.

At one, the at least one absorber mass 112 facing side of the management structure 114 , lies the guide surface 304-a , At one, the middle area 314 of the rolling element 142 facing side of the single piece 309 , lies a guide surface 304-b , Analogously, on the other components which have surfaces, the counter-guide surfaces of the rolling body 142 facing, corresponding guide surfaces formed.

The management structure 114 includes on its guide surface 304-a the exemption 306-a , The exemption 306-a is in a radially outer area 320 the tread 150-b in the management structure 114 , with the rolling element 142 with its rolling surface 146-b in a deflected state of the absorber mass 112 is in a rolling contact, smaller than in a radially inner region 322 in which the rolling elements 142 with the leadership structure 114 does not form a rolling contact in a deflected state. This allows the rolling element 142 when in the axial direction with its counterface 302-a at the guide surface 304-a the management structure 114 starts, in the radially outer region 320 in which he also makes a rolling contact with the tread 150-b has received an axial guidance. The radially outer area 320 can also be used as a functional area 342 be designated. The functional area 342 So is the area where the rolling element 142 in a deflected state of the absorber mass 112 So if the absorber vibration damper 110 rotating at a certain speed, with the treads 148 or 150 can be in contact. Because of the exemption 306-a in the radially inner region 322 , outside the functional area 342 , a greater extent than in the functional area 342 may possibly be avoided that in the axial direction in the functional area 342 between the mating surface 302-a and the leadership structure 114 an axial tarnishing and thereby friction arises. The exemption 306-a at least in the functional area 342 in the embodiment of the 5a to 5d a rectangular cross section.

The exemption 306-b is designed essentially analog, but in their position to the functional area 342 the tread 148-b customized. The exemption 306-b is located on the guide surface 304-b attached to one of the leadership structure 114 in the axial direction facing away from the single-piece mass 309 lies. At the running surface 148-b in the absorber mass 112 or the single-shot mass 309 lies the functional area 342 opposite to the functional area 342 at the management structure 114 namely, a radially inner region 324 , In a radially outer area 326 indicates the exemption 306-b a greater extent than in the functional area 342 on.

In the functional area 342 indicates the exemption 306-a , like in the 5c recognizable, then to the guide surface 304-a a radius 334 on. The radius 334 that at least partially enters the opening of the leadership structure 114 that the tread 150-b includes, extends over a conical section 336 with the tread 150-b connected.

The exemption 306-b is essentially how in 5d recognizable, designed analogously, but has a larger diameter. Similarly, the unspecified described and designated exemptions on the opposite side in the axial direction of the central region 314 educated.

The counterpart surface 302-a on the rolling element 142 is over a radius 328 , as in 5c recognizable, with the rolling surface 146-b connected. To the radius 328 concludes a covenant 330 which is directed in an axial direction. Radially outward closes to the waistband 330 a chamfer 332 so that the mating surface 302-a receives a conical section. The Bund 330 has radially outward greater extent than the exemption 306-a , This can, for example, lead to when the rolling elements 142 with the mating surface 302-a in the axial direction on the guide surface 304-a has, the guide surface 304-a and at least the federal government 330 in the area in which they overlap in the radial direction, abut each other. The counterpart surface 302-b , is like in 5b recognizable, designed analog. Likewise, the non-described mating surfaces are formed in a similar manner. In some other embodiments, not shown, the individual counter guide surfaces, guide surfaces and / or exemptions may also differ from each other.

The 3 and 4 show different representations of a vibration damper unit 300 , which also the Tilgerschwingungsdämpfer 110 includes, as well as a torsion damper not described in detail and illustrated, the spring element 108 is recognizable. The torsion damper may be a torsional damper, similar to the torsional damper 102 or to act a torsion damper other construction. Here, the Tilgerschwingungsdämpfer 110 , whose leadership structure 114 in a similar manner as in the embodiment of the vibration damper unit 100 , be connected to the output side or output hub. Optionally, the Tilgerschwingungsdämpfer 110 be connected in other ways with an output side or an input side.

The absorber vibration damper 110 or its absorber mass 112 is essentially analogous to the embodiment of the 5a to 5d formed, but differs by a rolling element 142-z , Identical and similar components are designated by the same reference numerals. Details are only based on the enlarged view of 4 described.

The rolling element 142-z also has mating surfaces, which are denoted by the reference numerals 302-j and 302-k are designated. The counterpart surface 302-j is in the axial direction between the middle area 314 and the rolling surface 144-b arranged. The counterpart surface 302-k is in the axial direction between the rolling surface 144-b and the rolling surface 146-b arranged. Similarly, there are corresponding mating surfaces on the other side of the rolling element 142-z , In this case, the mating surfaces 302-j and 302-k different shapes. The counterpart surface 302-j is conical and has an axial and a radial direction component. The counterpart surface 302-k is completely directed in an axial direction, that expands only in a radial direction and has only one axial direction component. It also has an exemption 306-j at the single-piece mass 309 in the axial direction, outside the functional area a smaller extent, as an exemption 306-k at the management structure 114 ,

In some other embodiments, not shown, the exemptions on the single-piece mass and the guide structure in the axial direction may have the same or similar dimensions. Optionally, the release on the single-piece sealing compound can be dispensed with in some embodiments.

Furthermore, the Tilgerschwingungsdämpfer 110 according to the embodiment of 3 to 4 Insensitivity to a fat on. By means of defined distances between the relatively moving components, adhesion and / or the occurrence of shear forces can for example be reduced or even avoided in some embodiments.

The 6a to 6f show a detailed view of one of the individual parts 307 or 309 , Representative in the following is the single-piece mass 309 described. The single-piece mass 309 has two kidney-shaped passage openings, each of which is the tread 148-b include. Furthermore, the single-penetration mass has 309 also two through holes 342 each for receiving the absorber mass attachment structure 113 serve to the single-piece masses 307 . 308 and 309 to connect with each other.

The exemption 306 is in the enlarged view of the kidney-shaped recess of 6b shown in dashed lines. As can be seen, the exemption points 306 outside the functional area 342 a greater extent than in the functional area 342 on. The functional area 342 lies essentially in the area of the tread, that of a kidney tip 346 opposite. This is the functional area 342 within an angle γ, each starting from the kidney tip 346 , spanned. In some embodiments, the angle γ may have a value between 55 ° and 65 °, for example 60 °.

Outside the functional area 342 can the exemption 306 have a width b ₁ , which is in a range of values from 0.5 mm to 1.2 mm, for example, 0.8 mm. The width b ₁ is an extension of the exemption 306 that differ from the guide surface 304 up to the rolling surface 148-b extends. A depth not shown, that is to say an extension in an axial direction, can be, for example, in a range of values between 1 mm and 5 mm, for example 3 mm. The transitions between the running surface 148-b and the corresponding guide surface 304 may be flat for manufacturing reasons.

In the functional area 342 , such as in 6d recognizable, rejects the exemption 306 a depth t. The depth t may be, for example, a value between 0.2 mm and 0.4 mm, for example 0.3 mm. The depth t is an extension in an axial direction. A width b _{2 of} the exemption 306 in the functional area 342 may for example have a value of 0.1 mm to 0.2 mm or 0.15 mm. The radius 334 may for example be a value of 0.1 mm to 0.3 mm, for example, 0.2 mm.

In some embodiments, the exemption is 306 outside the functional area 342 not like in the 5a to 5d shown formed with a rectangular cross-section, but also has radii and fillets and / or conical sections. For example, the exemption 306 be formed without chamfer or not just include a chamfer or exclusively a conical section.

The 7a to 7e show different views of the leadership structure 140 , which can also be referred to as a track plate. The management structure 140 has an opening arranged concentrically to a central axis M. 350 on. Furthermore, the management structure includes 140 eight kidney-shaped passages that cover the treads 150-a exhibit. The kidney-shaped openings are substantially arranged so that their kidney tip 364 pointing radially inward. In the enlarged view of the 7b is also the exemption 306 shown in dashed lines. Furthermore, the management structure includes 140 four circular through holes 360 which is for attachment to the guide structure 114 serve. In each case between two passage openings 360 are two kidney-shaped recesses with the treads 150-a arranged. The exemption 306 has the same dimensions as for the 6a to 6e described on.

The 8a to 8e show further schematic representations of the management structure 114 , which can also be referred to as a hub disc. The management structure 114 has two in the radial direction opposite arranged Federansteuerstege 374-a and 374-b on. As in 8d recognizable, are the Federansteuerstege 374-a at a different axial height than a radially inner region 372 the management structure 114 , Via an axial section 350 are the spring drive webs 374-a and also 374-b with the radially inner area 372 the management structure 114 connected. In some other embodiments, not shown, the guide structure may be formed without the Federansteuerstege and be connected in any other way with a secondary side of a torsion damper.

Analogous to the management structure 140 also includes the management structure 114 eight, essentially kidney-shaped through-holes, each of which has a tread 150-b includes. Also with the management structure 114 the kidney-shaped passage openings are arranged so that the kidney tip 346 radially inward. Analogous to the management structure 140 also includes the management structure 114 four through holes 360 for connection with the management structure 140 , In each case between two passage openings 360 two kidney-shaped openings are arranged. The above all in the enlarged representations of 8c and 8b recognizable exemption 306 is essentially analogous to the exemptions already described 306 in the absorber mass or the other management structure 140 educated. In some other embodiments not shown, the kidney-shaped recesses and / or the passage openings may not be provided as passage openings, but only as recesses open in an axial direction in the guide structure.

The 9a and 9b show a damper vibration damper 400 , This is essentially similar to the Tilgerschwingungsdämpfer 110 , Identical or substantially identical components or components are therefore designated by the same reference numerals. For example, instead of the Tilgerschwingungsdämpfers 110 in the previously described embodiments of vibration damper units and the Tilgerschwingungsdämpfer 400 be used.

The absorber vibration damper 400 differs from the absorber vibration damper 110 essentially by the exemption. This is at the Tilgerschwingungsdämpfer 400 with the reference numeral 406 designated. In the 9b is the exemption in the management structure 114 shown enlarged and is therefore described with reference to this. At the time of release 406 It is a stamping, which results when the opening, the tread 148 and 150 includes, in the component, so the Einzeltigermassen 307 . 309 or the leadership structures 114 or 140 is introduced or punched. Because of the exemption 406 the punching is, results between the rolling elements 142 which can also be termed a role and leadership structures 114 and 140 and the single-piece masses 307 and 309 another contact geometry. Instead of the stamped exemption 306 Thus, the punching mechanism itself, which is produced during punching, can also be used as rounding, freeing and / or axial contact point. In some other exemplary embodiments, not shown, the release on the single-release body can be produced in a different way than in the guide structure and / or have a different shape and / or size. Optionally, in some embodiments, the relief may include the stamping indentation, which may have been altered by embossing or other methods.

The rolling element 142 has in the embodiment of 9a and 9b a mating surface 402 on, which is conical. When the rolling element 142 in the axial direction on the guide structure 114 starts, he touches, as in the 9b illustrated, with its conical mating surface 402 the exemption 406 , The exemption 406 is therefore part of the guidance surface 304-a , The exemption 406 may have similar dimensions or comparable dimensions as the exemption 306 exhibit. The exemption 406 also indicates, in one area 408 outside the functional area, a larger dimension than in the functional area. The exemption 406 is designed so that a rolling contact area 412 , ie an area in which the rolling element 142 and for example, the tread 150-b in the management structure 114 in the radial direction, in the radial direction the smallest possible distance to a Reibkontaktbereich 410 exhibit. Here is the Reibkontaktbereich 410 the area in which the rolling element 142 in the axial direction with the guide surface 304-a and / or the exemption 406 in contact. This is always a Reibkontaktbereich 410 in a functional area 342 the corresponding Wälzkontaktbereichs 412 , This can be done analogously for the other exemptions and also for the embodiment of 5a to 8e be valid.

Characterized in that this distance in the radial direction, wherein from a radial direction of the rolling body 142 is assumed to be kept as small as possible, in some embodiments, a roller friction can be reduced to a minimum. This may be possible, for example, because a Reibkontaktbereich 410 , which can also be referred to as start-up diameter, so the rolling element 142 to the absorber mass 112 and the rolling element 142 to one of the leadership structures 114 or 140 in the axial direction, only very slightly or slightly larger than the diameter of the Wälzkontaktbereichs 412 of the rolling element is executed in the radial direction itself. The smaller the axial run-up diameter, the lower is the axial friction (M _R = F × r × μ × n).

In order to avoid a foreign friction by an axial contact of the absorber masses on the guide structures, therefore, the following interpretation is usually made, taking into account the tolerance position for Tilgerschwingungsdämpfer. The rolling element leads with its counter-guide surface or its collar, the absorber mass in the axial direction so that at a maximum axial displacement of the small roller collar, ie in the axial direction outside, comes to rest on the guide structure and not on the single-piece mass. If the rolling element comes to rest on the single-piece sealing compound, maximum friction would occur, which is undesirable. Theoretically, no axial forces act on the absorber components. However, due to dynamic effects, such as, for example, crankshaft axial pulses, tumbling and / or geometric or tolerance-dependent component errors, such as alignment or obliquity, slight axial forces may occur which are to be absorbed by the rolling element or its roller axial collars. In order to avoid excessive tilting of the absorber mass with low centrifugal force, so for example at an engine start and / or engine stop, a minimum collar height or a minimum diameter of the counter-guide surface on the rolling element is required. The higher the federal government, the higher the foreign debt that occurs. To avoid this, many counter-guide surfaces or roller collars are tapered or tapered. As a result, the effective radius of the foreign friction again strongly approaches the rolling point of the rolling element itself. Under certain circumstances, however, this can lead to the conical surface of the roller body starting in a punctiform or linear manner with respect to an axial surface of the single-piece sealing compound or the guide structure. This may possibly promote wear, because it can cause higher surface pressures.

In order to reduce this surface pressure and the resulting wear, is in the embodiments of the 3 to 9b the contact surface between the counter guide surfaces and the guide surfaces on the Einzeletilgermassen, which can also be referred to as plates or increases the guide structures. This is done by the transition from the guide surface, too can be referred to as the plate plane, to the tread, which can also be referred to as a career, is rounded. Due to the geometry measures for reducing friction, Coulomb friction can therefore be limited to a minimum during movement of the absorber components in some embodiments.

Furthermore, by the design of the rolling element 142 respectively. 142-z , whose counterfeiting surfaces 302 respectively. 402 , the guide surfaces 304 and the exemptions 306 respectively. 406 In some embodiments, a friction between points with a large relative motion to each other can be avoided. It can therefore in some embodiments, a low-friction storage by supporting the at least one absorber mass 112 over the mating surfaces 302 close to a pitch point or a rolling contact area 412 be enabled. Nevertheless, a Verkippsicherung the absorber mass 112 be obtained via a statically determined state.

10 shows a schematic representation of a method 420 for providing a damper vibration damper 110 or 400 , For example, for a drive train of a motor vehicle for damping a vibration component of a rotational movement. The procedure is in one operation 422 at least one absorber mass 112 , on at least one management structure 114 , movably arranged. For this purpose, at least one rolling element 142 used a counterfeiting surface 302 or 402 having. The absorber mass 112 is configured to vibrate in response to the rotational movement to dampen the vibration component thereof. The mating surfaces 302 or 402 are each designed to work together with a guide surface 304 at least partially the rolling elements 142 to lead axially. In another process 424 will be an exemption 306 or 406 made, so that the exemption 306 or 406 to the guide surface 304 connects or the guide surface 304 the exemption 306 or 406 includes, wherein the guide surface 304 at the absorber mass 112 and / or the leadership structure 114 is arranged.

Of course, the at least one management structure 114 . 140 that have at least one absorber mass 112 and the at least one rolling element 142 as for the embodiments of 3 to 10 described also with other Tilgerschwingungsdämpfern or vibration damper units, which differ from the vibration damper unit 100 or the absorber vibration damper 110 be different, used or implemented.

The exemption 306 . 406 , which can also be referred to as rounding, can, for example, in a punching operation of the treads 148 . 150 , which may also be referred to as a kidney-shaped path, are introduced. For example, this can be done as a pre-embossing, before the actual punching process or as embossing in a calibration process, when the punched kidney shape is calibrated again to improve the surface quality.

The exemption 306 . 406 can be performed radii-shaped, or geometrically optimized. The exemption 306 . 406 , which can also be referred to as an embossment, can, for example, in the functional area 342 , which may also be referred to as web use area, be kept smaller than at a rest of the tread 148 . 150 , which can also be referred to as kidney contour. The rolling element 142 so for example, only in the functional area 342 , which may also be referred to as Abrollstrecke, have an axial contact and not on the remaining surfaces. As a result, for example, an additional foreign friction can be prevented.

The 11 to 12 show the structure of an absorber mass 430 , which can also be referred to as Tilgerfliehgewicht. The absorber mass 430 has at least three single-shot masses 431 . 432 and 433 on. The two outer single-piece masses 431 and 433 , which may also be referred to as external panels, are hardened. The entire composite is pinned or riveted, for example, with an absorber mass attachment structure 434 , Before pinning, the two rolling elements 142 One of them is enlarged in the 13 shown, inserted. The rolling element 142 is designed as a so-called stepped roller.

In a middle area 314 , which can also be referred to as the center region, has the rolling element 142 the largest diameter. This is in the middle single-piece mass 432 , which is uncured, a roller conveyor freed. It has no role management function. The middle single-shot mass 432 has only the task to represent the absorber mass, for example as a spacer to the two outer Einzeletilgermassen 431 and 433 , In a rolling movement of the middle range 314 of the rolling element 142 it can lead to an axial start of a middle federal government 436 , which can also be referred to as a central collar, to the respective outer individual shotgun masses 431 and 433 come. This is undesirable, but often unavoidable. This often creates a foreign friction. A similar effect occurs when the two outer coil collars 435 start at the management structures. This problem is solved by the previously described embodiments.

The 14a to c show different representations of a vibration damper unit 470 , which also as a two-mass flywheel with an internal absorber vibration damper 472 can be designated. The vibration damper unit 470 is substantially similar or analogous to the already described vibration damper units and includes in addition to the Tilgerschwingungsdämpfer 472 also a torsion damper 474 , This is a torque on a housing 476 as a primary side on at least one spring element 478 transfer. About the at least one spring element 478 is a secondary side 480 with the housing 476 coupled. The secondary side 480 also includes a leadership structure 482 for at least one absorber mass 484 of the absorber vibration damper 472 , The management structure 482 of the absorber vibration damper 472 is via a connection structure 486 , which may be formed for example as a rivet, with a driven side 488 connected, so that a torque is transmitted.

The absorber vibration damper 472 includes another leadership structure 490 which is in the axial direction opposite to the guide structure 482 is arranged. The at least one absorber masses 484 is between the leadership structures 482 and 490 arranged in the axial direction. Motor side, so one of the housing 476 facing side of the management structure 490 , which can also be referred to as a track plate, is on the management structure 490 a thin-walled fender 492 applied or arranged adjacent in the axial direction.

The fender 492 points, such as in 14b recognizable, an axial section 494 which extends substantially in an axial direction and a radial portion 496 which extends substantially in a radial direction.

The fender 492 is designed so that there is an area in which the absorber masses 472 move, with the axial section 494 bounded radially inward. The fender 492 protrudes in a radially outer region close to the guide structure 482 , which may also be referred to as a hub disc, in order to prevent grease on the at least one damper mass or other Tilgerbauteile.

Further, with the fender 492 also kidney-shaped openings in the guide structure 490 covered, which include the treads and in the 14a to 14c are not recognizable. In a radially inner region, the fender extends 492 with the axial section 494 to a transmission side, forming a cylinder. On the axial section 494 or the cylinder thus formed is a support ring 498 coated or sprayed with an elastomeric layer. The support ring 498 is formed so that it in the axial direction of the guide structures 490 and 482 touched or in contact with them.

In other words, the support ring 498 axially up to the guide structures 490 and 482 introduced to the Tilgerschwingungsdämpfer 474 radially inside seal. In some embodiments, for example, to effect a bias, an O-ring 500 be used. This can, for example, at a bend of the mudguard 492 in which the axial section 494 and the radial section 496 meet, be inserted.

To an interior of the vibration damper unit 470 in addition to seal, is radially inside, the motor side, a plastic disc spring seal 502 intended. After radially outward is a sealing effect on another disc spring 504 realized, which is arranged on the transmission side. The plastic plate spring gasket 502 is located substantially at an axial height to the support ring 498 and supports in the axial direction between the housing 476 and the fender 492 from.

The diaphragm spring preload of the diaphragm spring 504 and the plate spring of the plastic plate spring gasket 502 each can be independent because of a ball bearing 506 for a fixed axial position of the primary side or the housing 476 to the secondary side 480 provides. In some other embodiments, not shown, in which the vibration damper unit instead of the ball bearing comprises a plain bearing or a sliding bearing is provided, the two disc springs may be in a balance of forces.

The 15 shows a further embodiment of a vibration damper unit 510 , This is substantially similar to the vibration damper unit 470 , The same or similar components are therefore designated by the same reference numerals.

Instead of the ball bearing of the embodiment of 14a to 14c is at the vibration damper unit 510 a plain bearing 512 intended. Because the plain bearing 512 is used, the secondary-side components, so the absorber vibration damper 472 or its management structure 482 in the axial direction to the primary side or to the housing 476 fixed. This is the leadership structure 482 on both sides, each with a plate spring 514 and 516 applied. The plate spring 516 rests between the housing 476 and the secondary side 480 or the management structure 482 from. The plate spring 514 is supported by a cover component 518 that stuck to the case 476 is connected, also on the housing 476 from. In other words, the cup springs are based on the primary side Component off. The two cup springs 514 and 516 are in an equilibrium of forces and center radially, primary or secondary side. In a fitted condition, this will cause a release preload for the left cup spring 516 pressed until the axial bearing is on "block". This assumes that a release preload force plus a Belleville spring force of the right belleville spring 514 is greater than a maximum force of the left plate spring 516 ,

The 16a and 16b relate to another vibration damper unit 520 , This is essentially similar to the vibration damper units 100 . 470 or 510 , The same or similar components or components are therefore designated by the same reference numerals. The vibration damper unit 520 also includes the torsion damper 474 and the absorber vibration damper 472 , The absorber vibration damper 472 comprises four absorber masses arranged in the circumferential direction 484 , each with two rolling elements 142 along the management structure 482 are movably guided.

To dampen the absorber masses 484 , which may also be referred to as absorber weights when they fall radially inward, comprises the vibration damper unit 520 at least one support ring 522 , The support ring 522 is formed as a cylindrical member having a circular cross-section and includes, such as in the enlarged section of 16d recognizable, two different layers 524 and 526 , The radially outer layer 524 comprises or consists entirely of an elastic material, for example an elastomer or an elastomer layer or a rubber. The radially inner layer 526 comprises as a material a carrier layer or a carrier material. As a carrier material, for example, polyamide (abbr .: PA) or a polyamide material can be used. In some embodiments, the support ring 522 produced in a two-component technique (abbr .: 2K-technology) or another injection molding process. The radially inner layer 526 points, as in the 16b recognizable, a radially outward toothing 528 on. For example, the support ring may be formed without the teeth.

At its directed in an axial direction M edges 530 and 532 has the support ring 522 each one radially outwardly directed chamfer 534 and 536 , as well as each radially inward chamfer 538 and 539 on. In this case, the radially outer chamfers extend 534 and 536 further in an axial direction M, as the radially inner chamfers 538 and 539 ,

The support ring 522 or a plurality of support rings, for example, to a cylindrical component 523 , as in 16c recognizable, be raised with a radial play. This radial clearance, in some embodiments, may allow the support ring 522 when the at least one absorber mass hits 484 performs a rotational movement, because a striking of one of the absorber masses 484 on the support ring 522 usually generates a radial and a tangential force. The twist can be only a few degrees. By the rotation of the support ring 522 can be an impact on the support ring 522 reduced and the place of impact of the absorber mass 484 on the support ring 522 be changed with different contacts. An abutment damping thus takes place via a stop ring radially inside. In some embodiments, such a uniform distribution of wear on the support ring 522 be enabled.

At the vibration damper unit 520 takes place as in the 16a and 16b recognizable, yet another Endlagenfixierung the absorber masses 484 via a spacer bolt 542 , The spacer bolt 542 is with an elastic layer 544 , For example, an elastomer encased. The elastic layer 544 can be sprayed, stuck and / or pressed on. The spacer bolt 542 can be in all possible ways on the leadership structure 482 be attached.

Each in the circumferential direction between two directly adjacent absorber masses 484 is a spacer bolt 542 arranged. The end position fixation over the spacer bolt 542 can with some vibration damper units 520 prevent or at least reduce the risk that the rolling elements 142 in the absorber mass 484 a track length of the treads 150 respectively. 148 completely "extends". Instead, the absorber mass 484 a few degrees before being "slowed down".

The 16e shows another support ring 550 , This is essentially analogous to the support ring 522 formed and also includes the two layers 524 and 526 , These are connected to each other without teeth, but may also have a toothing in other variants. The support ring 550 points, in contrast to the support ring 522 no cylindrical shape with a circular cross-section, but a polygonal shape. A surface 551 of the support ring 550 has a corrugated or wavy shape. This allows the support ring 550 obtained resilient or elastic properties.

The 16f and 16g show different cross-sectional views of a support ring 555 , This has only one layer, but as a variant analogous to the support rings 522 or 555 also be formed multi-layered. The support ring 555 has a cylindrical section 556 and a conical section 557 on, in the axial direction M to the cylindrical portion 556 followed. The support rings 550 and 555 can be essentially analogous to the support ring 522 on the vibration damper unit 520 or other vibration damper units.

The 17a and 17b show different representations of an absorber vibration damper 560 , The absorber vibration damper 560 is substantially similar to the Tilgerschwingungsdämpfer 110 of the 2a and 2 B educated. Identical or similar components are therefore designated by the same reference numerals. For reasons of clarity, reference is made to the reference symbols of the individual components of the tumble decoupling structure 116 waived. The absorber vibration damper 560 differs from the absorber vibration damper 110 through a support ring 562 instead of the support body 154 ,

The support ring 562 includes a plurality of straight sections 564 , In each case two circumferentially adjacent sections 564-a and 564-b are over a plug-in section 566 connected with each other. The plug-in section 566 is curved radially outwards. As in the enlarged view of 17b better recognizable, includes the support ring 562 in each of its plug sections 566 a passage opening 568 , The support ring 562 can be designed as a two-component component or 2K variant. The support ring 562 includes a support ring carrier 570 and on its radially outwardly directed surface a coating 572 , As a material, the support ring carrier 570 For example, comprise a polyamide or a polyamide material. The coating 572 may include, for example, an elastomer as a material. A radially inward surface 574 of the support ring 562 or the support ring carrier 570 is cylindrical.

Also analogous to the Tilgerschwingungsdämpfer 110 also includes the Tilgerschwingungsdämpfer 560 a plurality of attachment structures 138 , These serve a further, not shown, guide structure, which can also be referred to as a track plate, with the guide structure 114 in the axial direction opposite, so that the absorber masses 112 are received in the axial direction between the two guide structures. At the absorber vibration damper 560 of the 17a to 17c becomes the support ring 562 at the attachment structures 138 , which may also be referred to as spacer bolts, fixed radially and tangentially. The support ring 562 is at the attachment structures 138 attached. One attachment structure each 138 protrudes through one of the passage openings 568 in the support section 566 ,

The at least one absorber mass 112 may in some embodiments flat with a straight inner surface 576 on the straight section 564 , which can also be referred to as a straight support ring surface strike. At the same time and / or before reaching a rolling end position in the tread 148 , which can also be referred to as a kidney, beats the absorber mass 112 with its outer contour on the coating 572 on, showing the attachment structure 138 surmounted.

17c shows a vibration damper unit 580 which is essentially analogous to the vibration damper unit 100 is formed and next to the Tilgerschwingungsdämpfer 560 according to the embodiment of 17a and 17b also the torsion damper 102 having.

The 18a to 18c show further different representations of a vibration damper unit 600 which a torsion damper 602 and a damper vibration damper 618 includes. A housing 604 as the first primary side is via a plurality of radially outer spring elements 606 with a first secondary side 608 coupled. With the first secondary side 606 is arranged on radially further inside, further spring elements 610 a second secondary side 612 rotatably coupled.

The second secondary side 612 , from both sides to the radially inner spring elements 610 arranged cover sheets is provided via a mounting structure 614 at a management structure 616 of the absorber vibration damper 618 attached. To the management structure 616 is in the axial direction opposite another guide structure 620 arranged. Between the leadership structures 616 and 620 is at least an absorber mass 622 each with two rolling elements 624 guided. These each roll in two treads 626 the management structure 620 from. Also the absorber mass 622 includes treads 628 , in the rolling elements 624 intervention.

The absorber mass 622 includes a significantly extended in the axial direction dowel pin 630 , At the dowel pin 630 it is a mounting structure, with the three Einzeletilgermassen 631 . 632 and 633 to the absorber mass 622 are connected. The dowel pin 630 has in a axial direction M a greater extent than the absorber mass 622 on. The dowel pin 630 extends axially into the guide structures 620 and 616 , which can also be referred to as web sheets. The dowel pin 630 has at its ends, in the axial direction 637 and 638 lie, each having a larger diameter than in a central region of the dowel pin 630 , In the middle area of the passport 630 with the smaller diameter, are in one assembled state the individual absorber masses 631 to 633 , The axial end 637 can be attached to a middle area of the passport 630 For example, after this through the single-piece masses 631 to 633 was guided, plugged or fastened. At its axial ends 637 and 638 can the dowel pin 630 each have a rubber jacket or Elastomerummantelung.

In the embodiment of the 18a and 18c have the leadership structures 616 and 620 radially outward a plurality of kidney-shaped contours 636 on. The kidney-shaped contour 636 is each directed radially outward and serves as an attachment for a dowel pin 630 , The kidney-shaped contour 636 is open radially outward. With the axial ends 637 and 638 becomes the dowel pin 630 in an assembled state to the kidney-shaped contours 636 guided. The kidney-shaped contours 636 allow movement of the absorber mass 622 , which can also be referred to as absorber movement, in a normal operation without contact.

When starting the engine or stopping the engine, it may happen that the absorber mass 622 leaves an ideal track. In such situations, the absorber mass 622 over the rubber coated dowel pins 630 close to the track sheet contour or the kidney-shaped contours 636 be guided. This is a movement of the absorber mass 622 in the circumferential direction, ie before reaching a tail 640 with the rolling element 624 limited because of the axially larger diameter at the ends 637 and 638 of the passport 630 or the elastomer previously tangential to the guide structures 620 and 616 attacks.

The 18d and 18e show another Tilgerschwingungsdämpfer 650 , This is essentially analogous to the Tilgerschwingungsdämpfer 618 trained, however, differs in the formation of the kidney-shaped contour. Also with the absorber vibration damper 650 include the leadership structures 620 and 616 kidney-shaped contours 652 , In contrast to the radially outward open kidney-shaped contours 636 are the kidney-shaped contours 652 at the absorber vibration damper 650 completely off the leadership structure 620 or 616 or their material enclosed. In other words, the kidney-shaped contours 652 closed radially outward. It is thus in contrast to the vibration damper unit 600 , in which a stop on the outer contour is effected, allows a stop in recesses.

With both absorber vibration dampers 618 and 650 a stop of the absorber masses takes place 622 over the dowel pins 630 , which may also be referred to as stop pins on the guide structures 616 and 620 , which can also be referred to as Tilgerträger. The axial ends 637 and 638 of the passport 630 can be formed either as an elastomer in one piece or as an O-ring. It can be at each of the ends 637 and 638 in each case an O-ring can be used.

18f shows a Tilgerschwingungsdämpfer 660 , which is essentially analogous to the Tilgerschwingungsdämpfern 618 and 650 is formed, however, a contour 662 along the the dowel pins 630 the absorber mass 622 lead, differs. The contour 662 is open radially outward. It is at the contour 662 around a radially outwardly directed outer contour of the guide structures 620 and 616 , The contour 662 has a waveform and extends completely over an area that the two dowel pins 630 one of the absorber masses 622 can take in the circumferential direction. Thus, the same or a similar effect can be achieved as with the kidney-shaped contours 636 However, this may be a sheet metal or a guide structure 620 be used with a smaller outer diameter. In other words, the contour can 662 For example, be used when an outer diameter of the guide structures 620 and 616 the kidney recess 636 or even the slit-shaped kidney recess 652 of the 18 does not allow.

19a shows a schematic perspective view of a damping mass 670 , The absorber mass 670 includes three single-piece masses 671 . 672 and 673 , In this case, a material which is in the axial direction of the internal single-shot mass 672 , an elastomer. In other words, between the two outer Einzeletilgermassen 671 and 673 , which can also be referred to as external flyweights, an elastomer clamped.

The elastomer or the internal single-piece sealant 672 extends radially inward to a tangential region 676 the absorber mass 670 , The tangential area 676 the absorber mass 670 is the area with which the absorber mass 670 can come into contact with a support body. The elastomer or the internal single-shot mass 672 has a greater extent radially inward than the outer Einzeletilgermassen 671 and 673 , The single-piece masses 671 to 673 are over two attachment structures 675 connected with each other. The attachment structure 675 may be formed, for example, as a rivet. The absorber mass 670 includes two treads 686 for two rolling elements 684 to the absorber mass 670 to lead a leadership structure. An impact damping can be achieved via a stop buffer radially inside the absorber mass 670 respectively.

19b shows a Tilgerschwingungsdämpfer 680 with four absorber masses 682 , These are each about two rolling elements 684 , each in a tread 686 the absorber mass 682 run, moving on a leadership structure 688 guided. Like in the 19c recognizable, includes the absorber mass 682 two single-piece weights 690 and 692 , Between the individual parts 690 and 692 is a support section 694 arranged or clamped. The absorber mass 682 may have a lower mass, which may also be referred to as Fliehgewichtsmasse, as absorber masses of other types. This difference can be for example 4%. The single-piece masses 690 , and 692 and also the support section 694 each have an elastomeric coating on their radially inwardly directed surfaces 696 on. In this case, the support section protrudes 694 further radially inward than the Einzeletilgermassen 690 and 692 , This allows the support section 694 For example, act as a support body or support ring. In other words, is at the absorber mass 682 a support ring as a support section 694 at the absorber mass 682 or is clamped to this.

The 19d shows a further schematic representation of a perspective view of a Tilgerschwingungsdämpfers 700 , This is essentially analogous to the Tilgerschwingungsdämpfer 680 trained, but includes a damping mass 702 extending from the absorber mass 682 different. Also the absorber mass 702 includes two single-piece weights 692 and 690 , Between the individual parts 692 and 690 is also a support section 704 clamped. Also the absorber mass 702 may have a lower mass compared to other absorber masses. The difference can be, for example, 5%. The support section 704 has a T-profile in a cross-section. As a result, the support section 704 a larger impact surface 706 as the support section 694 on. The impact surface 706 is a radially inwardly directed surface of the support portion 704 , whose extension in an axial direction of an axial extension of the absorber mass 702 equivalent. The support section 704 points both at its sides directed in the axial direction 708 and 709 , which in the radial direction to the Einzeletilgermassen 690 and 692 connect as well as at the impact surface 706 an elastomeric coating 710 on.

In other words, the absorber masses 670 . 682 and 702 all include or wear the elastomeric material for impact and / or cushioning. It is essentially in a radially inner region of the absorber mass 670 . 682 or 702 sandwiched or injected between the outer individual sealant masses, which may also be referred to as outer plates. The elastomeric material extends into the tangential region of the absorber mass 670 . 682 or 702 to the Endlagenbedämpfung to a spacer bolt 711 display. Depending on the required damper work or a damping volume of the elastomer, the support portion or the elastomer is wider, based on an expansion in an axial direction as in the absorber mass 702 or narrower, as with the absorber masses 670 and 682 , executed. In a radially inner area 712 the absorber vibration damper 680 or 700 can the absorber masses 670 . 682 or 702 or their elastomer layer 710 . 696 or 672 hit a good sliding material, which can still rotate about a rotation axis. For example, it may be a ring made of a polyamide.

The vibration damper units or Tilgerschwingungsdämpfer the described embodiments have different guide structures, which may also be formed as a web plates and / or hub disc. For a good Tilgerfunktion it may be necessary that the guide structures have very low flatness deviations and especially in the radial direction no position deviations. Such flatness deviations and positional deviations can sometimes occur after a case hardening process. In order to prevent this, a so-called "fixture hardening" is used to harden the guide structures. This is a hardening process for management structures with a absorber function.

The hardening process has the following process sequence: After carburizing, the glowing component, ie the guide structure, is guided in a hardening device via a precisely fitting, axially slotted receiving mandrel to an inner diameter and then clamped axially between plates. Subsequently, the management structure is quenched. In this case, a guide structure inner diameter, which can also be referred to as a partial inner diameter, shrinks on the receiving mandrel. Thus, in the curing process, the kidney-shaped recesses forming the treads may be maintained at their desired and intended positions. It should therefore be prevented that they "forgiven" themselves in a radial position. With a high axial force then the guide structure or the component can be removed from the mandrel. The guide structure is then level and exact position.

The embodiments disclosed in the foregoing description, the appended claims and the appended figures, as well as their individual features, may be relevant and implemented both individually and in any combination for the realization of an embodiment in its various forms.

LIST OF REFERENCE NUMBERS

100

vibration unit

102

Dampers

104

primary

106

secondary side

108

spring element

110

Tilgerschwingungsdämpfer

112

absorber mass

113

Tilgermassenbefestigungsstruktur

114

management structure

116

Swash decoupling structure

118

output side

120

output hub

122

sprocket

123

direction of rotation

124

deck component

126

shell

128

spring range

130

Federelementansteuerschuh

132

Federansteuersteg

134

attachment structure

136

reduction

137

attachment section

138

attachment structure

140

second management structure

142

rolling elements

144

rolling surface

146

rolling surface

148

tread

150

tread

154

support body

156

fastening eye

157

Thighs outside

158

support section

159

parallel leg

160

embossed structure

161

parallel leg

162

Part decoupling component

163

Through opening

164

Part decoupling component

165

leg

166

Abtriebsnabenflansch

168

wing

170

Area between wings

172

Output attachment receiving portion

174

Management structure ahead

176

concave inward arched section

178

wing edge

180

Output attachment structure

182

Swash decoupling connection lead

184

Output Mounting fixture

186

spacer

188

attachment structure

300

vibration unit

302

Mating face

304

guide surface

306

exemption

307

Einzeltilgermasse

308

Einzeltilgermasse

309

Einzeltilgermasse

312

Through opening

314

middle area

316

face

318

recess

320

radially outboard area

322

radially inward area

324

radially outboard area

328

radius

330

Federation

332

chamfer

334

radius

336

conical section

342

functional area

346

kidney tip

350

opening

360

opening

372

radially inward area

374

Federansteuersteg

400

Tilgerschwingungsdämpfer

402

Mating face

406

exemption

408

Area outside functional area

410

frictional contact

412

Wälzkontaktbereich

420

method

422

process

424

process

430

absorber mass

431

Einzeltilgermasse

432

Einzeltilgermasse

433

Einzeltilgermasse

434

attachment structure

435

Roll collar outside

436

middle fret

470

vibration unit

472

Tilgerschwingungsdämpfer

474

Dampers

476

casing

478

spring element

480

secondary side

482

management structure

484

absorber mass

486

connecting structure

488

output side

490

management structure

492

mudguard

494

axial

496

radial section

498

support ring

500

O-ring

502

Plastic disc spring seal

504

Belleville spring

506

ball-bearing

510

vibration unit

512

bearings

514

Belleville spring

516

Belleville spring

518

deck component

520

vibration unit

522

support ring

523

cylindrical component

524

radially outer layer

526

radially inner layer

528

gearing

529

support ring

530

edge

532

edge

534

chamfer

536

chamfer

538

chamfer

539

chamfer

542

Spacer stud

544

elastic layer

550

support ring

551

surface

555

support ring

556

cylindrical section

557

conical section

560

Tilgerschwingungsdämpfer

562

support ring

564

section

566

plug-in section

568

Through opening

570

Support ring carrier

572

coating

574

Surface radially inside

576

palm

580

vibration unit

600

vibration unit

602

Dampers

604

casing

606

spring element

608

secondary side

610

spring element

612

second secondary side

614

attachment structure

616

management structure

618

Tilgerschwingungsdämpfer

620

management structure

622

absorber mass

624

rolling elements

626

tread

628

tread

630

dowel

631

Einzeltilgermasse

632

Einzeltilgermasse

633

Einzeltilgermasse

636

kidney-shaped open contour

637

End of passport

638

End of passport

640

tail

650

Tilgerschwingungsdämpfer

652

kidney-shaped contour

660

Tilgerschwingungsdämpfer

662

contour

670

absorber mass

671

Einzeltilgermasse

672

Einzeltilgermasse

673

Einzeltilgermasse

675

attachment structure

676

tangential area

680

Tilgerschwingungsdämpfer

682

absorber mass

684

rolling elements

686

tread

688

management structure

690

Einzeltilgermasse

692

Einzeltilgermasse

694

support section

696

elastomer layer

700

Tilgerschwingungsdämpfer

702

absorber mass

704

support section

706

impact surface

708

side surface

709

side surface

710

elastomer layer

711

Spacer stud

712

radially inward area

M

axial direction

d

Inner diameter sprocket

D

Inner diameter envelope space absorber mass

t

depth

b ₁

Wide release

b ₂

Wide release

γ

Angle functional area

R

radial direction

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102010054297 A1 [0004]

Claims (15)

Tailstock vibration damper ( 110 ), for example for a drive train of a motor vehicle, for damping a vibration component of a rotational movement, having the following features: at least one absorber mass ( 112 ) configured to vibrate in response to the rotational movement to dampen the vibration component thereof; at least one management structure ( 114 ) against which the absorber mass ( 112 ) is movably arranged; and at least one rolling element ( 142 ) with a mating surface ( 302 ), which is designed to work together with a guide surface ( 304 ) at least partially the rolling element ( 142 ) axially; the guide surface ( 304 ) at the absorber mass ( 112 ) and / or the management structure ( 114 ) is arranged, wherein to the guide surface ( 304 ) an exemption ( 306 . 406 ) and / or the guide surface ( 304 ) an exemption ( 306 . 406 ). Tune vibration damper according to claim 1, wherein the exemption ( 306 . 406 ) directly to the guide surface ( 304 ) and / or the exemption ( 306 . 406 ) running around to a tread ( 148 . 150 ) for the rolling element ( 142 ) is arranged. Tune vibration damper according to one of the preceding claims, wherein the exemption ( 406 ) comprises a punching device. Tune vibration damper according to one of the preceding claims, wherein the exemption ( 306 ) is at least partially produced by embossing. Tune vibration damper according to one of the preceding claims, wherein the exemption ( 306 . 406 ) includes a radius. Tune vibration damper according to one of the preceding claims, wherein the exemption ( 306 . 406 ) in a functional area ( 342 ), in which the rolling element ( 142 ) in a deflected state of the absorber mass ( 142 ) a rolling contact area ( 412 ) is smaller than outside the functional area ( 342 ). Tune vibration damper according to one of the preceding claims, wherein the exemption ( 306 . 406 ) in the axial direction of the guide surface ( 304 ) has a depth which has at least a value of 0.2 mm. Tune vibration damper according to one of the preceding claims, wherein the exemption ( 306 . 406 ) from a tread ( 148 . 150 ) to the guide surface ( 304 ) has at least an extension of 0.1 mm. Tune vibration damper according to one of the preceding claims, wherein the rolling element ( 142 ) is designed as a stepped roller and at least two rolling surfaces ( 144 . 146 ), which have different diameters. Tune vibration damper according to one of the preceding claims, wherein the counter-guide surface ( 302 ) of the rolling element ( 142 ) is conically formed at least in sections. Tune vibration damper according to one of the preceding claims, wherein a distance in the radial direction between a Wälzkontaktbereich ( 412 ), in which the rolling element ( 142 ) and the absorber mass ( 112 ) or the rolling elements ( 142 ) and the management structure ( 114 ) in the radial direction and a Reibkontaktbereich ( 410 ), in which the rolling element ( 142 ) and the absorber mass ( 112 ) or the rolling elements ( 142 ) and the management structure ( 114 ) in the axial direction, maximum 1 mm. Procedure ( 420 ) for providing a Tilgerschwingungsdämpfers ( 110 ), for example, for a drive train of a motor vehicle, for damping a vibration component of a rotational movement, having the following features: Movable Arranging ( 422 ) at least one absorber mass ( 112 ), which is designed to perform a vibration in response to the rotational movement in order to dampen the vibration component thereof, on at least one guide structure (FIG. 114 ), by means of at least one rolling element ( 142 ), which has a mating surface ( 302 ), which is designed to work together with a guide surface ( 304 ) at least partially the rolling element ( 142 ) axially; and manufacturing ( 424 ) an exemption ( 306 . 406 ), so that the exemption ( 306 . 406 ) to the guide surface ( 304 ) or the guide surface ( 304 ) the exemption ( 306 . 406 ), wherein the guide surface ( 304 ) at the absorber mass ( 112 ) and / or the management structure ( 114 ) is arranged. The method of claim 14, wherein the manufacturing ( 424 ) of the exemption ( 306 . 406 ) when producing a tread ( 148 . 150 ) with a punching process, so that the punching indentation the exemption ( 406 ) is or comprises. The method of claim 12, wherein the manufacturing ( 424 ) the exemption ( 306 ) by means of an embossing process. The method of claim 14, wherein the coining of the exemption ( 306 ) before and / or after the introduction of a tread ( 148 . 150 ) for the Rolling elements in the absorber mass ( 112 ) and / or the management structure ( 114 ) he follows.

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