WO2015165670A1

WO2015165670A1 - Tuned mass damper

Info

Publication number: WO2015165670A1
Application number: PCT/EP2015/056831
Authority: WO
Inventors: David Förster
Original assignee: Zf Friedrichshafen Ag
Priority date: 2014-04-28
Filing date: 2015-03-30
Publication date: 2015-11-05
Also published as: DE102014207957A1; EP3137788A1

Abstract

A tuned mass damper (110, 238), for example, for a powertrain of a motor vehicle, for damping an oscillation portion of a rotary motion, comprises at least one tuned mass (112) designed to perform an oscillation according to the rotary motion in order to damp the oscillation portion thereof. Furthermore, the tuned mass damper (110, 238) comprises at least one guide structure (114, 140) designed to guide the tuned mass (112) in a movable manner. The tuned mass damper (110, 238) comprises at least one support body (154) designed to come in contact with an outer contour (192) of the tuned mass (112) in at least one support region (194), wherein the support region (194) is inside an average extension (198) of the tuned mass (112), wherein the average extension (198) comprises a maximum 80% portion of a length (200) of the tuned mass and is arranged symmetrically to the centre of gravity (196) of the tuned mass (112).

Description

Tilgerschwingungsdämpfer

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.

In the field of automotive engineering, but also in other areas of mechanical and plant engineering damper assemblies or vibration damper units are used, which are used for damping at least one vibration component of a rotary motion and optionally for transmitting a torque of the rotary motion. 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.

Tilgerschwingungsdämpfer there are different embodiments. In most cases, at least one absorber mass is movably guided in relation to at least one guide structure in order to execute a vibration in response to the rotational movement in order to dampen the vibration component thereof. To avoid that two absorber masses abut each other or fall radially inward at too low speeds, some Tilgerschwingungsdämpfer on a support ring, the support region to the absorber masses rotationally symmetrical about a guide structure for the absorber mass is. The support ring may possibly be provided for other reasons. In some operating states, for example at low rotational speeds, it may happen that the at least one absorber mass is deflected maximally in relation to the at least one guide structure. It can then happen that the at least one absorber mass strikes the guide structure. This may cause noise, which is undesirable. In these cases, a soft support of the absorber masses may also be necessary, for example via the support ring, to prevent the absorber masses are deflected too far.

The support ring or a contact of the absorber mass with the support ring can cause the absorber mass to tilt about an axis which is parallel to an axis of rotation of the absorber vibration damper. It may thereby happen that one of the rolling elements, which guides the absorber mass movably with respect to the guide structure, loses contact with the guide structure or the absorber mass or lifts it off a running surface in the absorber mass or in the guide structure. In a subsequent impact of the rolling element on the corresponding component, a stop noise may occur. These impact noises are undesirable.

Such torsional vibration dampers are described for example in DE 10 2009 042 836 A1. In the Tilgerschwingungsdämpfern described therein stop bumpers are provided to prevent tilting of the absorber masses.

In the area of corresponding damper 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 design, function and other parameters. For example, there is a need to improve a compromise on space, friction, ease of manufacture, and noise of a damper assembly.

This requirement is borne by a Tilgerschwingungsdämpfer according to claim 1 bill. A Tilgerschwingungsdämpfer according to an embodiment, 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, which is designed to perform in response to the rotational movement to a vibration to dampen the vibration component thereof. Furthermore, the Tilgerschwingungsdämpfer comprises at least one guide structure which is adapted to movably guide the absorber mass and at least one support body which is adapted to contact an outer contour of the absorber mass, in at least one support region, wherein the support region within an average extent the absorber mass is, wherein the average extent has a proportion of not more than 80% of an absorber mass length and is arranged symmetrically to the center of gravity of the absorber mass.

Due to the fact that the support area lies within an average extent of maximally 80% of the absorber mass, in some embodiments it can be made possible that the tilting of the at least one absorber mass can be at least reduced or even completely prevented. The at least one absorber mass does not tip, for example, if a moment balance on the absorber mass is zero. The support body is thus designed and arranged to come into contact with the absorber mass in the support region such that a force exerted on the absorber mass via the support body or introduced into the absorber mass results in a moment balance of zero on the at least one absorber mass. The torque balance can also be close to zero, then the tilting is less reduced.

In some embodiments, the at least one absorber mass is guided over at least one rolling element on the guide structure. The absorber masses can roll on the rolling elements in some Tilgerschwingungsdämpfern. The rolling element can in turn roll on the guide structure. Thereby, the Tilgerschwingungsdämpfer perform a harmonic oscillating motion, which may be directed against a vibration component of a rotational movement or a stimulating torque to dampen them. For example, tilting the absorber mass can lead to the rolling body lifting off the running surface of the absorber mass or the running surface of the guide structure. If the rolling element then strikes the tread again, an impact noise may occur. Because the at least one Tilgermasse is supported by the support body in the support area so that the tilting is avoided, the lifting of the rolling body from the tread can be at least reduced or even completely avoided. As a result, resulting noise can be reduced or even completely avoided.

For example, an outer contour of the component is not in a passage opening or recess which is introduced in the component. The outer contour can be, for example, a surface or contour of the absorber mass which is directed essentially in a radial direction and / or has a radial directional component.

In some other embodiments, the support region may be within an average extension corresponding to a maximum of 60% or even a maximum of 50% of the absorber mass length. Depending on the shape of the at least one Tilger mass can be avoided in some embodiments in a contact between absorber mass and support body so that the absorber mass rotates.

Optionally, in some embodiments, the at least one support region lies exclusively within the extension. In some embodiments, it can thus be avoided that support areas lying outside the expansion can lead to a tilting of the absorber masses.

In addition or as an alternative, the at least one support region in some exemplary embodiments is located on an outer contour, which is directed radially inward, of the absorber mass. In some embodiments, it can thus be made possible that a deflection of the absorber mass radially outward is not restricted by the support body. Optionally, in some embodiments, the at least one support region can also lie on a radially outwardly directed outer contour of the absorber mass.

Additionally or alternatively, in some embodiments, the at least one support body and the at least one absorber mass are formed in order to come into contact with one another in at least two different support areas. In some embodiments, a supporting behavior of the support body can thereby be limited to Different operating conditions of Tilgerschwingungsdämpfers be adjusted. For example, the absorber mass and the support body in a first support area in operation at a first speed and in a second support area in an operation at a second speed in contact. Under certain circumstances, the first speed may be less than the second speed. In some embodiments, the support regions may also overlap at least partially.

Additionally or alternatively, the at least one support region is in some embodiments at least one point, at least one line and / or at least one surface. In some embodiments, by a shape of the support region, a tilting of the absorber mass can be avoided.

Additionally or alternatively, in some embodiments, the support body has at least two support sections that have different stiffnesses. In some embodiments, this can be used to determine or specify a shape of the support region that forms between the absorber mass and the support body. For example, the support sections may deform elastically to different degrees during an action of a force or in contact with the absorber mass. In some embodiments, at least one of the support portions may have an elasticity of 100 N / mm. The elasticity of other support sections on the same support body may be larger, smaller or equal. The support portion may be, for example, a portion of the support body that forms or includes the support area upon contact with the absorber mass. In contrast, a contact portion may be, for example, a portion of the absorber mass that forms or includes the support region upon contact with the support body. The support region can therefore be the common region in which the support body and absorber mass touch.

Additionally or alternatively, the absorber mass in some Ausführungsbei games on its outer contour on at least one contact portion in which the absorber mass with the support body in at least one support area comes into contact. In some embodiments, the contact section has a different stiffness than the outer contour of the absorber mass outside the contact section. In some embodiments, in this way, the shape of the support area, which is at a collision of the absorber mass and the support body results, are determined by the elasticity of the contact portion. In some embodiments, the absorber mass has a plurality of contact portions. The individual contact sections may have different stiffnesses.

Additionally or alternatively, in some embodiments, the at least one support section expands in a radial direction farther than an average extension of the support body. In some embodiments, a shape and / or a position of the support region that forms between the absorber mass and the support body can be determined by a geometry of the support section. Optionally, the support portion may be in the form of a projection. In embodiments in which the support region is located on a radially inwardly directed outer contour of the absorber mass, the support portion may protrude radially outward from the support body or a base body of the support body.

Additionally or alternatively, at least one absorber mass may have on its outer contour a contact portion which expands further in a radial direction than an average outer contour of the absorber mass. In some embodiments, a shape of the support region and / or also a position of the support region can be determined by a geometry of the contact section on the absorber mass.

Additionally or alternatively, the at least one support portion or the at least one contact portion in some embodiments has a shape of a trapezoid. In some embodiments, the support portion or the contact portion may thus have in a simple manner different surfaces, with different inclinations and also edges, at which the support area may result with the absorber mass or the support body. In some embodiments, in which the support portion has the trapezoidal shape, a shorter of the mutually parallel sides of the trapezoid is directed to the absorber mass. The fact that the side of the trapezium is directed with the longer of the parallel sides to a major extent of the support body or the absorber mass, in some embodiments, may be a better connection of the support portion to the support body or the contact portion are made possible to the absorber mass. optional For example, the contact portion and / or the support portion may have all possible shapes, such as convexity, concavity, triangle, rectangle, quadrangle, polygon, and / or the like.

Additionally or alternatively, the support body is formed in some embodiments as a ring. In some embodiments, for example, a simple assembly of the one-piece component can be made possible.

In some embodiments, the Tilgerschwingungsdämpfer may include a plurality of support bodies, which are arranged adjacent to each other in the circumferential direction. Thus, under certain circumstances, an installation space for areas of the support body lying between the support sections, which actually do not come into contact with the absorber mass, could be saved. Optionally, the Tilgerschwingungsdämpfer in some embodiments, a plurality of support bodies, which are arranged adjacent to each other in the axial direction. For example, in embodiments in which it is a Tilgerschwingungsdämpfer with external absorber masses, the support body can be arranged in each case axially aligned with the absorber masses adjacent in the axial direction.

Additionally or alternatively, the at least one support body in some embodiments in the circumferential direction, relative to a rotational axis about which rotates the Tilgerschwingungsdämpfer rotatably disposed. In some embodiments, a defined stop position or a defined position of the support region between the absorber mass and the support body can thus be made possible.

Additionally or alternatively, the at least one support body in some embodiments in the radial and / or axial direction without play, for example, based on a rotational axis of rotation, arranged. In some embodiments, such a support region, which forms between the absorber mass and the support body, can be defined. Optionally, in some embodiments, the support body may be arranged to be movable relative to the guide structure, at least in the axial direction. In some embodiments, such a position of the support region can still be defined in the radial direction and in the circumferential direction. Beispiels- example, the support body in an axial direction to perform a movement up to one millimeter. A play-free arrangement may for example be rigid and / or such that no movement of the components in the direction of each other is permitted.

In some embodiments, the at least one support body is attached to the guide structure. As a result, in some embodiments, an additional component for fixing the support body relative to the rotation axis can be omitted.

In addition or as an alternative, the at least one support body in some embodiments comprises a base body which, at least on a surface facing the absorber mass, comprises a covering at least in sections. In this case, a material of the covering differs from a material of the base body. In some embodiments, under certain circumstances, a simpler production of the support body, for example by the choice of the material for the base body and a corresponding choice of the material for the coating, can be achieved. In some embodiments, the support body may include as a material, for example, a metal, a steel, a plastic, a thermoplastic and / or an elastomer. For example, the plastic, the thermoplastic and / or the elastomer may be fiber-reinforced. Additionally or alternatively, the pad may comprise a metal, a steel, a plastic, a thermoplastic, an elastomer and / or a fiber-reinforced plastic. In some embodiments, by an elastic covering, for example made of an elastomer, an elasticity of the

Support section are determined. For example, the pad can be attached or glued to the support body. Optionally, the support body may be manufactured in a two-component injection molding process.

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

Fig. 1a shows a schematic representation of a partial elevation of a top view of a vibration damper unit with a Tilgerschwingungsdämpfer according to an embodiment; Fig. 1 b shows a schematic cross-sectional view through the in Fig.

1 a vibration damper unit shown along a sectional plane A-A;

Fig. 1 c shows an enlarged detail of Fig. 1 a;

FIG. 2 a shows a schematic representation of a plan view of the absorber vibration damper of the vibration damper unit according to the embodiment of FIGS. 1 a and 1 b;

2b shows a schematic cross-sectional view through the in Fig.

2a absorber vibration damper of the vibration damper unit shown along a sectional plane R-R;

Fig. 2c shows a schematic cross-sectional view through the in Fig.

2a absorber vibration damper of the vibration damper unit shown along a sectional plane C-C;

FIG. 2d shows a schematic cross-sectional view through the embodiment shown in FIG.

2a shown absorber vibration damper of the vibration damper unit along a sectional plane A-A;

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

3a shows a schematic representation of a plan view of a damper mass according to an embodiment;

3b shows a schematic representation of a plan view of the absorber mass according to FIG. 3a, which is in contact with a supporting body; FIG. 3c shows a further schematic representation of a plan view of the absorber mass according to FIGS. 3a and 3b; FIG.

FIGS. 3d to 3i show schematic representations of different exemplary embodiments of a support region between the absorber mass according to FIGS. 3a to 3c and a support body;

4 shows a schematic cross-sectional representation through a hydrodynamic converter with a damper vibration damper according to one exemplary embodiment.

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 different, in terms of individual, several or all features, for example their dimensions, unless otherwise explicitly or implicitly stated in the description.

1 a and 1 b shows different views of a vibration damper unit 100, for example, for a drive train, not shown, of a motor vehicle. This comprises a torsion damper 102, which has at least one primary side 104 and at least one secondary side 106, between which at least one spring element 108 is coupled in such a way that torque is transmitted from the primary side 104 to the secondary side 106 via the at least one spring element 108.

Further, the vibration damper unit 100 comprises a Tilgerschwingungsdämpfer 1 10 comprising at least one damping mass 1 12 and at least one guide structure 1 14, wherein the guide structure 1 14 is formed to guide the at least one damper mass 1 12 to dampen a vibration component of a rotational movement , In the damper vibration damper 1 10 is the damping of the vibration Thus, by the at least one absorber mass as a damper element, which transmits no torque.

Furthermore, the vibration damper unit 100, which can also be referred to as a flywheel with a torsion damper, also includes a wobble decoupling structure 16 which is designed to move the at least one damper mass 1 12 in the axial direction M in a rotationally fixed and / or rotationally restricted manner with an output side 1 18, which is formed in the embodiment of FIGS. 1 a to 2 e as the output hub 120, the vibration damper unit 100 to connect. The absorber mass 1 12 may comprise, for example, a plurality of mutually adjacent in the axial direction M Einzeleltilgermassen. These can each be connected to one another via at least one absorber mass attachment structure 1 13, which may be, for example, a rivet or another fastening means. In further, not shown embodiments, the absorber mass can also be formed in other ways, for example in one piece. In the exemplary embodiment, the Tilgerschwingungsdämpfer 1 10 six absorber masses 1 12. In some other, not shown Tilgerschwingungsdämpfern also a different number of absorber masses can be used.

In the case of the vibration damper unit 100, a torque is conducted via a ring gear 122 in a direction of rotation indicated by the arrow 123 onto the primary side 104 of the torsion damper 102. For this purpose, the ring gear 122 is rotatably connected to a cover member 124 of the torsion damper 102. The cover component 124 is connected to a housing shell 126 of the torsion damper 102 and delimits with a radially outer region of the housing shell 126 a spring region 128 for receiving the spring element 108. In the spring region 128, as can be seen in FIG. 1a, there are a plurality of circumferentially arranged by spring elements 108. Via the primary side 104, a spring element driving shoe 130 is actuated, which receives in the spring region 128 and transmits a torque to the at least one spring element 108. Via the spring element 108, the torque is transmitted to a Federansteuersteg 132 of the secondary side 106. The secondary side 106 is at least one fastening structure 134, which may be formed, for example, as a rivet, spacer sleeve, Distanzniet, spacers or the like, taumelfest with the Tilgerschwingungsdämpfer 1 10 and its guide structure 1 14 connected. The secondary side 106 has a passage opening through which the attachment structure 134 is guided. Concentric with the passage opening is a countersink 136 in which a head of the attachment structure 134 is sunk. In the circumferential direction, the secondary side 106 is connected to the Tilgerschwingungsdämpfer 1 10 via a plurality of such attachment structures 134. For example, further attachment structures 136-a to 136-c can be seen in FIGS. 1a and 1b.

From the guide structure 1 14, the torque on the wobble decoupling structure 1 1 6 is transmitted to the output hub 120. The output hub 120 has an internal toothing. This is a straight toothing. Via the output hub 120, the torque is transmitted to an output shaft, not shown. Both the wobble coupling structure 1 1 6, as well as the Tilgerschwingungsdämpfer 1 10, will be described in more detail with reference to FIGS. 2a to 2e.

The ring gear 122 has an inner diameter d which is smaller than an inner diameter D of an attaching portion 137 of the cover member 124 extending in an axial direction. The fixing portion 137 defines an enveloping space in a radial direction in which the at least one absorber mass 1 12 can move in a deflected state. In a deflected state, the absorber mass 1 12 thus assumes a larger diameter D than an inner diameter of the toothed rim 122. For mounting through the toothed ring 122, the at least one absorber mass 1 12 can be sunk radially inward into the absorber vibration damper 1 10.

FIGS. 2 a to 2 e show different schematic illustrations of the absorber vibration damper 1 10, which can also be referred to as absorber or speed-adaptive absorber. The guide structure 1 14, which may be formed, for example, as a track plate is connected 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, which in the axial direction opposite to the first guide structure 1 14 is arranged. Also, the second guide structure 140 may be formed, for example, as a track plate. In axial direction between the first guide structure 1 14 and 140, the at least one damper mass 1 12, which can also be referred to as energy storage or flyweight, passed over a rolling element 142. As can be seen in FIG. 2 a, the absorber mass 1 12 is guided via two rolling elements 142-a and 142-b between the two guide structures 1 14 and 140.

In the rolling elements 142 of the embodiments 2a to 2e is a so-called step roller having rolling surfaces 144 and 146 with different diameters. The rolling surface 146 has a smaller diameter than the rolling surface 144. The absorber mass 1 12 has at least one running surface 148, in which the rolling element 142 rolls with the rolling surface 144. Similarly, the guide structures 1 14 and 140 each have a running surface 150, in which the rolling elements 142 unrolls with the rolling surface 146. In the region of the running surfaces 148 and 150 are shown in dashed lines exemptions 306, which serve to reduce friction between the rolling elements 124 with the absorber mass 1 12 and the guide structures 1 14 and 140. In some other embodiments, not shown, the exemptions may also be omitted.

On the guide structure 1 14 and a support body 154 is attached. The support body 154 may be formed in some embodiments as a plastic ring. The support body 154 is arranged concentrically to a central axis M and has a plurality of radially outwardly directed fastening eyes 156. These are C-shaped and engage from radially inward in each case around one of the attachment structures 138. The guide structures 14 and 140 have, as can be seen in FIG. 1a in the second guide structure 140, an embossing structure 160 against which the support body 154 can support with his attachment eye 156. The support body 154 has a plurality of support portions 158. In this case, each two support sections 158-a and 158-b, as shown in Fig. 1 a recognizable, arranged so that they can come into contact with a damping mass 1 12, for example, the absorber mass 1 12-a. The support portions 158-a and 158-b are symmetrical about an imaginary line of symmetry connecting in a state of equilibrium the axis of rotation M and the center of gravity of the absorber mass. In embodiments, there may or may be two support areas per absorber mass, which are arranged symmetrically to one another. In other embodiments, the support regions may also be arranged asymmetrically with respect to each other. In this case, the absorber mass and the support body can meet, for example, in one of the support areas in a movement in one direction of rotation and in the other support area in a movement counter to the direction of rotation.

In the following, support section 158-a will be described by way of example with reference to the enlarged view of FIG. 1 c. The support portion 158-a has a substantially trapezoidal shape. In this case, one of the parallel legs 159, which is shown by dashed lines in Fig. 1 c, namely the longer, on one of the absorber mass 1 12 opposite side of the support portion 158-a and integrally connects to a main body of the support body 154 and is located in this. Opposite a shorter, parallel to the legs 159 leg 1 61 is arranged, which faces the absorber mass 1 12. The leg 1 61 is connected to the main body of the support body 154 via a further leg 1 65. The leg 165 lies on a side facing the support section 158-b. The leg 165 connects via a radius to the main body of the support body 154. In the circumferential direction opposite the legs 159 and 1 61 are connected to another leg 157. This is substantially formed as a straight line and without radius or with a smaller radius than the leg 1 65 connected to the main body of the support body 154. In some embodiments, legs 159 and 161 are not parallel to each other. The support section 158 or the trapezoid is filled with material. This may be, for example, a material or a material of the base body and / or a material or a material of a coating or a covering. In some other embodiments, not shown, the support portion or the region enclosed by the legs may be hollow.

The support body 154 and its support portions 158 will be described in more detail with reference to FIGS. 3a to 4.

The tumble decoupling structure 1 1 6 is in axial direction only with the guide structure 1 14 and not with the guide structure 140 in contact and includes a first Teilentkopplungsbauteil 1 62 and a second Teilentkopplungsbauteil 1 64 64. The two Teilentkopplungsbauteile 1 62 and 1 64 are on a driven hub flange. 1 66 of the Output hub 120 attached. The output hub flange 1 66 has a plurality of vanes 1 68 in the vibration damper unit 100. In the vibration damper unit 100 four wings 1 68-a to 1 68-d, each offset by an angle of 90 ° to each other, arranged. The vanes 1 68-a to 1 68-d have a greater extent radially outward than regions 170-a to 170-d, each of which lies between two vanes 1 68-a to 1 68-d. The output hub flange 1 66 or its wings 1 68a to 1 68-d have in the axial direction, as can be seen for example in FIGS. 2 b and 2 c, in a radially outer area a smaller extent in an axial direction than 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 partial decoupling members 162 and 164 is connected to the output hub flange 1 66.

The Teilentkopplungsbauteile 1 62 and 1 64 are identical in construction in the vibration damper unit 100. In some embodiments, the Teilentkopplungsbauteile 1 62 and 1 64 may be formed, for example, as a spring plate or Axialblattfeder. 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.

Since the Teilentkopplungsbauteile 1 62 and 1 64 are constructed identical, the shape of the Teilentkopplungsbauteils 1 62 is described representative. As can be seen in FIG. 2 a, the partial decoupling component 1 62 has a symmetrical shape. Symmetry line is the section line CC. Starting from a guide structure projection 174-a, which serves for attachment to the guide structure 1 14, the partial decoupling member 1 62 is described in the clockwise direction. The partial decoupling member 1 62 has four such guide structure projections 174-a to 174-d. On the guide structure projection 174-a further includes in the circumferential direction a concave radially inwardly curved portion 176-a.

To the concave inwardly curved portion 176 includes a further radially outwardly extending wing projection 178-a, which serves for attachment to the wing 1 68-a and the output hub flange 1 66. Further in the clockwise direction, another concave inwardly curved portion 176-b connects to the winged protrusion 178-a until the next guide-structure protrusion 174-b. The guide structure protrusion 174-b is followed by a driven-attachment receiving portion 172-b. The output attachment receiving portion 172-b has a concave inwardly curved recess in the region of the line of symmetry. A guide structure projection 174-c again adjoins the output attachment receiving section 172-b. To the left of the line of symmetry in FIG. 2 a, the partial decoupling component 1 62 is designed analogously. Radially inside, the partial decoupling member 1 62 has a through hole 1 63, with which the part decoupling member 1 62 is arranged concentrically to the rotation axis M. The through hole 1 63 has a larger radius than the output hub 120.

The partial decoupling member 1 62 is attached to the output hub 120 and the output hub flange 1 66, respectively, via a plurality of output attachment structures 180. The partial decoupling member 1 62 is attached to the wing 1 68-a with its output projection structures 180-a and 180-b, which may be formed, for example, as rivets or standoffs or other attachment means, with its winged projection 178-a. Substantially in the radial direction, the partial decoupling member 1 62 with its wing projection 178-b is attached to the wing 1 68-c with the output attachment structures 180-d and 180-c. In some other embodiments, not shown, only one output attachment structure per wing can be arranged. With its guide structure projections 174-a to 174-d, the partial decoupling component 1 62 is attached to the guide structure 1 14 and thereby also to the Tilgerschwin- vibration damper 1 10. The guide structure 14 has four wobble decoupling attachment projections 182-a to 182-d for this purpose. The tumble decoupling attachment protrusions 182-a to 182-d protrude further radially inward than an average radially inward surface of the guide structure 14. The guide structure protrusions 174-a to 174-d are each provided with one of the tumble decoupling attachment protrusions 182 -a to 182-d are connected via a fastening structure 188. The attachment structure 188 may be formed, for example, as a rivet. In such cases, the guide structure 1 14 is riveted to the second part of the decoupling member 1 62.

The second partial decoupling member 164 is disposed and fixed at 90 ° to the first partial decoupling member 162, with the two partial decoupling members 162 and 164 sandwiching the output hub flange 166 in the axial direction. The second partial decoupling component 164 is therefore fastened, with its wing projections 178-e and 178-f, to the wing 1 68-d and the wing 1 68-b opposite the latter. For this purpose, as well as the partial decoupling component 1 62 output attachment structures 180 are used. On the wing 168-b, the output attachment structures 180-e and 180-f can be seen, with which the Teilentkopplungsbauteil 1 64, which is disposed on a part of the decoupling member 1 62 side facing the Abtriebsnabenflansches 1 66. The partial decoupling component 162 has two output attachment receptacles 184 in its output fastening receiving sections 172-a and 172-b. In the driven attachment receiving portion 172-b, these are designated by the reference numerals 184-e and 184-f. The output attachment receptacles 184 take a part of the output attachment structure 180, so for example a rivet head, in the axial direction.

In the vibration damper unit 100, the output attachment receivers 184 are each formed as through holes through which the head or a part of the output attachment structure 180 can protrude. In this case, the output attachment receptacles 184 have a greater extent than the output attachment structure 180, so that the partial decoupling member 1 62 does not have the output attachment structures 180, with which the partial decoupling member 164 is attached to the output hub flange 1 66, comes into contact with or is fixed by them. In some embodiments, such a space can be reduced in the axial direction. Likewise, the output attachment structures 180-a and 180-b as well as 180-c and 180-d pierce corresponding through-holes or output attachment receptacles in the partial decoupling member 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 Teilentkopplungsbauteil 1 64 is also connected to the guide structure 1 14. Since the guide structure 1 14 has a smaller extent in the axial direction than the output hub flange 1 66, a spacer 186 is arranged on the guide structure 1 14. The spacer 186 may be formed, for example, as a plastic ring. The spacer 186 has a plurality of tumble decoupling attachment projections 182-e to 182-h substantially analogous to the guide structure 14. The partial decoupling component 1 62 with its guiding structure projections 174 is fixed to the latter. For example, at the tumble decoupling attachment protrusion 182-h of the spacer 186, the guide structure protrusion 174-e is riveted. For this purpose, a fastening structure 188 is used, which may be formed, for example, as a rivet or rivet connection.

One of the fastening structures 188 can be seen, for example, in the sectional representation of FIG. 2d. The spacer 186 is fastened to the guide structure 14 via the attachment structure 134, with which the guide structure 1 14 or the absorber 10 is also connected in a tumble-resistant manner to the secondary side 106 of the torsion damper 102. In the vibration damper unit 1 10 eight of the mounting structures 134 are provided in the circumferential direction. These can be, for example, a rivet, a spacer bolt or another fastener. In some other embodiments, not shown, a different number of attachment structures may be provided.

The Tilgerschwingungsdämpfer 1 10, comprising the interconnected or riveted guide structures 1 14 and 140 and guided over the rolling elements absorber masses is flexibly connected via the tumble decoupling structure 1 16 to the rotation axis M with the output side 1 18 or output hub 120, while in Rotation direction is stiff to transmit torque can. For example, the tumble decoupling structure 1 1 6 may allow a movement in an axial direction of the guide structure 1 14 of 0.1 mm to 1 mm or 1, 5 mm.

Embodiments may include damper vibration dampers of all possible types. For example, the Tilgerschwingungsdämpfer also have a central guide structure or a central track plate, wherein the at least one absorber mass is arranged in the axial direction on both sides of the guide structure.

3a to 3c each show a schematic representation of a plan view of the absorber mass 1 12 in different operating conditions. In the Tilgerschwingungsdämpfer 1 10 acts on the at least one absorber mass 1 12 a centrifugal force and gravity. If the speed is low enough, the centrifugal force loses importance compared to the gravity, then it may happen that the gravitational force stimulates the absorber masses 1 12 to vibrate. The absorber mass 1 12 rolls with its running surfaces 148-a and 148-b on the two rolling elements 142, which are designated for differentiation by reference numerals 142-a and 142-b, as already described for FIGS. 1 a to 2 e , The rolling elements 142-a and 142-b in turn roll on the guide structures 1 14 and 140 not shown in FIGS. 3a to 3c.

Tilgerschwingungsdämpfer perform in an operating condition usually a harmonic oscillating motion, for example, counteracts an exciting torque acts. For example, in an operating state at a low speed, it may therefore happen under certain circumstances that the at least one absorber mass is deflected maximum. In this case, the rolling elements can be up to an end of Laufflä- Chen the guide structure and / or be moved to an end of the running surfaces of the absorber mass. The absorber mass can be greatly delayed. This may result in a striking sound that is audible. In order to reduce or at least completely avoid this impact noise, the absorber mass can be braked softly shortly before reaching the maximum oscillation angle. This can for example be similar to an airbag in a car.

In some Tilgerschwingungsdämpfern a radially disposed within the absorber masses elastic support ring is used. In a contact between the absorber mass and the support ring, it may then happen that the absorber mass is tilted about an axis which is parallel to the axis of rotation M. The axis of rotation can also be referred to, for example, as a track plate rotation axis or axial direction. This can possibly lead to a rolling element, for example comparable to the rolling element 142-b, lifting off from a running surface, comparable to the running surface 148-b on the absorber mass 1 12 or from a running surface on the guide structure. Subsequently, the rolling element strikes again on the corresponding running surface.

By hitting the rolling element on the tread can also create an undesirable impact noise. The absorber mass is then again in an untilted position, as shown for the absorber mass 1 12 in Fig. 3a. In the untilted position is at the absorber mass 1 12 a moment balance, as seen in Fig. 3a, equal to zero.

The absorber mass 1 12 may for example be made in one piece or comprise a plurality of Einzeletilgermassen, which are arranged in the axial direction next to each other. The absorber mass 1 12 comprises two openings, each having a running surface 148, which may also be referred to as a raceway.

The force F _Ro iiei .R is the frictional force on the rolling element 142-b, the force F _Ro iiei N relates to the normal force at the pitch point of the rolling element 142-b. Similarly, the force F _Ro iie2.N refers to the normal force on the rolling element 142-a and the force F _Ro iie2.R refers to the frictional force on the rolling element 142-a. Corresponding distances from the lines of action of the forces to the center of gravity 196 of the absorber mass are denoted by r ₃ to r ₆ . In order to avoid the impact noise, the support body 154 is provided in the Tilgerschwingungsdämpfer 1 10. 3b shows the absorber mass 1 12 with the schematically illustrated support body 154, which is designed to come into contact with an outer contour 192 of the absorber mass 1 12 in at least one support region 194, wherein the support region 194 lies within an average extent 198, as shown in Fig. 3c, wherein the mean extent 198 has a proportion of at most 80% of an absorber mass length 200 and is arranged symmetrically to the center of gravity 196 of the absorber mass 1 12. Optionally, the support region 194 can also lie within an extension 198 which corresponds at most to a proportion of 60%, 50% and / or 30% of the absorber mass length 200.

Due to the fact that the support region 194 lies on the outer contour 192 and within the extension 198, even if the absorber mass 1 12 is in contact with the support body 154, a moment balance of zero can be present at the absorber mass 1 12. Thus, in some embodiments, at least the risk can be reduced or even completely avoided that the rolling elements 142-a or 142-b lift off the running surfaces, while the absorber mass 1 12 is supported on the support body 154. In other words, the rolling elements 142-a and 142-b should keep contact with the running surfaces 148-a and 148-b.

The outer contour 192 is a surface of the absorber mass 1 12, which is directed substantially in a radial direction and which is not completely enclosed by a material of the absorber mass 1 12. For example, in this connection, a passage opening in the absorber mass 1 12 would not be encompassed by the outer contour 192.

As can be seen in FIG. 3 b, the position of the support region 194 results in the following moment balance when the absorber mass 1 12 is in contact with the support body 154:

/ ^■ φ = - Support Ν ^" Γ1 + Support.R ^■ Γ2 - FR ₀ || G2 R ^' Γ3 - FR ₀ || G2.N ^" Γ ₄ + FR ₀ || G1 .R ^" Ts + FR ₀ || G1 .N ^" ^ 6 / ^■ ψ = o

In this case, F _st ütz.N stands for the normal force in the support portion 194 and F _st ütz.R for the friction force in the supporting portion 194. / denotes the moment of inertia and φ the rotation angle of the absorber mass 1 12 to its center of gravity 196 and ψ is the angular acceleration.

The forces thus act on the absorber mass 1 12 so that the absorber mass 1 12 does not rotate by φ. One factor that has an influence on this can be, for example, the support force that is introduced into the absorber mass 1 12 in a system between the support body 154 and the absorber mass 1 12.

Since all forces on damper mass 1 12 vary over time, in some embodiments it will be difficult in a practical application that the torque balance is zero at all times. Therefore, in some embodiments, it may be difficult to prevent rotation of the absorber mass 1 12 upon contact between the support body 154 and the absorber mass 1 12. In other words, it may sometimes be unavoidable to produce a rotation of the absorber mass 1 12. A position of the support portion 194, which can also be called the support ring contact point, can be chosen so that the rotation of the absorber mass 1 12 at a support contact is minimal or as low as possible. For example, a suitable position of the support region 194 can be determined by means of a multi-body simulation (abbreviation: MKS tool).

For example, the position of the support portion 194 on the absorber mass 1 12, also be described so that when the absorber mass 1 12 is deflected maximum, so is located at the tail or the rolling elements 142-b and 142-a each at a

Tread end 190 of the tread 148-b and 148-a are located, then the should

Support portion 194 within an average extent 198 of the absorber mass 1 12, which corresponds to a share of 80% of an absorber mass length 200, are located. Optionally, the support region 194 can also be located within an average extent 198, which corresponds to a proportion of 60%, 40% and / or 30% of the absorber mass length 200. The absorber mass length 200 may be, for example, an extension of the absorber mass, which is in a state of equilibrium of the absorber mass 1 12 in a mounting situation perpendicular to a connecting line between the rotation axis M of the vibration damper unit 100 and the absorber mass center 196. For example, the absorber mass length 200 may be a maximum extent of the absorber mass 1 12, which has these perpendicular to the connecting line.

The support region 194 is therefore not located on an outer contour 192 of the absorber mass 1 12, which is outside the extension 198 of 80% of the maximum absorber mass length 200. These regions of the outer contour 192 are designated by reference numerals 202-a and 202-b. The outer regions 202-a and 202-b may, for example, in each case have an extent corresponding to a proportion of 10% of the maximum absorber mass length 200 in the case of a symmetrical absorber mass 1 12. In the case of an asymmetrical absorber mass, the outer regions in which the support region does not form may possibly have different lengths.

In one operation, the absorber mass 1 12 in many embodiments, always two support areas 194, which may also be referred to as optimal contact points have. In this case, the absorber mass 1 12 and the support body 154, for example, on the support portion 194 at a maximum swing angle and at another support area, for example, at a minimum swing angle, meet. In some embodiments, the two support areas for the different oscillation angle may also be at least partially superimposed. In other words, the two contact points may coincide.

In the present embodiment, the support body 154 is disposed radially within the absorber mass 1 12, concentric with the output hub 120. As a result, the at least one support region 194 lies on a radially inwardly directed outer contour 192 of the absorber mass 1 12.

FIGS. 3d to 3i each show a plan view from a radial direction on the outer contour 192 of the absorber mass 1 12 or the support portion 158 of the support body 154. FIGS. 3d to 3i thus show different shapes of support regions 194-d to 194-k, which can result between the absorber mass 1 12 and the support body 154, if appropriate for different exemplary embodiments. In some embodiments, this may be to oversights on the absorber mass 1 12 from radially inside. For example, for this purpose, the outer contour 192 of the absorber mass 1 12 or a contact portion 204 on the absorber mass 1 12, at which the support body 154 with the outer contour 192 of the absorber mass 1 12 comes into contact, be designed accordingly. Additionally or alternatively, the support body 154 or one of the support portions 158 may be formed accordingly. For example, the contact portion 204 and / or the support portion 158 may have a corresponding shape and / or elasticity.

The support area 194-d is formed as a point. The support region 194-d can essentially, in an axial direction M, lie centrally on the outer contour 192. In some other embodiments, not shown, the support region 194-d may also be closer to an edge 206 of the outer contour 192.

Fig. 3e shows a support region 194-e, which is formed as a line, which may also be called a contact line. The support region 194-e extends over a complete extension of the outer contour 192 or the support portion 158 in an axial direction. In some other embodiments, not shown, the support portion 194-e may also be spaced from an edge 206 or an edge opposite thereto.

FIG. 3f shows a support region 194-f, which is likewise designed as a contact line. However, this extends parallel to an edge 206 of the outer contour 192 or the support portion 158. The support portion 194-f is located centrally between the edge 206 and one of these in the axial direction M opposite edge 208. In some other embodiments, not shown, the support area 194-f may also be arranged asymmetrically with respect to the two edges 206 and 208.

In Fig. 3g, two support portions 194-g and 194-h are shown. These are each formed as broken lines. The lines begin at edge 206 and terminate the edge 208. In a central region, the support regions 194-g and 194-h are each interrupted. At this point, the support portion 158 and the outer contour 192 are not in contact with each other.

FIG. 3h shows a support region 194-i, which has the shape of a rectangle. The support region 194-i may also be referred to as a contact surface or as a two-dimensional contact surface. In contrast, for example, the support regions 194-e to 194-g can also be referred to as one-dimensional contact lines.

In other words, the support portion 194 may have all possible shapes. For example, instead of a contact point, a contact line or a contact surface may also be present. These may be formed interrupted, for example. For example, per absorber mass 1 12 of a plurality of support portions 194 may be provided, which are adjacent to each other in the axial direction and / or in the circumferential direction. In some embodiments, tilting of the absorber mass 1 12 can at least be reduced or even avoided by a one-dimensional or two-dimensional support region 194 and / or a plurality of contact points, for example by specific design of the support section 158. In some embodiments, unintentional tilting may be forced. This can be done, for example, by tolerances or different stiffnesses of the individual support sections 158 and / or contact sections 204.

The support body 154 may comprise all possible materials, for example a thermoplastic, a fiber-reinforced thermoplastic, a steel, an elastomer or a combination of these materials.

In other embodiments, not shown, the support body may be designed so that its support portions, which may also be referred to as contact areas, rotationally symmetrical about a central axis, which may also be referred to as orbital axis of rotation, are located to the absorber mass. In such embodiments, a geometry of the absorber mass or its outer contour can be varied so that the described support areas arise. In some other embodiments, not shown, the support body may be formed so that itself the support region is located on a radially outwardly directed outer contour of the absorber mass.

Furthermore, the vibration damper unit 100 can also have a support ring or support body, which is designed such that at least one support region with the absorber mass 1 12 is located on an outer contour 192 directed in the circumferential direction, ie between a radially outwardly directed outer contour 192 and a radially outwardly directed outer contour 192 Absorber Mass 1 12. The vibration damper unit 100 may also have a support body having support areas with the absorber masses 1 12, which lie outside the said 80% of the central absorber mass length 200, that is, for example, in the areas 202.

The support body may not be integrally formed in other embodiments, not shown, as in the embodiments shown in the figures. For example, per absorber mass a plurality of supporting bodies, which can also be referred to as support elements, are used.

The support body 154, which may also be referred to as a support ring, may be used in a variety of vibration damper units, for example in a dual mass flywheel. In further embodiments, the support ring 154 may also be used in a single-mass flywheel. Basically, the support body 154 according to embodiments, for example, in air or in applications in which it is in a fluid, such as oil, are used. The support ring concept can be transferred to other applications, for example in other dimensions.

4 shows the use of the support body 154 in a torque converter 210. In this case, the support body 154 is located in a fluid-filled interior 212. The support body 154 is used in the torque converter 210 of FIG. 4 on a Tilgerschwingungsdämpfer 214. The torque converter 210 comprises a housing 214, with a drive-side housing shell 21 6 and a drive-side housing shell 218. In this, an impeller designated generally by the reference numeral 220 is formed. Around the axis of rotation M, in the circumferential direction consecutively, a plurality of pump impeller blades 222 are provided on an inner side of the housing shell 218.

Axially opposite the impeller 220, a turbine wheel 224 is provided inside the housing 214. This includes impeller blades 222, axially opposed, circumferentially successive turbine blades 226. Axially between the inner portion of impeller blades 222 and turbine blades 226 are stator blades 228 of a nozzle generally designated 230. This is rotatably supported by a non-descript freewheel assembly 232 on a support hollow shaft, not shown, in a rotational direction about the rotation axis M. By the impeller 220, the turbine 224 and the stator 230 is formed with the present in the housing 214 fluid, generally oil, a hydrodynamic circuit that can be used for torque transmission or increase.

Inside the housing 214, a vibration damper assembly, generally designated by reference numeral 234, is also provided. The torsion damper arrangement 236 comprises two torsion dampers 240 and 242 in a radially staggered manner. The radially outwardly positioned first torsion damper 240 comprises a disc-shaped first primary side 246 its radially inner region and a friction element of a lock-up clutch 248 which is pressed by a clutch piston 250 against an inner side of the housing 214 to produce the lock-up state. A first secondary side 252 is provided with a disk-like member 260 having circumferential support portions 254 in its radially outer region, which may also be referred to as spring drive webs. At least one spring element 256 may be coupled to the peripheral support regions 254. Further, with the Umfangsabstützbereichen 254 also, the spring elements 256 radially outwardly supporting, ring-like support member 258, for example by riveting, be connected. In its radially inner region, the disk-like component 260 forms a second primary side 262. This is surrounded on both axial sides by two, the second secondary side 264 providing cover disk elements. The cover disk elements are radial internally connected to an output hub 266. Furthermore, one of the cover disk elements is firmly connected to the turbine wheel 224, for example by riveting.

The disk-like component 260 forms a guide structure 268, in particular with a region lying between the two torsion dampers 240 and 242, on which the at least one absorber mass 1 12 is movably guided. In the case of the vibration damper unit shown in FIG. 4, the absorber mass is 12 each two on both sides of the guide structure 268 lying Einzeletilgermassen 270 and 272, so formed as an external absorber mass, which may for example also be firmly connected to each other. The support body 154 is fixed radially to the at least one damping mass 1 12 on the guide structure 268. In the embodiment of Fig. 4, the support body 154 in the axial direction only at an axial height, on which the Einzeleltilgermasse 270 is located. In some other embodiments, not shown, the support body may also be arranged on both sides in the axial direction to the guide structure, so that it can have 270 and 272 support areas with two Einzeletilgermassen.

In other words, the support body 154 can be used in Tilgerschwingungsdämpfern with internally and / or externally guided absorber masses 1 12. The choice or position of the support region 194, which may also be referred to as a stop location, can be taken with lateral or central Tilgerträgern or management structures regardless of the design of the Tilgerschwingungsdämpfers. The support body 154 is fixed, for example in the circumferential direction rigidly on the guide structure 1 14 and / or 140 and may be arranged in the radial and / or axial direction with a game or rigidly on the guide structure 1 14 and / or 140.

With the support body 154 according to at least one of the embodiments, in some embodiments, at least the risk can be reduced or even completely avoided that the at least one absorber mass 1 12 tilts in contact with the support body 154 and causes resulting noise. As a result, in some embodiments, for example, noises, such as "rattling", can be minimized, which can occur, in particular, when the internal combustion engine is switched off and / or started on the damper vibration damper 1 10 or 238. 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.

REFERENCE CHARACTERS

100 vibration damper unit

102 torsional damper

104 primary side

106 secondary side

108 spring element

1 10 Tilgersc wingungsdämpfer

1 12 absorber mass

1 13 absorber mass attachment structure

1 14 Management structure

1 1 6 tumble decoupling structure

1 18 output side

120 output hub

122 sprocket

123 direction of rotation

124 cover component

126 housing shell

128 spring range

130 spring element driving shoe

132 spring control bar

134 attachment structure

136 subsidence

137 fixing 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 fixing eye 157 thighs outside

158 support section

159 parallel leg

160 embossed structure

161 parallel leg

162 partial decoupling component

163 passage opening

164 partial decoupling component

165 thighs

166 output hub flange

168 wings

170 area between wings

172 output attachment receiving section

174 Leadership structure lead

176 concavely curved section

178 wing projection

180 output attachment structure

182 wobble decoupling connection tab

184 output attachment

186 spacers

188 mounting structure

190 tread end

192 outer contour

194 support area

196 focus

198 extension

200 absorber mass length

202 outdoor area

204 contact section

206 edge

208 opposite edge

210 torque converter

212 interior, oil filled 214 housing

21 6 housing shell

218 housing shell

220 impeller

222 impeller blade

224 turbine wheel

226 turbine wheel bucket

228 stator blade

230 stator

232 freewheel arrangement

234 vibration damper assembly

236 torsion damper arrangement

238 absorber vibration damper

240 torsion damper

242 torsion damper

246 first primary page

248 lock-up clutch

250 clutch pistons

252 first secondary side

254 circumferential support area

256 spring element

258 support component

260 disc-like component

262 second primary page

264 second secondary side

266 output hub

268 management structure

270 single-piece mass

272 single-piece shotgun

306 exemption

M axial direction

d inner diameter sprocket D Inner diameter Enveloping space Tilgermasse

FRolle ... Force on the rolling element

Fstütz _... Force in the support area

FFlieh centrifugal force

J moment of inertia

φ angle

r ... distance

m ^* a / m ^* g, product of mass and acceleration

Claims

claims

1 . Tilgerschwingungsdämpfer (1 10, 238), for example for a drive train of a motor vehicle, for damping a vibration component of a rotary movement, comprising: at least one absorber mass (1 12), which is designed to perform in response to the rotational movement to a vibration To dampen vibration component thereof; and at least one guide structure (1 14, 140) adapted to movably guide the absorber mass (1 12); and at least one support body (154) configured to contact an outer contour (192) of the absorber mass (1 12) in at least one support region (194), the support region (194) being disposed within an average extent (198 ) of the absorber mass (1 12), wherein the average extent (198) has a proportion of at most 80% of an absorber mass length (200) and symmetrical to the center of gravity (196) of the absorber mass (1 12) is arranged.

2. A damper vibration damper according to claim 1, wherein the at least one support portion (194) lies exclusively within the extension (198).

3. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one support portion (194) on a radially inwardly directed outer contour (192) of the absorber mass (1 12).

4. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the at least one support body (154) and the at least one absorber mass (1 12) are formed in order to contact each other in at least two different support areas (194).

5. A damper vibration damper according to any one of the preceding claims, wherein the at least one support body (154) and the at least one absorber mass (1 12) are formed to contact in at least one support region (194), the at least one point, at least one line and / or at least one surface.

6. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the at least one support body (154) has at least two support portions (194) having different stiffnesses.

7. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the absorber mass (1 12) on its outer contour at least one contact portion (204), in which the absorber mass (1 12) with the support body (154) in at least one support region (194) in contact which has a different rigidity than the outer contour (192) outside the contact portion (204).

8. A damper vibration damper according to one of the preceding claims, wherein the at least one support body (154) has at least one support portion (158) which expands in a radial direction farther than an average extent of the support body (154).

9. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one absorber mass (1 12) on its outer contour (192) has a contact portion (204) which expands further in a radial direction than an average extent of the outer contour (192).

10. A damper vibration damper according to claim 8 or 9, wherein the at least one support portion (158) or the at least one contact portion (204) has substantially a shape of a trapezoid.

1 1. A damper vibration damper according to any one of the preceding claims, wherein the at least one support body (154) is a ring.

12. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one support body (154) in the circumferential direction, relative to a rotational axis, is arranged rotationally fixed.

13. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one support body (154) in the radial and / or axial direction without play, based on a rotation axis, is arranged.

14. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one support body (154) on the guide structure (1 14, 140) is attached.

15. Tilgerschwingungsdämpfer according to one of the preceding claims, wherein the at least one support body (154) comprises a base body, the absorber mass (1 12) facing surface at least partially comprises a covering, the material of which differs from the material of the base body.