WO2015165672A1

WO2015165672A1 - Vibration damping unit

Info

Publication number: WO2015165672A1
Application number: PCT/EP2015/056834
Authority: WO
Inventors: Alexander Manger; Bernhard Schierling; Christoph Fauss; Michael Traut
Original assignee: Zf Friedrichshafen Ag
Priority date: 2014-04-28
Filing date: 2015-03-30
Publication date: 2015-11-05
Also published as: DE102014207962A1; EP3137787A1

Abstract

The invention relates to a vibration damping unit (1, 90), for example for a powertrain of a motor vehicle, comprising a torsional damper (3) that has at least one primary side (5) and at least one secondary side (7), between which at least one spring element (9) is coupled such that a torque is transmitted from the primary side (5) to the secondary side (7) via the at least one spring element (9). The at least one spring element (9) is arranged in a spring region (11) which comprises a lubricant during the operation of the vibration damping unit (1, 90). The vibration damping unit (1, 90) further comprises a tuned mass damper (13, 92) which comprises at least one absorber mass (15, 94) and at least one guide structure (17, 98). The guide structure (17, 98) is designed to movably guide the at least one absorber mass (15, 94) in order to damp a vibration component of a rotational movement. The vibration damping unit (1, 90) also has a sealing membrane (19, 102) which at least partly separates the spring region (11) from the at least one absorber mass (15, 94) in order to reduce a penetration of the lubricant into the at least one absorber mass (15, 94). The sealing membrane (19,102) is supported against the guide structure (17, 98) and a cover component (21) of the vibration damping unit (1, 90).

Description

Schwinqunqsdämpfereinheit

Embodiments relate to a vibration damper unit, which can be used for example in the context of a drive train of a motor vehicle, for example 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 rotational movement 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 drive train of a motor vehicle corresponding deviations from a uniform or uniform rotational movement, for example, by a deployment characteristic of the torque of an internal combustion engine, caused. To decouple, or at least damp, these from subsequent components, such as a transmission, differential, or other corresponding components of a powertrain, damper assemblies are used there.

Such vibration damper units are described, for example, in DE 10 201 1 086 927 A1, which comprise a torsion damper and also a damper vibration damper which has at least one damper mass and at least one guide structure. About at least one sealing device, the spring elements and the at least one absorber mass are sealed on an output side of the torsion damper to a clutch and to a transmission. In the area of corresponding vibration damper units, 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 that occurs, ease of manufacture, and improved performance in an operation of a vibration damper unit.

This demand is borne by the vibration damper units according to claims 1 and 13.

A vibration damper unit according to an exemplary embodiment, for example for a drive train of a motor vehicle, comprises a torsion damper having at least one primary side and at least one secondary side, between which at least one spring element is coupled in such a way that torque is transmitted from the primary side to the secondary side via the at least one spring element , The at least one spring element is arranged in a spring region, which comprises a lubricant during the operation of the vibration damper unit. The vibration damper unit further comprises a damper vibration damper comprising at least one damper mass and at least one guide structure, wherein the guide structure is adapted to movably guide the at least one damper mass to damp a vibration component of a rotary motion. Furthermore, the vibration damper unit comprises a sealing membrane which at least partially separates the spring area from the at least one damper mass in order to reduce the advance of the lubricant to the at least one damper mass. In this case, the sealing membrane is supported on the guide structure and a cover component of the vibration damper unit.

Characterized in that the sealing membrane at least partially separates the spring region of the at least one absorber mass to reduce penetration of the lubricant to the at least one absorber mass and the sealing membrane is supported on the guide structure and the cover member of the vibration damper unit, in some embodiments, the risk may be reduced that Lubricant reaches the at least one absorber mass or the guide structure and this dirty or glued. Thus, it can be avoided in some embodiments that the at least one absorber mass is possibly hindered or limited by lubricant in their mobility. Furthermore, the sealing effect or protective function for the at least one absorber mass can be achieved in many embodiments by using the sealing membrane on the guide structure and the cover component of the vibration damper unit, without taking up much installation space.

For example, a lubricant may be a medium that may enhance a function of the torsion damper or spring elements, such as a liquid, paste, grease, lubricating fluid, or other lubricating medium. The lubricant may in some cases only be introduced during assembly or during operation in the vibration damper unit.

In some embodiments, the sealing membrane is supported on the guide structure and the cover member in an axial direction. In some embodiments, it can thus be made possible that an axial force curve from the guide structure to the cover component takes place at least partially over the sealing membrane. Thus, if necessary, other components for transmitting the axial force can be reduced or even completely eliminated.

Additionally or alternatively, a wear reduction structure is arranged between the sealing membrane and the cover component in further exemplary embodiments. A material of the wear reduction structure may differ, for example, from a material of the cover component. In some embodiments, with a possible relative movement between the sealing membrane and the cover component, wear between these two components can at least be reduced or even avoided. The wear-reduction structure may be, for example, a separate component which is arranged between the sealing membrane and the cover component. Furthermore, the wear reduction structure can also be a coating, painting, gating or the like on the sealing membrane and / or the cover component. For example, the Schlei ßreduzierungsstruktur be arranged in the axial direction between the sealing membrane and the cover component.

In some embodiments, the cover member is part of a housing of the vibration damper unit. In some embodiments, the spring region in which the spring element is received can thus be formed or limited in a simple manner. If necessary, the cover component can be fastened to another housing component, for example welded to it.

In some other embodiments, the sealing membrane is additionally or alternatively attached to the guide structure of the Tilgerschwingungsdämpfers. In some embodiments, positioning of the sealing membrane, at least in a circumferential direction and / or a radial direction, can thus be made possible in a simple manner.

Additionally or alternatively, the sealing membrane may comprise at least a first partial membrane and a second partial membrane. In some embodiments, such a simple assembly of the sealing membrane can be made possible.

For example, the first partial membrane may be arranged on an axially opposite side to the second partial membrane. In some embodiments, it can thus be made possible that the guide structure and the absorber masses are arranged in the axial direction between the two partial membranes.

Additionally or alternatively, the second sub-membrane may have a support area which is supported against the cover component. In some embodiments, such an Axialkraftverlauf can be effected by the guide structure on the second part of the membrane to the cover member. Optionally, the support region can also be formed on the first part membrane.

Additionally or alternatively, in some other embodiments, the second sub-membrane has an overlap portion that overlaps with an overlap portion of the first sub-membrane. Thus, in some embodiments be made possible that the sealing membrane is indeed formed in several parts, but nevertheless in a region in which the two sub-membranes adjoin one another, form a closed or even tight envelope. In some embodiments, at least one of the overlap sections extends at least partially or substantially in an axial direction. For example, the overlapping sections may then overlap in the axial direction. Optionally, the overlapping sections can also extend at an angle to the axial direction, that is to say be conical, for example.

Additionally or alternatively, in embodiments in which the at least one absorber mass is arranged in the axial direction outside the guide structure, the sealing membrane can be supported radially within the at least one absorber mass on the guide structure. In some embodiments, which relate to an internal guide structure with at least one outer absorber mass, can be made possible so that the sealing membrane is arranged and / or fixed with a sufficient distance in the axial direction to the absorber masses. Thus, for example, touching, grinding and / or contact of the absorber masses on the sealing membrane can at least be reduced or even prevented.

In some embodiments, the at least one absorber mass is arranged in the axial direction between at least a first and a second guide structure. In such embodiments, the sealing membrane may be secured to at least one of the guide structures with a fastener interconnecting the first and second guide structures. In some embodiments, so further components or fasteners for fixing or securing the sealing membrane may be reduced or even completely eliminated.

Additionally or alternatively, the vibration damper unit comprises in some embodiments, a plate spring and / or a plate spring package. The Tilgerschwingungs- damper is supported in these embodiments in an axial direction on the plate spring or the disc spring assembly against the primary side of the torsional vibration damper and / or the vibration damper unit and the sealing membrane against the cover component. In some embodiments, the axial positioning can thus be tion of the Tilgerschwingungsdämpfers or a Axialkraftverlauf between the primary side and the cover component can be effected. The primary side can be, for example, a housing of the vibration damper unit and / or of the torsion damper.

Exemplary embodiments according to a further aspect relate to a vibration damper unit, for example for a drive train of a motor vehicle, having a torsion damper which has at least one primary side and at least one secondary side, between which at least one spring element is coupled such that a torque transmission from the primary side to the Secondary side via the at least one spring element. Furthermore, the vibration damper unit comprises a damper vibration damper comprising at least one damper mass and at least one guide structure, wherein the guide structure is adapted to movably guide the at least one damper mass to damp a vibration component of the rotational movement. The vibration damper unit also includes a seal diaphragm that at least partially separates the damper unit from a space outside the damper unit to at least reduce lubricant penetration to the space portion outside the damper unit, or intrusion into the damper unit. The sealing membrane is supported on the guide structure via a wear-reducing structure against a cover component of the vibration damper unit. A material of the wear reduction structure differs from a material of the cover component.

Due to the fact that the sealing membrane is supported by a wear reduction structure against a cover component of the vibration damper unit, in some embodiments it may be possible to at least reduce wear and / or noise during a relative movement between the sealing membrane and the cover component. Thus, in some embodiments, a function of the vibration damper unit can be improved and, under certain circumstances, a lifetime of the vibration damper unit can also be increased. The wear reduction structure may be, for example, a separate component that is not connected to either the cover component or the sealing membrane. Additionally or alternatively, the wear reduction structure is arranged in some embodiments in the circumferential direction movable between the sealing membrane and the cover component. In some embodiments, such an ability of the wear reduction structure to reduce wear can be increased. Furthermore, in some embodiments, means for fixing the wear-reducing structure can thus be dispensed with.

Additionally or alternatively, in some embodiments, the vibration damper unit includes a Belleville spring or a Belleville spring package that is configured and arranged to effect an axial force progression from a primary side of the vibration damper unit via the guide structure, seal membrane, and wear reduction structure to the cover component. In some embodiments, without the provision of further components, an axial securing of the wear reduction structure can be made possible.

Hereinafter, with reference to the accompanying figures, embodiments, to which embodiments are not limited, described in more detail.

Show it:

Fig. 1 is a schematic cross-sectional view of a vibration damper unit according to an embodiment;

FIG. 2 shows a further schematic cross-sectional view of the vibration dampenings according to the exemplary embodiment of FIG. 1; FIG.

3 is a schematic cross-sectional view of a vibration damping according to a further embodiment;

4 shows a further schematic cross-sectional representation of the vibration damping according to the embodiment of FIG. 3; Fig. 5 is a schematic representation of a partial elevation of a view of a

Vibration damper unit according to another embodiment;

FIG. 6 shows a schematic cross-sectional view through the vibration damper unit shown in FIG. 5 along a section C; FIG.

Fig. 7 is a schematic representation of a partial elevation of a view of a

Vibration damper unit according to another embodiment;

8 shows a schematic cross-sectional view through the vibration damper unit shown in FIG. 7 along a section A. FIG.

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 and 2 show schematic cross-sectional views of a vibration damper unit 1 according to an embodiment.

The vibration damper unit 1, for example for a drive train of a motor vehicle, comprises a torsion damper 3, which has at least one primary side 5 and at least one secondary side 7 between which at least one spring element 9 is coupled, so that a torque transmission from the primary side 5 to the secondary side 7 via the at least one spring element 9 takes place. The primary side 5 can also be used as a primary flywheel or as part of a housing of the vibration be formed damper unit. The at least one spring element 9 is arranged in a spring region 11. The spring portion 1 1 comprises during operation of the vibration damper unit 1, not shown in FIGS. 1 and 2 lubricant. The primary side 5 or the housing has an opening 82. For example, the lubricant can be introduced into the spring region 11 via the opening 82.

Furthermore, the vibration damper unit 1 comprises a damper vibration damper 13 which comprises at least one damper mass 15 and at least one guide structure 17. The guide structure 17 is designed to movably guide the at least one damper mass 15 in order to damp a vibration component of a rotational movement. The vibration damper unit 1 also comprises a sealing membrane 19 which at least partially separates the spring region 11 from the at least one damper mass 15, in order to reduce the advance of the lubricant to the at least one damper mass 15. The sealing membrane 19 is supported on the guide structure 17 and a cover component 21 of the vibration damper unit 1.

In the embodiment, the Tilgerschwingungsdämpfer 13 comprises a plurality of circumferentially adjacent to each other arranged absorber masses. The exemplary embodiment is described with reference to the one absorber mass 15 that can be seen in FIG. 2. Reducing the lubricant's advance can also be a complete prevention of the lubricant's advance to the at least one absorber mass 15.

The cover component 21 is connected to the primary side 5 via an axial section 23 extending substantially in an axial direction, for example by welding. For this purpose, the axial section 23 has a directed in an axial direction shoulder 25, against which a correspondingly formed shoulder 27 of the cover member 21 is applied. In some other, not shown embodiments, the connection between the cover member and the housing or the primary side can also be done in other ways. For example, the cover component may be formed integrally with the housing. The cover member 21 extends substantially in a radial direction parallel to the primary side 5 and extends further radially inwardly as the spring member 9 extends radially inwardly.

In the vibration damper unit 1, a torque is transmitted from a crankshaft, not shown, via a crankshaft screw 29 to the primary side 5. Further, a ring gear 84 is connected to the primary side 5 and the housing. In some other embodiments, not shown, the means for torque introduction may also be designed differently.

Either directly via the primary side 5 or an indentation 31 in the primary side 5, the spring element 9 of the torsion damper 3 is driven. Additionally or alternatively, the control of the spring element 9 via spring element control shoes 32, as they can be seen for example in Fig. 2 done. In this case, the primary side 5 serves to drive the spring element control shoes 32. The spring element 9 transmits the torque to the secondary side 7, which adjoins in the circumferential direction adjacent to the spring element 8 and may be formed, for example, as Federansteuersteg. On the secondary side 7, the torque can be transmitted to an output shaft, not shown, which rotates about a rotation axis M. In the secondary side 7, a radially inner through hole 33 is introduced. This can serve, for example, for assembly purposes. In some other, not shown embodiments, this through hole can also be omitted. The component comprising the secondary side 7 may also be referred to as a hub or hub disc.

The guide structure 17 of the Tilgerschwingungsdämpfers 13 is attached to the secondary side 7 with a connecting structure 34. In the Tilgerschwingungsdämpfer 13 according to the embodiment of FIGS. 1 and 2 is a Tilgerschwingungsdämpfer with internal absorber masses. The absorber mass 15 is guided between two guide structures 17-a and 17-b, which are opposite one another in the axial direction and which may be formed, for example, in each case as a track plate. The first guide structure 17-a and the second guide structure 17-b are via the connection structure 34 with each other and also connected to the secondary side 7. The connection structure 34 may be, for example, a spacer, a spacer sleeve or a rivet, which connects the two guide structures 17-a and 17-b with each other and / or spaced from each other.

The absorber mass 15 is guided via a roller body 37, as can be seen in FIG. 2, on the first guide component 17-a and the second guide component 17-b. For this purpose, the guide components 17-a and 17-b each have a raceway 39-a and 39-b for the rolling element 37. In the circumferential direction further, not shown absorber masses can be performed on other rolling elements on the guide structure 17. The damper mass 15 essentially has a plurality of plate-shaped individual filter masses 41a, 41b and 41c, which are arranged substantially parallel to one another. These are connected to each other via a non-illustrated fastener. The absorber mass 15 has a passage opening 43, which passes through the rolling element 37. In the present embodiment, the passage opening in the outer Einzeletilgermassen 41 -a and 41 -b has a larger diameter than in the inner Einzeletilgermasse 41-c. Accordingly, the rolling element 37 has different diameters, with which it is located in the passage opening 43 of the absorber mass 15. With its axially outermost rolling surfaces 45, and 47, which represent the smallest diameter of the rolling element 37 in the present embodiment, the rolling element 37 rolls along raceways 39-a and 39-b, which are located on or in the guide structures 17 -a and 17-b are off.

In some other embodiments, not shown, the absorber masses can be designed differently. For example, these may comprise a greater or lesser number of Einzeletilgermassen or be integrally formed. Also, the rolling elements may be formed in other ways, for example not as a step roller. So he may for example have a uniform diameter.

The Tilgerschwingungsdämpfer 13 further comprises a support body 49. This may for example be annular and is arranged via a shoulder 51 on the secondary side 7 radially within the absorber mass 15. The support body 49 can serve, for example, as a radial stop for the absorber mass 15. In some other, not shown embodiments of a vibration damper unit, which may also be referred to as a two-mass flywheel with a speed-adaptive absorber, a chambering of the torsion damper and the Tilgerschwingungsdämpfers via at least one sealing membrane or a plurality of sealing membranes, as well as the support body, which may also be formed as a support ring can be reached.

As can be seen in FIG. 1, the sealing membrane 19 is likewise fastened to the guide structures 17-a and 17-b by means of the connecting structure 34, which connects the two guide structures 17-a and 17-b. By the connecting structure 34, the sealing membrane in the axial, radial and circumferential direction is fixed to the guide structure 17. In some other embodiments, not shown, a montage or production-related game may be allowed between the sealing membrane and the guide structure.

The sealing membrane 19 comprises a first sub-membrane 59 and a second sub-membrane 60. The sub-membrane 59 is arranged on one side of the guide structure 17-a, which faces away from the absorber mass 15. Similarly, the second sub-membrane 60 is disposed on one side of the guide structures 17-b, which faces away from the absorber mass 15. The first sub-membrane 59 has a side portion 64-b which expands substantially in a radial direction. The side portion 64-b projects further radially outward than a radial height to which the absorber mass 15 can be deflected. Radially inwardly, the side portion 64-b of the first sub-membrane 59 extends at least to a radial height on which the connecting structure 34 is arranged. Thus, in the exemplary embodiment of FIGS. 1 and 2 or the partial membranes 59 and 60 or their side sections 64-b and 64-a, the sealing membrane 19 only just extends to over half the radial extent of the guide structures 17-a and 17-b , In further embodiments, not shown, the sealing membrane may also extend further radially inward. In some other embodiments, not shown, the sealing membrane may also be formed as a one-piece component. The side portion 64-b has an indentation 66, with which the side portion 64-b conforms to a corresponding recess of the guide member 17-a. As a result, for example, a space can be reduced in the axial direction. In a region in which the absorber mass 15 can protrude radially outward from the guide structures 17a and 17b, the sub-membrane 59 or the side portion 64-b has a shoulder, so that the sub-membrane 59 is substantially flush with an inner side 68 of the guide structure 17-a expands in a radial direction. At a radial height which is slightly further radially outward than an outer edge of the absorber masses 15 at a maximum deflection, a separating portion 70 adjoins the side portion 64-b. The separating portion 70 extends substantially in an axial direction and engages over the absorber masses 15. In the present embodiment, the separating portion 70 extends in the axial direction to a side 72 of the absorber mass 15, which is directed in an axial direction and that of the first guide structure 17-a is turned away. In some other embodiments, not shown, the separating portion may also have an angle to the axis of rotation M and may for example be conical.

The sub-membrane 60 has a side portion 64-a that is substantially analogous to the side portion 64-b. To the side portion 64-a of the partial membrane 60 includes an overlap portion 74 at. The overlapping portion 74 extends substantially in an axial direction. In this case, the overlapping section 74 is arranged at a greater radial height than the separating section 70 of the sub-membrane 59. The first sub-membrane 59 and the second sub-membrane 60 overlap in the axial direction. For this purpose, the overlapping section 74 of the sub-membrane 60 overlaps with an overlapping section 76 which adjoins the separating section 70 of the sub-membrane 59 in the axial direction. The overlapping section 76 rests with its radially outwardly directed side against a radially inwardly directed side of the overlapping section 74.

In some other embodiments, not shown, the overlapping sections may also be spaced or overlapped in opposite ways. Further, the ends of the sub-membranes may also abut each other in the axial direction or be spaced from each other. The overlapping sections te may for example be connected or not connected to each other.

The overlapping section 74 of the second partial membrane 60 is adjoined by a supporting region 62 on a side of the overlapping section 74 opposite the lateral section 64-a, that is to say on a side of the overlapping section 74 facing the spring element 9. The supporting region 62 extends essentially radially outwards from the overlap portion 74. The support portion 62 overlaps in the radial direction with the cover member 21st The cover component 21 has a shoulder 78 on its inner side facing the spring element 9, so that the cover component 21 has a smaller axial extent at a radial end which points towards the sealing membrane 19. In some other embodiments, not shown, the cover member may be formed without this paragraph.

The sealing membrane 19 or the second partial membrane 60 is supported with the support region 62 against the cover component 21 on the inside of the cover component 21. Between the cover component 21 and the support region 62, a wear reduction structure 80 is arranged. In the present embodiment, the wear reduction structure 80 is a friction ring. This may include as a material, for example, a plastic or Teflon. The wear reduction structure 80 may be attached to either the support portion 62 or the cover member 21. Optionally, the wear-reducing structure 80 may also be arranged floating between the cover component and the support region, that is to say in the circumferential direction. In some embodiments, the wear reduction structure, which may also be referred to as a stop ring, may be disposed axially floating between the hub and the absorber carrier.

In further embodiments, not shown, the sealing membrane can be supported directly on the cover component. In some other embodiments, not shown, the wear reduction structure may also be a coating, a gating and / or a coating on the support region and / or the cover component. In the axial direction, between the primary side 5 and, the primary side 5 facing guide structure 17-a, a disc spring assembly 53 is arranged. The cup spring package 53 is supported in the radial direction with respect to an angle ring 55. The angle ring 55 comprises two legs which enclose an angle of 90 °. One of the legs abuts against the primary side 5. With the other leg of the angle ring 55 is centered on a washer 57 which is secured to the crankshaft screw 29 on the primary side 5. The cup spring package 53 is supported in the axial direction between the primary side 5 and the first guide structure 17-a. In other words, in the embodiment of Figs. 1 and 2, a seal with the sealing membrane 19 via the cup spring assembly 53 and a stop ring causes. The cup spring package 53 is centered on the angle ring 55, which may also be designed as a pressure ring.

3 and 4 show schematic cross-sectional views of a further embodiment of a vibration damper unit 90. The vibration damper unit 90 shown in FIGS. 3 and 4 differs from the vibration damper unit 1 shown in FIGS. 1 and 2 substantially by a Tilgerschwin- vibration damper 92 with external absorber masses 94-a and 94-b, which may also be referred to as a speed-adaptive absorber with a central hub disc. Therefore only differences will be described. Substantially identical or similar components are designated by the same reference numerals as in FIGS. 1 and 2.

The two individual sealant masses 94-a and 94-b are arranged so that they receive a guide structure 98 in the axial direction between them. The component, which can also be referred to as hub disc and includes the guide structure 98, also serves as a secondary side 7 for the torsion damper 3. As can be seen in Fig. 4, the two Einzeletilgermassen 94-a and 94-b are connected to each other via a mounting structure 96 , The fastening structure 96 may be formed, for example, as a rivet. The attachment structure 96 is also guided through a through opening 100 in the guide structure 98, which is lined with a coating, for example an elastomer or a plastic. The absorber mass 94 is guided substantially analogously to the embodiment of FIGS. 1 and 2 via a rolling body 97 on the guide structure. Analogous to the sealing membrane 19 of FIGS. 1 and 2, a sealing membrane 102 of the vibration damper unit 90 also comprises a first part membrane 104 and a second part membrane 106. Here, the first part membrane 104 is between the primary side 5 and the single-piece mass 94-a and the second part membrane 106 arranged on a side facing away from the primary side 5 of the individual piece of adhesive 94-b. The two partial membranes 104 and 106 have an extent in the radial direction which is greater than a radial extent of the absorber mass 94 or of a spatial region in which the absorber mass 94 moves in the radial direction. The sealing diaphragm 102 or the partial diaphragms 104 and 106 are connected to the guide structure 98 radially within a maximum spatial area in which the damper mass 94 moves, via a fastening means 108, as can be seen in FIG. 4.

In regions in which the guide structure 98 has the passage opening 33 radially inside the absorber mass 95, the radially inner ends of the partial membranes 104 and 106 are guided such that they protrude through the passage opening 33. In contrast to the sealing membrane 19, the sealing membrane 102 forms a completely closed envelope or encapsulation for the absorber masses 94.

The two sub-membranes 104 and 106 each have a side portion 110 and 112 which extends substantially in a radial direction and is arranged and aligned parallel to an outer edge of the absorber mass. In some other embodiments, not shown, the side sections may also have heels and / or indentations, for example for stabilization. At the side portion 1 10 closes at a radial height which is slightly higher than a maximum space area in which the damper mass moves 94, the separating portion 70 analogous to the embodiment of FIGS. 1 and 2 at. The overlapping section 76, which overlaps with the overlapping section 74 of the partial membrane 106, adjoins this.

Further, in the embodiment of Figs. 3 and 4 with the crankshaft screw 29 a Beilagwinkelscheibe 1 14 attached to the primary side 5. On this Beilagwinkelscheibe 1 14 is supported in the radial direction from a plastic ring 1 1 6. The plastic ring 1 16 has on its primary side 5 side facing a paragraph 1 18. In some other, not shown embodiments may be used instead of the plastic ring and / or the Beilagwinkelscheibe a similar component made of a different material or with a different shape. At the shoulder 1 18 of the plastic ring 1 1 6 is supported radially inwardly from a plate spring 120. In the axial direction, the plate spring 120 is supported between the primary side 5 and the plastic ring 1 1 6. The plastic ring is supported in an axial direction on the sealing membrane 102 and the partial membrane 104.

In some embodiments, the first sub-membrane 104 may be supported with the separation portion 70 and its overlap portion 76 in the axial direction on the side portion 1 12 of the second sub-membrane 102. This applies analogously to the sub-membranes 59 and 60 of the embodiment of FIGS. 1 and 2. In some other embodiments, not shown, instead of the plate spring and a plate spring assembly may be arranged analogously or similar to the embodiment of FIGS. 1 and 2. Additionally or alternatively, an Axialkraftverlauf in the embodiment of FIGS. 1 and 2 similar to the arrangement of Figs. 3 and 4 are effected.

The sealing membrane 19 or 102 may be a thin material, for example a sheet metal. The support of the sealing membrane 19 or 102 takes place on the cover plate 21 and the guide structure 17 and 98, which can also be referred to as Tilgerträger. Characterized in that the sealing membranes 19 and 102 are arranged and formed in the embodiment of FIGS. 1 to 4 to avoid or at least reduce the risk that a lubricant from the spring portion 1 1 passes to the absorber mass 15 and 94, the Function of the absorber vibration damper 13 and 92 are better or more trouble-free. This is possible because in some vibration damper units under unfavorable circumstances occurring problem can be solved. In some vibration damper units, for example, for sealing a fat space or a spring region of a two-mass flywheel or a torsional vibration damper radially or externally between the cover member and the guide structure, which can also be referred to as a track-carrying Tilgerbauteil, medium or directly attached a resilient sheet metal component. This may possibly only create a seal to the outside become. The radially inside of the spring elements, which can also be referred to as a spring set, arranged Tilgerschwingungsdämpfer, which can also be referred to as drehzahladapti- ver absorber is either not at all or only by a very complex guide structure, which can also be referred to as a track plate, against spray grease protected. In this context, the term "lubricating grease" can be understood to mean a grease, for example a lubricant, which is thrown radially inward when the spring element is compressed very rapidly. This grease or lubricant can get under very unfavorable circumstances between components of Tilgerschwingungsdämpfers and possibly by its shear strength, a free movement of the absorber masses, which can also be referred to as centrifugal weights, prevent or at least limit. The function of the Tilgerschwingungsdämpfers in this case may be hampered or limited and a torsional vibration decoupling could be possible only reduced.

In the vibration damper units 1 and 90 of Fig. 1, 2, 3 and 4 so the sealing membrane 19 and 102 for a chambering of the vibration damper units 1 and 90 used to avoid that lubricant from the spring portion 1 1 to the absorber masses 15 or 94 penetrates. Furthermore, due to the arrangement and design of the sealing membranes 19 and 102, in some embodiments a complex part of the guide structure can be dispensed with. This may be the case, in particular, in embodiments which relate to a damper vibration damper with internal absorber masses.

FIGS. 5 and 6 are schematic representations of another embodiment of a vibration damper unit 130. This differs from the prior art

Vibration damper units 1 and 90 of the preceding embodiments substantially in the formation of a sealing membrane 132. Therefore, only differences will be described below. Identical or substantially similar components are designated by the same reference numerals as in the preceding embodiments. The vibration damper unit 130 also includes a torsion damper 3, which has at least one primary side 5 and at least one secondary side 7, between which at least one spring element 9 is coupled in such a way that a torque transmission from the primary side 5, which may also be formed as a primary flywheel, to the secondary side 7 takes place via the at least one spring element. Analogous to the preceding exemplary embodiments, a plurality of spring elements 9 can be arranged in the circumferential direction, as can be seen for example in FIG. 5. The spring elements 9 are supported in the circumferential direction relative to the secondary side 7.

The vibration damper unit 130 also includes a damper vibration damper 13 that includes at least one damper mass 15 and at least one guide structure 17, the guide structure 17 being configured to movably guide the at least one damper mass 15 to dampen a vibrational component of rotational motion. Further, the vibration damper unit 130 includes the seal diaphragm 132 that at least partially separates the vibration damper unit 130 from a space portion 134 located outside the vibration damper unit 130, advances a lubricant to the space portion 134 located outside the vibration damper unit 130, or infiltrates or dirt particles into the vibration damper unit 130 at least reduce. The sealing membrane 132 is supported on the guide structure 17 via the wear reduction structure 80 against a cover component 21 of the vibration damper unit 130. A material of the wear-reduction structure 80 differs from a material of the cover component 21 and of a material of the sealing membrane 132.

The wear reduction structure 80 is a separate component in the embodiment of FIGS. 5 and 6. For example, the wear reduction structure 80 may be formed as a friction ring. The wear reduction structure 80 may be circumferentially movably disposed between the sealing membrane 132 and the cover member 21 in some embodiments. In these cases, the wear reduction structure 80, which may also be a stop ring, not connected to the sealing membrane 132 or the cover member 21 and / or fixed thereto. The sealing membrane 132 is substantially similar or similar to the partial membrane 60 of the embodiment of FIGS. 1 and 2 formed. In the embodiment of FIGS. 5 and 6, the sealing membrane 132 has no part which is arranged in the axial direction between the Tilgerschwingungsdämpfer 13 and the primary side 5. Furthermore, the sealing membrane 132 also does not comprise a section in order at least in sections to effect a sealing action between the torsion damper 3 and the absorber vibration damper 13.

Radially inwardly, the sealing membrane 132 extends further than to a radial height on which the connection structures 34 for connecting the guide structures 17-a, which in some embodiments may also be formed as a motor-side track plate, and 17-b are arranged, as shown in FIG 5 recognizable. The sealing membrane 132 is also connected to the connection structure 34 with the guide structure 17-b. A radially inner edge 156 of the sealing membrane 132 is substantially circular, but has at least one recess 157 for assembly reasons. Reference numeral 158 denotes a radially inner end of the guide structure 17-b, which extends almost as far as a radially outer region 136 of an output hub 138. The output hub 138 has an internal toothing. Thus, optionally also radially inside the absorber mass 15, an at least partially sealing effect can be made possible.

The secondary side 7 is connected via a fastening structure 140 to a flange 142 of an output hub 138. The attachment structure 140 may be formed, for example, as a rivet or rivet bolt. In some embodiments, the secondary side may also be encompassed by the hub.

The sealing membrane 132, which can also be referred to as a sealing plate or membrane, has, as can be seen in FIG. 5, because the covering component 21 is not shown, likewise the supporting region 62. This extends substantially in a radial direction. To the support portion 62 includes via a shoulder 144 a side portion 146, which extends in a substantially radial direction. The side portion 146 will be described in more detail below. At the support area 62 and radially outwardly of the shoulder 144, the wear reduction structure 80 is placed, which is not shown in Fig. 5.

In the radial direction connects to the shoulder 144, as part of the side portion 146, a flyweight section 148 at. The flyweight section 148 is located at an axial height which substantially corresponds to an axial height on which there is an inner edge 150 of the second guide structure 17-b, which may also be formed as a gear-side track plate. The flyweight section 148 is adjoined by a further shoulder 152 by a guide structure section 154, which essentially conforms to an outer contour, that is to say a side of the guide structure 17-b facing away from the absorber mass 15. For this purpose, the sealing membrane 132 in the guide structure section 154 in the areas around the connecting structure 34 each indentations 155 on.

Similar to the previous embodiments, the cup spring assembly 53 is supported via an angle ring 55 on the primary side 5. The angle ring 55 has a greater extent radially outward than the plate spring package 53, so that the plate spring assembly in the axial direction is fully supported on the angle ring 55 and not on an inner side of the primary side 5. In the axial direction, a plastic ring 160 is disposed between the first guide structure 17-a and the cup spring assembly 53, which may also be referred to as thrust washer. In other embodiments, this may also include or be made of another material. This results in an axial force curve for the vibration damper unit 130, which exclusively via the primary side 5, the angle ring 55, the plate spring package 53, the plastic ring 1 60, the guide structure 17-a, the secondary side 7, the second guide structure 17-b, the sealing membrane 132nd and the wear reduction structure 80 extends to the cover member 21. Instead of the plate spring package 53 may be arranged in some embodiments, only a plate spring.

The vibration damper unit has, as can be seen in FIG. 6, a connection structure 1 62, which is connected to the primary side 5 via a bearing flange 164. For this purpose, a plurality of rivet bolts 166 is used. Of course, in other, not shown embodiments, the connection structure may be formed in other ways or in other ways with the primary side 5 Ver. to be bound. Furthermore, an additional mass 1 68 is attached to the primary side 5 designed as a housing.

The cover component 21 has, in the embodiment of FIGS. 5 and 6, as can be seen in FIG. 6, an indentation 170. By the indentation 170, the cover member 21 is deformed in the axial direction towards the spring element 9 and a spring portion 1 1 tapers. About the indentation 170, a control of the spring element 9 is possible. In some other embodiments, the control of the spring element can also be done in other ways, for example via spring control shoes.

FIGS. 7 and 8 show different views of a vibration damper unit 180 according to a further embodiment. This is essentially analogous to the vibration damper unit 130 according to the embodiment of FIGS. 5 and 6, and also includes the sealing membrane 132. Therefore, only differences will be described below. The same or substantially similar components are given the same reference numerals.

In the embodiment of Figs. 7 and 8, the secondary side 7, which may also be referred to as a hub or hub disc, is integrally connected to the component comprising the output hub 182. The output hub 182 includes an internal gear similar to the previous embodiments. Furthermore, the primary side 5 is connected to a sprocket 184 on a drive side.

The angle ring 55, against which the plate spring package 53 is supported, is supported in the radial direction on a washer 186. In the embodiment of FIGS. 7 and 8, the leg of the angle ring 55, which is arranged parallel to the primary side 55, radially outward on a smaller extent than the plate spring package 53. Thus, the cup spring assembly 53 is supported at least in sections on an inner side of the primary side 5. In some other embodiments, not shown, this arrangement can also be designed differently.

The exemplary embodiments disclosed in the preceding description, the following claims and the attached figures as well as their individual features Both individually as well as in any combination for the realization of an embodiment in its various forms and importance be implemented.

REFERENCE CHARACTERS

I vibration damper unit

3 torsion dampers

5 primary side

7 secondary side

9 spring element

I I pen area

13 absorber vibration damper

15 absorber mass

17 Management structure

19 sealing membrane

21 cover component

23 axial section

25 paragraph axial section

27 paragraph cover component

29 crankshaft screw

31 Indentation

32 spring element driving shoe

33 through hole

34 connection structure

37 rolling elements

39 career leadership structure

41 individual filter mass

43 passage opening

45 rolling surface

47 rolling surface

49 supporting body

51 paragraph

53 plate spring package

55 angle ring

57 washer

59 partial membrane Partial membrane support area

side portion

impressing

inside

separating section

Page absorber mass

overlapping portion

paragraph

Wear reducing structure opening

Vibration damper unit Tilgerschwingungsdämpfer Tilgermasse

attachment structure

rolling elements

management structure

coating

sealing membrane

part membrane

fastener

side portion

Beilagwinkelscheibe

Plastic ring

paragraph

Belleville spring

Vibration damper sealing membrane

space area

radially outboard area 138 output hub

140 fixing structure

142 flange output hub

144 paragraph

146 side section

148 centrifugal weight section

150 inside leadership structure

152 paragraph

154 management structure section

155 imprint

156 radially inner edge sealing membrane

157 recess sealing membrane

158 radially inner edge Guide structure 160 Plastic ring

162 connection structure

164 bearing flange

166 rivet bolts

168 additional mass

170 Indentation

180 vibration damper unit

182 output hub

184 sprocket

M rotation axis

Claims

claims

1 . Vibration damper unit (1, 90), for example for a drive train of a motor vehicle, having the following features: a torsion damper (3) having at least one primary side (5) and at least one secondary side (7) coupled between the at least one spring element (9) is such that a torque transmission from the primary side (5) to the secondary side (7) via the at least one spring element (9), wherein the at least one spring element (9) in a spring portion (1 1) is arranged, which during operation of the Vibration damper unit (1, 90) comprises a lubricant; and a damper vibration damper (13, 92) comprising at least one damper mass (15, 94) and at least one guide structure (17, 98), wherein the guide structure (17, 98) is designed to hold the at least one damper mass (15, 94). movable to dampen a vibration component of a rotational movement; and a sealing membrane (19, 102) at least partially separating the spring portion (11) from the at least one damper mass (15, 94) to reduce lubricant penetration to the at least one damper mass (15, 94) the sealing membrane (19, 102) on the guide structure (17, 98) and a cover member (21) of the vibration damper unit (1, 90) is supported.

2. Vibration damper unit according to claim 1, wherein the sealing membrane (19, 102) on the guide structure and the cover member (21) of the vibration damper unit (1, 90) is supported in the axial direction.

3. Vibration damper unit according to one of the preceding claims, wherein between the sealing membrane (19, 102) and the cover member (21) a wear reduction structure (80) is arranged, which differs from the material of the cover component (21).

4. Vibration damper unit according to one of the preceding claims, wherein the cover member (21) is a part of a housing (5) of the vibration damper unit (1, 90) and / or of the torsion damper (3).

5. Vibration damper unit according to one of the preceding claims, wherein the sealing membrane (19, 102) on the guide structure (17, 98) is attached.

6. Vibration damper unit according to one of the preceding claims, wherein the sealing membrane (19, 102) comprises a first part membrane (59) and a second part membrane (60).

7. vibration damper unit according to claim 6, wherein the first sub-membrane (59) is arranged on an axially opposite side to the second sub-membrane (60).

8. Vibration damper unit according to one of the preceding claims 6 or 7, wherein the second sub-membrane (60) has a support region (62) which bears against the cover member (21).

A vibration damper unit according to any one of the preceding claims 6 to 8, wherein the second sub-diaphragm (60) has an overlapping portion (74) overlapping an overlapping portion (76) of the first sub-diaphragm (59).

10. Vibration damper unit according to one of the preceding claims; according to one of the preceding claims, wherein the at least one absorber mass (94) in the axial direction outside of the guide structure (98) is arranged and the sealing membrane (102) radially within the at least one absorber mass (94) on the guide structure (98) is supported.

1 1. Vibration damper unit according to one of the preceding claims 1 to 9, wherein the at least one absorber mass (15) in the axial direction between at least a first and a second guide structure (17-a, 17-b) is arranged and the sealing membrane (19) with a connecting structure ( 34), the first and second leaders connecting structure (17-a, 17-b) is attached to at least one of the guide structures (17-a, 17-b).

12. Vibration damper unit according to one of the preceding claims, further comprising a plate spring (120) or a cup spring pacts (53), wherein the Tilger- vibration damper (13, 92) in an axial direction over the plate spring (120) or the plate spring package (53) against the primary side (5) and over the sealing membrane (19, 102) against the cover member (21) is supported.

13. Vibration damper unit (130, 180), for example for a drive train of a motor vehicle, having the following features: a torsion damper (3) having at least one primary side (5) and at least one secondary side (7) between which at least one spring element (9) is coupled so that a torque transmission from the primary side (5) to the secondary side (7) via the at least one spring element (9); and a damper vibration damper (13) comprising at least one damper mass (15) and at least one guide structure (17), said guide structure (17) being adapted to movably guide said at least one damper mass (15)

Dampening vibration component of a rotary motion; and a sealing membrane (132) separating the vibration damper unit (130, 180) at least partially from a space portion (134) located outside the vibration damper unit (130, 180) to allow lubricant to advance to the outside of the vibration damper unit (130, 180) Space (134) or at least to reduce penetration of interfering bodies or dirt particles into the vibration damper unit (130, 180), wherein the sealing diaphragm (132) rests against the guide structure (17) and against a cover component (80) via a wear reduction structure (80). 21) of the vibration damper unit (130, 180) is supported, wherein a material of the wear reduction structure (80) differs from a material of the cover component (21).

14. The vibration damper unit according to any one of claims 3 to 13, wherein the wear reducing structure (80) is circumferentially movably disposed between the seal diaphragm (132) and the cover member (21).

15. Vibration damper unit according to one of the preceding claims, further comprising a plate spring (55) or a plate spring package (53) which is designed and arranged to a Axialkraftverlauf of the primary side (5) via the guide structure (17), the sealing membrane (132) and effecting the wear reducing structure (80) to the cover member (21).