DE102011085106A1 - Torsional vibration damping device for use in torque transmission device of motor vehicle, has flange provided with recess, and absorber mass that is connected with flange, where distance element is connected to absorber material - Google Patents

Abstract

The torsional vibration damping device (1) has a flange (2) provided with a recess (3), and an absorber mass (4a,4b) that is connected with the flange. The absorber mass is displaced under centrifugal force relative to the flange. A distance element (6a) is firmly connected to the absorber material or is formed integrally with the absorber material. The distance element is partially arranged within the recess of the flange. A stopper damping element (9) is arranged between an edge area of the recess and an edge area of the distance element in radial direction (R). An independent claim is included for a torque transmission device of a motor vehicle, which has a torsion damper.

Description

The present invention relates to a torsional vibration damper device with a flange having at least one recess, at least one associated with the flange and under centrifugal force relative to the displaceable damper mass, and at least one spacer element which is fixedly connected to the absorber mass or formed integrally with the absorber mass. Further, the present invention relates to a torque transmission device for a motor vehicle having at least one torsion damper and at least one torsional vibration damper device, wherein the torsional vibration damper device is disposed on an output side of the torsion damper.

In the DE 102 24 874 A1 For example, a torsional vibration absorber device with a flange having a plurality of recesses is disclosed. Several Tilgermassenpaare are each connected to the flange and displaceable under centrifugal force relative to the flange. Each absorber mass pair has two absorber masses spaced apart by rivets, which can come into contact with an edge region of the respective recess of the flange when the absorber mass pair is displaced under centrifugal force.

It is an object of the present invention to provide a torsional vibration damper device and a torque transmission device for a motor vehicle in which impact noises, especially at low speeds and in start / stop operation, can be damped.

This object is achieved by a torsional vibration damper according to claim 1 with a flange having at least one recess, at least one associated with the flange and under centrifugal force relative to the displaceable damper mass, and at least one spacer element fixedly connected to the absorber mass or in one piece the absorber mass is formed. The spacer is at least partially disposed within the recess of the flange. In the radial direction of the torsional vibration damper device, at least one stop damping device is arranged between an edge region of the recess and an edge region of the spacer, by means of which stop noises of the spacer element on the flange can be reduced or suppressed, in particular at low rotational speeds and in start / stop operation.

Preferred embodiments of the present invention are set forth in the dependent claims.

The torsional vibration absorber is, in particular, a centrifugal pendulum for a motor vehicle. The centrifugal pendulum can be arranged on an output side of a torsion damper. In particular, the flange of the torsional vibration damper device may be formed as the output flange of a dual mass flywheel. The output flange can be non-rotatably connected to a coupling. The clutch may be a single clutch or a double clutch.

For example, the flange of the torsional vibration damper device designed as a centrifugal pendulum can have four recesses, in each of which a spacing element fixedly connected to an absorber mass or integrally formed with the absorber mass is arranged. Tilgermasse or absorber masses and spacer element or spacer elements each form a pendulum mass, which can shift under centrifugal force relative to the flange.

The pendulum masses are tuned and mounted on the flange so that they move at low speeds, especially at speeds less than 600 rev / min under centrifugal force relative to the flange. An abutment of the spacer elements or the respective pendulum mass at the edge region of the respective recess of the flange is reduced or suppressed by the stop damping device.

The damper mass and the spacer are juxtaposed in the axial direction of the torsional vibration damper device and fixedly connected to each other, for example, by one or more rivets extending in the axial direction. However, other types of connection, for example by specially shaped stepped bolts or screws, are possible.

The flange of the torsional vibration damper device is rotatably mounted about a central axis of rotation. Relative to a circumference of the flange, the spacer element of the respective absorber mass is preferably at least in the idle state, that is not under centrifugal force, positioned in the radial direction within the recess of the flange. However, it is also possible that outer areas of the spacer and / or the associated absorber mass are already positioned in the rest position in the circumferential direction of the flange outside the respective recess of the flange.

Preferably, the recess is disposed in an outer periphery of the flange. This makes it possible, as far as possible to arrange the pendulum mass, that is the absorber mass and the spacer element, relative to the flange as far as possible, whereby for the same eradication of the torsional vibrations a lower pendulum mass, that is absorber mass plus mass of the spacer, can be used. However, it is also possible that the recess is formed as an opening, that is separated by an outer web from the outer periphery of the flange.

According to a particularly preferred embodiment, the stop damping device is connected to the one or more spacer elements. Under centrifugal force is thus achieved that the stop damping device is displaced with the spacer to the outside. When the absorber mass has reached its maximum deflection, the centrifugal force continues to ensure that the stop damping device is pressed against the edge region of the spacer element over its entire, radially inward length, whereby undesired detachment of the stopper damping device from the spacer element can be prevented.

Preferably, the stop damping device is connected to the spacer element positively and / or cohesively. For example, provided at the respective ends of the stop damping device clips, which are clipped into corresponding recesses of the spacer element or the spacer elements.

Alternatively or in addition to the connection of the stop damping device with the spacer elements or it is also possible to connect the stop damping device or a further stop damping device with the edge region of the recess of the flange.

Preferably, the stop damping device is formed band-shaped. In particular, the stop damping device is preferably designed as an elastomer or rubber band.

According to a further preferred embodiment, one or both axial edges of the stop damping device are chamfered or rounded. The chamfering or rounding preferably takes place on the flange side, that is to say on the surface of the stopper damping device facing the flange. By chamfering or rounding a space is formed, in which the stop damping device can deform in contact with its abutment partner, in particular with the edge region of the recess of the flange. The risk that it comes to a breaking out of the stop damping device in contact with its abutment partner is thus reduced.

In particular, it is advantageous if the recess of the flange is formed substantially W-shaped. Alternatively or additionally, the stop damping device is formed substantially V-shaped. Preferably, the W and V have rounded angles. Under the influence of centrifugal force, the stop damping device contacts the edge region of the recess of the flange first in the radius of the rounded W, that is to say in the concave region of the recess of the flange. When the absorber mass then tilts together with the spacer, the stopper damping device applies over a greater length to the outer leg of the W. The resulting friction provides additional damping of the movement. In the start / stop mode, the central area of the W projecting outward in the radial direction of the torsional vibration absorber device, that is to say the convex area of the recess of the flange, ensures that the absorber mass can not shift inwardly in the radial direction. Since the stop damping device is substantially V-shaped, the damping takes place in both directions of rotation of the torsional vibration damper device through the legs of the V.

The spacer element preferably has an area lying on the outside in the radial direction of the torsional vibration absorber device and an area lying on the inside in the radial direction. The abutment damping device is designed and arranged only for damping the region lying in the radial direction, so that it is not formed circumferentially around the spacer element. However, it is also possible that the stop damping device is designed to run around the entire outer circumference of the spacer.

In particular, it is advantageous if the stop damping device is arranged only at the radially inward region of the spacer and connected thereto. Preferably, the radially inward region and the radially outward region of the spacer element are formed substantially equally strong in the radial direction. However, it is also possible that the masses of the radially inner region and the radially outer region of the spacer are substantially equal. Due to the aforementioned structure, it is possible that, after the stopper damper has been compressed by abutment against its abutment partner, the radially outward portion of the spacer member comes into abutment with the radially outer edge portion of the recess. This end stop thus forms an overload protection for the torsional vibration damper device, resulting in a shortened tolerance chain. Alternatively or additionally, however, it is also possible that the overload protection by a guide device of Drehschwingungstilgervorrichtung, that is, a running in a flange side and an absorber mass-side opening bolt or a roller carried by the bolt is formed when the bolt or the roller reaches the end of the respective opening or track and comes to rest there.

Further preferably, the absorber masses and the flange overlap in at least one overlap region. In the overlapping area a guide device is arranged, through which the absorber mass is connected to the flange and is displaceable under centrifugal force relative to the flange. The guide means may include, for example, a flange-side port, a damper-mass-side port, and a bolt extending through both ports in the axial direction of the torsional vibration absorber device. The flange-side opening is formed, for example, as an oval or slot, while the absorber mass-side opening is formed, for example, substantially kidney-shaped and pointing radially outward. In addition, the bolt may be provided with a roller to minimize friction and improve the responsiveness of the torsional vibration absorber device.

Furthermore, it is advantageous if the absorber masses are arranged in pairs in the axial direction of the torsional vibration damper on both sides of the flange and in the axial direction by the one or more spacer elements which are fixedly connected to the absorber mass pair or integrally formed with the absorber mass pair, are spaced from each other. As a result, a particularly compact construction of the torsional vibration damper device can be achieved with simultaneously high pendulum mass.

The above object is further achieved according to the invention by a torque transmission device for a motor vehicle according to claim 10 having at least one torsional damper and at least one torsional vibration damper device according to at least one of the preceding embodiments, wherein the torsional vibration damper device is disposed on an output side of the torsion damper. In particular, the torsion damper may be a dual-mass flywheel, wherein the flange of the torsional vibration damper device is designed in particular as the output flange of the dual-mass flywheel.

The present invention will be explained in more detail below with reference to preferred embodiments in conjunction with the accompanying figures. In these show:

1 a half section through a particularly preferred embodiment of a torsional vibration damper device,

2 a cross-sectional view of the torsional vibration damper along the section line YY 1 .

3 a cross-sectional view of an embodiment of a torsional damper with the torsional vibration damper of the 1 and 2 and

4 the torsional vibration absorber device from the 1 and 2 with deflected absorber mass pair.

In the 1 and 2 is a particularly preferred embodiment of a torsional vibration damper device 1 represented for a motor vehicle. Features that are not marked in the present description as essential to the invention are to be understood as optional. Therefore, the following description also concerns further embodiments of the torsional vibration absorber device 1 which have sub-combinations of the features to be explained below.

As in 3 is the torsional vibration absorber device 1 preferably in the drive train of a motor vehicle on an output side of a torsion damper 100 and in the drive direction before a clutch 101 , For example, a single clutch or a double clutch arranged. At the torsion damper 100 it is preferably a dual mass flywheel. To transmit a torque is the torsion damper 100 or on the output side of the torsion damper 100 arranged torsional vibration absorber device 1 preferably non-rotatable with the clutch 101 connected.

The torsional vibration absorber device 1 preferably has several absorber masses 4a . 4b , in particular several Tilgermassenpaare 5 , spaced evenly about the circumference of the torsional vibration absorber device 1 are arranged. Preferably, the absorber masses 4a . 4b cheek-shaped. In the illustrated embodiment, the torsional vibration damper device 1 four absorber mass pairs 5 on.

The torsional vibration absorber device 1 further includes a rotatably mounted about a central axis flange 2 on. Preferably, the flange 2 the torsional vibration absorber device 1 designed as output flange of the dual mass flywheel. In its outer periphery is the flange 2 with recesses 3 Mistake. However, it is also possible that the recesses 3 when Openings or openings within the flange 2 are formed, that is separated from the outer periphery of the flange by a web. The number of recesses 3 or the perforations corresponds to the number of Tilgermassenpaare 5 ,

Each absorber mass pair 5 is in the area of a recess 3 arranged, with the absorber mass pair 5 in an edge region of the recess 3 with the flange 2 overlaps. Such an overlap area 12 is in the circumferential direction of the torsional vibration absorber device 1 on both sides of the recess 3 intended. Each of the overlapping areas 12 has a guide device 13 on, through which the respective Tilgermassenpaar 5 in the axial direction of the torsional vibration absorber device 1 with the flange 2 is connected and under centrifugal force relative to the flange 2 is relocatable.

For this purpose, the guide device 13 one flange-side opening each 15 on. In the illustrated embodiment, the flange-side opening 15 formed as an oval, but may also be formed as a slot or a kidney-shaped hole. In addition, the management facility includes 13 absorber mass ports 16 that in every absorber mass 4a . 4b of the Tilgermassenpaars 5 are provided. The absorber mass-side openings 16 are formed in the illustrated embodiment as kidney-shaped holes, the kidney shape facing in the direction of the outer periphery.

Through the absorber mass-side openings 16 and the flange-side opening 15 each extends a bolt 14 in the axial direction of the torsional vibration absorber device 1 , At the bolt 14 it may be, for example, a stepped bolt or a rivet. Also glands are possible. For better guidance and to reduce friction within the openings 15 . 16 the bolt can have rolling bodies rotatably mounted in its outer circumference. In addition, the bolt can 14 also have collar elements between the one absorber mass 4a and the flange 2 on one side and the other absorber mass 4b and the flange 2 are arranged on the other side, that is in the axial direction A of the torsional vibration damper device 1 spaced from each other to improve the guidance in the axial direction A.

Preferably, the flange 2 a substantially annular shape, wherein the absorber masses 4a . 4b or the absorber mass pairs 5 cheek-shaped in the outer circumference of the ring are arranged. When the torsional vibration absorber device 1 , as shown in the preferred embodiment, four absorber mass pairs 5 has, each absorber mass pair extends 5 over a ring segment of preferably 90 ° in order to maximize the available pendulum mass. However, it is also possible to have a smaller or larger number of Tilgermassenpaaren 5 or absorber masses 4a . 4b provide, which accordingly a larger or smaller ring segment of the flange 2 extend.

Between the axial direction A of the torsional vibration damper device 1 opposing absorber masses 4a . 4b an absorber mass pair 5 are preferably one or more spacers 6a . 6b arranged. The spacers 6a . 6b are with the absorber masses 4a . 4b firmly connected to the formation of the pendulum mass. In the illustrated embodiment, this are per Tilgermassenpaar 5 three rivets 11 provided, each in corresponding holes through the absorber masses 4a . 4b and the spacers 6a . 6b extend through. Instead of the rivets, however, other connection means are possible, for example, stepped bolts or screws. It is also possible the absorber mass 4a . 4b and at least the adjacent spacer element 6a . 6b to train in one piece.

Thus, the absorber masses 4a . 4b preferably in pairs in the axial direction A of the torsional vibration damper device 1 on both sides of the flange 2 arranged in the axial direction A by one or more spacer element 6a . 6b that with the absorber mass pair 5 firmly connected or in one piece with the Tilgermassenpaar 5 are formed, spaced from each other. Instead of the absorber mass pair 5 However, it is also possible, only a single absorber mass 4a or 4b with a single or multiple spacers 6a . 6b to provide as pendulum mass.

In the radial direction R of the torsional vibration absorber device 1 is a stop damping device 9 between an edge region of the recess 3 and an edge region of the spacer or elements 6a . 6b arranged. In the axial direction A of the torsional vibration absorber device 1 is the stopper damping device 9 between next to an absorber mass 4a . 4b , preferably between the two absorber masses 4a . 4b , angeordent.

It is possible that the stop damper device 9 annular around a complete outer periphery of the spacer element 6a . 6b extends. Preferably, the stop damping device 9 However, band-shaped and extends only on the inside in the radial direction R side of the spacer 6a . 6b that is, on the central axis of the torsional vibration absorber device 1 facing side of the spacer element 6a . 6b ,

The stop damping device 9 is with the spacer (s) 6a . 6b connected. In the illustrated embodiment, the connection is made by two clips 10 at the free ends of the band-shaped stop damper 9 are provided, and preferably in one piece with the stop damping device 9 are formed. These clips 10 engage positively in corresponding recesses in the one or more spacer elements 6a . 6b are provided. Alternatively or in addition to the positive connection but also a cohesive connection of the stop damping device 9 with the spacer or elements 6a . 6b possible, for example by gluing.

The stop damping device 9 is preferably formed as an elastomer or rubber band. In particular, it is advantageous if one or both axial edges of the stop damping device 9 chamfered or rounded, as shown in the cross-sectional view in FIG 2 is shown. The chamfers or fillets extend either over the entire elastomer or rubber band or are provided only in individual areas of the elastomer or rubber band. The arranged between the two mutually in the axial direction A opposite chamfers or fillets, flange side web of the elastomer or rubber band is just as wide as, preferably slightly narrower than, the flange 2 ,

As in 1 represented, is the recess 3 of the flange 2 preferably formed substantially W-shaped, wherein the angle of the W are rounded, that is rounded concave and convex. The outer contour of or within the W-shaped recess 3 arranged spacers 6a . 6b is substantially triangular, with the central axis of the torsional vibration damper device 1 rounding point is rounded. Accordingly, provided at this rounding tip stop damper device 9 essentially V-shaped. The angle of the V is equally rounded.

The or the spacer elements 6a . 6b are in the radial direction R of the torsional vibration absorber device 1 in an outside, that is near the periphery 7 and an inner, ie near the center area 8th divisible. Preferably, the radially outer region 7 and the radially inner region 8th formed in the radial direction R equal strong or thick. However, it is also possible that the masses of the radially outer region 7 and the radially inner region 8th are substantially equal in size, that is, the radially outer region 7 of the spacer or elements 6a . 6b in the radial direction R has a lower thickness than the radially inner region 8th , The aforementioned definitions are limits of a preferred interval for determining the radially outer and the radially inner region 7 . 8th specific.

As in 1 is shown, the stopper damper 9 preferably only in the radially inner region of the respective spacer element 6a . 6b arranged. This has the consequence that a contact of the stop damping device 9 with the edge region of the recess 3 of the flange 2 first in the radius of the W, that is in the concave area of the recess 3 , and then only between the leg of the V, that is the straight edge of the stop damping device 9 and the outer leg of the W, that is the straight edge of the edge region of the recess 3 takes place.

Should the pendulum mass deflect more strongly, the area lying in the radial direction R comes out 7 of the respective spacer element 6a . 6b More precisely, a concave flank section of the spacer element (s) 6a . 6b , in contact with the outer edge region of the recess 3 of the flange 2 More specifically, a convex flank portion in the outer edge region of the recess 3 of the flange, which is on the left in 4 is indicated. Accordingly, this area constitutes an end stop providing overload protection for the torsional vibration absorber device 1 forms at too strong deflections of the pendulum mass.

The foregoing embodiments relate to a torsional vibration absorber device 1 with a flange 2 , the at least one recess 3 has, at least one with the flange 2 connected and under centrifugal force relative to the flange 2 displaceable absorber mass 4a . 4b , and at least one spacer element 6a . 6b that with the absorber mass 4a . 4b firmly connected or in one piece with the absorber mass 4a . 4b is formed, wherein the spacer element 6a . 6b at least partially within the recess 3 of the flange 2 is arranged. In the radial direction R of the torsional vibration absorber device 1 is between a peripheral area of the recess 3 and an edge region of the spacer element 6a . 6b at least one stop damping device 9 arranged.

Moreover, the preceding embodiments relate to a torque transmission device for a motor vehicle with at least one torsional damper 100 , in particular a dual-mass flywheel, and at least one torsional vibration damper device 1 according to at least one of the preceding embodiments, wherein the torsional vibration damper device 1 on an output side of the torsion damper 100 is arranged, and in particular the flange 2 of the Drehschwingungstilgervorrichtung 1 is designed as output flange of the dual mass flywheel.

LIST OF REFERENCE NUMBERS

1

 Drehschwingungstilgervorrichtung

2

 flange

3

 recess

4a

 absorber mass

4b

 absorber mass

5

 Tilgermassenpaar

6a

 spacer

6b

 spacer

7

 outside area

8th

 inside area

9

 Stop damper

10

 clips

11

 rivet

12

 overlap area

13

 guide means

14

 bolt

15

 flange-side opening

16

 absorber mass opening

100

 Dampers

101

 clutch

A

 axial direction

R

 radial direction

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 10224874 A1 [0002]

Claims (10)

Torsional vibration absorber device ( 1 ) with a flange ( 2 ), the at least one recess ( 3 ), at least one with the flange ( 2 ) and under centrifugal force relative to the flange ( 2 ) displaceable absorber mass ( 4a . 4b ), and at least one spacer element ( 6a . 6b ), with the absorber mass ( 4a . 4b ) or in one piece with the absorber mass ( 4a . 4b ), wherein the spacer element ( 6a . 6b ) at least partially within the recess ( 3 ) of the flange ( 2 ) and in the radial direction (R) of the torsional vibration damper device (FIG. 1 ) between an edge region of the recess ( 3 ) and an edge region of the spacer element ( 6a . 6b ) at least one stop damping device ( 9 ) is arranged. Torsional vibration absorber device ( 1 ) according to claim 1, wherein the recess ( 3 ) in an outer periphery of the flange ( 2 ) is trained. Torsional vibration absorber device ( 1 ) according to claim 1 or 2, wherein the stop damping device ( 9 ) with the spacer element or elements ( 6a . 6b ) is connected, preferably positively connected and / or materially connected. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 3, wherein the stop damping device ( 9 ) is formed band-shaped, preferably as an elastomer or rubber band. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 4, wherein one or both axial edges of the stop damping device ( 9 ), preferably flange side, chamfered or rounded. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 5, wherein the recess ( 3 ) of the flange ( 2 ) is substantially W-shaped, and / or the stop damping device ( 9 ) is formed substantially V-shaped. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 6, wherein the spacer element ( 6a . 6b ) in the radial direction (R) of the torsional vibration absorber device (FIG. 1 ) on the outside and in the radial direction (R) on the inside ( 7 . 8th ), and the stop damping device ( 9 ) only for damping the radial direction (R) inside area ( 8th ), preferably at the spacer element ( 6a . 6b ), is formed and arranged. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 7, wherein the absorber mass ( 4a . 4b ) and the flange ( 2 ) in at least one overlapping area ( 12 ) overlap, and in the overlap area ( 12 ) a management facility ( 13 ) is arranged, through which the absorber mass ( 4a . 4b ) with the flange ( 2 ), preferably in the axial direction (A) of the torsional vibration absorber device (FIG. 1 ) and under centrifugal force relative to the flange ( 2 ) is displaceable. Torsional vibration absorber device ( 1 ) according to at least one of claims 1 to 8, wherein the absorber masses ( 4a . 4b ) in pairs in the axial direction (A) of the torsional vibration absorber device (FIG. 1 ) on both sides of the flange ( 2 ) are arranged and in the axial direction (A) by the or the spacer elements ( 6a . 6b ), which with the absorber mass pair ( 5 ) firmly connected or in one piece with the Tilgermassenpaar ( 5 ) are formed, are spaced from each other. Torque transmission device for a motor vehicle with at least one torsion damper ( 100 ), in particular a dual-mass flywheel, and at least one torsional vibration damper device ( 1 ) according to at least one of claims 1 to 9, wherein the torsional vibration damper device ( 1 ) on an output side of the torsion damper ( 100 ), and in particular the flange ( 2 ) of the torsional vibration damper device ( 1 ) is formed as the output flange of the dual mass flywheel.

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