DE102011122960B3 - A torsional vibration absorber device and a torque transmission device for a motor vehicle - Google Patents

Abstract

A torsional vibration damping device (7) having a flange (8) mounted rotatably about a central axis and at least one absorber mass (9) displaceable relative to the flange (8) by centrifugal force, characterized in that the absorber mass (9) between two in the axial direction (A) of Drehschwingungstilgervorrichtung (7) opposite side elements (11 a, 11 b) is mounted displaceably, and the side members (11 a, 11 b) rotatably connected to the flange (8), wherein the absorber mass of a plurality, in the axial direction next to each other or spaced from each other, is not separately formed by riveting interconnected parts and each part of the absorber mass (9) by means of several in the axial direction (A) extending rollers (14) between the two side elements (11 a, 11 b) is pivotally mounted, wherein the rollers (14) extend in their middle region respectively through holes (2) in each part of the absorber mass (9), where at the axial ends (15a, 15b) of the rollers (14) are slidably mounted in corresponding recesses or openings (17a, 17b) of the side members (11 a, 11 b), wherein the recesses or openings (17 a, 17 b) substantially kidney-shaped or oval or elongated hole-shaped.

Description

The present invention relates to a torsional vibration absorber device according to the preamble of claim 1. Furthermore, the present invention relates to a torque transmitting device for a motor vehicle having at least one torsional 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 10 2006 028 556 A1 a torsional vibration absorber device according to the preamble of claim 1 is disclosed. The torsional vibration absorber device has a flange which is rotatably supported about a central axis. Under centrifugal force, a plurality of absorber masses arranged radially on the outside can be displaced relative to the flange in order to eliminate torsional vibrations occurring during operation, in particular in the low-speed range of rotation. The absorber masses are arranged in the axial direction of the torsional vibration damper device on both sides of the flange and connected to each other by means of stepped bolts which extend through corresponding openings in the flange. Out DE 196 15 890 A1 For example, another rotary vibration absorber device housed in a housing is known.

As a further prior art, the publications DE 196 15890 196 15890 C1 . DE 198 31 160 A1 . DE 10 2008 005 138 A1 . DE 10 2009 042 825 A1 . DE 10 2004 036 791 A1 and DE 10 2006 028 556 A1 called.

It is an object of the present invention to provide a torsional vibration absorber device and a torque transmission device for a motor vehicle in order to simplify the structure of the absorber mass or the absorber masses of the torsional vibration damper device.

The object is achieved by a torsional vibration damper device having the features of claim 1 and by a torque transmission device having the features of claim 8. According to the invention this object is achieved by a torsional vibration damper device according to claim 1 with a rotatably mounted about a central axis flange and at least one displaceable under centrifugal force relative to the flange absorber mass. The absorber mass is displaceably mounted in the axial direction of the torsional vibration damper device between two mutually opposite side elements under the action of centrifugal force. The side elements are non-rotatably connected to the flange.

Thus, the side elements in the axial direction of the torsional vibration damper device limitations to prevent a possible axial movement of the absorber mass or of parts of the absorber mass, by the opposing side elements a two-sided leadership of the absorber mass in the axial direction from the outside is possible.

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

In the central axis about which the flange of the torsional vibration damper device is rotatably mounted, it may, for example, be an axis of rotation defined by a crankshaft of an internal combustion engine and / or an input shaft of a transmission. Similarly, the axis of rotation can be defined by the input or output flange of a torsion damper, in particular a dual-mass flywheel, and / or by the pressure or counterpressure plate of a coupling.

The flange is substantially annular. One or more absorber masses are to be arranged as far as possible in the radial direction of the torsional vibration damper device and arranged displaceable relative to the flange in the radial direction under centrifugal force. Each of the absorber masses may be formed in one piece, but may also be formed of several parts. If the respective absorber mass is formed in several parts, it is no longer necessary by the two in the axial direction on both sides of the absorber mass arranged side elements to connect the individual parts of the absorber mass separately, for example, to rivet. One-piece absorber masses can be designed, for example, as cast components, while the individual parts of multi-part absorber masses are designed, for example, as sheet metal components, preferably as stamped parts. In the case of multipart absorber masses, these are absorber masses whose individual parts are arranged next to one another in the axial direction or spaced apart from one another. The spacing can be effected by one or more further components and / or an air gap.

The side members, between which one or more absorber masses are arranged, are non-rotatably connected to the flange. In particular, the connection of the side members with the flange outside the absorber mass or outside the absorber masses, so that the total mass of the absorber mass or the absorber masses not through openings or recesses in the absorber mass or in the absorber masses, in which connecting means for non-rotatable connection with the Flange are arranged is reduced. In particular, both side elements are on the same side of the Flange arranged and connected to the flange, preferably by the same connecting means. As connecting means preferably bolts, in particular stepped bolts, are provided, which extend in the axial direction of the torsional vibration damper device through the two side members and the flange to connect selbige together.

One of the two side elements is preferably located directly on the flange. For this purpose, the flange in its radial outer region preferably has a circumferential, that is annular recess, in which a radial portion of the one side member is at least partially accommodated.

According to a preferred embodiment, both side elements are formed as sheet metal components. In particular, it is advantageous if both side elements are formed as stamped parts. As a result, a cost-effective production of the two side elements is possible.

According to a particularly preferred embodiment, at least one of the two side elements has in its outer circumference an axially extending peripheral portion which overlaps the absorber mass at least partially in its outer periphery. The peripheral portion of the side member thus forms a burst protection for the absorber mass during operation of the torsional vibration damper device.

In particular, it is advantageous if the two side elements together have a substantially U-shaped cross-section. "Substantially U-shaped" in this context means that each of the two side elements may, for example, also have an L-shaped cross-section, but the two side elements do not collide against the free end sides of the bases of their respective L. Other, for example channel-shaped embodiments of the side elements are possible,

Preferably, the absorber mass is pivotably mounted by means of one or more rollers extending in the axial direction between the two side elements. Preferably, the recesses or apertures for the rollers are the only recesses or apertures having the absorber mass, whereby the total mass effective for eradication can be maximized.

Preferably, the two side elements on recesses or openings, in which axial ends of the roller are slidably mounted. In particular, it is advantageous if the recesses or openings are substantially kidney-shaped. However, other embodiments, such as oval or slot-shaped recesses or openings are possible.

According to another preferred embodiment, the roller has a first collar disposed between one of the side members and a first side surface of the absorber mass, and a second collar disposed between the other of the side members and the other side surface of the absorber mass. If the absorber mass is formed in one piece, the two side surfaces belong to the same component. If the damper mass is formed in several parts, the two side surfaces belong to different, in the axial direction of the torsional vibration damper directly juxtaposed or from each other, for example, by a further part spaced parts of the absorber mass. By the two collars, which are preferably formed integrally with the rest of the role, in particular the roller axis, can be dispensed with separate means for attaching the role.

Preferably, at least two absorber masses are distributed in the circumferential direction of the torsional vibration damper device. Furthermore, at least one stop damping device is preferably arranged between adjacent ends of the absorber masses. The stop damping device serves as an end stop for the displacement of the absorber mass under centrifugal force.

In particular, it is advantageous if the stop damping device is designed as a damping ring. Preferably, a bolt extends through the damping ring, by which the two side plates are in particular preferably connected to the flange. With this construction, the number of parts required for manufacturing the torsional vibration absorber device is reduced and the structure of the torsional vibration absorber device is simplified.

The aforementioned object is further achieved according to the invention by a torque transmission device for a motor vehicle with 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 arranged on an output side of the torsion damper.

In particular, the torsion damper is a dual mass flywheel, wherein the flange of the torsional vibration damper device is preferably formed as the output flange of the dual mass flywheel. Preferably, the torsional vibration absorber device is in Direction of action of the motor vehicle drive between the dual mass flywheel and the clutch is arranged. "In the effective direction of the drive" in this context means that the effect of the torsional vibration damper device between the dual mass flywheel and the clutch is present on the drive train of the motor vehicle. For this purpose, the torsional vibration damper device can be arranged in the axial direction of the drive train between the dual-mass flywheel and the clutch, but this need not necessarily. For example, the Drehschwingungstilgervorrichtung or the absorber masses and the side elements of the torsional Schwingungstilgervorrichtung at least partially in the outer circumference of the dual mass flywheel, in particular in the outer periphery of a bow spring of the dual mass flywheel be arranged.

According to a particularly preferred embodiment, the flange of the torsional vibration damper device is formed as part of a secondary mass of the dual mass flywheel. This makes it possible to reduce the number of parts for manufacturing the torque transmission device and to simplify the structure of the torque transmission device.

• 1 einen Halbschnitt durch ein besonders bevorzugtes Ausführungsbeispiel einer Drehmomentübertragungsvorrichtung, wobei eine Tilgermasse einer Drehschwingungstilgervorrichtung angeschnitten ist,
• 2 einen Halbschnitt durch die Drehmomentübertragungsvorrichtung aus 1, wobei eine Anschlagdämpfungseinrichtung der Drehschwingungstilgervorrichtung angeschnitten ist, und
• 3 eine Draufsicht auf Tilgermassen und Anschlagdämpfungseinrichtungen der Drehschwingungstilgervorrichtung aus den 1 und 2.

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 torque transmission device, wherein a damping mass of a torsional vibration damper device is cut,
• 2 a half-section through the torque transmitting device 1 wherein a stopper damper of the torsional vibration damper device is cut, and
• 3 a plan view of absorber masses and stop damping devices of the torsional vibration damper from the 1 and 2 ,

In the 1 to 3 a particularly preferred embodiment of a torque transmission device 1 is shown 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 relates to other embodiments of the torque transmission device 1 which have sub-combinations of the features to be explained below. In particular, the following description also relates to such embodiments that only a torsional vibration damper device 7 affect.

The torque transmission device 1 is preferably part of a drive train of a motor vehicle. Regarding 1 For example, the torque transmission device 1 on the left side is connected to a crankshaft of an internal combustion engine, not shown, while it is connected on the right side with a transmission, not shown. The torque transmission device 1 indicates on its input side, that is on the left in 1 , a torsion damper 3 on.

Preferably, the torsional damper 3 around a dual-mass flywheel, its primary mass 4 is rotatably connected to the crankshaft of the engine. In its outer periphery has the primary mass 4 a starter tooth wreath 2 on, rotatably with the primary mass 4 connected, and acts on the pinion of a starter motor. About one or more bow springs 6 extending in the circumferential direction U of the torque transmission device 1 is the primary mass 4 of the dual mass flywheel against a secondary mass 5 of the dual mass flywheel for damping torsional vibrations biased. For this purpose, the primary mass 4 and the secondary mass 5 in the figures only indicated, when using two bow springs 6 diametrical approaches on which the opposite ends of each bow spring 6 are in plant. Instead of bow springs 6 However, the dual mass flywheel may also have other energy storage for damping torsional vibrations.

The secondary mass 5 that is provided on the output side of the dual mass flywheel preferably includes a torsional vibration damper device 7 associated flange 8th , At the same time, the bow springs 6 opposite side of the flange 8th also serve as a counter-pressure plate of a clutch. By one in the axial direction A limited displaceable pressure plate of the clutch is a clutch disc between the platen and the pressure plate clamped. When the clutch disc is clamped between the counter-pressure plate and the pressure plate of the clutch, a torque of the internal combustion engine is frictionally transferable to a rotatably connected to the clutch disc output shaft which forms, for example, the input shaft of a flanged to the clutch transmission.

The clutch may be formed, for example, as a normally-engaged clutch, that is, as a clutch in which the force of an engaging disc spring acting on the pressure plate, in the non-actuating state, the force of disengaging leaf springs, which act on the pressure plate outweighs. Upon actuation, the plate spring is acted upon by an actuator with a force, through which the clutch is disengaged. On the other hand, the clutch can also be designed as a normally-disengaged clutch, that is, as a clutch in which the force of the disengaging leaf springs acting on the pressure plate, in the non-actuating state, the force of a lever spring acting on the pressure plate outweighs. Upon actuation, the lever spring is acted upon by an actuator with a force through which the clutch is engaged.

The clutch can equally as a depressed clutch, that is, as a clutch, in which the actuator exerts a pressing force on the plate spring or the lever spring, or as a drawn coupling, that is, as a clutch, wherein the actuator is a pulling force on the plate spring or Lever spring exercises, be trained. Furthermore, the coupling may be formed on the one hand as a dry clutch and on the other hand as a wet clutch. In addition, the coupling can be designed as a single clutch or as a double or multiple clutch.

Relative to the effect of the drive, namely in 1 from left to right, that is coming from the crankshaft of the engine over the primary mass 4 , the bow springs 6, the secondary mass 5 , the rotary vibration absorber device 7 and the clutch on the rotatably connected to the clutch disc output shaft or transmission input shaft, is the torsional vibration absorber device 7 arranged in the effective direction of the drive between the dual mass flywheel and the clutch. Thus, an axis of rotation of the torque transmitting device 1, that is, a central axis about which, among other things, the Drehschwingungstilgervorrichtung 7 is rotatably mounted, for example, defined by the crankshaft of the internal combustion engine and / or the output shaft or the transmission input shaft.

Next to the flange 8th has the torsional vibration absorber device 7 one or more absorber masses 9 on. The absorber masses 9 are in the circumferential direction U the Drehschwingungstilgervorrichtung 7 distributed, preferably evenly distributed, arranged. With respect to the flange 8 are the absorber masses 9 displaced under centrifugal force, that is, at least in the radial direction relative to the flange 8th pivotable.

As in 3 represented, for example, six absorber masses 9 in the circumferential direction U be arranged evenly distributed. However, it is also possible that the torsional vibration damper device 7 less than six, for example four, or more than six, for example eight, in the circumferential direction U spaced absorber masses 9 having. Also an odd number of circumferentially U spaced absorber masses 9 is possible.

The individual, in the circumferential direction U distributed absorber masses distributed 9 can be formed in one piece, for example. In the case of one-piece absorber masses, it makes sense to form these as cast components. Alternatively, however, it is also possible for each of the absorber masses 9 form multiple parts, that is, from several, in the axial direction A form successive parts, as in 1 is shown. It can be the individual parts of the absorber mass 9 be directly in contact with each other or separated by another component or an air gap. Preferably, the individual parts of the absorber mass 9 as sheet metal components, in particular as stamped parts formed.

The absorber masses 9 are between two in the axial direction A the torsional vibration absorber 7 opposing side members 11a . 11b stored displaced under centrifugal force. The two side elements 11a . 11b are non-rotatable with the flange 8th connected. The two side elements 11a . 11b are preferably formed as sheet metal components, in particular preferably as stamped parts.

The page elements 11a . 11b include one of the primary masses 4 facing, first side member 11a and a flange facing, the second side member 11b , A first radial portion 12a of the first side member 11a is from the primary mass 4 , especially with the primary mass 4 connected starter tooth ring 2 through an air gap in the axial direction A of the torque transmission device 1 spaced.

The second page element 11b is preferably in direct contact with the flange 8th , For this purpose, the flange 8th in its radially outer edge region preferably has an annular recess in which the second side member 11b or a second radial section 12b of the second side element 11b at least partially included.

Next to the radial sections 12a . 12b has the first page element 11a preferably a first peripheral portion 13a on while the second page element 11b preferably a second peripheral portion 13b having. The two peripheral sections 13a . 13b extend in the axial direction A the torsional vibration absorber device 7 wherein a free end of the first peripheral portion 13a to the flange 8th points while a free end of the second peripheral portion 13b to with the primary mass 4 the torque transmission device 1 connected starter ring gear 2 has.

In sum, the two side elements 11a . 11b together one essentially U -shaped cross-section, wherein each of the side elements 11a . 11b has a substantially L-shaped cross-section. The free end faces of the two peripheral sections 13a . 13b the cross-sectionally substantially L-shaped side elements 11a . 11b are in the axial direction A spaced apart by an air gap. However, it is also possible that the two end faces are in contact with each other. Likewise it is possible that only one of the two side elements 11a . 11b one in the axial direction A extending peripheral portion 13a . 13b that has the absorber masses 9 at least partially overlaps in its outer circumference and thus a burst protection for the absorber masses 9 in operation of the torsional vibration absorber device 7 represents.

To the pivoting area of the absorber masses 9 For example, it is possible to enlarge the peripheral sections 13a . 13b form thinner than the radial sections 12a . 12b the side members 11a, 11b. Preferably, the peripheral portion 13a respectively. 13b with the radial portion 12a and 12b of the respective side member 11a respectively. 11b each executed in one piece, wherein the peripheral sections 13a . 13b can be produced for example by a forming process. Simultaneously with or before or after the aforementioned forming process, the peripheral sections 13a . 13b to reduce their thickness by another forming process are stretched.

Each of the absorber masses 9 is by means of one or more in the axial direction A extending roles 14 between the two side elements 11a . 11b pivoted. Axial ends 15a, 15b of the rollers 14 are slidable in corresponding recesses or openings 17a, 17b of the side elements 11a . 11b stored. The recesses or perforations 17a, 17b are preferably substantially kidney-shaped, but may also be oval or oblong-shaped. In their middle region, the rollers 14 each extend through holes 20 in the absorber masses 9 , The absorber mass holes 20 are equally preferably substantially kidney-shaped, but may also be formed oval or oblong hole-shaped.

Every role 14 preferably has a first collar 16a between the first side member 11a and a first side surface 10a the absorber mass 9 is arranged, and a second collar 16b that is between the second page element 11b and a second side surface 10b of the absorber mass 9 is arranged on. On the one hand, this makes it possible to separate means for attaching the rollers 14 be omitted, and on the other hand, the axial guidance of the respective absorber mass 9 through the collar 16a . 16b improved.

If the absorber mass 9 is formed in one piece, include the two side surfaces 10a . 10b to the same absorber masses 9 and are in the axial direction A arranged opposite each other. If the absorber mass 9 formed in several parts, the two side surfaces 10a, 10b belong to different parts of the absorber mass 9 or to the outer parts of the absorber mass 9 and are also in the axial direction A arranged opposite each other. Preferably, the collars 16a . 16b one piece with the rest of the roll 14 , in particular the roller axle, formed.

In the circumferential direction U the torque transmission device 1 or the Drehschwingungstilgervorrichtung 7 is between two adjacent ends of two adjacent absorber masses 9 each at least one stop damping device 18 arranged. This stop damping device 18 preferably has a component coated or encased with elastic material. The elastic material may be, for example, an elastomeric or rubber-containing material.

Preferably, the stop damping device 18 designed as a damping ring. In particular, it is advantageous if a bolt passes through the damping ring 19 extends, through which the two in the axial direction A opposite side elements 11a . 11b with the flange 8th are connected. The stop damping device 18 forms for the respective absorber mass 9 an end stop to the pivoting of the absorber mass 9 under centrifugal force limit.

To the parallelism of the two side elements 11a . 11b to ensure a plurality of bolts 19 in the circumferential direction U arranged distributed to the two side elements 11a . 11b with the flange 8th connect to. Bolts 19 are each arranged between two adjacent absorber masses 9. Bolts 19 are preferably designed as stepped bolts or rivets. However, it is also possible, for example, by means of appropriate spacer sleeves, the two side elements 11a . 11b with the flange 8th to screw.

If the distance from the respective bolt 19 to the neighboring absorber masses 9 big enough and the recesses or openings 17a . 17b the page elements 11a . 11b are formed accordingly, the stop damping device 18 also be omitted.

To space in the axial direction A the torque transmission device 1 To save it is advantageous if at least parts of the torsional vibration damper device 7 in the same radial plane as the bow springs 6 of the dual mass flywheel are arranged. Preferably, at least partial areas of the side elements 11a . 11b and / or the absorber masses 9 in the outer circumference, that is radially outside the bow springs 6 arranged the dual mass flywheel.

The foregoing embodiments relate to a torsional vibration absorber device 7 with a rotatably mounted about a central axis or mounted flange 8th and at least one of centrifugal force relative to the flange 8th displaceable absorber mass 9 , where the absorber mass 9 between two in the axial direction A the torsional vibration absorber 7 opposing side members 11a . 11b is mounted displaceably, and the side elements 11a . 11b non-rotatable with the flange 8th are connected.

In addition, the preceding embodiments relate to a torque transmission device 1 for a motor vehicle with at least one torsional damper 3 , in particular a dual-mass flywheel, and at least one torsional vibration damper device 7 according to at least one of the preceding embodiments, wherein the torsional vibration damper device 7 on an output side of the torsion damper 3 is arranged, and in particular the flange 8th the torsional vibration absorber device 7 is designed as output flange of the dual mass flywheel.

LIST OF REFERENCE NUMBERS

1

The torque transfer device

2

Starter gear

3

Dampers

4

primary mass

5

secondary mass

6

bow spring

7

Drehschwingungstilgervorrichtung

8th

flange

9

absorber mass

10a

first side surface

10b

second side surface

11a

first page element

11b

second side element

12a

first radial section

12b

second radial section

13a

first peripheral section

13b

second peripheral portion

14

role

15a

first axial end

15b

second axial end

16a

first collar

16b

second collar

17a

first opening

17b

second opening

18

Stop damper

19

bolt

20

hole

A

axial direction

U

circumferentially

Claims (11)

A torsional vibration damping device (7) having a flange (8) mounted rotatably about a central axis and at least one absorber mass (9) displaceable relative to the flange (8) by centrifugal force, characterized in that the absorber mass (9) between two in the axial direction (A) of Drehschwingungstilgervorrichtung (7) opposite side elements (11 a, 11 b) is mounted displaceably, and the side members (11 a, 11 b) rotatably connected to the flange (8), wherein the absorber mass of a plurality, in the axial direction next to each other or spaced from each other, is not separately formed by riveting interconnected parts and each part of the absorber mass (9) by means of several in the axial direction (A) extending rollers (14) between the two side elements (11 a, 11 b) is pivotally mounted, wherein the rollers (14) extend in their center region through holes (2) in each part of the absorber mass (9), w obei the axial ends (15a, 15b) of the rollers (14) are slidably mounted in corresponding recesses or openings (17a, 17b) of the side members (11 a, 11 b), wherein the recesses or openings (17 a, 17 b) substantially kidney-shaped or oval or elongated hole-shaped. Torsional vibration absorber device (7) according to Claim 1 , wherein the two side elements (11 a, 11 b) are formed as sheet metal components, preferably as stamped parts. Torsional vibration absorber device (7) according to Claim 1 or 2 , Wherein at least one of the two side elements (11 a, 11 b) in its outer periphery in the axial direction (A) ersteckenden circumferential portion (13 a, 13 b), which the Tilgermasse (9) overlaps at least partially in its outer periphery. A torsional vibration absorber device (7) according to at least one of Claims 1 to 3 , wherein the two side elements (11 a, 11 b) together have a substantially U-shaped cross-section. A torsional vibration damper device (7) according to any one of Claims 1 to 4 wherein the roller (14) has a first collar (16a) disposed between one of the side members (11a) and a first side surface (10a) of the absorber mass (9) and a second collar (16b) interposed between the other the side elements (11b) and the other side surface (10b) of the absorber mass (9) is arranged. A torsional vibration absorber device (7) according to at least one of Claims 1 to 5 , wherein at least two absorber masses (9) in the circumferential direction (U) of the torsional vibration damper device (7) are arranged distributed, and between adjacent ends of the absorber masses (9) at least one stop damping device (18) is arranged. Torsional vibration absorber device (7) according to Claim 6 in that the stopper damping device (18) is designed as a damping ring, through which a bolt (19) extends, by which the two side elements (11a, 11b) are connected to the flange (8). Torque transmission device (1) for a motor vehicle with at least one torsional damper (3) and at least one torsional vibration damper device (7) according to one of Claims 1 to 7 wherein the torsional vibration damper device (7) is disposed on an output side of the torsion damper (3). Torque transmission device (1) according to Claim 8 wherein, the flange (8) of the torsional vibration damper device (7) is formed as the output flange of the torsion damper. Torsional vibration absorber device (7) according to Claim 1 , wherein the absorber mass (9) is formed as a sheet metal component. Torsional vibration absorber device (7) according to Claim 1 or 10 , wherein the spacing of the parts of the absorber mass (9) by one or more further components and / or an air gap takes place.

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