WO2016058604A1

WO2016058604A1 - Torsional vibration damper with centrifugal force pendulum

Info

Publication number: WO2016058604A1
Application number: PCT/DE2015/200462
Authority: WO
Inventors: Lionel Huber
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2014-10-16
Filing date: 2015-09-23
Publication date: 2016-04-21
Also published as: DE102014221005B3

Abstract

The invention relates to a torsional vibration damper (1) having an input part (2) arranged about a rotational axis (d) and an output part (3) which can rotate to a limited degree with respect to said input part (2) about the rotational axis (d) and counter to the effect of a spring device (6), and a centrifugal force pendulum (17) with a side facing the spring device (6) and a side facing away therefrom, a pendulum flange (21) which is connected in a rotationally fixed fashion to the output part (3) and pendulum masses (22) which are arranged distributed over the circumference on the pendulum flange (21) and are suspended in an oscillating fashion in the centrifugal force field of the rotating output part (3). In order to be able to balance the torsional vibration damper (1) in an improved way, a cover plate (18) which is fixedly connected to the pendulum flange (21) and engages radially over the centrifugal force pendulum (17) is provided on the side facing away from the spring device (6), and at least one mass element (26) with a balancing device (28) provided in a receptacle region (29) of the at least one mass element (26) on the cover plate (18) is attached radially to the outside of the cover plate (18).

Description

Torsional vibration damper with centrifugal pendulum

The invention relates to a torsional vibration damper with an input part arranged about an axis of rotation and with respect to said output part limited to the rotation axis against the action of a spring device and a centrifugal pendulum with a side facing and facing the spring device, a pendulum flange rotatably connected to the output part and to the pendulum flange arranged distributed over the circumference, pendulum in the centrifugal force field of the rotating output part suspended pendulum masses.

From the documents DE 10 2012 200 966 A1 and DE 10 2013 205 181 A1, generic torsional vibration dampers with centrifugal force pendulums are known in which the centrifugal force pendulum is arranged on the output side. The pendulum flange of the centrifugal force pennet with the pendulum suspended pendulum masses is riveted to a flange, which acts on the output side effective between input part and output part spring means. With the flange and the pendulum flange a hub part is connected, which is rotationally received on a shaft such as transmission input shaft. One way to balance the centrifugal pendulum is not provided. Furthermore, the centrifugal pendulum on the opposite side of the spring device is unprotected.

The object of the invention is the advantageous development of the generic torsional vibration damper in particular to achieve a protection and a balancing ability of the centrifugal pendulum. The object is solved by the subject matter of claim 1. The dependent claims give advantageous embodiments of the subject matter of claim 1 again.

The proposed torsional vibration damper includes an input part arranged about an axis of rotation, which is connected, for example, to a crankshaft of an internal combustion engine and can serve as a primary flywheel mass or contains a primary flywheel mass. The input part can be made of sheet metal stamped and formed from one or more disc parts. At the input part, a starter ring gear for a starter motor or the like can be accommodated. At the input part, a balancing device, for example in the form of introduced into the input part balancing bores or balancing weights may be provided to balance, for example, the input part or a sub-assembly of input part, spring means and output side flange.

Furthermore, an output part is provided which can be rotated about the axis of rotation and which is rotatable relative to the input part against the action of a spring device in a relatively limited manner.

The spring device is preferably formed from circumferentially arranged helical compression springs, for example bow springs, which can be arranged radially one above the other and / or nested into one another, whereby due to the design of their spring parameters such as stiffness and spring capacity a torsional vibration damper with a single or multi-stage characteristic can be provided over the angle of rotation between input part and output part. The spring device can be connected in parallel over at least a portion of the angle of rotation effective friction device. The helical compression springs of the spring device are preferably accommodated in an annular channel and can be mounted in a ring channel. be included in a lubricant reservoir. Preferably, the annular chamber is associated with the input part, wherein a plurality of, for example, two deformed disc parts of the input part form a radially inwardly open annular chamber. The helical compression springs are thereby acted upon at least on rotation of the input part and the output part against each other preferably in the pulling and pushing direction in each case on the input side and output side. For this purpose, in the disk parts axially engaging in the annular chamber Anpragungen be provided, which act on the end faces of the helical compression springs. Axially between the Anpragungen can be provided by radially inwardly into the annular chamber engaging arms of an output-side flange part, which act on the output side of the end faces of the helical compression springs.

With the flange part a hub part is integrally connected or as a separate component, for example by means of rivets, which transmits the torque transmitted via the input part to a subsequent drive train component. The torque transmission can take place via a shaft such as transmission input shaft, wherein the hub part is rotationally interlocked with the shaft. Here, shaft is also understood to mean a journal which is connected, for example, to an input part of a drive train assembly, for example a double clutch, a hydrodynamic torque converter, a rotor of an electric machine or the like. Here, a rotatable mass of the drive unit can serve as a secondary flywheel, so that the torsional vibration damper is formed as a divided flywheel with a primary flywheel assigned to the input part and a secondary flywheel assigned to the output part with arranged between this spring means. It is understood that the hub part next to the mentioned Zugmo- Mentors can also transmit thrust moments of the drive unit via the torsional vibration damper on the internal combustion engine.

In order to isolate torsional vibrations in the drive train, a centrifugal force pendulum with a side facing the spring device and arranged on the output part is arranged in the torsional vibration damper on the output part. For this purpose, a pendulum flange is arranged on the output part, for example on the hub flange and / or the flange part for the output-side loading of the spring device, for example by means of rivets connected thereto. On the pendulum pendulum masses are arranged distributed over the circumference. The pendulum masses are pendulum suspended from pivot bearings against the pendulum flange, so that these pendulum masses form a speed-adaptive torsional vibration damper under the influence of centrifugal force of the rotating torsional vibration damper or its output part, which can be tuned to one or more vibration orders of the internal combustion engine. The pendulum masses can be arranged on both sides of a one-sided pendulum flange, wherein axially opposite pendulum masses can be connected to each other by pendulum masses by means of connecting means, which pass through corresponding recesses of the pendulum flange. Alternatively, the pendulum flange can absorb the pendulum masses in recesses to provide a particularly axially narrow-built centrifugal pendulum. Furthermore, the pendulum can be formed from two axially spaced portions forming, for example, a radially outside the riveting provided with the flange and / or the hub part ring portion having disc portions, wherein in the areas of the pendulum masses are added.

To protect the centrifugal pendulum on the side facing away from the spring device from external influences, such as dirt entry and the like, is at the Feather device facing away from a fixedly connected to the pendulum flange, the centrifugal pendulum radially overlapping cover plate provided. In order to continue to balance the centrifugal pendulum or, in special cases, the entire torsional vibration damper in a sufficient manner, at least one mass element with a balancing device provided in a receiving region of the at least one mass element on the cover plate is radially attached to the outside of the cover plate. The balancing device can be formed from attached balancing weights. However, it has proved to be particularly advantageous to provide balancing bores in the at least one mass element. For this purpose, the at least one mass element is preferably designed with respect to its material thickness in such a way that corresponding, a few axial deep balancing bores covering the balancing mass can be formed. For this purpose, the material thickness of the at least one mass element may be formed stronger than the material thickness of the cover plate, at least in a receiving region of the mass element on the cover plate.

The at least one mass element may for example be formed from a plurality of ring segments, which are distributed over the circumference connected to the cover plate, for example, riveted. In a particularly advantageous manner, the at least one mass element may be designed as a ground ring with a sheet metal thickness which is increased in relation to the sheet thickness of the cover sheet. It has furthermore proven to be advantageous to reshape the at least one mass element in such a way that a double or multiple material layer can be provided at least on the receiving region.

According to an advantageous embodiment of the torsional vibration damper, the balancing bores are arranged at a radial height of and in the circumferential direction between rivets between the cover plate and the at least one mass element. In such an exemplary embodiment with a multilayer mass element, the rivets for fastening the mass element can be riveted to the cover plate by means of at least one material layer adjacent to the cover plate and countersunk in at least one material layer, so that the axial installation space of the torsional vibration damper can be reduced by the rivet - or closing heads of the rivets substantially aligned with the axial end face of the mass element substantially. It has also proven to be advantageous to encapsulate the centrifugal pendulum also radially outward. For this purpose, the at least one mass element can have an axial projection radially on the outside, which axially overlaps the centrifugal force pendulum radially on the outside. With an appropriate design of the axial projection, for example, by appropriate material thickness and the like, the axial approach can be designed as burst protection for the centrifugal pendulum.

In an advantageous embodiment, the torsional vibration damper may have a sub-assembly of the pendulum, the pendulum masses, the cover plate, the at least one mass element and a hub disc of the output part, which is connected to the flange part for the output-side application of the spring means, for example, riveted. In this case, the sub-assembly can be designed as a self-testable unit. Advantageously, this subassembly is balanced by means of the balancing device in front of a connection with the flange part.

The invention will be explained in more detail with reference to the embodiments illustrated in Figures 1 to 5. Showing:

Figure 1 shows the upper part of a rotatable about a rotational axis torsional vibration damper in section.

FIG. 2 shows a subassembly of the torsional vibration damper of FIG. 1 along the cutting line of the riveting of the cover plate with the mass ring

FIG. 3 shows the subassembly of FIG. 2 along the section line of FIG

balancing hole

Figure 4 is a comparison with the torsional vibration damper of Figure 1 modified torsional vibration damper with a mass ring without axial approach

and

FIG. 5 shows a torsional vibration damper which is modified relative to the torsional vibration damper of FIG. 4 and has two mass rings placed one against the other.

FIG. 1 shows the upper part of the torsional vibration damper 1 which can be rotated about the axis of rotation d and accommodated in a predetermined installation space B of a drive train in partial section. The input part 2 is received by means of the screws 4 on a crankshaft of an internal combustion engine. Coaxially to the axis of rotation d, the output part 3 is arranged and rotationally connected by means of the hub part 5 with an externally toothed shaft or an externally toothed pin of a subsequent drive train assembly. Input part 2 and output part 3 are arranged against each other about the rotation axis against the action of the spring means 6 rotatable.

The input part 2 is formed from the formed disc parts 7, 8 and receives radially outside the starter ring gear 9. The disc parts 7, 8 are tightly connected to each other - here welded together - and form the inwardly open annular chamber 10, in which distributed over the circumference arranged helical compression springs 1 1, 12 - here nested bow springs - the spring means. 6 are received and supported radially. The input-side loading of the end faces of the helical compression springs 1 1, 12 in the tensile and shear direction by means of axially into the annular chamber 10 engaging embossings of the disc parts 7, 8. The output-side loading of the end faces by means of the flange 13, which for this purpose radially expanded arms 14, the axially between the embossments each between the end faces of two circumferentially adjacent helical compression springs 1 1, 12 engage. The flange 13 is connected to the hub part 5 by interposing the shims 15 by means of the rivets 16.

By means of the rivet 16, the centrifugal pendulum 17 is further connected to the flange 13 and the hub part and thus to the output part 3. The centrifugal pendulum 17 forms with the hub part 5, the cover plate 18 with the ground ring 19, the sub-assembly 20, which is prefabricated and balanced prior to joining by means of the rivet 16 by means of these riveted in scope - not visible here - rivets. The connection of the input part 2 with the spring device 6 and the Flansch- part 13 is then carried out by making the riveting of the flange 13 with the hub part 5, the pendulum 21, the cover plate 18 and the shims 15 by means of the rivet 16, wherein the penetration of the riveting tool the then closed openings 34 serve.

The centrifugal pendulum 17 is accommodated on the output part 3 by means of the pendulum flange 21. Radially outside are distributed over the circumference of each two spaced over the circumference, non-visible pivot bearings pendulum masses 22 on both sides of the pendulum pendulum added. Here, axially opposite pendulum masses 22 are connected together to pendulum mass pairs. For this purpose, provided with stop buffers 24 and recesses 25 of the pendulum flange 21 by cross-connecting means 23 are provided. This also by means of the rivet 16 On the hub part 5 recorded cover 18 covers the centrifugal pendulum 17 on the opposite side of the spring device 6 in the direction of transmission and protects it against external influences, such as pollution. The cover plate 18 is formed with a lower material thickness than the other components made of sheet metal and carries radially outwardly the mass element 26 designed as a mass ring 19. The mass ring 19 is fastened to the cover plate 18 by means of non-visible, distributed over the circumference rivet. Viewed in the circumferential direction between these rivets, the balancing bores 27 of the balancing device 28 are provided. In order to achieve an optionally increased drilling depth of the balancing bores 27, two material layers 30, 31 are provided in the receiving region 29 of the mass ring 19 on the cover plate 18, which takes place in the embodiment shown by folding material of the mass ring 19 by material deformation. In addition, the material thickness of the mass ring is larger, for example, at least twice as large as the material thickness of the cover plate 18th

The mass ring 19 has a centrifugal pendulum 17 radially outwardly axially overlapping axial projection 32, which serves as a burst protection 33 and 17 retarded under centrifugal force accelerated components in case of defect of the centrifugal force pendulum.

FIG. 2 shows the subassembly 20 of FIG. 1 along the section line through one of the rivets 35, by means of which the ground ring 19 is fastened to the cover plate 18. The rivets 35 are sunk into the ground ring 19 by the openings 36 of the material layer 31 is greater than the diameter of the rivet or closing head of the rivet 35 is formed.

FIG. 3 shows the subassembly 20 of FIG. 1 along the section line through the balancing bores 27 of the balancing device 28, which in the circumferential direction - if necessary - between the rivets 35 (FIG. 2) for receiving the mass ring 19 the cover plate are arranged. By offset in the circumferential direction arrangement of rivets 35 and balancing bores 27, these can be provided at the same radial height in the receiving region 29 of the mass ring 19 on the cover plate 18. 4 shows the upper part of the torsional vibration damper 1 a, which has a modified bursting protection 33a relative to the torsional vibration damper 1 of Figure 1, in partial section. To form the burst protection 33a, the axial mass ring 19a provided on the cover plate 18a without an axial projection is formed only from a sheet metal ring with two folded material layers 30a, 31a. On the disc part 8a of the input part 2a of the axially opposite the centrifugal pendulum 17a bursting ring 32a is provided, which is welded in the embodiment shown radially outside the outer periphery of the centrifugal pendulum 17a with the disc part 8a. Alternatively, a corresponding Berstring can be provided integrally on the disc part, for example, by multiple folding of a sheet metal part by means of a forming process.

5 shows the partial section of another, the torsional vibration damper 1 a of Figure 4 similar torsional vibration damper 1 b in the same representation. In contrast to this, the mass ring 19b of two juxtaposed and riveted by means of the rivets 35b with the cover plate 18b, annular or ring segment-shaped mass elements 26b formed.

Reference sign list torsional vibration damper

a torsional vibration damper

b Torsional vibration damper

introductory

a front section

output portion

screw

hub part

spring means

disk part

a disc part

Starter gear

0 ring chamber

1 helical compression spring

2 helical compression spring

3 flange part

4 arm

5 shim

6 rivet

7 centrifugal pendulum

7a centrifugal pendulum

8 cover plate

8a cover plate

8b cover plate

9 massaging

9a massaging

9b massaging

0 sub-assembly

1 pendulum flange

2 pendulum mass 3 connecting means 4 stop buffer 5 recess 6 mass element 6b mass element 7 balancing bore 8 balancing device 9 receiving area 0 material layer 0a material layer 1 material layer 31 a material layer

32 approach

32a Berstring

33 Burst protection 33a Burst protection

34 opening

35 rivet

35b rivet

36 opening

B space d rotation axis

Claims

claims

1 . Torsional vibration damper (1, 1 a, 1 b) with an about an axis of rotation (d) arranged input part (2, 2a) and with respect to this about the rotational axis (d) against the action of a spring means (6) limited rotatable output part (3) and a centrifugal force pendulum (17) with a side facing the spring device (6) and facing away, rotatably connected to the output part (3) pendulum flange (21) and distributed on the pendulum (21) distributed over the circumference, in the centrifugal force field of the rotating output part (3 ) pendulum suspended pendulum masses (22), characterized in that on the spring means (6) facing away from the pendulum (21) fixedly connected, the centrifugal pendulum (17) radially overlapping cover plate (18, 18 a, 18 b) is provided and radially on the outside of the cover plate (18, 18a, 18b) at least one mass element (26, 26b) with a in a receiving region (29) of the at least one mass element (26, 26b) on the cover plate (18, 18a, 18b) v located balancing device (28) is attached.

2. torsional vibration damper (1, 1 a, 1 b) according to claim 1, characterized in that the at least one mass element (26, 26b) as a ground ring (19, 19a, 19b) with respect to the plate thickness of the cover plate (18, 18a, 18b) enlarged sheet thickness is formed.

3. torsional vibration damper (1, 1 a, 1 b) according to claim 1 or 2, characterized in that the at least one mass element (26, 26 b) at least on the receiving area (29) a double material layer (30, 30 a, 31, 31 a ) having.

4. torsional vibration damper (1, 1 a, 1 b) according to any one of claims 1 to 3,

characterized in that the balancing device (28) in the form of balancing bores (27) in the at least one mass element (26, 26 b) is introduced.

5. torsional vibration damper (1, 1 a, 1 b) according to claim 4, characterized in that the balancing bores (27) at a radial height of and in the circumferential direction between rivets (35) between the cover plate (18, 18a, 18b) and the at least one mass element (26, 26 b) are arranged.

6. torsional vibration damper (1, 1 a) according to one of claims 3 to 5, characterized in that the rivet (35) between an adjacent material layer (30, 30a) of the at least one mass element (26) and the cover plate (18, 18a) arranged and arranged sunk in the second material layer (31, 31 a).

7. torsional vibration damper (1) according to one of claims 1 to 6, characterized in that an axial projection (32) of the at least one mass element (26) radially outside an outer circumference of the centrifugal pendulum (17) overlaps axially.

8. torsional vibration damper (1) according to claim 7, characterized in that the axial projection as a burst protection (33) for the centrifugal pendulum (17) is formed.

9. torsional vibration damper (1, 1 a, 1 b) according to any one of claims 1 to 8,

characterized in that from the pendulum flange (21), the pendulum masses (22), the cover plate (18, 18a, 18b), the at least one mass element (26, 26b) and a hub part (5) of the output part (3) has a Unterzusammenbau ( 20) is formed, which is connected to a flange part (13) for the output-side loading of the spring means (6).

10. torsional vibration damper (1, 1 a, 1 b) according to claim 9, characterized in that the sub-assembly (20) by means of the balancing device (28) is balanced before connection to the flange part (13).