CN110662909A

CN110662909A - Torsional vibration damper

Info

Publication number: CN110662909A
Application number: CN201880034692.8A
Authority: CN
Inventors: B·施托贝尔; A·斯塔费尔
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2017-06-02
Filing date: 2018-05-15
Publication date: 2020-01-07
Also published as: DE112018002776A5; WO2018219396A1; DE102018111607A1

Abstract

The invention relates to a torsional vibration damper (10), in particular a dual mass flywheel, a belt disk decoupler or a disk damper, for damping torsional vibrations in the drive train of a motor vehicle, having a primary mass (12) and a secondary mass (20) which form a surrounding receiving channel (14), the secondary mass can be rotated in a limited manner relative to the primary mass (12) by means of an energy storage element (16), in particular an arc spring, wherein the secondary mass (20) has an output flange (18) which projects into the receiving channel (14) for tangential abutment against the energy storage element (16), wherein the output flange (18) has a transfer flange (28) and a connecting flange (30), the transmission flange bears tangentially against the energy storage element (16), and the connection flange is coupled to the transmission flange (28) in a torque-transmitting manner via a free angle. The radial region of the free angle that is realized away from the energy storage element (16) can be transferred into the output flange (18) by means of the multi-part output flange (18), so that a torsional vibration damper (10) having a soft spring characteristic curve and a large free angle can be realized.

Description

Torsional vibration damper

Technical Field

The invention relates to a torsional vibration damper, in particular a dual mass flywheel, a belt disk decoupler or a disk damper, by means of which torsional vibrations in the drive train of a motor vehicle can be damped.

Background

A torsional vibration damper configured as a dual mass flywheel is known, for example, from DE 102015221022 a1, which has a primary mass and a secondary mass which can be rotated in a limited manner relative to the primary mass by means of an arcuate spring, wherein the secondary mass has an output flange which projects into a receiving channel which is formed by the primary mass and serves to receive the arcuate spring.

The following requirements continue to exist for torsional vibration dampers in the drive train of motor vehicles: as soft a spring characteristic as possible is provided and at the same time a sufficiently large free angle is provided.

Disclosure of Invention

The object of the invention is to provide the following measures: which enables a torsional vibration damper with a soft spring characteristic and a large free angle to be realized.

According to the invention, this object is achieved by a torsional vibration damper having the features of claim 1. Preferred configurations of the invention, which can each represent an aspect of the invention individually or in combination, are described in the dependent claims and in the following description.

According to the invention, a torsional vibration damper, in particular a dual mass flywheel, a belt disk decoupler or a disk damper, is provided for damping torsional vibrations in a drive train of a motor vehicle, having a primary mass and a secondary mass which are designed as a circumferential receiving channel and which can be rotated in a limited manner relative to the primary mass by means of an energy storage element, in particular an arc spring, wherein the secondary mass has an output flange which projects into the receiving channel for tangential abutment on the energy storage element, wherein the output flange has a transmission flange which bears tangentially against the energy storage element and a connection flange which is coupled to the transmission flange in a torque-transmitting manner via a free angle.

The at least two-part design of the output flange of the secondary mass allows the free angle to be set by torque-transmitting coupling of the transmission flange to the connection flange of the multi-part output flange. Since no further components have to be arranged in the circumferential direction of the coupling between the transmission flange and the connection flange, a free angle of almost any size can be provided, which in extreme cases is even only slightly less than 360 °. The free angle in the region of the energy storage element can be reduced or even completely avoided, so that more space is left for the energy storage element in the circumferential direction. This can enable the energy storage element to extend more in the circumferential direction and thus achieve a greater distance in order to enable the energy storage element to be compressed by that distance. In this way, a softer spring characteristic curve of the energy storage element, which leads to a more comfortable torsional vibration damping that is perceived, can be achieved compared to a otherwise identical torsional vibration damper in which the free angle to be provided engages the energy storage element in the circumferential direction. The transfer of the free angle away from the radial region of the energy storage element into the output flange can be achieved by the multi-part output flange, so that a torsional vibration damper with a soft spring characteristic and a large free angle can be achieved.

The primary mass and the secondary mass can form a spring-mass system, which is coupled to the primary mass in a torsionally limited manner via an energy storage element, in particular in the form of an arc spring, and which can damp rotational irregularities in the rotational speed and in the torque of the drive power generated by the motor vehicle engine in a specific frequency range. In this case, the moments of inertia of the primary and/or secondary masses and the spring characteristic of the energy storage element, for example, consisting of arcuate springs inserted into one another, can be selected such that vibrations in the frequency range of the dominant engine stage of the motor vehicle engine can be damped. In particular, the moment of inertia of the primary mass and/or the secondary mass can be influenced by the additional mass installed. The primary mass can have a disk to which a cover can be connected, as a result of which an essentially annular receiving space for the energy storage element can be delimited. The primary mass can be stopped tangentially on the energy storage element, for example, by a stamp projecting into the receiving space. An output flange of the secondary mass can project into this receiving space, which can tangentially stop against the opposite end of the energy storage element. When the torsional vibration damper is part of a dual-mass flywheel, the primary mass can have a flywheel that can be coupled to a drive shaft of the motor vehicle engine. When the torsional vibration damper is part of a reel assembly as a reel decoupler (which serves to drive motor vehicle auxiliaries by means of a traction means), the primary mass can form a reel on the radially outer surface of which a traction means, in particular a wedge belt, acts for transmitting torque. It is possible to introduce torque via the primary mass and to derive torque via the secondary mass during normal operation. However, it is also possible to introduce torque via the secondary mass and to derive torque via the primary mass during normal operation.

In particular, the primary mass and the transmission flange bear tangentially against the energy storage element, wherein in particular the energy storage element is designed to bear permanently tangentially against the primary mass and the transmission flange during ongoing operation. In this way, it is possible to avoid the provision of a free angle in the radial region of the energy storage element, so that more installation space can be provided in the circumferential direction for the energy storage element.

Preferably, the energy storage element is preloaded between the primary mass and the transmission flange of the output flange. The pretensioning of the energy storage element ensures that the energy storage element is not lifted from the primary mass or from the transmission flange even in the event of forces during ongoing operation. This also makes it possible to avoid unnecessary material stresses by the stop of the energy storage element on the primary mass or on the transmission flange.

In particular, it is preferred that the free angle provided between the primary mass and the secondary mass is only given by the free angle provided between the transmission flange and the connection flange in the output flange when the direction of relative rotation is reversed. The desired free angle is thus achieved only by the multi-part output flange. This makes it possible to avoid the free angle or a part of the free angle to be set being set at another location. This facilitates the configuration of the remaining components and avoids unnecessary relative movements of adjacent components.

In particular, the transmission flange has a first stop acting in the tangential direction for each relative rotational direction, and the connection flanges each have a second stop acting in the tangential direction, which is directed toward the first stop, wherein the first stop and the second stop can be positioned at a maximum distance from each other in the circumferential direction by the free angle. When the transmission flange passes beyond the connection flange, in the one relative direction of rotation, a first stop provided for this relative direction of rotation abuts against a second stop which is opposite in the circumferential direction. When the relative rotational direction is reversed and the connecting flange exceeds the transmission flange, a second stop provided for this relative rotational direction can be pivoted by the provided free angle toward a first stop lying opposite in the circumferential direction, can be stopped on this first stop and can drive the transmission flange by means of this first stop. When the relative direction of rotation is then reversed again, a first stop of the transmission flange provided for this relative direction of rotation can be rotated by a set free angle toward a second stop opposite in the circumferential direction, stop against this second stop and be driven by the transmission flange. A plurality of constructive solutions can be used to achieve a stop of the transfer flange and the connecting flange which stops each other in the tangential direction. The stop can be realized, for example, by a pin, a through-hole or the like projecting in the axial direction.

Preferably, the transmission flange and the connection flange are coupled by means of a toothing system via a free angle in a torque-transmitting manner. Torque-transmitting couplings can be easily realized by means of the toothing. The free angle can be easily realized by the pitch of the teeth. Furthermore, the toothing can be easily arranged in the axial region of the material thickness of the transmission flange and the connection flange, so that the toothing can be arranged close to the installation space in a neutral manner. This enables the axial installation space requirement to be kept small.

In particular, the toothing is preferably arranged substantially centrally in the axial direction with respect to the energy storage element or is arranged laterally in the axial direction to a center line of the energy storage element extending in the circumferential direction in the direction of the curvature of the transmission flange or of the connection flange. The output flange can be embodied as a substantially planar disk which can be clamped between two parts of the multi-part hub, so that a particularly low installation space requirement of the output flange, which extends centrally with respect to the energy storage element, is achieved. Preferably, in the case of a one-piece hub, the output flange can extend in a curved manner, so that the connecting flange can be fixed on the end face of the hub. In particular, when the rubber damper is to be fixed on the end face of the hub, the connecting flange can also be fixed using a fixing means which is provided for fixing the rubber damper to the hub. In this case, it is advantageous if the toothing is arranged laterally offset with respect to the energy storage element in an axial region of the connecting flange on the end face of the hub. For this purpose, the transmission flange can have, for example, teeth projecting in the axial direction, which engage in tooth spaces of radially projecting teeth of the connection flange. The connection flange is particularly preferably constructed from a hub, so that the hub and the connection flange are constructed in one piece and a low number of components can be achieved.

In particular, the toothing is arranged within the receiving channel or radially inside with respect to the receiving channel. When the toothing is arranged within the receiving channel, it can be arranged on a particularly large radius, which also enables a particularly large free angle. When the toothing is arranged radially inside with respect to the receiving channel, the production costs remain low, since a significantly smaller radius requires correspondingly less machining for the formation of the toothing. The teeth can be arranged on a larger or smaller radius depending on the free angle to be set and the number of pairs of teeth required to transmit a particular maximum torque.

Preferably, friction means are provided between the transmission flange and the connection flange for damping torsional vibrations arising from resonance. The spring-mass system of the torsional vibration damper can be sufficiently damped by the intentionally provided friction, so that excessively strong deflections in the resonance region can be avoided. For this purpose, a relative movement with friction can be generated by means of a relative movement of the transmission flange relative to the connection flange. The friction device can have a first friction partner fixed to the transmission flange and a second friction partner fixed to the connection flange, which are pressed frictionally against one another, for example by means of a spring. These friction partners can be represented, for example, by axial friction rings.

The invention also relates to a reel assembly for driving a motor vehicle auxiliary device by means of a traction means, having a reel for driving the traction means, a hub which can be coupled to a drive shaft of a motor vehicle engine for introducing a torque, and a torsional vibration damper which can be designed and expanded as described above, wherein the reel is part of a primary mass of the torsional vibration damper and the hub is part of a secondary mass of the torsional vibration damper. The transfer of the free angle away from the radial region of the energy storage element into the output flange can be achieved by the multi-part output flange of the torsional vibration damper used as a belt disk decoupler, so that a torsional vibration damper with a soft spring characteristic and a large free angle can be achieved.

Drawings

The invention is elucidated below by way of example with reference to the accompanying drawings, in which the features presented below can present an aspect of the invention both individually and in combination. The figures show:

figure 1 is a schematic cross-sectional side view of a first embodiment of a torsional vibration damper,

figure 2 is a schematic cross-sectional top view of the torsional vibration damper of figure 1,

FIG. 3 is a schematic cross-sectional side view of a second embodiment of a torsional vibration damper

Fig. 4 is a schematic cross-sectional top view of the torsional vibration damper of fig. 3.

Detailed Description

In fig. 1 and 2, a torsional vibration damper 10 is illustrated by way of example as a spool decoupler in a spool assembly for driving auxiliary devices of a motor vehicle by means of a traction means, said torsional vibration damper having a primary mass 12 in the form of a spool which delimits an annular receiving channel 14 for an energy storage element 16 in the form of an arc spring. The outlet flange 18 of the secondary mass 20 projects radially from the inside to the outside into the receiving channel 14. The energy storage element 16 is tensioned at its tangential ends between the primary mass 12 and the output flange 18 with a pretension, without play in the circumferential direction, i.e. without a free angle. The secondary mass 20 has, for example, a two-part hub 22, to which the output flange 18 is fastened. Additionally, a rubber bumper 24 is fixed to the hub 22. The fastening means 26 provided for fastening the rubber buffer 24 and configured as screws also fasten the output flange 18, which extends centrally to the energy storage element 16, to the hub 22 and hold the multi-part hub 22 together. The fastening means 26 may be configured, for example, as a screw connection, a pin connection and/or an interference fit. The rubber bumper 24 can be easily positioned on the hub 22 by configuring the fixing means 26 as positioning pins.

The output flange 18 of the secondary mass 20 has a radially outer transfer flange 28 and a radially inner connecting flange 30. The transmission flange 28 bears tangentially against the energy storage element 16 for transmitting torque, while the connection flange 30 is fixed to the hub 22 by means of the fixing means 26 for transmitting torque. As shown in fig. 2, the transfer flange 28 and the connecting flange 30 are coupled by teeth 36. The transmission flange 28 has a first stop 32 in a toothing 36, which can stop against a second stop 34 of the connection flange 30 in order to transmit torque. Between the

stops

32, 34, in the circumferential direction, a significant gap is provided, which defines a free angle at which the primary mass 12 can twist relative to the secondary mass 20 before the energy storage element 16 is compressed to store mechanical energy when the relative twisting is switched.

In the embodiment of the torsional vibration damper 10 shown in fig. 1 and 2, the teeth 36 are arranged on a large radius, so that the teeth 36 are positioned in the receiving channel 14. As shown in fig. 3, the teeth 36 may also be arranged on a small radius, such that the teeth 36 are positioned radially inward with respect to the receiving channel 14. As a result, as shown in fig. 4, the region to be machined for producing the toothing 36 is smaller than in the embodiment of the output flange 18 shown in fig. 2.

List of reference numerals

10 torsional vibration damper

12 primary mass

14 receiving channel

16 energy storage element

18 output flange

20 secondary mass

22 hub

24 rubber buffer

26 securing device

28 transfer flange

30 connecting flange

32 first stop

34 second stop

36 tooth part

Claims

1. A torsional vibration damper, in particular a dual mass flywheel, a tape disc decoupler or a disc damper, for damping torsional vibrations in a drive train of a motor vehicle, the torsional vibration damper having:

a primary mass (12) configured with a surrounding receiving channel (14); and

a secondary mass (20) which can be rotated in a limited manner relative to the primary mass (12) by means of an energy storage element (16), in particular an arc spring, wherein the secondary mass (20) has an output flange (18) which projects into the receiving channel (14) for tangential abutment against the energy storage element (16), wherein the output flange (18) has a transmission flange (28) which bears tangentially against the energy storage element (16) and a connecting flange (30) which is coupled to the transmission flange (28) via a free angle in a torque-transmitting manner.

2. The torsional vibration damper as claimed in claim 1, characterized in that the primary mass (12) and the transmission flange (28) bear tangentially against the energy storage element (16), wherein in particular the energy storage element (16) is configured to bear permanently tangentially against the primary mass (12) and the transmission flange (28) during ongoing operation.

3. The torsional vibration damper as claimed in claim 1 or 2, characterized in that the energy storage element (16) is preloaded between the primary mass (12) and a transmission flange (28) of the output flange (18).

4. The torsional vibration damper as claimed in any of claims 1 to 3, characterized in that the free angle provided between the primary mass (12) and the secondary mass (20) on reversal of the relative rotational direction is given solely by the free angle provided between the transmission flange (28) and the connecting flange (30) in the output flange (18).

5. The torsional vibration damper as claimed in one of claims 1 to 4, characterized in that the transmission flange (28) has a first stop (32) which acts in the tangential direction for each relative direction of rotation, and the connection flanges (30) each have a second stop (34) which acts in the tangential direction and points toward the first stop (32), wherein the first stop (32) and the second stop (34) can be positioned at a maximum in the circumferential direction at the free angle from one another.

6. The torsional vibration damper as claimed in any of claims 1 to 5, characterized in that the transmission flange (28) and the connection flange (30) are coupled via a tooth (36) via a free angle energy transmission torque.

7. The torsional vibration damper as claimed in claim 6, characterized in that the toothing (36) is arranged substantially centrally in the axial direction with respect to the energy storage element (16) or is arranged laterally in the axial direction to a center line of the energy storage element (16) extending in the circumferential direction in the curved course of the transmission flange (28) or the connection flange (30).

8. The torsional vibration damper as claimed in claim 6 or 7, characterized in that the toothing (36) is arranged within the receiving channel (14) or radially inwardly with respect to the receiving channel (14).

9. The torsional vibration damper as claimed in any of claims 1 to 8, characterized in that friction means are provided between the transmission flange (28) and the connection flange (30) for damping torsional vibration increases caused by resonance.

10. A reel assembly for driving a motor vehicle auxiliary device by means of a traction means, having a reel for driving the traction means, a hub (22) for introducing a torque, which can be coupled to a drive shaft of a motor vehicle engine, and a torsional vibration damper (10) according to one of claims 1 to 9, wherein the reel is part of a primary mass (12) of the torsional vibration damper (10) and the hub (22) is part of a secondary mass (20) of the torsional vibration damper.