阅读说明：本技术 离心摆 (Centrifugal pendulum ) 是由 拉尔夫·埃德尔 于 2020-09-23 设计创作，主要内容包括：本发明涉及一种用于衰减经由机动车发动机的驱动轴导入的转动非均匀性的离心摆,其设有可围绕转动轴线转动且可与驱动轴耦联的承载法兰、可相对于承载法兰摆动引导且朝向承载法兰的第一轴向侧的第一摆块和可相对于承载法兰摆动引导且朝向承载法兰的背离第一轴向侧的第二轴向侧的第二摆块,第一和第二摆块用于产生抵抗转动非均匀性的复位力矩,其中第一摆块与第二摆块经由铆接连接部运动固定地彼此连接,其中铆接连接部由第一摆块和/或由第二摆块一件式地构成。通过铆接连接部与第一摆块和/或第二摆块一件式的设计方案可以减少构件数量和制造成本,使得能够实现低成本地制造离心摆。(The invention relates to a centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine, comprising a support flange which can be rotated about a rotational axis and which can be coupled to the drive shaft, a first pendulum mass which can be pivoted relative to the support flange and faces a first axial side of the support flange, and a second pendulum mass which can be pivoted relative to the support flange and faces a second axial side of the support flange facing away from the first axial side, the first and second pendulum masses being used to generate a restoring moment which counteracts the rotational irregularities, wherein the first pendulum mass and the second pendulum mass are connected to one another in a kinematically fixed manner via a riveted connection, wherein the riveted connection is formed by the first pendulum mass and/or by the second pendulum mass in one piece. The design of the riveted connection in one piece with the first and/or second pendulum mass can reduce the number of components and the production costs, so that a low-cost production of the centrifugal pendulum is possible.)

1. A centrifugal pendulum for attenuating rotational non-uniformities introduced via a drive shaft of a motor vehicle engine, the centrifugal pendulum having:

a carrier flange (16) which can be rotated about a rotational axis and which can be coupled to a drive shaft;

a first pendulum mass (18) for generating a restoring moment against the rotational inhomogeneity, which is guided in a pendulum manner relative to the carrier flange (16) and faces a first axial side of the carrier flange (16), and

a second pendulum mass (20) for generating a restoring moment against the rotational non-uniformity, said second pendulum mass being guided in a manner that enables it to pivot relative to the carrier flange (16) and facing a second axial side of the carrier flange (16) facing away from the first axial side,

wherein the first pendulum mass (18) and the second pendulum mass (20) are connected to one another in a kinematically fixed manner by means of a riveted connection (24),

it is characterized in that the preparation method is characterized in that,

the rivet connection (24) is formed in one piece from the first pivot piece (18) and/or from the second pivot piece (20).

2. Centrifugal pendulum according to claim 1, characterized in that the first pendulum mass (18) has a riveting opening (28) and the second pendulum mass (20) has a protrusion (26) protruding in axial direction towards the first pendulum mass (18), wherein in particular the protrusion (26) of the second pendulum mass (20) is riveted with the riveting opening (28) of the first pendulum mass (18) by plastically deforming the protrusion (26) into an upset.

3. Centrifugal pendulum according to claim 2, characterized in that the rivet opening (28) is provided in a depression (30) of the first pendulum mass (18), wherein in particular in the depression (30) the material thickness of the first pendulum mass (18) is smaller than in the remaining first pendulum masses (18).

4. Centrifugal pendulum according to one of claims 1 to 3, characterized in that the first pendulum mass (18) has a first transition region (32) which engages at least partially axially into the through-opening (22) of the carrier flange (16) and/or the first pendulum mass (18) has a second transition region (34) which engages at least partially axially into the through-opening (22) of the carrier flange (16), wherein the riveted connection (24) is formed at least partially by the first transition region (32) and/or the second transition region (34).

5. Centrifugal pendulum according to claim 4, characterized in that the first adapter region (32) bears axially against the second pendulum mass (20) and/or the second adapter region (34) bears axially against the first pendulum mass (18).

6. Centrifugal pendulum according to one of claims 1 to 4, characterized in that the first pendulum mass (18) and the second pendulum mass (20) are positioned at a defined axial distance apart by at least one spacer element, in particular a stepped bolt, wherein the riveted connection (24) clamps the spacer element at least proportionally between the first pendulum mass (18) and the second pendulum mass (20).

7. Centrifugal pendulum according to the combination of claims 4 and 6, characterized in that a gap (S) is formed radially outside the riveted connection (24) between the first transition region (32) and the second pendulum mass (20) and/or between the second transition region (34) and the first pendulum mass (18).

8. Centrifugal pendulum according to one of claims 1 to 7, characterized in that the first pendulum mass (18) has a plurality of first pendulum plates connected to one another and the second pendulum mass (20) has a plurality of second pendulum plates connected to one another, wherein in the first pendulum mass (18) only the innermost first pendulum plate or all first pendulum plates facing the carrier flange (16) and/or in the second pendulum mass (20) only the innermost second pendulum plate or all second pendulum plates facing the carrier flange (16) are deformed in the axial direction to form the riveted connection (24) and/or to form an adapter region (32, 34).

9. Centrifugal pendulum according to one of claims 1 to 8, characterized in that the carrier flange (16) is reinforced by hardening.

Technical Field

The invention relates to a centrifugal pendulum with which a restoring torque can be generated against rotational irregularities in the drive train of a motor vehicle in order to damp rotational irregularities.

Background

DE 102017111749 a1 discloses a centrifugal pendulum in which a pendulum mass is provided which can be displaced relative to a support flange via rollers guided in corresponding roller tracks and which, in the event of rotational speed fluctuations, can generate a restoring torque which counteracts the rotational speed fluctuations in order to damp the rotational speed fluctuations. The pendulum masses which are arranged on different axial sides of the carrier flange and which are opposite one another are riveted to one another via separate rivets.

There is a continuing need to reduce the manufacturing costs of centrifugal pendulums.

Disclosure of Invention

The object of the invention is to specify measures which enable a low-cost production of a centrifugal pendulum.

This object is achieved according to the invention by a centrifugal pendulum for damping rotational inhomogeneities introduced via a drive shaft of a motor vehicle engine. Preferred embodiments of the invention are given in the following description, which may represent one aspect of the invention individually or in combination.

According to the invention, a centrifugal pendulum for damping rotational inhomogeneities introduced via a drive shaft of a motor vehicle engine is provided with: a carrier flange rotatable about an axis of rotation and couplable to the drive shaft; a first pendulum mass for generating a restoring moment against rotational inhomogeneities, the first pendulum mass being guided in a pendulum manner relative to the carrier flange and facing a first axial side of the carrier flange; and a second pendulum mass for generating a restoring moment against rotational irregularities, which is guided in a pivotable manner relative to the carrier flange and faces a second axial side of the carrier flange facing away from the first axial side, wherein the first pendulum mass and the second pendulum mass are connected to one another in a kinematically fixed manner via a riveted connection, wherein the riveted connection is formed by the first pendulum mass and/or by the second pendulum mass in one piece.

Due to the design of the rivet connection in one piece with the first and/or second pivot piece, separate rivets can be dispensed with, whereby the number of components and the production costs can be reduced. Instead of a separate rivet, the rivet connection can be designed as part of at least one pendulum block, which is demoulded together with the pendulum block. The following knowledge can be utilized here: the respective pendulum mass can be made of steel and/or a plurality of metal plates, so that it is simply possible, by means of a preferably non-cutting machining of the pendulum mass, in particular during the production of the pendulum mass from a semi-finished product, to provide a portion of the riveted connection which is plastically deformed during riveting. For example, the material region of the first pendulum mass and/or of the second pendulum mass can project in the axial direction, whereby the projecting material region can serve as a rivet shank, the free end of which is plastically deformed into an upset when riveting with the other pendulum mass. Alternatively, the riveted connection can be produced by a snap connection ("Clinchen") in that: the protruding material regions are formed together with the other pendulum mass. Due to the design of the riveted connection in one piece with the first pendulum mass and/or the second pendulum mass, the number of components and the production costs are reduced, so that a low-cost production of the centrifugal pendulum is possible.

Under the influence of centrifugal forces, at least one pendulum mass of the centrifugal pendulum is intended to occupy a position which is as far away from the center of rotation as possible. Thus, the "zero position" is the position which is radially furthest away from the centre of rotation and which the pendulum mass can occupy in the radially outer position. The pendulum mass assumes this radially outer position at a constant driving speed and a constant driving torque of the motor vehicle engine. When the rotational speed fluctuates, the pendulum mass deflects along its pendulum path due to its inertia. Therefore, the pendulum mass can be moved in the direction of the center of rotation. The centrifugal force acting on the pendulum mass is thus divided into a tangential component with respect to the pendulum rail and a further normal component with respect to the pendulum rail. The tangential component provides a restoring force which will bring the pendulum mass back to its "zero position" again, while the normal force component acts on a force-introducing element which introduces rotational speed fluctuations, in particular a flywheel connected to the drive shaft of the motor vehicle engine, and there generates a counter torque which counteracts the rotational speed fluctuations and dampens the introduced rotational speed fluctuations. In the case of particularly strong rotational speed fluctuations, the pendulum mass can therefore be pivoted to the greatest extent outwards and can assume the radially inner position to the greatest extent. For this purpose, the rails provided in the carrier flange and/or the pendulum mass have a suitable curvature, in which the coupling elements, in particular designed as rollers, can be guided. Preferably, at least two rollers are provided, which are guided on the roller track of the support flange and on the pivot track of the pivot block. In particular, more than one pendulum mass is provided. Preferably, a plurality of pendulum masses are guided on the carrier flange in a uniformly distributed manner in the circumferential direction. The inertial mass of the pendulum mass and/or the relative movement of the pendulum mass with respect to the carrier flange are designed in particular for damping specific frequency ranges of rotational inhomogeneities of an engine arrangement, in particular of a motor vehicle engine. For example, two pendulum masses are provided which are connected to one another via bolts or rivets, in particular in the form of support bolts, between which the support flange is positioned in the axial direction of the torsional vibration damper.

In particular, the first pendulum mass has a riveting opening and the second pendulum mass has a projection projecting in the axial direction towards the first pendulum mass, wherein in particular the projection of the second pendulum mass is riveted to the riveting opening of the first pendulum mass by plastically deforming the projection into an upset. The projection can be formed by a material region protruding from the remaining material of the second pendulum mass and as a rivet projection forms a rivet shank, the free end of which can be plastically formed as an upset of the rivet connection. If the material thicknesses of the components of the first pendulum mass and of the second pendulum mass which point toward the carrier flange are to be different from each other, the projections are preferably formed in the thicker components, so that they can have as large an extent in the axial direction of the centrifugal pendulum as possible. In particular, the height of the rivet projection extending in the axial direction of the centrifugal force pendulum can substantially correspond to or even exceed the material thickness of the carrier flange, so that the first pendulum mass and the second pendulum mass can be riveted to one another without separate, intermediate connecting components. It is only necessary to provide a rivet opening in the first pendulum mass, so that the projection can be deformed into an upset on the axial side of the first pendulum mass facing away from the second pendulum mass to establish the rivet connection. If the riveting is carried out by a snap connection, the riveting opening can be omitted, as a result of which a correspondingly higher inertial mass for the first pendulum mass can be achieved compared to the rivet opening introduced.

The rivet opening is preferably provided in a depression of the first pendulum mass, wherein in particular in the depression the material thickness of the first pendulum mass is smaller than in the remaining first pendulum masses. The respective pendulum mass may have a relatively large axial thickness in order to be able to provide a sufficiently large moment of inertia for the intended damping effect. By providing the depression in the first pendulum mass, the axially projecting projection of the second pendulum mass does not need to extend over the entire maximum material thickness of the first pendulum mass. Instead, it is sufficient that the thinner region of the first pendulum mass, which is formed by the depression, is sufficient, in particular around the rivet opening, to provide sufficient strength to the rivet connection. A particularly small thickness even in the region of the depression is sufficient if the riveted connection is established by a snap connection. This enables that the protrusions may also protrude from a material having a thinner material thickness. In particular, typical material thicknesses for the pendulum mass may be sufficient to produce a pendulum mass having axially extending projections which may bridge the axial thickness of the carrier flange through-openings formed in the carrier flange.

In particular, it is preferred that the first pendulum mass has a first transition region which engages at least partially axially into the through-opening of the carrier flange and/or the first pendulum mass has a second transition region which engages at least partially axially into the through-opening of the carrier flange, wherein the riveted connection is formed at least partially by the first transition region and/or the second transition region. The transition region can be provided, for example, by a downward-curved course of the respective pendulum mass, wherein in particular the material thickness in the transition region corresponds substantially to the material thickness outside the transition region. The adapter region of the respective pendulum mass can thus protrude into the correspondingly largely designed through-opening of the carrier flange. The axially projecting projection of the second pendulum mass and/or the projecting region produced by the snap connection can thus easily project far enough into the first pendulum mass to establish a form-fitting and in particular non-releasable connection. Furthermore, a rough centering is already possible by the adapter region of the respective pendulum mass inserted into the through-opening, which facilitates the installation of the centrifugal pendulum.

In one embodiment, it can be provided that the first transfer region bears axially against the second pivot piece and/or that the second transfer region bears axially against the first pivot piece. By means of the contacting adapter regions, the axial relative positions of the parts of the pendulum masses outside of the at least one adapter region can be predetermined relative to one another, without additional step bolts or other spacer elements being required for this purpose, which are clamped between the pendulum masses. This can further reduce the number of components.

In a further embodiment, it can be provided that the first pendulum mass and the second pendulum mass are positioned at a defined axial distance apart by at least one spacer element, in particular a stepped bolt, wherein the rivet connection clamps the spacer element at least proportionally (antielig) between the first pendulum mass and the second pendulum mass. The spacer element therefore does not need to be fastened, in particular riveted, separately to the first and/or second pendulum mass. Alternatively, the axial clamping force for fixing the spacer element can be provided by the pressing force of the riveted connection between the pendulum masses.

In particular, a gap is formed radially outside the riveted connection between the first and second pivot regions and/or between the second pivot region and the first pivot. By means of this gap, it is possible to keep the pendulum masses connected to one another via the riveted connection under axial prestress. By means of this pretensioning force, at least one spacer element can also be clamped with sufficient strength.

Preferably, the first pendulum mass has a plurality of first pendulum plates connected to one another and the second pendulum mass has a plurality of second pendulum plates connected to one another, wherein in the first pendulum mass only the innermost first pendulum plate or all first pendulum plates facing the carrier flange and/or in the second pendulum mass only the innermost second pendulum plate or all second pendulum plates facing the carrier flange are deformed in the axial direction to form the riveted connection and/or to form the adapter region. The respective pendulum mass can be produced at low cost by a set of pendulum plates which are arranged one above the other and connected to one another, wherein in particular pendulum plates of preferably identical shape can be stamped from sheet metal. If all the wobble plates have a downwardly bent adapter region, the wobble plates following one another can be partially inserted into one another, whereby a rough centering is achieved, which facilitates the assembly. However, it is also possible for a small number of wobble plates, in particular only precisely one wobble plate per wobble block, to have a downwardly bent transition region, so that the other wobble plates can be designed as low-cost, mass-producible universal parts. In order to form the axially protruding material region, in particular the projection, only the innermost rocker plate of the rocker plates of the second rocker block facing the carrier flange is necessary and sufficient. This makes it possible to keep the deformation costs of the stamped wobble plate low.

Particularly preferably, the carrier flange is reinforced by hardening. The hardened support flange can be formed substantially in a disk-shaped radial plane of constant axial thickness without the need for an axially projecting partial region. Since, apart from the punched-out partial regions, for example for the through-openings, plastic deformation of the carrier flange is not necessary, the carrier flange does not need to be of ductile design but can be hardened. The axial bridging is achieved only by the pendulum mass. By means of the hardened carrier flange, wear can be reduced without affecting the mounting of the pendulum mass.

Drawings

The invention is explained below by way of example with reference to the drawings by way of preferred embodiments, in which the features shown below can represent an aspect of the invention both individually and in combination. The figures show:

fig. 1 shows a schematic cross-sectional view of a torsional vibration damper;

FIG. 2 shows a schematic cross-sectional view of the torsional vibration damper of FIG. 1 with an exploded view of the centrifugal pendulum; and

fig. 3 shows a schematic detail of the torsional vibration damper in fig. 1.

Detailed Description

The torsional vibration damper 10 shown in fig. 1 can be used to damp torsional vibrations in the torque of a drive shaft of an internal combustion engine in a drive train of a motor vehicle. In the exemplary embodiment shown, torsional vibration damper 10 has a centrifugal pendulum 12, which can be connected in a rotationally fixed manner to a drive shaft of an internal combustion engine, for example, via splines provided in a hub 14. The centrifugal pendulum 12 has a hardened, substantially disk-shaped carrier flange 16 riveted to the hub 14, on the respective axial sides of which a first pendulum mass 18 and a second pendulum mass 20 are arranged in a pivotably guided manner, wherein in each case a plurality of first pendulum masses 18 and second pendulum masses 20 are arranged in succession, which are distributed in particular uniformly in the circumferential direction. The first and second pendulum masses 18, 20, which are axially opposite one another, are connected to one another via at least one riveted connection 24 which extends through a through opening 22 of the carrier flange 16.

As shown in fig. 2, the rivet connection 24 can be formed by an axially projecting projection 26 of the second pendulum mass 20, which projection 26 is inserted into a rivet opening 28 of the first pendulum mass 18. The free end of the projection 26 projecting from the rivet opening 28 may be plastically deformed into an upset. In this case, the rivet opening 28 can be provided in a depression 30 of the first pendulum mass 18, so that the axial extension of the projection 26 is sufficient to form the rivet connection 24.

As can be seen in particular in fig. 3, the first pivot piece 18 can have a first transfer region 32 which is bent downward and in which a depression 30 with a rivet opening 28 is also provided. The second pendulum mass 20 has a second transition region 34 which is bent downward. The first transition region 32 and the second transition region 34 are joined to some of the through openings 22 of the carrier flange 16. A gap S is formed between the first transition region 32 and the second transition region 34, so that the rivet connection 24 can exert an axial prestress between the first pendulum mass 18 and the second pendulum mass 20, for example in order to clamp a spacer element between the first pendulum mass 18 and the second pendulum mass 20.

List of reference numerals

10 torsional vibration damper

12 centrifugal pendulum

14 hub

16 bearing flange

18 first pendulum block

20 second pendulum block

22 through hole

24 riveted connection

26 projecting part

28 riveted opening

30 sink part

32 first transfer area

34 second transition area

S gap