WO2015149771A1

WO2015149771A1 - Centrifugal pendulum comprising radially pre-stressed pendulum masses

Info

Publication number: WO2015149771A1
Application number: PCT/DE2015/200140
Authority: WO
Inventors: Alain Rusch; Steffen Lehmann
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2014-04-01
Filing date: 2015-03-11
Publication date: 2015-10-08
Also published as: DE112015001598A5

Abstract

The invention relates to a centrifugal pendulum, in particular for a clutch disk, said pendulum comprising a support part that rotates about a rotational axis and pendulum masses which have restricted pivoting motion transversely to the rotational axis in relation to the support part, are mounted on pivot bearings effective in a radially outer direction and are distributed around the circumference. In order to prevent, at low engine speeds or when the centrifugal pendulums are stationary, a radial displacement of the pendulum masses arranged above the rotational axis, said pendulum masses are elastically pre-stressed from the radially inner direction against the pivot bearings.

Description

FLYING PENDANT WITH RADIAL PREPARED PENDULUM MASSES

The invention relates to a centrifugal pendulum in particular for a clutch disc with a support member rotating about an axis of rotation and limited relative to the support member transversely to the axis of rotation limited pivotable under centrifugal force radially outward effect

Schwenklagern recorded, distributed over the circumference arranged pendulum masses.

Centrifugal pendulums serve to reduce torsional vibrations, in particular internal combustion engines subject to torsional vibration. For this purpose, pendulum masses distributed over the circumference are attached to a carrier part arranged coaxially to the crankshaft of the internal combustion engine. These pendulum masses perform in the field of centrifugal acceleration of the rotating support member vibrations along predetermined paths when they are excited by the rotational irregularities such as torsional vibrations. Due to these vibrations, phase-selective energy is withdrawn from the torsional vibrations introduced and supplied again, so that a calming of a drive train with the internal combustion engine subject to torsional vibration is achieved by the decaying action of the centrifugal pendulum. Since both the natural frequency of the torsional vibrations to be considered as exciting frequency and the natural frequency of the centrifugal pendulum are proportional to the rotational speed of the carrier part, a Tilgerwirkung in terms of a speed-adaptive absorber is achieved by the centrifugal pendulum over the entire speed range of the application.

Centrifugal pendulum, for example, as known from DE 10 2009 042 836 A1 discloses a support member such as pendulum or support flange, and this pendulum masses distributed at this limited pivotally distributed over the circumference. The pivoting movement is achieved by pivot bearings, which are formed in sections of the pendulum masses and the carrier part introduced raceways and on these rolling rolling elements such as rollers. Due to the kinematically determined only in the centrifugal direction bearing the pendulum masses relative to the support member lose at insufficient speed or stationary support member, for example, when starting and stopping the engine, Auskuppel- and stopping operations and the like lying radially above the axis of rotation pendulum masses make contact with the rolling elements and meet with, the raceways opposite boundaries of the cutouts on the rolling elements. This can lead to unwanted noise when stopping and when starting the engine. In order to eliminate such noises, a centrifugal pendulum for a clutch disc is known from German patent application no. 10 2013 218 457.3, in which damping elements are provided in the circumferential direction between pendulum masses adjacent to one another in the circumferential direction for damping shocks of these against one another.

The object of the invention is the advantageous development of an integrated in particular in a clutch disc centrifugal pendulum to reduce any impact noises occurring.

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 centrifugal pendulum with a arranged around a rotation axis and rotating around this support member. The centrifugal pendulum can in this case be rotationally interlocked directly with a shaft such as transmission input shaft or integrated, for example, in an aggregate of the drive train. Furthermore, the centrifugal pendulum can be integrated into a clutch disc, for example radially inside of friction linings of the clutch disc, and, for example, axially spaced from an optionally present torsional vibration damper. In this case, the centrifugal pendulum can be integrated in the torsional vibration damper, for example, by serving as a carrier part one or two disc parts of the torsional vibration damper. The support member may be a flange, which with another rotating about the axis of rotation component in particular the clutch plate or another arranged in the drive train unit such as dual mass flywheel or comparable torsional vibration damper, hydrodynamic torque converter optionally with torsional vibration damper, electric machine, in particular rotor this, clutch unit, in particular its housing or intermediate plate of a double clutch or the like is connected. Transversely to the axis of rotation, for example, bounded in the sense of a pendulum radially and circumferentially oriented pendulum tracks

are pivotally mounted under centrifugal force radially outward pivot bearings pendulum masses, which are arranged distributed over the circumference. Depending on the number and design of the pivot bearing pendulum masses can perform oscillatory or pivotal movements that correspond to a monofilar suspended pendulum, a bifilar pendulum with parallel or trapezoidal thread guide or a freeform of the pendulum motion. In order to achieve a stabilization of the pendulum masses on the pivot bearings, the pendulum masses are biased from radially inward elastically against the pivot bearings. In this case, especially at low speeds, for example, during start and stop operations this, when disengaging arranged between the engine and transmission friction clutch with the proposed clutch disc and similar Betriebszu- states the pendulum masses, in particular arranged with respect to their center of gravity radially over the axis of rotation Pendulum masses stabilized on the pivot bearings, so that impact noise of the pendulum masses over other components of the centrifugal pendulum, in particular the pivot bearings are avoided or at least limited.

In an advantageous embodiment, the pendulum masses are arranged on both sides of the carrier part and connected axially in pairs with each other by means of the carrier part by cross-connecting means. In this case, axially opposed pendulum masses form a pendulum mass pair enclosing the support part. In a further advantageous embodiment, the support member may be formed of two axially spaced disc parts, wherein the disc parts receive the distributed over the circumference pendulum masses between them.

To form the pivot bearing the pendulum masses are compared to the support member or the two forming this disc parts by means of two circumferentially spaced pivot bearing limited pivotally received. The pivot bearings are in this case preferably formed of raceways, which are arranged as indicated on arcuate cutouts of the support member and the pendulum masses. Rolling bodies roll on the raceways, such as rollers, which in each case engage in the correspondingly associated cutouts and thereby fix the pendulum masses pivotably on the carrier part. By appropriate design of mutually substantially complementary raceways of the pendulum masses on the one hand and the carrier part on the other hand, the conditional by the pivotal mounting means of the pivot bearing pendulum movement of the pendulum masses against the support member is specified.

For radially elastic support between the pendulum masses and the support member or a component associated with this, which does not oscillate with the pendulum masses, each is a radially effective energy storage between a bearing between the pivot bearings on the pendulum masses and a bearing on the support member braced. Under bearing on the support member and a bearing point on another, to be understood with the support member firmly connected component. The energy storage is formed from at least one compression spring, plate spring, leaf spring or a magnet arrangement with two magnetic poles facing each other. Combinations of these energy stores can form a common energy store. With axially spaced pendulum masses connected to a pendulum mass pair, an energy store can be provided only on a pendulum mass or on both pendulum masses.

In an advantageous embodiment, pressure springs are provided as energy storage, whose end faces are supported by means of spring cups with receiving profiles or Abwälzprofilen against the bearings. The spring cups take the compression spring captive and form each receiving or Abwälzprofile against the bearings of the associated pendulum masses and / or with respect to the support member. Under rolling profile are positive and non-positive recordings of the spring cups on the support member and / or to understand the pendulum masses. Furthermore, under rolling of the spring cups in this sense, a pivot bearing of suspension cups preferably on the support member and / or to understand the pendulum masses. The spring cups themselves can be taken captive at the bearings. In an advantageous embodiment, in the sense of a telescopic spring arrangement, the spring cups can be connected to one another by means of a pin arranged radially within the compression springs and radially displaceable in at least one of the spring cups. Under recording profile is the solid, non-rolling recording of the spring cups on the support member or the pendulum masses to understand. An angle compensation between the pendulum masses and the carrier part is done by the springs themselves.

In an advantageous embodiment of the centrifugal pendulum, at least two different pendulum types with different partial circumference can be provided distributed over the circumference. For example, long can alternate with short pendulum masses over the circumference. The long and short pendulum masses can form long and short pairs of pendulum masses in an axially opposite arrangement on a support member. The long and short pendulum masses can continue to be guided on different aerial tramways. In particular, such sets of long and short pendulum masses such as pendulum mass pairs and / or circumferentially arranged short and long pendulum masses can be tuned to different Tilgerfrequenzen, so that, for example, in internal combustion engines with Shut-off cylinders each a part of the pendulum masses can each be tuned to a switching state of the internal combustion engine.

The invention will be explained in more detail with reference to the embodiments illustrated in Figures 1 to 9. Showing:

1 shows a centrifugal pendulum with a carrier part formed from two disc parts in 3D view,

FIG. 2 shows the centrifugal pendulum of FIG. 1 in an exploded view;

3 shows the energy accumulator installed in the centrifugal pendulum of FIGS. 1 and 2 in various views,

FIG. 4 shows the spring cup of FIG. 3 in different views;

FIG. 5 shows a centrifugal pendulum changed in relation to the centrifugal force pendulum of FIGS. 1 and 2, with the front disc part removed in the non-pivoted state of the pendulum masses,

FIG. 6 shows the centrifugal pendulum of FIG. 5 with pivoted pendulum masses,

FIG. 7 shows the centrifugal pendulum of FIGS. 4 to 6 in a 3D view,

8 shows the centrifugal pendulum of Figures 4 to 7 in an exploded view

and

Figure 9 shows different views and embodiments of the usable in the centrifugal pendulum of Figures 4 to 8 energy storage.

Figures 1 and 2 show the centrifugal pendulum 1 in a 3D view and exploded view. The support part 2 rotating about the rotation axis d is formed from the two disk parts 4, 5, which are preferably designed as identical parts. The disk parts 4, 5 have radially inside the internal teeth 6 for caulking on a hub of a clutch disc or for non-rotatable connection with a shaft, such as a transmission input shaft or the like. Furthermore, a radially inner annular region 7 is formed offset axially with respect to a radially outer annular region 8, so that when an abutment of the two disc parts 4, 5 between the outer annular regions 8, an annular space 9 is formed, in which distributed over the circumference arranged pendulum masses 1 1st are introduced with little play. At the inner ring portions 7 aligned openings 12 are provided which can serve to accommodate the centrifugal pendulum 1 on a test device or by means of the disc parts 4, 5 with itself or with another component such as flange of a arranged in a drive train unit, such as a Drehschwingungsdämp- fer, a clutch unit, a hydrodynamic torque converter or the like may be connected.

The pendulum masses 1 1 are pivotally received by means of spaced respectively circumferentially pivot bearings 13, 14 on the support member 2. For this purpose, corresponding cutouts 15, 16, 17, 18 are made in the disk parts 4, 5 and in the pendulum masses 1 1. On the radially outer surfaces of the cutouts 15, 16 of the disc parts 4, 5 and on the radially inner surfaces of the cutouts 17, 18 of the pendulum masses 1 1 are raceways 19, 20, 21, 22 attached as formed, on each of which a rolling element 23, here rolls a roller 24 with bearings 25. By the interpretation of the shape and position of the raceways 19, 20, 21, 22 while pivoting movement as pendulum motion of the pendulum masses 1 1 is set relative to the rotating support member 2 in the centrifugal force field. In order to avoid hard stops, the stop buffer 26 are provided in the circumferential direction between the pendulum masses 1 1.

To avoid a radial displacement of the pendulum masses 1 1 radially inward from the pivot bearings 13, 14 not defined in this direction at radially above the axis of rotation d pendulum masses and insufficient centrifugal force are the energy storage 27 between the pendulum masses 1 1 and the support member 2 and the Disk parts 4, 5 braced at the bearings 3, 10. In the illustrated embodiment, the energy storage 27 from compression springs 28 and from both sides introduced into these spring cups 29, 30 are formed. The spring cups 29 are firmly connected by means of receiving profiles 31 to preferably centrally between the pivot bearings 13, 14 recesses introduced 32 with the receiving profiles 31 complementarily shaped receiving profiles 33. The disk parts 4, 5 have to the formation of the receiving profiles 34 of the spring cups 30 complementary receiving profiles 35 cutouts 36.

From Figure 3 shows the detailed design of the energy storage 27 in the view a), the longitudinal section b) and the 3D view c). The spring cups 29, 30 are taken captive by means of the mandrels 37 on the end faces of the compression spring 28. The rolling profiles 31, 34 are axially divided and point-symmetrical, so that they form with the complementarily formed rolling profiles 33, 35 of the disc parts 4, 5 and the pendulum masses 1 1 (Figure 2) axial stops and are thus secured axially, the disc parts 5 may nevertheless be designed as identical parts. In the embodiment shown are the Feather cups 29, 30 formed as equal parts and form with their receiving profiles 31, 34 with the receiving profiles 33, 35 a firm connection.

FIG. 4 shows the spring cups 29, 30 in detail in a) 3D view, b) in view of the mandrel 37 and c) in section along the section line B-B of the view b). The mandrel 37 is inserted into the compression spring and has an undercut 38 for fixing the compression spring.

Figures 5 to 8 show in sync with respect to the centrifugal pendulum 1 of Figures 1 and 2 changed centrifugal pendulum 1 a in view of non-twisted pendulum masses 1 1 a, 1 1 b (Figure 5) and twisted pendulum masses 1 1 a, 1 1 b (Figure 6) with each removed front disc part 5a of the support member 2a, in 3D view (Figure 7) and in exploded view (Figure 8). The centrifugal pendulum 1 a has two different lengths pendulum masses 1 1 a, 1 1 b, which are also designed with different pendulum properties and are formed, for example, with different oscillation angles such as angles of oscillation, so that with the centrifugal pendulum 1 a two different exciter frequencies can be eradicated. Similarly, the support member 2 a of the two disc parts 4 a, 5 a formed between the pendulum masses 1 1 a, 1 1 b limited pivotally receive. The pendulum masses 1 1 a, 1 1 b are supported by the energy storage 27a, 27b against the pulley parts 4a, 5a and keep the pendulum masses 1 1 a, 1 1 b even with stationary centrifugal pendulum 1 a in a radially outer stop position relative to the pulley parts 4a , 5a.

The energy storage 27a, 27b of compression springs 28a formed with spring cups 29a, 30a and 29b, 30b. To stabilize the spring cups 29a, 30a and 29b, 30b against each other when compressing the compression springs 28a are arranged between these pins 39a, which are designed differently for length compensation in at least one spring cup here relative to the pendulum mass types. The pendulum masses 1 1 a associated energy storage 27a are supported by means of the spring cups 29a, 30a between the pendulum masses 1 1 a and the disk parts 4a, 5a from. The pendulum masses 1 1 b associated energy storage 27b are supported by means of the spring cups 29b, 30b between the pendulum masses 1 1 b and the disk parts 4a, 5a from. The spring cups 29a, 29b are hereby designed differently and shown in detail in FIG. FIG. 9 shows the energy store 27a in the detailed illustrations a-c and the energy store 27b of FIGS. 5 to 8 in the detailed illustrations d-f. The view shown in 3D, in section along the section line AA and in view of the rolling profile 31a Energy storage 27a contains the tensioned between the spring cups 29a, 30a compression spring 28a, in the interior of the pin 39a is received axially displaceable in the spring cup 29a. The pin 39a serves to axially stabilize the compression spring 28a along its compression axis. Both spring cups 29a, 30a have round rolling profiles 31a, 34a in cross-section, which roll on correspondingly complementarily formed rolling profiles on the pendulum masses 1a and on the disk parts 4a, 5a. The spring cap 29a further comprises a relative to the rolling profile 31 a radially expanded cheek 40a to stabilize the rolling profile 31 a in the disc parts 4a, 5a.

The in the same way as the energy storage 27a in a 3D view, in section along the section line AA and in view of the rolling profile 31 b illustrated energy storage 27b contains the tensioned between the spring cups 29b, 30b compression spring 28a, in the interior of the pin 39a in the Spring cup 29b is received axially displaceable. In contrast to the energy store 27a, the energy store 27b has a spring cap 29b, which has an axially enlarged round pin 41b with the rolling profile 31b. This pin 41 b is inserted into an opening of the disc parts 4 a, 5 a and forms in the sense of the present description, the rolling profile 31 b with respect to the opening to form a sliding bearing. The cheek 40b serves for the axial stabilization of the pin 41b with respect to the disk parts 4a, 5a. In one embodiment, not shown, instead of the sliding bearing a rolling bearing can be provided by a pin bearing 41b and opening a roller bearing as preferred needle roller bearing is introduced.

LIST OF REFERENCE NUMBERS

centrifugal pendulum

a centrifugal pendulum

support part

a carrier part

depository

disk part

a disc part

disk part

a disc part

internal gearing

ring area

annulus

0 storage location

1 pendulum mass

1 a pendulum mass

1 b pendulum mass

2 opening

3 swivel bearings

4 swivel bearings

5 section

6 section

7 section

8 section

9 career

0 career

1 career

2 career

3 rolling elements

4 roll

5 rolling bearings

6 stop buffers 7 Energy storage 7a Energy storage 7b Energy storage 8 compression spring

8a compression spring

9 spring cap

9a spring cap

9b spring plunger

0 spring cup

0a spring cap

0b spring plunger

1 receiving profile 31 a rolling profile 31 b rolling profile

32 recess

33 recording profile

34 receiving profile profile 34a rolling profile

35 recording profile

36 section

37 thorn

38 undercut 39a pin

40a cheek

40b cheek

41b pin

d rotation axis

A-A cutting line

B-B cutting line

Claims

claims

1 . Centrifugal pendulum (1, 1 a) in particular for a clutch disc with a about an axis of rotation (d) rotating support member (2, 2a) and relative to the support member (2, 2a) transversely to the axis of rotation (d) limited pivotally on under centrifugal force acting radially outward Swivel bearings (13, 14) received, distributed over the circumference arranged pendulum masses (1 1, 1 1 a, 1 1 b), characterized in that the pendulum masses (1 1, 1 1 a, 1 1 b) from radially inward against elastic the pivot bearings (13, 14) are biased.

2. Centrifugal pendulum according to claim 1, characterized in that the pendulum masses are arranged on both sides of the support member and axially opposite each other in pairs by means of the support member by cross-connecting means are connected.

3. centrifugal pendulum (1, 1 a) according to claim 1, characterized in that the carrier part (2, 2 a) of two axially spaced disc parts (4, 4 a, 5, 5 a) is formed, between which the pendulum masses (1 1, 1 1 a, 1 1 b) are included.

4. centrifugal pendulum (1, 1 a) according to claim 2 or 3, characterized in that the pendulum masses (1 1, 1 1 a, 1 1 b) by means of two circumferentially spaced, from at arcuate cutouts (15, 16, 17, 18) arranged raceways (19, 20, 21, 22) of the pendulum masses (1 1, 1 1 a, 1 1 b) and the support member (2, 2 a) and on each of a raceway (19, 20, 21, 22) of the Pendulum masses (1 1, 1 1 a, 1 1 b) and the support part (2, 2 a) rolling elements (23) formed pivot bearings (13, 14) on the support flange (2, 2 a) are pivotally mounted.

5. centrifugal pendulum (1, 1 a) according to claim 4, characterized in that in each case a radially effective energy storage (27, 27 a, 27 b) between a bearing point (3) between the pivot bearings (13, 14) on the pendulum masses (1 1, 1 1 a, 1 1 b) and a bearing point (10) on the support part (2, 2 a) is braced.

6. centrifugal pendulum (1, 1 a) according to claim 5, characterized in that the energy store (27, 27 a, 27 b) from at least one compression spring (28, 28 a), plate spring, leaf spring or a magnet arrangement is formed with two magnetic poles facing each other ,

7. centrifugal pendulum (1, 1 a) according to claim 6, characterized in that the end faces of a compression spring (28, 28 a) by means of spring cups (29, 29 a, 29 b, 30, 30 a, 30 b) Receiving profiles (31, 34) or rolling profiles (31 a, 31 b, 34 a) relative to the bearing points (3, 10) are supported.

8. centrifugal pendulum (1, 1 a) according to claim 6 or 7, characterized in that the energy storage (27, 27 a, 27 b) captive at the bearing points (3, 10) are added.

9. centrifugal pendulum (1 a) according to any one of claims 6 to 8, characterized in that the spring cups (29a, 29b, 30a, 30b) by means of one within the compression springs (28a) arranged in at least one of the spring cups (29a, 29b) radially displaceable pin (39 a) are interconnected.

10. centrifugal pendulum (1 a) according to one of claims 1 to 9, characterized in that distributed over the circumference at least two different pendulum types are provided with different part circumference.