WO2018086648A1

WO2018086648A1 - Centrifugal pendulum

Info

Publication number: WO2018086648A1
Application number: PCT/DE2017/100817
Authority: WO
Inventors: Peter Roland
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2016-11-10
Filing date: 2017-09-25
Publication date: 2018-05-17
Also published as: DE112017005660A5; DE102017122153A1

Abstract

The invention relates to a centrifugal pendulum (1) having a pendulum mass carrier (2) arranged rotatably about an axis of rotation and a plurality of pendulum masses (6), which are arranged spread out over the circumference and are supported radially outwards, each by means of two self-aligning bearings (7), which are spaced apart in the circumferential direction, on the pendulum mass carrier (2) under the effect of the centrifugal force of the rotating pendulum mass carrier (2), and which pendulum masses are received so as to be capable of oscillating, wherein the self-aligning bearings (7) in each case have axially opposing recesses (8, 9) having tracks (10, 11) in the pendulum masses (6) and in the pendulum mass carrier (2), and a self-aligning roller (12) axially overlapping the recesses (8, 9) rolls on said tracks (10, 11). In order to keep the self-aligning rollers (12) at their axial positions in the absence of centrifugal force, the self-aligning rollers (12) have a radial profile (13) at least partially overlapping the recesses (8, 9) and a radial clearance (s) of the pendulum masses (6) relative to the pendulum mass carrier (2) is limited at most to a radial height (h) of the radial profile (13).

Description

centrifugal pendulum

The invention relates to a centrifugal pendulum with a rotatably mounted about an axis arranged pendulum mass carrier and distributed over the circumference, supported by two circumferentially spaced pendulum bearings on the pendulum mass carrier under centrifugal force of the rotating pendulum mass carrier radially outward and pendulum supported pendulum masses, the pendulum bearings each axially have opposite recesses with raceways in the pendulum masses and the pendulum mass carrier, on soft tracks a recesses axially overlapping pendulum roller rolls.

Centrifugal pendulum serve the speed-adaptive torsional vibration damping of torsional vibrations in drive trains, which are caused in particular by an internal combustion engine serving as a drive in the drive train. Such centrifugal pendulums are arranged for example on an input and / or output side of a torsional vibration damper, a clutch disc, a friction clutch, a hydrodynamic torque converter, a flywheel or the like or separately in rotational connection with a crankshaft of the internal combustion engine. Here, a pendulum mass carrier of the centrifugal pendulum is rotatably arranged about a rotation axis. Relocatable pendulum mass units are suspended from the pendulum mass carrier by means of spherical rollers, which are aligned in the self-adjusting centrifugal force field under centrifugal force of the rotating pendulum mass carrier and are adjusted by corrective pendulum movements when torsional vibrations occur. gene absorb the kinetic energy of torque peaks and caching and release again, so that a calmed torque curve is achieved. From DE 10 2012 212 970 A1 a arranged in a torsional vibration damper centrifugal pendulum is known. Here, the individual pendulum mass units or pendulum masses against the pendulum mass carrier formed from side parts by means of a radial profile in the form of profiled spherical rollers with two circumferential Borden out to make their pendulum motion uniform and to guide the spherical rollers positionally secured.

From DE 10 2015 200 766 A1 a centrifugal pendulum is known in which pendulum masses are arranged on both sides of the pendulum mass carrier and axially opposite pendulum masses are connected by means of recesses of the pendulum mass carrier by cross-connecting means for pendulum mass units. A guide of the pendulum mass units on the pendulum mass carrier by means of spherical rollers, which have a central region with a first diameter and edge regions with stumpfenartig reduced smaller diameter, wherein at both diameters a support element is applied, which is arranged between the pendulum masses and the pendulum mass carrier and thus the Spherical rollers axially on the pendulum mass carrier leads.

In order to be able to introduce the spherical roller with radial profile into the recesses of the pendulum flange or the pendulum masses arranged between the disc parts, the recesses must at least have the diameter of the radial profile. This allows the spherical roller to rotate during operation with insufficient centrifugal force about its longitudinal axis and parts of the radial profile can immerse in the recesses, which can lead to noise, malfunction and damage the centrifugal pendulum.

The object of the invention is the development of a centrifugal pendulum with increased reliability. In particular, the object of the invention is to propose a centrifugal pendulum, the spherical rollers remain positionally secured in the recesses even with low or nonexistent centrifugal force.

The object is solved by the subject matter of claim 1. The dependent of the claim 1 claims give advantageous embodiments of the subject matter of claim 1 again.

The proposed centrifugal pendulum is particularly intended for a drive train of a motor vehicle and can be used separately as a speed-adaptive torsional vibration damper. The centrifugal pendulum can be integrated in a one-mass flywheel, which is connected directly to the crankshaft of the internal combustion engine. Alternatively, the centrifugal pendulum be integrated into another unit of the drive train, for example, on and / or output side in a torsional vibration damper such as a dual mass flywheel, for example in a clutch disc, in a friction clutch, in a hydrodynamic torque converter or to a rotor of an electric machine or the like , For this purpose, a pendulum mass carrier arranged so as to be rotatable about an axis of rotation is provided, on which at least one pendulum masses, which are preferably distributed between two and six circumferentially distributed pendulum masses, are displaceable by means of two pendulum bearings spaced apart from one another in the circumferential direction.

The pendulum bearings are each formed of axially juxtaposed recesses with tracks of the pendulum mass carrier and the pendulum mass. The axial adjacent recesses pass through a pendulum roller and roll on their careers, so that the pendulum masses are supported radially outward against the action of centrifugal force and added pendulum in the centrifugal force field on pendulum mass carrier. The spherical rollers roll in each case on tracks with predetermined shape curves, which are provided complementary to each other in the pendulum masses and in the pendulum mass carrier. Due to the nature of the form curves of the raceways while the pendulum is given as pendulum vibration of a pendulum mass, for example, a pendulum oscillation in free form or a pendulum oscillation corresponding to a bifilar pendulum suspended parallel or trapezoidal.

Corresponding centrifugal pendulum pendulum mass carrier rotatably mounted about a rotation axis and a plurality of pendulum masses arranged distributed over the circumference. The pendulum masses are supported by means of two spaced apart circumferentially pendulum bearings on the pendulum mass carrier under centrifugal force of the rotating pendulum mass carrier radially outward and added pendulum. The self-aligning bearings each have axially opposite recesses with raceways in the pendulum masses and in the pendulum mass carrier. On the tracks rolls a the recesses axially overlapping spherical roller. Essentially, two embodiments of such centrifugal pendulum pendulum are provided. In a first embodiment, the pendulum mass carrier may be formed as a pendulum. A pendulum flange is to be understood as meaning a single or a plurality of segmented, essentially radially aligned disk parts with recesses and raceways for the spherical rollers. On the pendulum pendulum masses are arranged on both sides, each axially adjacent as For example, have axially aligned recesses with raceways. Two mutually axially opposed pendulum masses are connected to each other by means of connecting means which pass through recesses of the pendulum, which are dimensioned so that the pendulum masses can swing undisturbed along their intended pendulum track with a corresponding swing angle. The pendulum masses connected in this way form a pendulum mass unit. The connecting means may be designed as stops for limiting the oscillation angle of the pendulum mass units and for this purpose have, for example, stop dampers such as rubber elements or the like.

The alternative embodiment of a centrifugal pendulum includes a pendulum mass carrier, which is formed from two substantially radially aligned disc parts or disc subsegments. The disc parts have a receiving portion with axially spaced apart disc sections, between which the pendulum masses are received. The disk parts may be formed substantially flat as ring parts or radially inside or radially outside in corresponding contact portions together and connected to each other. The pendulum bearings are formed from axially opposite recesses with raceways in the disc parts and recesses with raceways in the pendulum masses and each one of the axially adjacent recesses durchgreifen- the pendulum role.

The spherical rollers have a the recesses at least partially overlapping radial profile. This is to be understood that the spherical rollers each radially overlap the recesses in the region of their Wälzkontakts to a career. For this purpose, on the spherical rollers on both sides of the corresponding recess a ring board or the like may be provided as a radial profile. The ring board so the radial profile has for this purpose a corresponding, the recess radially overlapping radial height. In order to prevent immersion of the radial profiles in the recesses, for example the pendulum flange or the pendulum masses of a pendulum mass carrier with two blade parts, a radial clearance of the pendulum masses relative to the pendulum mass carrier is limited to a radial height of the radial profile. This means that in operating conditions, for example, in the absence or insufficient centrifugal force, the spherical rollers can lose their rolling contact to the raceways by falling radially, for example, in an arrangement above the axis of rotation in the absence of centrifugal force, a rotation of the spherical roller from its longitudinal axis insofar as it is prevented that immersion of the ring rims is avoided in the corresponding recess. This is done by a Radialspielbegrenzung between pendulum mass carrier and pendulum masses. The Radialspielbegrenzung can be provided by appropriate stops between pendulum mass and Pen- delmassenträger. The attacks can be formed axially expanded in particular from the pendulum mass carrier.

It has proved to be advantageous to form per pendulum mass two spaced stops in the circumferential direction, which are arranged for example radially within the pendulum bearings.

According to an advantageous embodiment of the proposed centrifugal pendulum, the radial clearance can be formed substantially constant over a swing angle of the pendulum masses. This means that the attacks with radial play stops are modeled on the pendulum movements of the pendulum masses relative to the pendulum mass carrier. For this purpose, at least one of the axially extended stop surfaces of a stop contact between pendulum masses and pendulum mass carrier on an arcuate form of training. For example, may be provided in the pendulum mass carrier axially with the pendulum masses overlapping attacks, which form the radial clearance with a radially inner stop profile of the pendulum masses. The radially inner stop profile may be provided on the outer circumference of the pendulum masses, for example punched or reworked tool falling.

The stops on the pendulum mass carrier can be provided as axially extended pins. The pins can be pressed into openings of the pendulum mass carrier, screwed or otherwise connected to this. In the case of a pendulum mass carrier designed as a pendulum flange, in each case a pin can be widened in both axial directions and thus form a stop for both pendulum masses of a pendulum mass unit. In the formation of the pendulum mass carrier of two disc parts, the pins between the two disc parts can be arranged and fixed or extended only a short pin of a disc part. It is understood that instead of the pins and noses from the pendulum mass carrier can be issued or stamped. The pins can be made of steel or plastic.

For example, to avoid noise may be provided between the radial clearance between pendulum masses and pendulum mass carrier limiting stop surfaces an elastic coating. For example, the coating may be provided on the pendulum masses and / or on the pins.

It has proven to be advantageous to provide the pins and the tangential displacement with respect to these via the oscillation angle of the pendulum masses. sch lagflächen the pendulum masses depending on the location of stop buffers to limit the swing angle of the pendulum masses provided. For example, in an embodiment of at least two stop buffers for limiting a swing angle of the pendulum masses with respect to the pendulum mass carrier with an annular elastic sheath, which are circumferentially more widely spaced than the pendulum bearings, a stop surface may be provided, which is substantially parallel to the track of the pendulum mass is guided. The sheath may be formed, for example, as an O-ring. In an alternative embodiment, a single stop buffer per pendulum mass or pendulum mass unit may be provided in the circumferential direction between the two pendulum bearings, wherein the elastic sheath may be V-shaped. In this case, from the modified stop geometry of the stop buffer, a stop geometry of the pendulum masses relative to the stop such as pin, which is formed steeper than the raceway of the pendulum masses radially outward in the pendulum direction of the pendulum mass.

The invention will be explained in more detail with reference to the embodiments illustrated in Figures 1 to 4. Showing:

1 shows a section of a centrifugal pendulum in section,

FIG. 2 shows a partial view of a centrifugal force pendulum modified relative to the centrifugal pendulum of FIG. 1,

Figure 3 is a centrifugal pendulum of Figure 2 similar centrifugal pendulum in the same representation

and FIG. 4 shows the centrifugal pendulum of FIG. 3 with several partial views superimposed at different oscillation angles.

FIG. 1 shows a section of the centrifugal pendulum pendulum 1 arranged so as to be rotatable about an axis of rotation in section. The centrifugal pendulum 1 is designed as a variant with the pendulum mass carrier 2 shown in the two disc parts 3, 4. The two disc parts 3, 4 take in the receiving portion 5 distributed over the circumference arranged pendulum masses 6, of which only a single pendulum mass 6 is shown in section, axially between them. The pendulum masses 6 are accommodated in a pendulum manner by means of pendulum bearings 7, which are each spaced apart in the circumferential direction, relative to the pendulum mass carrier 2. For this purpose, the self-aligning bearings 7 in the disk parts 3, 4 and in the pendulum masses 6 axially opposite recesses 8, 9 with raceways 10, 1 1, on which roll the recesses 8, 9 axially overlapping spherical rollers 12. The spherical rollers 12 have for axial positioning on the pendulum masses 6 and on the disk parts 3, 4, the radial profile 13 with the two ring rims 14 with the radial height h. In order to add the spherical rollers 12 in the recess 8, this has a corresponding clear width. The centrifugal pendulum 1 is shown in a stationary state without centrifugal force and arranged above the axis of rotation pendulum mass 6. Under the action of gravity, the pendulum mass 6 falls radially inwards. In order to prevent immersion of the ring rims 14 in the recess 8 in this operating state, the pins 15 are arranged between the two disc parts 3, 4, which form the abutment 16 to the stop surfaces 17 of the pendulum masses 6 after exhaustion of a radial clearance. The radial clearance used here is over the entire oscillation angle of the pendulum 6 smaller than the radial height h, so that the ring rims 14 at each

The angle of oscillation, the recesses 8 radially overlap and thus dipping this is excluded in the recess 8, although this has a clear width at least corresponding to the outer circumference of the ring rims 14.

Figure 2 shows the centrifugal pendulum 1 of Figure 1 with respect to the supported pendulum masses 6 similar centrifugal pendulum 1 a in partial view. In the embodiment shown, the pendulum mass carrier 2a is formed as a pendulum flange 3a, arranged on both sides pendulum masses 6a and connected by means of the connecting means 18a, 19a such as standoffs to pendulum mass units 20a. On the pendulum flange 3a corresponding recesses 21a, 22a, for the connecting means 18a, 19a are provided for this purpose. The spherical rollers 12a of the pendulum bearing 7a have the radial profile 13a with the ring rims 14a, which radially engage over the recesses 9a of the pendulum flange 3a. Between the pendulum masses 6a and the pendulum flange 3a while the radial clearance is set s, which is smaller than the height h of the ring rims 14a, so that immersion of the ring rims 14a in the recesses 9a is avoided. The radial play s between the pendulum flange 3a and pendulum masses 6a in the operating state shown at radially outwardly accelerated pendulum masses 6a in the centrifugal force field is set between the radially arranged within the pendulum bearing 7a pins 15a and the abutment surfaces 17a of the pendulum masses 6a. The abutment surfaces 17a are formed bent in the circumferential direction and adapted to the course of the raceways 10a of the pendulum masses 6a to form the radial clearance s constant over the swing angle of the pendulum masses 6a. Upon reaching the maximum swing angle of the pendulum masses designed as a stop buffer connecting means 18a to the recesses 21 a on. The connecting means 18a are in this case provided with a non-visible elastic sheath, for example O-rings, in order to achieve elastic stops and at least to reduce the formation of noise.

3 shows the centrifugal pendulum 1 a of Figure 2 similar centrifugal pendulum 1 b. In contrast to this, the connecting means 18b, 19b of the pendulum mass carrier 2b arranged on both sides on the pendulum mass carrier 2b, which is designed as a pendulum flange 3b, are arranged between the self-aligning bearings 7b viewed in the circumferential direction. Accordingly, the recess 21 b is also provided for the connecting means 18b, 19b between the pendulum bearings 7b in the pendulum flange 3b. The limitation of the oscillation angle of the pendulum masses 6b takes place by means of the stop buffer designed as a connecting means 18b, which for this purpose have the V-shaped casing 23b made of an elastic material and strike elastic upon reaching the maximum swing angle on the walls of the recess 21b.

Due to the changed abutment conditions of the pendulum masses 6b or pendulum masses 20b formed from axially opposite pendulum masses 6b and / or optionally a pendulum movement changed due to the formation of the raceways 10b, 11b, for example with a rotary portion of the pendulum masses 6b about their center of gravity, the abutment conditions or the change Adjusting the radial clearance s via the swing angle. In the embodiment shown, the course of the abutment surface 17b is to illustrate a uniform radial clearance s on the swing angle of the pendulum masses 6b the outer circumference of the pendulum masses 6b compared to the recorded in the pendulum flange 3b pins 15b towards larger angles of oscillation steeper than the course of the tracks 10b of the pendulum masses 6b.

FIG. 4 shows a representation of a deflection of the pendulum mass 6b of the centrifugal force pendulum 1b of FIG. 3 in relation to the pendulum flange 3b at a plurality of oscillation angles α = 0 °, α = 30 ° and α = 56 °. As seen from the synopsis of the individual oscillation angle α, the radial clearance s between the pin 15b and the correspondingly shaped abutment surface 17b remains constant over the oscillation angle α.

List of accessories for centrifugal pendulum

a centrifugal pendulum

b Centrifugal pendulum

Pendulum mass carrier

a pendulum mass carrier

b pendulum mass carrier

disk part

a pendulum flange

b pendulum flange

disk part

receiving portion

pendulum mass

a pendulum mass

b pendulum mass

aligning bearing

a self-aligning bearing

b self-aligning bearings

recess

a recess

0 career

0a career

0b career

1 career

1 b raceway

2 pendulum roller

2a pendulum roller

3 radial profile

3a radial profile

4 ring board 14a ring board

15 pen

15a pen

15b pin

16 stop

17 stop surface 17a stop surface 17b stop surface

18a connection medium

18b connection medium

19a connection medium

19b connection medium

20a pendulum mass unit

20b pendulum mass unit

21 a recess

21 b recess

22a recess

23b sheathing h height

s radial play

Claims

claims

1 . Centrifugal pendulum (1, 1 a, 1 b) arranged with a pendulum mass carrier (2, 2a, 2b) rotatable about a rotation axis and a plurality of circumferentially spaced pendulum bearings (7, 7a, 7b) arranged on the pendulum mass carrier (2, 2a, 2b) under the centrifugal force of the rotating pendulum mass carrier (2, 2a, 2b) supported radially outward and pendulum receiving pendulum masses (6, 6a, 6b), wherein the self-aligning bearings (7, 7a, 7b) respectively axially opposite recesses ( 8, 9, 9a) with raceways (10, 10a, 10b, 11, 11b) in the pendulum masses (6, 6a, 6b) and in the pendulum mass carrier (2, 2a, 2b), on soft raceways

(10, 10a, 10b, 1 1, 1 1 b) a the rollers (12, 12a) rolls over the recesses (8, 9, 9a) axially, characterized in that the spherical rollers (12, 12a) a the recesses (8 , 9, 9a) have at least partially overlapping radial profile (13, 13a) and a radial clearance (s) of the pendulum masses (6, 6a, 6b) relative to the pendulum mass carrier (2, 2a, 2b) to a maximum radial height (h) of the radial profile (13, 13a) is limited.

Second centrifugal pendulum (1, 1 a, 1 b) according to claim 1, characterized in that the radial clearance (s) over a swing angle of the pendulum masses (6, 6a, 6b) is formed substantially constant.

3. centrifugal pendulum (1, 1 a, 1 b) according to claim 1 or 2, characterized in that in the pendulum mass carrier (2, 2a, 2b) axially with the pendulum masses (6, 6a, 6b) overlapping stops (16) are provided , which with a radially inner stop surface (17, 17a, 17b) of the pendulum masses (6, 6a, 6b) form the radial play (s).

4. centrifugal pendulum (1, 1 a, 1 b) according to claim 3, characterized in that the stops (16) in the pendulum mass carrier (2, 2 a, 2 b) introduced pins (15, 15 a, 15 b) and the abutment surfaces (17 , 17a, 17b) are formed.

5. centrifugal pendulum (1, 1 a, 1 b) according to claim 3 or 4, characterized in that the pins (15, 15 a, 15 b) are made of steel or plastic.

6. centrifugal pendulum (1, 1 a, 1 b) according to one of claims 3 to 5, characterized in that the pins (15, 15 a, 15 b) are provided with an elastic sheath.

7. centrifugal pendulum (1 a) according to one of claims 1 to 6, characterized in that at least two stop buffers for limiting a swing angle of the pendulum masses (6a) relative to the pendulum mass carrier (2a) have an annular elastic casing and viewed in the circumferential direction are further spaced from each other as the self-aligning bearings (7a).

8. centrifugal pendulum (1 b) according to one of claims 1 to 6, characterized in that for limiting an oscillating angle of the pendulum masses (6b) is provided in each case a stop buffer with an elastic sheath in the circumferential direction between the pendulum bearings (7b) is provided.

9. centrifugal pendulum (1 a, 1 b) according to one of claims 1 to 8, characterized in that the pendulum mass carrier (2 a, 2 b) as a pendulum (3 a, 3 b) with bilaterally arranged pendulum masses (6 a, 6 b) is formed, in each case two axially opposite pendulum masses (6a, 6b) by means of recesses (21 a, 21 b, 22a) of the pendulum (3a, 3b) by cross-connecting means (18a, 18b, 19a) are interconnected to pendulum mass units (20a, 20b).

10. centrifugal pendulum (1) according to one of claims 1 to 8, characterized in that the pendulum mass carrier (2) comprises two receiving portion (5) having disc parts (3, 4) is formed, wherein the pendulum masses (6) axially between them in are received in the receiving portion (5).