CN109307044B

CN109307044B - Prestressed pendulum damping device

Info

Publication number: CN109307044B
Application number: CN201810841836.2A
Authority: CN
Inventors: R.弗胡格; G.格里科; F.凯勒雷特
Original assignee: Valeo Embrayages SAS
Current assignee: Valeo Embrayages SAS
Priority date: 2017-07-27
Filing date: 2018-07-27
Publication date: 2022-08-23
Anticipated expiration: 2038-07-27
Also published as: CN109307044A; FR3069605A1; DE102018117736A1; FR3069605B1

Abstract

A oscillation damping device, in particular for integration in a drive train of a motor vehicle, in particular in a clutch, the device comprising: a support (12); a plurality of rockers arranged about an axis of rotation X of said support; the pendulum (13) comprises an oscillating mass (14); rolling members (16) interposed between the oscillating masses and the support so as to roll on the rolling tracks of the support and of the oscillating masses during oscillation of the oscillating masses with respect to the support; -a coating member (30) coupled with the oscillating mass or with the support and elastically bearing centripetally or centrifugally, respectively, on a coating track (32) defined by the support or by the oscillating mass, at least in a rest position of the support in which it is stationary and extends horizontally, and having the same shape as the rolling track of the support.

Description

Prestressed pendulum damping device

Technical Field

The present invention relates to a wobble damping device, in particular for a clutch of a motor vehicle, and to a torsion damping device incorporating such a wobble damping device.

Background

Oscillation damping devices are conventionally used to filter vibrations caused by the non-periodicity (aperiodisms) of the engine of a motor vehicle. The oscillation damping device is conventionally rigidly fixed by rivets to the phasing washer of a torsional damping device, in particular a clutch, a hydrodynamic torque converter or, a dry or wet dual clutch.

Conventionally, it comprises an annular support intended to be driven in rotation and a plurality of oscillating masses mounted to oscillate on the support about an axis parallel to the axis of rotation of the support. The displacement of the oscillating mass with respect to the support is generally guided by two rolling members, each cooperating with a rolling track of the support and a rolling track of the oscillating mass. The rolling tracks of the support and of the oscillating masses extend such that the rolling members are supported centrifugally and centripetally on said tracks, respectively.

The oscillating mass is conventionally constituted by a pair of counterweights which clamp a support and are rigidly coupled to each other, usually by means of spacers (entretoise) defining the rolling track of the oscillating mass.

When the pendulum damping device rotates at reduced speed (typically less than 800 revolutions per minute) during the idling phase of the vehicle, in particular at start-up, the centrifugal force exerted on the oscillating mass during engine stop or in case of gear change is reduced, and the oscillating mass therefore tends to approach the rotation axis. The contact of the oscillating masses with the rolling tracks can therefore be interrupted, which leads to undesirable noise and shocks that can reduce the service life of the oscillation damping device.

There is therefore a need for a swing damping device that at least partially addresses these problems.

The present invention aims to meet this need.

Disclosure of Invention

To this end, the invention proposes a device for damping oscillations, in particular intended to be integrated in a drive train of a motor vehicle, in particular in a clutch, comprising:

-a support;

a plurality of rockers arranged around the rotation axis X of the support,

the, preferably each, pendulum comprises:

-an oscillating mass;

-rolling members interposed between said oscillating masses and the support so as to roll on the rolling tracks of the support and of the oscillating masses during oscillation of the oscillating masses with respect to the support;

-a coating member associated with the oscillating mass or with the support and elastically bearing centripetally or centrifugally, respectively, at least in a rest position of the support in which the support is stationary and extends horizontally (axis X is vertical), on a coating track defined by the support or by the oscillating mass, respectively, having the same shape as said rolling track of the support, and preferably at least until the rotation speed of the support about axis X is greater than 300 revolutions per minute, preferably greater than 500 revolutions per minute, preferably greater than 700 revolutions per minute, preferably greater than 800 revolutions per minute, or even whatever the rotation speed.

Thus, at reduced rotation speeds, the radial displacement of the oscillating masses is hindered, on the one hand, by the rolling members bearing on the rolling tracks of the supports and resisting radial displacements away from the axis X, and, on the other hand, by the application members bearing on the application tracks and resisting radial displacements towards the axis X. The elasticity of the support allows a slight compression of the oscillating mass, but also of the rolling members. Thus, the rolling members are kept in contact with the rolling tracks between the supports and the rolling tracks of the oscillating masses.

The elasticity of the bearing also advantageously makes it possible to compensate for play caused by manufacturing tolerances or wear. The service life of the device is prolonged.

The same shape of the application track and of the rolling track of the support advantageously makes it possible to guarantee a substantially constant intensity of the compression force, irrespective of the angular position of the oscillating mass with respect to the support during its oscillating movement.

Preferably, the support exerts a compressive force of less than 15N, preferably less than 10N and preferably greater than 1N. Preferably, the force is in the range of 1 to 3N for a twin-flywheel Damper (DVA) and in the range of 5 to 15N for a truck primary.

Preferably, the application track of the support is shaped such that in said rest position, during oscillation of the oscillating mass on the support, the compression force varies by less than 10N, preferably less than 5N, preferably less than 3N, preferably less than 1N. In other words, the action of the application member is substantially independent of the angular position of the oscillating mass with respect to the support.

When the application track is defined by a support, the oscillation damping device according to the invention may also comprise one or more of the following optional and preferred features:

the application member is a ball, roller or pin fixed to the oscillating mass and on which bearings, for example ball bearings, are mounted, the bearings being preferably supported on the support by elastic rings;

the application member is a roller comprising a first and a second lateral pin mounted to rotate in a first and a second seat provided in the oscillating mass, respectively, and in particular in a first and a second seat provided in a first and a second counterweight of the oscillating mass.

In a first embodiment, the oscillating mass comprises a first and a second counterweight rigidly coupled to each other, preferably by a spacer, which grip the support and elastically compress the application member so as to elastically urge the application member towards the axis X, the thickness of the first and second counterweight preferably being less than 7mm, 5mm, 4mm, 3mm or 2 mm;

in a second embodiment, the oscillating mass comprises a spring, preferably a leaf spring, mounted so as to elastically urge the application member towards the axis X;

the oscillating mass comprises a first and a second counterweight, said springs being mounted between the first and the second counterweight, the thickness of the first and the second counterweight being preferably greater than or equal to 3mm, preferably greater than or equal to 4 mm.

When the application track is defined by an oscillating mass, the oscillation damping device according to the invention may also comprise one or more of the following optional and preferred features:

the application member is a ball, roller or pin fixed on the support and on which are mounted first and second bearings, for example ball bearings, preferably borne on first and second counterweights of the oscillating mass by means of elastic elements, such as elastic rings;

the application member is a roller mounted rotatably on the support;

the application member is clamped between two walls of the support, which elastically compress the application member to push it away from the axis X, said walls preferably having a thickness of less than 2mm, preferably less than 1 mm;

in a second embodiment, the support comprises a spring, preferably a leaf spring, mounted so as to elastically urge the application member away from the axis X;

the support comprises walls between which the spring is mounted.

In general, it is preferred that the application member and/or the support and/or the oscillating mass comprise a region of elastomeric material which imparts elasticity to the bearing of the application member on the oscillating mass and/or the support.

The invention also relates to a torsion damping device integrated with a pendulum damping device according to the invention.

The torsional damping device according to the invention is preferably selected from the group consisting of double-damped flywheel dampers, torque converters and friction discs.

The invention also relates to a motor vehicle equipped with a torsional damping device according to the invention.

Drawings

Other features and advantages of the invention will become apparent upon reading the detailed description and upon reference to the drawings in which:

fig. 1 shows a torsion damping device in a perspective view; and

figures 2a-2d, figures 3a-3c, figures 4a-4c, figures 5a-5c and figure 6 show different embodiments of the invention.

Detailed Description

For each of fig. 2 a-6, the figure numbered "b" is a section of the figure numbered "a" along the cutting plane a-a. Fig. 2c and 2d show a detail of fig. 2 a.

The diagram numbered "a" each time shows that the oscillating mass is in a central position with respect to the oscillating movement on the support. For fig. 3a to 5c, the diagram numbered "c" each time represents the oscillating mass in an extreme position of oscillation with respect to the support.

Fig. 6 shows a cross-section of the application member in a particular embodiment in a radial cross-sectional plane.

The same reference numbers will be used throughout the different drawings to refer to the same or like parts.

Definition of

When the application member cannot be detached from the oscillating mass or from the support, it is said to be "coupled" (solidarire) with the oscillating mass or support. It may be rigidly fixed to the oscillating mass or support or movably mounted on the oscillating mass or support.

Unlike simple contacts, "elastic bearings" generate a pressure force from one component on the other, the elasticity allowing the pressure force to be varied by the relative displacement of the two components.

Unless otherwise stated, it is to be understood that,

"axially" means "parallel to the axis of rotation X of the support";

"radially" means "along a transverse axis intersecting the axis of rotation of the support";

"transverse" means "in a plane perpendicular to the axis of rotation of the support";

- "angularly" or "circumferentially" means "around the axis of rotation of the support";

"radially orthogonal" means "perpendicular to the radial direction and in the transverse plane".

"transverse plane" means a plane perpendicular to the axis of rotation of the support.

"radial plane" means a plane containing the radial axis and the axis X.

"axial plane" means a plane containing the axis X.

A "radius" is a straight line formed by the intersection of a transverse plane and a radial plane.

The "thickness" of the component refers to the dimension measured along the axis X.

"centrifugal support" means a support force comprising a component oriented away from the axis X.

By "centripetal support" is meant a support force comprising a separation oriented towards the axis X.

"Motor vehicle" means not only passenger vehicles but also industrial vehicles, including in particular heavy goods vehicles, public transport vehicles or agricultural vehicles.

Unless otherwise stated, the verbs "comprising", "having" or "including" must be interpreted broadly, i.e. without limitation.

Detailed Description

Applicator rail defined by supports

As shown in fig. 1, the oscillation damping device 10 comprises a support 12 which is rotationally displaceable about an axis X and a plurality of rockers 13 which are movable relative to the support 12.

The support 12 has a generally annular flat overall shape. It comprises a radially outer edge 15 having a generally circular overall shape and being substantially transverseFirst and second main faces 12 ₁ And 12 ₂ 。

The support is conventionally made of cut metal sheet, generally made of steel, whose thickness is generally less than 10mm, preferably less than 9mm, preferably less than 8 mm.

To the plate, auxiliary members for damping and/or limiting and/or guiding the oscillating movement of the oscillating mass, such as damping pads and/or stops and/or guides (for example made of a polymer) may be fixed.

Each pendulum 13 comprises an oscillating mass 14 and one or more (e.g. two) rolling members 16. Typically, each oscillating mass is mounted to oscillate on the support by means of two rolling members (preferably rollers) passing through rolling windows 20 provided in the thickness of the support.

Each oscillating mass 14 generally comprises a first and a second counterweight 14 having a substantially planar shape ₁ And 14 ₂ Respectively associated with the first and second main faces 12 of the support 12 ₁ And 12 ₂ Extending opposite each other.

First and second weights 14 ₁ And 14 ₂ Preferably rigidly fixed to each other by spacers 18. The spacer is clamped between the two weights and extends into the rolling window 20 of the support. The spacers define the rolling tracks 22 of the oscillating masses.

Each rolling member 16 thus bears on the one hand on the rolling track 24 of the support, preferably defined by the inner contour of the rolling window 20 of the support, and on the other hand on the rolling track 22 of the oscillating mass defined by the spacers of the oscillating mass.

The oscillating masses are preferably distributed equiangularly about the axis X. Preferably, their number is greater than 2 and/or less than 8. The device may in particular comprise three, five or seven oscillating masses. In the example shown in fig. 1, the device comprises three oscillating masses distributed uniformly about the axis X.

For each oscillating mass, the device comprises a coating member 30, the coating member 30 bearing elastically on a coating track 32 when the support rotates about the axis X at a speed of less than 800 revolutions per minute, and in particular when the support is at a standstill. The application track 32 is constituted by all the points of support that may come into contact with the application member 30, in particular during the oscillation of the oscillating mass 14.

According to the invention, the shape of the application track 32 is substantially identical to the shape of the rolling track of the support when the device is viewed along the axis X, as shown in figure 2 a. For greater clarity, the application track and the rolling track of the support are shown in fig. 2a in solid and bold lines.

In the embodiments of fig. 2a-2d, 4a-4c and 5a-5c, the application track 32 is defined by the radially outer edge 15 of the support 12. Advantageously, the support 12 becomes light. In the embodiment of fig. 3a-3c, the application track 32 is defined by the edges of an application window 40 provided in the thickness of the support 12.

In the embodiment of fig. 2a-2d, the application member 30 is on the first and second weights 14 ₁ And 14 ₂ Is compressed so as to be pushed onto the application track. The support resilience is obtained by the ability of the two weights to resiliently move apart and close to each other.

The action of the weight on the application member 30 causes a force with a centripetal component, corresponding to the weight 14 ₁ And 14 ₂ Bearing surface S on application member 30 ₁ And S ₂ And (4) inclining. As shown in fig. 2b, in a cross-section along a radial plane A-A passing substantially in the center of the application member 30, a surface S ₁ And S ₂ Preferably the ground surface S ₁ And S ₂ Is inclined with respect to the radius R by an angle a having an absolute value in the range of 5 to 85 degrees, preferably more than 20 degrees, more than 30 degrees, more than 40 degrees and/or less than 70 degrees, less than 60 degrees, less than 50 degrees.

In the embodiment of fig. 2a-2d, the application member 30 is housed in a housing provided in the first and second weight member 14, respectively ₁ And 14 ₂ Basin 34 in ₁ And 34 ₂ The ball of (1). Preferably, the cavity 34 ₁ And 34 ₂ Are substantially oblong, and more preferably, are radially oriented. Thus, during the separation or approach of the two clump weights to each other, the cavity 34 ₁ And 34 ₂ Allowing a slight radial displacement of the application member relative to the weight.

In the embodiment of fig. 2a-2d, the cavity 34 ₁ And 34 ₂ Is transverse. Cavity 34 ₁ And 34 ₂ Advantageously conical, for generating radial forces by axial clamping.

In the embodiment of fig. 4a-4c, the application member 30 is constituted by a roller 42 having an axis Y, the roller 42 being provided with a first and a second pin 44 ₁ And 44 ₂ First and second pins 44 ₁ And 44 ₂ Are respectively accommodated in first and second balance weight blocks 14 ₁ And 14 ₂ First and second seats 46 ₁ And 46 ₂ In (1). Thus, roller 42 is rotatable about axis Y, remaining stationary relative to the weight. In this embodiment, the bearing elasticity of the application member on the support 12 is preferably obtained by compression of an elastomeric ring 48 having an axis Y surrounding the roller 42. Preferably, the ring 48 is received in a peripheral groove 50 defined on a peripheral surface 52 of the roller 42, the peripheral groove 50 extending between the first and second weights.

The application member of fig. 5a-5c is similar to the application member of fig. 4a-4 c. The elasticity is however not due to the presence of an elastic ring between the application member 30 and the application track 32, but rather to the elastic support exerted by the spring 60 associated with the oscillating mass 14. In the embodiment of fig. 5a-5c, the spring 60 is a leaf spring, each of its two ends being fixed to the oscillating mass 14. More specifically, in the embodiment of fig. 5a-5c, the end of the spring 60 is mounted about a pivot 62 along an axis parallel to the axis X ₁ And 62 ₂ Rotating, pivot 62 ₁ And 62 ₂ At two counterweights 14 respectively ₁ And 14 ₂ Extending therebetween.

The operation is directly derived from the above.

In use, the pendulum oscillates under the non-periodic action of the engine. The centrifugal force exerted on the oscillating mass depends on the rotation speed of the support. When this speed is high, typically greater than 800 revolutions per minute, the oscillating mass pushes the rolling members against the rolling tracks. The rolling of the rolling member is thus guided and silent. Typically, the force exerted by the oscillating mass on the rolling members is greater than 50N, or even greater than 80N, preferably substantially 100N. The effect of the application member is small, for example less than 10N, or even zero.

When the rotational speed of the support is reduced, the centrifugal force exerted on the oscillating mass is reduced. Therefore, the oscillating mass tends to approach the axis X. If they are sufficiently close to the axis X, the rolling members can no longer be sandwiched between the rolling tracks of the support and of the oscillating mass.

However, the application member 30 is elastically urged against the support 12 by the oscillating mass 14. The support of the application member 30 on the application track 32 tends to move the oscillating mass away from the axis X, but this movement is hindered by the support of the rolling members on the rolling tracks of the oscillating mass.

The rolling members 16 are therefore elastically prestressed, in particular at a rotational speed of less than 800 revolutions per minute.

However, the pre-stress has a low strength, typically less than 30 newtons in the rest position. This prestress is in particular substantially negligible with respect to the pressure generated by the centrifugal action during rotation of the support.

In general, the application member 30 exerts a force F on the support 12 comprising a centripetal component, preferably oriented towards the axis X, as shown in fig. 2 a.

Thus, the application member 30 resists the displacement of the oscillating mass towards the axis X.

The application track need not be provided on the support. Likewise, it may be arranged on the oscillating mass. The pasting component is connected with the supporting component. Preferably, the application member mounted on the support is configured to be able to roll on the application track.

Such an embodiment is shown in fig. 6. The application member comprises a pin 70 fixed to the support 12 and on which pin 70 two ball bearings 72 are mounted ₁ And 72 ₂ First and second weights 14 ₁ And 14 ₂ Through first and second resilient rings 74, respectively ₁ And 74 ₂ Against the first and second ball bearings.

All the equivalent techniques described above when the application track is defined by the support can be implemented when the application track is defined by the oscillating mass.

It is now clear that the present invention provides a solution that allows to ensure a permanent contact of the rolling members with the rolling tracks, irrespective of the rotation speed of the support, in particular when the rotation speed is less than 800 revolutions per minute. However, this solution does not hinder a good operation of the device, in particular at high rotation speeds, the action of the application member having a low strength.

In addition, the elasticity of the bearing ensures a minimum compression force even when the rolling member or the application member is worn.

Finally, the shape of the application track is defined such that the compressive force exerted by the application member remains substantially constant irrespective of the angular position of the oscillating mass on the support.

The noise level at low rotational speeds is advantageously significantly reduced. In addition, the service life of the device is increased.

Of course, the invention is not limited to the specific embodiments described above.

Claims

1. A swing damping device, the swing damping device comprising:

a support (12);

a plurality of rockers arranged about an axis of rotation X of said support;

the swing member (13) includes:

an oscillating mass (14);

rolling members (16) interposed between the oscillating masses and the support so as to roll on the rolling tracks of the support and of the oscillating masses during oscillation of the oscillating masses with respect to the support;

-a coating member (30) coupled with the oscillating mass or with the support and elastically bearing centripetally or centrifugally, respectively, on a coating track (32) defined by the support or by the oscillating mass, at least in a rest position of the support in which it is stationary and extends horizontally, and having the same shape as the rolling track of the support.

2. The oscillation damping device of claim 1, wherein the bearing applies a compression force (F) of less than 10N.

3. The oscillation damping device of claim 2, wherein the application track is shaped such that in the rest position, the compression force varies by less than 3N during oscillation of the oscillating mass on the support.

4. A wobble damping device as claimed in any one of claims 1 to 3, wherein the coating member is a ball, roller or pin fixed to the support and on which are mounted first and second bearings which bear on first and second weights, respectively, of the oscillating mass.

5. The oscillation damping device of claim 4 wherein the application member comprises first and second lateral pins mounted for rotation in first and second seats provided in the oscillating mass.

6. A device according to any one of claims 1 to 3, wherein said oscillating mass comprises a first and a second counterweight rigidly coupled to each other, which clamp said support and elastically compress the application member to elastically urge it towards the axis X.

7. The oscillation damping device of any one of claims 1 to 3 wherein the oscillating mass comprises a spring mounted to resiliently urge the application member towards axis X.

8. The oscillation damping device of any one of claims 1 to 3, wherein the application member and/or the support and/or the oscillating mass comprise a region of elastomeric material that imparts elasticity to the bearing of the application member on the oscillating mass and/or the support.

9. The oscillation damping device of claim 1 wherein the oscillation damping device is integrated into a drive train of a motor vehicle.

10. The oscillation damping device of claim 9 wherein the oscillation damping device is integrated into a clutch.

11. The oscillation damping device of claim 4 wherein the first and second bearings are supported on first and second weights of the oscillating mass, respectively, by resilient elements.

12. The oscillation damping device of claim 11 wherein the resilient element is a resilient ring.

13. A torsion damping device comprising a oscillation damping device according to any one of the preceding claims, selected from a double flywheel damper, a hydrodynamic torque converter and a friction disc.

14. A motor vehicle equipped with a torsional damping device according to claim 13.