KR102418733B1 - Vibration absorption device - Google Patents

Abstract

The present invention relates to a vibration absorbing device for a motor vehicle transmission, the device having an axis of rotation (X) and comprising a support (10) and an oscillator (20), the oscillator comprising a counterweight (25) and two rolling elements (30a) , 30b), wherein the support and the counterweight define a rolling track of the rolling element called a "support rolling track" and a "counterweight rolling track", respectively, so that the rolling of the rolling element on the rolling track is a support The mass of the counterweight, the so-called "ambient mass", which is located outside the cylindrical space defined by the support during rotation of the support about the axis X with respect to exceed

Description

Vibration Absorber {VIBRATION ABSORPTION DEVICE}

The present invention relates to a vibration absorbing device used in a transmission of an automobile.

In the transmission of an automobile, to filter out vibrations due to irregular rotation caused by explosions in the cylinders of the engine, a damping device typically coupled to a clutch selectively connecting the engine to a gearbox is used. This clutch may be a friction clutch for a manual transmission vehicle, or it may be arranged in a hydrodynamic coupling device for an automatic transmission vehicle, such as a lock-up clutch. Due to this damping device, usually in the form of a monoblock inertial flywheel, flexible flywheel or vibration absorber, the vibration effect of the engine is transmitted through the gearbox and causes shocks, noises or annoying noises that are particularly undesirable for the occupants of the vehicle. this is alleviated

The desire to achieve better filtering performance led to the integration of a pendulum oscillator in the vibration absorber.

In particular, pendulum oscillators comprising a counterweight capable of oscillating freely in a plane perpendicular to the axis of the transmission are known from the prior art.

From DE 10 2009 051 724, a vibration absorbing device is known comprising a support and a counterweight freely moving on a support, which consists of two flanges connected to each other by a roller passing through the flange. Also from DE 10 2011 086 436, FR 2 826 079, DE 10 2009 023 337, DE 10 2010 054 296, DE 10 2009 042 812 or DE 10 2011 104 137, installed over a support and Devices are known which comprise a counterweight consisting of two flanges connected by a spacer, which are freely moved by means of a counterweight and rollers supported on a support. Variations of such devices are also disclosed in US 2001/0195794, GB 5 985 811 or CH 191290.

The counterweight's mass is basically supported by flanges that act as an inertial mass that is involved in absorbing vibrations.

The trend in the automobile market consists in reducing the number of cylinders in an engine while increasing the power generated by the engine. As the power generated by each cylinder is increased, the devices generate a vibration spectrum that is difficult to filter and amplify the irregular rotation of the engine. In particular, an increase in the mass of flanges that are unstablely installed on the support may cause unstable shaking of the counterweight, which impairs the filtering efficiency of this vibration spectrum.

Therefore, there is a need for an apparatus for more efficiently filtering such a vibration spectrum.

On the other hand, the device according to the prior art disclosed above is not well adapted to the transmission of modern automobiles, in particular to small cylinder vehicles used in cities where the space between the engine and other elements of the transmission is limited.

Accordingly, there is a need for a more compact device.

It is an object of the present invention to meet this need, at least in part.

The present invention provides a vibration absorbing device for use in a transmission of a motor vehicle, comprising an oscillator and a support having a rotational axis (X) and comprising a counterweight and two rolling bodies,

- the support and the counterweight define rolling tracks for the rolling elements called "support rolling track" and "counterweight rolling track", respectively, so that rolling of the rolling elements on the rolling track produces a counterweight with respect to the support displace,

- a vibration absorbing device wherein the counterweight comprises a first flange and a second flange extending substantially radially with respect to the axis (X).

According to a first aspect, at least one, preferably all rolling elements are accommodated between said first and second flanges.

Advantageously, in use, the rolling element operates mechanically with essentially simple compression between the rolling track of the counterweight and the rolling track of the support. In this way, the oscillation of the counterweight is stabilized and the filtering of the vibration is improved. On the other hand, the risk of rupture due to aging is limited and the service life is improved.

According to a second aspect, the mass of the counterweight located outside the cylindrical space defined by the support during rotation of the support about the axis X, the so-called ambient mass, is greater than 30% of the total mass of the counterweight; preferably greater than 50%.

This ambient mass away from the axis X is particularly effective for damping vibrations. For performance comparable to that of prior art devices, the mass of the counterweight can be reduced. It is also possible to increase this mass as desired without increasing the thickness of the counterweight. The device is therefore advantageously very compact.

According to any one of the aspects, the device according to the invention may further comprise one or more of the following optional features and the additional features of the other aspects according to all possible combinations:

- the moment of inertia of the counterweight located outside the cylindrical space defined by the support during rotation of the support about the axis X is greater than 30%, preferably greater than 50% of the total moment of inertia of the counterweight .

- the rolling elements are partially or preferably fully accommodated between the flanges so that the counterweight can limit the axial play of the rolling elements.

- the support body is partially received between the flanges, such that the support body can limit the axial play of the counterweight.

- The axial play of the rolling element between the flanges is less than 1 mm.

- The rolling element has a roller or ball shape in the form of a cylinder or barrel, and one or more of the sides of the cylinder or barrel are arbitrarily curved.

- said first and/or second flanges have no openings to protect the members received therebetween.

- said first and/or second flanges are planar in order to simplify manufacturing and to be very compact.

- the thickness of the flange is less than 3 mm, preferably less than 1.5 mm and/or more than 0.2 mm, preferably more than 0.5 mm.

- the difference between the thickness of the counterweight and the thickness of the support is less than 5 mm, said thickness being measured along the axis of rotation (X).

- the difference between the radii of the cylindrical space defined during rotation about the axis (X) by means of a counterweight on the one hand and by the part of the support extending between the flanges on the other side exceeds the thickness of the support (E _s ) , preferably greater than 2*E _s , preferably greater than 3*E _s , preferably greater than 4*E _s , preferably greater than 10*E _s , preferably greater than 20*E _s .

- The center of gravity of the counterweight draws an epicycloid trajectory at the radially outer stop position of the counterweight. in other words,

- The counterweight comprises a spacer connecting the flanges.

- the spacer passes through the window of the support;

- The rolling track of the counterweight is provided on the spacer.

- the spacer is arranged partially, preferably completely, between the first flange and the second flange.

- the spacer is cut from a metal plate from which the support is cut, and the spacer consists at least partially, preferably completely, as part of a metal plate separated for cutting the window of the support.

- the spacer takes on a T-shape or anchor-shaped, and one branch of the spacer projects radially through the radial opening of the window of the support, which preferably defines the rolling track of the support, thereby simplifying the manufacture of the device.

- the spacer is in contact with the support in a radially inner stop position;

- said flanges extend beyond the spacer in the radial direction towards said axis (X), preferably cooperating with a support to improve the guiding of the counterweight, in another embodiment, on the contrary, the radially inner edge of the flange on the contrary of the spacer It may be superimposed on the inner edge.

- In another embodiment, the counterweight comprises two spacers called "radial inner spacer" and "radial outer spacer" (which their relative positions define).

- the radial outer spacer is located outside the cylindrical space defined by the support body during rotation of the support body about the axis X;

- the radial outer spacer is greater than 50%, preferably greater than 80%, preferably greater than 90% of the surrounding mass.

- If a radially outer spacer is present, the radially inner spacer is less than 40%, preferably less than 30%, or less than 20% of the mass of the counterweight.

- In the absence of a radially outer spacer, said spacer is greater than 50%, greater than 70%, or greater than 80% of the mass of the counterweight.

- the radially inner spacer and/or the radially outer spacer, preferably only the radially inner spacer, is in contact with the support in the radially inner stop position.

- the radial inner spacer is integral with the radial outer spacer, so that the radial inner and outer spacers constitute a single spacer, preferably a single cutout from one metal plate.

- All rolling elements of all oscillators of the device are placed in the same window of the support.

The invention also relates to a transmission of a motor vehicle selected from a friction clutch and a hydrodynamic converter, said transmission comprising a vibration absorbing device according to the invention.

Finally, the invention relates to a motor vehicle equipped with a transmission according to the invention.

BRIEF DESCRIPTION OF THE DRAWINGS The present invention may be better understood by the teachings of the detailed description set forth below and by way of example in the accompanying drawings.
1 shows a vibration absorbing device according to a first embodiment of the present invention, in which the flanges are shown transparently;
FIG. 2 shows a partial view of the absorbent device of FIG. 1 in a cross-sectional view along plane II;
3 is an exploded perspective view of a rolling element and components (a flange, a radially inner spacer and a radially outer spacer) of a counterweight according to an embodiment of the present invention;
4 shows a vibration absorbing device according to one embodiment, installed on the support plate of a double damping flywheel;
Figure 5 is an exploded perspective view of the vibration absorption device of Figure 4;
6 and 7 are respectively an exploded perspective view of a device according to the present invention;
8 and 9 each show a device according to an embodiment of the invention in an axial view on the one hand and an enlarged perspective view on the other hand;
In different drawings, the same or similar members are denoted by the same reference numerals.

Justice

For convenience, the “radial” direction is oriented at right angles to and passes through one axis. The axis defines the "axial" direction. The “perpendicular” direction is perpendicular to the axis and the radial direction at the same time. Unless otherwise specified, the axis is the axis of rotation (X) of the support of the vibration absorber.

By “axial” or “radial” plane or surface is meant a plane or surface whose normal vectors are collinear with respect to an axis or direction of an axis. By “longitudinal” plane or cross-section is meant a plane or cross-section including an axis. Unless otherwise specified, this axis is the axis of rotation (X).

The terms "radially inner" and "radially outer" define a position relative to the axis X: a radially inner object is closer to the axis X than a radially outer object.

The “inward-facing” and “outward-facing” orientations correspond to the orientation of the surface toward or opposite the axis (X). Normals to this surface are not necessarily radial.

"Radially outer stop position" and "radially inner stop position" mean any position at which an object can no longer be displaced along the radial direction, either radially outwardly or inwardly. A radially outer or inner stop position is not necessarily a blocking position, but is any radial stop position that permits displacement in an axial or vertical direction, or more generally in a direction comprising at least one non-radial component.

Unless otherwise specified, thickness corresponds to the largest dimension measured along axis (X). This may also be referred to as "full thickness".

Other objects, such as moving objects that are not mechanically interlocked by an engine, are typically referred to as "free movement".

The moment of inertia of an object means the moment of inertia of this object with respect to the axis of rotation (X) of the device.

A member "received between" the two flanges is disposed entirely in the space located between the two general planes defined by these flanges. It can be located partially or completely in the space located between these flanges.

By "comprising one (or two)" is meant, unless otherwise specified, including at least one (or at least two).

"Determining one" means "determining at least one," unless otherwise specified.

details

The embodiments shown in the drawings are preferred embodiments and are provided by way of example only. Accordingly, the present invention is not limited to these embodiments.

A vibration absorbing device 5 of the axis X according to a first embodiment is shown in FIGS. 1 to 3 . The vibration absorber 5 comprises a support 10 defining three windows 15 distributed equiangularly about an axis X, in which three identical pendulum oscillators 20 are arranged. is installed. Accordingly, only one oscillator 20 will be described.

The oscillator 20 is composed of a counterweight 25 and two rolling elements 30a and 30b.

The counterweight, the support and the rolling element may in particular consist of a metal alloy, preferably an aluminum alloy or steel, in particular a machined steel, such as a 16MnCr5 carbonitride material.

support

The support 10 is preferably in the form of a disk of preferably substantially constant thickness of less than 12 mm, or less than 8 mm and/or more than 2 mm, or more than 3 mm. The support may have a central recess 35 of the axis X into which the transmission shaft may be engaged. Preferably, the support is defined as a substantially planar metal plate.

The closed window 15 defines a radially inner support surface 40 and a radially outer support surface 45 on which counterweights and rolling elements can be supported, respectively.

In this way, the radially outer bearing surface 45 can define a rolling track of the support for the rolling element.

The support may further comprise perforations capable of securing the support on the attachment, for example on the support plate 50 of the double damping flywheel as shown in FIGS. 4 and 5 . In a variant, the support may also constitute a support plate of the double damping flywheel.

counter weight

The counterweight 25 is composed of a first axial flange 55a and a second axial flange 55b, a radially inner spacer 60 and a radially outer spacer 65 . The radial inner spacer 60 and the rolling elements 30a and 30b are disposed on the window 15 . A radial inner spacer 60 passes through the window end to end in an axial direction along the thickness of the support. The flanges sandwich the rolling elements, the radially inner spacer and the radially outer spacer. They are fixed to the radially inner spacer 60 and the radially outer spacer 65 , for example by way of rivets 70 . The radially inner spacer 60 and/or the radially outer spacer 65 may also be integral with one or both flanges. Preferably, the counterweight constitutes a slider that moves on the support in the axial plane via a rolling element.

1 , the flanges are substantially planar annular and each extend substantially in an axial plane. In one embodiment not shown, the flanges may have curved faces that adjust to the difference in thickness between the radially inner spacer 60 and the radially outer spacer 65 . The flanges may be flat or have a recess. Preferably, they can be flat to increase the total inertia of the counterweight. Preferably, the thickness (E _j ) of the flange is between 0.4 mm and 2.0 mm, alternatively between 0.7 mm and 1.2 mm. Preferably, the thickness of the flange (E _j ) is less than the thickness of the support (E _s ), preferably less than 0.9*E _s , preferably less than 0.7*E _s , preferably less than 0.5*E _s , preferably is less than 0.3*E _s , preferably less than 0.1*E _s . A flange of small thickness can be easily cut from a metal plate.

Preferably, the mass of each flange is less than 20%, or less than 10% of the total mass of the counterweight.

The radial outer spacer 65 is preferably more than 30%, preferably more than 40%, preferably more than 50%, preferably more than 60%, preferably more than 70% of the total mass of the counterweight. The preferably annular, radially outer spacer, preferably at least partially, preferably completely, extends radially out of the support and together with the flanges form a rider transverse to the support. Preferably, the radially outer spacer has a radially inner surface 75 and a radially outer surface 80 extending parallel to the axis X and preferably substantially cylindrical. The radius of the radial inner surface 75 is greater than the radius of the support body.

In one embodiment, the radial inner surface 75 is not in contact with the support and the bearing of the radial inner spacer on the radial inner support surface 40 of the window 15 defines a radially inner stop position of the counterweight. do. In another embodiment, on the contrary, contact is made between the support and the radial inner surface 75 which defines the radially inner stop positions ( FIGS. 4 and 5 ).

Preferably, the counterweight is configured such that it cannot come into contact with an adjacent counterweight. Preferably, in the position of maximum proximity between two adjacent counterweights, the distance between said adjacent counterweights is less than 3 cm, less than 1 cm, preferably less than 5 mm.

The radially inner spacer has a radially outer surface that defines a rolling track 85 of the counterweight. The rolling track 85 of the counterweight includes a plurality of bowls each receiving a rolling element. The window 15 and the radial inner spacer 60 are formed to prevent any contact between the two rolling elements 30a and 30b.

The rolling track 85 of the counterweight preferably has a profile complementary to that of the rolling element upon contact between the radially inner spacer and the rolling element, preferably ensuring axial guidance of the rolling element.

The radially inner spacer preferably has a substantially complementary radial inner surface 95 to the radially inner supporting surface 40 of the window 15 .

Thus, advantageously, contact between these two faces is possible along a larger area, so that shock and noise are limited.

The radially inner spacers hang on the sidewalls 105a, 105b of the window, opposite first and second sides 100a and second sides formed to define the extreme position of the counterweight in the oscillating motion of the counterweight relative to the support. 100b) is provided.

rolling element

In the vibratory motion of the counterweight, the rolling elements 30a, 30b can slide and/or preferably roll the counterweight along the rolling track of the counterweight in the bowl in which they are received.

The side, preferably the axial side, of the rolling element may be flat. However, as shown in FIG. 2 , the rolling element may have a protrusion in the form of, for example, a circumferential annular bead and/or pin 110 to define a surface in contact with the first flange and/or the second flange. have. Thereby, the vibrations of the rolling elements on the rolling track of the support and the rolling track of the counterweight are not hindered by friction with the flange. This improves vibration filtering.

The rolling element has a radially extending groove (relative to its rolling axis) which can cooperate with annular beads and/or grooves provided on the rolling track of the support and on the rolling track of the counterweight to ensure axial guidance. and/or cyclic beads.

Preferably, in the rolling track of the support, the difference between the thickness of the rolling element and the thickness of the support is less than 5 mm, more preferably less than 3 mm, or less than 1 mm. Preferably, the axial play of the rolling element between the first flange and the second flange is less than 5 mm, less than 3 mm, or less than 1 mm.

work

Preferably, after installing the vibration absorber on the transmission of the vehicle, the axis X is substantially perpendicular to the direction of earth's gravity.

When the support is not rotating, as shown in FIG. 1 , if a counterweight 25 is placed on top of the device, it rests on the support. Thus, contact of the counterweight is made between the radial inner spacer and the inner support surface 40 . If the counterweight is located at the bottom of the device, it rests on the rolling element rather than directly on the support.

While the support body rotates about the axis X, the counterweight 25 and the rolling element 30 are subjected to centrifugal acceleration. Preferably, the device is configured such that the counterweight is off the inner support surface 40 . Thus, the rolling element is compressed between the rolling track of the counterweight and the rolling track of the support at radially outer stop positions.

While the support is rotating, the counterweight 25 is rotationally interlocked about the axis of rotation (X). Under the influence of changes in the rotational speed of the support, the counterweight can vibrate relative to the support in the axial plane. The rolling element thus guides the movement of the counterweight relative to the support by displacing it in the axial plane by sliding and/or preferably rolling along the rolling track of the support and the rolling track of the counterweight.

The radial play of the counterweight relative to the rolling element and the support can advantageously prevent blockage of the counterweight in the oscillating movement of the counterweight.

The oscillating motion of the counterweight is limited by the contact of the sidewalls of the window with the sides 100a, 100b of the radial inner spacer in the lateral stop position of the oscillation, for example, as shown in FIG. 1 . In particular, these stops are defined such that no impact can occur between two adjacent counterweights.

During the oscillatory motion, under the influence of centrifugal acceleration, the rolling elements and the counterweight are arranged at a radially outer stop position of the rolling elements and the counterweight. The window 15 and the radially inner spacer 60 are formed so that the counterweight follows a broken line trajectory in its oscillating motion. On the other hand, the counterweight may be displaced by translational and rotational motions in the axial plane in its oscillating motion. Such movements, called compound movements, disclosed for example in WO 2012/171515 and DE 10 2011 085983, improve the filtering of vibrations.

4 and 5 show a second embodiment of the present invention. The support of the vibration absorber is installed on the support plate 50 of the double damping flywheel via rivets 115 formed to prevent friction between the counterweight and the support plate. The support plate 50 takes the form of an axial planar disc and typically cooperates with a double damping flywheel via legs 120 . It includes a central recess 125 into which the rotating shaft of the engine can engage parallel to the axis X and fixed to the support plate. The vibration absorber of FIGS. 4 and 5 is in particular the flanges 55a , 55b cut in order to prevent the counterweight from contacting the fixing rivet 115 on the support plate of the double damping flywheel in the oscillating motion of the counterweight. It is distinguished from the device disclosed above in that it has a part.

Also in this embodiment, the support is cut out such that it comprises a single window 15 through the support in its thickness. The radial inner spacers and rolling elements of the pendulum oscillator 20 are all housed within this single window. When the support is not rotating, if the counterweight is placed on top of the device, the radial outer surface 130 of the support and the radial inner surface 75 of the radially outer spacer 65 contact, whereby the counterweight rests directly on the support. . Accordingly, preferably, no contact can be made between the radial inner spacer and the support.

6 and 7 show a vibration absorbing device according to another embodiment of the present invention. The window 15 through the support in this embodiment comprises a radial opening 135 at the periphery of the support. The counterweight is formed of an anchor-type spacer (140), on which the flanges are fixed by means of rivets (70). The spacer 140 is formed to be accommodated in the window. It comprises a radial inner portion corresponding to the radial inner spacer 60 of the disclosed embodiments, a radial outer portion corresponding to the radial outer spacer 65 and an integral bridge connecting the radial inner portion and the outer portion. The outer portion projects from the window in a radial direction, and the integral bridge passes through the radial opening 135 of the window.

The radially inner portion is greater than 50%, greater than 60%, or greater than 70% of the mass of the counterweight.

In the embodiment shown in FIGS. 8 and 9 , the counterweight comprises a radially inner spacer 60 extending into the window 15 and having the flanges secured by rivets 70 . The counterweight further comprises a preferably cylindrical radially outer spacer 145 which also connects the flanges and is disposed within the radial opening 140 of the window 15 . Said radial outer spacer supports a ring 150, preferably made of an elastomeric material, such as rubber, which can be bearing-beared against one or both sides of the radial opening of the window. Thereby, the damping of the counterweight in the oscillating motion of the counterweight is improved.

The invention is not limited to the embodiments disclosed and shown.

In particular, in one embodiment, the flanges are constituted by a grating. The device may also include more or conversely fewer windows and/or oscillators. The counterweight may not include a radially outer spacer.

All features and all possible combinations of different aspects of the invention are contemplated.

Claims (9)

A vibration absorbing device for a transmission of an automobile, comprising: an oscillator (20) having a rotating shaft (X), a support (10), and an oscillator (20) comprising a counterweight (25) and two rolling elements (30a, 30b),
The support and the counterweight define rolling tracks for the rolling elements, called "support rolling track" and "counterweight rolling track", respectively, so that rolling of the rolling elements on the rolling tracks produces a counterweight with respect to the support. move,
A cylindrical space is formed by the support during rotation of the support about the axis X, and the mass of the counterweight located outside the cylindrical space, the so-called "peripheral mass", is the total weight of the counterweight. Exceeds 30% of the mass,
wherein all rolling elements of each oscillator of the device are arranged in a single window of a support, wherein the difference between the thickness of the counterweight and the thickness of the support is less than 5 mm, the thicknesses being measured along the axis of rotation (X) to do
vibration absorber. According to claim 1,
wherein said ambient mass is greater than 50% of the total mass of the counterweight.
vibration absorber. According to claim 1,
The counterweight includes first and second flanges 55a; 55b extending substantially radially with respect to the axis X, between the flanges receiving at least one rolling element, the flanges comprising the characterized in that they are connected by radially outer spacers (65) exceeding 90% of the surrounding mass
vibration absorber. 4. The method of claim 3,
and a radial inner spacer (60) traversing the window (15) of the support along the thickness of the support and connecting the flanges.
vibration absorber. delete According to claim 1,
further comprising an anchored spacer (140), wherein the radially outer portion of the anchored spacer passes through the radial opening (135) of the window (15) of the support to form a radial projection
vibration absorber. 4. The method of claim 3,
at least one rolling element is received between the first flange and the second flange
vibration absorber. A transmission of an automobile selected from a friction clutch and a hydrodynamic converter, the transmission comprising:
8. A vibration absorbing device according to any one of claims 1 to 4, 6 and 7 comprising
transmission. With a transmission according to claim 8
car.

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