DE102014113038A1 - Device for vibration damping - Google Patents

Abstract

A device (10) for vibration damping, which is intended for a motor vehicle transmission, wherein the device has a rotation axis X and a carrier (12) and an oscillator mounted on the carrier oscillator (14), wherein the oscillator a rolling body (18a, 18b), a weight (16) and a cushioning block (20) which limits the displacement of the weight relative to the carrier, the carrier and the weight defining "carrier roller paths" (28a; 28b) and "weight roller paths" (46a; 46b), respectively in that, by rolling the roller on the roller tracks, the weight is displaced relative to the carrier, the weight comprising two jaws (36a, 36b) and at least two fixing members (40) each connecting the jaws firmly, the cushioning block is rotationally fixed by a positive connection with the fixing member about an axis parallel to the axis X, wherein the carrier defines a window (24) which is closed and the carrier in the thickness of the Tr gers traversed, at least one fixing member (40a) is disposed in the window and at least one fixing member (40b; 40c) is arranged outside the window.

Description

Technical area

The present invention relates to a vibration damping device intended for a motor vehicle transmission.

State of the art

In a motor vehicle transmission, for filtering the vibrations due to nonuniformities caused by ignitions in the engine cylinders, conventionally a damper device associated with a clutch selectively connecting the engine to the transmission is used. This clutch may be arranged a friction clutch for a motor vehicle with manual transmission or in a device for hydrokinetic coupling for a vehicle with an automatic transmission as a lock-up clutch. Because of this damping device, which is generally a one-piece flywheel, flexible flywheel, or vibration damping device, it dampens the effect of engine vibrations that would otherwise be transmitted through the transmission and cause shocks, noise or noise disturbances to the occupants of the motor vehicle are particularly undesirable.

The attempt to obtain an increasingly efficient filtering of the oscillations led to the integration of a pendulum oscillator in these vibration damping devices.

Pendulum oscillators with weights which are able to oscillate freely in an axial plane, ie in a plane orthogonal to the transmission axis, are known from the prior art. From the DE 10 2009 042 836 a device for vibration damping is known with a freely movable on a support weight, which consists of two jaws, which are interconnected by three fastening members which traverse the carrier through a window formed in the carrier. The fasteners hold the jaws and prevent during operation of the device whose deflection in an axial plane that generates parasitic vibrations.

There is a need for a device that is quieter in operation and more effective at filtering the vibration spectra generated by an engine.

The object of the invention is therefore to meet this need at least partially.

Brief description of the invention

The invention proposes a device for vibration damping, which is intended for a motor vehicle transmission, wherein the device has a rotation axis X and a support and an oscillator mounted on the oscillator oscillator, said oscillator having a rolling body and a weight,
wherein the carrier and the weight define "carrier roller tracks" and "weight rollerways", respectively, such that by rolling the roller on the roller tracks the weight is displaced with respect to the carrier,
wherein the weight has two jaws and a fastening member which connects the jaws firmly.

According to a first aspect of the invention, the carrier defines a window which is closed and traverses the carrier in the thickness of the carrier, wherein the fastening member is arranged in the window and the fastening member and the window are formed so as to control the oscillating movement of the oscillator in Do not interfere with the wearer.

The fixing member advantageously contributes to the rigidity of the weight and makes it possible to prevent the deflection of the jaws in an axial plane in oscillating the weight.

Thus, the quality of the vibration filtering is improved while ensuring quiet operation of the device.

According to a second aspect of the invention, the vibration damping device comprises a damping block, which limits the displacement of the weight with respect to the carrier, wherein the damping block is non-rotatable by a positive connection with the fastening member about an axis parallel to the axis X.

The damping block is thus advantageously secured in a simple and effective manner on the fastening member. The wear of the damping block is also limited. The risk of detachment of the damping block from the attachment member, which can lead to a direct contact between the weight and the carrier, is thus reduced.

According to a third aspect, the vibration damping device comprises a damping block, which limits the displacement of the weight with respect to the carrier and is non-rotatable by a positive connection with the fastening member about an axis parallel to the axis X,
the weight has at least two fastening members which firmly connect the jaws,
the carrier defines a window that is closed and traverses the carrier in the thickness of the carrier, and
At least one fastening member is arranged in the window and arranged at least one fastening member outside the window.

The arrangement of the fastening members according to the third aspect of the invention advantageously allows the attachment of a damping block on the oscillator to effectively dampen the shocks of the weight on the carrier and thereby to ensure optimum stiffness of the weight. Low-noise operation of the device according to the invention is also ensured.

• – das im Fenster angeordnete Befestigungsorgan liegt dem Rand des Fensters direkt gegenüber;
• – der Träger ist teilweise zwischen den Backen angeordnet, wodurch der Träger den axialen Ausschlag des Gewichts begrenzen kann,
• – der Träger weist einen Trägerausschnitt auf, in dem ein Rollkörper angeordnet ist;
• – der axiale Ausschlag eines Rollkörpers zwischen den Backen ist kleiner als die Dicke des zwischen den Backen enthaltenen Teils des Befestigungsorgans;
• – die Backen weisen Backenausnehmungen auf, in denen die Rollkörper angeordnet sind und die vorzugsweise die Backen in ihrer Dicke durqueren;
• – die Backen begrenzen den axialen Ausschlag der Rollkörper;
• – die Backen sind so ausgebildet, dass sie in einer ersten Richtung bzw. in einer entgegengesetzten zweiten Richtung erste und zweite Rollkörperanschläge definieren, die den axialen Ausschlag des Rollkörpers in Bezug auf das Gewicht begrenzen; auf diese Weise werden die Stöße zwischen Rollkörper, Gewicht und Träger verringert, was die Betriebsgeräusche der Vorrichtung senkt;
• – die Backen sind eben;
• – die Dicke einer Backe beträgt weniger als 8 mm, vorzugsweise weniger als 5 mm und/oder mehr als 1 mm;
• – ein Rollkörper hat die Form einer zylinder- oder tonnenförmigen Rolle, die eine ringförmige Überdicke haben kann;
• – es ist kein Rollkörper in das Fenster eingesetzt;
• – das Befestigungsorgan ist an mindestens eine Backe, vorzugsweise an beide Backen genietet;
• – die Vorrichtung weist ein zweites und sogar ein drittes Befestigungsorgan auf, das bzw. die außerhalb des Fensters angeordnet ist bzw. sind;
• – das außerhalb des Fensters angeordnete Befestigungsorgan ist radial außerhalb des Trägers angeordnet;
• – das außerhalb des Fensters angeordnete Befestigungsorgan ist radial außerhalb des im Fenster angeordneten Befestigungsorgans angeordnet;
• – der Umfang des Befestigungsorganabschnitts, an dem der Dämpfungsblock angebracht ist, weist, entlang der Achse X gesehen, mindestens eine Symmetrieachse auf und/oder ist teilweise konkav und/oder hat eine insgesamt langgestreckte Form und/oder weist in einer orthoradialen Richtung eine größere Abmessung auf als in radialer Richtung und/oder weist mehrere Vorsprünge auf;
• – die Kontaktfläche zwischen dem Dämpfungsblock und dem Befestigungsorgan ist im Wesentlichen parallel zur Achse X;
• – das Befestigungsorgan definiert ein Zwischenelement, das sich zwischen den beiden Backen erstreckt, dessen Form, entlang der Achse X gesehen, nicht umlaufend ist;
• – die Dicke des Zwischenelements, d. h. seine entlang der Achse X gemessene Abmessung, ist größer oder gleich der Dicke des Trägers;
• – das Befestigungsorgan ist nur einem einzigen Dämpfungsblock zugeordnet;
• – der Dämpfungsblock besteht aus einem Elastomermaterial, vorzugsweise aus Kautschuk;
• – der Dämpfungsblock ist am Oszillator, vorzugsweise an einem Befestigungsorgan und/oder am Träger angebracht und definiert mindestens eine Stellung mit orthoradialem Anschlag;
• – der Umfang des Trägers definiert eine Vertiefung, an der sich der Dämpfungsblock vorzugsweise in der Stellung mit orthoradialem Anschlag abstützt;
• – das außerhalb des Fensters angeordnete Befestigungsorgan liegt der Vertiefung radial gegenüber und außerhalb dieser Vertiefung;
• – der Dämpfungsblock weist eine Öffnung auf, die den Dämpfungsblock in der Dicke des Dämpfungsblocks durchquert, wobei das Befestigungsorgan in der Öffnung angeordnet ist und auf der einen und auf der anderen Seite der Öffnung axial hervorsteht;
• – der Dämpfungsblock ist außerhalb des Fensters angeordnet;
• – der Dämpfungsblock ist an mindestens zwei Befestigungsorganen befestigt;
• – der Dämpfungsblock ist zwischen den beiden Backen angeordnet und vorzugsweise sandwichartig zwischen den beiden Backen eingeschoben;
• – der Umfang der Öffnung des Dämpfungsblocks ist, entlang der Achse X gesehen, geschlossen;
• – der Dämpfungsblock weist eine im Wesentlichen ebene Fläche auf, die zur Achse X ausgerichtet ist;
• – das zweite Befestigungsorgan und möglicherweise das dritte Befestigungsorgan durchquert/durchqueren den Dämpfungsblock vollständig durch die in der Dicke des Blocks definierte Öffnung und steht/stehen auf der einen und auf der anderen Seite der Öffnung axial hervor;
• – der Dämpfungsblock umklammert das Zwischenelement teilweise, vorzugsweise vollständig;
• – der Dämpfungsblock berührt den Träger in mindestens einer Stellung des Gewichts;
• – die axiale Verlagerung des Dämpfungsblocks wird durch die Backen und/oder durch ein Befestigungsorgan begrenzt;
• – das erste, zweite und dritte Befestigungsorgan bilden, entlang der Achse X gesehen, Spitzen eines vorzugsweise gleichschenkligen, sogar gleichseitigen Dreiecks;
• – in dem Fenster ist ein einziges Befestigungsorgan angeordnet;
• – das Gewicht ist vorzugsweise vollständig innerhalb des virtuellen Zylinders, der durch den Träger bei seiner Drehung um die Achse X definiert wird, angeordnet.

According to one of these aspects, a device according to the invention can furthermore, as mentioned below, comprise one or more additional features of the further aspects and optional features according to all possible combinations:

• - The arranged in the window attachment member is the edge of the window directly opposite;
• The support is partially disposed between the jaws, whereby the wearer can limit the axial deflection of the weight,
• - The carrier has a carrier cut, in which a rolling body is arranged;
• - The axial deflection of a rolling body between the jaws is smaller than the thickness of the part contained between the jaws of the fastening member;
• - The jaws have jaw recesses in which the rolling bodies are arranged and preferably duri through the jaws in thickness;
• - The jaws limit the axial deflection of the rolling elements;
• - The jaws are formed so that they define first and second rolling body stops in a first direction or in an opposite second direction, which limit the axial deflection of the rolling body with respect to the weight; in this way the shocks between the rolling body, the weight and the carrier are reduced, which lowers the operating noise of the device;
• - the cheeks are level;
• The thickness of a jaw is less than 8 mm, preferably less than 5 mm and / or more than 1 mm;
• - A rolling body has the shape of a cylindrical or barrel-shaped roller, which may have an annular over-thickness;
• - there is no rolling element inserted into the window;
• - The attachment member is riveted to at least one jaw, preferably both jaws;
• - The device has a second and even a third fastening member which is or is arranged outside the window or are;
• - The arranged outside the window attachment member is arranged radially outside of the carrier;
• - The arranged outside the window fastening member is arranged radially outside of the window arranged in the fastening member;
• The circumference of the mounting member portion to which the damper block is attached has at least one axis of symmetry, viewed along the axis X, and / or is partially concave and / or has an overall elongated shape and / or has a larger dimension in an orthoradial direction as in the radial direction and / or has a plurality of projections;
• - The contact surface between the damping block and the fastening member is substantially parallel to the axis X;
• - The attachment member defines an intermediate element which extends between the two jaws, the shape of which, viewed along the axis X, is not circumferential;
• The thickness of the intermediate element, ie its dimension measured along the axis X, is greater than or equal to the thickness of the support;
• - The attachment member is assigned to a single damping block;
• - The damping block is made of an elastomeric material, preferably of rubber;
• - The damping block is mounted on the oscillator, preferably on a fastening member and / or on the carrier and defines at least one position with orthoradialem stop;
• - The scope of the carrier defines a recess on which the damping block is preferably supported in the position with orthoradial stop;
• - The arranged outside the window attachment member is the recess radially opposite and outside of this recess;
• - The damping block has an opening which traverses the damping block in the thickness of the damping block, wherein the fastening member is arranged in the opening and axially protrudes on one and on the other side of the opening;
• - The damping block is located outside the window;
• - The damping block is attached to at least two fastening members;
• - The damping block is disposed between the two jaws and preferably sandwiched between the two jaws inserted;
• The circumference of the opening of the damping block is closed, as viewed along the axis X;
• - The damping block has a substantially flat surface which is aligned with the axis X;
• - traverses the second attachment member and possibly the third attachment member / traverse the damping block completely through the opening defined in the thickness of the block and stand / stand out axially on one and on the other side of the opening;
• - The damping block clasps the intermediate element partially, preferably completely;
• - The damping block touches the carrier in at least one position of the weight;
• - The axial displacement of the damping block is limited by the jaws and / or by a fixing member;
• - The first, second and third fastening member form, seen along the axis X, peaks of a preferably isosceles, even equilateral triangle;
• - In the window, a single fastening member is arranged;
• The weight is preferably located entirely within the virtual cylinder defined by the support as it rotates about the axis X.

The invention also relates to a motor vehicle transmission, which is selected from a friction clutch and a hydrokinetic converter, wherein the transmission has a device according to the invention for vibration damping.

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

Brief description of the figures

The invention will be better understood upon reading the following detailed description and upon consideration of the accompanying drawings. Show:

1 an apparatus for vibration damping according to an embodiment of the invention, wherein the jaws are shown transparent,

2 in a perspective exploded view of a section of the device 1 .

3 in an axial enlarged view of the device for vibration damping 1 with the oscillator in a position with orthoradial stop and a jaw removed.

In the various figures, identical or analogous organs have been designated by the same reference numerals.

definitions

Conventionally, a "radial" orientation is orthogonal to an axis and passes through this axis. The axis defines the "axial" orientation. An "orthoradial" orientation is orthogonal to both the axis and a radial orientation. Unless otherwise stated, the axis is the axis of rotation X of the carrier of the device for vibration damping.

By "axial" or "radial" plane or surface is meant a plane or surface in which a normal vector is collinear with an axis or with a radial orientation. "Longitudinal" or "Longitudinal" is a plane or section in which or in which the axis is included. Unless otherwise stated, this axis is the axis of rotation X.

The terms "radially inward" and "radially outward" define relative positions with respect to the axis X: a radially inner object is closer to the axis X than a radially outer object.

Orientations "inward" and "outward" correspond to orientations of a surface toward the axis X or opposite to the axis X. The normal to this surface is not necessarily radial.

By "position with outer radial stop" and "position with inner radial stop" is meant any position in which an object according to a radial direction can not be moved radially outwards or inwards. A position with external or internal radial abutment is not necessarily a blocking position, as in some radial-stop positions displacement in an axial or orthoradial direction or more generally in a direction comprising at least one component which is not radial is permitted.

"Position with orthoradial stop" is any position in which an object can not be moved along an orthoradial direction. An orthoradial stop position is not necessarily a locked position, as in some orthoradial stop positions, it is permissible to move in an axial or radial direction, or more generally in a direction that includes at least one component that is not orthoradial.

Unless otherwise indicated, a thickness corresponds to the largest dimension measured along the axis X. It can also be referred to as "total thickness".

A moving object that is not mechanically driven by another object, such as a motor, is conventionally referred to as "free-moving."

Unless otherwise indicated, "one (or two) means ..." or "one (or two) ... comprehensively" means "having at least one (or at least two) ...".

For an item that is "in" a "window", at least a portion of the item or even the entire item is contained in the window.

Unless otherwise stated, "defined" means "defined at least one".

Detailed description

The examples illustrated by the drawing are preferred embodiments which are given by way of illustration only. The invention is thus not limited to these embodiments.

In the 1 to 3 is a device 10 for vibration damping with an axis X according to an embodiment shown. The vibration damping device has a carrier 12 on which six identical pendulum oscillators are mounted, which are distributed at the same angle. Thus, only an oscillator 14 described.

The oscillator 14 consists of a weight 16 and two rolling bodies 18a and 18b ,

A damping block 20 is attached to the weight.

The weight, the carrier and the rolling elements may consist of a metal alloy, preferably of an aluminum or steel alloy, in particular of tempered steel, for example of 16MnCr5.

The damping block may be made of elastomeric material, preferably of rubber.

carrier

The carrier 12 has the shape of a disc, preferably with a substantially constant thickness, which is preferably less than 12 mm and even less than 8 mm and / or more than 2 mm and even more than 3 mm. The carrier may have a central recess 22 having the axis X, in which a drive shaft along the axis X can engage. The carrier is preferably defined in a substantially planar sheet metal.

The carrier defines a closed and continuous in the thickness of the wearer window 24 wherein the weight completely traverses the wearer through the window.

The carrier also has two carrier cutouts 26 on, which traverse the carrier in its thickness and in which the rolling bodies are arranged.

Each carrier cutout, the circumference of which is closed along the axis X, defines a carrier roll path 28a / 28b on which a rolling body can shift.

The carrier also has a recess 30 on, which lies on the circumference of the carrier and a radially outer bearing surface 32 defined at which the damping block 20 can get into contact.

The window 24 and / or the recess 30 is or are preferably in the carrier between the carrier cutouts 26 educated.

As in 1 illustrated, the recess is located radially substantially outside the window 24 ,

Thus, the material bridge carries 34 formed between the recess and the window contributes to the rigidity of the carrier and limits the deflection of the carrier in an axial plane during operation of the device. This arrangement of the recess and the window improves the damping quality of the device.

The carrier may further comprise bores which allow attachment of the carrier to a slave device, for example to a support cover of a dual damper flywheel. As a variant, the carrier can also form the support cover of the double-damping flywheel.

Weight

The weight consists of baking 36a and 36b axially on one side and on the other side of the support 12 extend, and from three identical attachment organs 40a . 40b and 40c that connect the jaws stiffly together. The jaws have holes that allow the passage of the fastening organs. The fasteners engage in the holes and are riveted to the jaws, thereby preventing any relative displacement of one jaw with respect to the other. Each attachment member has a central part or an intermediate element 41 which lies between the two jaws and whose shape is not circumferential. As in 3 illustrated, the intermediate element, as seen along the axis X, an overall elongated shape, wherein the dimension along an orthoradial direction is greater than along a radial dimension. The intermediate element also has radially inward 42a and outward facing surfaces 42b which are substantially planar and substantially parallel to the axis X and on which a contact with the damping block takes place. The intermediate element has a plurality of projections 43a to 43d on, which improve the connection between the damping block and the fastening member by positive engagement.

At the in 2 illustrated embodiment are the two fastening members 40b and 40c outside the window 24 in the radially outer recess 30 , wherein the third attachment member 40a within the window 24 lies. In a variant, not shown, the two fasteners may be within the window. It is then preferably arranged only a fixing member in the radially outer recess.

As in the 1 to 3 illustrated, is preferably at least one fastening member with respect to another radially inward. The fastening member outside the window is preferably arranged radially outside the fastening element arranged in the window.

Further preferably, the three attachment members are arranged to form the three peaks of an isosceles, even equilateral triangle, as viewed along the axis X.

As in particular in 3 illustrated, may be arranged in the window fastener 40a not with the window 24 contact the wearer.

The shortest distance between the edge 42 of the window 24 and the fixing member arranged in the window 40a is preferably more than 0.5 mm and even more than 1 mm.

The thickness of the intermediate element E _e is preferably more than the thickness of the carrier E _s , preferably more than 1.1 × E _s , preferably more than 1.2 × E _s .

The jaws each have two jaw recesses 44a and 44b on, in which the rolling bodies 18a respectively. 18b penetrate.

A jaw recess 44a or 44b can thus be a weight roller conveyor 46a respectively. 46b define.

The jaws are substantially annular and planar and each extending in a substantially axial plane. In one embodiment, not shown, the jaws may have a curved surface. In one embodiment, not shown, the jaws have jaw recesses which do not traverse the weight in thickness and do not overlap with the side surfaces of the rolling bodies, so that the rolling bodies arranged between the two jaws are protected.

A weight is preferably designed so that it can not come into contact with an adjacent weight. In a position of maximum approximation between two adjacent weights, the distance between the adjacent weights is preferably greater than the thickness of the carrier E _s .

Preferably, the weight, preferably completely, is within the virtual cylinder defined by the carrier as it rotates about the axis X.

roll body

With an oscillating movement of the weight, the rolling bodies can slide and / or preferably roll along the weight roller tracks and the carrier roller track.

As in 3 illustrated, a rolling body preferably has a circumferential shape and preferably a barrel or cylinder shape and may have a mean annular thickness 48 have to roll on the carrier roll. The middle annular over-thickness is preferably formed so that it can not penetrate into the jaw recesses into which the ends of the rolling bodies penetrate. It can thus come into abutment with the opposite side surfaces of the jaws and thus limit the axial deflection of the rolling body.

The difference between the distance between the two jaws and the thickness of the annular over-thickness is preferably less than 5 mm, even less than 3 mm and even less than 1 mm.

damping block

As in the 1 to 3 illustrates is the attenuation block 20 placed between the two jaws and can be sandwiched between them. The damping block has an opening which traverse the damping block in its thickness. As in 1 illustrated, it preferably has two through holes 50a and 50b on. An attachment member is disposed in each of these openings and completely traverses the damping block. Each attachment member is preferably forcefully mounted in the damping block to form a rigid assembly. For this purpose has every opening 50a and 50b preferably a shape corresponding to the shape of the intermediate element 41 is essentially complementary. In this way, no rotation of the damping block with respect to the fastening member is possible.

The damping block has an overall elongated shape and has a radially inwardly directed peripheral surface 52 on that to the area 32 the depression 30 is essentially complementary, where it comes into contact, as in 3 shown. The radially inwardly directed peripheral surface 52 is preferably substantially flat. The length of this surface is preferably greater than the distance between the two fastening members arranged outside the window, and preferably greater than 3 cm. Thus, the damper block may have a contact zone with the outwardly facing surface of the recess 30 form whose surface is optimal, whereby the shocks can be damped in a substantially radial direction between the weight and the carrier. Consequently, the noise-free operation of the device is improved.

In addition, with this contact surface with optimum surface, it is possible to reduce the wear of the damper block. Namely, at a given frictional force, the friction stress defined by the frictional force divided by the surface on which the contact is made is reduced.

The damping block also has rounded side surfaces 54 formed to be substantially complementary to the side surfaces 55 to be the depression. Thus, when the oscillator enters an orthoradial stop position, the damping block can effectively dissipate the energy of impact between the oscillator and the carrier. Since the two rounded side surfaces of the damping block mainly work by compression in the contact area with the carrier, the wear is limited by friction.

business

After assembly of the vibration damping device to a vehicle transmission, the axis X is preferably substantially orthogonal to the direction of gravitational force.

When the carrier 12 not spinning, like in 3 illustrates, and the oscillator 14 located in the upper part of the device, the damping block rests on the carrier.

Thus, in transitional phases, for example when the engine is at a standstill, the oscillator may transition from a radially outer stop position to a radially inner stop position in which the damping block 20 rests on the support, wherein the transition between the two stop positions is noiseless. When the weight 16 located in the lower part of the device, it is not directly on the support but on the rolling elements 18a and 18b on.

When the carrier is rotated about the axis X, the weight and the rolling elements are subjected to the effect of centrifugal acceleration. The device is designed so that the damping block from the radially outer bearing surface, which lies in the circumferential groove dissolves. The rolling elements then come in contact with the carrier and weight roller tracks. The rolling elements then work mainly on bending.

Upon rotation of the carrier becomes the weight 16 rotated about the rotation axis X. Under the effect of changes in the rotational speed of the carrier, the weight may oscillate with respect to the carrier in an axial plane. The rolling elements then guide the movements of the weight with respect to the carrier and thereby displace by a sliding movement and / or preferably by a rolling movement in an axial plane along the carrier roller tracks 28a and 28b and the roller coasters 46a and 46b ,

The radial deflection of the weight with respect to the rolling elements and on the carrier advantageously makes it possible to prevent the blockage of the weight during its oscillating movement. The fastening element arranged in the window then shifts between two end positions in the window and never reaches the edge 42 of the window 24 in contact. The intermediate element 41 of the fastener 40a and the window 24 are in particular designed so that the intermediate element in all positions of the weight, for example in the position with radial outer stop or in the position with orthoradialem stop of the weight, from the edge 42 of the window is spaced. In addition, this fixing member ensures the maintenance of a high rigidity, whereby a bending of the jaws is prevented with respect to an axial plane under the effect of the centrifugal force acceleration.

The oscillating motion of the weight is due to the contact of the side surfaces 55 the recess with the side surfaces 54 of the damping block in the oscillation positions with orthoradial stop of the oscillator, as in 3 illustrated limited. When the damping block abuts the side walls, the elastic properties of the damping block forming material promote low-noise damping of the weight on the carrier.

The invention is not limited to the described and illustrated embodiment.

In one embodiment, the carrier in particular has a plurality of windows in which fastening members are arranged, so that the connection between the jaws of the weight is further stiffened.

All possible combinations and features with respect to the different aspects of the invention are conceivable.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009042836 [0004]

Claims (20)

Contraption ( 10 ) for vibration damping intended for a motor vehicle transmission, the device having a rotation axis X and a support ( 12 ) and an oscillator mounted on the carrier oscillator ( 14 ), wherein the oscillator is a rolling body ( 18a . 18b ), a weight ( 16 ) and a damping block ( 20 ), which limits the displacement of the weight with respect to the carrier, the carrier and the weight being "carrier roller paths" (US Pat. 28a ; 28b ) or "weight roller tracks" ( 46a ; 46b ), so that by rolling the roller on the roller tracks, the weight is displaced relative to the carrier, the weight being two jaws (FIG. 36a ; 36b ) and at least two attachment organs ( 40 ), each of which firmly connect the jaws, wherein the damping block is non-rotatable by positive engagement with the attachment member about an axis parallel to the axis X, wherein the carrier is a window ( 24 ), which is closed and traverses the carrier in the thickness of the carrier, wherein at least one fastening element ( 40a ) is arranged in the window and at least one fastening member ( 40b ; 40c ) is located outside the window. Device according to the preceding claim, wherein only one fixing member is arranged in the window. Apparatus according to claim 1 or 2, wherein the fixing member arranged in the window directly faces the edge of the window. Device according to one of the preceding claims, wherein the fixing member arranged outside the window is arranged radially outside of the carrier. Device according to one of the preceding claims, wherein the fixing member arranged outside the window is arranged radially outside of the fixing member arranged in the window. Device according to one of the preceding claims, wherein the damping block is arranged outside the window. Apparatus according to claim 6, wherein the periphery of the carrier defines a recess on which the damping block is supported. Device according to claims 4 to 7, wherein the fixing member arranged outside the window is arranged radially opposite the recess and outside it. Device according to one of the preceding claims, wherein the damping block is attached to at least two fastening members. Device according to one of the preceding claims, wherein the fastening member is associated with only a single damping block. Device according to one of the preceding claims, wherein the fastening elements considered along the axis X form peaks of a preferably isosceles triangle. Device according to one of the preceding claims, wherein the damping block has a passage opening ( 50a ; 50b ) in the thickness of the damping block, in which a fastening member is arranged, wherein the fastening member on one side and on the other side axially protrudes. Device according to one of the preceding claims, wherein the axial displacement of the damping block is limited by the jaws and / or by a fastening member. Device according to one of the preceding claims, wherein the damping block has a substantially flat surface which is aligned with the axis X. Device according to one of the preceding claims, wherein the damping block consists of an elastomeric material, preferably of rubber. Device according to one of the preceding claims, wherein no rolling body is inserted into the window. Device according to one of the preceding claims, wherein the weight is preferably arranged completely in the virtual cylinder, which is defined by the carrier in its rotation about the axis X. Transmission of a motor vehicle, which is selected from a friction clutch and a hydrokinetic converter, wherein the transmission comprises a device for vibration damping according to one of the preceding claims. Motor vehicle equipped with a device according to the preceding claim. Contraption ( 10 ) for vibration damping intended for a motor vehicle transmission, the device having a rotation axis X and a support ( 12 ) and an oscillator mounted on the carrier oscillator ( 14 ), wherein the oscillator is a rolling body ( 18a ; 18b ), a weight ( 16 ) and one Attenuation block ( 20 ), which limits the displacement of the weight with respect to the carrier, the carrier and the weight being "carrier roller paths" (US Pat. 28a ; 28b ) or "weight roller tracks" ( 46a ; 46b ), so that by rolling the roller on the roller tracks, the weight is displaced relative to the carrier, the weight being two jaws (FIG. 36a ; 36b ) and at least two attachment organs ( 40 ), each of which firmly connect the jaws, wherein the damping block is non-rotatable by positive engagement with the attachment member about an axis parallel to the axis X, wherein the carrier is a window ( 24 ), which is closed and traverses the carrier in the thickness of the carrier, wherein at least one fastening element ( 40a ) is arranged in the window and at least one fastening member ( 40b ; 40c ) is arranged outside the window, wherein the support has a depression on its circumference ( 30 ), wherein the damping block at the recess ( 30 ) is supported.

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