WO2013117839A1

WO2013117839A1 - Pendular shock-absorbing device for a motor vehicle transmission

Info

Publication number: WO2013117839A1
Application number: PCT/FR2013/050170
Authority: WO
Inventors: Jonathan ROST; Clément TONDELLIER; Paolo Viola; Roel Verhoog
Original assignee: Valeo Embrayages
Priority date: 2012-02-07
Filing date: 2013-01-28
Publication date: 2013-08-15
Also published as: FR2986591A1; FR2986591B1

Abstract

The invention relates to a pendular shock-absorbing device comprising pendular bodies (39) movably mounted onto a pivotable support element (26, 33) provided with abutments (30, 47) capable of limiting the movement of the pendular body (39) between two end positions. The pendular body (39) is designed to engage, in each of the end positions, with the support element (26, 33) at one of the circumferential ends (43, 44) thereof and at one of the radially inner (46) or outer (45) edges thereof.

Description

Pendulum damping device for a motor vehicle transmission

The present invention relates to a pendulum damping device in a torque transmission for a motor vehicle, in particular in a double damping flywheel.

The document FR 2 826 079 describes a double damping flywheel for a motor vehicle, comprising a primary flywheel intended to be coupled to a motor shaft, such as for example a crankshaft, and a secondary flywheel, intended to be coupled to a drive shaft. input of a gearbox via a clutch.

The primary flywheel comprises two elements, a flywheel and a cover, welded to one another at their radially outer periphery, so as to delimit a sealed internal volume in which are mounted curved elastic members such as coil springs. helical.

The elastic members extend circumferentially and bear, at a first end, on the flywheel and / or on the cover and, at a second end, on an annular web connected to the secondary flywheel.

In operation, the elastic members are pressed against chutes disposed at the outer periphery of the aforementioned volume under the effect of centrifugal forces. This volume includes grease to ensure the proper functioning of the elastic members.

The double damping flywheel further comprises pendular damping means, housed in the aforementioned internal volume, and comprising pendular masses mounted movably on the annular web, in particular by means of guide rollers. These masses are arranged radially inside or outside the curved elastic members. The guide rollers are mounted in arcuate elongated holes of the pendular masses and the annular web. The edges of the oblong holes thus form raceways for the rollers.

In operation, the circumferential ends of the pendular masses come into abutment, so as to limit the movement of the masses and prevent the rollers abut against the ends of the oblong holes. The circumferential ends of the masses may include rubber damping means to limit noise.

A known variant of the document DE 10 2009 042 825, consists in providing studs extending between the circumferential ends of the masses in order to limit the displacement of the masses by abutment of their circumferential ends on these pads.

In each case, the abutment surfaces are relatively limited, which can cause damage to the ends of the masses, noise and poor control of the stability of the masses when they come into abutment, extreme position.

The invention aims in particular to provide a simple, effective and economical solution to this problem.

For this purpose, it proposes a pendulum damping device, in particular for a motor vehicle transmission, comprising at least one pendular mass movably mounted on a support member adapted to pivot about an axis, the support element comprising abutments adapted to limit the displacement of the pendulum mass between two extreme positions, the pendulum mass having two circumferential ends and radially inner and outer edges connecting said circumferential ends, the pendulum mass comprising abutment zones on the support element at the one of its circumferential ends and at its radially inner edge or its radially outer edge, characterized in that the inner edge of the pendulum mass comprises a first abutment zone located near a first circumferential end and a second stop zone located near a second circumferential end, so as to abut, in a first extreme position, on the support element at the first circumferential end and the second zone of its radially inner edge and, in a second extreme position, on the support member at the second circumferential end and the first zone of its radially inner edge.

The pendulum mass thus comprises, for each end position, two abutment zones spaced apart from one another to limit the displacement of the pendulum mass towards its end position, which makes it possible to ensure the stability of the pendulum mass during the contact and reduce the risk of degradation.

Preferably, the circumferential ends, on the one hand, and the radially inner edge or the radially outer edge, on the other hand, of the pendulum mass comprise elastically deformable means intended to bear against the support element in the one or other of the extreme positions of the pendulum mass.

These deformable means make it possible to reduce the impacts during the contacts, so as to limit the noise during operation.

The deformable means may be made of elastomer. According to one embodiment of the invention, the deformable means comprise studs protruding from the pendulum mass, located at each of the circumferential ends of the pendulum mass, on the one hand, and at the radially inner edge or the radially outer edge, on the other hand.

According to another embodiment of the invention, the deformable means are in the form of a band extending from one circumferential end to the other of the pendulum mass, extending along the radially inner edge or the radially outer edge of the pendulum mass.

Advantageously, the support element comprises an annular web comprising an annular portion from which at least two radial tabs, the pendulum mass being designed to abut, in each extreme position, on a radial tab at a circumferential end of the pendulum mass, on the one hand, and on the outer periphery of the annular part, at the radially inner edge of the pendulum mass, on the other hand.

In this case, each abutment zone of the inner edge may have a concave shape, with a radius of curvature substantially equal to the radius of the outer periphery of the annular portion of the annular web.

Preferably, the pendulum mass comprises at least two oblong holes in the shape of a circular arc for mounting at least two rollers, said rollers being engaged in arc-shaped holes of at least one support fixed to the annular sail.

According to a possibility of the invention, the mass comprises a central part, on both sides of which are arranged at least two lateral parts, the elastically deformable means comprising at least one part engaged by complementary shape in the central part of the pendulum mass and retained on both sides by the side portions, and at least one projecting portion, adapted to abut against the support member.

In addition, the pendulum mass may be designed to abut on the support member first at one of its circumferential ends, then at its radially inner edge or its radially outer edge, or conversely, for each extreme position.

When the masses comprise elastic damping means, such a time shift between the two stops provides a gradual damping of the masses, with stiffness constants that change over time.

Preferably, the circumferential ends of the pendulum mass comprise deformable means having a constant stiffness different from that of the deformable means equipping the radially inner edge or the radially outer edge of the pendulum mass, the deformable means abutting in a first time having a lower stiffness than the deformable means abutting in a second time.

The invention will be better understood and other details, characteristics and advantages of the invention will appear on reading the following description given by way of non-limiting example with reference to the accompanying drawings in which:

FIG. 1 is an exploded perspective view of a double damping flywheel according to the invention,

FIG. 2 is a view in axial section of the double damping flywheel of FIG. 1,

FIG. 3 is an exploded perspective view of the annular web, the supports and the pendular damping means of the double damping flywheel of FIGS. 1 and 2,

FIG. 4 is a view corresponding to FIG. 3, illustrating an alternative embodiment of the invention,

- Figures 5 to 7 are side views and in partial radial section of the double damping flywheel of Figures 1 to 3, in three different positions of the pendulum masses,

FIG. 8 is a perspective view of a pendulum mass,

FIG. 9 is an exploded perspective view of the pendulum mass of FIG. 8;

FIGS. 10 and 11 are views respectively corresponding to FIGS. 8 and 9, illustrating a pendulum mass according to another embodiment of the invention,

FIG. 12 is a detailed view of part of the double damping flywheel, in which the guide roller has been removed,

FIG. 13 is a view of a guide roller,

FIG. 14 is a view corresponding to FIG. 12, in which the guide roller is shown, FIGS. 15 and 16 are views corresponding to FIG. 14, illustrating two other embodiments of the invention,

FIGS. 17, 18 and 19 are views respectively corresponding to FIGS. 14, 12 and 13, illustrating another embodiment of the invention,

FIG. 20 is a front view of the pendulum mass of FIGS. 17 and 18,

FIG. 21 is a perspective view of the annular web, supports and pendular damping means according to another embodiment,

FIG. 22 is a front view of the assembly of FIG. 21,

FIG. 23 is a sectional view along the line A-A of FIG. 22,

- Figures 24 and 25 are views respectively corresponding to Figures 22 and 23 of an alternative embodiment of the invention.

A double damping flywheel according to a first embodiment of the invention, in particular for a motor vehicle transmission, is shown in FIGS. 1 and 2. It comprises a primary flywheel 1 comprising a central hub 2, called a primary hub 2, comprising a cylindrical tubular portion 3 from which a radial portion 4 extends radially outwardly. The radial portion 4 of the primary hub 2 is fixed to the end of a crankshaft 5 (FIG. 2) of an internal combustion engine by means of screws 6. This radial portion 4 is also fixed radially at the periphery. internal of an annular plate 7, axially flexible or not, This sheet 7 has holes 8 in the middle part, whose function will be described later.

A primary annular mass of inertia 9 is fixed to the radially outer periphery of the annular plate 7.

The primary mass of inertia 9 comprises a part 10 (FIG. 2) extending radially, the radially outer periphery of which is extended forward by cylindrical rim 1 1. The front face of the radial portion 10 comprises two diametrically opposite projecting elements 12 (FIG. 1) intended to form bearing faces.

The free edge of the cylindrical flange 1 1 is fixed, for example by welding, to the radially outer periphery of another annular sheet 13, more particularly to the rear radial face of this sheet 13. A ring gear 14, intended to mesh with a starter belt is fixed on the front face of the sheet 13.

The sheet 13 comprises two elements 13a projecting axially rearward, diametrically opposed, arranged facing the projecting elements 12 of the primary mass of inertia and each forming two bearing faces.

The primary mass of inertia 9 and the annular plate 13 define an internal space, intended to be filled with grease and serving to accommodate curved elastic members 15.

These elastic members 15 are helical compression springs, mounted in the aforementioned internal space. More particularly, during assembly, the ends 16, 17 of the curved elastic members bear against the bearing faces defined by the projecting members 12, 13a. The primary mass of inertia 9 and the annular plate 13 thus form guide washers.

Curved chutes 18 in cylinder portions are mounted between the inner wall of the cylindrical flange 11 and the elastic members 15, these chutes 18 serving to support the elastic members 15 when they deform by centrifugation in operation.

A secondary flywheel 19 is centered and guided in rotation on the primary flywheel 1.

The secondary flywheel 19 comprises a so-called secondary mass of inertia 20, comprising in its center a bore 21 for mounting and centering the secondary mass of inertia 20 on the part cylindrical 3 of the primary hub 2, through a ball bearing 22 (Figure 2).

The secondary mass of inertia 20 has holes 23 (FIG. 1) serving for the passage of a tool for screwing or unscrewing the fastening screws 6 of the primary flywheel 1 on the end of the crankshaft 5, and holes 24 for These rivets 25 make it possible in particular to fix an annular web 26 to the second mass of inertia 20.

As best seen in Figure 3, the annular web 26 has an annular portion 27 from which two diametrically opposed legs 28 extend radially outwardly.

Each lug 28 comprises two opposite bearing faces 29 of the resilient members located radially on the outside, and two opposite bearing faces 30, the function of which will be described later, located radially inward with respect to the faces of FIG. support 29.

The bearing faces 29 of the elastic members 15 form an angle relative to each other and diverge from each other outwardly. The faces 30 also form an angle relative to each other and diverge radially inwardly.

In operation, when a torque is transmitted from the primary flywheel 1 to the secondary flywheel 19, the elastic members 15 bear, at a first end 16 or 17, against the bearing faces 12, 13a of the primary flywheel 1, and at a second end 17 or 16 against the bearing faces 29 of the tabs 28 of the annular web 26, belonging to the secondary flywheel 19.

The resilient members 15 can dampen and absorb vibrations and motor rotation acyclisms, as is known per se.

In an embodiment not shown, the elastic members 15 are associated with friction means for dissipating the energy by friction.

On the contrary, in the embodiment shown, no additional friction means is added, the energy being dissipated by the natural friction between the primary mass 9 and the secondary mass 19, largely due to the friction of the elastic members 15.

Two diametrically opposite stops 31 extend radially outwardly from the annular web 26. Each abutment 31 has two opposite lateral bearing surfaces 32 forming an angle with each other and diverging from each other. the other radially inwards.

Supports 33 in the form of annular sheets are mounted on either side of the annular web 26.

Each support 33 has a radially inner portion 34, intended to be fixed to the annular web 26, to the opposite support 33 and to the secondary mass of inertia 20, via the rivets 25.

Other rivets 35 serve to fix the subassembly consisting of the supports 33 and the annular web 26 (Figure 2).

The holes 8 formed in the sheet 7 of the primary flywheel 1 are arranged opposite the rivets 25 and allow the passage of a riveting tool.

Each support 33 further includes a radially outer portion 36, connected to the radially inner portion by a generally frustoconical portion 37 (Figure 3). The radially outer portion 36 is axially offset from the radially inner portion 34, opposite the web 26. Thus, the radially inner portions 34 of the supports 33 are pressed against the annular web 26 while the radially outer portions 36 are spaced apart. , of a determined axial distance, for example between 7 and 20 mm.

Some areas of the frustoconical portions 37 are perforated, so that the radially outer portions 36 are connected to the radially inner portions 34 by radial tabs 38. The radially inner portions have fastening tabs 34a extending into the perforated areas and in which are formed holes 34b for mounting the rivets 25. This embodiment provides a flat area for the support of the secondary flywheel 20 and the rivet head 25 while reducing the diameter of the axial offset, in order to enlarge the internal radial space for the implementation of the pendulum masses. Four pendular masses 39 are mounted between the radially outer portions 36 of the supports 33, around the annular web 26. More particularly, each mass 39 is mounted circumferentially between a tab 28 and a stop 31.

The radially outer portion 36 of each support 33 has four pairs of elongated arc-shaped holes 40, the concavity of which is turned radially inwards. Each pair of oblong holes 40 is intended for mounting a mass 39. The oblong holes 40 of one of the supports 33 are arranged facing the oblong holes 40 of the other support 33.

Each pendulum mass 39 has three portions 39a, 39b of the same overall arc shape, respectively a central portion 39a and two side portions 39b, disposed on either side of the central portion 39a. The different parts 39a, 39b are fixed to each other by means of three rivets 41, the rivet heads 41 resting on countersinks 42 formed in the side portions 39b. Alternatively, it is possible to fix the three parts 39a, 39b and 39c by gluing or welding.

As is better seen in FIGS. 8 and 9 in particular, each of the portions 39a, 39b has two circumferential ends 43, 44 which are substantially radial, connected by a curved outer peripheral edge 45 and an inner peripheral edge 46. The inner peripheral edge 46 is composed of two zones 46a, 46b each extending over one half of said edge 46, each zone 46a, 46b being curved and having a radius of curvature substantially equal to the radius of the outer periphery 47 of the annular web 26. The inner peripheral edge 46 has thus two adjacent concave zones 46a, 46b, in contrast to the outer peripheral edge 47 which is continuous. Each of the parts 39a, 39b further has two elongated holes 48a, 48b in the shape of a circular arc, whose concavity faces outwards, each arranged between two rivets 41.

As best seen in Figures 12 and 14, the radially inner edges 49a oblong holes 48a of the central portion 39a are located radially inwardly relative to the radially inner edges 49b of the oblong holes 48b of the side portions 39b. In addition, the radially outer edges 50a of the oblong holes 48a of the central portion 39a are located radially outwardly with respect to the radially outer edges 50b of the oblong holes 48b of the side portions 39b.

Guide rolls 51 are mounted loosely in the arcuate oblong holes 48a, 48b, 40 of the masses 39 and supports 33.

As can be seen more clearly in FIGS. 13 and 14, each roller 51 comprises a central cylindrical zone 51a of diameter D1, bordered on both sides by two cylindrical intermediate zones 51b, of diameter D2, and two end zones. cylindrical 51 c, of diameter D3. The diameter D1 is greater than the diameter D2, itself greater than the diameter D3.

E1 denotes the radial dimension of the oblong holes 48a of the central portions 39a of the masses 39, that is to say the distance from the inner peripheral edge 49a to the corresponding outer peripheral edge 49b.

E2 denotes the radial dimension of the oblong holes 48b of the lateral portions 39b of the masses 39. Finally, e3 is the radial dimension of the oblong holes 40 of the supports 33.

The assembly with clearance of the rollers 51 in the masses 39 and in the supports 33 implies that e1 is greater than D1, that e2 is greater than

D2 and that e3 is greater than D3.

Moreover, D1 is greater than e2 and D2 may possibly be greater than e3. The axial length of the central zone 51a of each roller 51 is slightly less than the axial thickness of the central portion 39a of the corresponding mass 39. The fact that D1 is greater than e2 implies that, when the rollers 51 are mounted in the masses 39, they are housed captively in the corresponding oblong holes 49a, 49b. Indeed, the radial shoulders 52 formed between the central zone 39a and the intermediate zones of the rollers are able to abut against radial shoulders 53, situated radially inwards, formed between the oblong holes 49a of the central portion 39a and the oblong holes 49b of the lateral parts 39b of the masses 39.

The shoulders 53a located radially outward facing the internal shoulders 53, have a greater clearance chamfer angle than that of the internal shoulders 53, so as to avoid the friction of the rollers 51 on the outer shoulders 53a.

Likewise, the radial shoulders 54 formed between the intermediate zones 51b and the end zones 51c of the rollers 51 (FIG. 12) are designed to bear, in operation, respectively against the front face of the rear support 33 and against the rear face of the front support 33, which ensures the correct axial positioning of the masses 39 between the supports 33. The distance between the two shoulders 54 is slightly smaller than the distance between the two radially outer portions 36 of the supports 33.

Preferably, at least some of the aforementioned shoulders may be frustoconical or be oblique with respect to the radial plane, in particular the shoulders 52 and 53, so as to ensure the centering of the masses 39 during the rapid rotation of the rollers 51 inside. oblong holes 48a, 48b of the masses 39.

The radial dimensions of the various shoulders are relatively small, so as to limit friction.

It is recalled that in operation, the masses 39 and the rollers 51 are pushed radially outwards by the centrifugal forces. Thus, in operation, the rollers 51 bear on the edges internal peripherals 49b of the oblong holes 48b of the lateral portions 39b of the masses 39 (FIG. 14) or on the inner peripheral edges 49a of the oblong holes 48a of the central portions 39a of the masses 39 (FIG. 15).

The embodiment of FIG. 14 has the advantage of preventing the masses 39 from tilting. In the embodiment of FIG. 15, the rolling of the rollers 51 is only on the part 49a. The realization of the masses 39 is easier because the two parts 39b do not need a very precise alignment of the inner peripheral edges 49b with respect to each other. In addition, in operation, the rollers 51 bear on the outer peripheral edges of the oblong holes 40 of the supports 33.

As can be seen more clearly in FIGS. 8 to 11, each mass 39 may comprise resiliently deformable damping means at its circumferential ends 46, 44 and its radially inner edge 46 intended to bear against the faces support 29 of the tabs 28 or against the bearing faces 32 of the stops 31, and against the radially outer edge 47 of the annular web 26.

In the embodiment of FIGS. 8 and 9 in particular, these damping means are formed by an elastomeric strip 55 extending continuously from one circumferential end 43 to another 44, passing through the radially inner edge 46 of the central portion 39a of the corresponding mass 39. This strip 55 comprises dovetail studs 56 on its side facing the central portion 39a, inserted and locked in openings 57 of complementary shape to the central portion 39a, opening at the circumferential ends 43, 44 and radially inner edge 46. In addition, the shape of the strip 55 follows the profile of the inner peripheral edge 46 of the central portion 39a, so that the strip 55 also has two adjacent concave areas 58a, 58b (FIG. 8), each zone 58a, 58b having a radius of curvature substantially equal to the radius of the outer periphery 47 of the annular web 26. Preferably, the radial edge internally 46 of the central portion 39a is located radially outwardly relative to the radially inner edges 46 of the side portions 39b, so as to trap the web 55 between the side portions 39b after mounting.

The band 55 protrudes beyond the circumferential ends and the inner edge of the lateral portions 39b of the masses 39, in order to bear against the bearing faces 29 of the lugs 28 and / or on the outer peripheral edge 47 of the annular veil 26.

The mounting of the masses 39 is carried out as follows. First, the dovetail pads 56 are mounted in the openings 57 so as to position the elastomeric strip along the circumferential ends 43, 44 and the corresponding edge 46 of the central portion 39a. The central zones 51 with rollers 51 are also engaged with clearance in the oblong holes 48a of the central portions 39a of the masses 39. The lateral portions 39b of the masses 39 are then pressed on either side of the central portion 39a, the zones intermediate 51 b rollers 51 being housed with clearance in the oblong holes 48b of said side portions 39b. The different portions 39a, 39b of the masses 39 are then fixed to each other by the rivets 41. The rollers 51 are then mounted captively on the corresponding masses 39 and the elastomeric strip 55 is also fixed on the central portion 39a, between the lateral parts 39b, which allows easy handling of the assembly before assembly of the masses 39 between the The elastomer strip 55 is thus held radially and axially.

In the embodiment of Figures 10 and 1 1, the damping means are formed by four cylindrical studs 59 made of elastomer, housed in holes 57 in the form of a cylinder portion. A hole 57 opens at each of the circumferential ends 43, 44 of the central portion 39a, two other holes 47 opening at each of the concave portions 46a, 46b of the inner edge 46 of the central portion 39a of the mass 39 corresponding. The edges of these holes 47 extend over more than 180 °, so that when the cylindrical studs 59 are housed in these holes 47, they can not escape to the outside. Of course, the dimensions of the holes 47 and the pads 59 are adapted so that a sufficient portion of the pads (for example between 0.5 and 5 mm) protrudes outwardly from the central portion 39a, in order to come into bearing against the bearing faces 30 of the tabs 28 and / or against the outer peripheral edge 47 of the annular web 26.

As previously, the lateral portions 39b are fixed on either side of the central portion 39a, by means of rivets 41, so as to maintain the cylindrical studs 59 in the holes 47 mentioned above.

In operation, the masses 39 are movable between two extreme positions shown in FIGS. 5 and 7, an intermediate position being represented in FIG.

In the extreme position shown in Figure 5, the masses 39 are positioned obliquely to the circumferential direction. One 44 of the circumferential ends 43, 44 abuts against the corresponding bearing face 32 of the abutment 31, the concave zone 58a of the elastomeric strip 55 which is opposite the aforementioned circumferential end 44 bearing against the outer periphery 47 of the annular web 26.

In the extreme position shown in FIG. 7, the masses 39 are also positioned obliquely with respect to the circumferential direction. One 43 of the circumferential ends 43, 44 abuts against the corresponding bearing surface 30 of the tab 28, the concave zone 58b of the elastomeric strip 55 which is opposite the aforementioned circumferential end 43 bearing against the outer periphery 47 of the annular web 26.

In operation, the masses 39 are intended to swing in a pendular manner from one extreme position to another, via the intermediate position shown in Figure 6 wherein the masses 39 are spaced from the annular web 26, lugs 28 and abutments 31.

This pendulum movement of the masses 39 makes it possible to absorb the vibrations and the rotational acyclisms of the motor.

As a variant, the support can be made, at first, at a circumferential end 43, 44 or respectively of a concave zone 58a, 58b, and then, in a second step, the support can be realized at the concave zone 58a, 58b or respective circumferential end 43, 44. This makes it possible to obtain progressive damping of the masses 39, with stiffness constants which change over time.

In an alternative embodiment, the deformable means equipping the circumferential ends 43, 44, on the one hand, and the radially inner edge 46, on the other hand, have different stiffnesses, the deformable means bearing in a first place presenting a lower stiffness than the deformable means bearing in a second time.

In the extreme positions of FIGS. 5 and 7, the rollers 51 do not come into contact with the ends of the oblong holes 40, 48a, 48b of the supports 33 and masses 39, which makes it possible to limit the noise during operation. In general, the pendular damping means also contribute to reducing the noise in operation.

FIGS. 4 and 16 show another variant embodiment in which the masses 39 are made in one piece, the rollers 51 having a generally cylindrical shape, two flanges 60 extending radially outwards and being spaced apart axially from one of the other.

In this particular embodiment, the masses 39 may be devoid of elastically deformable damping means 55, 59. Each flange 60 is interposed between a radial face of one of the supports 33 and a radial face of the mass 39. The flanges 60 thus make it possible to avoid the friction of the masses 39 against the supports 33, the radial dimensions of the flanges 60 being limited to reduce friction.

FIGS. 17 to 20 illustrate yet another embodiment in which the radial dimension e2 of the oblong holes 49b of the lateral portions 39b of the masses 39 is greater than the radial dimension e3 of the oblong holes 40 of the supports 33 and greater than the radial dimension e1 oblong holes 49a of the central portions 39a of the masses 39.

Similarly, the diameter D2 of the intermediate zones 51b of the rollers 51 is greater than the diameter D3 of the end zones 51c, itself greater than the diameter D1 of the central zone 51a.

As before, the shoulders 52, 53 and / or 54 may have a frustoconical shape or be oblique with respect to the radial plane.

The oblong holes 49a of the central portions 39a of the masses 39 have enlarged ends 63, visible in dashed lines in FIG. 20, so as to allow the intermediate zones 51b of the rollers 51 to pass through said enlarged ends 63.

This embodiment makes it possible to reduce the Hertz pressures between the rollers 51 and the masses 39, and between the rollers 51 and the supports 33 since it makes it possible to increase the diameter of the zones 51b of the rollers 51 intended to roll.

In this embodiment, the intermediate zones 51b of the rollers 51 are intended to roll against the edges of the oblong holes 49b of the lateral portions 39b of the masses 39. The central zones 51a are, in turn, not intended to roll directly. at the edges of the oblong holes 49a of the central portions 39a of the masses 39. Of course, a variant could consist in providing the opposite. Figures 21 to 23 show another embodiment of the invention, in which the radially outer portions 36 of the supports 33 comprise tabs 61 made of material with the supports 33 and made by cutting and deformation of said supports.

Each tongue 61 extends radially, the two ends of the tongue being attached to the corresponding support 33.

Each tongue 61 is further deformed axially, so as to extend axially in the direction of the annular web 26. Each tongue 61 thus has a zone 62 bearing on the annular web 26, more particularly on one of the lugs 28 or on one of the stops 31 of the annular web 26.

The tongues 61 may be prestressed by bearing on the annular web 26, the prestressing force exerted by each tongue 61 then being less than 200 N.

Of course, the tongues 61 may also comprise a single end connected to the corresponding support 33, the other end bearing against the annular web 26.

The tongues 61 in particular provide a bracing function. They can be elastically deformable, so as to compensate for any deformation of the annular web 26 and prevent such deformation has an effect on the geometry or flatness of the support 33.

FIGS. 24 and 25 illustrate an embodiment variant in which rivets 65 provide the spacer function between the supports 33, more particularly between the radially outer portions 36 of said supports 33. The invention thus proposes a torque transmission device, of the double damping flywheel type, in which the torque transmission functions of the annular web 26 and support of the pendulum masses 39 have been dissociated, so as to ensure that the deformation of the annular web 26 has no influence on the displacement or the trajectory of the annular masses 39. This ensures the efficiency of the pendulum damping means. 

Claims

1. Pendulum damping device, in particular for a motor vehicle transmission, comprising at least one pendulum mass (39) movably mounted on a support member (26, 33) adapted to pivot about an axis, the support element (33) having abutments (30, 47) capable of limiting the displacement of the pendulum mass (39) between two extreme positions, the pendulum mass (39) having two circumferential ends (43, 44) and radially inner edges (46). ) and outer (45) connecting said circumferential ends (43, 44), the pendulum mass (39) comprising abutment areas on the support member (26, 33) at its circumferential ends (43, 44), said characterized in that the pendulum mass (39) comprises abutment zones at its radially inner edge (46), said inner edge (46) of the pendulum mass (39) having a first abutment zone (46a) located near a first circumferential end (43) and a second abutment area (46b) located proximate a second circumferential end (44) to abut the support member (26) in a first extreme position, at the first circumferential end (43) and the second zone (46b) of its radially inner edge (46) and, in a second extreme position, at the second circumferential end (44) and the first region (46a) of its radially inner edge (46).

2. Device according to claim 1, characterized in that the circumferential ends (43, 44), on the one hand, and the radially inner edge (46) or the radially outer edge (45), on the other hand, of the pendulum mass (39) comprise resiliently deformable means (55, 59) intended to bear against the support element (26) in one or other of the extreme positions of the pendulum mass (39).

3. Device according to claim 2, characterized in that the deformable means (55, 59) are made of elastomer.

4. Device according to claim 2 or 3, characterized in that the deformable means comprise studs (59) projecting from the pendulum mass (39), located at the circumferential ends (43, 44) of the pendulum mass (39). ), on the one hand, and the radially inner (46) or radially outer (45) edge, on the other hand.

5. Device according to claim 2 or 3, characterized in that the deformable means are in the form of a strip (55) extending from one circumferential end (43) to the other (44) of the pendulum mass (39), along the radially inner (46) or radially outer (45) edge of the pendulum mass (39).

6. Device according to one of claims 1 to 5, characterized in that the support member comprises an annular web (26) comprising an annular portion (27) from which extend at least two radial tabs (28). the pendulum mass (39) being designed to abut, in each extreme position, on a radial lug (28) at a circumferential end (43, 44) of the pendulum mass (39), on the one hand , and on the outer periphery (47) of the annular portion, at the radially inner edge (46) of the pendulum mass (39), on the other hand.

7. Device according to claim 6, characterized in that each zone (46a, 46b) of the inner edge (46) has a concave shape with a radius of curvature substantially equal to the radius of the outer periphery (47) of the annular portion ( 27) of the annular web (26).

8. Device according to claim 6 or 7, characterized in that the pendulum mass (39) comprises at least two oblong holes (48) in the form of a circular arc for mounting at least two rollers (51), said rollers (51) being engaged in arc-shaped holes (40) of at least one support (33) attached to the annular web (26).

9. Device according to one of claims 2 to 8, characterized in that the mass (39) comprises a central portion (39a), from which and are disposed at least two side portions (39b), the elastically deformable means (55, 59) having at least a portion engaged by complementary shape in the central portion (39a) of the pendulum mass (39) and retained on both sides by the side portions (39b), and at least one projecting portion, adapted to abut against the support member (26).

10. Device according to one of claims 1 to 9, characterized in that the pendulum mass (39) is designed to abut on the support member (26) first at one of its circumferential ends. (43, 44), then at its radially inner edge (46) or its radially outer edge (45), or vice versa, for each end position.

1 1. Device according to claim 10, characterized in that the circumferential ends (43, 44) of the pendulum mass (39) comprise deformable means having a constant stiffness different from that of the deformable means equipping the radially inner edge (46) or the radially outer edge (45) of the pendulum mass (39), the deformable means abutting in a first time having a lower stiffness than the deformable means abutting in a second time.