WO2013117841A1

WO2013117841A1 - Pendular shock-absorbing device

Info

Publication number: WO2013117841A1
Application number: PCT/FR2013/050173
Authority: WO
Inventors: Jonathan ROST; Clément TONDELLIER
Original assignee: Valeo Embrayages
Priority date: 2012-02-07
Filing date: 2013-01-28
Publication date: 2013-08-15
Also published as: FR2986593B1; FR2986593A1

Abstract

The invention relates to a pendular shock-absorbing device comprising pendular bodies (39), each having a central portion (39a) and two side portions (39b). Each portion (39a, 39b) includes two arcuate oblong holes (48a, 48b) in which guide rollers (51) are mounted. Each roller (51) comprises a cylindrical central area (51a), two cylindrical intermediate areas (51b), and two cylindrical end areas (51c). The intermediate areas (51b) have a diameter (D2) that is different than the diameter (D1) of the central area (51a) so as to form shoulders (52) that prevent the roller (51) from being axially removed from the oblong holes (48a, 48b) of the pendular body (39). Further, the end areas (51c) have a diameter (D3) that is smaller than the diameter (D2) of the adjacent intermediate areas (51b) so as to form a shoulder (54) which is engage with mountings (33).

Description

Pendulum damping device

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 ends of the guide rollers are mounted in arcuate elongated holes of the annular web. The edges of the holes oblongs thus form raceways for the ends of the rollers.

Document DE 10 2010 054 556 describes an annular web for a double damping flywheel equipped with pendular damping means.

The annular web consists of two annular parts attached to each other and defining between them a space housing pendular masses. Each mass comprises two elongated arc-shaped holes, the concavity of which is turned radially outwards, serving for assembly with a set of two rollers. The ends of the rollers are engaged in recesses of the aforementioned parts of the annular web, each recess having a generally arcuate oblong shape, with a concavity turned radially inwardly.

The rollers comprise radial flanges extending between the pendular masses and the portions of the annular web.

These flanges are for example formed by elastic rings mounted in grooves cylindrical rollers. In this case, assembly of the assembly is carried out in the following manner.

First the rollers are engaged in the oblong holes of the masses. The elastic rings are then mounted on either side of the masses, in the corresponding grooves of the pendular masses. First ends of the rollers are then engaged in the recesses of a first portion of the annular web, the second portion of the annular web then being mounted on the first, so that the second ends of the rollers engage in the corresponding recesses. of the second part. The two parts of the annular web are then fixed to each other, for example by welding.

Such an arrangement is relatively complex. In particular, the mounting of elastic rings in grooves of the rollers is tedious.

The patent application FR 1 153794, filed by the Applicant and not yet published, proposes a torsion damping device equipped with pendulum damping means comprising masses each formed of a central portion and at least two lateral portions, disposed on either side of the central portion, each of said portions comprising arcuate oblong holes .

Guide rollers are movably mounted in the elongated holes of the aforesaid portions, the ends of the rollers being mounted in arcuate elongated holes of two supports attached to one another and forming a phasing washer.

The rollers comprise an enlarged central cylindrical zone, of diameter smaller than the radial dimension of the oblong holes formed in the central parts of the masses, but of diameter greater than the radial dimension of the oblong holes formed in the lateral parts of the masses.

The mounting of the pendular damping means is carried out as follows.

First, the rollers are engaged in the central parts of the masses, so that the central areas of the rollers are located in the oblong holes of the central parts of the masses. The side portions are then disposed on either side of the central portions, so that the rollers extend through the oblong holes of said side portions. The central part and the corresponding lateral parts of each mass are then fixed to each other by rivets. The rollers are thus mounted captively in the masses. Indeed, after assembly, the widened central areas of the rollers abut against the lateral parts of the masses, which prevents the rollers from escaping axially.

In this case, however, the axial centering of the masses between the supports is not ensured, the masses being able to rub against the supports in operation, which reduces the efficiency of the pendular damping means. The invention aims in particular to provide a simple, effective and economical solution to this problem.

For this purpose, it proposes a pendular damping device comprising at least one pendulum mass comprising a central part and at least two lateral parts, arranged on either side of the central part, each of said parts comprising at least one oblong hole. in an arc, and at least one guide roller movably mounted in the oblong holes of said parts, the roller being intended to be mounted in oblong holes in a circular arc of two supports, at two end zones. cylindrical roller, the roller having a central cylindrical zone, housed in the oblong hole of the central portion of the pendulum mass, characterized in that the roller comprises two cylindrical intermediate zones, housed in the oblong holes of the lateral parts of the pendulum mass , extending between the central zone and each of the end zones, the intermediate zones having a diameter different from the diameter of e the central zone, so as to form shoulders preventing the axial withdrawal of the roller from the oblong holes of the pendulum mass, the end zones having a diameter smaller than the diameter of the adjacent intermediate zones, so as to form a shoulder intended to come to bear against the corresponding supports.

This axially immobilizes the roller inside the pendulum mass, which facilitates the mounting of the damping device on the supports. In addition, the different shoulders ensure the centering of the masses between the supports, which makes it possible to avoid any friction of the masses on the supports in operation. The efficiency of the pendulum damping device is therefore guaranteed.

According to one embodiment, the diameter of the central zone is greater than the diameter of the intermediate zones, the lateral parts of the mass forming axial stops for the shoulders provided between the central zone and the intermediate zones of the roll, so as to prevent the axial withdrawal of said roll from said mass.

The pendulum mass may, in this embodiment, have a large mass.

According to another embodiment, the diameter of the central zone is smaller than the diameter of the intermediate zones, the shoulders provided between the central zone and the intermediate zones of the roller being intended to come axially in abutment on the central part of the mass, in order to prevent axial removal of said roll from said mass.

This embodiment makes it possible to reduce the Hertz pressures between the roll and the mass, and between the roll and the supports.

In this embodiment also, the arc-shaped oblong hole of the central portion may have an enlarged end, allowing insertion of the roll into said oblong hole.

The enlarged end thus allows the passage of the widest areas of the roll, namely the intermediate areas.

Preferably, at least some of the roll shoulders and / or some of the abutment surfaces of said shoulders are frustoconical or extend obliquely to the radial plane.

This characteristic makes it possible to guarantee the proper centering of the mass during the rapid rotation of the roller inside the oblong holes.

The central zone of the roll is intended to bear on the edges of the oblong hole of the central part of the pendulum mass.

In this embodiment, the rolling of the rollers is only on the central part. The realization of the masses is therefore easy because the lateral parts of the pendular masses do not have to be aligned very precisely.

In a variant, the intermediate zones of the roller are intended to bear on the edges of the oblong holes of the lateral parts of the roller. pendulum mass. This has the advantage of preventing the tilting of the masses in operation.

The invention also relates, according to a second aspect of the invention, to a torque transmission device for a motor vehicle, comprising a torque input member and a torque output member rotatable with respect to the other, and resilient members mounted between the input and torque output members, the torque output member, or respectively the torque input member, having an annular web, the elastic members being mounted between the annular web and the torque entry element, or respectively between the annular web and the torque output member, characterized in that two annular supports extend radially on either side of the annular web and are fixed to said annular web, the torque transmission device further comprising a pendulum damping device according to the first aspect of the invention, the pendulum masses being arranged axially between the annular supports, the end regions of the rollers being movably mounted in arcuate oblong holes of the annular supports.

In the document FR 2 826 079 in particular, the torque transmitted by the annular web during operation can cause a deformation thereof and thus a deformation of the edges of the oblong holes forming the raceways. This can have an impact on the trajectory and, more generally, on the displacement of the pendular masses, which can affect the efficiency of the pendulum damping device.

In the torque transmission device according to the invention, the pendular masses are not mounted on the annular web, but on independent supports which do not provide the torque transmission function and which are therefore not deformed in operation.

The trajectory of the pendular masses is thus not affected by any deformation of the annular web, so that the efficiency of the pendular damping device is preserved. The invention finally relates to a method for mounting a pendular damping device of the aforementioned type, characterized in that it comprises the steps of:

- insert the roll in the central part of the pendulum mass, so that the central zone of said roll is located in the oblong hole of the central part,

- arrange the lateral parts on either side of the central part of the pendulum mass, so that the intermediate areas of the roller are located in the oblong holes of the lateral parts,

- Fix the central portion and the side portions to each other, for example by means of rivets, so that the roller is held axially in position in the oblong holes of the pendulum mass.

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 view, in perspective, 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 view, in perspective, of the annular web, the supports and the pendular damping means of the double damping flywheel of FIGS. 1 and 2,

- Figures 4 to 6 are side views and in partial radial section, the double damping flywheel of Figures 1 to 3, in three different positions of the pendular masses,

FIG. 7 is a perspective view of a pendulum mass; FIG. 8 is an exploded perspective view of the pendulum mass of FIG. 7; FIGS. 9 and 10 are views respectively corresponding to FIGS. 7 and 8, illustrating a pendulum mass according to another embodiment of the invention,

FIG. 11 is a detailed view of part of the double damping flywheel, in which the guide roller has been removed,

FIG. 12 is a view of a guide roller,

FIG. 13 is a view corresponding to FIG. 11, in which the guide roller is represented,

FIG. 14 is a view corresponding to FIG. 13, illustrating another embodiment of the invention,

FIGS. 15, 16 and 17 are views respectively corresponding to FIGS. 13, 11 and 12, illustrating yet another embodiment of the invention,

FIG. 18 is a front view of the pendulum mass of FIGS. 15 and 16,

FIG. 19 is a perspective view of the annular web, supports and pendular damping means, according to another embodiment,

FIG. 20 is a front view of the assembly of FIG. 19,

FIG. 21 is a sectional view along the line A-A of FIG. 20,

- Figures 22 and 23 are views respectively corresponding to Figures 20 and 21, an alternative embodiment of the invention.

A double damping flywheel according to a first embodiment of the invention is shown in Figures 1 and 2. It comprises a primary flywheel 1 comprising a central hub 2, called 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 part radial 4 is also fixed to the radially inner periphery 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 radially extending annular portion 10 (FIG. 2) whose radially outer periphery is extended forward by a cylindrical rim January 1. The front face of the annular portion 10 comprises two projecting elements 12 (Figure 1) diametrically opposed, 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 reference already used for the ring gear protruding 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.

Chutes 18 are mounted between the inner wall of the cylindrical rim January 1 and the elastic members 15, these chutes 18 serving to the support of 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 secondary mass of inertia 20, comprising in its center a bore 21 for mounting and centering the secondary mass of inertia 20 on the cylindrical portion 3 of the primary hub 2, by the intermediate 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 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 stop 31 has two opposite lateral bearing faces 32 forming an angle with each other and diverging one from the other. on the other side 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 27 (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, that for the purpose of enlarge the internal radial space for the implantation of 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 parts 39a, 39b of the same general arc-shaped 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 can be seen more clearly in FIGS. 7 and 8, each of the parts 39a, 39b has two circumferential ends. 43, 44 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 parts 46a, 46b each extending over one half of said edge 46, each portion 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 thus has two adjacent concave zones 46a, 46b, in contrast to the outer peripheral edge 47 which is continuous.

Each of the portions 39a, 39b further has two arcuate oblong holes 48a, 48b whose concavity faces outwards, and each disposed between two rivets 41.

As best seen in Figures 1 1 and 13, 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. 12 and 13, each roll 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 parts Lateral 39b of the masses 39. Finally, e3 designates the radial dimension of the oblong holes 40 of the supports 33.

The assembly with play 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. 11) 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, 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 the oblong holes 48a, 48b of the masses. 39. The radial dimensions of the different 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 inner peripheral edges 49b of the oblong holes 48b of the lateral portions 39b of the masses 39 (FIG. 13) or on the inner peripheral edges 49a of the oblong holes 48a of the central portions 39a of the masses 39 (Figure 14).

The embodiment of FIG. 13 has the advantage of preventing the masses 39 from tilting. In the embodiment of FIG. 14, the rolling of the rollers 51 is only performed 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. 7 to 10, 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 of support 29 of the lugs 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. 7 and 8 in particular, these damping means are formed by an elastomer 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 pads 56 dovetail on its side facing the central portion 39a, inserted and locked in openings 57 of complementary shape of the central portion 39a, opening at the circumferential ends 43, 44 and the 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 this strip 55 also has two adjacent concave zones 58a, 58b (FIG. 7), 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 radially inner edge 46 of the central portion 39a is located radially outwardly relative to the radially inner edges 46 of the side portions 39b, so that trapping the band 55 between the lateral parts 39b after assembly.

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 9 and 10, 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, once 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. 4 and 6, an intermediate position being represented in FIG.

In the extreme position shown in Figure 4, 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 Figure 6, the masses 39 are also positioned obliquely 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 elastomer strip 55 which is opposite the end circumferential 43 being in abutment against the outer periphery 47 of the annular web 26.

In operation, the masses 39 are intended to oscillate pendulously from one end position to another, through the intermediate position shown in Figure 5 in which the masses 39 are spaced apart from the annular web 26, tabs 28 and stops 31.

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

As a variant, the masses 39 can bear only at a circumferential end 43, 44 or a concave zone 58a, 58b. As a variant also, the support can be carried out, 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 furthermore achieved 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. 4 and 6, 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. 15 to 18 illustrate 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 holes oblongs 40 of the supports 33 and greater than the radial dimension e1 of the 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.

The oblong holes 49a of the central portions 39a of the masses 39 have enlarged ends 63, visible in dashed lines in FIG. 18, so as to allow the passage of the intermediate zones 51b of the rollers 51 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 towards the annular web 26. Each tongue 61 thus has a zone 62 bearing on the annular web 26, more particularly on one of the tabs 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. These tongues 61 may 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 comprising at least one pendulum mass (39) comprising a central part (39a) and at least two lateral parts (39b), arranged on either side of the central part (39a), each of said parts ( 39a, 39b) comprising at least one elongated arc-shaped hole (48a, 48b) and at least one guide roller (51) movably mounted in the oblong holes (48a, 48b) of said portions (39a, 39b) ), the roller (51) being adapted to be mounted in arcuate elongated holes (40) of two supports (33), at two cylindrical end regions (51c) of the roller (51), the roller (51) having a central cylindrical zone (51a), housed in the oblong hole (48a) of the central portion (39a) of the pendulum mass (39), characterized in that the roller (51) has two zones cylindrical intermediates (51b), housed in the oblong holes (48b) of the lateral parts (39b) of the pendulum mass (39), extending between the central zone (51 a) and each of the end zones (51 c), the intermediate zones (51 b) having a diameter (D2) different from the diameter (D1) of the central zone (51 a), so forming shoulders (52) preventing the axial withdrawal of the roller (51) from the oblong holes (48a, 48b) of the pendulum mass (39), the end zones (51c) having a diameter (D3) less than diameter (D2) of the intermediate zones (51b) adjacent, so as to form a shoulder (54) intended to bear against the corresponding supports (33).

2. Pendulum damping device according to claim 1, characterized in that the diameter (D1) of the central zone (51 a) is greater than the diameter (D2) of the intermediate zones (51 b), the lateral parts (39b). mass (39) forming axial stops for the shoulders (52) formed between the central zone (51a) and the intermediate zones (51b) of the roller (51), so as to prevent the axial withdrawal of said roller (51); ) out of said mass (39).

3. A pendulum damping device according to claim 1, characterized in that the diameter (D1) of the central zone (51 a) is smaller than the diameter (D2) of the intermediate zones (51 b), the shoulders (52) arranged between the central zone (51 a) and the intermediate zones (51 b) of the roller (51) being intended to come axially in abutment with the central part (39a) of the mass (39), so as to prevent the axial withdrawal of said roll (51) out of said mass (39).

Pendulum damping device according to claim 3, characterized in that the elongated arc-shaped hole (48a) of the central portion (39a) has an enlarged end (63) for insertion of the roller (51). ) in said oblong hole (48a).

Pendulum damping device according to one of claims 1 to 4, characterized in that at least some of the shoulders (52, 54) of the roller and / or some of the abutment surfaces (53) of said shoulders (52, 54 ) are frustoconical or extend obliquely to the radial plane.

6. pendular damping device according to one of claims 1 to 5, characterized in that the central region (51 a) of the roller (51) is intended to bear on the edges of the oblong hole (48a) of the central portion (39a) of the pendulum mass (39).

7. Pendulum damping device according to one of claims 1 to 5, characterized in that the intermediate zones (51 b) of the roller (51) are intended to bear against the edges of the oblong holes (48b) of the parts laterals (39b) of the pendulum mass (39).

A torque transmission device for a motor vehicle having a torque input member (1) and a torque output member (19) rotatable relative to each other and resilient members ( 15) mounted between the torque input and output members (1, 19), the torque output member (19), or the torque input member (1), respectively, having an annular web ( 26), the resilient members (15) being mounted between the annular web (26) and the element torque inlet (1), or respectively between the annular web (26) and the torque output member (19), characterized in that two annular supports (33) extend radially on either side of the annular web (26) and are fixed to said annular web (26), the torque transmission device further comprising a pendulum damping device according to one of claims 1 to 7, the pendulum masses (39) being arranged axially between the annular supports (33), the end regions (51c) of the rollers (51) being movably mounted in arcuate elongated holes (40) of the annular supports (33).

9. A method of mounting a pendulum damping device according to one of claims 1 to 7, characterized in that it comprises the steps of:

- insert the roller (51) in the central part (39a) of the pendulum mass (39), so that the central zone (51a) of said roller (51) is located in the oblong hole (48a) of the central portion (39a),

arranging the lateral parts (39b) on either side of the central portion (39a) of the pendulum mass (39), so that the intermediate zones (51b) of the roll (51) are located in the oblong holes (48b) of the lateral parts (39b),

- fixing the central portion (39a) and the side portions (39b) to each other, for example by means of rivets (41), so that the roller (51) is held axially in position in the holes oblong (48a, 48b) of the pendulum mass (39).