WO2018224313A1 - Pendular damping device - Google Patents

Abstract

Pendular damping device, comprising: - a support (2) able to rotate about an axis (X), - at least one pendular body (3) comprising: a first and a second pendulum mass (5) spaced axially in relation to one another and movable relative to the support (2), and - at least one rolling member guiding the movement of the pendular body (3) relative to the support (2), characterised in that the device also comprises an axial clamping means (35) arranged axially between the first and second pendular masses (5), partially housed in an opening (36) formed in the support and able to rub against the first and second pendular masses (5) for certain relative movements of the pendular body and the support.

Description

 PENDULAR DAMPING DEVICE

 The present invention relates to a pendular damping device, in particular for a motor vehicle transmission system.

 In such an application, the pendulum damping device can be integrated with a torsion damping system of a clutch capable of selectively connecting the heat engine to the gearbox, in order to filter the vibrations due to the acyclisms of the engine. Such a torsion damping system is for example known as the double damping flywheel.

 Alternatively, in such an application, the pendulum damping device may be integrated with a friction disc of the clutch or with a hydrodynamic torque converter.

Such a pendular damping device conventionally implements a support and one or more pendular bodies movable relative to this support, the displacement relative to the support of each pendulum body being guided by two rolling members cooperating on the one hand with bearing tracks secured to the support, and secondly with rolling tracks secured to the pendular bodies. Each pendulum body comprises for example two pendular masses riveted together.

 At low rotational speeds of the support, the pendular bodies are no longer centrifuged and are sensitive to the force of gravity. This causes undesirable displacements of the pendular bodies which shock the support or the rolling members.

 It is known to choose the damping device, for example via the shape of the rolling tracks, so that the latter filters the excitation order of a two-cylinder combustion engine of the vehicle, also called "order 1 ", the order of excitation of a thermal engine being in known manner the number of explosions of this engine per revolution of crankshaft. Such devices are very sensitive to the force of gravity and the noise related to the undesirable displacements of the pendulum bodies are then amplified.

 To remedy this problem, it is for example known from the application DE 10 2012 221 103 to provide springs between two circumferentially adjacent pendulum bodies, so that the pendular bodies thus connected resist the force of gravity exerted alternately on the latter when the device is driven by a rotational movement. The insertion of these springs supposes to provide additional housings in the pendular bodies or to provide appropriate fastening means on these pendular bodies, which is expensive and complex. Due to the insertion of the springs, an additional resonant frequency appears elsewhere.

The object of the invention is to reduce the influence of gravity on the pendular bodies, in particular the radial drop at the engine stop, especially when the latter are intended to filter the order of excitation of a two cylinder engine of the vehicle, while remedying all or some of the above disadvantages.

 The invention aims to meet this need, and it achieves in one of its aspects, using a pendulum damping device, comprising:

a support able to move in rotation about an axis,

 at least one pendular body, movable relative to the support, comprising: a first and a second pendular mass axially spaced relative to one another and movable relative to the support, the first pendular mass being arranged axially with a first side of the support and the second pendulum mass being arranged axially on a second side of the support, and at least one connecting member of the first and second pendulum masses matching said masses, and

 - At least one rolling member guiding the displacement of the pendular body relative to the support, the rolling member cooperating on the one hand with at least one running track secured to the support and on the other hand with at least one raceway integral with the pendulum body,

characterized in that the device also comprises an axial clamping means arranged axially between the first and second pendulum masses, partially housed in an opening in the support and able to rub on the first and second pendulum mass for certain relative displacements of the pendulum body and support.

 According to the invention, the axial clamping means exerts a frictional force on the pendular masses and therefore on the pendular body which opposes the displacement of this pendular body relative to the support, which makes it possible to limit the noises associated with the undesirable shocks between the support and the pendular body or between the running member and the pendulum body or between the running member and the support, which may occur at the end of said relative displacements.

 These relative displacements may occur in particular at the engine stop, especially in the starting phase of the engine, particularly in case of significant angular acceleration of the support.

 For the purposes of this application:

 - "axially" means "parallel to the axis of rotation of the support" or "parallel to the longitudinal axis of the running gear", as the case may be,

 - "radially" means "along an axis belonging to a plane orthogonal to the axis of rotation of the support and intersecting this axis of rotation of the support",

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

- "orthoradially" means "perpendicular to a radial direction", - "solidaire" means "rigidly coupled", and

 the rest position of the device is that in which the pendulum body is subjected to a centrifugal force, but not to torsional oscillations originating from the acyclisms of the heat engine. In this position of the device, the pendulum body is also said in the rest position.

 According to one aspect of the invention, the axial clamping means can be compressed between the pendulum masses. The axial clamping means may exert on the pendulum body an axial clamping is less than 4N, preferably less than 2N, preferably less than 0.5N, distributed equally on each of the two pendulum masses. The overall clamping force, expressed in Newtons, can be between 20% and 1 10% of the weight of the pendulum body, expressed in Newtons. Preferably, this clamping force is between 50% and 90% of the weight of the pendulum body, in particular between 60% and 80%> of this weight. This clamping force depends both on the intrinsic characteristics of the axial clamping means and the coefficient of friction between said means and the masses, this coefficient being notably related to the presence of grease or oil.

 According to a first function of the axial clamping means, the opening may be configured to limit the displacement of the axial clamping means relative to the support beyond a first deflection of the pendular body relative to the support. The axial clamping means then has a role of end-of-stroke damping.

 In the sense of the demand, the pendulum body debates in reaction to oscillations of torsion that the support undergoes. The deflection in the clockwise or counterclockwise direction of the pendulum body makes it possible to generate a torque that opposes these torsional oscillations to at least partially attenuate them. The path of travel depends in particular on the shape of the raceways and the running gear.

 Beyond the first deflection, for example in the clockwise direction, for example counterclockwise, the axial clamping means is locked relative to the support and rubs on the pendular masses to brake and possibly stop the displacement of the pendular body. . Thus, the noise of end of travel shocks is attenuated due to the energy absorbed by friction.

Below the first deflection, that is to say between the first deflection and the rest position, the opening may be configured so that the axial clamping means follows the movement of the pendular body guided by the rolling members on running tracks.

The opening may have a radially outer edge. This radially outer edge makes it possible to prevent the axial clamping means from escaping radially. Below the first deflection and in normal filtration operation, the axial clamping means may come into contact with this radially outer edge under the effect of the centrifugal force. In this same normal operation, the axial clamping means can stay away from this edge radially. outside. This is related to the predominance of the clamping force relative to the centrifugal force so that the axial clamping means does not shift radially.

 Below this first deflection, the axial clamping means does not rub on the pendular masses.

 According to another aspect of the invention, there may be an intermediate deflection, between the first deflection and the rest position, from which the opening no longer follows the trajectory of the pendulum body. The radially outer edge then exerts a force on the axial clamping means which opposes its displacement and thus generates hysteresis.

 The shape of the radially outer edge can be defined so that the friction gradually increases until the first deflection.

 Alternatively, the opening may be configured to limit the displacement of the axial clamping means for any movement of the pendular body relative to the support. The axial clamping means thus rubs on the pendulum masses for any deflection of the pendular body relative to the support.

 The axial clamping means may be disposed in the opening with a mounting clearance so that said means is not completely fixed relative to the support. This mounting clearance makes it possible not to hinder the compression of the axial clamping means between the pendular masses. The circumferential dimension of the opening may be just greater than the circumferential dimension of the axial clamping means. This game can be between 1% and 10% of the dimension

circumferential axial clamping means in the opening.

 According to a second function of the axial clamping means, the opening may be configured to limit the displacement of the axial clamping means when the pendulum body is no longer centrifuged so that the axial clamping means rubs on the pendulum masses to brake the radial fall of the pendulum body. The axial clamping means then has a role of generating anti-gravity hysteresis.

 When the pendulum body is no longer centrifuged, especially at the engine stop, the rolling member loses contact with the running track secured to the support.

 The opening may have a radially inner edge. In their fall, the pendulum masses drive the axial clamping means which comes into contact with this radially inner edge. Friction occurs when the axial clamping means is in contact with this radially inner edge.

According to one aspect of the invention, the axial clamping means can allow stopping the radial drop of the pendulum body. The axial clamping means may exert an axial force at least equal to the force of gravity divided by the coefficient of friction between the axial clamping means and the pendular masses. The coefficient of friction may be 0.05 in the fat, 0.08 in the oil and between 0.2 and 05 in a dry environment.

 This eliminates shocks between the pendulum body and the support and the associated noise. The noise related to the shocks between the rolling members and the pendulum body is also attenuated. The fall distance of the rolling members is reduced because of the arrest of the fall of the pendulum body or at least of its slowing down.

 The radial dimension of the opening may be just greater than the dimension of the axial clamping means. This radial clearance can be between 1% and 10% of the radial dimension of the axial clamping means in the opening. The width of the opening may be between 0.6 and 2 times the axial thickness of the support.

 This game makes it possible at the same time not to hinder the movement of the axial clamping means when the pendulum body debates and to limit the radial drop as soon as the bearing member has lost contact with the running track secured to the support.

 According to the invention, the axial clamping means can present only the function

end of stroke damping in which case the opening does not limit the displacement of the axial clamping means radially.

 Alternatively, the axial clamping means can only have an anti-gravity hysteresis generating role. The opening is then dimensioned so as not to limit the displacement of the axial clamping means for any deflection of the pendulum body.

 In another variant, the axial clamping means may have both a function

end-of-stroke damping and an anti-gravity hysteresis generating role.

 According to one aspect of the invention, the axial clamping means can cooperate with axial inner faces of substantially flat pendulum masses. These faces are opposite the support.

 The fact that the faces are flat advantageously allows to have only the radial clearance between the axial clamping means and the opening to control, the axial clamping means can be positioned in any way on the flat faces. This allows for good accuracy and good control of radial play.

 The friction occurring as soon as the axial clamping means comes into contact with the radially inner edge of the opening, it is particularly advantageous that the radial clearance is minimized.

According to another aspect of the invention, the first and second pendulum masses may be configured to block the displacement of the axial clamping means relative to the pendulum body when the pendulum body is no longer centrifuged. The axial clamping means prevents the fall of the pendulum body. The axial clamping means thus makes it possible to leave the bearing in contact with the rolling tracks so that the shocks between the pendulum body and the support, between the running member and the pendulum body or between the rolling member and the support are non-existent or greatly reduced, in particular to the engine stop.

 Unlike the limitation of the displacement of the pendulum body by friction, the friction does not intervene in the blocking.

 According to this aspect of the invention, the first and second pendulum masses define grooves receiving the axial clamping means and an edge of the grooves radially blocks the displacement of the axial clamping means relative to the pendulum masses.

 The axial inner faces with which the axial clamping means cooperate are therefore not flat.

 The axial clamping means then extends between the bottoms of each of the grooves.

 According to this aspect, the grooves of the pendular masses can allow the total displacement of the pendulum body. Throughout the range of deflection of the pendular body, the axial clamping means does not reach a circumferential end of the grooves.

 Preferably, when the axial clamping means rubs groove bottoms of the inner axial faces, the clamping force is less than 4N, preferably less than 2N, preferably less than 0.5N.

 Regardless of the shape of the opening and / or the pendular masses, the axial clamping means may comprise an elastic return member, in particular a straight spring or an elastomer block. The clamping force is correlated with the characteristics of the elastic return member.

The axial clamping means may also comprise two cups intended to rub on the first and second pendulum masses under the action of the elastic return member. The cups can be plastic, composite, or metal. The cups can be made of mild steel, especially DD13, CIO with nitriding or carbonitriding.

 The cups may extend radially out of the opening to interpose axially between the pendular masses and the support to limit axial shocks.

 In a variant, the axial clamping means comprises only a spring whose axial ends rub against the axial inner faces.

 According to one embodiment of the invention, the elastic return member is a spring and each cup comprises a friction portion and a holding portion, each holding portion being either internal to the spring, or external to the spring, or having an inner portion and an outer portion of the spring.

The holding portion allows the cup not to escape, especially radially in all configurations of the device. The cups may have a U-shaped profile. The cups may have a "W" shaped profile. The cups may have a "T" shaped profile. The cups may be identical or have complementary shapes.

 The friction portion and the holding portion may be in one piece.

 The friction portion may define a substantially flat friction surface, for example circular.

 When the pendulum masses have grooves, the friction portions cooperate with the bottom of these grooves.

 The holding portions may be shaped to maintain the prestressed spring before assembly of the device. As a variant, the spring is prestressed by the pendular masses.

According to another embodiment, the return member is an elastomer block and the cups comprise only a friction portion attached to the elastomer block, for example overmolded. In the present case, at least one of the cups is smaller than the opening to allow insertion of the axial clamping means into the opening.

 According to another aspect of the invention, the axial clamping means may be able to contact the edge of the opening of the support either:

 - via the cups, and / or

 - via a cylindrical ring distinct from the cups.

 This advantageously makes it possible not to damage the spring or the elastomer block. This also makes it possible to avoid the noise of shocks between the elastic return means and the edge of the opening.

 The cylindrical ring is especially provided when the guide portion is disposed within the spring or nonexistent, for example when using an elastomer block.

 Alternatively, the axial clamping means can contact the edge of the opening via the elastic return element which allows a flexible contact by deformation of said member in the circumferential or radial direction.

 We will now mention characteristics that can indifferently apply to one of the implementation examples mentioned above.

 In all of the above, the device may comprise two bearing members associated with the pendulum body. The device is then called "two-wire".

According to a first configuration of the device, each running member is associated with a connecting member which defines the running track of the pendulum body. The connecting member, also called spacer, is then a bearing spacer. Each rolling member and the associated connecting member are arranged in a single window formed in the support. The bearing track secured to the support is defined by an edge of this window.

 The rolling member may cooperate with the running track secured to the support and with the running track secured to the pendulum body only via its outer surface. Thus, the same portion of this outer surface may roll alternately on the running track secured to the support and on a running track integral with the pendulum body when the running member moves. The rolling member can then be solicited solely in compression between the raceways.

 The rolling member may comprise pins cooperating with guide slots formed in the pendulum masses. These guide slots prevent the falling of the rolling member when the pendulum body is not centrifuged. The shape of these guide slots may be chosen so as not to interfere with the trajectory of the running member as it rolls. The rolling member is for example a roll of circular section in a plane perpendicular to the axis of rotation of the support. The axial ends of the roll may be devoid of a thin annular flange. The roller is for example made of steel. The roll may be hollow or full.

 In this configuration, the connecting member is for example force-fitted via each of its axial ends into openings in the pendulum masses. Alternatively, the connecting member may be welded, riveted or screwed via its axial ends on each pendulum mass.

 In this first configuration, the two connecting members may be associated with the same connecting member or "rolling spacer". The two rolling members are then received in the same window whose edge defines two raceways.

 According to a second configuration of the device, each rolling member cooperates with two running tracks integral with the pendulum body, each running track being defined by the edge of a cavity formed in one of the pendulum masses. These cavities are distinct from any grooves receiving the axial clamping means. For each rolling member, the integral bearing raceway is, in turn, defined by the edge of a cavity of the support separate from the window in which the connecting members extend. The running gear and the connecting members are at a distance from one another.

 According to this second configuration, each rolling member can then comprise successively axially:

a portion cooperating with the tread defined by the edge of the cavity of the first pendulum mass, a portion cooperating with the tread defined by the edge of the cavity of the support, and

a portion cooperating with the raceway defined by the edge of the cavity of the second pendulum mass,

 The portions of each rolling member may be cylindrical successive and different radii.

 In this second configuration, the connecting members are for example rivets, for example three, and each extends into a window dedicated to it. The windows can be distinct from the cavities of the support.

 The opening associated with the axial clamping means may be dedicated to this axial clamping means, that is to say that it does not receive any other element in particular, no connecting member of the pendular masses, in particular no rolling member. The opening may be distinct from the window receiving the connecting member, the opening may be distinct from the cavity receiving the running member.

 The shape of the first and second rolling tracks may be such that the pendulum body is only displaced relative to the support in translation about a fictitious axis parallel to the axis of rotation of the support.

 Alternatively, the shape of the rolling tracks may be such that each pendulum body is displaced relative to the support at a time:

 in translation about a fictitious axis parallel to the axis of rotation of the support and,

- Also in rotation around the center of gravity of said pendulum body, such a movement being again called "combined movement" and disclosed for example in the application DE 10 2011 086 532.

 In all that above, the device comprises for example a number between two and eight, including three or five pendulous bodies. An axial clamping means may be associated with each of these bodies. The case where two axial clamping members by pendular body is also possible.

 All these pendular bodies may succeed one another circumferentially. The device may thus comprise a plurality of planes perpendicular to the axis of rotation in each of which all the pendular bodies are arranged.

 In all of the above, the support can be unique. The support can be made in one piece, being for example entirely metallic.

In all the foregoing, the device may comprise at least one interposition piece, at least a part of which is axially arranged between the support and a pendular mass of the pendular body or between the support and the rolling member. This piece is in particular distinct from the axial clamping means. The interposition piece is for example fixed on a pendular mass or the support or formed by a coating deposited on a pendular mass or on the support. Such an interposition piece can thus block the axial displacement of the pendular body relative to the support, thereby avoiding axial shocks between said parts, and thus wear and unwanted noises, especially when the support and / or the pendulum mass are made of metal. Several interposition pieces, for example in the form of pads, may be provided. The interposition pieces are in particular made of a damping material, such as plastic or rubber.

The interposition pieces are for example carried by the pendular bodies, being in particular fixed on the pendular masses. The interposition pieces can be positioned on a pendular body so that there is always at least one interposition piece at least a portion of which is axially interposed between a pendulum mass and the support, whatever the positions relative to the support and said mass when moving relative to the support of the pendulum body.

 In all of the above, each pendular body may comprise at least one abutment damping member against the support. This abutment damping member may be complementary to the action of the axial clamping means. Each of these abutment damping members can then come into contact with the support to damp the abutment of the pendulum body against the latter, for example:

 - at the end of a displacement in the clockwise direction of this pendulum body from the rest position, and / or

 - at the end of a movement in the counterclockwise direction of the pendulum body from the rest position, and / or

 - in case of radial fall of the pendulum body.

 Where appropriate, each abutment damping member can damp the stop of the pendulum body against the support at the end of a displacement in the clockwise direction from the rest position, at the end of a displacement in the direction counterclockwise from the rest position but also in case of radial fall of the pendulum body. The same abutment damping member can thus be associated with a pendulum body for damping all the abovementioned contacts between the pendulum body and the support.

 Each abutment damping member may be associated with a connecting member of the pendular body and carried by the latter. Each abutment damping member may then have a cylindrical shape with an axis parallel to the axis of rotation of the support. Each connecting member may be associated with a single abutment damping member.

Each abutment damping member may have elastic properties for damping shocks related to the contact between the support and the pendulum body. This damping is then allowed by a compression of the abutment damping member. The abutment damping member is for example elastomer or rubber.

 The invention also relates to a component for a transmission system of a motor vehicle, the component being in particular a double damping flywheel, a hydrodynamic torque converter, a friction clutch disc, a flywheel secured to the crankshaft, a double dry or wet clutch, a simple wet clutch and a hybrid module comprising an electric machine, which comprises a pendulum damping device as presented above.

 The support of the pendular damping device can then be one of:

a veil of the component,

 a guiding washer of the component,

 a phasing washer of the component, or

 a support separate from said web, said guide washer and said phasing washer.

The invention further relates, in another of its aspects, to a vehicle powertrain comprising:

 a propulsion engine of the vehicle, in particular with two, three or four cylinders, and

a component for tel transmission system as defined above.

figures

 The invention will be better understood on reading the following description of a nonlimiting example of implementation thereof and on examining the appended drawing in which:

FIG. 1 represents, from the front and in section, a first example of a pendulum damping device according to the invention, the device being in a first configuration,

 FIG. 2 schematically shows different forms of the opening of FIG. 1 each in a rest position of the device;

FIGS. 3 to 9 represent different examples of the axial clamping means that can equip the device of FIG.

 FIG. 10 represents a second example of a device according to the invention,

 - Figure 1 1 shows a third example of the device according to the invention, the device being in a second configuration.

Figure the

FIGS. 1a and 1b show the same pendular damping device 1 in the rest position. The device 1 is particularly suitable for equipping a motor vehicle transmission system, for example being integrated with an unrepresented component of such a system. This component is, for example, a double damping flywheel, a hydrodynamic torque converter, a friction clutch disc, a flywheel secured to the crankshaft, a double wet or dry clutch, a simple wet clutch and a hybrid module including an electric machine.

 The device 1 comprises in the example considered:

 a support 2 able to move in rotation about an axis X,

a plurality of pendular bodies 3, movable relative to the support 2.

 According to the examples of implementation of the invention which will be described later, the support 2 is unique and made in one piece.

 According to the example considered, it is observed that the device 1 comprises five pendulous bodies 3. The pendular bodies 3 follow one another circumferentially around the periphery of the X axis.

 The support 2 of the damping device 1 can be one of:

 a veil of the component,

 a guiding washer of the component,

 a phasing washer of the component, or

 a support separate from said web, said guide washer and said phasing washer, for example a flange of the component.

 In the example considered, the support 2 generally has a ring shape having two opposite sides 4 which are here planar faces.

 As can be seen in particular in Figures la and lb, each pendulum body 3 comprises:

a first and a second pendular masses 5 spaced axially with respect to each other and movable relative to the support 2, the first pendulum mass being disposed axially of a first side 4 of the support and the second pendulum mass 5 being arranged axially on a second side of the support 2, and

 two connecting members 6 solidarizing the two pendulum masses 5.

 In FIG. 1a, one of the pendulum masses 5 is shown in transparency to show the rolling tracks 12, 13 and the rolling members 11.

 The device also comprises rolling members 11 guiding the displacement of the pendulum bodies 3 with respect to the support 2. In the example in question, two bearing members are associated with each pendulum body 3. Each rolling member 11 cooperates on the one hand with a running track 12 secured to the support 2 and on the other hand with a running track 13 integral with the pendulum body 3. Each rolling member 11 thus has a longitudinal axis

Y parallel to the axis of rotation X of the support 2.

 In the example considered in FIGS. 1 to 10, the device 1 is in a first

configuration, in which the connecting members 6 define the rolling tracks 13. The connecting members 6, also called spacers, are then "rolling spacers" angularly offset.

 In the example, the pendulum masses 5, the connecting members 6 and the rolling members 11 are for example steel.

 Each rolling member 11 and the associated connecting member 6 are arranged in the same window 19 formed in the support 2. The rolling track 12 is defined by an edge 23 of this window 19, more precisely by a radially outer portion of this edge. Each rolling member 11 cooperates with the rolling track 12 and with the rolling track 13 only via the outer surface of a rolling portion 29. Each rolling member 11 is stressed only in compression between the rolling tracks 12, 13 .

 In the example shown in Figure 1, each connecting member 6 is secured to the pendulum masses 5 being force-fitted via each of its ends in openings 17 formed in the pendulum masses 5. In the example that we 10, each connecting member 6 is screwed onto each of the pendulum masses 5. In variants not shown, the connecting members 6 are secured by welding or riveting pendulum masses 5.

 In the example shown in Figure la, the device 1 further comprises damping abutment members 20 against the support 2 which are in particular visible on the pendulum body 3 at the top of Figure la.

 In the example considered, a single abutment damping member 20 is associated with each connecting member 6. This single abutment damping member 20 covers the radially inner edge of the connecting member 6. This member of abutment damping 20 extends between two circumferential ends 22. Each end 22 is elongate in shape along an axis parallel to the Y axis and is here received in a clearance 21 formed in a lateral edge of the connecting member 6. Each of these ends 22 is force-fitted in the opening of the pendulum mass 5 also receiving the connecting member 6 so as to secure the abutment damping member 20 to the pendulum body 3.

 Each abutment damping member 20 may, in the example considered, be made of elastomer or rubber.

 In the example considered, each stop damping member 20 dampens the shocks between the pendulum body 3 and the support 2:

 - at the end of a displacement in the clockwise direction of this pendulum body 3 from the rest position, in which are the pendular bodies 3 in the figure la, and

- at the end of a displacement in the counterclockwise direction of the pendulum body 3 from the rest position, and - In case of radial drop of the pendulum body 3, for example when stopping the engine of the vehicle.

 In a variant not shown, several separate damping members may be associated with the same connecting member. The abutment damping members are then positioned so as to damp the shocks associated with the abutment of the pendulum body against the support at the end of a movement in the clockwise direction from the rest position. The other abutment damping member is positioned so as to damp the shocks associated with the abutment of the pendulum body against the support at the end of a movement in the counterclockwise direction from the rest position.

 At the end of these movements, the single or abutment damping members 20 come into contact with the edge of the window 19, more precisely the radially inner portion of this edge.

 In the example considered, the device 1 also comprises interposition pieces 25. On each pendulum mass 5 is fixed a single interposing part 25 opposite the support 2. Each interposition piece 25 is positioned and configured so to always be interposed axially between the support and the pendulum 5 and the support and the rolling members 11 regardless of the relative positions of the support and the pendulum body 3.

 In the example considered, each interposition piece 25 extends between two circumferential ends interconnected by a central portion. Each interposition piece 25 comprises four snap-fastening zones. The fastening zones cooperate with fastening apertures 26, opening, formed in the pendulum mass 5.

 In the example considered, the interposition pieces 25 are in particular made of a damping material, such as plastic.

In the example considered, each rolling member 11 comprises a cylindrical bearing portion 29 defining the outer rolling surface and also two pins 30 cooperating with guide slots 31 formed in the pendulum masses 5. The nipples are cylindrical of smaller diameter to the diameter of the rolling portion and arranged axially on either side. The guide slots 31 are here through. Guide slots in the interposition piece are superimposed on the guide slots 31 of the pendular masses. In the example considered, the device 1 finally comprises an axial clamping means 35 arranged axially between the first and second pendulum masses 5, partially housed in an opening 36 formed in the support 2 and able to rub on the first and second pendulum mass. for some relative displacements of the pendulum body and the support. We will see in the examples described with reference to Figures 3 to 9, the opening 36 is here dedicated to the axial clamping means 35, that is to say, it receives no other element.

The opening 36 is distinct from the windows 19.

Figure lb

 In the example under consideration, with reference to FIG. 1b, the axial clamping means 35 comprises an elastic return member 40, more specifically a straight spring, and two cups 41 intended to rub on the first and second pendulum masses 5 under the yoke. action of the elastic return member 41.

 The cups 41 may be plastic, composite, or metal.

 In the example considered, the opening is also configured to limit the displacement of the axial clamping means when the pendulum body 3 is no longer centrifuged so that the cups 41 rub on the pendulum masses 5 to brake the radial fall of the body pendulum. The axial clamping means 35 then has a role of generating antigravity hysteresis. The opening 36 has a radially inner edge 39. In their fall, the pendulum masses 5 drive the axial clamping means 35 which comes into contact with this radially inner edge. The friction occurs when the axial clamping means 35 is in contact with this radially inner edge 39.

 In the example considered, the radial dimension of the opening 36 is just greater than the dimension of the axial clamping means. This radial clearance is in particular between 1% and 10% of the radial dimension of the axial clamping means in the opening.

 In the example considered, the cups 41 cooperate with axial inner faces of substantially flat pendulum masses. These faces are facing faces 4 of the support. Apart from the possible areas of contact with the cups 41, it does not matter that the pendulum masses are flat, these masses may in particular include holes for fixing with the connecting members, the rolling members, the interposition pieces etc. ..

 In the example considered, the cups 41 extend radially out of the opening 36 to interpose axially between the pendulum masses 5 and the support 2 in order to limit the axial shocks. They then act in addition to the interposition pieces 35.

 In the example considered, the interposition pieces 25 are configured so as not to interfere with the cups 41.

Figure 2

In the example considered in FIG. 1 and corresponding to the first schematic representation of FIG. 2, the opening 36 is configured so that the axial clamping means 35 follow the movement of the pendulum body 3 guided by the rolling members 11. on the rolling tracks 12, 13. The opening 36 has a radially outer edge 38 which makes it possible to prevent the axial clamping means 35 from escaping radially.

 Beyond a first travel in the clockwise direction and counterclockwise, the opening 35 is configured to limit the displacement of the axial clamping means 35 relative to the support 2. Beyond this first travel, the means axial clamping 35 comes into contact with the circumferential ends of the opening 36, which blocks it with respect to the support 2. The axial clamping means 35 then rubs on the pendulum masses 5 to brake then,

possibly stop the displacement of the pendulum body 3.

 In the example considered in the second schematic representation of FIG. 2, a variant of the shape of the opening 36 is presented in solid lines and compared to the shape of the opening of the first schematic representation illustrated in dashed lines. According to this representation, the opening 36 no longer follows the trajectory of the pendulum body 3 from an intermediate travel between the first deflection and the rest position. From this intermediate deflection, the axial clamping means 35 is in contact with the radially outer edge 38 which exerts a force on the axial clamping means which opposes its displacement.

In the example considered in the third schematic representation of FIG. 2, the shape of the opening 36 moves away from the trajectory of the pendulum body 3 and then again coincides with this trajectory, which makes it possible to create a variable friction depending on the shape of the opening. In this representation, the clamping means is shown in several configurations.

 Finally, in the example considered in the fourth schematic representation of FIG. 2, the opening 36 is asymmetrical with respect to a position of occupying the axial clamping member 35 in the rest position. The axial clamping means can therefore rub on the pendulum masses from different deflections in the clockwise direction and in the counterclockwise direction.

 In the examples considered in FIGS. 1 and 2, the axial clamping means 35 has both an end-of-stroke damping function and an anti-gravity hysteresis generating role.

Figure 3 to 9

 Figures 3 to 9 show alternatives to axial clamping means described in Figure lb. In each of the alternatives of FIGS. 3 to 8, the axial clamping means 35 comprises a spring 40 and each cup 41, formed in one piece, comprises a friction portion 45 and a holding portion 46. alternatively, the friction portion defines a circular flat surface which rubs on a flat surface of the pendulum masses 5.

In FIG. 3, the holding portion 46 is external to the spring so that each cup 41 has a "U" shaped profile in the plane of the figure. FIG. 4 differs from FIG. 3 in that the holding portion comprises, in addition to its outer part, an inner part which gives the cup 41 a profile in the form of "W" in the plane of the figure. Each of these two alternatives have identical cups.

 In FIG. 5, the axial clamping means 35 comprises two distinct cups 41 of complementary shape, one comprising only a portion of support external to the spring which extends substantially throughout the opening 36 and the other comprising only one inner holding portion. The axial clamping means 35 of Figure 6 differs from that of Figure 5 only in that the two cups 41 cooperate with one another so as to maintain the spring 40 compressed. The holding portions 46 have complementary lugs 48 which limit the maximum elongation of the spring. In all other alternatives, the spring is kept compressed by the pendular masses whose axial spacing is defined by the connecting members.

 In the alternative shown in FIG. 7, the cups 41 are different but each comprise a holding portion 46 external to the spring. These portions 46 overlap radially so that one of them is sandwiched between the other portion and the spring 40.

 In each of these alternatives, the axial clamping means 35 comes into contact with the edge of the opening 36 via the cups, more precisely via the outer part or parts of the spring of the holding portions so as not to damage the spring.

 In the alternative shown in FIG. 8, the identical cups 41 comprise internal retaining portions 46 so that each cup 41 has a "T" -shaped profile in the plane of the figure. In this alternative, the axial clamping means then comprises a cylindrical ring 49 distinct from the cups 41 arranged around the spring 40 in the opening 36 through which the axial clamping means comes into contact with the edge of the opening 36.

 Finally, the alternative described in FIG. 9 presents an axial clamping means 35 comprising an elastomer block 51 instead of the spring on which are fixed, for example overmolded, the two cups 41 and the cylindrical ring 49. cups 41 is smaller than the opening 36 to allow insertion of the axial clamping means 35 while the other cup is larger than the opening 36 to prevent the axial clamping means out.

Figure 10

 FIG. 10 shows a second example of device 1 according to the invention, in which the management of the radial drop of the pendular bodies 3 is carried out differently.

In this example, the pendulum masses 5 are configured to block the displacement of the axial clamping means 35 relative to the pendulum body 3 when the latter is no longer centrifuged, here two in number per pendulum body. In particular, in this example of the invention, the pendulum masses 5 define grooves 60 receiving the axial clamping means 35. The edge of the groove 60 comes into contact with the axial clamping means 35 when the pendular body is no longer centrifuged and blocks its movement. The radial fall is not limited by friction but by blocking.

 Each axial clamping means 35 extends between a bottom of each groove 60. Each axial clamping means 35 thus cooperates with both the bottom of the groove 60 and the edge of the groove so that the axial clamping means does not cooperate with a substantially flat face of the pendular masses unlike the first example described.

 In the example considered, the groove 60 allows the total displacement of the pendulum body 3. Throughout the range of displacement of the pendular body 3, the axial clamping means 35 do not reach the circumferential ends of the groove 60.

 In the example considered, each axial clamping means is housed in a dedicated opening 36 and configured to limit the displacement of the axial clamping means 35 for any displacement of the pendular body 3 relative to the support 2. Each axial clamping means 35 rubs and on the pendulum masses 3 for any deflection of the pendulum body 3 relative to the support 2. There is a mounting clearance to not hinder the compression of the axial clamping means 35. These openings are particularly visible in Figure 10b which shows the device without revealing the pendular masses.

 In the example considered, each axial clamping means 35 comprises a straight spring 40 and two cups 41. The cups 41 cooperate with the grooves 60 and the spring 40 comes into contact with the edge of the opening 36. The cups 41 are not not here interposed between the pendulum masses 5 and the support 2.

 In the example considered, the device comprises three pendular bodies 3. The connecting members 11 are here screwed on the pendulum masses 5 and each connecting member 6 is disposed in a mutualized window with a connecting member of a pendulum body 3 directly adjacent. These windows 19, three in number, each define two bearing tracks of the support 13.

 In the example considered, each of the connecting members 11 carries a single organ

abutment damping device 20 which comes into contact with the edge of a window 19 only in a clockwise or counterclockwise movement. One of the stop damping members 20 acts clockwise while the other acts counterclockwise. Each damping member does not act in both directions as in the example of FIG.

Figure 11

Finally, it is presented with reference to FIG. 11, a third example of the device 1 according to the invention, the device being here in a second configuration. In this example, each rolling member 11 cooperates with two integral running tracks 13 of the pendular body, each running track being defined by the edge of a cavity 50 formed in one of the pendulum masses 5. These cavities 50 are distinct from the possible grooves receiving the axial clamping means. For each rolling member January 1, the bearing track 12 secured to support is, in turn, defined by the edge of a cavity 52 of the support 2 separate windows 19 in which the connecting members 6 extend. rolling members 1 1 and the connecting members 6 are at a distance from each other.

 In this configuration example, each rolling member 11 can then comprise successively axially:

a portion cooperating with the rolling track defined by the edge of the cavity 50 of the first pendulum mass 5,

 a portion cooperating with the rolling track 12 defined by the edge of the cavity of the support 2, and

 a portion cooperating with the rolling track defined by the edge of the cavity 50 of the second pendulum mass 5,

 The portions of each rolling member January 1 are cylindrical successive and different radii.

 In the example, the connecting members 6 are rivets and each extends into a window 19 which is dedicated thereto.

 In the example considered, the opening 36 receiving the axial clamping means is disposed circumferentially between the two cavities 52. This axial clamping means can be one of those described in FIGS. 3 to 9. The pendulum masses 5 of this example can also define grooves as presented with reference to the second example of Figure 10.

 In the aforementioned examples, the axial clamping means 35 is compressed between the pendulum masses 5. In these examples, the axial clamping means 35 can exert on the pendulum body an axial clamping of 0.5 N, distributed equally on each of the two pendular masses 5. The overall clamping force, expressed in Newtons, may be between 20% and 1 10%) of the weight of the pendulum body, expressed in Newtons. Preferably, this clamping force is between 50% and 90%> of the weight of the pendulum body, in particular between 60% and 80%) of this weight.

 In particular in the configuration of the examples of FIGS. 1 to 9, the axial clamping means 35 can make it possible to stop the radial drop of the pendulum body. The axial clamping means can then exert an axial force at least equal to the gravitational force divided by the coefficient of friction between the axial clamping means and the pendulum masses.

Claims

claims  Pendulum damping device (1), comprising:  a support (2) able to move in rotation around an axis (X),  at least one pendular body (3) movable relative to the support (2), comprising: first and second pendular masses (5) axially spaced relative to one another and movable relative to the support (2); ), the first pendulum mass (5) being disposed axially of a first side (4) of the support (2) and the second pendulum mass (5) being disposed axially of a second side (4) of the support (2), and at least one connecting member (6) of the first and second pendulum masses (5) matching said masses, and - At least one rolling member (11) guiding the displacement of the pendulum body (3) relative to the support (2), the rolling member (11) cooperating on the one hand with at least one raceway (12). secured to the support (2) and on the other hand with at least one running track (13) integral with the pendulum body (3), characterized in that the device also comprises an axial clamping means (35) arranged axially between the first and second pendulum masses (5), partially housed in an opening (36) formed in the support and able to rub on the first and second pendulum masses (5) for certain relative displacements of the pendulum body and the support.  2. Device (1) according to claim 1, the opening (36) being configured to limit the displacement of the axial clamping means (35) relative to the support (2) beyond a first deflection of the pendulum body ( 3) relative to the support.  3. Device (1) according to claim 1, the opening (36) being configured to limit the displacement of the axial clamping means (35) for any deflection of the pendulum body (3) relative to the support (2).  4. Device (1) according to any one of the preceding claims, the opening (36) being configured to limit the displacement of the axial clamping means (35) when the pendulum body (3) is no longer centrifuged so that the axial clamping means (35) rubs on the pendulum masses (5) to brake the radial drop of the pendulum body.  5. Device (1) according to one of the preceding claims, the axial clamping means cooperating with axial inner faces of substantially flat pendulum masses (5). 6. Device (1) according to one of the preceding claims, the first and second pendulum masses (5) being configured to block the displacement of the axial clamping means (35) relative to the pendulum body (3) when the pendulum body n is more centrifuged. 7. Device (1) according to the preceding claim, the first and second pendulum masses define grooves (60) receiving the axial clamping means (36) and an edge of the grooves (60) radially blocks the displacement of the axial clamping means (35) relative to the pendulum masses (5).  8. Device (1) according to any one of the preceding claims, the axial clamping means (35) comprises an elastic return member (40), in particular a straight spring or an elastomer block.  9. Device (1) according to the preceding claim, the axial clamping means (35) also comprises two cups (41) intended to rub on the first and second pendulum masses (5) under the action of the elastic return member (40).  10. Device (1) according to the preceding claim, the elastic return member (40) is a spring and each cup (41) comprising a friction portion (45) and a holding portion (46), each holding portion (45) being either internal to the spring or external to the spring, or having an inner portion and an outer portion to the spring.  11. Device (1) according to the preceding claim, the axial clamping means (35) is adapted to contact the edge of the opening of the support is:  - via the cups (41), and / or  - via a cylindrical ring (49) separate from the cups.  12. Component for a transmission system of a motor vehicle, the component being in particular a double damping flywheel, a hydrodynamic torque converter, a friction clutch disc, a flywheel integral with the crankshaft, a double clutch dry or wet, a simple wet clutch and a hybrid module comprising an electric machine, comprising a pendulum damping device (1) according to any one of Claims 1 to 11.