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WO2004016968A1 - Cam-driven damping double flywheel and cam follower for motor vehicle - Google Patents

Cam-driven damping double flywheel and cam follower for motor vehicle Download PDF

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Publication number
WO2004016968A1
WO2004016968A1 PCT/FR2002/002860 FR0202860W WO2004016968A1 WO 2004016968 A1 WO2004016968 A1 WO 2004016968A1 FR 0202860 W FR0202860 W FR 0202860W WO 2004016968 A1 WO2004016968 A1 WO 2004016968A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
double damping
flywheels
flywheel according
damping flywheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/FR2002/002860
Other languages
French (fr)
Inventor
Pascal Thery
Gino Villata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Embrayages SAS
Original Assignee
Valeo Embrayages SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Embrayages SAS filed Critical Valeo Embrayages SAS
Priority to DE10297771T priority Critical patent/DE10297771T5/en
Priority to AU2002341046A priority patent/AU2002341046A1/en
Priority to PCT/FR2002/002860 priority patent/WO2004016968A1/en
Publication of WO2004016968A1 publication Critical patent/WO2004016968A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13157—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses with a kinematic mechanism or gear system, e.g. planetary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13407—Radially mounted springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/0052—Physically guiding or influencing
    • F16F2230/0064—Physically guiding or influencing using a cam

Definitions

  • Double cam damper flywheel and cam follower in particular for motor vehicles
  • the invention relates to a double damping flywheel, in particular for a motor vehicle, comprising two coaxial flywheels, one of which is fixed at the end of a driving shaft and the other of which is linked in rotation to a driven shaft, these two flywheels being connected to each other by a torsion damper for the transmission of a torque between the two shafts with absorption and damping of torsional vibrations and rotation irregularities.
  • a torsion damper comprises an input element integral with the first steering wheel, an output element connected to the second steering wheel, springs mounted between the input element and the output element to absorb by elastic deformation the relative rotations between the two flywheels and friction means mounted between the input and output elements or between the two flywheels, to dampen their relative rotation.
  • the springs of the torsion damper can be oriented circumferentially or radially and / or comprise blocks of elastically deformable material such as rubber or an elastomer.
  • the torque limiters sometimes provided in these double flywheels generally comprise two parts tightened one on the other by an elastic force, one of these two parts being linked to the first flywheel and the other to the second flywheel, the force of tightening being determined so that the torque transmitted by the two parts is greater than the maximum torque supplied by the motor but significantly less than the torque produced at the resonance of the second flywheel which is several times greater than the maximum engine torque.
  • torsion dampers of the cam type and cam follower roller in which a cam carried by one of the flywheels cooperates with a cam follower roller carried by the other of the flywheels, with elastically deformable means on which acts the cam and which exert on the flywheels an elastic return torque tending to cancel the relative rotations between the two flywheels.
  • the object of the present invention is in particular to provide significant improvements to such a device.
  • It relates to a double damping flywheel, in particular for a motor vehicle, which is of the cam and cam follower type with a very simple and space-saving structure. It also relates to a double damping flywheel of this type, the torsion damper of which also forms torque limiter and avoids any risk of disturbance or degradation of the transmission at resonance.
  • a double damping flywheel in particular for a motor vehicle, comprising two coaxial flywheels, the first of which is rotated by a driving shaft and the second of which is mounted for rotation on the first, and means torsion dampers mounted between the two steering wheels and comprising input means linked to the first steering wheel, output means linked to the second steering wheel, and elastically deformable return means exerting on the steering wheels a return torque, the input and output means comprising a cam carried by one of the flywheels and at least one cam follower carried by the other of the flywheels and compelled to follow the profile of the cam during the relative rotations between the flywheels, the movement of the cam follower on the profile of the cam causing a deformation of said return means, the profile of the cam extending around the axis of rotation of the flywheel and comprising a first part corresponding to a deformation substantially null of the return means and of the second and third parts situated on either side of the first part and corresponding to maximum deformations of the return means
  • the limitation of the transmitted torque is done without shock and without jerks, without the means elastic return of the torsion damping device abuts.
  • the cam follower is movable beyond the second and third parts of the cam profile on parts of this profile for which the values of the restoring torque exerted on the flywheels are lower than the values reached when the cam follower is on the second and third parts of the cam profile.
  • the two flywheels when the torque transmitted between the flywheels reaches a predetermined maximum value, the two flywheels can continue to rotate relative to each other in the same direction, the maximum value of the transmissible torque decreasing before increasing again to maximum values when the cam follower passes over the aforementioned second and third parts of the cam profile.
  • passing through the resonant frequency which corresponds to a rotational speed lower than the idle speed in the case of an internal combustion engine of a motor vehicle, cannot cause any oscillation of high amplitude liable to damage or destroy the transmission.
  • the cam follower is mounted for rotation on an arm carried by said other flywheel and extending in a plane perpendicular to the axis of rotation of the flywheels.
  • the device according to the invention comprises several cam followers, each mounted on an aforementioned arm and distributed angularly in a regular manner around the axis of rotation of the flywheels.
  • the or each aforementioned arm is substantially rigid and is pivotally mounted on said other flywheel about an axis parallel to the axis of rotation of the flywheels.
  • the return means comprise at least one spring acting on this arm.
  • the springs are compression springs and are oriented substantially radially, being mounted between the arms of the cam followers.
  • the or each aforementioned arm is associated with at least one return spring working in flexion.
  • this return spring is a leaf spring, one end of which is fixed, in particular by embedding or the like, on said other flywheel. The other end of the leaf spring can be in sliding support on said other flywheel.
  • this return spring comprises at least one continuous ring mounted floating on said other flywheel and the arms of the cam followers bear on this ring at points distributed regularly around the axis of rotation.
  • the or each aforementioned arm is flexible and is fixed by one end to said other flywheel.
  • each arm then comprises a leaf spring working in flexion, one end of which is fixed, in particular by embedding or the like, on said other flywheel.
  • each leaf spring can be of the iso-stressed type, formed by several superposed blades of different lengths.
  • the cam can be located either radially outside the cam followers, or radially inside the latter.
  • the double damping flywheel according to the invention has the advantage of a simple, efficient and economical structure in which the operation of the cam followers in torque limiter ensures excellent protection of the transmission in passing by resonance. .
  • the cam profile can be given any desired shape and thus differentiate the operation of the torsion damper and the torque limiter as a function of the direction of rotation of the first flywheel relative to the second. In addition, it is thus possible to determine at will the progressiveness of the elastic return torque between the flywheels.
  • FIG. 1 is a schematic front view in partial section of a double damping flywheel according to one invention
  • FIG. 2 is a sectional view along line II-II of Figure 1;
  • - Figure 3 is a partial schematic front view of an alternative embodiment of the double damping flywheel;
  • FIG. 4 is a schematic half-view in axial section of the device of Figure 3;
  • FIG. 5 is a schematic half-view in axial section of an alternative embodiment
  • FIG. 6 is a partial schematic front view of another alternative embodiment.
  • FIG. 7 is a partial schematic front view of another alternative embodiment;
  • FIG. 8 is a schematic view on a small scale of the elastic return means of the device of Figure 7;
  • - Figure 9 is a schematic front view of yet another alternative embodiment;
  • FIG. 10 is a partial diagrammatic view on a larger scale of a cam follower arm of the device in FIG. 9.
  • FIGS. 1 and 2 schematically represent a double damping flywheel according to the invention, comprising a first flywheel 10 intended to be fixed at the end of a driving shaft not shown, such as the crankshaft of an internal combustion engine, and carrying at its outer periphery a starter ring 12 and a second flywheel 14 coaxial with the first flywheel 10 and rotatably mounted thereon by means of a bearing 16 such as a ball bearing or the like, this second flywheel 14 generally forming the reaction plate of a clutch (not shown) connecting to a driven shaft such as the input shaft of a gearbox.
  • a driving shaft not shown such as the crankshaft of an internal combustion engine
  • the two flywheels 10 and 14 are linked to each other in rotation by a torsion damper comprising inlet means 18, which are carried by the first flywheel, outlet means 20 which are carried by the second flywheel 14, and elastically deformable means such as springs 22 which develop an elastic return torque tending to bring the flywheels 10 and 14 into a relative angular position of rest shown in FIG. 1.
  • a torsion damper comprising inlet means 18, which are carried by the first flywheel, outlet means 20 which are carried by the second flywheel 14, and elastically deformable means such as springs 22 which develop an elastic return torque tending to bring the flywheels 10 and 14 into a relative angular position of rest shown in FIG. 1.
  • the input means 18 of the torsion damper are arms pivotally mounted on the first flywheel 10 around axes 24 parallel to the axis of rotation 26 of the two flywheels, these arms 18 extending transversely in a plane perpendicular to the axis of rotation 26 and each carrying a roller 28 mounted for rotation about an axis 30 parallel to the axis 26 of rotation of the flywheels, each roller 28 being in abutment on the outer profile of a cam 32 centered on the axis of rotation and forming the aforementioned outlet means 20 integral with the second flywheel 14.
  • Each arm 18 comprises a first end 34 close to the outer periphery of the flywheels 10 and 14 and a second end 36 close to the external profile of the cam 32.
  • the springs 22 of the torsion damper are mounted between the ends 34 of the arms 18 and the ends 36 of the adjacent arms 18 so as to oppose a rotation of the arms 18 around the axes 24 in a direction corresponding to a radial displacement of the rollers 28 outwards.
  • each arm 18 comprises two spring seats 38 which are offset circumferentially and radially and the end 36 of each arm 18 also comprises two spring seats 40 offset in the same way as the seats 38 of the other end of the arm, so that the springs 22 which are mounted between the seats 38 of the end 34 of an arm 18 and the seats 40 of the opposite end 36 of an adjacent arm 18 extend substantially radially with respect to the axis of rotation 26 of the flywheels and are deformable axially during the relative rotations between the flywheels .
  • the springs 22 are compression springs and keep the rollers 28 in abutment on the outer profile of the cam 32.
  • the double damping flywheel according to the invention comprises four arms 18 each carrying a roller 28 and the external profile of the cam 32 comprises four lobes 42 of convex rounded shape, which are centered on the axis of rotation 26 and which are connected together by vertices 44 which constitute the parts of the cam profile furthest from the axis of rotation 26.
  • This device operates as follows: The torsional vibrations and the torque irregularities which are produced by the internal combustion engine are transmitted by the shaft leading to the first flywheel 10 and generate relative rotations between the two flywheels 10 and 14. A rotation of the flywheel 10 in one direction or the other relative to the flywheel 14 from the rest position shown in FIG. 1 results in a radial displacement towards the outside of the rollers 28 which roll on the profile outside of the cam 32 and therefore by a rotation of the arms 18 around the axes 24 in the direction tending to bring their ends 34 closer to the axis of rotation and to move their others apart ends 36. This results in compression of the springs 22 which tend to oppose this relative rotation of the flywheel 10 relative to the flywheel 14 and to bring the two flywheels back into the rest position shown in FIG. 1.
  • the mounting of the springs 22 between the ends 34 and 36 of the arms 18 is such that the springs 22 are compressed substantially along their axis and therefore work in good conditions, without the risk of reducing their service life.
  • the springs 22 are oriented substantially radially, they are sensitive to the centrifugal force resulting from the rotation of the flywheels and, for this reason, their radially internal ends are guided on relatively long radial fingers extending outwards from the seats 40 provided on the ends 36 of the arms 18.
  • the seats 38 of the ends 34 of the arms 18 remain substantially parallel to the seats 40 of the ends 36 of the adjacent arms 18.
  • the device according to the invention makes it possible to very strongly dampen this resonance phenomenon and very effectively limit its effects, thanks to the fact that the rollers 28 carried by the arms 18 of the torsion damper can pass from a lobe 42 to the next lobe of the external profile of the cam by rolling on the vertices 44 of the cam profile, the torsion damper thus playing the role of a torque limiter whenever necessary.
  • the restoring forces developed by the springs 22 first increase during this relative rotation, until the rollers 28 pass the vertices 44 of the cam profile, then decrease and increase again until the rollers 28 pass on the following vertices 44 of the cam profile and so on. These restoring forces are therefore first in phase with the resonance phenomenon and then in phase opposition, which makes it possible to very effectively dampen the resonance phenomenon and to prevent its development.
  • friction means arranged between the flywheels 10 and 14 and / or between the input and output means of the torsion damper, not shown in Figures 1 and 2 may be provided to dampen the relative rotations of the two flywheels which are absorbed by the springs 22, in particular at resonance.
  • the lobes 42 of the external profile of the cam 32 can be given any desired shape corresponding to a desired progressiveness of the compression of the springs 22. It is thus possible to vary the compression of these springs in a non-linear fashion as a function of the angular deflections between the flywheels , and we can determine different variations of these compressions in one direction of rotation and in the opposite direction.
  • the angular movement, usable for torsional damping in normal operation (outside the resonance) is a little less than 45 ° on either side of a rest position, this angular movement being determined by the number of rollers 28 and arms 18.
  • the angular clearance for damping vibrations in normal operation would be approximately 60 ° on either side of a rest position, outside of resonance.
  • this angular movement could reach 90 ° on either side of a rest position.
  • FIGS. 1 and 2 An advantage of the embodiment of FIGS. 1 and 2 is that the arms 18, due to their mounting on a pivot axis in an approximately median zone of these arms, are not very sensitive to the centrifugal force. It can advantageously be provided that the effect of the centrifugal force is greater on the part of the arm not carrying the roller 28, which results in a positive holding of the roller on the cam surface, in rotation.
  • the cam 32 is a solid part which is located radially outside the rollers 28 carried by the arms 18 and is mounted on the first flywheel 10 which is formed of a flexible sheet, the arms 18 carrying the rollers 28 are articulated by one end around axes 24 on the second flywheel 14 and the springs 22 extend more or less radially between the other end of the arms 18 and the base of the fingers 50 formed on a plate 52 secured to the second flywheel 14 and carrying the axes 24 of articulation of the arms 18.
  • each roller 28 rolls on an internal cam profile comprising lobes 42 of concave rounded shape connected together by vertices 44 which project radially towards the axis of rotation of the flywheels.
  • the arms 18 are made of pressed sheet metal and have a substantially U-shaped cross section.
  • the rollers 28 are mounted on ball or needle bearings.
  • the axes 24 of articulation of the ends of the arms 18 transmit the engine torque but are not subjected to the forces exerted by the springs 22 and are not very sensitive to the centrifugal force.
  • the centrifugal force is added to the stiffness of the springs acting on the arms 18, so that the return torque of the flywheels increases with the rotation speed, which is a definite advantage. This allows in particular to have a lower return torque at low revs, which is favorable to the absorption of vibrations.
  • friction means of the torsion damper which include a friction washer 52 integral in rotation with the second flywheel 14 and applied to the first flywheel 10 by an elastic washer 54 held between this friction washer 52 and a application washer 56 secured to the first flywheel 10.
  • the torsion damper is located radially outside the screws 58 for fixing the first flywheel 10 on the end of the driving shaft 60, these fixing screws 58 being insertable and maneuverable through orifices 59 of the second flywheel 14.
  • the mass of inertia of the first flywheel is formed by material arranged in the available places, that is to say on the periphery of the first flywheel as indicated at 64 between the arms 18 carrying the rollers 28.
  • the mass of inertia of the first flywheel is formed by the cam 32 which is fixed at the periphery of the flexible sheet 10 for connection to the driving shaft 60.
  • the cam 32 is formed from a stamped sheet metal whose radially internal peripheral part is fixed to the driving shaft 60 by the screws 58 and whose radially external periphery is fixed by rivets 66 on an inertial mass 68 of annular shape carrying the starter ring 12.
  • the rollers 28 carried by the arms 18 are radially inside the cam 32 and roll on the internal profile of the latter.
  • the arms 18 are formed by bending tabs, one end of which is fixed in the manner of embedding on a plate 70 integral with the second flywheel 14. The other end of the bending tabs is fixed on a yoke 72 of support of the roller 28 by means of a bearing.
  • the radially internal part of the yoke 72 is supported on a spring leaf 74 whose one end is fixed to the plate 70 by the means for fixing the tongues 18 and the other end of which is in sliding support on a boss 76 of the plate 70, this boss being preferably treated to reduce wear.
  • the internal profile of the cam 32 has rounded lobes 42 which are connected by vertices 44.
  • each arm 18 has tabs 80 oriented radially towards the axis of rotation and which extend on either side of the spring rings 78 to hold them in place.
  • rollers 28 roll on an internal cam profile comprising lobes 42 and vertices 44 as already described, and are mounted by means of yokes 72 corresponding substantially to those of FIGS. 5 and 6 on the end of the flexion arms 18 which are of the isostress type and which are formed by superposition of flexion blades 82 of different length, fixed together by embedding or the like on a plate 84 secured to one of the flywheels.
  • An advantage of the double-damping dampers described in the above is that the cam and arm system carrying the cam follower rollers is located radially outside the fixing screws of the first flywheel 10 on the motor shaft , so that the number of arms and rollers is completely independent of the number of fixing screws on the motor shaft and can be chosen at will.
  • the springs of the torsion damper are helical compression springs
  • their orientation may be radial or substantially radial, as shown, or different, this orientation depending on the shape given to the arms 18.
  • the compression curve of the return springs can be determined at will from the shape of the cam profile and can be different in one direction of rotation and in the opposite direction.
  • the torsional damper and in particular the rolling surfaces of the rollers 28 can be protected from fouling by a deflector 88 extending along the second flywheel 14 between that -ci and the cam 32 forming a mass of inertia carried by the flexible flywheel 10, the deflector 88 preventing the particles of material coming from the linings of the friction disc 94 from coming between the rollers 28 and the cam surface, and orifices 90 aeration and evacuation of the particles of friction materials can be formed in the flexible flywheel 10 at the abovementioned friction means 52, 54, 56, in order to evacuate these particles outside. Ventilation holes 92 can be formed in the second flywheel 14, radially inside the friction surface thereof.
  • holes 96 can be formed in the cylindrical part of the cam 32, in the vicinity of the rollers 28, in order to evacuate the dust and the centrifuged particles to the cam surface outside.

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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
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Abstract

The invention concerns a damping double flywheel, in particular for motor vehicle, comprising two flywheels linked in rotation by a torsional damper consisting of a cam (32) integral with one of the flywheels and of arms (18) mounted pivotably in the other flywheel and bearing cam followers (28), associated with springs (22) countering the relative rotations of the flywheels, the torsional damper forming a torque limiter as a result of the passage of the cam followers (28) on peaks (44) of the cam profile.

Description

Double-volant amortisseur à came et suiveur de came, en particulier pour véhicule automobile Double cam damper flywheel and cam follower, in particular for motor vehicles

L'invention concerne un double-volant amortisseur, en particulier pour véhicule automobile, comprenant deux volants d'inertie coaxiaux dont l'un est fixé en bout d'un arbre menant et dont l'autre est lié en rotation à un arbre mené, ces deux volants étant reliés l'un à l'autre par un amortisseur de torsion pour la transmission d'un couple de rotation entre les deux arbres avec absorption et amortissement des vibrations de torsion et irrégularités de rotation.The invention relates to a double damping flywheel, in particular for a motor vehicle, comprising two coaxial flywheels, one of which is fixed at the end of a driving shaft and the other of which is linked in rotation to a driven shaft, these two flywheels being connected to each other by a torsion damper for the transmission of a torque between the two shafts with absorption and damping of torsional vibrations and rotation irregularities.

Dans la technique classique, un amortisseur de torsion comprend un élément d'entrée solidaire du premier volant, un élément de sortie relié au second volant, des ressorts montés entre l'élément d'entrée et l'élément de sortie pour absorber par déformation élastique les rotations relatives entre les deux volants et des moyens de friction montés entre les éléments d'entrée et de sortie ou entre les deux volants, pour amortir leur rotation relative.In the conventional technique, a torsion damper comprises an input element integral with the first steering wheel, an output element connected to the second steering wheel, springs mounted between the input element and the output element to absorb by elastic deformation the relative rotations between the two flywheels and friction means mounted between the input and output elements or between the two flywheels, to dampen their relative rotation.

De façon connue, les ressorts de l'amortisseur de torsion peuvent être orientés circonférentiellement ou radialement et/ou comprendre des blocs de matériau élastiquement déformable tel que du caoutchouc ou un élastomère. Les limiteurs de couple parfois prévus dans ces doubles volants comprennent en général deux pièces serrées l'une sur l'autre par une force élastique, l'une de ces deux pièces étant liée au premier volant et l'autre au second volant, la force de serrage étant déterminée pour que le couple de rotation transmissible par les deux pièces soit supérieur au couple maximal fourni par le moteur mais nettement inférieur au couple produit à la résonance du second volant qui est plusieurs fois supérieur au couple maximal du moteur.In known manner, the springs of the torsion damper can be oriented circumferentially or radially and / or comprise blocks of elastically deformable material such as rubber or an elastomer. The torque limiters sometimes provided in these double flywheels generally comprise two parts tightened one on the other by an elastic force, one of these two parts being linked to the first flywheel and the other to the second flywheel, the force of tightening being determined so that the torque transmitted by the two parts is greater than the maximum torque supplied by the motor but significantly less than the torque produced at the resonance of the second flywheel which is several times greater than the maximum engine torque.

On a déjà proposé, par exemple dans FR-A-2 714We have already proposed, for example in FR-A-2 714

435, des amortisseurs de torsion du type à came et à galet suiveur de came, dans lesquels une came portée par l'un des volants coopère avec un galet suiveur de came porté par l'autre des volants, avec des moyens élastiquement déformables sur lesquels agit la came et qui exercent sur les volants un couple de rappel élastique tendant à annuler les rotations relatives entre les deux volants.435, torsion dampers of the cam type and cam follower roller, in which a cam carried by one of the flywheels cooperates with a cam follower roller carried by the other of the flywheels, with elastically deformable means on which acts the cam and which exert on the flywheels an elastic return torque tending to cancel the relative rotations between the two flywheels.

La présente invention a notamment pour but d'apporter des perfectionnements importants à un tel dispositif.The object of the present invention is in particular to provide significant improvements to such a device.

Elle a pour objet un double-volant amortisseur, en particulier pour véhicule automobile, qui est du type à came et suiveur de came avec une structure très simple et peu encombrante. Elle a également pour objet un double-volant amortisseur de ce type, dont l'amortisseur de torsion forme également limiteur de couple et évite tout risque de perturbation ou de dégradation de la transmission à la résonance.It relates to a double damping flywheel, in particular for a motor vehicle, which is of the cam and cam follower type with a very simple and space-saving structure. It also relates to a double damping flywheel of this type, the torsion damper of which also forms torque limiter and avoids any risk of disturbance or degradation of the transmission at resonance.

Elle propose à cet effet un double-volant amortisseur, en particulier pour véhicule automobile, comprenant deux volants d'inertie coaxiaux dont le premier est entraîné en rotation par un arbre menant et dont le second est monté à rotation sur le premier, et des moyens amortisseurs de torsion montés entre les deux volants et comprenant des moyens d'entrée liés au premier volant, des moyens de sortie liés au second volant, et des moyens de rappel élastiquement déformables exerçant sur les volants un couple de rappel, les moyens d'entrée et de sortie comprenant une came portée par l'un des volants et au moins un suiveur de came porté par 1 ' autre des volants et astreint à suivre le profil de la came lors des rotations relatives entre les volants, le déplacement du suiveur de came sur le profil de la came provoquant une déformation desdits moyens de rappel, le profil de la came s 'étendant autour de l'axe de rotation du volant et comportant une première partie correspondant à une déformation sensiblement nulle des moyens de rappel et des deuxième et troisième parties situées de part et d'autre de la première partie et correspondant à des déformations maximales des moyens de rappel lors des rotations relatives entre les volants, respectivement dans un sens direct de rotation et dans un sens opposé ou sens rétro, caractérisé en ce que le suiveur de came est déplaçable sur le profil de came sur 360° autour de l'axe de rotation des volants, son passage sur les deuxième et troisième parties du profil de came limitant à des valeurs maximales prédéterminées le couple transmissible entre les volants .To this end, it offers a double damping flywheel, in particular for a motor vehicle, comprising two coaxial flywheels, the first of which is rotated by a driving shaft and the second of which is mounted for rotation on the first, and means torsion dampers mounted between the two steering wheels and comprising input means linked to the first steering wheel, output means linked to the second steering wheel, and elastically deformable return means exerting on the steering wheels a return torque, the input and output means comprising a cam carried by one of the flywheels and at least one cam follower carried by the other of the flywheels and compelled to follow the profile of the cam during the relative rotations between the flywheels, the movement of the cam follower on the profile of the cam causing a deformation of said return means, the profile of the cam extending around the axis of rotation of the flywheel and comprising a first part corresponding to a deformation substantially null of the return means and of the second and third parts situated on either side of the first part and corresponding to maximum deformations of the return means during the relative rotations between the flywheels, respectively in a direct direction of rotation and in a opposite or retro direction, characterized in that the cam follower can be moved on the cam profile through 360 ° around the axis of rotation of the flywheels, its passage over the uxth and third parts of the cam profile limiting the transmissible torque between the flywheels to predetermined maximum values.

Ainsi, dans le dispositif selon l'invention, c ' est le passage du suiveur de came sur certaines parties du profil de la came qui limite le couple transmissible par le dispositif à des valeurs maximales prédéterminées .Thus, in the device according to the invention, it is the passage of the cam follower over certain parts of the profile of the cam which limits the torque transmissible by the device to predetermined maximum values.

Il n'est donc plus nécessaire de prévoir des moyens spécifiques de limitation du couple, tels que des moyens de serrage élastiques de deux pièces l'une sur l'autre, qui étaient prévus dans la technique antérieure .It is therefore no longer necessary to provide specific means for limiting the torque, such as elastic clamping means of two pieces one on the other, which were provided in the prior art.

En outre, la limitation du couple transmis se fait sans choc et sans-à-coups, sans que les moyens élastiques de rappel du dispositif amortisseur de torsion viennent en butée.In addition, the limitation of the transmitted torque is done without shock and without jerks, without the means elastic return of the torsion damping device abuts.

Selon une autre caractéristique de l'invention, le suiveur de came est déplaçable au-delà des deuxième et troisième parties du profil de came sur des parties de ce profil pour lesquelles les valeurs du couple de rappel exercé sur les volants sont inférieures aux valeurs atteintes quand le suiveur de came est sur les deuxième et troisième parties du profil de came.According to another characteristic of the invention, the cam follower is movable beyond the second and third parts of the cam profile on parts of this profile for which the values of the restoring torque exerted on the flywheels are lower than the values reached when the cam follower is on the second and third parts of the cam profile.

Ainsi, dans le dispositif selon l'invention, lorsque le couple transmis entre les volants atteint une valeur maximale prédéterminée, les deux volants peuvent continuer à tourner l'un par rapport à l'autre dans le même sens, la valeur maximale du couple transmissible diminuant avant de réaugmenter jusqu'à des valeurs maximales au passage du suiveur de came sur les deuxième et troisième parties précitées du profil de came. De cette façon, le passage par la fréquence de résonance, qui correspond à une vitesse de rotation inférieure au régime de ralenti dans le cas d'un moteur à combustion interne de véhicule automobile, ne peut provoquer aucune oscillation de forte amplitude susceptible d'endommager ou de détruire la transmission.Thus, in the device according to the invention, when the torque transmitted between the flywheels reaches a predetermined maximum value, the two flywheels can continue to rotate relative to each other in the same direction, the maximum value of the transmissible torque decreasing before increasing again to maximum values when the cam follower passes over the aforementioned second and third parts of the cam profile. In this way, passing through the resonant frequency, which corresponds to a rotational speed lower than the idle speed in the case of an internal combustion engine of a motor vehicle, cannot cause any oscillation of high amplitude liable to damage or destroy the transmission.

Selon une autre caractéristique de l'invention, le suiveur de came est monté à rotation sur un bras porté par ledit autre volant et s 'étendant dans un plan perpendiculaire à l'axe de rotation des volants.According to another characteristic of the invention, the cam follower is mounted for rotation on an arm carried by said other flywheel and extending in a plane perpendicular to the axis of rotation of the flywheels.

De préférence, le dispositif selon l'invention comprend plusieurs suiveurs de came, montés chacun sur un bras précité et répartis angulairement de façon régulière autour de l'axe de rotation des volants. Dans un premier mode de réalisation de l'invention, le ou chaque bras précité est sensiblement rigide et est monté pivotant sur ledit autre volant autour d'un axe parallèle à l'axe de rotation des volants.Preferably, the device according to the invention comprises several cam followers, each mounted on an aforementioned arm and distributed angularly in a regular manner around the axis of rotation of the flywheels. In a first embodiment of the invention, the or each aforementioned arm is substantially rigid and is pivotally mounted on said other flywheel about an axis parallel to the axis of rotation of the flywheels.

Les moyens de rappel comprennent au moins un ressort agissant sur ce bras.The return means comprise at least one spring acting on this arm.

Dans une forme de réalisation particulièrement avantageuse, les ressorts sont des ressorts de compression et sont orientés sensiblement radialement, en étant montés entre les bras des suiveurs de came .In a particularly advantageous embodiment, the springs are compression springs and are oriented substantially radially, being mounted between the arms of the cam followers.

Dans un autre mode de réalisation de l'invention, le ou chaque bras précité est associé à au moins un ressort de rappel travaillant en flexion. Avantageusement, ce ressort de rappel est un ressort à lame dont une extrémité est fixée, en particulier par encastrement ou analogue, sur ledit autre volant . L'autre extrémité du ressort à lame peut être en appui glissant sur ledit autre volant.In another embodiment of the invention, the or each aforementioned arm is associated with at least one return spring working in flexion. Advantageously, this return spring is a leaf spring, one end of which is fixed, in particular by embedding or the like, on said other flywheel. The other end of the leaf spring can be in sliding support on said other flywheel.

Dans une variante de réalisation, ce ressort de rappel comprend au moins un anneau continu monté flottant sur ledit autre volant et les bras des suiveurs de came prennent appui sur cet anneau en des points répartis régulièrement autour de l'axe de rotation.In an alternative embodiment, this return spring comprises at least one continuous ring mounted floating on said other flywheel and the arms of the cam followers bear on this ring at points distributed regularly around the axis of rotation.

Dans un autre mode de réalisation, le ou chaque bras précité est flexible et est fixé par une extrémité sur ledit autre volant .In another embodiment, the or each aforementioned arm is flexible and is fixed by one end to said other flywheel.

Avantageusement, le ou chaque bras comprend alors un ressort à lame travaillant en flexion dont une extrémité est fixée, en particulier par encastrement ou analogue, sur ledit autre volant. De plus, chaque ressort à lame peut être du type isocontrainte, formé de plusieurs lames superposées de longueurs différentes.Advantageously, the or each arm then comprises a leaf spring working in flexion, one end of which is fixed, in particular by embedding or the like, on said other flywheel. In addition, each leaf spring can be of the iso-stressed type, formed by several superposed blades of different lengths.

Selon les modes de réalisation, la came peut se trouver soit radialement à l'extérieur des suiveurs de came, soit radialement à l'intérieur de ces derniers.According to the embodiments, the cam can be located either radially outside the cam followers, or radially inside the latter.

Elle peut être réalisée en tôle ou être formée d'une pièce massive. De façon générale, le double-volant amortisseur selon l'invention présente l'avantage d'une structure simple, efficace et économique dans laquelle le fonctionnement des suiveurs de came en limiteur de couple assure une excellente protection de la transmission au passage par la résonance.It can be made of sheet metal or be made of a solid piece. In general, the double damping flywheel according to the invention has the advantage of a simple, efficient and economical structure in which the operation of the cam followers in torque limiter ensures excellent protection of the transmission in passing by resonance. .

De plus, on peut donner au profil de came toute forme souhaitée et ainsi différencier le fonctionnement de l'amortisseur de torsion et du limiteur de couple en fonction du sens de rotation du premier volant par rapport au second. De plus, on peut ainsi déterminer à volonté la progressivité du couple de rappel élastique entre les volants.In addition, the cam profile can be given any desired shape and thus differentiate the operation of the torsion damper and the torque limiter as a function of the direction of rotation of the first flywheel relative to the second. In addition, it is thus possible to determine at will the progressiveness of the elastic return torque between the flywheels.

L'invention sera mieux comprise et d'autres caractéristiques, détails et avantages de celle-ci apparaîtront plus clairement à la lecture de la description qui suit, faite à titre d'exemple en référence aux dessins annexés dans lesquels :The invention will be better understood and other characteristics, details and advantages thereof will appear more clearly on reading the description which follows, given by way of example with reference to the appended drawings in which:

- la figure 1 est une vue schématique de face et en coupe partielle d'un double-volant amortisseur selon 1 ' invention ;- Figure 1 is a schematic front view in partial section of a double damping flywheel according to one invention;

- la figure 2 est une vue en coupe selon la ligne II-II de la figure 1 ; - la figure 3 est une vue schématique partielle de face d'une variante de réalisation du double- volant amortisseur ;- Figure 2 is a sectional view along line II-II of Figure 1; - Figure 3 is a partial schematic front view of an alternative embodiment of the double damping flywheel;

- la figure 4 est une demi-vue schématique en coupe axiale du dispositif de la figure 3 ;- Figure 4 is a schematic half-view in axial section of the device of Figure 3;

- la figure 5 est une demi-vue schématique en coupe axiale d'une variante de réalisation ;- Figure 5 is a schematic half-view in axial section of an alternative embodiment;

- la figure 6 est une vue schématique partielle de face d'une autre variante de réalisation . - la figure 7 est une vue schématique partielle de face d'une autre variante de réalisation ;- Figure 6 is a partial schematic front view of another alternative embodiment. - Figure 7 is a partial schematic front view of another alternative embodiment;

- la figure 8 est une vue schématique à petite échelle des moyens de rappel élastiques du dispositif de la figure 7 ; - la figure 9 est une vue schématique de face d'encore une autre variante de réalisation ;- Figure 8 is a schematic view on a small scale of the elastic return means of the device of Figure 7; - Figure 9 is a schematic front view of yet another alternative embodiment;

- la figure 10 est une vue schématique partielle à plus grande échelle d'un bras de suiveur de came du dispositif de la figure 9.FIG. 10 is a partial diagrammatic view on a larger scale of a cam follower arm of the device in FIG. 9.

On se réfère d'abord aux figures 1 et 2 qui représentent schématiquement un double-volant amortisseur selon l'invention, comprenant un premier volant d'inertie 10 destiné à être fixé en bout d'un arbre menant non représenté, tel que le vilebrequin d'un moteur à combustion interne, et portant à sa périphérie externe une couronne de démarreur 12 et un second volant d'inertie 14 coaxial au premier volant 10 et monté à rotation sur celui-ci au moyen d'un palier 16 tel qu'un roulement à billes ou analogue, ce second volant d'inertie 14 formant en général le plateau de réaction d'un embrayage (non représenté) de liaison à un arbre mené tel que l'arbre d'entrée d'une boîte de vitesses. Les deux volants d'inertie 10 et 14 sont liés l'un à l'autre en rotation par un amortisseur de torsion comprenant des moyens d'entrée 18, qui sont portés par le premier volant 10, des moyens de sortie 20 qui sont portés par le second volant d'inertie 14, et des moyens élastiquement déformables tels que des ressorts 22 qui développent un couple de rappel élastique tendant à rapporter les volants 10 et 14 dans une position angulaire relative de repos représentée en figure 1.Reference is first made to FIGS. 1 and 2 which schematically represent a double damping flywheel according to the invention, comprising a first flywheel 10 intended to be fixed at the end of a driving shaft not shown, such as the crankshaft of an internal combustion engine, and carrying at its outer periphery a starter ring 12 and a second flywheel 14 coaxial with the first flywheel 10 and rotatably mounted thereon by means of a bearing 16 such as a ball bearing or the like, this second flywheel 14 generally forming the reaction plate of a clutch (not shown) connecting to a driven shaft such as the input shaft of a gearbox. The two flywheels 10 and 14 are linked to each other in rotation by a torsion damper comprising inlet means 18, which are carried by the first flywheel, outlet means 20 which are carried by the second flywheel 14, and elastically deformable means such as springs 22 which develop an elastic return torque tending to bring the flywheels 10 and 14 into a relative angular position of rest shown in FIG. 1.

Selon l'invention, les moyens d'entrée 18 de l'amortisseur de torsion sont des bras montés pivotants sur le premier volant 10 autour d'axes 24 parallèles à l'axe de rotation 26 des deux volants, ces bras 18 s ' étendant transversalement dans un plan perpendiculaire à l'axe de rotation 26 et portant chacun un galet 28 monté à rotation autour d'un axe 30 parallèle à l'axe 26 de rotation des volants, chaque galet 28 étant en appui sur le profil extérieur d'une came 32 centrée sur l'axe de rotation et formant les moyens de sortie précités 20 solidaires du second volant d'inertie 14.According to the invention, the input means 18 of the torsion damper are arms pivotally mounted on the first flywheel 10 around axes 24 parallel to the axis of rotation 26 of the two flywheels, these arms 18 extending transversely in a plane perpendicular to the axis of rotation 26 and each carrying a roller 28 mounted for rotation about an axis 30 parallel to the axis 26 of rotation of the flywheels, each roller 28 being in abutment on the outer profile of a cam 32 centered on the axis of rotation and forming the aforementioned outlet means 20 integral with the second flywheel 14.

Chaque bras 18 comprend une première extrémité 34 voisine de la périphérie extérieure des volants 10 et 14 et une seconde extrémité 36 voisine du profil extérieur de la came 32. Les ressorts 22 de 1 ' amortisseur de torsion sont montés entre les extrémités 34 des bras 18 et les extrémités 36 des bras adjacents 18 de façon à s'opposer à une rotation des bras 18 autour des axes 24 dans un sens correspondant à un déplacement radial des galets 28 vers l'extérieur.Each arm 18 comprises a first end 34 close to the outer periphery of the flywheels 10 and 14 and a second end 36 close to the external profile of the cam 32. The springs 22 of the torsion damper are mounted between the ends 34 of the arms 18 and the ends 36 of the adjacent arms 18 so as to oppose a rotation of the arms 18 around the axes 24 in a direction corresponding to a radial displacement of the rollers 28 outwards.

Dans l'exemple représenté, l'extrémité 34 de chaque bras 18 comprend deux sièges de ressort 38 qui sont décalés circonférentiellement et radialement et l'extrémité 36 de chaque bras 18 comprend également deux sièges de ressort 40 décalés de la même façon que les sièges 38 de l'autre extrémité du bras, de telle sorte que les ressorts 22 qui sont montés entre les sièges 38 de l'extrémité 34 d'un bras 18 et les sièges 40 de l'extrémité en regard 36 d'un bras 18 adjacent s'étendent sensiblement radialement par rapport à l'axe de rotation 26 des volants et sont déformables axialement lors des rotations relatives entre les volants.In the example shown, the end 34 of each arm 18 comprises two spring seats 38 which are offset circumferentially and radially and the end 36 of each arm 18 also comprises two spring seats 40 offset in the same way as the seats 38 of the other end of the arm, so that the springs 22 which are mounted between the seats 38 of the end 34 of an arm 18 and the seats 40 of the opposite end 36 of an adjacent arm 18 extend substantially radially with respect to the axis of rotation 26 of the flywheels and are deformable axially during the relative rotations between the flywheels .

Les ressorts 22 sont des ressorts de compression et maintiennent les galets 28 en appui sur le profil extérieur de la came 32.The springs 22 are compression springs and keep the rollers 28 in abutment on the outer profile of the cam 32.

Dans l'exemple représenté, le double-volant amortisseur selon l'invention comprend quatre bras 18 portant chacun un galet 28 et le profil extérieur de la came 32 comprend quatre lobes 42 de forme arrondie convexe, qui sont centrés sur l'axe de rotation 26 et qui sont reliés entre eux par des sommets 44 qui constituent les parties du profil de came les plus éloignées de l'axe de rotation 26.In the example shown, the double damping flywheel according to the invention comprises four arms 18 each carrying a roller 28 and the external profile of the cam 32 comprises four lobes 42 of convex rounded shape, which are centered on the axis of rotation 26 and which are connected together by vertices 44 which constitute the parts of the cam profile furthest from the axis of rotation 26.

Ce dispositif fonctionne de la façon suivante : Les vibrations de torsion et les irrégularités de couple qui sont produites par le moteur à combustion interne sont transmises par l'arbre menant au premier volant d'inertie 10 et génèrent des rotations relatives entre les deux volants 10 et 14. Une rotation du volant 10 dans un sens ou dans l'autre par rapport au volant 14 à partir de la position de repos représentée en figure 1 se traduit par un déplacement radial vers l'extérieur des galets 28 qui roulent sur le profil extérieur de la came 32 et donc par une rotation des bras 18 autour des axes 24 dans le sens tendant à rapprocher leurs extrémités 34 de l'axe de rotation et à en éloigner leurs autres extrémités 36. Il en résulte une compression des ressorts 22 qui tendent à s'opposer à cette rotation relative du volant 10 par rapport au volant 14 et à ramener les deux volants dans la position de repos représentée en figure 1.This device operates as follows: The torsional vibrations and the torque irregularities which are produced by the internal combustion engine are transmitted by the shaft leading to the first flywheel 10 and generate relative rotations between the two flywheels 10 and 14. A rotation of the flywheel 10 in one direction or the other relative to the flywheel 14 from the rest position shown in FIG. 1 results in a radial displacement towards the outside of the rollers 28 which roll on the profile outside of the cam 32 and therefore by a rotation of the arms 18 around the axes 24 in the direction tending to bring their ends 34 closer to the axis of rotation and to move their others apart ends 36. This results in compression of the springs 22 which tend to oppose this relative rotation of the flywheel 10 relative to the flywheel 14 and to bring the two flywheels back into the rest position shown in FIG. 1.

Le montage des ressorts 22 entre les extrémités 34 et 36 des bras 18 est tel que les ressorts 22 sont comprimés sensiblement le long de leur axe et travaillent donc dans de bonnes conditions, sans risque de réduction de leur durée de service. Comme les ressorts 22 sont orientés sensiblement radialement, ils sont sensibles à la force centrifuge résultant de la rotation des volants et, pour cette raison, leurs extrémités radialement internes sont guidées sur des doigts radiaux relativement longs s 'étendant vers l'extérieur depuis les sièges 40 prévus sur les extrémités 36 des bras 18.The mounting of the springs 22 between the ends 34 and 36 of the arms 18 is such that the springs 22 are compressed substantially along their axis and therefore work in good conditions, without the risk of reducing their service life. As the springs 22 are oriented substantially radially, they are sensitive to the centrifugal force resulting from the rotation of the flywheels and, for this reason, their radially internal ends are guided on relatively long radial fingers extending outwards from the seats 40 provided on the ends 36 of the arms 18.

Lors de la rotation des bras 18 autour des axes 24, les sièges 38 des extrémités 34 des bras 18 restent sensiblement parallèles aux sièges 40 des extrémités 36 des bras 18 adjacents.During the rotation of the arms 18 around the axes 24, the seats 38 of the ends 34 of the arms 18 remain substantially parallel to the seats 40 of the ends 36 of the adjacent arms 18.

Lorsque la rotation relative du volant d'inertie 10 par rapport au volant 14 est d'environ 45° par rapport à la position de repos représentée en figure 1, les galets 28 se trouvent sensiblement sur les sommets 44 du profil extérieur de la came 32 et les forces de rappel développés par les ressorts 22 sont maximales, sans toutefois que ces ressorts soient comprimés en butée, c'est-à-dire à spires jointives. Dans cette position, le couple de rotation transmis entre les volants est à une valeur maximale, les forces développées par les ressorts 22 étant déterminées pour que cette valeur maximale du couple transmissible soit supérieure au couple maximum produit par le moteur à combustion interne. Comme cela est bien connu dans la technique, un double-volant amortisseur du type représenté aux figures 1 et 2 est soumis à un phénomène de résonance pour une vitesse de rotation qui est inférieure au régime de ralenti du moteur à combustion interne, et qui est susceptible d'engendrer des couples de rotation très nettement supérieurs au couple maximum produit par le moteur en fonctionnement normal, de sorte que ce phénomène de résonance est susceptible d'endommager, voire de détruire certaines parties de la transmission reliant l'arbre moteur à la boîte de vitesses .When the relative rotation of the flywheel 10 relative to the flywheel 14 is approximately 45 ° relative to the rest position shown in Figure 1, the rollers 28 are located substantially on the vertices 44 of the outer profile of the cam 32 and the restoring forces developed by the springs 22 are maximum, without however that these springs are compressed in abutment, that is to say with contiguous turns. In this position, the torque transmitted between the flywheels is at a maximum value, the forces developed by the springs 22 being determined so that this maximum value of the transmissible torque is greater than the maximum torque produced by the internal combustion engine. As is well known in the art, a double damping flywheel of the type shown in FIGS. 1 and 2 is subjected to a phenomenon of resonance for a rotational speed which is less than the idle speed of the internal combustion engine, and which is likely to generate torque significantly higher than the maximum torque produced by the engine in normal operation, so that this resonance phenomenon is likely to damage or even destroy certain parts of the transmission connecting the engine shaft to the gearbox .

Le dispositif selon l'invention permet d'amortir très fortement ce phénomène de résonance et d'en limiter très efficacement les effets, grâce au fait que les galets 28 portés par les bras 18 de l'amortisseur de torsion peuvent passer d'un lobe 42 au lobe suivant du profil extérieur de la came en roulant sur les sommets 44 du profil de came, l'amortisseur de torsion jouant ainsi le rôle d'un limiteur de couple chaque fois que nécessaire.The device according to the invention makes it possible to very strongly dampen this resonance phenomenon and very effectively limit its effects, thanks to the fact that the rollers 28 carried by the arms 18 of the torsion damper can pass from a lobe 42 to the next lobe of the external profile of the cam by rolling on the vertices 44 of the cam profile, the torsion damper thus playing the role of a torque limiter whenever necessary.

De façon plus détaillée, le fonctionnement est le suivant :In more detail, the operation is as follows:

Au passage par la vitesse de résonance, c'est-à- dire essentiellement au démarrage et à l'arrêt du moteur à combustion interne, le couple et l'énergie transmis au second volant d'inertie 14 augmentent brutalement, ce qui se traduit par une rotation du volant 14 par rapport au volant 10 dans un sens déterminé. Du fait de cette rotation, les galets 28 portés par les bras 18 roulent sur le profil de la came 32 jusqu'aux sommets 44 précités, puis passent ces sommets et roulent sur les parties adjacentes 42 du profil de came, et ainsi de suite, la rotation relative entre les volants n'étant pas limitée. Les forces de rappel développées par les ressorts 22 augmentent tout d'abord au cours de cette rotation relative, jusqu'à ce que les galets 28 passent les sommets 44 du profil de came, puis diminuent et réaugmentent jusqu'à ce que les galets 28 passent sur les sommets 44 suivants du profil de came et ainsi de suite. Ces forces de rappel sont donc tout d'abord en phase avec le phénomène de résonance puis en opposition de phase, ce qui permet d'amortir très efficacement le phénomène de résonance et d'empêcher son développement .When passing through the resonant speed, that is to say essentially when starting and stopping the internal combustion engine, the torque and the energy transmitted to the second flywheel 14 suddenly increase, which is reflected by a rotation of the steering wheel 14 relative to the steering wheel 10 in a determined direction. As a result of this rotation, the rollers 28 carried by the arms 18 roll on the profile of the cam 32 to the aforementioned vertices 44, then pass these vertices and roll on the adjacent parts 42 of the cam profile, and so on, the relative rotation between the flywheels is not limited. The restoring forces developed by the springs 22 first increase during this relative rotation, until the rollers 28 pass the vertices 44 of the cam profile, then decrease and increase again until the rollers 28 pass on the following vertices 44 of the cam profile and so on. These restoring forces are therefore first in phase with the resonance phenomenon and then in phase opposition, which makes it possible to very effectively dampen the resonance phenomenon and to prevent its development.

On peut par exemple déterminer le profil de came et les caractéristiques des ressorts 22 pour que le couple transmissible entre les volants quand les galets 28 arrivent sur les sommets 44 du profil de came, soit sensiblement égal à 1,5 fois environ le couple maximum produit par le moteur en fonctionnement normal, alors que le couple de rotation à la résonance peut atteindre dix fois cette valeur.One can for example determine the cam profile and the characteristics of the springs 22 so that the transmissible torque between the flywheels when the rollers 28 arrive on the vertices 44 of the cam profile, is substantially equal to approximately 1.5 times the maximum torque produced by the motor in normal operation, while the torque at resonance can reach ten times this value.

Bien entendu, des moyens de friction agencés entre les volants 10 et 14 et/ou entre les moyens d'entrée et de sortie de l'amortisseur de torsion, non représentés en figures 1 et 2 peuvent être prévus pour amortir les rotations relatives des deux volants qui sont absorbées par les ressorts 22, notamment à la résonance .Of course, friction means arranged between the flywheels 10 and 14 and / or between the input and output means of the torsion damper, not shown in Figures 1 and 2 may be provided to dampen the relative rotations of the two flywheels which are absorbed by the springs 22, in particular at resonance.

On peut donner aux lobes 42 du profil extérieur de la came 32 toute forme voulue correspondant à une progressivité désirée de la compression des ressorts 22. On peut ainsi faire varier de façon non linéaire la compression de ces ressorts en fonction des débattements angulaires entre les volants, et on peut déterminer des variations différentes de ces compressions dans un sens de rotation et dans le sens opposé .The lobes 42 of the external profile of the cam 32 can be given any desired shape corresponding to a desired progressiveness of the compression of the springs 22. It is thus possible to vary the compression of these springs in a non-linear fashion as a function of the angular deflections between the flywheels , and we can determine different variations of these compressions in one direction of rotation and in the opposite direction.

Dans l'exemple représenté, le débattement angulaire, utilisable pour l'amortissement de torsion en fonctionnement normal (en dehors de la résonance) est un peu inférieur à 45° de part et d'autre d'une position de repos, ce débattement angulaire étant déterminé par le nombre de galets 28 et de bras 18.In the example shown, the angular movement, usable for torsional damping in normal operation (outside the resonance) is a little less than 45 ° on either side of a rest position, this angular movement being determined by the number of rollers 28 and arms 18.

Avec un dispositif selon l'invention comprenant trois galets 28 et trois bras 18, le débattement angulaire pour l'amortissement des vibrations en fonctionnement normal serait d'environ de 60° de part et d'autre d'une position de repos, en dehors de la résonance . Avec deux galets 28 et deux bras 18 diamétralement opposés, ce débattement angulaire pourrait atteindre 90° de part et d'autre d'une position de repos.With a device according to the invention comprising three rollers 28 and three arms 18, the angular clearance for damping vibrations in normal operation would be approximately 60 ° on either side of a rest position, outside of resonance. With two rollers 28 and two diametrically opposite arms 18, this angular movement could reach 90 ° on either side of a rest position.

Un avantage du mode de réalisation des figures 1 et 2 est que les bras 18, du fait de leur montage sur un axe de pivotement dans une zone approximativement médiane de ces bras, sont peu sensibles à la force centrifuge. On peut avantageusement prévoir que l'effet de la force centrifuge est plus important sur la partie du bras ne portant pas le galet 28, ce qui a pour résultat un maintien positif du galet sur la surface de came, en rotation.An advantage of the embodiment of FIGS. 1 and 2 is that the arms 18, due to their mounting on a pivot axis in an approximately median zone of these arms, are not very sensitive to the centrifugal force. It can advantageously be provided that the effect of the centrifugal force is greater on the part of the arm not carrying the roller 28, which results in a positive holding of the roller on the cam surface, in rotation.

Dans la variante de réalisation représentée très schématiquement et de façon partielle en figures 3 et 4, la came 32 est une pièce massive qui se trouve radialement à l'extérieur des galets 28 portés par les bras 18 et est montée sur le premier volant 10 qui est formé d'une tôle flexible, les bras 18 portant les galets 28 sont articulés par une extrémité autour d'axes 24 sur le second volant 14 et les ressorts 22 s'étendent plus ou moins radialement entre l'autre extrémité des bras 18 et la base des doigts 50 formés sur une plaque 52 solidaire du second volant d'inertie 14 et portant les axes 24 d'articulation des bras 18.In the variant embodiment shown very diagrammatically and partially in FIGS. 3 and 4, the cam 32 is a solid part which is located radially outside the rollers 28 carried by the arms 18 and is mounted on the first flywheel 10 which is formed of a flexible sheet, the arms 18 carrying the rollers 28 are articulated by one end around axes 24 on the second flywheel 14 and the springs 22 extend more or less radially between the other end of the arms 18 and the base of the fingers 50 formed on a plate 52 secured to the second flywheel 14 and carrying the axes 24 of articulation of the arms 18.

Dans cette variante de réalisation, chaque galet 28 roule sur un profil intérieur de came comportant des lobes 42 de forme arrondie concave reliés entre eux par des sommets 44 qui font saillie radialement vers l'axe de rotation des volants.In this variant embodiment, each roller 28 rolls on an internal cam profile comprising lobes 42 of concave rounded shape connected together by vertices 44 which project radially towards the axis of rotation of the flywheels.

Pour réduire le poids et donc la sensibilité à la force centrifuge, les bras 18 sont réalisés en tôle emboutie et ont une section transversale sensiblement en U. Les galets 28 sont montés sur des roulements à billes ou à aiguilles. Les axes 24 d'articulation des extrémités des bras 18 transmettent le couple moteur mais ne sont pas soumis aux efforts exercés par les ressorts 22 et sont peu sensibles à la force centrifuge. On remarquera aussi que, quand les galets 28 sont radialement à l'intérieur de la surface de came, la force centrifuge s'ajoute à la raideur des ressorts agissant sur les bras 18, de sorte que le couple de rappel des volants augmente avec la vitesse de rotation, ce qui est un avantage certain. Cela permet notamment d'avoir un couple de rappel plus faible aux bas régimes, ce qui est favorable à l'absorption des vibrations.To reduce the weight and therefore the sensitivity to centrifugal force, the arms 18 are made of pressed sheet metal and have a substantially U-shaped cross section. The rollers 28 are mounted on ball or needle bearings. The axes 24 of articulation of the ends of the arms 18 transmit the engine torque but are not subjected to the forces exerted by the springs 22 and are not very sensitive to the centrifugal force. It will also be noted that, when the rollers 28 are radially inside the cam surface, the centrifugal force is added to the stiffness of the springs acting on the arms 18, so that the return torque of the flywheels increases with the rotation speed, which is a definite advantage. This allows in particular to have a lower return torque at low revs, which is favorable to the absorption of vibrations.

On a représenté schématiquement en figure 4 des moyens de friction de l'amortisseur de torsion, qui comprennent une rondelle de friction 52 solidaire en rotation du second volant 14 et appliquée sur le premier volant 10 par une rondelle élastique 54 maintenue entre cette rondelle de friction 52 et une rondelle d'application 56 solidaire du premier volant 10.There is schematically shown in Figure 4 friction means of the torsion damper, which include a friction washer 52 integral in rotation with the second flywheel 14 and applied to the first flywheel 10 by an elastic washer 54 held between this friction washer 52 and a application washer 56 secured to the first flywheel 10.

Comme on le voit également en figure 4, l'amortisseur de torsion se trouve radialement à l'extérieur des vis 58 de fixation du premier volant 10 sur l'extrémité de l'arbre menant 60, ces vis de fixation 58 étant insérables et manoeuvrables à travers des orifices 59 du second volant 14.As can also be seen in FIG. 4, the torsion damper is located radially outside the screws 58 for fixing the first flywheel 10 on the end of the driving shaft 60, these fixing screws 58 being insertable and maneuverable through orifices 59 of the second flywheel 14.

Dans la forme de réalisation des figures 1 et 2 , la masse d'inertie du premier volant est formée par de la matière disposée aux endroits disponibles, c'est-à-dire en périphérie du premier volant comme indiqué en 64 entre les bras 18 portant les galets 28. Dans la variante de réalisation des figures 3 et 4, la masse d'inertie du premier volant est formée par la came 32 qui est fixée en périphérie de la tôle flexible 10 de liaison à l'arbre menant 60.In the embodiment of FIGS. 1 and 2, the mass of inertia of the first flywheel is formed by material arranged in the available places, that is to say on the periphery of the first flywheel as indicated at 64 between the arms 18 carrying the rollers 28. In the alternative embodiment of FIGS. 3 and 4, the mass of inertia of the first flywheel is formed by the cam 32 which is fixed at the periphery of the flexible sheet 10 for connection to the driving shaft 60.

Dans la forme de réalisation des figures 5 et 6, la came 32 est formée d'une tôle emboutie dont la partie périphérique radialement interne est fixée sur l'arbre menant 60 par les vis 58 et dont la périphérie radialement externe est fixée par des rivets 66 sur une masse d'inertie 68 de forme annulaire portant la couronne de démarreur 12. Les galets 28 portés par les bras 18 sont radialement à l'intérieur de la came 32 et roulent sur le profil interne de celle-ci. Les bras 18 sont formés par des languettes de flexion dont une extrémité est fixée à la façon d'un encastrement sur une plaque 70 solidaire du second volant d'inertie 14. L'autre extrémité des languettes de flexion est fixée sur une chape 72 de support du galet 28 par l'intermédiaire d'un roulement. La partie radialement interne de la chape 72 est en appui sur une lame de ressort 74 dont une extrémité est fixée sur la plaque 70 par les moyens de fixation des languettes 18 et dont l'autre extrémité est en appui glissant sur un bossage 76 de la plaque 70, ce bossage étant de préférence traité pour réduire l'usure.In the embodiment of FIGS. 5 and 6, the cam 32 is formed from a stamped sheet metal whose radially internal peripheral part is fixed to the driving shaft 60 by the screws 58 and whose radially external periphery is fixed by rivets 66 on an inertial mass 68 of annular shape carrying the starter ring 12. The rollers 28 carried by the arms 18 are radially inside the cam 32 and roll on the internal profile of the latter. The arms 18 are formed by bending tabs, one end of which is fixed in the manner of embedding on a plate 70 integral with the second flywheel 14. The other end of the bending tabs is fixed on a yoke 72 of support of the roller 28 by means of a bearing. The radially internal part of the yoke 72 is supported on a spring leaf 74 whose one end is fixed to the plate 70 by the means for fixing the tongues 18 and the other end of which is in sliding support on a boss 76 of the plate 70, this boss being preferably treated to reduce wear.

Comme dans les modes de réalisation précédents, le profil interne de la came 32 comporte des lobes arrondis 42 qui sont reliés par des sommets 44.As in the previous embodiments, the internal profile of the cam 32 has rounded lobes 42 which are connected by vertices 44.

Le fonctionnement de la forme de réalisation des figures 5 et 6 est sensiblement identique à celui déjà décrit. On peut aussi noter que l'utilisation de lames de flexion à la place des ressorts hélicoïdaux 22 des figures 1 à 4 évite les problèmes de guidage de ces ressorts hélicoïdaux soumis à la force centrifuge. Par ailleurs, les lames de ressort 74 ont avantageusement une double courbure, concave vers l'extérieur à leur extrémité de fixation et convexe vers l'extérieur à leur extrémité opposée, ce qui permet un taux de travail plus élevé de ces lames et des sollicitations en flexion mieux réparties.The operation of the embodiment of Figures 5 and 6 is substantially identical to that already described. It can also be noted that the use of bending blades in place of the helical springs 22 of FIGS. 1 to 4 avoids the problems of guiding these helical springs subjected to the centrifugal force. Furthermore, the spring blades 74 advantageously have a double curvature, concave towards the outside at their fixing end and convex towards the outside at their opposite end, which allows a higher working rate of these blades and the stresses in bending better distributed.

Dans la forme de réalisation représentée schématiquement aux figures 7 et 8, on retrouve sensiblement le montage de la figure 3, c'est-à-dire que les galets 28 sont portés par des bras 18 montés et articulés sur l'un des volants autour d'axes 24 parallèles à l'axe de rotation, et roulent sur un profil intérieur d'une came 32 portée par l'autre volant d'inertie. Toutefois, dans la forme de réalisation des figures 7 et 8, les moyens de rappel élastique sont formés par des anneaux 78 en acier à ressort qui sont montés flottants autour de l'axe de rotation entre les bras 18, et qui ont une forme initiale sensiblement circulaire, mais qui sont radialement comprimés vers l'axe de rotation par les bras 18, comme représenté schématiquement en figure 8.In the embodiment shown schematically in Figures 7 and 8, we find substantially the assembly of Figure 3, that is to say that the rollers 28 are carried by arms 18 mounted and articulated on one of the flywheels around axes 24 parallel to the axis of rotation, and roll on an inner profile of a cam 32 carried by the other flywheel. However, in the embodiment of FIGS. 7 and 8, the elastic return means are formed by rings 78 made of spring steel which are mounted floating around the axis of rotation between the arms 18, and which have an initial shape substantially circular, but which are radially compressed towards the axis of rotation by the arm 18, as shown diagrammatically in FIG. 8.

Par exemple, chaque bras 18 comporte des pattes 80 orientées radialement vers l'axe de rotation et qui s'étendent de part et d'autre des anneaux à ressort 78 pour les maintenir en place.For example, each arm 18 has tabs 80 oriented radially towards the axis of rotation and which extend on either side of the spring rings 78 to hold them in place.

Dans la variante de réalisation représentée aux figures 9 et 10, les galets 28 roulent sur un profil interne de came comportant des lobes 42 et des sommets 44 comme déjà décrit, et sont montés au moyen de chapes 72 correspondant sensiblement à celles des figures 5 et 6 sur l'extrémité de bras de flexion 18 qui sont du type isocontrainte et qui sont formés par superposition de lames de flexion 82 de longueur différente, fixées ensemble par encastrement ou analogue sur une plaque 84 solidaire d'un des volants d' inertie .In the alternative embodiment shown in FIGS. 9 and 10, the rollers 28 roll on an internal cam profile comprising lobes 42 and vertices 44 as already described, and are mounted by means of yokes 72 corresponding substantially to those of FIGS. 5 and 6 on the end of the flexion arms 18 which are of the isostress type and which are formed by superposition of flexion blades 82 of different length, fixed together by embedding or the like on a plate 84 secured to one of the flywheels.

Un avantage des double-volants amortisseurs décrits dans ce qui précède est que le système de came et de bras portant les galets suiveurs de came se trouve radialement à l'extérieur des vis de fixation du premier volant d'inertie 10 sur l'arbre moteur, de sorte que le nombre de bras et de galets est totalement indépendant du nombre de vis de fixation sur l'arbre moteur et peut être choisi à volonté .An advantage of the double-damping dampers described in the above is that the cam and arm system carrying the cam follower rollers is located radially outside the fixing screws of the first flywheel 10 on the motor shaft , so that the number of arms and rollers is completely independent of the number of fixing screws on the motor shaft and can be chosen at will.

De plus, les structures des amortisseurs de torsion décrits et représentés sont simples et relativement peu coûteuses et ne demandent pas de graissage.In addition, the structures of the torsion dampers described and shown are simple and relatively inexpensive and do not require lubrication.

Lorsque les ressorts de l'amortisseur de torsion sont des ressorts hélicoïdaux de compression, leur orientation peut être radiale ou sensiblement radiale, comme représenté, ou différente, cette orientation dépendant de la forme donnée aux bras 18. Comme déjà indiqué, la courbe de compression des ressorts de rappel peut être déterminée à volonté à partir de la forme du profil de came et peut être différente dans un sens de rotation et dans le sens opposé .When the springs of the torsion damper are helical compression springs, their orientation may be radial or substantially radial, as shown, or different, this orientation depending on the shape given to the arms 18. As already indicated, the compression curve of the return springs can be determined at will from the shape of the cam profile and can be different in one direction of rotation and in the opposite direction.

Par ailleurs, et comme représenté schématiquement en figure 4, l'amortisseur de torsion et notamment les surfaces de roulement des galets 28 peuvent être protégés de 1 ' encrassement par un déflecteur 88 s 'étendant le long du second volant d'inertie 14 entre celui-ci et la came 32 formant masse d'inertie portée par le volant flexible 10, le déflecteur 88 empêchant les particules de matériau provenant des garnitures du disque de friction 94 de venir entre les galets 28 et la surface de came, et des orifices 90 d'aération et d'évacuation des particules des matériaux de friction peuvent être formés dans le volant flexible 10 au niveau des moyens de friction 52, 54, 56 précités, pour évacuer ces particules à l'extérieur. Des orifices d'aération 92 peuvent être formés dans le second volant d'inertie 14, radialement à l'intérieur de la surface de friction de celui-ci.Furthermore, and as shown diagrammatically in FIG. 4, the torsional damper and in particular the rolling surfaces of the rollers 28 can be protected from fouling by a deflector 88 extending along the second flywheel 14 between that -ci and the cam 32 forming a mass of inertia carried by the flexible flywheel 10, the deflector 88 preventing the particles of material coming from the linings of the friction disc 94 from coming between the rollers 28 and the cam surface, and orifices 90 aeration and evacuation of the particles of friction materials can be formed in the flexible flywheel 10 at the abovementioned friction means 52, 54, 56, in order to evacuate these particles outside. Ventilation holes 92 can be formed in the second flywheel 14, radially inside the friction surface thereof.

Dans le mode de réalisation de la figure 5, on peut former des trous 96 dans la partie cylindrique de la came 32, au voisinage des galets 28, pour évacuer à l'extérieur la poussière et les particules centrifugées vers la surface de came. In the embodiment of FIG. 5, holes 96 can be formed in the cylindrical part of the cam 32, in the vicinity of the rollers 28, in order to evacuate the dust and the centrifuged particles to the cam surface outside.

Claims

REVENDICATIONS 1 - Double-volant amortisseur, en particulier pour véhicule automobile, comprenant deux volants d'inertie (10, 14) coaxiaux dont le premier est entraîné en rotation par un arbre menant et dont le second est monté à rotation sur le premier, et des moyens amortisseurs de torsion comprenant des moyens d'entrée liés au premier volant, des moyens de sortie liés au second volant, des moyens de rappel élastiquement déformables exerçant sur les volants un couple de rappel, les moyens d'entrée et de sortie comprenant une came (32) portée par l'un des volants et au moins un suiveur de came (28) porté par l'autre des volants et astreint à suivre le profil de la came1 - Double damping flywheel, in particular for a motor vehicle, comprising two coaxial flywheels (10, 14), the first of which is driven in rotation by a driving shaft and the second of which is mounted for rotation on the first, and torsional damping means comprising input means linked to the first flywheel, output means linked to the second flywheel, elastically deformable return means exerting a return torque on the flywheels, the input and output means comprising a cam (32) carried by one of the flywheels and at least one cam follower (28) carried by the other of the flywheels and compelled to follow the profile of the cam (32) lors des rotations relatives entre les volants, le déplacement du suiveur de came (28) sur le profil de la came provoquant une déformation desdits moyens de rappel, le profil de la came s ' étendant autour de l'axe de rotation (26) du volant et comportant une première partie (42) correspondant à une déformation sensiblement nulle des moyens de rappel et des deuxième et troisième parties (44) situées de part et d'autre de la première partie et correspondant à des déformations maximales des moyens de rappel lors des rotations relatives entre les volants dans les deux sens de rotation, caractérisé en ce que le suiveur de came (28) est déplaçable sur le profil de came sur 360° autour de l'axe de rotation (26) des volants, son passage sur les deuxième et troisième parties (44) du profil de came limitant à des valeurs maximales prédéterminées le couple transmissible entre les volants. 2 - Double-volant amortisseur selon la revendication 1, caractérisé en ce que le suiveur de came (28) est déplaçable au-delà des deuxième et troisième parties (44) du profil de came sur des parties (42) du profil de came pour lesquelles les valeurs du couple de rappel exercé sur les volants (10, 14) sont inférieures aux valeurs atteintes quand le suiveur de came (28) est sur les deuxième et troisième parties (44) précitées du profil de came.(32) during the relative rotations between the flywheels, the displacement of the cam follower (28) on the profile of the cam causing a deformation of said return means, the profile of the cam extending around the axis of rotation ( 26) of the steering wheel and comprising a first part (42) corresponding to a substantially zero deformation of the return means and of the second and third parts (44) located on either side of the first part and corresponding to maximum deformations of the means return during relative rotations between the flywheels in both directions of rotation, characterized in that the cam follower (28) can be moved on the cam profile 360 ° around the axis of rotation (26) of the flywheels, its passage over the second and third parts (44) of the cam profile limiting the transmissible torque between the flywheels to predetermined maximum values. 2 - Double damping flywheel according to claim 1, characterized in that the cam follower (28) is displaceable beyond the second and third parts (44) of the cam profile on parts (42) of the cam profile for which the values of the restoring torque exerted on the flywheels (10, 14) are lower than the values reached when the cam follower (28) is on the aforementioned second and third parts (44) of the cam profile. 3 - Double-volant amortisseur selon la revendication 1 ou 2 , caractérisé en ce que le suiveur de came (28) est monté à rotation sur un bras (18) porté par ledit autre volant (10) et s ' étendant dans un plan perpendiculaire à l'axe de rotation (26) des volants.3 - Double damping flywheel according to claim 1 or 2, characterized in that the cam follower (28) is rotatably mounted on an arm (18) carried by said other flywheel (10) and extending in a perpendicular plane to the axis of rotation (26) of the flywheels. 4 - Double-volant amortisseur selon la revendication 3, caractérisé en ce qu'il comprend plusieurs suiveurs de came (28) , montés chacun sur un bras (18) précité et répartis angulairement de façon régulière autour de l'axe de rotation (26) .4 - Double damping flywheel according to claim 3, characterized in that it comprises several cam followers (28), each mounted on an aforementioned arm (18) and distributed angularly in a regular manner around the axis of rotation (26 ). 5 - Double-volant amortisseur selon la revendication 3 ou 4, caractérisé en ce que le ou chaque bras (18) est sensiblement rigide et est monté pivotant sur ledit autre volant autour d'un axe (24) parallèle à l'axe de rotation (26) des volants.5 - Double damping flywheel according to claim 3 or 4, characterized in that the or each arm (18) is substantially rigid and is pivotally mounted on said other flywheel about an axis (24) parallel to the axis of rotation (26) flounces. 6 - Double-volant amortisseur selon l'une des revendications 3 à 5, caractérisé en ce que les moyens de rappel comprennent au moins un ressort (22) agissant sur ledit bras (18) . 7 - Double-volant amortisseur selon l'une des revendications 4 à 6, caractérisé en ce que chaque ressort (22) des moyens de rappels est monté entre deux bras (18) portant des suiveurs de came (28) .6 - Double damping flywheel according to one of claims 3 to 5, characterized in that the return means comprise at least one spring (22) acting on said arm (18). 7 - Double damping flywheel according to one of claims 4 to 6, characterized in that each spring (22) of the return means is mounted between two arms (18) carrying cam followers (28). 8 - Double-volant amortisseur selon la revendication 6 ou 7 , caractérisé en ce que les ressorts (22) sont des ressorts de compression et sont orientés sensiblement radialement .8 - Double damping flywheel according to claim 6 or 7, characterized in that the springs (22) are compression springs and are oriented substantially radially. 9 - Double-volant amortisseur selon la revendication 7 ou 8, caractérisé en ce que chaque ressort (22) est guidé à ses extrémités sur des sièges (38, 40) des bras (18) précités.9 - Double damping flywheel according to claim 7 or 8, characterized in that each spring (22) is guided at its ends on seats (38, 40) of the arms (18) mentioned above. 10 - Double-volant amortisseur selon la revendication 9, caractérisé en ce que les sièges (40) des extrémités radialement internes des ressorts (22) comprennent des doigts de maintien (50) s 'étendant axialement à l'intérieur des ressorts (22) .10 - Double damping flywheel according to claim 9, characterized in that the seats (40) of the radially internal ends of the springs (22) comprise retaining fingers (50) extending axially inside the springs (22) . 11 - Double-volant amortisseur selon l'une des revendications 7 à 10, caractérisé en ce qu'au moins deux ressorts (22) sont associés à chaque bras (18) précité.11 - Double damping flywheel according to one of claims 7 to 10, characterized in that at least two springs (22) are associated with each aforementioned arm (18). 12 - Double-volant amortisseur selon l'une des revendications 4 à 11, caractérisé en ce que chaque bras (18) est réalisé en tôle.12 - Double damping flywheel according to one of claims 4 to 11, characterized in that each arm (18) is made of sheet metal. 13 - Double-volant amortisseur selon la revendication 6, caractérisé en ce que le ou chaque bras (18) précité est associé à au moins un ressort de rappel (74) travaillant en flexion. 14 - Double-volant amortisseur selon la revendication 13 caractérisé en ce que ledit ressort de rappel est un ressort à lame (74) dont une extrémité est fixée, en particulier par encastrement ou analogue, sur ledit autre volant.13 - Double damping flywheel according to claim 6, characterized in that the or each arm (18) mentioned above is associated with at least one return spring (74) working in bending. 14 - Double damping flywheel according to claim 13 characterized in that said return spring is a leaf spring (74) one end of which is fixed, in particular by embedding or the like, on said other flywheel. 15 - Double-volant amortisseur selon la revendication 14, caractérisé en ce que l'autre extrémité du ressort à lame (74) est en appui glissant sur un bossage (76) dudit autre volant.15 - Double damping flywheel according to claim 14, characterized in that the other end of the leaf spring (74) is in sliding support on a boss (76) of said other flywheel. 16 - Double-volant amortisseur selon la revendication 13, caractérisé en ce que ledit ressort de rappel comprend un ou plusieurs anneaux continus (78) montés flottants autour de l'axe de rotation entre les bras (18) des suiveurs de came.16 - Double damping flywheel according to claim 13, characterized in that said return spring comprises one or more continuous rings (78) mounted floating around the axis of rotation between the arms (18) of the cam followers. 17 - Double-volant amortisseur selon la revendication 3 ou 4 , caractérisé en ce que le ou chaque bras (18) est flexible et est fixé par une extrémité sur ledit autre volant .17 - Double damping flywheel according to claim 3 or 4, characterized in that the or each arm (18) is flexible and is fixed by one end to said other flywheel. 18 - Double-volant amortisseur selon la revendication 17, caractérisé en ce que le ou chaque bras (18) comprend un ressort à lame travaillant en flexion, dont une extrémité est fixée par encastrement ou analogue, sur ledit autre volant.18 - Double damping flywheel according to claim 17, characterized in that the or each arm (18) comprises a leaf spring working in bending, one end of which is fixed by embedding or the like, on said other flywheel. 19 - Double-volant amortisseur selon la revendication 18, caractérisé en ce que chaque ressort à lame comprend plusieurs lames (82) superposées de longueurs différentes formant un ressort du type isocontrainte. 20 - Double-volant amortisseur selon l'une des revendications précédentes, caractérisé en ce que le profil de came (32) se trouve radialement à l'intérieur du ou des suiveurs de came (28) .19 - Double damping flywheel according to claim 18, characterized in that each leaf spring comprises several blades (82) superimposed of different lengths forming a spring of the iso-stressed type. 20 - Double damping flywheel according to one of the preceding claims, characterized in that the cam profile (32) is located radially inside the cam follower (s) (28). 21 - Double-volant amortisseur selon l'une des revendications 1 à 19, caractérisé en ce que le profil de came (32) se trouve radialement à l'extérieur du ou des suiveurs de came (28) .21 - Double damping flywheel according to one of claims 1 to 19, characterized in that the cam profile (32) is located radially outside the cam follower (s) (28). 22 - Double-volant amortisseur selon l'une des revendications précédentes, caractérisé en ce que la came (32) est réalisée en tôle.22 - Double damping flywheel according to one of the preceding claims, characterized in that the cam (32) is made of sheet metal. 23 - Double-volant amortisseur selon l'une des revendications précédentes, caractérisé en ce que la came (32) et les bras (18) des suiveurs de came se trouvent radialement à l'extérieur des moyens (58) de fixation du premier volant.' (10) sur l'arbre menant (60) .23 - Double damping flywheel according to one of the preceding claims, characterized in that the cam (32) and the arms (18) of the cam followers are located radially outside the means (58) for fixing the first flywheel . ' (10) on the driving shaft (60). 24 - Double-volant amortisseur selon l'une des revendications précédentes, caractérisé en ce que la surface de came et les suiveurs de came (28) sont protégés de l'encrassement par un déflecteur (88) s 'étendant le long du second volant d'inertie (14) entre celui-ci et ladite came (32) .24 - Double damping flywheel according to one of the preceding claims, characterized in that the cam surface and the cam followers (28) are protected from fouling by a deflector (88) extending along the second flywheel of inertia (14) between the latter and said cam (32). 25 - Double-volant amortisseur selon l'une des revendications précédentes, caractérisé en ce que des trous (90, 92, 96) d'aération et d'évacuation des poussières sont formés dans les volants d'inertie et/ou dans la came (32) . 25 - Double damping flywheel according to one of the preceding claims, characterized in that holes (90, 92, 96) for ventilation and evacuation of dust are formed in the flywheels and / or in the cam (32).
PCT/FR2002/002860 2002-08-12 2002-08-12 Cam-driven damping double flywheel and cam follower for motor vehicle Ceased WO2004016968A1 (en)

Priority Applications (3)

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DE10297771T DE10297771T5 (en) 2002-08-12 2002-08-12 Dual mass flywheel damper with cams and cam followers, especially for motor vehicles
AU2002341046A AU2002341046A1 (en) 2002-08-12 2002-08-12 Cam-driven damping double flywheel and cam follower for motor vehicle
PCT/FR2002/002860 WO2004016968A1 (en) 2002-08-12 2002-08-12 Cam-driven damping double flywheel and cam follower for motor vehicle

Applications Claiming Priority (1)

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PCT/FR2002/002860 WO2004016968A1 (en) 2002-08-12 2002-08-12 Cam-driven damping double flywheel and cam follower for motor vehicle

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WO2008010052A3 (en) * 2006-07-18 2008-05-08 Toyota Motor Co Ltd Power transmission device
FR2938030A1 (en) * 2008-11-05 2010-05-07 Valeo Embrayages Torque transmission device for motor vehicle, has arm with end supported on guiding surface, where distance from guiding surface to rotational axis varies with angular displacement of hub and disk to cause elastic deformation of arm
DE102009007373A1 (en) 2009-02-04 2010-08-05 Magna Powertrain Ag & Co Kg Dual Mass Flywheel
US20100210365A1 (en) * 2007-09-10 2010-08-19 Magna Powertrain Ag & Co Kg Dual-mass flywheel
EP1998075A3 (en) * 2007-05-29 2010-08-25 LuK Lamellen und Kupplungsbau Beteiligungs KG Device for suppressing torsional oscillation
WO2011006264A1 (en) * 2009-07-16 2011-01-20 Magna Powertrain Inc. Dual mass flywheel with cam plate
FR3008152A1 (en) * 2013-07-08 2015-01-09 Valeo Embrayages DOUBLE FLYWHEEL DAMPER WITH IMPROVED AMORTIZATION MEANS
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