• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Damping device (1) for a vehicle propulsion chain, comprising: a support (2) movable in rotation around an axis (X), the support (2) comprising a housing (8) extending around said axis, the support comprising an edge (12) radially outwardly defining said housing (8), a plurality of masses (14) arranged in the housing (8) so as to succeed one another around said axis (X), and a plurality of elastic return members (17), each return member (17) being interposed between two adjacent masses (14) and extending between two ends (18), each end (18) being integral with one of the two masses (14).
    公开号:FR3018881A1
    申请号:FR1457245
    申请日:2014-07-25
    公开日:2015-09-25
    发明作者:Roel Verhoog
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a damping device for a vehicle propulsion chain. The invention is particularly, but not exclusively, intended to improve the filtering of torsional oscillations at the mechanical bridge of the propulsion system of the vehicle. The term "mechanical bridge" designates the location of the propulsion chain at which the shafts of the wheels, the shaft of the gearbox and a differential are located. It is known to use for this purpose damping devices, also called "drummers", comprising elements able to oscillate to achieve this filtering. This filtering, however, is not sufficiently stable over time and / or according to the temperature at which the device is subjected. In addition, the hysteresis to which the elements of the device are subjected during their oscillations degrades over time and / or according to the temperature. This hysteresis trajectory makes it possible to damp the vibrations at the two frequencies framing the resonant frequency of the drummer. There is a need to remedy all or some of the disadvantages mentioned above.
    [0002] The invention aims to meet this need and it succeeds, according to one of its aspects, using a damping device for a vehicle propulsion chain, comprising: a support movable in rotation around an axis, the support comprising a housing extending around said axis, the support comprising an edge delimiting radially outwardly said housing, a plurality of masses arranged in the housing so as to succeed each other around said axis, each mass comprising a contour radially outer facing radially opposite said edge of the support, and - a plurality of elastic return members, each elastic return member being interposed between two adjacent masses and extending between two ends, each end being integral with one of the two masses. At least one of: - masses, - return members, and - said edge of the support can be configured so that when one of the masses moves relative to the support due to a rotation of the support around the axis, this displacement corresponding for each integral end of the mass of one of the elastic return members associated with said mass to a displacement of an angular value measured from a position of said end in which the mass is at rest, said resilient return member exerts on this mass during this movement a force at least approximately proportional to said angular value associated with the displacement of said end integral with said mass. For the purposes of the present application, the relationship between the force exerted by the elastic return member and said angular displacement value is sufficiently close to a proportional relationship for the device to have a resonant frequency. The above relationship between force exerted by the elastic return member and angular value may be proportional. By modeling the masses of the device by a single mass and by modeling the elastic return members of the device by a single elastic return member, the single elastic return member may have a coefficient of stiffness of between 0.1 Nm / ° and 10 Nm / °, being for example equal to 1 Nm / ° to within 10%. The moment of inertia of the device can in this case be between 0.001 kg.m2 and 0.1 kg. m2, being for example equal to 0.01 kg.m2 to 10%. This coefficient of stiffness expressed in Nm / ° then corresponds to the coefficient of proportionality establishing the proportional relation mentioned above. Using the single-mass model and single elastic return member cited above, the stiffness coefficient of the single elastic return member may be greater than 1 N / mm, especially 10 N / mm. The rotational displacement of the support is caused by torsional oscillations to which the support is subjected. By virtue of this configuration of the device, the force exerted by each elastic return member on the corresponding mass may be at least approximately proportional to the angular displacement of the integral end of this mass of each elastic return member. It is thus possible to obtain a damping device whose single resonant frequency remains stable over time, independently of the temperature. There is then a device, or drummer, with relatively stable filtering properties. The vehicle is for example a passenger vehicle with a four-cylinder engine. When this motor rotates at a speed of between 600 rpm and 2000 rpm, the frequency of the torsional oscillations that one seeks to filter using the device is in particular between 5 Hz and 20 Hz, being in particular of the order of 10 Hz or 15 Hz. The resonant frequency of the device is then between 5 Hz and 20 Hz, being in particular of the order of 10 Hz or 15 Hz. For the purposes of this application: - "radially "Means" in a plane perpendicular to the axis of rotation of the support and in a direction intersecting said axis of rotation ", -" axially "means" along a direction parallel to the axis of rotation of the support ", - "Angularly" means "around the axis of rotation of the support". - An end of the elastic return member is integral with a mass when it is directly or indirectly attached to the mass. - "resting position of a mass" means the position of that mass before the support moves in rotation due to torsional oscillations, - "angular value" means the angle measured from the axis of rotation of the support between two positions successively occupied by said end of the elastic return member secured to the mass during its movement relative to the support. Each mass can be made in one piece, being for example different from two mass parts secured together via connecting members, such as rivets for example. Each mass is for example entirely contained axially in the housing formed in the support.
    [0003] Each elastic return member may not be connected, directly or otherwise, to anything other than the two adjacent masses between which it is interposed. The only fasteners of each elastic return member to the outside are then those at each of its ends integral with one of the masses to which this elastic return member is associated. This avoids the use of the retaining piece of the prior art on which one end of an elastic return member is fixed, its other end being fixed to the ground. This improves the compactness of the device since it is no longer necessary to use this holding part. The elastic return member comprises for example several springs in parallel or in series The housing in which the masses are arranged may extend all around the axis. According to a first example of implementation of the invention, the device comprises a plurality of rolling members, two rolling members being associated with each mass and being interposed radially between said mass and said edge of the housing. Each rolling member, when moved by the rotation of the support, can transmit this displacement to the mass with which it is associated. Torque can thus be transmitted from the support to the masses via the rolling members. The damping device then behaves in a manner close to but different from that of a pendular system, such a system being well known to those skilled in the art for damping the torsional oscillations in vehicle transmission systems. According to this first example of implementation of the invention, the radially outer contour of each mass may comprise in said plane two concave portions defining rolling tracks for the rolling member on said mass, said contour also comprising in said plane. another concave portion disposed between the two raceways. These two concave portions defining the rolling tracks may have the same shape, for example in said plane, circular arcs of the same radius for these two concave portions. According to this first example of implementation of the invention, the edge delimiting radially outwardly the housing may have in said plane at each mass two concave portions defining rolling tracks for the running member on the support.
    [0004] These concave portions may be identical to each other. These are, for example, arcs of the same radius from one of these concave portions to the other. The rolling member may have a circular cross section, being then a cylinder also called "roll". This roller may or may not have rims protruding radially at each of its axial ends. Where appropriate, in said plane, the rolling tracks for the rolling member on the support and the rolling tracks for the rolling member on said mass may be circular arcs, and in a particular example, the ratio between the radius of the rolling tracks on the support and the radius of the rolling tracks on the mass is between 1/4 and 4.
    [0005] According to this first example of implementation, the rolling tracks on the mass and / or the rolling tracks on the support may have such shapes that when the mass oscillates from its rest position, the distance between the axis of rotation the support and each integral end of said mass of one of the elastic return members associated with said mass decreases. Still according to this first example of implementation, the rolling tracks on the mass and / or the rolling tracks on the support may have such shapes that when the mass oscillates from its rest position, each end secured to said mass of one of the elastic return members associated with said mass describes a spiral, in particular an Archimedean spiral. Such a configuration allows the relationship between the force exerted by the elastic return member and said angular displacement value to be exactly proportional. In such a case, greater stability of the resonance frequency of the device is ensured. According to this first example of implementation of the invention, the device may comprise a hysteresis generating system. This hysteresis generator then makes it possible to confer hysteresis on the displacement of the mass with respect to the support, when the support is subjected to torsional oscillations.
    [0006] According to this first example of implementation of the invention, each mass may be axially constrained when it is arranged in the housing, under the effect of axial retaining members, for example using springs. The means for obtaining this axial stress of the masses can form the hysteresis generating system mentioned above. The housing can be closed at both axial ends. One of the axial ends of the housing is for example closed by a bottom wall of the support while the other axial end of the housing can be closed by a cover attached to the support. When the housing is closed at its two axial ends, a spring can be disposed opposite each of these axial ends to axially maintain the mass in this housing. In the example just described, a spring is for example interposed functionally between the mass and the bottom wall of the support while another spring is interposed functionally between the mass and the cover. According to a second example of implementation of the invention, each elastic return member may comprise a spring, respectively several identical springs and, for two elastic return members associated with the same mass, the empty length of the spring, respectively the springs, of one of these return members may be chosen with respect to the empty length of the spring, respectively of the springs, of the other elastic return member so as to form a hysteresis generator. The two elastic return members associated with the same mass can thus be chosen so as to impart hysteresis to the movement of the mass relative to the support when the support is subjected to torsional oscillations. According to this second example of implementation of the invention, the radially outer contour of each mass may have in said plane two convex portions and a concave portion disposed between the two convex portions. The two convex portions each have the same shape, for example. It may be in said plane of circular arcs, in which case the rays may be equal from one convex portion to another. The concave portion is for example in said plane an arc of a circle. The ratio between the radius of the concave portion and the radius of the convex portions is in particular between 1 and 20. Still according to this second example of implementation of the invention, the radially outwardly delimiting edge of the housing may have in said plane to level of each mass two concave portions, the concave portions of said edge and the convex portions of said mass being configured to guide the movement of said mass. The shapes of said edge and of the radially outer contour of the masses can thus make it possible to obtain the at least approximately proportional relation mentioned above between the force exerted by the elastic return members on the mass and the angle at which the ends move. said elastic return members integral with this mass. Torque can thus be transmitted from the support to the masses via the cooperation between the concave portions of said edge and the convex portions of said mass. Where appropriate, each concave portion of said edge may be an arc in said plane. Each concave portion may then have the same radius and the ratio between this radius and that of the convex portions of the radially outer contour of the mass may be between 1 and 20. These concave portions of the edge according to the second embodiment of the invention. The invention may be identical to the concave portions of said edge according to the first example of implementation of the invention According to this second example of implementation of the invention, the concave portions of said edge and the convex portions of said mass may have forms such that, when the mass oscillates from its rest position, the distance between the axis of rotation of the support and each end integral with the mass of one of the return members associated with said mass decreases. In other words, during its oscillations from its rest position, the mass can then be closer to the axis of rotation of the support.
    [0007] The concave portions of said edge and the convex portions of said mass have for example shapes such that, when the mass oscillates from its rest position, each end integral with said mass of one of the return members associated with said mass describes a spiral, including an Archimedean spiral. In such a case, greater stability of the resonance frequency of the device is ensured. The at least approximately proportional relation mentioned above then becomes exactly proportional. According to this second example of implementation of the invention, the device is devoid of rolling member interposed radially between the mass and the edge of the housing. In all the above, the device can be arranged in parallel with the path taken by the couple during its transmission within the propulsion chain. The device "sees" for example only the torsional oscillations mentioned above. The invention further relates, in another of its aspects, a vehicle propulsion system comprising a device as defined above. In what follows, "upstream" and "downstream" are understood in relation to the direction of torque transmission from the engine of the vehicle to the wheels of the vehicle.
    [0008] The device can be placed upstream, especially directly upstream, of the mechanical bridge of the propulsion chain. In a variant, the device may be placed upstream, in particular directly upstream, of one of the wheels of the vehicle. In another variant, the device may be placed downstream, especially directly downstream, of the vehicle gearbox. In another variant, the device can be disposed both: downstream of an elastic return member connected to the primary flywheel, forming for example part of the heat engine, of the propulsion chain, and upstream of another elastic return member forming the input of the gearbox.
    [0009] The invention will be better understood on reading the following description of non-limiting examples of implementation thereof and on examining the appended drawing, in which: FIG. 1 is an exploded view of FIG. 1 is a front view of the device of FIG. 1; FIG. 3 is a sectional view along AA of the device of FIG. 2; FIG. 4 is a sectional view along C-C of the device of FIG. 2; FIG. 5 is a sectional view along BB of the device of FIG. 4; FIG. 6 is a partial view of the device represented in FIG. 2 when the masses have moved, and - Figure 7 is a view similar to Figure 2 of a device according to a second example of implementation of the invention. FIG. 1 shows a damping device 1 according to a first embodiment of the invention. This damping device 1 is in the example considered configured to allow filtering the torsional oscillations at the mechanical bridge of the propulsion chain of a vehicle. In the example considered, the vehicle is a passenger vehicle whose engine comprises four cylinders. In this example, the damping device may have a single resonance frequency of approximately 10 Hz for motor rotation speeds of between 600 rpm and 2000 rpm, this value being particularly suitable for the mechanical bridge. The device 1 comprises a support 2 movable in rotation about an axis X. This support 2 comprises in the example in a plane perpendicular to the X-axis a radially outer contour 3 substantially circular. The support 2 comprises in its center an empty zone 4 allowing the passage of a shaft of the propulsion chain. This empty zone 4 is formed inside a radially inner portion 6 of the support 2. A housing 8 is formed in the support 2, for example all around the axis X. This housing 8 extends here between the radially inner portion 6 of the support 2 and a radially outer portion 9 defined radially externally by the contour 3. In the example, the radially inner portion 6 and the radially outer portion 9 are made in one piece. These radially inner 6 and radially outer portions 9 are here connected by a bottom wall 10 which closes in the example considered one of the axial ends of the housing 8. The device 1 further comprises in the example considered a hood 11 to be assembled on the support 2, so as to seal the axial end of the housing 8 which is not closed by the bottom wall 10. The radially outer portion 9 has an edge 12 radially outwardly defining the housing 8. In the housing 8 is a plurality of masses 14. These masses succeed each other when moving in the housing 8 about the axis X. Each mass 14 has a radially outer contour 16 disposed radially facing the edge 12 of the support 2. Each mass 14 extends over a limited angular sector measured around the axis X, between two circumferential ends 15 of said mass 14. As can be seen in FIG. 1, first cavities 16 are formed in each mass 14 at each circumferential end 15. The cavities 16 formed in the circumferential ends 15 facing two adjacent masses 14 are opposite.
    [0010] In the example considered, each circumferential end 15 has two first cavities 16 which are superimposed along the X axis. Each of these first cavities 16 is here blind and extends from a circumferential end 15 towards the inside of the mass 14. on a limited angular sector measured around the axis X. From one circumferential end 15 to the other, the first cavities 16 do not communicate in the example illustrated between them.
    [0011] In a variant, each first cavity 16 at a circumferential end 15 of a mass communicates with the first corresponding cavity 16 formed at the other circumferential end 15 of this mass 14. As can also be seen in FIG. 1, each mass 14 has moreover in the example considered second cavities 13 formed in the axial end faces of said mass 14. Each of these second cavities 13 is here blind. In the example considered, each axial end face of a mass has only one second cavity 13. As shown in FIGS. 1 and 3, each second cavity 13 receives a spring 70 and a support element 71 comprising a hollow portion inside which is disposed the spring 70, the latter extending between an end fixed to the second cavity 13 and an end fixed to the support element 71. Each spring 70 allows to constrain axially the mass 14, so that the latter is held axially in the housing 8. The springs 70 thus allow the existence of an elastic restoring force between the mass 14 and the cover 11 while other springs 70 allow the existence of an elastic restoring force between the mass 14 and the bottom wall 10 of the housing 8. The device 1 also comprises a plurality of elastic return members 17. Each resilient return member 17 here comprises two identical springs interposed between two adjacent masses 14 and connecting these two masses 14. In the example, the two springs of the same elastic return member 17 are axially superimposed. Each spring 17 extends between two ends 18, each end 18 being integral with one of the two masses 14. In variants not shown, each elastic return member 17 comprises only one spring. As can be seen in FIG. 2, each spring 17 has: - a first end portion 75 disposed in a first cavity 16 of one of the two masses 14 with which it is associated, - a second end portion 76 arranged in a first cavity 16 of the other of the two masses 14 with which it is associated, and - a median portion 77, disposed between the first 75 and second 76 end portions and extending into the housing 8 outside the masses 14 .
    [0012] Each end 18 of the spring 17, terminating one of the first or second end portions 75 or 76 is for example fixed directly or not to the wall of the first cavity 16 corresponding, for example by crimping. In the example of FIG. 5, each end 18 of the spring 17 is indirectly attached to a mass 14 via a piece 77 attached to the wall of the first cavity 16.
    [0013] In the example considered, each spring 17 is connected to nothing other than the two masses 14 between which it is interposed. Each spring 17 is characterized by a coefficient of stiffness k and an idle length lo, also called "prestressing". The device 1 aims to transmit to the masses 14 the acyclic torque to which the support 2 is subjected, in the event of torsional oscillations applied to the support 2, so as to allow filtering of these torsional oscillations propagating in the propulsion chain. of the vehicle. For this purpose, the device 1 can be configured so that, when one of the masses 14 moves relative to the support 2 due to a rotation of the support 2 around the X axis caused by one of these oscillations, d an angular value 0 measured for each end 18 integral with the mass 14 of the springs of an elastic return member 17 associated with said mass, from a position of said end 18 corresponding to the rest state of said mass, each of these elastic return members 17 associated with this mass 14 exerts on this mass 14 during this displacement a force at least approximately proportional to this angular value O. FIG. 6, partially representing the device 1 of FIG. 2 after the masses 14 have moved relative to the support 2, to display the angle 0 traversed by the end 18 of the springs integral with said mass 14 from its position associated with the mass 14 at rest of the figure 2. In the example of FIGS. 1 to 6, the radially outer contour 16 of each mass 14 has in said plane three concave portions 20 separated in pairs by convex portions 21.
    [0014] Two of these concave portions 20, between which is disposed the other concave portion 20, define rolling tracks for rolling members 22 on the mass 14. The rolling members 22 are here rollers. Each concave portion 20 defining a track is for example a circular arc of the same radius R1, R1 being for example between 5 and 50 mm. In the example of FIGS. 1 to 6, the edge 12 radially outwardly defining the housing 8 has in said plane at each mass 14 two concave portions 30 and a convex portion 31 disposed between the concave portions 30. Each concave portion 30 is in the example considered a circular arc of the same radius R2. This radius R2 is for example between 12 and 120 mm. Still in the example considered, the convex portion 31 is also an arc of circle but of radius R3, for example between 1 and 100 mm.
    [0015] Each concave portion 30 of the contour 12 also defines a rolling track for one of the rolling members 22 on the support 2. Thus, each rolling member 22 is associated with: a rolling track on the mass, and a rolling track on the support 2, each running member 22 then moving in a space radially between the raceways on the support and on the mass with which it is associated. The shapes of the rolling tracks allow in this example that during the oscillations of the mass 14 due to the oscillations of the support 2, each end 18 directly or indirectly attached to said mass 14 of the springs 17 associated with said mass 14 approaches every oscillation of the X axis.
    [0016] These rolling tracks have for example shapes such that each of these ends 18 runs an Archimedean spiral during its oscillations from its rest position. In this case, each spring of an elastic return member 17 associated with a mass 14 exerts on the mass 14 during this oscillation a force at least approximately proportional to the angular value 0 mentioned above. The coefficient of proportionality between the force exerted by the single elastic return member modeling all of the elastic return members 17 of the device and the angular value for the single mass modeling all the masses 14 of the device can be between 0 , 1 Nm / ° and 10 Nm / °, being for example equal to 1 Nm / °, to 10%. A device 1 according to another embodiment of the invention will now be described with reference to FIG. This device 1 differs in particular from that which has just been described in that it lacks rolling members 22. This device 1 also aims to transmit to the masses 14 the acyclic torque to which the support 2 is subjected, so to allow filtering of torsional oscillations in the propulsion chain of the vehicle.
    [0017] For this purpose, for two elastic return members associated with the same mass 14, the empty length of the springs 17 of one of these two elastic return members may be chosen with respect to the empty length of the springs of the other resilient return member so that the movement of the mass 14 relative to the support 2 is done with hysteresis. Such a goal can also be achieved, in addition or not to the action exerted by the springs 17, the shapes of the edge 12 of the support 2 and the contour 16 of the masses 14. The latter can thus allow that, when a masses 14 moves relative to the support 2 due to a rotation of the support 2 caused by torsional oscillations in the propulsion chain, this corresponding displacement for each end 18 integral with the mass 14 of one of the return members elastic member 17 associated with said mass 14 at a displacement of an angular value θ measured from a position of said end 18 in which the mass 14 is at rest, said elastic return member 17 exerts on this mass 14 during this movement a force at less than approximately proportional to said angular value O. In the example of FIG. 7, the radially outer contour16 of each mass has in said plane two convex portions 40 and a portion concave 20 disposed between the two convex portions 40. The concave portion 20 is for example identical or not to the concave portion 20 of the example of Figures 1 to 6 which is flanked by the rolling tracks on the mass 14. In the For example, each convex portion 40 is an arc of the same radius R4. This radius is for example between 6 and 60 mm. Still in the example considered, the concave portion 20 is also a circular arc, but of radius R5, R5 being less than R4 and for example between 1 and 60 mm. In the example of FIG. 7, the edge 12 radially outwardly defining the housing 8 has in said plane at each mass 14 two concave portions 30 and a convex portion 31 disposed between the concave portions 30, similar to what has been described in reference to FIGS. 1 to 6. In this example, the convex portions 40 of the radially outer contour 16 of the masses 14 and the concave portions 30 of the edge 12 cooperate together to guide the displacement of the masses 14 when the support 2 moves in rotation around the axis X. The shapes of the portions 40 and 30, as well as the empty lengths of the springs of the elastic return members 17, can allow the displacement relative to the support 2 of each mass 14 to be done with hysteresis, and that each mass 14 is radially closer to the X axis as and when its oscillations. The portions 40 and 30 have particular shapes allowing that when the mass 14 moves, each end 18 secured to said mass 14 of one of the elastic return members 17 associated with said mass 14 describes a spiral, including an Archimedean spiral . The latter has for equation in polar coordinates p = ax19-kb The invention is not limited to the examples which have just been described. In particular, the device 1 can be disposed elsewhere in the propulsion chain of the vehicle. The expression "including one" shall be understood as synonymous with the expression "including at least one", except where the contrary is specified.
    权利要求:
    Claims (16)
    [0001]
    REVENDICATIONS1. A damping device (1) for a vehicle propulsion chain, comprising: - a support (2) movable in rotation about an axis (X), the support (2) comprising a housing (8) extending around said axis, the support comprising an edge (12) delimiting radially outwardly said housing (8), - a plurality of masses (14) arranged in the housing (8) so as to succeed each other around said axis (X), each mass (14) ) comprising a radially outer contour (16) arranged radially opposite said edge (12) of the support (2), and - a plurality of elastic return members (17), each return member (17) being interposed between two masses adjacent (14) and extending between two ends (18), each end (18) being integral with one of the two masses (14).
    [0002]
    2. Device according to claim 1, at least one: - masses (14), - return members (17), and - said edge (12) of the support (2) being configured so that when one of the masses (14) moves relative to the support (2) due to a rotation of the support (2) around the axis (X), this corresponding displacement for each end (18) integral with the mass (14). ) of one of the elastic return members (17) associated with said mass (14) to a displacement of an angular value (0) measured from a position of said end (18) in which the mass (14) is at rest , said elastic return member (17) exerts on this mass (14) during this displacement a force at least approximately proportional to said angular value (0) associated with the displacement of said end (18) integral with said mass (14).
    [0003]
    3. Device according to claim 1 or 2, each elastic return member (17) being connected to nothing other than the two adjacent masses (14) between which it is interposed.
    [0004]
    4. Device according to any one of claims 1 to 3, each elastic return member (17) comprising at least one spring, and for two elastic return members (17) associated with the same mass (14), the length to empty of the spring, respectively of the springs, of one of these elastic return members (17) being chosen with respect to the empty length of the spring, respectively of the springs, of the other elastic return member (17) so as to conferring hysteresis to the displacement of the mass (14) relative to the support (2).
    [0005]
    5. Device according to claim 4, the radially outer contour (16) of each mass (14) having in said plane two convex portions (40) and a concave portion (21) disposed between the two convex portions (40).
    [0006]
    6. Device according to claim 5, the edge (12) radially outwardly defining the housing (8) having in said plane at each mass (14) two concave portions (30), the concave portions (30) of said edge (12). ) and the convex portions (20) of said mass (14) being configured to guide the movement of said mass (14).
    [0007]
    7. Device according to claim 6, the concave portions (30) of said edge (12) and the convex portions (40) of said mass (14) having shapes such that, when the mass (14) oscillates from its rest position , the distance between the axis of rotation (X) of the support (2) and each end (18) integral with said mass (14) of one of the elastic return members (17) associated with said mass (14) decreases.
    [0008]
    8. Device according to claim 7, the concave portions (30) of said edge (12) and the convex portions (40) of said mass (14) having such shapes that, when the mass oscillates from its rest position, each end (18) integral with said mass (14) of one of the elastic return members (17) associated with said mass (14) describes a spiral, including an Archimedean spiral.
    [0009]
    9. Device according to any one of claims 1 to 3, further comprising a plurality of rolling members (22), two rolling members (22) being associated with each mass (14) and being interposed between said mass ( 14) and said edge (12) of the housing (8).
    [0010]
    10. Device according to claim 9, the radially outer contour (16) of each mass (14) comprising in said plane two concave portions (20) defining rolling tracks for the rolling member (22) on said mass (14). ), said contour (16) also comprising in said plane another concave portion (20) disposed between the two raceways.
    [0011]
    11. Device according to claim 10, the edge radially outwardly delimiting the housing having in said plane at each mass (14) two concave portions (30) defining rolling tracks for the rolling member (51). on the support.
    [0012]
    12. Device according to claim 11, the rolling tracks on the mass and / or the raceways on the support (2) having such shapes that when the mass (14) oscillates from its rest position, the distance between the axis of rotation (X) of the support (2) and each end (18) integral with said mass (14) of one of the elastic return members (17) associated with said mass (14) decreases.
    [0013]
    13. Device according to claim 12, the rolling tracks on the mass and / or the rolling tracks on the support having shapes such that when the mass oscillates from its rest position, each end (18) integral with said mass ( 14) of one of the elastic return members (17) associated with said mass (14) describes a spiral, in particular an Archimedean spiral.
    [0014]
    14. Device according to any one of claims 9 to 13, each mass (14) being axially constrained when it is disposed in the housing (8), under the effect of axial retaining members (70).
    [0015]
    15. Device according to any one of the preceding claims, the single elastic return member modeling all of the elastic return members (17) having a coefficient of stiffness greater than 1 N / mm, in particular 10 N / mm.
    [0016]
    16. A vehicle propulsion chain comprising a device (1) according to any one of the preceding claims.
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    FR3052520A1|2017-12-15|METHOD OF MAKING A PENDULUM DAMPING DEVICE
    FR3046647A1|2017-07-14|PENDULAR DAMPING DEVICE
    FR3059750B1|2019-11-29|PENDULAR DAMPING DEVICE
    同族专利:
    公开号 | 公开日
    WO2015140456A1|2015-09-24|
    FR3018881B1|2016-03-11|
    DE112015001362T5|2016-12-01|
    FR3018884A1|2015-09-25|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102004011830A1|2003-03-14|2004-09-23|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Torsional vibration damper for internal combustion engine, has rollers each arranged between outer and inner roller guide shells, and which movably support primary rotor that is connected to output shaft of internal combustion engine|
    WO2014005907A1|2012-07-06|2014-01-09|Schaeffler Technologies AG & Co. KG|Centrifugal pendulum|
    KR100422643B1|2001-06-15|2004-03-12|현대자동차주식회사|Flywheel for vehicles|DE102012025327B4|2012-12-22|2017-03-30|Audi Ag|Centrifugal pendulum device and drive train of a motor vehicle|
    FR3046649A1|2016-01-13|2017-07-14|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    FR3050499B1|2016-04-22|2018-09-21|Valeo Embrayages|PENDULAR DAMPING DEVICE|
    DE102017110022A1|2017-05-10|2018-11-15|Schaeffler Technologies AG & Co. KG|Centrifugal pendulum device with a biasing element for guiding the cylindrical rollers|
    FR3077609B1|2018-02-08|2021-02-19|Valeo Embrayages|PENDULUM CUSHIONING DEVICE|
    法律状态:
    2015-03-31| PLFP| Fee payment|Year of fee payment: 2 |
    2016-03-31| PLFP| Fee payment|Year of fee payment: 3 |
    2017-07-31| PLFP| Fee payment|Year of fee payment: 4 |
    2018-07-27| PLFP| Fee payment|Year of fee payment: 5 |
    2019-07-31| PLFP| Fee payment|Year of fee payment: 6 |
    2020-07-31| PLFP| Fee payment|Year of fee payment: 7 |
    2021-07-29| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1452306A|FR3018884A1|2014-03-20|2014-03-20|DAMPING DEVICE FOR VEHICLE PROPULSION CHAIN|
    FR1457245A|FR3018881B1|2014-03-20|2014-07-25|DAMPING DEVICE FOR VEHICLE PROPULSION CHAIN|FR1457245A| FR3018881B1|2014-03-20|2014-07-25|DAMPING DEVICE FOR VEHICLE PROPULSION CHAIN|
    DE112015001362.8T| DE112015001362T5|2014-03-20|2015-03-16|Damping device for a drive train of a vehicle|
    PCT/FR2015/050635| WO2015140456A1|2014-03-20|2015-03-16|Damping device for drive chain of a vehicle|
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