• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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    • 专利摘要:
    The invention relates to a torque transmission device (1) for a motor vehicle transmission chain comprising: - a torque input element (2) and a torque output element (3) rotatable one of relative to each other about an axis of rotation X; resilient damping means comprising at least one elastic blade (14, 15) coupling the input element (2) and the output element (3) so as to allow a torque transmission with vibration damping between the input element (2) and the output element (3); and - a centrifugal mass torsion damper (35) comprising at least one mass of inertia (21) rotatably mounted in rotation on a support (13) integral in rotation with one of the input and output elements (2, 3).
    公开号:FR3031368A1
    申请号:FR1550118
    申请日:2015-01-07
    公开日:2016-07-08
    发明作者:Jerome Boulet；Daniel Fenioux
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] TECHNICAL FIELD The invention relates to the field of transmissions for a motor vehicle and relates more particularly to a torque transmission device, such as a double damping flywheel, capable of filtering motor acyclisms.
    [0002] BACKGROUND OF THE INVENTION An explosion engine exhibits, as a result of successive explosions in the engine cylinders, acyclisms whose frequency varies in particular as a function of the number of cylinders and the speed of rotation of the engine. In order to filter the vibrations generated by the acyclisms upstream of the gearbox, it is known to equip the vehicle transmissions with a torque transmission device comprising means for damping vibrations, such as a double steering wheel. damper (DVA). Otherwise, vibrations entering the gearbox would cause in operation shocks, noises or noise particularly undesirable.
    [0003] The double damping flywheels comprise a primary flywheel and a coaxial secondary flywheel, mobile in rotation relative to each other. The primary flywheel is intended to be attached to the crankshaft of a combustion engine. The secondary flywheel forms a reaction plate for cooperating with a clutch disc. The primary and secondary flywheels are coupled in rotation by resilient deformable members for transmitting torque and damping rotational acyclisms. The resilient deformable members are generally helical springs circumferentially disposed in an annular chamber which is formed in the primary flywheel. The coil springs are, on the one hand, in abutment against bearing zones carried by the primary flywheel, and, on the other hand, in support against radial tabs of an annular web which is fixed by rivets to the steering wheel. secondary. Thus, any rotation of one of said flywheels relative to the other causes compression of the springs which exerts a restoring force adapted to return said flywheels to a relative angular position of rest. Such a double damping flywheel is for example described in document FR2936290. In order to reduce the fuel consumption of combustion engines, the number of cylinders of the engines tends to decrease. However, the decrease in the number of cylinders is accompanied by an increase in the amplitude of the acyclisms. Moreover, in order to improve driving comfort, in particular by avoiding particularly undesirable noises or noise, it is constantly sought to increase the filtration performance of the vibration dampers. Therefore, in view of the aforementioned developments, damping dual flywheels of the prior art are not fully satisfactory. SUMMARY The invention aims to overcome these problems by providing a torque transmission device for effectively filtering vibrations. According to one embodiment, the invention provides a torque transmission device for a motor vehicle transmission chain comprising: - a torque input member and a torque output member rotatable relative to one another; at the other around an axis of rotation X; resilient damping means coupling the input element and the output element so as to allow torque transmission with vibration damping between the input element and the output element, this transmission of torque with damping being accompanied by a relative rotation between the input member and the output member; the elastic damping means comprising at least one resilient blade integral in rotation with one of the input and output elements and cooperating with a support element carried by the other of said input and output elements; the resilient blade being arranged such that, in a relative angular position between the input member and the output member different from a relative rest position, the bearing member exerts a bending force on the resilient blade producing a counteracting force of the resilient blade on the bearing member, said reaction force having a circumferential component adapted to bias said input and output members toward said relative rest position; and a centrifugal mass torsion damper comprising at least one mass of inertia rotatably mounted in rotation on a support integral in rotation with one of the input and output elements.
    [0004] Thus, such a torque transmission device combines resilient elastic blade damping means with a centrifugal mass torsion damper which provides filtration performance particularly advantageous acyclisms.
    [0005] According to other advantageous embodiments, such a torque transmission device may have one or more of the following characteristics: the or each mass of inertia is able to oscillate with respect to the support of the centrifugal mass torsion damper in a plane orthogonal to the axis of rotation X in response to irregularities of rotation of said support. the resilient blade has a cam surface and the support member has a cam follower arranged to cooperate with the cam surface. the cam follower is a roller rotatably mounted on said input or output member via a rolling bearing. the support element is arranged radially outside the elastic blade. Such an arrangement makes it possible to retain the elastic blade radially when it is subjected to centrifugal force. the elastic blade is arranged to deform in a plane perpendicular to the axis of rotation X. the cam surface extends over an angular opening greater than 30 °, in particular greater than 45 ° or 60 °, for example greater than 90 °. the cam surface has, when observed along the axis of rotation X, a substantially concave shape, this concavity being on the side of the axis of rotation. the centrifugal mass torsion damper is arranged axially between the input element and the output element, which makes it possible to protect the centrifugal mass torsion damper and to facilitate its implantation in the transmission chain. one of the input and output elements comprises an axial recess in which at least one at least one mass of inertia is housed. - The support of the torsion damper centrifugal mass is integral in rotation with the output element. Thus, the centrifugal mass torsion damper is all the more effective if it is disposed at the outlet of one or more damping stages, and as a result, it is subjected to a level of torsional excitations less important, which prevents it from saturating. the elastic damping means comprise an attachment part which is connected to the elastic blade and which is secured in rotation to one of the input or output elements so as to rotate said elastic blade to said element of entry or exit. - According to one embodiment, the resilient damping means comprise a plurality of resilient blades each cooperating with a bearing member and the fixing portion is an annular body connected to the plurality of resilient blades. - The annular body can be monobloc and the annular body and the elastic blades formed in one piece. according to another embodiment, the elastic damping means comprise a plurality of resilient blades which each cooperate with a support element and the attachment part comprises a plurality of separate fastening elements which are each connected to a respective elastic blade and independently attached to said input or output element. - When the elastic damping means comprise an even number of resilient blades, two for example, the blades of each pair are symmetrical with respect to the axis of rotation X which contributes to the balance of the torque transmission device. - The support of the centrifugal mass torsion damper is a separate part of the elastic damping means. the support is located axially between the elastic damping means and the input element or between the elastic damping means and the output element. - According to one embodiment, the resilient damping means comprise a fixing portion which is connected to the resilient blade and which is rotationally secured to the output member so as to rotate said resilient blade to said output member. and the attachment portion of the resilient damping means and the support of the centrifugal mass torsion damper are fixed to each other. - According to an advantageous embodiment, the fixing portion of the resilient damping means and the support of the centrifugal mass torsion damper are fixed to the output member by common fasteners. the support of the centrifugal mass torsion damper extends axially between the at least one resilient blade of the resilient damping means and the input member. according to one embodiment, the bearing element is arranged radially outside the elastic blade and the at least one mass of inertia is disposed at a radial distance from the X axis less than the radial distance between the bearing element and the axis X. - in one embodiment, the support element is arranged radially outside the elastic blade and the centrifugal mass torsion damper is disposed at a radial distance from the X axis less than the radial distance between the bearing element and the X axis. In other words, the centrifugal mass torsion damper is disposed radially inside the bearing radius of the bearing element. . in one embodiment, the support comprises a ring on which said at least one mass of inertia is mounted oscillating and a flange comprising a portion of radial orientation which is fixed against the fixing portion of the elastic damping means and a portion axial orientation which develops axially towards the input member from the radial orientation portion and carries said ring. according to one embodiment, when the support of the centrifugal mass torsion damper extends axially between the elastic blade of the elastic damping means and the input element, the input element may comprise an axial recess, in particular of annular shape, wherein is housed at least partially said at least one mass of inertia. according to embodiments, the output member has an inner portion and an outer portion that is axially offset from the inner portion in a direction opposite to the input member and the centrifugal mass torsion damper is at least partially disposed radially outside said inner portion. the centrifugal mass torsion damper is disposed axially between the outer portion of the output member and the input member. according to one embodiment, the output element comprises a skirt developing, from the inner portion to the outer portion of the output member, axially in a direction opposite to said input member and the support of the damper of centrifugal mass twist comprises a ring which is fixed, for example by fitting or crimping, on the skirt. the elastic damping means comprise a fastening portion which is connected to the elastic blade and which is fixed on the inner portion of the output member so as to rotationally fasten said elastic blade to said output member and the element support is carried by the input member radially outwardly of the elastic blade and at least a portion of the at least one mass of inertia of the centrifugal mass torsion damper is disposed substantially at the same radial distance from the X axis as the bearing element. in other embodiments, the elastic blade is rotationally secured to the input element. in this case, the support of the centrifugal mass torsion damper can be fixed on the output member and carry the support member cooperating with the elastic blade. according to an advantageous variant, the elastic damping means comprise a plurality of resilient blades each cooperating with a respective support element carried by the support of the centrifugal mass torsion damper and the centrifugal mass torsion damper comprises a plurality of masses of inertia which are distributed circumferentially between the support elements. according to an advantageous embodiment, the or each mass of inertia comprises two flanks extending axially on either side of the support, the two flanks being connected to one another by means of connecting struts which each pass through an associated opening in the support. - According to a first type of torque transmission device, the centrifugal mass torsion damper is a pendulum damper comprising a plurality of inertia masses evenly distributed on the support. - In the case of a pendular damper, the device comprises means for guiding the masses of inertia which comprise, for each mass of inertia, two rolling members which each cooperate with a first raceway carried by said mass of inertia and with a second runway carried by the support. - Each first raceway is formed on one of the connecting struts and each second raceway is formed by an outer edge of one of the passage openings of a connecting strut formed in the support. according to a second type of torque transmission device, the centrifugal mass torsion damper is an inertial drummer and the mass of inertia is rotatably coupled to the support by means of a plurality of elastic return members capable of generating a force to return the mass of inertia relative to the support in a relative position of equilibrium. the moment of inertia of the centrifugal mass and the stiffness of the set of elastic members are such that the centrifugal mass has a resonance frequency of between 12 Hz and 60 Hz, and preferably of 6 nm to 9 nm for an engine having n cylinders. Such a resonance frequency can in particular be used to filter the vibrations that appear around 1000 revolutions / min. - The torque transmission device may further comprise a friction assembly arranged to exert a friction resisting torque between the input element and the output element during a relative rotation between the element of input and the output element. - The torque transmission device is for example a double damping flywheel. In other words, the input element is a primary flywheel intended to be fixed at the end of a crankshaft and the output element is a secondary flywheel which is intended to form a reaction plate for a clutch device. - The centrifugal mass torsion damper is housed axially between the primary flywheel and the secondary flywheel of the double damping flywheel. - The elastic damping means are housed axially between the primary flywheel and the secondary flywheel.
    [0006] According to one embodiment, the invention also provides a motor vehicle comprising a torque transmission device mentioned above. BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following description of several particular embodiments of the invention, given only to illustrative and non-limiting, with reference to the accompanying drawings. FIG. 1 is a partial rear view of a double damping flywheel according to a first embodiment, in which the secondary flywheel is not shown in order to allow visualization of the resilient elastic damping means 15 and of the pendulum damper. - Figure 2 is a partial front perspective view of the double damping flywheel of Figure 1 in which the primary flywheel is not shown. - Figure 3 is a sectional view of the double damping flywheel of Figure 1 according to the plane - Figure 4 is a sectional view of a double damping flywheel according to a second embodiment. FIG. 5 is a sectional view along the plane VV of FIG. 4. FIG. 6 is a cut-away view illustrating in detail the support and the mass of inertia of the inertial mixer of the double damping flywheel of FIGS. 5. - Figure 7 is a sectional view of a double damping flywheel according to a third embodiment. - Figure 8 is a broken perspective view of the double damping flywheel 30 of Figure 7. - Figure 9 is a broken perspective view of a double damping flywheel according to a fourth embodiment. - Figure 10 is a sectional view of a double damping flywheel according to a fifth embodiment. - Figure 11 is a broken perspective view of the double damping flywheel of Figure 10. - Figure 12 is a broken perspective view of a double damping flywheel according to a sixth embodiment. FIG. 13 is a graph illustrating the amplitude of the accelerations representative of the acyclisms at the input of the gearbox as a function of the engine speed, for transmission chains equipped with different damping double flywheels. DETAILED DESCRIPTION OF EMBODIMENTS In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations will be used to designate, according to the definitions given in the description, elements of the torque transmission device. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the torque transmission device determining the "axial" orientation and, from the inside towards the outside away from said axis, the "Circumferential orientation" is directed orthogonally to the axis of the torque transmission device and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one element with respect to another, with reference to the X axis of rotation of the torque transmission device, an element close to the axis is thus referred to as internal as opposed to an outer member located radially peripherally. Furthermore, the terms "rear" AR and "front" AV are used to define the relative position of one element relative to another in the axial direction, an element intended to be placed close to the engine being designated by before and an element intended to be placed close to the gearbox being designated by the rear. With reference to FIG. 3, a double damping flywheel 1 comprising a primary flywheel 2 intended to be fixed at the end of a crankshaft of an internal combustion engine, not shown, and a steering wheel secondary inertia 3 which is centered and guided on the primary flywheel 2 by means of a bearing 4, such as a rolling bearing ball. The secondary flywheel 3 is intended to form the reaction plate of a clutch, not shown, connected to the input shaft of a gearbox. The primary flywheels 2 and secondary 3 are intended to be mounted movably about an axis of rotation X and are furthermore movable in rotation relative to each other about said axis X. The primary flywheel 2 comprises a radially inner hub 5 supporting the bearing 4, an annular portion 6 extending radially from the hub 5 and a cylindrical portion 7 extending axially rearwardly from the outer periphery of the annular portion 6. The primary flywheel 2 is provided with orifices for the passage of fastening screws 8, for fixing the primary flywheel 2 on the crankshaft of the engine. The primary flywheel 2 carries, on its outer periphery, a ring gear 9 for driving in rotation of the primary flywheel 2, using a starter.
    [0007] The secondary flywheel 3 comprises a flat annular surface 10, turned towards the rear, intended to form a bearing surface for a friction lining of a clutch disk, not shown. In other words, the secondary flywheel 3 is intended to form a reaction plate of a clutch device. The secondary flywheel 3 comprises, close to its outer edge, studs 11 and orifices, not shown, for mounting a cover of the clutch device. In relation with FIG. 1, resilient damping means are observed coupling the primary flywheel 2 and the secondary flywheel 3 so as to allow transmission of the vibration damping torque between the primary and secondary flywheels 3. damping elastics comprise a fixing portion 13 and two resilient blades 14, 15 curved around the axis of rotation X from the fixing portion 13. The two elastic strips 14, 15 are symmetrical to each other by relative to the axis of rotation X.
    [0008] In the embodiment shown, the fastening portion 13 is formed of two separate arcuate fasteners 45 which are respectively formed integrally with each other of the two resilient strips 14, 15. Each elastic blade is thus fixed independently. However, in an embodiment not shown, the fastening portion 13 may consist of an annular and monobloc central body which is formed in one piece with, for example two elastic blades 14, 15. As shown on the part In FIG. 3, the fixing portion 13 is fixed on the secondary flywheel 3. To do this, the attachment portion 13 is provided with a plurality of circumferentially distributed orifices 16 allowing the passage of rivets 17 passing through. 3. Returning to FIG. 1, it can be seen that each elastic blade 14, 15 has a cam surface which is arranged to cooperate with a bearing element formed by a cam follower 22 carried by the primary flywheel 2. The cam followers 22 are here rollers 23 mounted rotatably on the primary flywheel 2. The cam followers 22 are held in abutment against their respective cam surfaces and are arranged for rolling against the said cam surface during relative movement between the primary and secondary flywheels 3. Furthermore, the cam followers 22 are arranged radially outside their respective cam surfaces so as to hold the blades radially. elastic members 14, 15 when subjected to centrifugal force. Each cam surface is arranged such that, for relative rotation between the primary flywheel 2 and the secondary flywheel 3 in one direction or the other, relative to a relative angular position of rest, the cam follower 22 moves on the cam surface and, in doing so, exerts a bending force on the resilient blade 14, 15. By reaction, the resilient blade 14, 15 exerts on the cam follower 22 a restoring force having a circumferential component which tends to return the primary flywheels 2 and secondary 3 to their relative angular position of rest. Thus, the resilient blades 14, 15 are capable of transmitting a driving torque from the primary flywheel 2 to the secondary flywheel 3 (forward direction) and a resistant torque of the secondary flywheel 3 to the primary flywheel 2 (retro direction). Furthermore, the torsional vibrations and the irregularities of torque which are produced by the motor and transmitted by the crankshaft to the primary flywheel 2 are damped by the flexion of the elastic blades 14, 15. In order to reduce the parasitic friction that may occur. assign the damping function, the rollers 23 are advantageously rotatably mounted on the primary flywheel 2 by means of rolling members 24, such as balls, rollers or needles. In the embodiment shown in Figure 3, the rollers 23 are each carried by a cylindrical rod 25 extending parallel to the axis of rotation X and an end of which is fixed inside a bore 26 formed in the primary flywheel 2. On the other hand, the cylindrical rod 25 is received inside a through-orifice formed in a sleeve 27. The cylindrical rod 25 comprises, forwards, a head 28 which rests against a countersink formed in the face rear of the sleeve 27. The roller 23 is rotatably mounted around the sleeve 27. To do this, the rolling members 24 cooperate, on the one hand, with a raceway formed on the outer periphery of the sleeve 27 and, d on the other hand, with a rolling track formed on the inner periphery of the roller 23. The rolling members are retained axially and protected, forwards, by a protective washer 29 fitted on the sleeve 27 and, rearwardly , pa r a shoulder 30 formed at the rear end of the sleeve 27.
    [0009] The sleeve 27 also carries a seat ring 31 which is mounted tightly around the sleeve 27. The seat ring 31 is axially bearing against the primary flywheel 2. In addition, the seat ring 31 cooperates with a surface of external restraint formed in the cylindrical portion 7 of the primary flywheel 2. The radial forces supported by the cam followers 22 are thus taken up by the primary flywheel 2 on a large axial dimension which limits the risk of deformation of the cylindrical rod 25. The double damping flywheel 1 may also be equipped with a friction assembly 32, shown in Figure 3, arranged to exert a friction-resistant torque during the relative rotation between the primary flywheel 2 and secondary 3.
    [0010] The friction assembly is thus able to dissipate by friction the energy accumulated in the elastic blades 14, 15. Furthermore, in connection with FIGS. 2 and 3, it can be seen that the double damping flywheel 1 is also equipped with a centrifugal mass torsion damper 35 of the pendulum damping type. The pendulum damper comprises a plurality of masses of inertia 21, also called pendulum weights, circumferentially distributed on a support 33. The pendulum weights 21 are able to oscillate relative to the support 33 in a plane orthogonal to the axis of rotation X in response to irregularities of rotation.
    [0011] The pendulum weights 21 have a general shape of an arc of a circle. Each pendulum weight 21 comprises two flanks 38, 39 which extend axially on either side of the support 33 and are connected axially to one another by means of two connecting struts 40. To do this, each flank 38, 39 has two cuts intended for mounting by force-fitting the connecting struts 40. Moreover, each connecting strut 40 passes axially through an opening in the support 33. The oscillations of the counterweight 21 are guided by means guidance. The guide means comprise, for each flyweight 21, two rolling elements 41 which each cooperate with a first rolling track carried by the pendulum 21 and with a second rolling track, carried by the support 33. For each element of bearing 41, the first and second raceways are arranged radially facing each other.
    [0012] In relation with the lower part of FIG. 3, it is observed that the first race tracks are carried by the connecting spacer 40 connecting the sidewalls 38, 39 of each counterweight 21 and that the second raceways are formed. by the outer edge of the passage openings of the connecting struts 40. The rolling element 41 is, for example, formed by a cylindrical roller of circular section. The first and second race tracks have a generally epicyclic or circular shape. The shapes of the rolling tracks are arranged in such a way that the pendulum weights 21 are tuned to an order taking a value close to the rank of the predominant harmonic vibrations generated by the engine. A motor operating with 2n cylinders generating primarily harmonic rank n the pendulum damper must be granted to an order taking a value close to n to dampen the main vibrations. The pendulum weights 21 and / or the support 33 may comprise abutment elements of elastomeric material for damping shocks, when the pendulum weights 21 arrive at the end of the stroke or when the engine is stopped. As represented in FIG. 3, the support 33 comprises a flange 34 which comprises a radially oriented portion 34a which is fixed against the attachment portion 13 of the elastic damping means and an axially oriented portion 34b which extends axially towards the primary flywheel 2 from the outer periphery of the radially oriented portion 34a. The flange 34 is fixed on the secondary flywheel 3 by means of the fasteners which secure the attachment portion 13 of the elastic damping means, namely the rivets 17.
    [0013] To do this, the radial orientation portion 34a of the flange 34 is equipped with a plurality of rivet passage orifices arranged opposite the orifices 16 formed in the fastening portion 13 of the resilient means. amortization. The support 33 further comprises a ring 36 in which are formed the passage orifices of the connecting struts 40 of the counterbalanced weights 21 and on either side of which are arranged the flanks 39, 39 of the counterweight 21. The ring 36 is attached to the radially oriented portion 34b of the flange 34 near its front end. The ring 36 is, for example, welded to the flange 34. Moreover, the annular portion 6 of the primary flywheel 1 has an annular axial recess 20 in which the forward flank 38 of the counterweight 21 is at least partially housed. the pendulum weights 21 are arranged axially between the resilient blades 14, 15 of elastic damping means and the primary flywheel 2. Moreover, the counterweight 21 are implanted at a radial distance from the X axis less than the radial distance implementation of the rollers 23 which provides a double damping flywheel 1 relatively compact. FIG. 13 illustrates the angular acceleration (in ordinate, expressed in rad / s2) of the input shaft of a gearbox representative of rotation acyclisms, as a function of the engine speed (in abscissa, expressed in revolutions / mn) for motor vehicle transmissions which are respectively equipped with: - a double damping flywheel whose elastic damping means are helical springs (Curve A); - A double damping flywheel whose elastic damping means are elastic blades (Curve B); and 30 - a double damping flywheel 1 whose elastic damping means are resilient blades 14, 15 and further comprising a pendular damper (Curve C).
    [0014] It can thus be seen that a double damping flywheel 1 as described above associating elastic damping means with elastic blades and a pendulum damping makes it possible to obtain vibration filtering performances which are much higher than those of the other damping double flywheels.
    [0015] Figures 4 to 6 illustrate a double damping flywheel 100 according to a second embodiment. Elements identical or similar to the elements of Figures 1 to 3, that is to say, fulfilling the same function, have the same reference numeral increased by 100. The general structure of the double damping flywheel 101 is identical to the structure of the one described in connection with Figures 1 to 3 and differs therefrom that the pendulum damper is replaced by an inertial drummer 135. An inertial drummer selectively filters the vibrations for a specific frequency range. FIGS. 5 and 6 show that the inertial drummer comprises a single mass of inertia 121 which is mounted oscillating on the support 2. The mass of inertia 121 comprises two annular flanks 138, 139 which extend from both sides. other of the ring 136 and which are connected to each other via a plurality of connecting struts 140 passing through openings 142 formed in the ring 136 of the support 133. The connecting struts 140 are received inside cutouts formed in the sidewalls 138, 139 and for securing the connecting struts 140 to said sidewalls 138, 139, by press fitting for example. The mass of inertia 121 of the inertial beater is rotatably coupled to the support 133 via a plurality of elastic members which here consist of helical springs 143, illustrated in FIGS. 5 and 6. The elastic members generate a restoring force which opposes the rotation of the mass of inertia 121 relative to its equilibrium position. The moment of inertia of the mass of inertia 121 as well as the stiffness of the set of elastic members are adjusted so that the resonant frequency of the inertial drummer corresponds to the frequency of the vibrations to be filtered. For example, the inertial drummer may have a resonance frequency between 12 Hz and 60 Hz, and preferably from 6n to 9n Hz for a motor having n cylinders. Such a resonance frequency can in particular be used to filter the vibrations that appear around 1000 revolutions / min. The support 133 comprises a plurality of windows 144 inside which the coil springs 143 are housed. The circumferential ends 146, 147 of the windows 144 thus form support seats intended to support the ends of the coil springs 143. Furthermore, each flank 138, 139 of the mass of inertia 121 comprises a plurality of cavities 148 each housing a helical spring 143. The cavities 148 are formed in the sides of the flanks 138, 139 facing the support 133 and are each in position. The cavities 148 have circumferential ends, not shown, which each form a bearing seat for one end of a coil spring 143. Thus, during a relative rotation of the mass of inertia 121 relative to the support 133 in a first direction of rotation, each coil spring 143 is compressed between a first end 146 of the 144 of the support 133 and between a first end of the cavities 148 formed in the flanks 138, 139 of the mass of inertia 121 while in a relative rotation of the mass of inertia 121 relative to the support 133 according to a second In the opposite direction of rotation, each helical spring 143 is compressed between a second end 147 of said window 144 and a second end of the cavities 148 of the sidewalls 138, 139. The coil springs 144 thus make it possible to return the mass of inertia 121 towards a position of equilibrium with respect to its support 133. It is observed on the curve D of FIG. 13, the angular acceleration of the input shaft of a gearbox representative of the rotational acyclisms, as a function of the engine speed for a motor vehicle transmission equipped with a double damping flywheel 101 whose elastic damping means are elastic blades 114, 115 and further comprising an iner drummer tial. It can thus be seen that a double damping flywheel 101 as described above associating elastic damping means with elastic blades and an inertial beater also makes it possible to obtain excellent vibration filtration performance. Figures 7 and 8 illustrate a double damping flywheel 201 according to a third embodiment. Elements identical or similar to the elements of Figures 1 to 3, that is to say, fulfilling the same function, have the same reference numeral increased by 200. In this embodiment, the secondary flywheel 203 has a radially internal portion 249, then called inner portion 249, and a radially outer portion 250, then called outer portion 250, offset axially rearwardly relative to the inner portion 249 and connected to said inner portion 249 via a skirt 251 As shown in the lower part of FIG. 7, the fastening portion 213 of the elastic damping means is fixed on the radially inner portion 249 of the secondary flywheel 203, by means of rivets 217 passing through orifices 216. of the fixing portion 213 of the elastic damping means and orifices formed in the secondary flywheel 203. The outer portion 250 carries the flat annular surface 2 10 for forming a bearing surface for a friction lining of a clutch disc. The skirt 251 develops axially rearward, that is to say in the direction opposite to the primary flywheel 202, from the inner portion 249 to the outer portion 250. Also, the axial offset of the outer portion 250 with respect to the inner portion 249 allows to provide an axial recess 220 in the secondary flywheel to allow the implantation of the centrifugal mass torsion damper 235, radially outside of the skirt 251.
    [0016] The centrifugal mass torsion damper 235 is here a pendulum damper having a structure substantially similar to that described with reference to FIGS. 1 to 3. However, the support 233 of the pendular damper is formed of a ring 236 which is fitted on the skirt 251. The ring 236 is fixed by crimping on the skirt 251. Such an embodiment has the advantage of allowing an arrangement of the pendulum weights 221 at a radial distance from the major axis X which allows 'increase their moment of inertia and, consequently, the efficiency of the pendulum damper. It can thus be seen in FIGS. 7 and 8 that part of the pendulum weights 251 extend at a radial distance from the axis X substantially equal to the distance between the axis of rotation of the rollers 223 on the primary flywheel 202 and the X axis. In other words, the counterbalanced weights 221 extend substantially on the same diameter as the rollers 223 and are arranged axially between the rollers 223 and the outer portion 250 of the secondary flywheel 203. FIG. 9 illustrates a double damping flywheel 301 according to a fourth embodiment. Elements identical or similar to the elements of Figures 1 to 3, bear the same reference numeral increased by 300 and elements identical or similar to the elements of Figures 4 to 6 bear the same reference numeral increased by 200. This double damping flywheel 301 differs from the previous embodiment of Figures 7 and 8 that the pendulum damper is replaced by an inertial drummer. The support 333 is formed of a ring 336 which is fixed by crimping on the skirt 351 of the secondary flywheel as in the embodiment of FIGS. 7 and 8. The mass of inertia 321 as well as the coil springs 343 each have a structure similar to that described in connection with FIGS. 4 to 6.
    [0017] Figures 10 and 11 illustrate a dual damping flywheel 401 according to a fifth embodiment. The elements that are identical or similar to the elements of FIGS. 1 to 3 bear the same reference number increased by 400. This embodiment differs in particular from the previous ones in that the resilient blades 414, 415 of the damping means are integral in rotation with the primary flywheel 402 while the cam follower 423 are movably mounted on a shaft 425 rotatably connected to the secondary flywheel 403. Also, in this embodiment, the attachment portion 413 of the elastic damping means is fixed on the primary flywheel 402. For this purpose, rivets 452 pass through orifices formed in the primary flywheel 402 and in the attachment portion 413 of the elastic means. The centrifugal mass torsion damper 435 is here a pendulum damper having a structure substantially similar to that described with reference to FIGS. 1 to 3. However, the support 433 of the pendular damper is formed of a ring 453 which is fitted on an inner portion 449 of the secondary flywheel 403. The ring 453 is attached to the secondary flywheel 403 by means of rivets 455, shown in FIG. 11, passing through the secondary flywheel 403 at a shoulder formed in an inner portion 449 of the secondary flywheel 403. through the holes in the secondary flywheel 403 and in the ring 453. The secondary flywheel 403 has an outer portion 450 in which 30 is formed the flat annular surface 210 for forming a bearing surface for a friction lining which is offset axially rearwardly relative to the inner portion 449. Such an axial offset allows to provide an axial recess 420 in the secondary flywheel 403 for allows The support 433 of the pendular damper 433 also carries the cam followers 423 cooperating with the elastic blades 414, 415.
    [0018] To do this, as shown in the upper part of Figure 10, the rollers 423 are carried by a cylindrical rod 425, here a rivet which extends parallel to the axis X and which passes through a bore formed in the support 433. As in the previous embodiments, the cylindrical rod 425 is received inside a sleeve 427 and the roller 423 is rotatably mounted on the sleeve 427 by means of rolling members 424. sleeve 427 also carries a seat ring 434 which is mounted tightly around the sleeve 427. The seat ring 434 is received in a recess 454 of complementary shape which is formed in the support 433 at the periphery of the passage opening. the cylindrical rod 425. Such an arrangement allows to take the radial forces exerted on the cam follower 423 on a sufficient axial dimension at the support 423 to limit the risk of deformation of the cylindrical rod 425. It can be observed in particular in FIG. 11 that the pendulum weights 421 are implanted at the same radial distance from the X axis as the cam followers 22. To do this, the pendulum weights 421 are distributed circumferentially between the support elements 422. Figure 12 illustrates a double damping flywheel according to a sixth embodiment. The elements that are identical or similar to the elements of FIGS. 1 to 3, FIGS. 4 to 6 and FIGS. 10 and 11 have the same reference number respectively increased by 500, 200 and 100. This double damping flywheel 501 does not differ from the previous embodiment, Figures 10 and 11, that in that the pendulum damper is replaced by an inertial drummer. The support 533 is thus formed of a ring 553 which is fixed on the secondary flywheel 503 and which carries the cam follower 523 cooperating with the elastic blades 514, 515. The inertia mass 521 and the helical springs 543 present as for them a structure similar to that described in relation with FIGS. 4 to 6. Although the invention has been described in connection with several particular embodiments, it is quite obvious that it is in no way limited thereto and that it includes all the technical equivalents of the means described and their combinations if they fall within the scope of the invention. The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set out in a claim. The use of the indefinite article "a" or "an" for an element or a step does not exclude, unless otherwise stated, the presence of a plurality of such elements or steps. In the claims, any reference sign in parentheses can not be interpreted as limiting the claim.
    权利要求:
    Claims (18)
    [0001]
    REVENDICATIONS1. Torque transmission device (1, 101, 201, 301, 401, 501) for a motor vehicle transmission chain comprising: - an input element (2, 102, 202, 302, 402, 502) of torque and a torque output member (3, 103, 203, 303, 403, 503) rotatable relative to each other about an axis of rotation X; resilient damping means coupling the input element and the output element so as to allow vibration-damped torque transmission between the input element and the output element, this transmission of torque with damping being accompanied by a relative rotation between the input member and the output member; the elastic damping means comprising at least one elastic blade (14, 15, 114, 115, 214, 215, 314, 315, 414, 415, 514, 515) integral in rotation with one of the input elements and and cooperating with a support member (22, 122, 222, 322, 422, 522) carried by the other 15 of said input and output members; the elastic blade being arranged such that, in a relative angular position between the input element and the output element different from a relative rest position, the support element exerts a bending force on the an elastic blade producing a counteracting force of the resilient blade on the support member, said reaction force having a circumferential component adapted to bias said input and output members towards said relative rest position; and a centrifugal mass torsion damper (35, 135, 235, 335, 435, 535) comprising at least one inertia mass (21, 121, 221, 321, 421, 521) rotatably mounted in rotation on a support (33, 133, 233, 333, 433, 533) integral in rotation with one of the input and output elements.
    [0002]
    Torque transmission device according to claim 1, wherein the centrifugal mass torsion damper (35, 135, 235, 335, 435, 535) is arranged axially between the input element and the centrifugal element. exit. 30
    [0003]
    A torque transmission device according to claim 1 or 2, wherein one of the input (2, 102) and output elements has an axial recess (20, 120, 220, 320, 420, 520) in which is at least partially housed said at least one mass of inertia (21, 121).
    [0004]
    4. Torque transmission device according to any one of claims 1 to 3, wherein the support (33, 133, 233, 333, 433, 533) is integral in rotation with the output element (3, 103, 203, 303, 403, 503).
    [0005]
    5. Transmission device according to claim 4, wherein the elastic damping means comprise a fastening portion (13, 113) which is connected to the elastic blade (14, 15, 114, 115) and which is secured in rotation to the output member (3, 103) so as to rotate said resilient blade to said output member and wherein the attachment portion (13, 113) of the resilient damping means and the support (33, 133 ) of the centrifugal mass torsion damper (35, 135) are fixed to each other.
    [0006]
    Transmission device according to claim 5, wherein the attachment portion (13, 113) of the resilient damping means and the support (33, 133) of the centrifugal mass torsion damper (35, 135) are attached to the output member (3, 103) by common fasteners (17, 117). 15
    [0007]
    Torque transmission device according to Claim 5 or 6, in which the support (33, 133) of the centrifugal mass torsion damper (35, 135) extends axially between the at least one elastic blade ( 14, 15, 114, 115) resilient damping means and the input member (2, 102).
    [0008]
    Torque transmission device according to one of Claims 4 to 7, in which the bearing element (22, 122) is arranged radially outside the spring blade (14, 15, 114, 115) and wherein the at least one mass of inertia (21, 121) is disposed at a radial distance from the X axis less than the radial distance between the support member and the X axis.
    [0009]
    The torque transmitting device according to claim 4, wherein the output member (203, 303, 403, 503) comprises an inner portion (249, 349, 449, 549) and an outer portion (250, 350). , 450, 550) which is axially offset from the inner portion (249, 349, 449, 549) in a direction opposite to the input member (202, 302, 402, 502) and wherein the damper Centrifugal mass torsion device (235, 335, 435, 535) is at least partially radially disposed outside said inner portion (249, 349, 449, 549) and axially between the outer portion (250, 350, 450). 550) of the output element (203, 303, 403, 503) and the input element (202, 32, 402, 502).
    [0010]
    A torque transmission device according to claim 9, wherein the output member (203, 303) has a skirt (251, 351) extending from the inner portion (249, 349) to the outer portion (250). , 350) of the output member (203, 303), axially in a direction opposite to said input member (202, 302) and wherein the support (233, 333) of the centrifugal mass torsion damper comprises a ring (236, 336) which is fixed to the skirt (251, 351).
    [0011]
    Torque transmission device according to claim 9 or 10, wherein the resilient damping means comprise a fixing portion (213, 313) which is connected to the elastic blade (214, 215, 314, 315) and which is fixed on the inner portion (249, 349) of the output member (203, 303) so as to rotationally secure said spring blade (214, 215, 314, 315) to said output member (203, 303) and the bearing element (222, 322) is carried by the inlet element (202, 302) radially outwardly of the elastic blade (214, 215, 314, 315) and in which at least a portion of the at least one mass of inertia (221, 321) of the centrifugal mass torsion damper (135, 235) is disposed at the same radial distance from the axis X as the bearing element (222). , 322).
    [0012]
    Torque transmission device according to any one of claims 1 to 3, wherein the elastic blade (414, 415, 514, 515) is secured in rotation to the input element (402, 502) and in wherein the support (433, 533) of the centrifugal mass torsion damper (435, 535) is attached to the output member (403, 503) and carries the supporting member (422, 522) cooperating with the elastic blade (414, 415, 514, 515).
    [0013]
    13. A torque transmission device according to claim 12, wherein the elastic damping means comprise a plurality of resilient blades (414, 415) each cooperating with a respective bearing element carried by the support (433) of the centrifugal mass torsion damper (435) and wherein the centrifugal mass torsion damper has a plurality of inertia masses (421) which are distributed circumferentially between the support members (422).
    [0014]
    Torque transmission device according to any one of claims 1 to 13, in which the or each mass of inertia (21, 121, 221, 321, 421, 521) comprises two flanks (38, 39, 138, 139, 238, 239, 338, 339, 438, 439, 538, 539) extending axially on either side of the support (33, 133, 233, 333, 433, 533), the two sides being connected to one another. to the other via connecting struts (40, 140, 240, 340, 440, 540) which each pass through an associated opening in the support.
    [0015]
    15. A cutting transmission device according to any one of claims 1 to 14, wherein the centrifugal mass torsion damper (35, 235, 435) is a pendulum damper having a plurality of inertia masses (21). , 221, 421) regularly distributed on the support (33, 233, 433).
    [0016]
    Torque transmission device according to any one of claims 1 to 14, wherein the centrifugal mass torsion damper (135, 335, 535) is an inertial drummer and the mass of inertia (121, 321 , 521) is rotatably coupled to the support (133, 333, 533) via a plurality of resilient members (143, 343, 543) for generating a force to return the mass of inertia by relative to the support in a relative position of equilibrium.
    [0017]
    A torque transmission device according to any one of claims 1 to 16, wherein the input member is a primary flywheel (2, 102, 202, 302, 402, 502) of a dual mass flywheel intended to be fixed at the end of a crankshaft and the output element is a secondary flywheel (3, 103, 203, 303, 403, 503) of the double damping flywheel (1, 101, 201, 301, 401, 501) which is intended to form a reaction plate for a clutch device. 20
    [0018]
    Motor vehicle having a torque transmission device (35, 135, 235, 335, 435, 535) according to any one of claims 1 to 18.
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    同族专利:
    公开号 | 公开日
    DE112016000285T5|2017-11-02|
    WO2016110648A1|2016-07-14|
    FR3031368B1|2017-07-07|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102009050670A1|2008-11-18|2010-05-20|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|One-piece pendulum|
    WO2014128380A1|2013-02-22|2014-08-28|Valeo Embrayages|Vibration damper for clutch friction disc of a motor vehicle|DE102016124402A1|2015-12-14|2017-06-14|Valeo Embrayages|Vibration damper with flexible tongue|
    DE102016124412A1|2015-12-14|2017-06-14|Valeo Embrayages|vibration|
    FR3054869A1|2016-08-08|2018-02-09|Valeo Embrayages|VIBRATION DAMPER COMPRISING A ROLLER CAM FOLLOWER|FR2936290B1|2008-09-23|2013-05-17|Valeo Embrayages|DOUBLE SHOCKWHEEL, IN PARTICULAR FOR MOTOR VEHICLE|
    法律状态:
    2016-02-01| PLFP| Fee payment|Year of fee payment: 2 |
    2016-07-08| PLSC| Search report ready|Effective date: 20160708 |
    2017-01-31| PLFP| Fee payment|Year of fee payment: 3 |
    2018-01-31| PLFP| Fee payment|Year of fee payment: 4 |
    2019-01-30| PLFP| Fee payment|Year of fee payment: 5 |
    2020-10-16| ST| Notification of lapse|Effective date: 20200906 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1550118A|FR3031368B1|2015-01-07|2015-01-07|ELASTIC BLADE TORQUE TRANSMISSION DEVICE EQUIPPED WITH CENTRIFUGAL MASS TORSION DAMPER|FR1550118A| FR3031368B1|2015-01-07|2015-01-07|ELASTIC BLADE TORQUE TRANSMISSION DEVICE EQUIPPED WITH CENTRIFUGAL MASS TORSION DAMPER|
    PCT/FR2016/050018| WO2016110648A1|2015-01-07|2016-01-06|Torque transmission device with elastic blade equipped with a centrifugal-mass torsion damper|
    DE112016000285.8T| DE112016000285T5|2015-01-07|2016-01-06|Torque transfer device with elastic spring strip equipped with a centrifugal mass torsional vibration damper|
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