• 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:
    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:FR3031367A1
    申请号:FR1550117
    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 element, for example by means of 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 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 resilient damping means comprise a fixing portion which is connected to the resilient blade and which is fixed on said input or output member so as to rotate said resilient blade to said input member or output member. the fixing part is fixed to the input or output element by means of fasteners, for example rivets. the fixing part and the elastic blade of the elastic damping means can be formed in one piece. the fixing part of the elastic damping means is advantageously fixed on the output element. according to one embodiment, the attachment portion of the elastic damping means further forms the support on which said at least one mass of inertia is mounted oscillatingly. Thus, the function of elastic coupling between the input and output elements and the support function of the mass (s) of inertia of the centrifugal mass torsion damper are made by the same element. - 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 may be integral and the annular body and the elastic blades formed integrally. according to another embodiment, the elastic damping means comprise a plurality of resilient blades which each cooperate with a support element and the fixing part comprises a plurality of separate fastening elements which are each connected to an elastic blade respective and independently attached to said input or output element. When the fixing portion has a plurality of separate fastening elements and the centrifugal mass torsion damper has a plurality of inertia masses, it is possible to distribute the masses of inertia on the fastening elements of such so that each of the fasteners form a support for at least one of said mass of inertia. 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. in a particular embodiment, the elastic blade may comprise an internal strand, an external strand and a bent portion connecting the inner strand and the outer strand. according to one embodiment, the or each mass of inertia comprises two flanks extending axially on either side of the attachment portion of the elastic damping means, the two flanks being connected to one another; other via connecting struts which pass through an opening in said fastening portion. According to one embodiment, each connecting strut passes through an associated opening formed in the fixing part. However, in another embodiment, it is also possible to provide for two or more connecting struts to pass through the same opening in the fastening portion. advantageously, the input or output element to which the fastening portion of the resilient damping means is secured in rotation comprises a plurality of fastening zones through which the fastening members pass, the fixing part being plated axially against said attachment areas of said attachment portion, said attachment areas projecting axially toward the other of said input or output members such that two circumferentially consecutive attachment areas are separated by a recess in which is housed at least partially one of the two flanks. Such an arrangement makes it possible to further limit the size. - According to one embodiment, the attachment portion of the resilient damping means has an axial recess accommodating at least partially a sidewall of at least one mass of inertia. In other words, the fastening portion has a smaller axial dimension at the deflection region of the or each mass of inertia so as to allow a reduction in axial size. - 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 fastening portion of the resilient damping means. - 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 fixing portion of the elastic damping means. each first rolling track is formed on one of the connecting struts and each second running track is formed by an outer edge of one of the passage openings of a connecting strut formed in the fixing part of the means. damping elastics. - 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 fixing portion of the elastic damping means via a plurality of resilient biasing members adapted to generate a force for biasing the inertia mass relative to the attachment portion in a relative equilibrium position. By way of example, the moment of inertia of the centrifugal mass and the stiffness of all the elastic members are such that the centrifugal mass has a resonance frequency of between 12 Hz and 60 Hz, and preferably of 6 nm. at 9n Hz 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. according to one embodiment, the elastic return members comprise a plurality of lamellae which are each formed in the fastening part, inside one of the passage openings of a connecting spacer, and each cooperate with said connecting strut. The elastic strips can in particular be formed in one piece with the fixing portion. In this case, the elastic strips are obtained during the cutting of the passage openings of the connecting struts in the fixing part. - 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. according to an advantageous embodiment, the friction assembly extends radially outside the at least one mass of inertia of the torsion damper centrifugal mass which limits the axial size of the combination of the friction assembly and the centrifugal mass torsion damper. the friction assembly comprises a friction washer and an elastic washer adapted to exert a force in an axial direction towards the input element so as to press the first friction washer against the input element. The attachment portion of the elastic damping means is fixed to the output member and has a lug housed in a groove of the friction washer so as to rotate said friction washer relative to the input member. during a relative rotation between the input element and the output element. the tab of the fixing portion extends radially outwards. 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 input element and between the output element, that is to say between the primary flywheel and the secondary flywheel when the torque transmission device is a double steering wheel damper. 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 solely for the purposes of the invention. illustrative and not limiting, with reference to the accompanying drawings. FIG. 1 is a partial 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 elastic damping means with elastic blades and of the pendulum damper. - Figure 2 is a sectional view of the double damping flywheel of Figure 1 along the plane II-II. FIG. 3 is a detailed perspective view of the resilient elastic damping means 10 and of the swinging shock absorber of the double damping flywheel of FIG. 1. FIG. 4 is a partial front view of a double damping flywheel according to a second embodiment in which the primary flywheel is not shown. FIG. 5 is an exploded partial view of the double damping flywheel of FIG. 4 partially illustrating the elastic damping means and the pendulum damper. - Figure 6 is a sectional view of a double damping flywheel according to a third embodiment comprising elastic damping means 20 with elastic blades and an inertial drummer. - Figure 7 is a partial view of the double damping flywheel of Figure 6 illustrating in detail the fixing portion of the elastic damping means with elastic blades forming a support for the mass of inertia of the inertial drummer. FIG. 8 is a cross-sectional view along a radial plane of the fastening portion of the resilient leaf spring damping means and the inertial beater of FIG. 7; FIG. 9 is a sectional view along the IX plane; -IX resilient elastic damping means and inertial drummer of Figure 8. 30 - Figure 10 is a graph illustrating the amplitude of the accelerations representative of the acyclisms at the entry of the gearbox depending on the regime engine, for transmission chains equipped with different double flywheels dampers. 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 The "circumferential" orientation is directed orthogonally to the axis of the torque transmission device and substantially 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 described as internal as opposed to an external element located radially at the periphery. 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.
    [0006] In relation to FIG. 2, 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. The secondary flywheel 3 has a flat rear annular surface 10, intended to form a bearing surface for a friction lining of a clutch disc, 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. The secondary flywheel 3 further comprises orifices 12, arranged vis-à-vis the orifices formed in the primary flywheel 2, and for the passage of the fastening screws 8, when mounting the double damping flywheel 1 on the crankshaft. In relation with FIG. 1, resilient damping means 15 are observed coupling the primary flywheel 2 and the secondary flywheel 3 so as to allow vibration-damped torque transmission between the primary and secondary flywheels 3. resilient damping means comprise a fixing portion which is here formed of a central body 13 and two resilient blades 14, 15 bent around the X axis and developing from the central body 13. The central body 13 is monobloc and ring-shaped. The central body 13 and the resilient blades 14, 15 are integrally formed. The two resilient blades 14, 15 are symmetrical to each other with respect to the axis of rotation X. As shown in the lower part of FIG. 2, the central body 13 is fixed on the secondary flywheel 3. To do this, the central body 13 is provided with a plurality of circumferentially distributed orifices 16 allowing the passage of rivets 17 passing further through orifices of the secondary flywheel 3. The central body 13 of the elastic damping means present an annular shape and is thus fitted on a skirt 18 of axial orientation 18 of the secondary flywheel 3 so as to ensure a centering of the elastic damping means relative to the secondary flywheel 3. The central body 13 is sandwiched axially between a head of the rivet 17 and an attachment zone 19 of the secondary flywheel 3. The attachment zones 19 protrude axially towards the primary flywheel 2. Thus, between two circumferentially consecutive fastening zones 19 , a recess 20 is formed in the secondary flywheel 3. This recess 20 illustrated on the upper part of Figure 2, can partially accommodate a mass of inertia 21 of a torsion damper centrifugal mass 35 which will be described so detailed thereafter. 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 support 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 surface and are arranged to roll against said cam surface during a relative movement between the flywheels In addition, the cam followers 22 are radially disposed outside their respective cam surfaces so as to radially maintain the resilient blades 14, 15 when subjected to centrifugal force. Each cam surface is arranged such that, for a 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 is moves on the cam surface and, in doing so, exerts a bending force on the resilient blade 14, 15. By reaction, the elastic 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). Moreover, the torsional vibrations and the irregularities of torque which are produced by the engine and transmitted by the crankshaft to the primary flywheel 2 are damped by the bending of the elastic blades 14, 15. In order to reduce the parasitic friction likely to affect the damping function, the rollers 23 are advantageously rotatably mounted on the primary flywheel 2 by means of rolling elements 24, such as balls, rollers or needles. In the embodiment shown in FIG. 2, the rollers 23 are each carried by a cylindrical rod 25 extending parallel to the axis of rotation X and one 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.
    [0007] The roller 23 is rotatably mounted around the sleeve 27. To do this, the rolling members 24 cooperate, on the one hand, with a rolling track formed on the outer periphery of the sleeve 27 and, on the other hand, with a running 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, aft, by a shoulder 30 formed at the rear end of the sleeve 27. The sleeve 27 also carries a seat ring 31 which is mounted tightly around the sleeve 27. The seat ring 31 is axially supported against the primary flywheel 2. In addition, the seat ring 31 cooperates with an outer retaining surface formed in the cylindrical portion 7 of the primary flywheel 2. The radial forces supported by the cam follower 22 are thus taken up by the primary flywheel 2 on an important axial dimension. which limits the risk of deformation of the cylindrical rod 25. The double damping flywheel is also equipped with a friction assembly, shown in FIG. 2, arranged to exert a friction-resistant torque during the relative rotation between the primary flywheels 2 and secondary 3. The friction assembly is thus able to dissipate the energy accumulated in the resilient blades 14, 15. The friction assembly comprises a friction washer 32 and a spring washer 33 Belleville type which is axially wedged to the rear by a circlip 34. The spring washer 33 exerts an axial force directed forward on the friction washer 32 so as to press against the primary flywheel 2. The circlip 34 is retained in a fixing groove on the internal periphery of the cylindrical portion 7 of the primary flywheel 2. The friction assembly is disposed radially outside the centrifugal mass torsion damper ge 35 which limits the axial size of the double damping flywheel 1. As shown in Figure 1, the central body 13 is equipped with two diametrically opposed legs 36 which are directed radially outwardly and slightly folded towards the before. Each of the tabs 36 is housed in a groove 37 formed in the inner periphery of the friction washer 32. Thus, the friction washer 37 can be rotated by the tabs 36 so that during a relative rotation between the primary flywheel 2 and secondary 3, the friction washer 37 moves relative to the primary flywheel 2 and thus exerts a friction torque opposing the relative rotation of the primary flywheels 2 and secondary 3. Moreover, in connection with the figures 2 and 3, it is observed 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. The support is here directly formed by the central body 13 of the elastic damping means. The pendulum weights 21 are able to oscillate with respect to the central body 13 in a plane orthogonal to the axis of rotation X, in response to the irregularities of rotation. The pendulum weights 21 have a general shape of an arc of a circle. Each pendulum weight 21 comprises two sidewalls 38, 39 which are arranged on either side of the central body 13 and are connected axially to one another by means of two connecting struts 40. To this end, each flank 38, 39 has two cutouts for mounting by force-fitting the connecting struts 40. Moreover, each connecting strut 40 axially passes through an opening in the central body 13. The oscillations of the pendulum weights 21 are guided by means guidance. The guide means comprise, for each counterweight 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 central body 13. For each element 41, the first and second raceways are arranged radially facing each other.
    [0008] In relation with the upper part of FIG. 2, it is observed that the first raceways 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.
    [0009] The pendulum weights 21 and / or the central body 13 may comprise abutment elements of elastomeric material for damping shocks, when the pendulum weights 21 arrive at the end of stroke or during engine stop. According to one embodiment, the heads of the rivets 17 may be covered with elastomeric material so as to form end stops. In relation with FIG. 1, it can be seen that each pendulum weight 21 is disposed circumferentially between two orifices 16 formed in the central body 13 and allowing the fastening rivets 17 of the central body 13 to pass over the secondary flywheel 3. Thus, as shown in the upper part of Figure 2, the rear flank 38 of each counterweight 21 is housed in a recess 20 of the secondary flywheel 3 separating two circumferentially consecutive fastening zones 19. Such an arrangement makes it possible to limit the axial size of the double damping flywheel 1 thus produced. FIG. 10 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 - a double damping flywheel 1 whose elastic damping means are elastic blades 14, 15 and further comprising a pendulum damping (Curve C).
    [0010] It is thus found that a double damping flywheel as described above associating elastic damping means with resilient blades and a pendulum damping makes it possible to obtain vibration filtering performances that are much greater than those of the other damping double flywheels.
    [0011] Figures 4 and 5 partially illustrate a double damping flywheel 101 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. In this embodiment, each elastic blade 114, 115 has a strand internal 142, an outer strand 144 and a bent portion 143 connecting the inner strand 142 and the outer strand 143. The bent portion 143 has an angle of about 180 ° so that a portion of the inner strand 142 is radially between a portion of the outer strand 144 and the axis X. In other words, the elastic blade 114, 115 has two radially offset regions of each other and separated by a radial gap. Such a shape of the resilient blades 114, 115 allows them to develop over longer lengths which allows to provide a cam surface having a large circumferential length. Thus, the angular stiffness of the elastic damping means can be reduced, which leads to a significant increase in filtration performance.
    [0012] Given the particular shape of the resilient blades 114, 115, the fixing portion 113 is here formed of two separate fasteners 145 of arcuate shape which are formed respectively in one piece with the two of them. two resilient blades 114, 115. Each fastener 145 is attached to the secondary flywheel 103 independently through a plurality of rivets 117, three in the illustrated embodiment. Furthermore, each of the fastening elements 145 forms a support on which is mounted oscillating a pendulum weight 121. In relation to FIG. 5, it is also observed that the fastening portion 113 may have a recess 151, that is, that is, a smaller axial dimension at the level of the deflection zone of each counterweight 121 which makes it possible to reduce the axial size of each pendulum balance 121.
    [0013] In connection with Figures 6 to 9, we will now describe 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 number increased by 200.
    [0014] The general structure of the double damping flywheel 201 is identical to the structure of that described in relation to FIGS. 1 to 3 and differs from it only in that the centrifugal force torsion damper is here an inertial drummer and not a pendulum damper. An inertial drummer selectively filters the vibrations for a specific frequency range.
    [0015] It can be observed in FIGS. 7 and 8 that the inertial drummer comprises a single mass of inertia 221 which is mounted oscillating on the central body 213 of the elastic damping means. The mass of inertia 221 comprises two flanks 238, 239 which extend on either side of the central body 213 and which are connected to one another by means of a plurality of connecting struts. 240 passing through openings 246 formed in the central body 213. The connecting struts 240 are received inside cutouts 247 formed in the flanks 238, 239 and for securing the connecting struts 240 to said flanks 238, 239 , by press fitting, for example. The front flank 239 has an annular shape. The rear flank 238 is itself composed of a plurality of arcuate elements 248 which are separated from one another at the attachment zones 219 of the central body 213 on the secondary flywheel 203. Each arcuate element 248 is connected to the sidewall. before 239 via a connecting strut 240. As shown in the upper part of Figure 6, each arcuate member 248 of the trailing edge is housed in a recess 220 of the secondary flywheel 203 separating two attachment areas 217 of the body central 213 on the secondary flywheel 203 circumferentially consecutive. Furthermore, as shown in the lower part of FIG. 6, the front flank 239 has rivets 217 at the head for fastening the central body 213 to the secondary flywheel 213, a recess 249 in which at least part of the recess is housed. The head of a rivet 217. Such an arrangement makes it possible to optimize the inertia of the mass with respect to its axial size.
    [0016] Moreover, the mass of inertia 221 of the inertial beater is rotatably coupled to the central body 213 via a plurality of elastic members, illustrated in FIG. 9. The elastic members generate a restoring force which opposes the rotation of the mass of inertia 221 with respect to its equilibrium position.
    [0017] The moment of inertia of the mass of inertia 221 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. In the embodiment shown in FIG. 9, the resilient members are elastic strips 250 which are formed in the central body 213 and extend inside the openings 246 for the passage of the connecting struts 240. The elastic strips 250 are integral with the central body 213. Each opening 246 is equipped with two elastic strips 250 which are disposed on either side of the connecting spacer 240 passing through said opening 246. Thus, one of the elastic lamellae 250 makes it possible to return the mass of inertia 221 towards a position of equilibrium during a relative rotation of the mass of inertia 213 with respect to the central body 213 in a first direction of rotation while the other of the lamellae Elastics 250 makes it possible to return the mass of inertia 221 towards its position of equilibrium during a relative rotation of the mass of inertia 221 with respect to the central body 213 in a second direction of rotation. Note, however, that other types of elastic members may be used. Thus, in another embodiment not shown, the elastic members are helical springs arranged in a circumferential orientation and having ends bearing against the mass of inertia 221 and against the central body 213. It is observed on the curve D of FIG. 10, the angular acceleration of the input shaft of a gearbox representative of rotation acyclisms, as a function of the engine speed for a motor vehicle transmission equipped with a double damping flywheel 201 whose elastic means damping means are elastic strips 214, 215 and further comprising an inertial drummer. It can thus be seen that a double damping flywheel 201 as described above associating elastic damping means with elastic blades and an inertial beater also makes it possible to obtain excellent vibration filtration performance. 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 as well as their combinations if these These are 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 undefined article "un" or "un" 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 a limitation of the claim.
    权利要求:
    Claims (18)
    [0001]
    REVENDICATIONS1. Torque transmission device (1, 101, 201) for a motor vehicle transmission chain comprising: - a torque input member (2, 102, 202) and a torque output member (3, 103, 203) movable in rotation relative to each other about an axis of rotation X - elastic damping means coupling the input element (2, 102, 202) and the output element ( 3, 103, 203) so as to allow vibration-damped torque transmission between the input member (2, 102, 202) and the output member (3, 103, 203), this transmission of torque with damping being accompanied by a relative rotation between the input element (2, 102, 202) and the output element (3, 103, 203); the elastic damping means comprising at least one elastic blade (14, 15, 114, 115, 214, 215) integral in rotation with one of the input and output elements (2, 3, 102, 103, 202 203) and cooperating with a support member (22) carried by the other of said input and output members (2, 3, 102, 103, 202, 203); the resilient blade (14, 15, 114, 115, 214, 215) being arranged such that in a relative angular position between the input member (2, 102, 202) and the output member (3 , 103, 203) different from a relative rest position, the support element (22) exerts a bending force on the elastic blade (14, 20, 114, 115, 214, 215) producing a force of contrary reaction of the elastic blade (14, 15, 114, 115, 214, 215) on the support element (22), this reaction force having a circumferential component able to recall said input and output elements ( 2, 3, 102, 103, 202, 203) to said relative rest position; and a centrifugal mass torsion damper (35, 135, 235) having at least one mass of inertia (21, 121, 221) rotatably mounted in rotation on a support (13, 113, 213) integral with rotating one of the input and output elements (2, 3, 102, 103, 202, 203).
    [0002]
    Torque transmission device according to Claim 1, in which the support (13, 113, 213) is integral in rotation with the output element (3, 103, 203).
    [0003]
    Torque transmission device according to claim 1 or 2, wherein the resilient damping means comprise a securing portion (13, 113, 213) which is connected to the elastic blade (14, 15, 114, 115, 214). , 215) and which is fixed on said input or output element (2, 3, 102, 103, 202, 203) so as to rotationally secure said elastic blade (14, 15, 114, 115, 214, 215 ) to said input or output element (2, 3, 102, 103, 202, 203) and wherein the fixing portion (13, 113, 213) further forms the support on which said at least one mass of inertia (21, 121, 221) is mounted oscillatingly.
    [0004]
    A torque transmission device according to claim 3, wherein the resilient damping means comprises a plurality of resilient blades (14, 15, 214, 215) which each cooperate with a support member (22) and wherein the fixing portion (13, 213) is a one-piece annular body connected to the plurality of resilient blades (14, 15, 214, 215).
    [0005]
    A torque transmission device according to claim 3, wherein the resilient damping means comprises a plurality of resilient blades (114, 115) which each cooperate with a support member (22) and wherein the attachment portion (113) has a plurality of separate fasteners (145) which are each connected to a respective resilient leaf (114, 115) and independently attached to said input or output member (2, 3, 102, 103). , 202, 203).
    [0006]
    Torque transmission device according to any one of claims 3 to 5, wherein the or each mass of inertia (21, 121, 221) has two flanks (38, 39, 138, 139, 238, 239). extending axially on either side of the fastening portion (13, 113, 213) of the elastic damping means, the two flanks (38, 39, 138, 139, 238, 239) being connected to one another. to the other via connecting struts (40, 140, 240) which pass through an opening in the fastening portion (13, 113, 213).
    [0007]
    Torque transmission device according to claim 6, in which the input or output element (2, 3, 102, 103, 202, 203) to which the fixing part (13, 113, 213) elastic damping means comprises a plurality of attachment zones (19, 119, 219) through which fastening members (17, 117, 217) of said fastening portion (13, 113, 213) pass, the fixing portion (13, 113, 213) being axially pressed against said attachment regions (19, 119, 219), said fixing regions (19, 119, 219) projecting axially towards the other of said input elements or outlet so that two circumferentially consecutive attachment regions (19, 119, 219) are separated by a recess (20, 120, 220) in which at least one of the two sidewalls (38, 138, 238) is housed.
    [0008]
    Torque transmission device according to claim 6 or 7, wherein the fixing portion (113) has an axial recess (151) at least partially accommodating a sidewall of at least one inertia mass.
    [0009]
    A torque transmitting device according to any of claims 3 to 8, wherein the centrifugal mass torsion damper (35, 135) is a pendulum damper having a plurality of inertia masses (21, 10 121 ) regularly distributed over the fixing portion (13, 113).
    [0010]
    10. A torque transmission device according to claim 9, comprising means for guiding the masses of inertia which comprise, for each mass of inertia (21,121), two rolling members (141) which each cooperate with a first rolling track. carried by said mass of inertia (21,121) and with a second raceway carried by the fixing portion (13, 113).
    [0011]
    A torque transmission device according to claims 9 and 10, when claim 9 is dependent on one of claims 6 to 8, wherein each first raceway is provided on one of the connecting struts (40, 140) and wherein each second raceway is formed by an outer edge of one of the passageways of a connecting strut (40, 140) in the attachment portion (13, 113).
    [0012]
    A torque transmitting device according to any one of claims 3 to 8, wherein the centrifugal mass torsion damper (235) is an inertial drummer and in which the mass of inertia (221) is coupled in rotation to the fixing portion (213) via a plurality of elastic return members (250) adapted to generate a force for biasing the inertia mass (221) relative to the attachment portion (213) ) in a relative position of equilibrium. 30
    [0013]
    Torque transmission device according to claim 12 when dependent on one of claims 6 to 8, wherein the spring return members comprise a plurality of lamellae (250) which are each formed in the attachment portion ( 213), inside one of the openings (246) for passage of a connecting strut (240) and each cooperate with said connecting struts (240).
    [0014]
    14. Torque transmission device according to any one of claims 1 to 13, further comprising a friction assembly arranged to exert a friction resisting torque between the input member (2, 102, 202) and the output member (3,103,203) in relative rotation between the input member and the output member.
    [0015]
    The torque transmission device according to claim 14, wherein the friction assembly extends radially outwardly of the at least one inertia mass (21, 121, 221) of the shock absorber. Centrifugal mass torsion (35, 135, 235).
    [0016]
    16. Torque transmission device according to claim 15, wherein the friction assembly comprises a friction washer (32, 132, 232) and a resilient washer (33, 133, 233) adapted to exert a force according to a axial direction towards the input member (2, 102, 202) so as to press the first friction washer (32, 132, 232) against the input member and wherein the attachment portion (13, , 113, 213) resilient damping means is attached to the output member (3, 103, 203) and includes a tab (36, 136, 236) housed in a groove (37) of the friction washer ( 32, 132, 232) to rotate said friction washer (32, 132, 232) relative to the input member (2, 102, 202) in a relative rotation between the element input (2, 102, 202) and the output element (3, 103, 203).
    [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) of a dual flywheel (1, 101, 201 ) to be fixed at the end of a crankshaft and the output member is a secondary flywheel (3, 103, 203) of the double damping flywheel which is intended to form a reaction plate for a clutch device.
    [0018]
    18. A motor vehicle having a torque transmission device (1, 101, 201) according to any one of claims 1 to 17.
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    同族专利:
    公开号 | 公开日
    FR3031367B1|2017-07-28|
    WO2016110646A1|2016-07-14|
    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|WO2018037180A1|2016-08-24|2018-03-01|Valeo Embrayages|Torque transmission device|
    WO2019001625A1|2017-06-29|2019-01-03|Schaeffler Technologies AG & Co. KG|Speed-adaptive torsional vibration isolation device|
    FR3097926A1|2019-06-27|2021-01-01|Valeo Embrayages|Torque transmission device equipped with a torque limiter|FR2936290B1|2008-09-23|2013-05-17|Valeo Embrayages|DOUBLE SHOCKWHEEL, IN PARTICULAR FOR MOTOR VEHICLE|FR3059379A1|2016-11-30|2018-06-01|Valeo Embrayages|TORSION DAMPER HAVING FRICTION DEVICE AND TILT LIMITING DEVICE|
    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
    FR1550117A|FR3031367B1|2015-01-07|2015-01-07|ELASTIC BLADE TORQUE TRANSMISSION DEVICE EQUIPPED WITH CENTRIFUGAL MASS TORSION DAMPER|FR1550117A| FR3031367B1|2015-01-07|2015-01-07|ELASTIC BLADE TORQUE TRANSMISSION DEVICE EQUIPPED WITH CENTRIFUGAL MASS TORSION DAMPER|
    PCT/FR2016/050016| WO2016110646A1|2015-01-07|2016-01-06|Torque transmission device with elastic blade equipped with a centrifugal-mass torsion damper|
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