• 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 clutch torsion damper comprising: - an input member and an output member movable in rotation relative to each other about an axis of rotation X; damping means for transmitting torque and damping rotation acyclisms between the input and output elements; the damping means comprise an elastic blade (22) provided with a cam surface (23), and a toothing (26) for securing in rotation said blade with one of said input and output elements. The damper has a cam follower (24), carried by the other of said input and output members, and arranged to cooperate with said cam surface (23). The cam surface (23) is arranged such that, for angular displacement between the input member and the output member with respect to an angular rest position, the cam follower (24) exerts a force bending on the elastic blade (22) producing a reaction force adapted to return said input and output elements to said angular position of rest.
    公开号:FR3018572A1
    申请号:FR1500505
    申请日:2015-03-13
    公开日:2015-09-18
    发明作者:Perez Carlos Lopez
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] Technical Field of the Invention The invention relates to a torsion damper for a clutch friction disc. The invention relates in particular to a pre-damper intended to equip a friction disc. Such a pre-damper is intended to filter the vibrations generated by the acyclismes of the combustion engine at idle speed. Otherwise, vibrations entering the gearbox would cause shocks, noises or noise particularly undesirable. STATE OF THE ART In a motor vehicle, a clutch friction disc makes it possible to transmit a torque between a driving shaft, such as a crankshaft of a combustion engine, and a driven shaft, such as a shaft of a clutch. gearbox input, by pinching said friction disk between a pressure plate and a flywheel. In addition, the clutch friction discs are generally equipped with torsion dampers for absorbing and damping the vibrations and acyclisms generated by the engine. Friction discs sometimes have two shocks coupled in series, called main damper and pre-damper. Such a friction disc is in particular described in document EP 0 732 525. Each damper is provided with rotary elements, input and output, which can be rotated with respect to each other around their common axis of rotation. Each damper is equipped with damping means arranged to transmit torque and dampen rotation acyclisms between its input and output elements. The elastic damping means equipping these torsion dampers are helical springs with a circumferential effect, the ends of which come, on the one hand, to bear against the input elements and, on the other hand, to bear against the elements Release. Thus, any rotation of one of said elements relative to the other causes a compression of the springs of the damper in one direction or the other and said compression exerts a restoring force able to return said elements to a relative angular position. rest.
    [0002] The dampers each comprise two guide rings, integral in rotation, a web disposed between the two guide rings and a plurality of helical springs acting circumferentially between the web and the two guide rings; by being mounted in housings, vis-à-vis, in the guide rings and the veil. Thus, the assembly and manufacture of dampers are relatively complex because they have many elements and the mounting of the coil springs in the housing of the guide rings and the sail is a delicate operation. In addition, because the volume of the coil springs is limited, the angular displacement between the inlet and the outlet of the torsion dampers is limited, so that the coil springs have a relatively high stiffness for optimum filtration of the acyclisms. OBJECT OF THE INVENTION The object of the invention is to remedy these problems by proposing a torsion damper whose manufacture and assembly are simplified. For this purpose, and according to a first aspect, the invention relates to a torsion damper for a clutch friction disc comprising: - an input member and an output member movable in rotation relative to the other around an axis of rotation X; damping means for transmitting a torque and damping the rotational acyclisms between the input and output elements; - The input element comprising two flanges, integral in rotation, arranged on either side of the damping means and thus defining a housing cassette of said damping means; said torsion damper being remarkable in that the damping means comprises a resilient blade rotatably integral with one of said input and output members and provided with a cam surface; and in that the damper has a cam follower, carried by the other of said input and output members, and arranged to cooperate with said cam surface; said cam surface being arranged such that, for angular displacement between the input member and the output member with respect to an angular rest position, the cam follower exerts a bending force on the blade elastic member producing a reaction force capable of biasing said input and output elements towards said angular position of rest. Thus, the construction and assembly of such a damper is simplified since it requires a limited number of components compared to a torsion damper 5 with coil springs. In addition, the damping means are less sensitive to the centrifugal force than the helical springs of the prior art so that the quality of the vibration damping is only slightly impacted by the centrifugal force. In addition, the structure of such a damper provides significant relative deflections which allows the use of damping means having a limited stiffness to improve efficiency. Moreover, such a damper may have a characteristic curve representing the variations of the torque transmitted as a function of the angular deflection which has slope variations without point of inflection or discontinuity. Thus, the characteristic curve does not exhibit a zone of abrupt change of stiffness which causes discontinuities and shocks affecting the quality of the damping. Finally, the cam surface being carried by the elastic blade, the manufacture of a damper according to the invention may be partly standardized. Indeed, only the geometry and characteristics of the blade require adaptations when the characteristics of a damper must be adapted to the characteristics of the intended application. According to other advantageous embodiments, such a torsion damper may have one or more of the following characteristics: the elastic blade is integral in rotation with the output element and the cam follower is carried by a fixing element allowing to fix the flasks to one another. Such an arrangement is particularly compact and requires a limited number of components. - The cam follower is a roller rotatably mounted on the fixing member of the flanges. - The roller is rotatably mounted on the fastening element of the flanges by means of a rolling bearing. The output element comprises a hub having internal splines intended to cooperate with splines of a gearbox input shaft and the elastic blade is carried by an annular body having teeth cooperating with complementary toothings formed. on the hub. Thus, the mounting damping means is simple since they cooperate by teeth with the output of the damper. the elastic blade is held axially on the hub. - The teeth of the hub cooperating with the toothing of the annular body is bordered on the one hand by an abutment surface and on the other hand by a crimping formed on the hub so as to allow axial retention of the annular body on the hub. the torsion damper comprises a second elastic blade provided with a cam surface and a second cam follower arranged to cooperate with the cam surface of said second elastic blade. Such an arrangement makes it possible to increase the torque capacity of the damper. - The first and second resilient blades are carried by an annular body and are symmetrical with respect to the axis of rotation X. Thus, the damper is balanced. the cam follower 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. In addition, this arrangement allows an increase in the stiffness of the elastic blade under the effect of the centrifugal force. the cam surface is formed at a free end of the elastic blade. the blade comprises a curved portion extending circumferentially at the free end of which the cam surface is formed. Such a structure makes it possible to obtain both a low rigidity and a satisfactory mechanical strength. the elastic blade comprises a plurality of lamellae arranged axially against each other. According to a second aspect, the invention relates to a clutch friction disc comprising a torsion damper according to the first aspect of the invention. In one embodiment, one of the two flanges of the input element of the torsion damper according to the first aspect of the invention is constituted by an output web of a second damper. The invention will be better understood, and other objects, details, features and advantages thereof will become more apparent in the following description of several particular embodiments of the invention, given solely for illustrative purposes and not limiting, with reference to the appended figures.
    [0003] In these figures: - Figure 1 is a front view of a clutch friction disc. FIG. 2 is an exploded view of the friction disc of FIG. 1. FIG. 3 is a sectional view of the friction disc of FIG. 1 in plane III. FIG. 4 is a sectional view of the friction disc. of Figure 1 in the plane IV-IV. Figure 5 is a partially exploded view of the pre-damper. FIG. 6 is a perspective view of a subassembly of the pre-damper of FIG. 5. FIG. 7 is a perspective view of the resilient blade damping means and the hub of the friction disc. Figure 8 is a perspective view of the resilient blade damping means. - Figure 9 illustrates the deflection of a blade of a torsion damper during an angular movement between the input and output elements of the damper, in a direct direction. - Figure 10 illustrates the deflection of the blade during an angular movement in a retro direction.
    [0004] FIG. 11 is an example of characteristic curves of a pre-damper, representing the torque transmitted as a function of the angular displacement. Figure 12 is a perspective view of the resilient blade damping means and the hub of the friction disc according to an alternative embodiment. FIG. 13 is a sectional view of the resilient blade damping means and the hub of FIG. 12. FIG. 14 is a detailed view of the assembly between the elastic blade and the hub of FIGS. 13 and 14. Figure 15 is a perspective view of an elastic blade according to an alternative embodiment.
    [0005] FIG. 16 is an exploded view of the elastic blade of FIG. 15. In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations will be used to denote, according to the definitions given in the description, elements of the clutch friction disc. By convention, the "radial" orientation is directed orthogonally to the axis X of rotation of the clutch disk 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 rotation of the clutch disk and orthogonal to the radial direction.
    [0006] The terms "external" and "internal" are used to define the relative position of one element relative to another, with reference to the axis X of rotation of the clutch disc, a member close to the axis is thus described as internal as opposed to an external element located radially periphery. The clutch friction disk 1, shown in Figures 1 to 4, is intended to be mounted integral in rotation with a driven shaft and to be disposed between a pressure plate of a clutch and a reaction plate, integral in rotation of a driving shaft. During a clutch operation, the pressure plate clamps the friction disk 1 against the reaction plate and the torque of the driving shaft is then transmitted to the driven shaft. The friction disc 1 comprises a support disc 2, illustrated in Figures 3 and 4, bearing on each of its faces, friction linings 3, 4 to be clamped between the pressure plates and reaction. The support disk 2 is fixed on two guide washers 5, 6, forming the input element of the main damper, arranged on either side of a web 7, forming the output element of said damper main. The guide washers 5, 6 are fixed to one another by riveting, for example.
    [0007] The damping means of the main damper are here elastic members with circumferential action, such as helical springs 8. The coil springs 8 are mounted in housing windows 9, 10 made, facing each other, in the guide washers 5, 6 and in the web 7. The coil springs 8 are for example mounted in pairs of concentric springs. The helical springs 8 are held axially in their respective housings by the outer edges 11 of the windows 9 of the guide washers 5, 6. The ends of the coil springs 8 bear against the radial edges of the housing windows 9, 10 in such a way that that said helical springs 8 are able to transmit a torque between the guide washers 5, 6 and the web 7. The coil springs 8 have a stiffness sufficient to allow the transmission of the maximum engine torque. The main damper is also equipped with axial-action friction means, represented in FIGS. 3 and 4, intended to dissipate the energy accumulated in the coil springs 8. The axial-action friction means comprise a friction washer 14 and an elastic washer 15, also called "Belleville" washer. The friction washer 14 is secured in rotation to the guide washer 6 by axial fingers, shown in FIG. 3, nested in orifices formed in said guide washer 6. The elastic washer 15 is interposed under stress between the washer 6 and the friction washer 15 so as to press said friction washer 15 against the web 7. The friction disc 1 is also equipped with a pre-damper which is shown in detail in FIG. such pre-damper essentially has the function of filtering noise such as box noises or dead noises in the engine idle speed range while the main damper is intended to filter the vibrations in the operating speed of the engine. vehicle. The pre-damper is here implanted radially below the helical springs 8 of the main damper and axially between the two guide rings 5, 6 of the main damper. The input element of the pre-damper comprises two flanges 12, 13, fixed in rotation, arranged axially on either side of the damping means of the pre-damper. The flanges 12, 13 thus form a housing cassette damping means of the pre-damper. In the embodiment shown, one of the flanges 13 is constituted by the veil 7 output of the main damper. The flange 12 is fixed in rotation on the web 7 20 by a plurality of fastening tabs 16 received in orifices 17 of complementary shape, formed in the web 7. In another embodiment not shown, the two flanges 13, 14 are distinct from the sail 7 output of the main damper. They are in this case, fixed in rotation to said web 7 in order to couple in series the main damper and the pre-damper. The pre-damper output member is a hub 18 to be rotatably coupled to a driven shaft, such as an input shaft of a gearbox. For this purpose, the hub 18 has internal longitudinal grooves 19 intended to cooperate with complementary splines formed on the driven shaft. The hub 18 comprises on its outer periphery a toothing 20 intended to mesh, with a determined circumferential clearance, with a corresponding toothing 21 formed on an inner periphery of the web 7. The toothing 20, 21 form angular abutments to limit the deflection relative between the input element and the output element of the pre-damper when the torque to be transmitted is greater than a threshold. When the circumferential clearance is caught, the web 7 and the hub 18 cooperate with each other by stop. In this case, the pre-damper no longer intervenes in the transmission of the torque that is directly transmitted from the sail 7 to the hub 18.
    [0008] The damping means comprise at least one resilient blade 22 mounted to rotate with the hub 18. To do this, the elastic blade 22 is carried by an annular body 25 having an internal toothing 26, shown in FIG. 8, cooperating with a external toothing, of complementary shape, formed on the hub 18. In an advantageous embodiment, represented in FIGS. 12 to 14, the annular body 25 carrying the elastic blades 22 is held axially on the hub 22. To do this, the external toothing formed on the hub 18 and cooperating with the internal toothing 26 of the annular body 25 is bordered, on the one hand, by an abutment surface 29 and, on the other hand, by a crimp 30 made on the body of the hub 18 In the embodiment shown in FIGS. 5 to 8, the damping means 15 comprise two elastic strips 22 carried by the annular body 25. The two elastic strips 22 are symmetrical with respect to the axis of rotation X of the clutch disc. The resilient blades 22 have, at one free end, a cam surface 23 which is arranged to cooperate with a cam follower: the rollers 24. The resilient blades 22 comprise a curved portion 27 extending substantially circumferentially. The radius of curvature of the curved portion 27 as well as the length of this curved portion 27 are determined according to the desired stiffness of the elastic blade 22. The resilient blade 22 may optionally be formed integrally or be composed of a plurality of lamellae 28a, 28b, 28c, 28d, 28e arranged axially against each other, as illustrated in FIG. In the embodiment of Figure 15, the resilient blades 22 and the annular body 25 are constituted by a plurality of lamellae 28a, 28b, 28c, 28d, 28e extending axially against each other. The slats can be glued to each other. In one embodiment, the plurality of lamellae 28a, 28b, 28c, 28d, 28e are mounted on a hub 18 as shown in FIGS. 12-14. In this case, the assembly between the lamellae 28a, 28b, 28c, 28d, 28e is performed during the crimping of the hub 18.
    [0009] The rollers 24 are here borne by fastening lugs 16 for securing the flange 12 to the web 7. The rollers 24 are advantageously rotatably mounted on said fastening lugs 16 about an axis of rotation parallel to the axis of rotation. X. The rollers 24 are held in abutment against their respective cam surfaces 23 and are arranged to roll against said cam surface 23 upon relative movement between the input and output members of the pre-damper. The rollers 24 are radially outwardly from their respective cam surfaces 23 so as to radially maintain the resilient blades 22 when subjected to centrifugal force. In order to reduce the parasitic friction which may affect the damping function, the rollers 24 may be rotatably mounted on the fastening lugs 16 by means of a rolling bearing. For example, the rolling bearing may be a ball bearing or roller. In one embodiment, the rollers 24 have an anti-friction coating. The cam surface 23 is arranged such that, for angular displacement between the input member and the output member, relative to a relative angular position of rest, the roller 24 moves over the surface of the cam. cam 23 and, in doing so, exerts a bending force on the elastic blade 22. By reaction, the elastic blade 22 exerts on the roller 24 a restoring force which tends to bring the input 1 and output 2 elements back to their position. relative angular position of rest. Thus, the resilient blades 22 are able to transmit a driving torque from the input member to the output member (forward direction) and a resisting torque from the output member to the input member (direction retro). The operation of resilient blade damping means (s) will now be detailed in connection with FIGS. 9 and 10. When a driving motor torque is transmitted from the input member to the output member (Direct direction), the torque to be transmitted causes a relative movement between the input element and the output element in a first direction (see Figure 9). The roller 24 is then moved at an angle α relative to the elastic blade 22. The displacement of the roller 24 on the cam surface 23 causes a flexion of the elastic blade 22 along an arrow A. To illustrate the bending of the blade elastic 22, the blade 22 is shown in solid lines 30 in its angular position of rest and in dashed lines during an angular deflection.
    [0010] The bending force P depends in particular on the geometry of the elastic blade 22 and its material, in particular its transverse modulus of elasticity. The bending force P is decomposed into a radial component Pr and a tangential component Pt. The tangential component Pt allows the transmission of the engine torque. In response, the elastic blade 22 exerts on the roller 24 a reaction force whose tangential component constitutes a restoring force which tends to bring the input and output elements of the pre-damper to their relative angular position of rest. When a resistive torque is transmitted from the output element to the input element (retro direction), the torque to be transmitted causes a relative deflection between the input element and the output element in a second direction opposite (see Figure 10). The roller 24 is then displaced by an angle β with respect to the elastic blade 22. In this case, the tangential component Pt of the bending force has a direction opposite to the tangential component of the bending force illustrated in FIG. Figure 9. Similarly, the resilient blade 22 exerts a reaction force, in a direction opposite to that illustrated in Figure 9, so as to bring the input and output elements to their relative angular position of rest. The torsional vibrations and the irregularities of torque which are produced by the internal combustion engine are transmitted by the shaft leading to the input element 1 and generate relative rotations between the input and output elements of the damper. These vibrations and irregularities are dampened by the bending of the resilient blade 22. FIG. 11 illustrates a characteristic curve of torsion dampers made in accordance with the teachings of the invention. This characteristic curve represents the transmitted torque, expressed in Nm, as a function of the angular deflection, expressed in degrees. The relative movement between the input and output elements, in the forward direction, is shown in dashed lines while the deflection in the retro direction is shown in solid lines. It is noted that a torsion damper according to the invention allows in particular to obtain damping characteristic curves whose slope varies gradually without discontinuity. Advantageously, the cam surface 23 and the resilient blade 22 are arranged such that the characteristic function of the torque transmitted as a function of the angular deflection is a monotonic function.
    [0011] For certain applications, the cam surface 23 and the elastic blade 22 may be arranged in such a way that the characteristics of the torque transmitted as a function of the angular displacement, in the retro direction and in the forward direction, are symmetrical with respect to the angular position of rest.
    [0012] Although the invention has been described in connection with several particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. A torsion damper, particularly a clutch, comprising: - an input member and an output member rotatable relative to each other about an axis of rotation X; damping means for transmitting torque and damping rotation acyclisms between the input and output elements; said torsion damper being characterized in that the damping means comprise an elastic blade (22) provided with a cam surface (23), and a toothing (26) for securing said blade in rotation with one of said input and output elements, and in that the damper comprises a cam follower (24), carried by the other of said input and output elements, and arranged to cooperate with said cam surface (23) ; said cam surface (23) being arranged such that, for angular displacement between the input member and the output member with respect to an angular rest position, the cam follower (24) exerts an bending force on the elastic blade (22) producing a reaction force adapted to return said input and output elements to said angular position of rest.
    [0002]
    2. Torsion damper according to the preceding claim characterized in that the damping means cooperate by toothing with the output member of 1 damper.
    [0003]
    The torsion damper according to one of the preceding claims, wherein the cam follower is a roller (24) held in abutment with the cam surface (23) and is arranged to roll against said cam surface (23). .
    [0004]
    A torsion damper according to claim 2, wherein the resilient blade (22) is carried by an annular body (25) having the toothing (26) for cooperating with complementary toothing of the output member.
    [0005]
    5. Shock absorber according to the preceding claim, characterized in that the output element comprises a hub (18) on which is formed the complementary toothing, the toothing of the annular body cooperating with the complementary toothing of the hub (18).
    [0006]
    The torsion damper according to one of claims 1 to 5, wherein the resilient blade (22) is axially supported on the output member.
    [0007]
    7. torsion damper according to claim 6, wherein the complementary toothing of the hub (18) cooperating with the toothing (26) damping means is bordered on the one hand by an abutment surface and on the other by a crimping formed on the hub (18) so as to allow axial retention of the damping means on the hub (18).
    [0008]
    A torsion damper according to any one of claims 1 to 7, wherein the damper comprises a second resilient blade (22) provided with a cam surface (23) and a second cam follower (24) arranged to cooperate with the cam surface (23) of said second elastic blade (22).
    [0009]
    The torsion damper of claim 8, wherein the first and second resilient blades (22) are carried by the annular body (25) and are symmetrical about the axis of rotation X.
    [0010]
    Torsion damper according to one of Claims 1 to 9, in which the cam follower (24) is arranged radially outside the spring blade (22).
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    同族专利:
    公开号 | 公开日
    KR20150120375A|2015-10-27|
    FR3002605B1|2015-04-24|
    BR112015017607A2|2017-07-11|
    FR3002605A1|2014-08-29|
    EP2959181B1|2017-03-15|
    FR3018572B1|2016-11-11|
    CN105074270A|2015-11-18|
    CN105074270B|2017-03-08|
    WO2014128380A1|2014-08-28|
    EP2959181A1|2015-12-30|
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    法律状态:
    2015-10-23| PLFP| Fee payment|Year of fee payment: 3 |
    2016-02-29| PLFP| Fee payment|Year of fee payment: 4 |
    2016-04-15| PLSC| Search report ready|Effective date: 20160415 |
    2017-02-28| PLFP| Fee payment|Year of fee payment: 5 |
    2018-02-26| PLFP| Fee payment|Year of fee payment: 6 |
    2019-10-25| ST| Notification of lapse|Effective date: 20191006 |
    2019-11-25| PLFP| Fee payment|Year of fee payment: 8 |
    2020-01-03| RN| Application for restoration|Effective date: 20191127 |
    2020-03-20| FC| Favourable decision of inpi director general on an application for restauration.|Effective date: 20200213 |
    2021-02-26| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1351599A|FR3002605B1|2013-02-22|2013-02-22|TORSION DAMPER FOR CLUTCH FRICTION DISC|
    FR1500505A|FR3018572B1|2013-02-22|2015-03-13|TORSION DAMPER FOR CLUTCH OF MOTOR VEHICLE|FR1500505A| FR3018572B1|2013-02-22|2015-03-13|TORSION DAMPER FOR CLUTCH OF MOTOR VEHICLE|
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