• 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 dry friction lining for a clutch, in particular a motor vehicle, comprising a friction material 2 fixed to a metal support 12 and comprising a friction face 6, at least one frustoconical groove 7, 8 being formed in the friction material, characterized in that the conicity of the frustoconical groove 7, 8 is between 10 and 35%, preferably between 17 and 30%.
    公开号:FR3048043A1
    申请号:FR1651387
    申请日:2016-02-19
    公开日:2017-08-25
    发明作者:Isabelle Alix；Gerard Crosland；Franck Delavente；Erick Lejamtel
    申请人:Valeo Materiaux de Friction SAS；
    IPC主号:
    专利说明:

    Annular friction pad for dry clutch
    The present invention relates to an annular friction lining for dry clutch, single or double, especially for motor vehicles, such as passenger vehicles or industrial vehicles.
    A clutch of a motor vehicle generally comprises a friction disk bearing on each of its faces friction linings fixed to a possibly common support, the support being fixed to a splined hub in engagement with an input shaft. a gearbox. A torsion damper is generally interposed between the friction lining support (s) and the splined hub. In addition, a progressivity device is conventionally placed between the two friction linings.
    The friction disk is placed between, on the one hand, a reaction plate connected directly or indirectly to the crankshaft of the engine of the vehicle and, on the other hand, a pressure plate of a clutch mechanism comprising a cover connected to the reaction plate and a clutch hub, such as for example an annular diaphragm, axially biasing the pressure plate which is rotatably connected to the lid while being able to move axially with respect to it in a limited manner.
    In the engaged position, the friction disc liners are clamped between the reaction plate and the pressure plate, so that the rotational torque of the engine is transmitted to the transmission input shaft.
    It is known to provide radial grooves in the friction linings, in order to eliminate any pollution (grease, oil, dust) that could be found on the friction surfaces.
    Such grooves also help to chase away any wear debris, especially during break-in, thus avoiding galling. These grooves also provide flexibility to the clutch disc to which the liner is attached, thereby improving clearance and minimizing clutch noise and vibration. However, these grooves weaken the friction linings and reduce their resistance to bursting. In addition, such grooves do not improve the performance of the clutch in the face of the so-called "fading" phenomenon. During a prolonged friction of the surfaces, the linings are subjected to a significant heating which has the effect of substantially reducing their coefficient of friction. This is caused by deterioration of the surface layers of the gaskets, thus acting as a lubricant between the healthy parts of the gaskets and the opposite friction surface of the countermaterial. This deterioration is directly related to the energy dissipated during the friction and the quality of the cooling of the linings.
    It is known in the prior art friction linings to limit this reduction in the coefficient of friction by a network of grooves with straight edges, radial or oblique on the one hand and circumferential on the other hand in the liner. These fittings are found to be satisfactory in terms of thermal resistance and stability of the coefficient of friction under normal conditions of use of the vehicle.
    However, under severe conditions of use, for example during a hill start sequence, the thermal power to be dissipated increases substantially. The thermal resistance of the lining is again degraded. This causes a decrease in the coefficient of friction. Therefore, under these severe conditions of use, the engine torque is not transmitted satisfactorily.
    Such disadvantages also limit the use of these friction linings in vehicles involving the transmission of power levels such as industrial vehicles, loaded passenger vehicles. The invention aims in particular to provide a simple, effective and economical solution to this problem. For this purpose, it proposes a friction lining for dry clutch, in particular of a motor vehicle, comprising a friction material fixed on a metal support and comprising a friction face, at least one frustoconical groove being formed in the friction material. , characterized in that the conicity of the frustoconical groove is between 10 and 35%, in particular between 17 and 30%.
    When the energy to be dissipated by the friction lining is high, especially under severe conditions of use, such a frustoconical groove satisfactorily cools the friction material in order to limit the degradation of its thermal resistance and thus to maintain its ability to transmit motor torque.
    The taper of the frustoconical groove can be defined with respect to an axis normal to the friction face.
    The friction face may be able to contact a counter-material, such as a reaction plate or a pressure plate of the clutch, to transmit the engine torque.
    According to a first variant of the invention the frustoconical groove is flared away from the metal support. According to a second variant of the invention, the frustoconical groove is flared towards the metal support.
    The first variant allows a satisfactory evacuation of dust and / or debris while the second variant makes it possible to maintain a maximized friction surface.
    The frustoconical groove may define a longitudinal axis and an orthogonal section of said frustoconical groove to this longitudinal axis may have: - a trapezoidal profile, and - an external flat base at a plane comprising the friction face of the friction material, and - a inner base parallel to the outer base.
    Successive inner bases can define a bottom of the frustoconical groove. This bottom may be parallel to the friction face.
    Alternatively, the bottom of the groove may be inclined, in particular curved, in a plane normal to the longitudinal axis.
    By placing itself in the first variant of the invention, the dimension of the outer base can be between 1.5 mm and 3 mm while the dimension of the inner base can be between 0.5 mm and 2.5 mm. . While placing in the second variant of the invention, the dimension of the outer base may be between 0.5 mm and 2.5 mm while the dimension of the inner base may be between 1.5 mm and 3 mm.
    According to another aspect of the invention, the ratio between: the minimum thickness of the friction material between the bottom of the frustoconical groove and the metal support, and the thickness of the friction material may be less than 0.2 .
    This small amount of material under the groove reduces the ability to axial deformation which leads over time to unevenness. This lack of flatness may take the form of a cone or a curtain of the friction face. The thickness of the friction material may be defined as the dimension of the friction material along an axis orthogonal to this friction face.
    The friction material may extend between the friction face and a fixing face facing the metal support.
    This ratio may preferably be between 0.08 and 0.14.
    According to one aspect of the invention, the ratio between: the minimum thickness of the friction material between the bottom of the frustoconical groove and the metal support, and the thickness of the metal support may be less than 1.
    This ratio may preferably be between 0.2 and 0.8.
    According to another aspect of the invention, the frustoconical groove extends in a substantially rectilinear, circumferential or ovoidal direction.
    The friction material may include a radially inner edge and a radially outer edge. The straight frustoconical groove can extend continuously between these two edges.
    According to another aspect of the invention, the frustoconical groove is inclined relative to any radius intersecting said groove. The longitudinal axis may in particular form an angle of between 10 and 20 °, in particular an angle of 15 °, with a radius intersecting the longitudinal axis at the radially inner edge.
    According to another aspect of the invention, a plurality of frustoconical grooves is formed in the friction material. Some may extend in a rectilinear direction, others may extend in a circumferential or ovoidal direction, these frustoconical grooves intersecting and forming friction pads forming the friction face.
    Such frustoconical grooves make it possible to maximize the surface of the friction face, in particular when these grooves are flared when approaching the metal support.
    According to another aspect of the invention, the thickness of the metal support is between 0.1 and 1 mm, in particular between 0.3 and 0.6 mm.
    According to another aspect of the invention, the thickness of the friction material is between 1.5 mm and 4 mm.
    According to another aspect of the invention, the friction material may be glued or overmolded on the metal support.
    According to another aspect of the invention, the friction lining may be annular.
    According to another aspect of the invention, the friction material comprises fibers, for example glass fibers, bonded together by an organic matrix. This matrix may comprise polymers, such as thermosetting resins, an elastomer, such as rubber and organic or inorganic fillers.
    The various elements of the friction material may be previously arranged to form a preform. The frustoconical grooves are obtained by removal of material once the annular shape of the friction lining obtained. As a variant, the friction material in its final form can be obtained by injection into a mold forming an imprint corresponding to the annular shape and the shape of the frustoconical grooves. The invention also relates to the use of a friction lining. according to the invention in a wet clutch for a motor vehicle. Such a clutch may comprise a liner having all or some of the features previously described for a lining in a dry clutch. The invention finally relates to a clutch disk, in particular for a motor vehicle, which comprises at least one friction lining as described above. The invention will be better understood and other details, features and advantages of the invention will become apparent on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which: FIG. 1 is a view in perspective of an example of friction lining according to the invention, - Figures 2a and 2b are detailed views of frustoconical grooves respectively according to a first variant and a second variant of the invention, - Figure 3 is a view detail of a frustoconical groove according to another example of the first variant, - Figures 4a, 4b, 5a and 5b are comparative graphs of performance of friction linings in and outside the perimeter of the invention, - the figure 6 is a diagram illustrating the reduction of the axial deformation of an example of a friction lining according to the invention under different conditions of use.
    Figure 1 shows an example of annular friction lining 1 for dry clutch. The lining 1 comprises a friction material 2 fixed on a metal support which will be illustrated later. The material 2 has radially inner 3 and outer 4 edges, a fixing face 5 facing a metal support, and a friction face 6 opposite to the attachment face and adapted to contact a counter-material, such as a reaction plate or a pressure plate of the clutch, for transmitting the engine torque.
    In the example described, the material 2 is glued or overmoulded on the metal support.
    In the example described, a plurality of frustoconical grooves 7, 8 is formed in the material 2, some 7 extending in a rectilinear direction, others 8 extending in a circumferential direction, these frustoconical grooves intersecting and forming friction pads 9, the meeting of these pads 9 defining the material 2 and the surface of these pads 9 furthest from the metal support forming the friction face 6.
    Furthermore, the straight frustoconical grooves 7 extend between the two radially inner edges 3 and outer 4 of the material 2 and all the grooves in the material 2 are frustoconical. The longitudinal axis of each rectilinear frustoconical groove 7 forms an angle of 15 ° with a radius intersecting the longitudinal axis at the radially inner edge 3.
    In the example described, the material 2 may comprise glass fibers, bound together by an organic matrix. This matrix may comprise thermosetting resins, an elastomer, a rubber and organic and inorganic fillers. The various elements of the friction material may be previously arranged to form a preform.
    The frustoconical grooves are obtained by removal of material once the annular shape of the friction lining obtained.
    Alternatively, the material 2 can be obtained by injection into a mold with an imprint corresponding to the annular shape and the shape of the frustoconical grooves.
    Figures 2a and 2b each show an orthogonal section of a frustoconical groove 7, 8 at a longitudinal axis of the illustrated groove. In FIG. 2a, according to a first variant, the frustoconical groove 7, 8 is flared away from the metal support 12 while in FIG. 2b, according to a second variant, the frustoconical groove 7, 8 is flared towards the metal support 12.
    According to the two variants, the frustoconical grooves 7, 8 have a trapezoidal profile, an outer base 14 flat to a plane comprising the friction face 6 and an inner base 15 parallel to the outer base. The successive inner bases here define a bottom 16 of the frustoconical groove and this bottom is parallel to the friction face 6. In a variant, the bottom of the groove can be inclined, in particular curved, in a plane normal to the longitudinal axis .
    According to the examples of FIGS. 2a and 2b, the taper of the frustoconical groove 7, 8 is between 10 and 35%, in particular between 17 and 30%, this taper being defined with respect to an axis normal to the friction face 6 .
    Finally, in the examples described in Figures 2a and 2b, the frustoconical groove 7.8 extends to the metal support 12 so that the friction pads 9 are disjoint from each other, the material 2 is then discontinuous. It should be noted that there may however remain a slight amount of material 2 under the frustoconical grooves 7, 8 not to touch the surface of the steel and not to transmit shear stresses in the glue joint to the interface between the material 2 and the metal support.
    In the example of the first variant described in FIG. 2a, the dimension of the outer base is between 1.5 mm and 3 mm while the dimension of the inner base is between 0.5 mm and 2.5 mm. .
    In the example of the first variant described in Figure 2b, the dimension of the outer base 14 is between 0.5 mm and 2.5 mm while the dimension of the inner base 15 is between 1.5 mm and 3 mm. These dimensions are calculated in the orthogonal planes as shown in Figures 2a and 2b.
    The materials 2 whose frustoconical grooves are described in Figures 2a and 2b can be made by another method to have frustoconical grooves extending to the metal support without fear of weakening the adhesive joint.
    The material 2 of FIGS. 2a and 2b may be obtained by another method than that already stated. This method comprises in particular the steps of: - producing the material 2 comprising the frustoconical grooves opening only at the level of the attachment face, - fixing the friction body on the metal support by adhesion of the fixing face, - machining the face friction, opposite the fixing face, until said groove opens at the second face of the friction body.
    The frustoconical groove 7, 8 shown in Figure 3 is another example of the first variant. In this example, the thickness of the material D-ι, defined between the friction face 6 and the attachment face 5, is between 1.5 mm and 4 mm and the thickness of the metal support D2 is between 0, 1 and 1 mm, in particular between 0.3 and 0.6 mm.
    In the example described in FIG. 3, the ratio R-ι between: the minimum thickness of the material between the frustoconical groove bottom and the metal support D3, and the thickness of the friction material Di is less than 0 2.
    Still in this example, the ratio R2 between: - the minimum thickness D3 of the material 2 between the bottom 16 of the frustoconical groove and the metal support 12, and - the thickness of the metal support D2 is less than 1.
    In the example described, the thickness of the friction material Di is defined as the dimension of the material 2 along an orthogonal axis with a friction face 6.
    In the example described in FIG. 3, the conicity, expressed as a percentage, is equal to:
    Figures 4a, 4b, 5a and 5b show the results of comparative tests of gaskets 1 in the scope of the invention and gaskets outside the perimeter of the invention.
    These tests were carried out on a test bench using a manual gearbox. To simulate the severe conditions of use, including hill start, it is imposed on the friction lining 1 to dissipate an energy of the order of 364 J / cm2. The gaskets 1 used for these tests have an internal diameter of the order of 137 mm and an outside diameter of about 200 mm. The dimension of the outer base of the frustoconical grooves is greater than 1.5 mm.
    During these tests, a sequence of starts has been imposed on each lining and the number of starts for which the lining transmits the engine torque satisfactorily has been accounted for.
    Under the conditions of the test, the seal satisfactorily transmits the torque when there is no slip, the coefficient of friction remains higher than 0.2 under plateau load conditions or constant setting.
    The structural characteristics of the gaskets used for tests outside the scope of the invention are shown in Table I, while the gaskets 1 within the scope of the invention used for the tests are shown in Table II.
    Table I
    Table II
    It should be noted that only the filling n ° 11 is flared when approaching the metal support 12.
    The results of the packing tests of Table I are reported in Figures 4a and 4b, and those of the packings of Table II in Figures 5a and 5b. The ordinate shows the number of starts under satisfactory torque transmission conditions expressed either as a function of Ri (FIGS. 4a and 5a) or as a function of R2 (FIGS. 4b and 5b).
    It can be seen that the packings of Table II are particularly advantageous, and that, for example, they make it possible to double the number of starts under severe conditions compared to the packings of Table I.
    The gaskets 1 according to the above examples also make it possible to reduce the ability to deform axially which causes a lack of flatness over time.
    Tests on gaskets at 25 ° C (initial state), then on gaskets having passed 4 hours at 140 ° C and finally on gaskets having passed 24h at 40 ° C and in 90% humidity were carried out (respectively A , B and C in Figure 6). At the end of these phases, these fillings were subjected to a load of 1000N which was gradually released to 20N.
    Each rectangle A, B, C represents, as a percentage, the reduction in the displacement in the plane comprising the friction face between a friction lining according to the invention and a control liner outside the perimeter of the invention.
    The axial displacement is respectively reduced by at least 65%, by at least 40% and by at least 50% for the A, B and C tests.
    In each of the tests presented, the examples of gaskets in and outside the scope of the invention differ only in the shape of their grooves. Their internal composition, their metal support, their number of grooves are identical to highlight the influence of the shape of the grooves according to the invention. The invention is not limited to the examples which have just been described.
    权利要求:
    Claims (11)
    [1" id="c-fr-0001]
    1. Clutch friction lining (1), in particular for a motor vehicle, comprising a friction material (2) fixed on a metal support (12) and comprising a friction face (6), at least one frustoconical groove (7, 8) being formed in the friction material, characterized in that the conicity of the frustoconical groove (7, 8) is between 10 and 35%, in particular between 17 and 30%.
    [2" id="c-fr-0002]
    2. friction lining (1) according to claim 1, characterized in that the frustoconical groove (7, 8) is flared away from the metal support (12).
    [3" id="c-fr-0003]
    3. friction lining (1) according to claim 1, characterized in that the frustoconical groove (7, 8) is flared closer to the metal support (12).
    [4" id="c-fr-0004]
    4. friction lining (1) according to claim 2, characterized in that the frustoconical groove (7, 8) defines a longitudinal axis, an orthogonal section of the frustoconical groove to this longitudinal axis having: - a trapezoidal profile, and - an outer base (14) flat to a plane comprising the friction face (6) of the friction material, and - an inner base (15) parallel to the outer base, the dimension of the outer base (14) being between 1 , 5 mm and 3 mm, the dimension of the inner base (15) being between 0.5 mm and 2.5 mm.
    [5" id="c-fr-0005]
    5. friction lining (1) according to claim 3, characterized in that the frustoconical groove (7, 8) defines a longitudinal axis, an orthogonal section of the frustoconical groove to this longitudinal axis having: - a trapezoidal profile, and - an outer base (14) flat to a plane comprising the friction face (6) of the friction material, and - an inner base (15) parallel to the outer base, the dimension of the outer base (14) being between 0 , 5 mm and 2.5 mm, the dimension of the inner base (15) being between 1.5 mm and 3 mm.
    [6" id="c-fr-0006]
    6. friction lining (1) according to one of the preceding claims, characterized in that the ratio (R-ι) between: - the thickness of the friction material between the bottom (16) of the frustoconical groove and the support metal D3, and the thickness of the friction material D1 is less than 0.2.
    [7" id="c-fr-0007]
    7. friction lining (1) according to one of the preceding claims, characterized in that the ratio (R2) between: - the minimum thickness of the friction material between the bottom (16) of the frustoconical groove and the metal support D3, and the thickness of the metal support D2 is less than 1.
    [8" id="c-fr-0008]
    8. friction lining (1) according to one of the preceding claims, characterized in that the frustoconical groove (7, 8) extends in a substantially rectilinear, circumferential or ovoidal direction.
    [9" id="c-fr-0009]
    9. friction lining (1) according to one of the preceding claims, characterized in that a plurality of frustoconical grooves (7, 8) is formed in the friction material, some (7) extending in a rectilinear direction , others (8) extending in a circumferential or ovoidal direction, these frustoconical grooves (7, 8) intersecting and forming friction pads (9).
    [10" id="c-fr-0010]
    10. friction lining (1) according to one of the preceding claims, characterized in that the thickness of the metal support (12) is between 0.1 and 1 mm, in particular between 0.3 and 0.6 mm .
    [11" id="c-fr-0011]
    11. Clutch disc, in particular for a motor vehicle, characterized in that it comprises at least one friction lining (1) according to one of claims 1 to 10.
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3048043A1|2017-08-25|ANNULAR FRICTION TRIM FOR DRY CLUTCH
    EP2362111B1|2020-08-05|Annular friction lining for a dry clutch
    EP0251849A1|1988-01-07|Damping flywheel, especially for a torque-transmitting device
    FR2700192A1|1994-07-08|Split steering wheel.
    FR2767368A1|1999-02-19|TORSIONAL OSCILLATOR AND METHOD FOR MANUFACTURING SUCH A SHOCK ABSORBER
    EP2753851B1|2015-11-18|Pinion vibration damping using viscoelastic patch
    FR2745878A1|1997-09-12|BALANCING MASS DEVICE COMPRISING A SYSTEM OF SMOOTH BEARINGS FOLLOWING A TRAINING
    FR2688564A1|1993-09-17|Double damping flywheel, particularly for motor vehicles
    EP0953783B1|2003-09-03|Clutch release bearing with vibration damping
    FR2657930A1|1991-08-09|TWO-DISC CLUTCH.
    FR2925639A1|2009-06-26|DOUBLE FLYWHEEL IMPROVED DAMPER FOR CLUTCH, IN PARTICULAR OF A MOTOR VEHICLE
    FR3029583A1|2016-06-10|PENDULUM DAMPING DEVICE FOR A MOTOR VEHICLE TORQUE TRANSMITTING DEVICE
    WO2013034861A1|2013-03-14|Pinion vibration damping using viscoelastic patch
    EP3483470A1|2019-05-15|Clutch friction device
    EP0704636A1|1996-04-03|Controllably sliding clutch, especially for automotive vehicles
    EP3101309B1|2018-01-03|Clutch disc
    WO2013079875A1|2013-06-06|Lining-holder disc having smooth engagement means made of an elastomer material
    EP1117946A1|2001-07-25|Clutch torsional vibration damper, in particular for motor vehicles
    WO2019158626A1|2019-08-22|Friction lining for clutch and friction disk for clutch comprising same
    FR3058195B1|2019-11-15|FILTERING MECHANISM BETWEEN TWO ROTATING BODIES AND CLUTCHES EQUIPPED WITH SUCH A MECHANISM
    FR3057931B1|2019-11-01|COUPLER TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE
    FR3058769B1|2019-11-01|ASSEMBLY FOR A TORQUE TRANSMISSION DEVICE
    EP1802886B1|2014-06-11|Dry friction lining for the friction device of a dry clutchfor a motor vehicle, a dry friction device, a dry friction clutch and a mould for moulding a friction lining
    EP3685070A1|2020-07-29|Torque transmission device, torsion damper and associated assembly
    EP2160521B1|2015-11-11|Device for dampening torsion oscillation in a friction clutch in particular for an automobile
    同族专利:
    公开号 | 公开日
    FR3048043B1|2018-03-09|
    CN107100945A|2017-08-29|
    DE102017103019A1|2017-08-24|
    KR20170098176A|2017-08-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20080236985A1|2007-04-02|2008-10-02|Ritsuo Toya|Wet type friction plate|
    EP2236851A1|2009-03-31|2010-10-06|Carl Freudenberg KG|Coupling lining|
    FR2956710A1|2010-02-22|2011-08-26|Valeo Materiaux De Friction|DRY FRICTION TRIM, IN PARTICULAR FOR A CLUTCH OF A MOTOR VEHICLE|WO2019158626A1|2018-02-16|2019-08-22|Valeo Materiaux De Friction|Friction lining for clutch and friction disk for clutch comprising same|
    US20190346000A1|2018-05-09|2019-11-14|Bremskerl North America, Inc.|Grooved Disc Brake|
    CN108916637B|2018-06-27|2020-06-16|西南科技大学|Friction surface influencing friction force and design method thereof|
    DE102019113727A1|2019-05-23|2020-11-26|Bayerische Motoren Werke Aktiengesellschaft|Switchable friction disc clutch for a motorcycle and motorcycle drive system with such a clutch|
    法律状态:
    2017-02-28| PLFP| Fee payment|Year of fee payment: 2 |
    2017-08-25| PLSC| Search report ready|Effective date: 20170825 |
    2018-02-26| PLFP| Fee payment|Year of fee payment: 3 |
    2019-02-28| PLFP| Fee payment|Year of fee payment: 4 |
    2020-11-06| ST| Notification of lapse|Effective date: 20201006 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1651387A|FR3048043B1|2016-02-19|2016-02-19|ANNULAR FRICTION TRIM FOR DRY CLUTCH|FR1651387A| FR3048043B1|2016-02-19|2016-02-19|ANNULAR FRICTION TRIM FOR DRY CLUTCH|
    DE102017103019.0A| DE102017103019A1|2016-02-19|2017-02-15|Annular friction lining for a dry clutch|
    KR1020170020954A| KR20170098176A|2016-02-19|2017-02-16|Annular friction lining for dry clutch|
    CN201710304086.0A| CN107100945A|2016-02-19|2017-02-17|Annular friction lining for dry clutch|
    [返回顶部]