• 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 device (1) with wear compensation, particularly for a motor vehicle, comprising a pressure plate (3) intended to bear against a friction disk of the clutch device (1), a diaphragm (9) for actuating the pressure plate (3) and means for compensating for wear of the friction disc being interposed between the diaphragm (9) and the pressure plate (3).
    公开号:FR3018879A1
    申请号:FR1452307
    申请日:2014-03-20
    公开日:2015-09-25
    发明作者:Fabien Lebeau；Gilles Lebas；Herve Maurel；Carsten Lauridsen
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a wear-catching clutch device, in particular for a motor vehicle. A clutch device conventionally comprises a reaction plate, a movable pressure plate and a friction disk mounted between said reaction and pressure plates. The movement of the pressure plate is controlled by a diaphragm, itself controlled by a clutch abutment. The clutch stop is controlled by an actuator controlled by an electronic computer to exert a predetermined force on the diaphragm and move it over a given distance. The pressure plate is thus movable between a clutch position in which the friction disk is clamped between said pressure and reaction plates, and a disengaging position in which the friction disk is released. The use of the clutch device causes wear of the friction disc liners and the counter-materials of the associated pressure and reaction plates. This results in a variation of the position of the pressure plate relative to the associated diaphragm and / or with respect to the reaction plate, generating a variation of the friction disk clamping force and a modification of the licking point and the stroke of the clutch stop. It is recalled that the licking point is the position from which a torque can be transmitted through the clutch device. A wear-catching clutch device is known from document FR 2780 119. This device comprises a cover inside which is mounted a pressure plate intended to bear on a friction disk, a diaphragm inserted between the cover and pressure plate, for actuating the pressure plate between a fully engaged position in which said pressure plate is pushed against the friction disk, and a fully disengaged position in which said pressure plate is moved away from the disk friction by means of return means of the pressure plate.
    [0002] Means for catching the wear of the friction disk are interposed between the diaphragm and the pressure plate, and comprise at least one retrofit member movable in a determined range and having a ramp cooperating with a counter-ramp turned on the side of the diaphragm. pressure plate, so as to adjust the distance between the diaphragm and the pressure plate and compensate the wear of the friction disc according to the angular position of the ramp relative to the counter-ramp. The device further comprises wear detecting means capable of permitting the displacement of the movable member of the wear compensating means in the event of wear of the friction disk and able to prevent such displacement when this wear does not occur. is not sufficient, said detection means comprising at least one movable detection member, in a given range, with respect to the catch member and having a ramp cooperating with a counter-ramp turned on the side of the pressure plate.
    [0003] Finally, the device comprises a pressure member constraining the ramps of said movable members against the associated counter ramps, the pressing member being adapted to cooperate with a fixed stop, so as to release said movable members when a wear of the friction disc is detected.
    [0004] The movable catch member is biased by means of a spring, so as to catch the clearance between the latter and the pressing member, when said movable catch member is released by the pressure member and the diaphragm . Furthermore, the mobile detection member is biased by a spring so as to catch the clearance between the latter and the pressing member, when said movable detection member is released by the pressing member and the diaphragm.
    [0005] In operation, the assembly is subjected, alternately, to successive phases of clutch and disengagement. In the clutch phase, the diaphragm presses on the pressure plate, via the catch member. In the disengaging phase, the pressure plate is returned to its disengaged position, by means of return means generally taking the form of elastically deformable tongues. When the friction disk is not worn and the counter-materials of the pressure and reaction plates are not worn, the pressing member constantly holds the detection member and the catch member resting on the disk pressure: said organs are immobilized. In case of wear, the pressure member bears on the stop and a play is created between the pressing member and the detection member. As the latter is constrained by a spring, it is moved to fill the game above. In the engaged position, the force applied by the diaphragm on the catch member prevents the displacement of the latter, by pressing and friction on the pressure plate. Then, when the diaphragm is moved to its disengaged position, the return tongues of the pressure plate tend to press the pressure plate against the catch member, and the catch member against the diaphragm. The force exerted by the return tongues is relatively small so as to allow, despite the friction in play, a displacement of the catch member, under the effect of the stress applied by the corresponding spring. This movement makes it possible to make up the clearance between the pressing member and the catching member. This compensates for the wear of the friction plate as well as the wear of the counter-materials of the associated pressure and reaction plates. Such a clutch device has a relatively complex structure, requiring the presence of a mobile retraction member and a movable detection member, which generates significant costs. The patent application FR 2 424 442 discloses a clutch device for wear compensating for a motor vehicle, comprising a pressure plate intended to abut on a friction disc of the clutch device, a diaphragm serving for actuation of the pressure plate between a fully engaged position in which said pressure plate is pushed against the friction disk, and a fully disengaged position in which said pressure plate is moved away from the friction disk by means of return means of pressure plate, a compensating member of the wear of the friction disc, interposed between the diaphragm and the pressure plate, and movable in rotation about an axis in a determined range, said catch member comprising a ramp co-operating with a counter-ramp turned on the side of the pressure plate, so as to adjust the distance between the diaphragm and the pressure plate and compensate the usur e friction disc according to the position of the ramp relative to the counter-ramp. The clutch device further comprises displacement means comprising a drive member adapted to engage with a toothed portion, for example a rack, of the catch member and adapted to move said catch member in case of friction disk wear, said toothed portion of the catch member including axially oriented teeth. In this case, the structure of the device is less complex since it no longer includes a mobile detection member. In FR 2 424 442, the catch member has an annular shape and the toothed portion is a rack in the form of a circular arc. The driving member is formed by an endless screw, pivotally mounted about an axis extending substantially in the direction of the toothed portion, that is to say along the tangent to the circumferential direction of the rack. . The auger has a helical thread engaging the teeth of the rack. The force of transmission of the net to the teeth of the rack is oriented normal to the surface of the net. This force is then directed obliquely to the direction of the rack, that is to say relative to the tangent to the circumferential direction of the rack. This force thus comprises a radially directed component, generating friction and a loss of efficiency in the transmission of effort, which can affect the operation of the device. The object of the invention is in particular to provide a simple, effective and economical solution to these problems. For this purpose, it proposes a clutch device with a wear-compensating clutch, in particular for a motor vehicle, comprising a pressure plate intended to bear on a friction disk of the clutch device, a diaphragm serving for actuation. of the pressure plate between a fully engaged position in which said pressure plate is pushed against the friction disk, and a fully disengaged position in which said pressure plate is moved away from the friction disk by means of return means. pressure plate, a compensating member of the wear of the friction disc, inserted between the diaphragm and the pressure plate, and movable in rotation about an axis in a determined range, said catching member comprising a co-operating ramp with a counter-ramp turned on the side of the pressure plate, so as to adjust the distance between the diaphragm and the pressure plate and compensate the usur e of the friction disk as a function of the position of the ramp relative to the counter-ramp, the clutch device comprising displacement means comprising a drive member adapted to engage a toothed portion, for example a rack, the catch member and adapted to move said catch member in case of wear of the friction disc, said toothed portion of the catch member extending in a circumferential direction and comprising axially oriented teeth , characterized in that the driving member is pivotally mounted about an axis extending substantially perpendicular to the direction of the toothed portion, said driving member being configured to transmit a force oriented perpendicularly to said pivot axis.
    [0006] In this way, in the case where the toothed portion is an arcuate rack for example, the transmission member applies a force directed solely in the direction of the rack, that is to say along the tangent to the circumferential direction of the rack. This effort therefore does not include a radial component generating friction and a loss of efficiency in the transmission of effort. The structure of such a device is also relatively simple, which reduces its cost. According to one characteristic of the invention, the retrofit member is in the form of a ring having an end adapted to bear on the diaphragm and an end having at least one ramp extending circumferentially, cooperating with the counter associated boom turned on the side of the pressure plate. In this case, the catch member may comprise a first and a second concentric annular portion connected to each other by radial tabs, the first annular portion of the catch member having the end adapted to come into operation. support on the diaphragm and the end comprising the ramp, the second annular portion of the catch member having an end comprising the toothed portion engaging with the displacement means.
    [0007] Preferably, the device comprises a lid inside which are mounted, at least in part, the pressure plate and the diaphragm, the diaphragm being interposed between the lid and the pressure plate, the lid having a stop adapted to cooperate with the catch member so as to immobilize it in position during disengagement, in particular in the fully disengaged position of the diaphragm.
    [0008] According to one embodiment, the displacement means may comprise a toothed wheel maintained in engagement with the toothed portion of the catch member, said toothed wheel being coupled in rotation to a ratchet wheel cooperating with a pawl whose position of free end is controlled and is independent of the friction disc wear, the position of the ratchet wheel relative to said free end of the ratchet varying according to the friction disc wear and the position of the disc plate. pressure so that the pawl is adapted to drive the ratchet wheel, in case of wear of the pressure plate, by moving the pressure plate between its engaged and disengaged positions. In this case, the toothed wheel can be held in abutment on the toothed part of the catch member by means of elastic means, such as for example an elastic tongue. Furthermore, the pawl and / or the elastic means for holding the gear wheel can be fixed to the cover, for example by means of the same rivet. The pawl may be in the form of a resilient lamella, a portion of which is able to bear against the lid so as to guarantee the correct axial positioning of the end of the pawl.
    [0009] According to another embodiment, the displacement means may comprise a pawl pivoting about a first axis and whose free end is held in abutment on the teeth of the toothed part of the catching member by means of elastic return means, the pawl being adapted to be arched in the bottom of a tooth in case of wear of the friction disk and during a disengaging phase, so as to cause the movement of the ramp of the catch member with respect to the associated counter ramp. The first axis may be formed at one end of a lever, said lever being pivotally mounted about a second axis fixed relative to the lid.
    [0010] In this case, another end of the lever, opposite the end of the lever supporting the pawl axis, may be able to bear against the catch member. Alternatively, another end of the lever, opposite the end of the lever supporting the pawl axis, may be adapted to bear against a portion of the diaphragm. The invention also relates to a double clutch, characterized in that it comprises at least one device of the aforementioned type. A dual clutch allows in particular to alternately couple the motor shaft of the vehicle with two coaxial input shafts of a gearbox, which can be of the robotic type. Thus, a dual clutch allows to change gears while maintaining the transmission of a torque engine to the vehicle wheels. Indeed, the two clutches are respectively associated with even and odd gear ratios. During a gearshift, a first clutch is disengaged while the second clutch is engaged, so that the engine torque is progressively transferred from the first to the second clutch. Each clutch comprises a mechanism comprising a diaphragm for cooperating with a pressure plate integral in rotation with the cover and the motor shaft. Each diaphragm is movable by means of a corresponding clutch abutment, between a rest position and an active position. Depending on the type of clutch, the active position of the diaphragm corresponds to a coupling or decoupling of the shafts of the engine and the gearbox and the rest position of the diaphragm corresponds to a decoupling or a coupling of these shafts. These are respectively a normally open clutch and a normally closed clutch. For safety reasons, at least one of the clutches is of the normally open type.
    [0011] The clutch stop is controlled by an actuator controlled by an electronic computer to exert a predetermined force on the diaphragm and move it over a given distance. The pressure plate of each clutch, biased by the corresponding diaphragm, is intended to clamp a friction disc on a corresponding reaction plate. A reaction plate may be provided for each clutch. Alternatively, a single reaction plate common to both clutches, mounted between the two friction discs, is used. Each friction disc is rotatably connected to an input shaft 10 of the gearbox and each reaction plate is for example integral in rotation with a flywheel connected to the drive shaft. Thus, the clamping of a friction disk between the corresponding pressure and reaction plates allows the transmission of a torque between the drive shaft and the associated gearbox shaft. As before, the use of the clutches causes wear of the friction linings of the friction discs as well as counter-materials of the associated pressure and reaction plates. This results in a variation of the position of each pressure plate relative to the associated diaphragm and / or the reaction plate, causing a variation in the friction disk clamping force and a change in the licking point and the race at the clutch stop. In this case, the licking point is the position from which a portion of the engine torque is transmitted to the gearbox shaft when closing the clutch. In general, such wear is more present at the friction disc and the pressure and reaction plates belonging to the first clutch, that is to say to the clutch associated with the odd-speed ratios. Thus, when the double clutch comprises only one device according to the invention, it preferably forms part of the first clutch. Of course, the double clutch according to the invention may comprise both a device equipping the first clutch and a device fitted to the second clutch. The invention will be better understood and other details, characteristics 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: FIGS. 1 to 6 illustrate a clutch device according to a first embodiment, in particular - Figure 1 is a front view of a clutch device - Figure 2 is a sectional view of the clutch device, according to line II FIG. 3 is a perspective view, partially cut away, of part of the clutch device; FIG. 4 is a detail view of a part of the device, in particular of FIG. the ratchet wheel and the associated pawl, illustrating an engaged condition of the device, in the absence of wear of the friction linings, - Figures 5 and 6 are views corresponding to Figure 4, illustrating a case of wear of the friction linings - Figures 7 to 9 illustrate a clutch device according to a second embodiment, in particular - Figure 7 is a perspective view and partially cut away, of a part of the clutch device - Figure 8 is a detail view and in perspective of a part of the device, - Figure 9 is a view schematically showing different positions of the pawl, - Figures 10 to 13 illustrate a clutch device according to a third embodiment, in particular - Figure 10 is a view of perspective and with partial tearing, of a part of the clutch device, - Figures 11 and 12 are detailed views of a part of the device, - Figure 13 is a schematic view of part of the device, - FIGS. 14 to 16 illustrate a clutch device according to a fourth embodiment, in particular - FIG. 14 is a perspective view, with partial tearing, of part of the clutch device, FIGS. 15 and 16 are detailed views of a part of the device. A clutch device 1, in particular for a motor vehicle, according to a first embodiment of the invention is illustrated in FIGS. 1 to 6 and comprises a bell-shaped cover 2 of axis A, inside which is mounted a pressure plate 3 for bearing on a friction disc of the clutch device. The cover 2 comprises an annular portion 4 extending radially, a radially outer peripheral portion 5, extending rearwardly, comprising zones 6, some of which allow the attachment of the cover 2 to an axially fixed member of the clutch device. and more than others allow the attachment of elastic tongues 7. More particularly, several groups of tabs 7 stacked one on the other can be fixed between the cover 2 and the pressure plate 3. Each tab 7 of the same group is then attached to zones 6 of the cover 2 at a first end and to tabs 8 of the pressure plate 3 at a second end. This fixing is provided by means of rivets. In this way, the pressure plate 3 is subjected to a large return force, for example between 0 and 600 N (in the case of a passenger vehicle) or between 0 and 2000 N (in the case of a passenger car). 'an industrial vehicle), directed axially forward. The pressure plate 3 is thus returned to a so-called declutching position, in which it is spaced apart from the friction disc. A diaphragm 9 is interposed axially between the cover 2 and the pressure plate 3 and serves to actuate the pressure plate 3 between a fully engaged position in which said pressure plate 3 is pushed against the friction disk, and a position fully disengaged wherein said pressure plate 3 is spaced from the friction disk by means of the elastic tongues 7. The diaphragm 9 is annular and has, at its radially inner periphery, fingers 10 extending radially inwards. These fingers 10 are intended to cooperate with a clutch abutment, as is well known per se. The diaphragm 9 further bears on areas 11 protruding from the cover, so that it deforms and pivots around said areas 11, in operation. Wear compensating means are interposed axially between the pressure plate and the diaphragm. More particularly, the diaphragm 9 cooperates with said wear compensating means in an area located radially outside the bearing areas 11 of the cover 2. These means comprise a movable catch member 12 comprising a radially inner annular portion 13 and a radially outer annular portion 14, the two parts 13, 14 being concentric and of axis A. The two parts 13, 14 are connected by lugs 15 extending radially. The radially inner portion 13 of the mobile retraction member 12 has an end 16 against which the diaphragm is able to come into abutment, and an end comprising at least one ramp 17 extending circumferentially, cooperating with an associated counter ramp 18 arranged directly on the pressure plate 3.
    [0012] By way of example, the angle of each ramp 17 of the catch member 2 and the associated counter ramp 18 of the pressure plate 3 is between 2 ° and 12 °. The radially outer portion 14 of the movable catch member 12 has an end 19 having a toothed portion forming a circumferentially extending rack 20 and a toothed portion 21 extending circumferentially, angularly offset from the rack 20. The other end 22 of the radially outer portion 14 bears on the pressure plate.
    [0013] The device 1 further comprises displacement means adapted to engage the catch member 12 and able to move said catch member 12 in case of wear of the friction disc. More particularly, the displacement means comprise a toothed wheel 23 kept in mesh with the rack 20.
    [0014] The toothed wheel 23 is pivotally mounted about an axis 24 fixed at one end of an elastic strip 25, the other end of said strip being fixed to the lid by means of a rivet 26. The elastic tongue 25 allows to maintain the toothed wheel 23 resting on the rack 20 of the movable catch member 12.
    [0015] The axis 24 is oriented radially, that is to say perpendicular to the tangent to the circumferential direction of the rack 20. The toothed wheel 23 is coupled in rotation to a ratchet wheel 27 cooperating with a pawl 28 whose position the free end 29 is controlled and is independent of the wear of the friction disc. The position of the ratchet wheel 27 with respect to said free end 29 of the pawl 28 varies as a function of the wear of the friction disk and the position of the pressure plate 3, so that the pawl 28 is adapted to driving the ratchet wheel 27, in case of wear of the pressure plate 3, by moving the pressure plate 3 between its engaged and disengaged positions.
    [0016] The pawl 28 is also in the form of an elastic lamella, one end of which is fixed to the lid by the aforementioned rivet 26 and the other end of which is bent in the manner of a hook so as to bear against teeth of the ratchet wheel 27. A portion 30 of the curved region of the pawl 28 bears on a tab 31 of the cover 2 forming a stop, so as to control the axial position of the end of the pawl 28. As is shown in Figure 4, the displacement means are inoperative when the friction disc linings are not or little worn and the counter-materials of the pressure plates 3 and associated reaction are not worn, for example when the cumulative axial wear is less than 0.1 mm. In fully engaged position, illustrated in FIG. 4, the diaphragm 9 bears on the catch member 12 so as to push the pressure plate 3 against the elastic return tongues 7. The pressure plate 3 and the corresponding reaction plate (axially fixed) then grip the friction disk carrying the liners. In this fully engaged position, the free end 29 of the pawl 28 is situated on the top of a tooth 32 so that, during the next disengaging phase, the free end 29 of the pawl 28 follows the ramp of the tooth corresponding 32 without ever fully reaching the bottom of the tooth 32 so as to push the ratchet wheel 27. Therefore, in the absence of pronounced wear, the ratchet wheel 27 is not rotated during the phases of successive clutch and disengagement.
    [0017] FIGS. 5 and 6 illustrate the case where the linings of the friction disc (or else the counter-materials of the pressure and reaction platens 3) exhibit significant wear, that is to say greater than 0.1 mm per second. example, that it is necessary to catch up in order to avoid a malfunction of the clutch device 1.
    [0018] In this case, the catching member 12, the pressure plate 3 and the ratchet wheel 27 are displaced along the axis A by a value sufficient to allow the free end 29 of the pawl 28, fixed axially because in stop on the cover 2, to jump a tooth 32 (Figure 5). In this way, during the disengagement phase, the free end 29 of the pawl 28 is bent on the bottom of the tooth 32 so as to rotate the ratchet wheel 27 during the ascent (the term " lift "is used with reference to Figure 5) of the pressure plate 3 and the catch member 12, as shown in Figure 6. The pivoting of the ratchet wheel 27 is performed in the direction indicated by the arrow 33 in Figure 6. The toothed wheel 23 being held in abutment on the rack 20 by the elastic tongue 25, the pivoting of the ratchet wheel 27 thus drives that of the toothed wheel 23 and the displacement of the catch member 12 in the direction indicated by the arrow 34. The pivoting of the catch member 12 relative to the pressure plate 3, and therefore the movement of the ramp 17 relative to the associated counter ramp 18, makes it possible to catch up with aforesaid wear, in whole or in part. If necessary, other wear-compensating phases, similar to those described above, can take place during the following clutch and disengagement phases, in the same manner as previously. Note that the toothed wheel 23 applies a force directed only in the direction of the rack 20, that is to say along the tangent to the circumferential direction of the rack 20. This force therefore does not include a radial component generating friction and a loss of efficiency in the transmission of effort. It will also be noted that the cover comprises lugs 35 forming axial abutments and having a notch adapted to cooperate with the toothed portion 21 in order to prevent the rotation of the catch member 12 when it bears on the lugs 35. These stops 35 thus provide the following functions: - limit the axial travel of the pressure plate 3 to a specified minimum lift, - form a fixed fulcrum by blocking the position of the catch member 12, prevent a surge catching or under-catching of wear, by blocking the effect of possible axial vibrations and possible torsional vibrations. Figures 7 to 9 show a clutch device 1 according to a second embodiment of the invention. This device 1 differs from that described above by the structure of the displacement means adapted to come into engagement with the catch member 12 and able to move said catch member 12 in case of wear of the friction disk. The elements having the same function and substantially the same structure as those described above have been designated by the same references.
    [0019] More particularly, the displacement means comprise latching means in the form of a pawl 36 pivotally mounted about an axis formed by a rivet 37 fixed to the cover 2. This axis 37 is oriented radially, it is that is to say perpendicular to the circumferential direction of the toothed portion 20. Note that in this embodiment, the toothed portion 20 (intended to cooperate with the pawl 36) and the toothed portion 21 (intended to cooperate with a stop 35) can be formed by one and the same toothed part. The pawl 36 comprises a pointed end zone 38 intended to cooperate with a toothed portion 20 of the catch member 12. As can be seen more clearly in FIG. 9, the teeth of the toothed portion 20 have sloping surfaces 39 permitting the sliding of the pointed zone 38 of the pawl 36 in a direction of movement of the pawl with respect to the catch member, and axially extending surfaces 40 forming stops which prevent the pawl 36 from moving relative to the catch member 12 in an opposite direction.
    [0020] The pawl 36 is constrained by a torsion spring 41, so that the pointed zone 38 is held in abutment against the corresponding teeth of the retraction member 12. The operation of such a clutch device 1 is to be now described in more detail. The displacement means are inoperative when the linings of the friction disc are not or little worn and that the counter-materials of the pressure plates 3 and associated reaction are not worn, for example when the cumulative axial wear is less than 0.1 mm.
    [0021] In the fully engaged position, in particular, the diaphragm 9 bears on the catch member 12, so as to push the pressure plate 3 against the elastic return tongues 7. The pressure plate 3 and the reaction plate corresponding (axially fixed) then grip the friction disc carrying the linings.
    [0022] In this fully engaged position, the free end (that is to say, the pointed zone 38) of the pawl 36 is located on the top of a tooth (see FIG. 9, position P1) so that, when the next declutching phase, the free end 38 of the pawl 36 follows the ramp 39 of the corresponding tooth without ever come to bear on the axial face 40 of the bottom of the tooth so as to push the catch member 12. By therefore, in the absence of pronounced wear, the catch member 12 is not rotated about its axis A during successive clutch and disengage phases. In the event of significant wear of the friction disc liners (or the counter-materials of the pressure and reaction plates 3), that is to say greater than 0.1 mm for example, it is necessary to catch up the clearance thus formed in order to avoid a malfunction of the clutch device 1. In this case, in the declutching phase, the catching member 12 and the pressure plate 3 are displaced by a value sufficient to allow the free end 38 of the pawl 36 to jump a tooth (P2 position in Figure 9) and allow the pawl 36 to pivot slightly about its axis 37. In this way, the free end 38 of the pawl 36 is bent-bouter on the bottom of the tooth, that is to say bears on the corresponding axial face 40 (position P3 in Figure 9), so as to rotate the catch member 12 during the ascent (the term "Lift" is used with reference to the figures) of the pressure plate 3 and the rattra member page 12. In the fully disengaged position, the pawl 36 is in the position referenced P4 in FIG. 9.
    [0023] The pivoting of the catch member 12 relative to the pressure plate 3, and thus the displacement of the ramp 17 relative to the associated counter ramp 18, makes it possible to make up the above-mentioned wear, in whole or in part. If necessary, other wear-compensating phases, similar to those described above, can be used during the following clutch and disengagement phases, in the same manner as previously. FIGS. 10 to 13 illustrate a third embodiment of the invention, which differs from those described with reference to FIGS. 7 to 9 in that the displacement means comprise latching means comprising a lever 42 pivotally mounted around an axis 37 formed by a rivet fixed to the cover 2. The axis 37 is oriented radially, that is to say perpendicularly to the circumferential direction of the rack. A first end 43 of the lever 42 is able to bear on the end 19 of the outer part 14 of the catch member 12, a pawl 36 being pivotally mounted about an axis 44 mounted at the second end. 45 of the lever 43. The axes 37 and 44 are parallel. The pawl 36 comprises, as before, a pointed end zone 38 intended to cooperate with the toothed portion 20 of the catch member 12. The teeth of the toothed portion 20 have oblique surfaces 39 allowing the sliding of the point region 38 of the pawl 36 in one direction of movement of the pawl 36 relative to the retraction member 12, and axially extending surfaces 40 forming stops preventing the pawl 36 from moving relative to the pawl member. catching 12 in an opposite direction.
    [0024] The pawl 36 is constrained by a torsion spring 41, so that the pointed zone 38 is held in abutment against the corresponding teeth of the catch member 12. The pitch of the toothed portion 20 is the distance separating by example two tops of adjacent teeth. To facilitate the realization of this toothed portion 20, it is necessary that the pitch is sufficiently large. For this, the latching means use the lever 42 to amplify the disengagement height, that is to say the stroke or the lifting of the pressure plate 3 during the disengaging phase. Indeed, the pitch of the toothed portion 20 is related to the geometry of the latching means and to the value of said lifting of the pressure plate 3. The use of such a lever 42 makes it possible to adapt to any type of mechanism and all the variations of the lifting of the pressure plate 3. The use of a lever 42 makes it possible to bring the pivot axis 44 of the pawl 36 closer to the catch member 12 when it rises when of the disengagement.
    [0025] With reference to FIG. 13, when the retrofit member 12 rises along the axis A by a determined value, the lever 42 tilts around the axis 37 at a determined angle and drives the pawl 36 downwards. mounted on the lever 42. The multiplication ratio R of the axial displacement of the pawl 36 is a function of the lengths of the parts of the lever 42 respectively connecting the first end 43 to the axis 37 (length a) and the second end 45 to the axis 37 (length b), and respective angles a, and ab relative to the horizontal (in the case of Figure 13). Indeed, the ratio R is defined by the following formula: R = (b.cos ab) / (a.cos aa).
    [0026] The operation of such a clutch device 1 is similar to that described above with reference to FIGS. 6 to 9.
    [0027] FIGS. 14 to 16 illustrate a variant in which the first end 43 of lever 42 comprises a tab 46 bent radially inwards, intended to bear against a radially outer lobe 47 of the diaphragm 9, the second end 45 of the lever serving , as previously, to the mounting of the pivot pin 44 of the pawl 36. A torsion spring 48 mounted around the axis of pivoting of the lever makes it possible to constrain the tab 46 of the lever 42 resting on the lobe 47 of the diaphragm 9 .
    [0028] When, during the disengagement phase, the diaphragm 9 is detached from the corresponding end 16 of the inner part 13 of the catch member 12, a stop 49 of the lever 42, extending from the second end 45 of the lever 42, bears against an area of the cover 2. In this case, the contact between the tab 46 of the lever 42 and the lobe 47 of the diaphragm 9 is interrupted. Of course, the contact between the tab 46 of the lever 42 with the lobe 47 of the diaphragm 9 may be obtained by other means not shown, such as for example by an elastic tongue connected to the cover 2 and ensuring a pinch of the lever 42 with the lobe 47, or by a tab linked to the cover 2 and exerting a force tending to bring the stop 49 of the lever 42 of the corresponding area of the cover 2. The multiplication ratio R obtained with such a lever 42 is similar to that described above. In each of the embodiments described above, the force exerted by the pawl 36 on the toothed portion 20 is directed solely in the direction of the toothed portion 20, that is to say along the tangent to the circumferential direction of the toothed portion 20. Toothed portion 20. This force therefore does not include a radial component generating friction and a loss of efficiency in the transmission of effort.
    权利要求:
    Claims (13)
    [0001]
    REVENDICATIONS1. Clutch device (1) with wear compensation, in particular for a motor vehicle, comprising a pressure plate (3) intended to bear on a friction disk of the clutch device (1), a diaphragm (9) for actuating the pressure plate (3) between a fully engaged position in which said pressure plate (3) is pushed against the friction disc, and a fully disengaged position in which said pressure plate (3) is pushed apart friction disc via return means (7) of the pressure plate (3), a member (12) for compensating the wear of the friction disk, interposed between the diaphragm (9) and the plate of pressure (3), and movable in rotation about an axis (A) in a determined range, said catch member (12) having a ramp (17) cooperating with a counter-ramp (18) turned on the side of the tray. pressure (3), so as to adjust the distance between the diaphragm (9) and the pressure plate (3) and compensate the wear of the friction disk as a function of the position of the ramp (17) with respect to the counter-ramp (18), the clutch device (1) comprising means for displacement comprising a drive member (23, 36) adapted to engage with a toothed part (20), for example a rack, of the catching member (12) and able to move said catch member (12) in the event of wear of the friction disc, said toothed portion (20) of the adjuster (12) extending in a circumferential direction and comprising axially oriented teeth, characterized in that the drive member ( 23, 36) is pivotally mounted about an axis (24, 37, 44) extending substantially perpendicular to the direction of the toothed portion (20), said driver (23, 36) being configured to transmit a stress oriented perpendicular to said pivot axis (24, 37, 44).
    [0002]
    2. Device (1) according to claim 1, characterized in that the catch member (12) is in the form of a ring having an end (16) adapted to bear against the diaphragm (9) and an end comprising at least one ramp (17) extending circumferentially, cooperating with the associated counter ramp (18) facing the side of the pressure plate (3).
    [0003]
    3. Device (1) according to claim 2, characterized in that the catching member (12) comprises a first and a second concentric annular parts (13, 14) connected to one another by radial tabs ( 15), the first annular portion (13) of the catch member (12) having the end (16) adapted to bear on the diaphragm (9) and the end with the ramp (17), the second annular portion (14) of the catch member (12) having an end (19) comprising the toothed portion (20) engaging with the moving means (23, 36).
    [0004]
    4. Device (1) according to one of claims 1 to 3, characterized in that it comprises a cover (2) inside which are mounted, at least in part, the pressure plate (3) and the diaphragm (9), the diaphragm (9) being interposed between the cover (2) and the pressure plate (3), the cover (2) comprising a stop (35) adapted to cooperate with the catch member (12) so as to immobilize it in position during disengagement, in particular in the fully disengaged position of the diaphragm (9).
    [0005]
    5. Device (1) according to one of claims 1 to 4, characterized in that the displacement means comprise a toothed wheel (23) maintained in engagement with the toothed portion (20) of the catch member (12), said toothed wheel (23) being rotatably coupled to a ratchet wheel (27) cooperating with a pawl (28) whose position of the free end (29) is controlled and is independent of the wear of the friction disk, the position of the ratchet wheel (27) with respect to said free end (29) of the pawl (28) varying according to the wear of the friction disk and the position of the pressure plate (3) so that the pawl (28) is able to drive the ratchet wheel (27), in case of wear of the pressure plate (3), by moving the pressure plate (3) between its engaged and disengaged positions.
    [0006]
    6. Device (1) according to claim 5, characterized in that the toothed wheel (23) is held in abutment on the toothed portion (20) of the catch member (12) by means of elastic means, such as for example an elastic tongue (25).
    [0007]
    7. Device (1) according to claim 5 or 6, characterized in that the pawl (28) and / or the elastic means (25) for holding the toothed wheel (23) are fixed on the cover (2), for example by means of the same rivet (26).
    [0008]
    8. Device (1) according to claim 4 and according to claim 5 or 6, characterized in that the pawl (28) is in the form of an elastic lamella, a portion (30) is adapted to bear on the cover (2) so as to ensure the correct axial positioning of the end (29) of the pawl (28).
    [0009]
    9. Device (1) according to one of claims 1 to 4, characterized in that the displacement means comprise a pawl (36) pivoting about a first axis (37, 44) and whose free end (38). ) is held in abutment on the teeth of the toothed portion (20) of the catching member (12) by means of elastic return means (41), the pawl (36) being able to be arched in the bottom of a tooth in case of wear of the friction disk and during a disengaging phase, so as to cause the movement of the ramp (17) of the catch member (12) relative to the counter associated ramp (18).
    [0010]
    10. Device (1) according to all of claims 4 and 9, characterized in that the first axis (44) is formed at one end (45) of a lever (42), said lever (42) being pivotally mounted around a second axis (37) fixed relative to the lid (2).
    [0011]
    11. Device (1) according to claim 10, characterized in that another end (43) of the lever (42), opposite the end (45) of the lever (42) supporting the axis (44) of the ratchet (36), is adapted to bear on the catch member (12).
    [0012]
    12. Device (1) according to claim 10, characterized in that another end (43) of the lever (42), opposite the end (44) of the lever (42) supporting the axis (44) of the ratchet (36), is adapted to bear on a portion (47) of the diaphragm (9).
    [0013]
    13. Double clutch, characterized in that it comprises at least one device (1) according to one of claims 1 to 12.
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    同族专利:
    公开号 | 公开日
    DE102015104166A1|2015-09-24|
    FR3018879B1|2017-10-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2280355A|1939-06-24|1942-04-21|W C Lipe Inc|Automatic wear take-up for friction clutches|
    JPH03134318A|1989-10-16|1991-06-07|Daikin Mfg Co Ltd|Clutch cover assembly|
    WO2001075322A1|2000-04-03|2001-10-11|Automotive Products Uk Limited|Automatically adjusting clutches|
    EP1657463A1|2004-11-12|2006-05-17|Aisin Seiki Kabushiki Kaisha|Clutch adjustment apparatus|FR3067422A1|2017-06-09|2018-12-14|Valeo Embrayages|CLUTCH MECHANISM FOR A MOTOR VEHICLE|
    CN110005727A|2017-12-11|2019-07-12|法雷奥离合器公司|The wear-compensating component of clutch|US4228883A|1978-04-27|1980-10-21|Borg-Warner Corporation|Automatic wear adjuster for Belleville spring clutches|
    BR9901492A|1998-06-18|2000-01-04|Mannesmann Sachs Ag|Pressure plate module ..|DE102016210012A1|2016-06-07|2017-12-07|Zf Friedrichshafen Ag|Clutch and motor vehicle|
    TR201713960A2|2017-09-20|2017-10-23|Doenmez Debriyaj Sanayi Ve Ticaret Anonim Sirketi|CLUTCH PRESSURE INCLUDING A COVERING MECHANISM|
    法律状态:
    2016-03-31| PLFP| Fee payment|Year of fee payment: 3 |
    2017-03-31| PLFP| Fee payment|Year of fee payment: 4 |
    2018-03-29| PLFP| Fee payment|Year of fee payment: 5 |
    2019-11-29| ST| Notification of lapse|Effective date: 20191106 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1452307A|FR3018879B1|2014-03-20|2014-03-20|CLUTCH DEVICE WITH WEAR RETENTION, IN PARTICULAR FOR A MOTOR VEHICLE|FR1452307A| FR3018879B1|2014-03-20|2014-03-20|CLUTCH DEVICE WITH WEAR RETENTION, IN PARTICULAR FOR A MOTOR VEHICLE|
    DE102015104166.9A| DE102015104166A1|2014-03-20|2015-03-19|Coupling device with wear adjustment, in particular for a motor vehicle|
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