WO2001088400A1 - Embrayage a friction a dispositif de rattrapage de jeu pilote pour vehicule automobile - Google Patents
Embrayage a friction a dispositif de rattrapage de jeu pilote pour vehicule automobile Download PDFInfo
- Publication number
- WO2001088400A1 WO2001088400A1 PCT/FR2001/001561 FR0101561W WO0188400A1 WO 2001088400 A1 WO2001088400 A1 WO 2001088400A1 FR 0101561 W FR0101561 W FR 0101561W WO 0188400 A1 WO0188400 A1 WO 0188400A1
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- WO
- WIPO (PCT)
- Prior art keywords
- plate
- clutch according
- ramps
- ramp
- internal
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
- F16D13/71—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members in which the clutching pressure is produced by springs only
Definitions
- the present invention relates to a friction clutch, for a motor vehicle with an internal combustion engine, and relates more particularly to a clutch equipped with a play take-up device due mainly wear of the friction linings, said device operating continuously as the wear of said linings.
- a conventional friction clutch generally comprises a reaction plate, .. possibly in two parts to form a damping flywheel, fixed in rotation on a first shaft, usually a driving shaft such as the crankshaft of the internal combustion engine, and supporting by its outer periphery a cover to which is attached at least one pressure plate.
- the pressure plate is integral in rotation with the cover and the reaction plate while being able to move axially under the stress of elastic means with controlled axial action, generally a metal diaphragm bearing on the cover, while a friction disc, carrying friction linings at its outer periphery, integral in rotation with a shaft, usually a driven shaft such as the input shaft of the gearbox, is interposed between the pressure plate and the reaction plate so to be clamped together when the clutch is in the engagement position.
- the diaphragm controls the axial movement of the pressure plate when it is actuated by a clutch release bearing.
- Document FR 2 426 834 discloses a play take-up device in which a first plate, in this case the pressure plate, is in two coaxial parts which can be moved axially relative to one another so that that the overall thickness of the first plate increases as wear increases.
- the two coaxial parts of the first plate are axially displaceable relative to each other by means of a take-up device which comprises ramp means carried in a complementary manner by the two coaxial parts which are also displaceable by rotation relative to each other in the direction of the increase in said overall thickness and prevented from rotating one relative to the other in the opposite direction to the previous one by unidirectional means.
- the setting in motion of relative rotation of the coaxial parts is controlled by a trigger sensitive to the state of wear and produced by an elastic means with circumferential action coupled between said two coaxial parts.
- a friction clutch in particular for a motor vehicle, of the type comprising a reaction plate intended to be locked in rotation on a driving shaft, a friction disc, carrying at its outer periphery friction linings, intended to be wedged in rotation on a driven shaft, a pressure plate, a cover fixed on the reaction plate, elastic means with axial action acting between the cover and the pressure plate, the pressure plate being integral in rotation with the cover while being able to move axially with respect to it, one of the two plates, reaction plate or pressure plate, called the first plate, being made up of two half-plates, a half-plate, said external, and a half-plate, said internal, the internal half-plate being that which faces a friction lining and which is intended to cooperate with it, the two half-plates being integral in rotation with the shaft m while being axially displaceable, one relative to the other, under the action of a backlash device due to the wear mainly of the friction linings, which backlash device comprises at least one pair of complementary
- the adjustment ramp is provided at the periphery of an inertia piece, so that the acyclism of the thermal engine of the motor vehicle is used to cause the complementary ramps to carry out their relative circumferential movement in the sense of catching up with the game.
- rotating acyclism results in alternating angular accelerations which can reach more or less two thousand radiant per square second; thanks to the inertial part subjected to these angular accelerations, when the clutch is disengaged and that, as a result, the two half-plates are no longer under the axial force of the elastic means with axial action, the adjustment ramp turns in the catching direction relative to the support ramp, since the unidirectional means prevents it from turning in the other direction.
- the operation of the play take-up device is automatic.
- this automation is a drawback since it leads to a recovery operation not linked to wear, an operation known as over-recovery.
- reaction plate or flywheel
- flywheel is a double damping flywheel whose natural frequency of vibrations is located in this range of low speeds and produces vibrations leading the external half-plate to move and to make up for a "play" which does not exist.
- Other parasitic phenomena can occur at higher speeds, for example above two thousand revolutions per minute.
- the object of the present invention is to avoid these drawbacks.
- a friction clutch for a motor vehicle with an internal combustion engine of the type comprising a reaction plate intended to be locked in rotation on a driving shaft, a friction disc, carrying at its outer periphery friction linings, intended to be locked in rotation on a driven shaft, a pressure plate, a cover fixed on the reaction plate, elastic means with axial action acting between the cover and the pressure plate, the pressure plate being integral in rotation with the cover while being able to move axially relative to it, one of the parts, reaction plate or pressure plate or cover, being made up of two half-pieces, displaceable axially, one with respect to the other, under the action of a backlash device due to wear, which backlash device comprises at least one pair of complementary ramps arranged circumferentially associated axially connected respectively to each of the two half-pieces, one of the ramps being adapted to move circumferentially with respect to the other ramp in the direction of increasing the overall thickness of said piece, known as the catching direction , and prevented from moving in the other
- said part is one of the two plates, reaction plate or pressure plate, said first plate, consisting of two half plates, a half plate, said external, and a half plate, said internal, the half - internal plate being that which faces a friction lining and which is intended to cooperate with it, the two half-plates being integral in rotation with the driving shaft but displaceable axially, one relative to the other, under the action of the play take-up device, one of the ramps known as the support ramp, being integral in rotation with one of the half-plates, the other ramp, called the adjustment ramp, being adapted to move circumferentially relative to the support ramp in the direction of increase in the overall thickness of said first plate, the adjustment ramp being provided at the periphery of the inertia piece.
- the support ramp is carried by the internal half-plate.
- the adjustment ramp is carried by the external half-plate.
- the first plate is the pressure plate.
- the elastic means with axial action consist of a diaphragm, and the external half-plate is provided with a support cord for the diaphragm.
- the adjustment ramp is carried by the internal periphery of the external half-plate; alternatively, the adjustment ramp is carried by the external periphery of the external half-plate.
- the adjustment and support ramps are helical threads having as their axis the axis of the clutch.
- the adjustment ramp consists of a series of ramps extending circumferentially at the end of an annular piece of cut and folded sheet metal.
- the unidirectional means is a split segment integral in rotation with the first plate at at least one point.
- the unidirectional means is a rod wound helically in rotation with the first plate at at least one point.
- control means are controlled by the elastic means with axial action.
- control means comprise a tongue-shaped brake, whether or not subject to the elastic means with axial action, adapted to cooperate with one of the ramps; the tongue is in the form of a pin mounted on a hinge.
- control means are sensitive to centrifugal force and / or to strong acceleration.
- control means consist of an elastic U-shaped tongue carried by the cover.
- control means comprise a lever articulated on the internal half-plate and its two branches are adapted to cooperate with the unidirectional means.
- control means comprise one (or more) cams mounted articulated eccentrically on the internal half-plate and adapted (s) to cooperate with the external half-plate.
- the control means comprise a rod carried by the internal half-plate and adapted to cooperate, under the effect of centrifugal force, with the external half-plate to prevent the latter from rotating in the direction allowed by the unidirectional means.
- the unidirectional means is a rod and the pilot rod and the unidirectional rod are in one piece.
- the unidirectional means is a rod and a mass, sensitive to centrifugal force and / or to angular acceleration, associated with it to brake, beyond a certain speed of rotation or a certain angular acceleration, the half external tray.
- At least one of the rods is subjected to the circumferential action of a spring.
- control means comprise an elastic means exerting a substantially tangential force and adapted to cooperate with the external half-plate under the action of the unidirectional means displaced by inertia.
- the adjustment ramps cooperate with counter-ramps or support ramps carried by a ring secured to the internal half-plate by friction, which is controlled elastically.
- the part consisting of two half-parts is the cover.
- the internal half-cover is constituted by the central part of the bottom of the cover, being externally threaded, while the external half-cover is internally threaded so that the internal and external half-covers are screwed one in the other.
- a wedge-shaped brake controlled by the diaphragm, can be inserted between the two half-covers.
- Figures 2 and 3 are similar to Figure 1 and relate to a variant
- Figure 6 is a view similar to Figure 1 and relates to yet another variant
- Figures 7 and 8 relate to yet another variant, Figure 7 being a sectional view along VII-VII of Figure 8;
- - Figures 9 and 10 relate to yet another variant, Figure 9 being a sectional view along IX-IX of Figure 10;
- Figures 11 to 13 relate to yet another variant, Figure 12 being a section along XII-XII of Figure 11 and Figure 13 a perspective view on a smaller scale of the spiral rods of Figure 11; - Figure 14 is a view similar to Figure 13 and shows a variant;
- Figures 15 to 17 relate to yet another variant, Figure 16 being a section along XVI-XVI of Figure 15 and Figure 17 a perspective view on a smaller scale of the open ring of Figure 15;
- Figures 18 to 21 relate to yet another variant, Figure 19 being a section along XIX-XIX of Figure 18 and Figures 20 and 21 of partial transverse sections of Figure 18;
- FIG. 22 and 23 are partial sections illustrating the operation of another variant of control means according to the invention.
- Figures 24 and 25 relate to yet another variant, Figure 24 being a sectional view along XXIV-XXIV of Figure 25;
- - Figure 26 is a view similar to Figure 1 and relates to yet another variant; - Figures 27 and 28 relate to yet another variant, Figure 28 being a section along XXVIII-XXVIII of Figure 27;
- Figures 33 and 34 relate to yet another variant, Figure 33 being a partial view in axial section similar to Figure 1 and Figure 34 a view along arrow XXXIV of Figure 33, showing another control means
- Figures 39 and 40 relate to yet another variant, Figure 39 being a partial cross-sectional view and Figure 40 a partial perspective view;
- Figures 41 and 42 relate to yet another variant, Figure 41 being a view similar to Figure 1 and Figure 42 a partial axial view;
- Figures 43 and 44 relate to yet another variant, Figure 43 being a partial view along the axis and Figure 44 a partial view in cross section;
- Figures 45 to 47 relate to yet another variant, Figure 45 being a view similar to Figure 1, Figure 46 a partial view along arrow XXXXVI of Figure 45 and Figure 47 a partial section along XXXVII- XXXXVII of FIG. 45.
- the clutch comprises a reaction plate 13 intended to be locked in rotation on a driving shaft, here the crankshaft of a heat engine of a motor vehicle, a friction disc 14 carrying at its outer periphery friction linings 15 and intended to be locked in rotation on a driven shaft.
- a cover 11 is fixed to the reaction plate 13 and elastic means with axial action, here a diaphragm 16, acts between the cover 11 and a pressure plate 12 integral in rotation with the cover 11 but able to move axially relative to it , the diaphragm 16 applying, bearing on the cover 11, the pressure plate 12 against the friction disc 14 so that the friction linings 15 are clamped between the plates pressure 12 and reaction 13; as known per se, the diaphragm 16 is mounted articulated on the cover 11 by balusters 21 and bears on the cover according to a circumferential bearing 20 which it has.
- the pressure plate 12 is made up of two half-plates; a half-plate 12A called an external half-plate, and a half-plate 12B, called an internal half-plate, which directly faces the friction disc 14; tangential tabs conventionally connect the internal half-plate 12B to the cover 11, for connection, with axial mobility, of the pressure plate 12 with the cover 11.
- the two half-plates 12A, 12B are integral in rotation with the driving shaft but axially movable, one relative to the other, under the action of a play take-up device.
- the play take-up device comprises complementary ramps 17, 18 arranged circumferentially and associated respectively with each of the two half-plates 12A, 12B.
- the outer half-plate 12A is an annular piece housed in a groove 23 in the internal half-plate 12B; said groove 23 extends axially, at the edge of a step 25, being open towards the cover 11; the axial length of the annular part 12A is greater than the axial depth of the groove 23 and its end which faces the cover is shaped into a support bead 19 for the diaphragm 16.
- the annular part 12A On its internal axial face, that is to say facing the axis of the clutch, the annular part 12A carries a helical thread 18, the axis of which is the axis of the clutch, constituting the ramp d adjusting.
- the annular part 12A cooperates with a helical thread 17, complementary to the thread 18, produced at the periphery of a split segment 24 and constituting the support ramp.
- the segment 24 surrounds the redent 25 and has one of its ends which is immobilized in rotation relative to the half-plate 12B, for example by a radial or axial pin.
- the winding direction of the helical threads constituting the support and adjustment ramps 17 is such that when the half-plate 12A is subjected to an acceleration the adjustment ramp 18 moves in rotation relative to the ramp d 'support 17 and the half-plate 12A, during this movement, advances axially relative to the internal half-plate 12B in the direction of the cover 11; for accelerations in the opposite direction, the friction of the adjustment ramp 18 on the support ramp 17 expands the segment 24 which carries the latter, this expansion leading to the blocking in rotation of the external half-plate 12A relative to the segment 24, therefore relative to the internal half-plate 12B: as can be seen, the segment 24 plays the role of a one-way means; thus, thanks to the arrangement which has just been described, the acyclism of the heat engine is sufficient to cause the external half-plate 12A to exit axially from the groove 23 if, of course, nothing prevents this exit, as explained below.
- the play take-up device also comprises a trigger constituted by a split elastic elastic pin 22 with radial expansion introduced into a passage 28 which it crosses formed in a radial end tab 29 of the internal half-plate 12B; the diameter of the passage 28 is less than the outside diameter of the pin 22 in the free state so that the latter is frictionally mounted in the passage 28 and immobilized axially with respect to the half internal plate 12B; this immobilization friction is provided with a value such that it can be overcome by the axial force due to the diaphragm 16 and that it cannot be overcome by the restoring force to which the pressure plate 12 is subjected , restoring force such as that usually coming from tangential tongues coupling in rotation said pressure plate 12, here the half-plate 12B, and the cover 11.
- a trigger constituted by a split elastic elastic pin 22 with radial expansion introduced into a passage 28 which it crosses formed in a radial end tab 29 of the internal half-plate 12B; the diameter of the passage 28 is less than the outside diameter of the pin
- the operation of the play take-up device according to the invention is as follows.
- FIG. 1 shows the clutch engaged, the friction linings 15 being new and clamped between the pressure plate 12 and the reaction plate 13.
- the pin 22 came into abutment on the cover 11, then the diaphragm continued its course and took off from the support cord 19; the internal half-plate 12B having retreated only by an amount equal to the clearance 26, the shoulder 19A of the support cord 19 is at a distance from the cover stop 11A corresponding to the wear measured axially; in a second step, the external half-plate 12A, which is no longer subjected to the action of the diaphragm, is free to move in the direction of the diaphragm 16, thanks to the accelerations to which it is subjected due to the acyclism of the engine, as explained above; the output of the external half-plate 12A continues until the shoulder 19A of the support cord 19 comes into abutment on the cover stopper 11A: thus, the play due to wear has been taken up.
- control means comprise a brake 30 adapted to cooperate indirectly with one of the ramps 17, 18, here with the ramp 18 carried by the split segment 24, for a certain position of the diaphragm 16 .
- the brake 30 is in the form of a cut and arched sheet metal tongue, secured, for example by a rivet 31, to the Belleville washer part of the diaphragm 16 while being situated on the face of the latter facing towards the pressure plate 12 ; the brake tab 30 extends in a radial notch formed in the redent 25 and its end, advantageously curved, is adapted to cooperate with the internal cylindrical face of the split segment 24.
- the brake tab 30 When the clutch is engaged, the brake tab 30 is at a distance from the split segment 24, FIG. 1; during disengagement of the clutch, the diaphragm tilting around the balusters 21, the brake tongue 30 approaches the split segment 24: in a first part of this disengagement race, the brake tongue 30 still does not cooperate with the segment split 24 and a catch-up operation is possible; in a second and last part of the disengagement path of the diaphragm 16, the brake tab 30 transmits a radial thrust force on the split segment 24, preventing the latter from rotating the external half-plate 12A and performing a catch-up operation.
- tongues 30 can be provided, distributed circumferentially, for example three tongues 30 at one hundred and twenty degrees from one another.
- each brake tab 30 is in the form of a pin, one branch of which is subject to the diaphragm 16; here this branch is located on the face of the diaphragm 16 facing the bottom of the cover 11 and the other branch is adapted to cooperate with the external cylindrical face of the external half-plate 12A; the arcuate part 32 of the tongue 30 which connects the two branches is in abutment on the cover 11, in a recess of the latter also of arcuate shape, and plays the role of an articulation transforming the axial force applied to the tongue 30 by the diaphragm 16 in a radial force applicable to the external half-plate 12A.
- FIG. 2 shows the clutch in the engagement position, the tongue 30, more precisely its free end advantageously rounded, being at a distance from the external half-plate 12A;
- FIG. 3 shows the clutch in the end of disengagement position, the tongue 30 immobilizing the external half-plate 12A.
- the actuating branch of the tongue 30 is subjected to centrifugal force and this must be taken into account for the adjustment of the moment from which the control means no longer authorize the operation of the take-up device. wear.
- the variant of Figures 4 and 5 is similar to that which has just been described with reference to Figures 2 and 3 except that here the tongue 30 is not secured to the diaphragm 16 but held resiliently in position between the cover 11 and the diaphragm 16.
- control means sensitive only to centrifugal force.
- the control means comprise a brake constituted by the free branch of an elastic tongue 40 in the shape of a U, the other branch of which is subject to the cover 11, here on a cylindrical skirt extending axially as has the cover 11, by a rivet 41; the free leg of the brake 40 is in elastic support on the external face of the external half-plate 12A which it prevents from turning; from a certain speed of rotation, for example 400 revolutions per minute, under the effect of centrifugal force, the brake 40 releases the external half-plate 12A and authorizes, under the conditions described above, an operation of catching.
- the centrifugal effect can be controlled by the choice of a mass 42 attached to the free branch of the brake 40.
- the control means comprise a lever 50 mounted articulated about an axis 51 carried by the internal half-plate 12B of the pressure plate 12; on either side of the axis 51, extend the two branches 52, 53 of the lever 50; the first branch 52 has its end, advantageously rounded, in contact with the internal face of the split segment 24 thanks to the action of a spring 54 which acts on the first branch 52 by bearing on the axis 51; the second branch 53 is at a distance from said internal face, as well as its end, also advantageously rounded; this second branch 53 is more massive than the first branch 52, thanks to its length and / or to a weight 55 which it carries; consequently, from a certain speed of rotation, the lever 50 rotates around the axis 51 under the effect of the centrifugal force which acts against the spring 54: in a certain range of speeds, neither of the two branches 52 , 53 is not in contact with the split segment 24 and a catch-up operation is authorized; beyond a certain speed, it is the second
- levers such as the lever 50 can be provided, for example three levers 50 also distributed circumferentially.
- Figures 9 and 10 show a variant in which the outer half-plate 112A of the pressure plate 12 is an annular piece of cut and folded sheet metal carrying axially, on one side, the support bead 119 with which the diaphragm 16 cooperates. and, on the other side, a series of ramps 118 extending circumferentially and cooperating with complementary ramps 117 in the form of studs from the internal pressure plate 112B.
- This annular part 112A is associated with a cam 133 rotatably mounted about an axis 134 parallel to the axis of the clutch and carried by the internal half-plate 112B of the pressure plate 112.
- the cam 133 is produced in the form of a circular section disc which cooperates at its periphery with the internal cylindrical face of the annular part 112A; the axis 134 is offset, on the left according to FIG. 10, relative to the diameter 135 which passes through the center of the cam 133.
- a light spring 136 of prestressing ensures contact between the cam
- the centrifugal force strongly plates the cam 133 on the annular part 112A, which prevents the latter from rotating, even in the direction of the arrow F; the cam 133 thus constitutes a control means, of the play take-up device, sensitive to the rotation speed of the clutch.
- the variant according to FIGS. 11 to 13 has, as previously, an annular part 212A similar to the annular part 112A of the previous variant and having ramps 218 adapted to cooperate with counter-ramps 217 formed at the periphery of a ring embedded in a groove of the internal half-plate 212B of the pressure plate 212; here, the split elastic pin 222, constituting the trigger and passing through a lug 239 of the internal half-plate 212B, carries an axial rivet 223 securing, to the pin 222, a radial lug 237 of abutment with which is adapted to cooperate axially in abutment the annular part 212A, thanks to a radial tab 238 which it has, so that, whatever the wear, the axial position of the support cord 219 is always the same.
- the unidirectional means ensuring the non-return function associated with the annular part 212A is a rod 240 wound helically on three turns, according to the example shown; at rest, the rod 240 has a diameter slightly greater than that of the internal periphery of the annular part 212A, so that once mounted it is tightened radially on said periphery and at slight radial distance from the redent 225; this slight distance has been exaggerated in FIG. 11 to facilitate reading; one end of the rod 240 is folded radially at 241, FIG.
- a second rod 242 is provided which surrounds the redent 225 in which is also housed one of its ends folded radially 243.
- the diameter of the second rod 242 is less than the diameter of the external cylindrical surface of the redent 225, so that once mounted it is clamped radially on said cylindrical surface and at a radial distance from the annular part 212A.
- the rod 242 does not disturb the operation of the play take-up device, at least up to a certain speed of rotation for which, under the effect of centrifugal force, it increases in diameter until it comes into contact with the annular part 212A; the winding of the rod 242 from its anchoring at 243 is in the opposite direction to that of the rod 240 from its anchoring 241 so that as from said speed of rotation, the annular part 212A is prevented from turning both in one direction and in the other.
- Figure 14 is similar to Figure 13 and shows a variant in which the two rods 240 and 242 are part of the same wire suitably wound on either side of a common loop 244 for anchoring.
- Figures 15 to 17 show a variant almost identical to that which has just been described with reference to Figures 11 to 14; here, the freewheeling and steering functions are ensured by a split ring 250, elastic, for example, as shown, of rectangular section and consisting of two half-rings 251, 252 connected according to a common part provided with a hole 253 for immobilization by a radial pin 254 relative to the internal half-plate 212B; the shape of the rod 250 is such that, seen from above in FIG.
- a ring or half-ring provides the freewheeling function while another ring or half-ring provides the steering function; it is possible to have both functions performed by the same rod, as in Figures 22 and 23; here, the freewheel ring 251, anchored at 254, is associated with a mass 362, such as a roller, as shown; the latter is in a housing 363 formed in the rod 251 and open towards the internal half-plate 212B; transversely, the housing 363 carries a radial wall opposite which is a ramp-shaped wall 364; a circumferential action spring 365 moves the mass 362 away from the ramp 364.
- the annular part 212A is free to rotate clockwise, with respect to FIG. 22; in the event of strong angular acceleration or when the speed of rotation is high, the mass 362, thanks to the ramp 364, strongly presses the rod 251 against the annular part 212A, thus preventing its rotation relative to the internal half-plate 212B.
- a stud 51 of the internal half-plate 12B carries, thanks to a rivet 52, a support 53 extending radially, as well as, on either side of it, two elastic blades 54 and 57, both radial; the split segment 24 has one of its ends terminated by a radial return 55 pinched between the support 53 and the tongue 57, its other end 56 being in abutment on the external end of the elastic blade 54 at a circumferential distance from the support 53.
- the internal half-plate 12B subjected to angular accelerations in the counterclockwise direction, allows the external half-plate 12A to move clockwise, relative to FIG. 25; however, in the event of strong acceleration, in this direction and by inertia due to its mass, the split segment 24 pushes the elastic blade 54 against the support 53; the elastic blade 57 relaxes and causes the split segment 24 to open, preventing the external half-plate 12A from rotating.
- the annular part 212A has ramps 218 adapted to cooperate with counter-ramps 317 carried by a cylindrical ring 351 with circular cross section centered on a redent 325 of the internal half-plate 312B; the split elastic pin 322 crosses a lug 339 of the internal half-plate 312B and carries a rivet 323 integrating, with the pin 322, a radial lug 337 of abutment with which is adapted to cooperate axially in abutment the annular part 212A by virtue of a return radial 238 that it presents.
- the unidirectional means ensuring the non-return function is a split rod 350 fixed by one of its ends to the ring 351 which it surrounds.
- the ring 351 is secured to the internal half-plate 312B by a friction controlled by a spring 352; thus, in the event of strong acceleration, the inertia of the assembly constituted by the ring 351, the split rod 350 and the annular part 212A overcomes the friction due to the spring 352 and the assembly moves in rotation without it being able to catch up.
- Figures 27 and 28 show a clutch of the kind of that of Figures 11 and 12 in which a pin 422 radially elastic passes through a tab 439 of the internal half-plate 412B and has a length such that it defines axially, in the position of engagement of the clutch, between its free end not resting on the reaction plate and a tab 411, obtained by cutting and folding the bottom of the cover 11, a clearance J1 corresponding to the lift stroke of the pressure plate 412 during walkout.
- the annular part 412A has ramps 418 adapted to cooperate with counter-ramps 417 formed at the periphery of a ring 413 embedded in a groove in the internal half-plate 412B of the pressure plate 412; this annular part 412A is adapted to cooperate with the tab 411 of the cover 11 thanks to a radial tab 438 which it itself has; in the engagement position of the clutch, this radial tab 438 is at an axial distance J2 from the tab 411 of the cover 11: of course, the clearance J2 is equal to the clearance J1 increased by the amount of wear to be axially caught , which tends to zero as the catch-up operations progress.
- the non-return function is provided by a helical spring 440, with radial expansion, of which a radial return 441 is linked to the internal half-plate 412B.
- this spring 440 does not support any axial load.
- the turns of the spring 440 are used as counter-ramps, the helical ramps being formed at the periphery of the annular part 512A; here, a ring 513, attached to the internal half-plate 412B, supports the first turn of the spring 440 while being shaped in a complementary manner.
- the annular part 412A or 512A is made of stamped sheet metal; according to FIG. 30, the annular part 612A is analogous to the annular part 512A in FIG. 29, but here it is massive, its female thread being obtained for example by machining or stamping.
- the annular part 712A is also massive and carries a thread at its external periphery cooperating with a thread formed at the internal periphery of an annular nose 714 of the internal half-plate 712B of the pressure plate 712; here, the radially expanded helical spring 440 performs the non-return function, one of its ends being stopped relative to the internal half-plate 712B by a return 441 which here extends axially.
- FIG. 32 is a variant of FIG. 29 in which the helical spring 440 has been replaced by a split ring of rolled pressed sheet metal.
- the rod 1022 associated with an elastic washer 1024, in a tab 1039 of the pressure plate is provided with a threaded tail 1023 which passes through the bottom of the cover to which it is subjected by means of a nut 1025.
- the split rod 1026 is immobilized, relative to the pressure plate, in rotation thanks to the return 1028 from one of its ends and axially thanks to a screw head 1027.
- the ramps 218 of the annular part 212A cooperate with counter-ramps 217 formed on the stud heads 2217 attached to the internal half-plate 212B of the pressure plate 212; these the heads are advantageously stepped so as to center the annular part 212A.
- Figures 37 and 38 The variant of Figures 37 and 38 is of the kind described in connection with Figures 11, 15 or 16; here, the radial tab 237 has a return 237A adapted to take place by elasticity in a housing 111, formed in the skirt of the cover 11, under the following conditions: at rest, that is to say in storage, the elastic pin 222 is retracted as much as possible in the half-tray 212B, towards the bottom of the cover 11, which half-tray 212B is distant from said bottom, while the return 237A of the radial tab 237, axially offset with respect to the housing 111, is in pressing on the internal periphery of the skirt of the cover 11; after mounting on the vehicle, during the first disengagement, which brings the half-plate 212B closer to the bottom of the cover 11, the return 237A is clipped into the housing 111: the detection is in some way armed; on the following re-engagement, the half-plate 212B moves relative to the elastic pin 222 until the friction disc is tightened:
- the split rod 850 which is adapted to cooperate with the internal periphery of the annular part 812A, has its cut ends so as to define therein external branches 853, 854 and internal branches 851, 852 ; the internal branches 851 and the external branch 853 of one end have a Y configuration, as well as the internal branches 852 and the external branch 854 of the other end; between these ends is arranged a lever 856 which extends radially; the outer end of the lever 855 is in line with the external arms 853 and 854, while the central part of the lever 855 is in line with the internal arms 851, 852; the internal end of the lever 855 is placed in a notch 857 of the half-plate 812B which is thus adapted to move this end in one direction or the other when it is subjected to an acceleration in one direction or the
- the cover 911 which consists of two half-covers, one 911 A said external half-cover, the other 911 B said internal half-cover, the pressure plate 912 being in one piece;
- the internal half-cover 911 B is constituted by the central part of the bottom of the cover 911 and carries the articulation means 921 of the diaphragm 16 on the cover 911;
- the external half-cover 911 A is internally threaded and the internal cover 911 B is externally threaded so that the internal half-cover 911 B is screwed into the external half-cover 911A.
- One or more wedge-shaped brakes 950 are locally inserted between the two half-covers 911 A, 911B to prevent a relative movement of rotation of one relative to the other; a tail 951 of the brake 950 crosses the diaphragm and said tail 951 has, beyond the diaphragm 16, a head 952; thus, the brake 950 is controlled by the diaphragm 16: the diaphragm 16 can move along the tail 951 from the corner 950 but on one side, to the right in FIG. 41, it cuts out the corner 950, during the wear of the friction disc 14, and on the other side, to the left in FIG. 41, it introduces the brake 950 between the two half-covers 911 A, 911 B, when disengaging; thus, it is the brake 950 which constitutes the end stop for lifting the plate 912.
- the rod 1050 is provided massive so that it is under the effect of its own inertia that it expands and blocks the ring 1012A or contracts and releases said ring 1012A; here, a spring 1014 applies one of the ends of the rod 1050 to a radial tab 1013 of the external half-plate 1012B while resting thereon; for an acceleration in the clockwise direction, with respect to FIG.
- the rod 1050 blocks the annular part 1012A; for acceleration in the opposite direction, it releases said annular part 1012A; if this acceleration, in said opposite direction, is much greater than the preload of the spring 1014, the other end makes contact with the radial tab 1013 and, taking support therefrom, the rod 1050 expands by compressing the spring 1014 and blocks the annular part 1012A.
- Figures 45 to 47 show a variant of the kind described with reference to Figures 27 and 28 in which the non-return function, or freewheeling, is provided by a rod 440, instead of a helical spring, and the ramps 418 of the annular part 412A cooperate with counter-ramps 417 in the form of studs forming part of the internal half-plate 412B.
- Counter ramps 417 extend radially so that a washer
- So-called detection 462 can also cooperate with these thanks to ramps 418A which it has at its periphery facing the internal half-plate 412B and which are similar to the ramps 418 of the annular part 412A; an elastic washer 463, here wavy, bearing on the tab 411 of the cover 11, keeps the ramps 418A and the counter-ramps 417 in contact.
- a helical spring 464 is disposed between the detection washer 462 and the annular part 412A which are thus coupled in rotation.
- the load of the corrugated elastic washer 463 is chosen to be less than that of the elastic return means of the pressure plate 412, such as tangential tongues, so that when disengaging the corrugated elastic washer
- the annular part 412A Since the first start of the engine equipped with such a clutch and after the first clutch-clutch cycle, the annular part 412A, thanks to the vibrations, is positioned; the helical spring 464 is armed.
- the detection washer 462 moves when the force due to the helical spring 464 overcomes that due to the corrugated elastic washer 463; when disengaged, wear is caught up by the annular part 412A which rotates and tightens the helical spring 464.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/275,810 US6779643B2 (en) | 2000-05-19 | 2001-05-21 | Friction clutch with controlled play compensation for motor vehicle |
AU2001262477A AU2001262477A1 (en) | 2000-05-19 | 2001-05-21 | Friction clutch with controlled play compensation for motor vehicle |
DE10196193T DE10196193B3 (de) | 2000-05-19 | 2001-05-21 | Reibungskupplung mit gesteuerter Spielnachstellvorrichtung für Kraftfahrzeuge |
KR1020027015306A KR100881147B1 (ko) | 2000-05-19 | 2001-05-21 | 자동차용 마찰 클러치 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0006480A FR2809147B1 (fr) | 2000-05-19 | 2000-05-19 | Embrayage a friction a dispositif de rattrapage de jeu pilote pour vehicule automobile |
FR00/06480 | 2000-05-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001088400A1 true WO2001088400A1 (fr) | 2001-11-22 |
Family
ID=8850452
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2001/001561 WO2001088400A1 (fr) | 2000-05-19 | 2001-05-21 | Embrayage a friction a dispositif de rattrapage de jeu pilote pour vehicule automobile |
Country Status (7)
Country | Link |
---|---|
US (1) | US6779643B2 (fr) |
KR (1) | KR100881147B1 (fr) |
AU (1) | AU2001262477A1 (fr) |
DE (2) | DE10196193B3 (fr) |
FR (1) | FR2809147B1 (fr) |
IT (1) | ITRM20010234A1 (fr) |
WO (1) | WO2001088400A1 (fr) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2831233A1 (fr) * | 2001-10-23 | 2003-04-25 | Valeo | Embrayage a friction, pour vehicule automobile, equipe d'un dispositif de rattrapage de jeu pilote |
EP2025961A1 (fr) * | 2007-07-25 | 2009-02-18 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Ensemble embrayage |
WO2013113530A1 (fr) * | 2012-02-02 | 2013-08-08 | Zf Friedrichshafen Ag | Ensemble embrayage et procédé de fabrication dudit ensemble embrayage |
WO2015127930A1 (fr) * | 2014-02-27 | 2015-09-03 | Schaeffler Technologies AG & Co. KG | Embrayage à friction comprenant un dispositif de rattrapage servocommandé |
EP4010605A4 (fr) * | 2020-05-15 | 2022-09-28 | Dönmez Debriyaj Sanayi Ve Ticaret Anonim Sirketi | Ensemble couvercle d'embrayage compensant l'usure de la garniture de manière précise et automatique |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10391567D2 (de) * | 2002-04-10 | 2005-03-10 | Luk Lamellen & Kupplungsbau | Kupplungsaggregat |
DE10330880A1 (de) * | 2003-07-09 | 2005-01-27 | Zf Sachs Ag | Druckplattenbaugruppe |
ATE448417T1 (de) * | 2005-04-08 | 2009-11-15 | Luk Lamellen & Kupplungsbau | Reibungskupplung |
WO2012024093A2 (fr) * | 2010-08-17 | 2012-02-23 | Borgwarner Inc. | Embrayage pneumatique comportant un élément de friction perfectionné |
DE102015205145A1 (de) * | 2014-04-17 | 2015-10-22 | Schaeffler Technologies AG & Co. KG | Reibungskupplung mit zweiteiliger Anpressplatte |
WO2016068817A1 (fr) * | 2014-10-27 | 2016-05-06 | MA-PA MAKINA PARÇALARI ENDÜSTRlSI A.Ş. | Embrayage à compensation automatique d'usure |
US10082184B2 (en) | 2015-03-02 | 2018-09-25 | Rolls-Royce Corporation | System and method for eliminating adverse clutch vibratory responses |
KR20180063257A (ko) * | 2015-10-05 | 2018-06-11 | 섀플러 테크놀로지스 아게 운트 코. 카게 | 마찰 클러치 |
US10215237B2 (en) | 2016-07-29 | 2019-02-26 | GM Global Technology Operations LLC | Multiple-piece backing plate having parts made of different materials |
US10132364B2 (en) | 2016-07-29 | 2018-11-20 | GM Global Technology Operations LLC | Backing plate providing axial stiffness |
US10788082B2 (en) * | 2018-05-21 | 2020-09-29 | Eaton Intelligent Power Limited | Transmission clutch including locking torsion spring |
FR3092883B1 (fr) * | 2019-02-19 | 2021-05-07 | Valeo Embrayages | Mecanisme d’embrayage a rattrapage d’usure |
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FR2426834A1 (fr) | 1978-05-26 | 1979-12-21 | Borg Warner | Compensateur d'usure automatique pour embrayage a ressort belleville |
US5069322A (en) * | 1989-07-20 | 1991-12-03 | Kabushiki Kaisha Daikin Seisakusho | Self adjusting clutch cover assembly |
US5090536A (en) * | 1990-03-14 | 1992-02-25 | Kabushiki Kaisha Daikin Seisakusho | Self adjuster for push type clutch |
GB2278894A (en) * | 1993-05-26 | 1994-12-14 | Luk Lamellen & Kupplungsbau | Friction clutch with wear adjustment |
US5469760A (en) * | 1992-07-23 | 1995-11-28 | Kabushi Kaisha Daikin Seisakusho | Clutch wear-compensating compound flywheel assembly |
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FR2750467A1 (fr) | 1996-06-27 | 1998-01-02 | Valeo | Embrayage a friction a dispositif de rattrapage de jeu pour vehicule automobile |
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US6029787A (en) * | 1992-11-25 | 2000-02-29 | Luk Lamellen Und Kupplungsbau Gmbh | Self-adjusting friction clutch |
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GB1567019A (en) * | 1976-03-24 | 1980-05-08 | Automotive Prod Co Ltd | Friction clutches |
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DE19744513C2 (de) * | 1997-10-09 | 2003-06-18 | Zf Sachs Ag | Druckplattenbaugruppe |
FR2775040B1 (fr) * | 1998-02-13 | 2000-07-21 | Valeo | Mecanisme d'embrayage pour vehicule automobile comportant un dispositif perfectionne de rattrapage d'usure des garnitures de friction |
JP3717690B2 (ja) * | 1998-12-18 | 2005-11-16 | 株式会社エクセディ | クラッチカバー組立体 |
-
2000
- 2000-05-19 FR FR0006480A patent/FR2809147B1/fr not_active Expired - Fee Related
-
2001
- 2001-05-02 IT IT2001RM000234A patent/ITRM20010234A1/it unknown
- 2001-05-21 DE DE10196193T patent/DE10196193B3/de not_active Expired - Fee Related
- 2001-05-21 WO PCT/FR2001/001561 patent/WO2001088400A1/fr active Application Filing
- 2001-05-21 AU AU2001262477A patent/AU2001262477A1/en not_active Abandoned
- 2001-05-21 DE DE10197401T patent/DE10197401B4/de not_active Expired - Fee Related
- 2001-05-21 US US10/275,810 patent/US6779643B2/en not_active Expired - Lifetime
- 2001-05-21 KR KR1020027015306A patent/KR100881147B1/ko active IP Right Grant
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FR2426834A1 (fr) | 1978-05-26 | 1979-12-21 | Borg Warner | Compensateur d'usure automatique pour embrayage a ressort belleville |
US5069322A (en) * | 1989-07-20 | 1991-12-03 | Kabushiki Kaisha Daikin Seisakusho | Self adjusting clutch cover assembly |
US5090536A (en) * | 1990-03-14 | 1992-02-25 | Kabushiki Kaisha Daikin Seisakusho | Self adjuster for push type clutch |
US5469760A (en) * | 1992-07-23 | 1995-11-28 | Kabushi Kaisha Daikin Seisakusho | Clutch wear-compensating compound flywheel assembly |
US6029787A (en) * | 1992-11-25 | 2000-02-29 | Luk Lamellen Und Kupplungsbau Gmbh | Self-adjusting friction clutch |
GB2278894A (en) * | 1993-05-26 | 1994-12-14 | Luk Lamellen & Kupplungsbau | Friction clutch with wear adjustment |
US5641048A (en) * | 1994-11-14 | 1997-06-24 | Luk Lamellen Und Kupplungsbau Gmbh | Friction clutch |
FR2750467A1 (fr) | 1996-06-27 | 1998-01-02 | Valeo | Embrayage a friction a dispositif de rattrapage de jeu pour vehicule automobile |
US6021877A (en) * | 1997-09-05 | 2000-02-08 | Mannesmann Sachs Ag | Thrust plate assembly |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2831233A1 (fr) * | 2001-10-23 | 2003-04-25 | Valeo | Embrayage a friction, pour vehicule automobile, equipe d'un dispositif de rattrapage de jeu pilote |
WO2003036116A3 (fr) * | 2001-10-23 | 2004-02-12 | Valeo Embrayages | Embrayage a friction, pour vehicule automobile, equipe d'un dispositif de rattrapage de jeu pilote |
US6957729B2 (en) | 2001-10-23 | 2005-10-25 | Valeo Embrayages | Friction clutch, for motor vehicle, equipped with a monitored play compensation device |
KR100910371B1 (ko) * | 2001-10-23 | 2009-08-03 | 발레오 앙브라이아쥐 | 마찰 클러치 |
EP2025961A1 (fr) * | 2007-07-25 | 2009-02-18 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Ensemble embrayage |
WO2013113530A1 (fr) * | 2012-02-02 | 2013-08-08 | Zf Friedrichshafen Ag | Ensemble embrayage et procédé de fabrication dudit ensemble embrayage |
WO2015127930A1 (fr) * | 2014-02-27 | 2015-09-03 | Schaeffler Technologies AG & Co. KG | Embrayage à friction comprenant un dispositif de rattrapage servocommandé |
CN106068394A (zh) * | 2014-02-27 | 2016-11-02 | 舍弗勒技术股份两合公司 | 带有力控制的补偿调节装置的摩擦离合器 |
CN106068394B (zh) * | 2014-02-27 | 2018-08-17 | 舍弗勒技术股份两合公司 | 带有力控制的补偿调节装置的摩擦离合器 |
EP4010605A4 (fr) * | 2020-05-15 | 2022-09-28 | Dönmez Debriyaj Sanayi Ve Ticaret Anonim Sirketi | Ensemble couvercle d'embrayage compensant l'usure de la garniture de manière précise et automatique |
Also Published As
Publication number | Publication date |
---|---|
ITRM20010234A1 (it) | 2002-11-04 |
AU2001262477A1 (en) | 2001-11-26 |
KR100881147B1 (ko) | 2009-02-02 |
DE10196193B3 (de) | 2012-12-06 |
KR20030025921A (ko) | 2003-03-29 |
DE10196193T1 (de) | 2003-04-24 |
ITRM20010234A0 (it) | 2001-05-02 |
US20030141163A1 (en) | 2003-07-31 |
FR2809147B1 (fr) | 2002-09-06 |
FR2809147A1 (fr) | 2001-11-23 |
DE10197401A5 (de) | 2013-04-11 |
DE10197401B4 (de) | 2013-09-19 |
US6779643B2 (en) | 2004-08-24 |
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