WO1998042994A1 - Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile - Google Patents
Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile Download PDFInfo
- Publication number
- WO1998042994A1 WO1998042994A1 PCT/FR1998/000596 FR9800596W WO9842994A1 WO 1998042994 A1 WO1998042994 A1 WO 1998042994A1 FR 9800596 W FR9800596 W FR 9800596W WO 9842994 A1 WO9842994 A1 WO 9842994A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- support
- plate
- clutch
- clutch according
- reaction plate
- Prior art date
Links
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
- F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
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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
- F16D2013/706—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the axially movable pressure plate is supported by leaf springs
Definitions
- Friction clutch with wear take-up device in particular for a motor vehicle.
- the present invention relates to friction clutches, in particular for motor vehicles.
- a friction clutch comprises at least one friction disc provided at its external periphery with friction linings, optionally split, intended to be clamped between a flywheel, forming a reaction plate, and a pressure plate.
- the flywheel is shaped to be linked in rotation to a first shaft, while the friction disc is shaped to be linked in rotation to a second shaft.
- the first shaft is a driving shaft
- the second shaft is a driven shaft, namely the input shaft of a movement gearbox, most often the shaft gearbox input.
- the flywheel possibly in two parts for, for example forming a double torsion damper flywheel, is fixed centrally to the engine crankshaft by means of fixing members, such as screws, while the friction disc has conventionally a central hub internally grooved for its connection in rotation to said input shaft. This hub is rigidly or elastically coupled to the friction linings.
- the pressure plate is linked in rotation, with freedom of axial movement, to the flywheel and has a friction face for the friction linings frontally, while the flywheel has a friction face for said linings dorsally.
- Elastic means with axial action bear on a cover and act on the dorsal face of the pressure plate to clamp the friction linings between the friction faces of the flywheel and the pressure plate. These elastic means are therefore engaging means tending to bring the pressure plate closer to the flywheel to tighten the friction linings.
- the cover is hollow in shape and is shaped at its outer periphery to be fixed to the steering wheel using fixing means.
- These fixing means can be of any type and consist, for example, of welding and / or crimping means.
- the pressure plate belongs to a unitary assembly, called the clutch mechanism, comprising the pressure plate - the engagement means, and the cover.
- This unitary assembly also includes declutching means associated with the clutching means to counteract the action of the clutching means.
- the pressure plate is in this case linked in rotation, with freedom of axial movement, to the steering wheel by means of first means of connection in rotation.
- the pressure plate has at its external periphery, projecting radially from the tabs, forming tenons, engaged in grooves, forming mortises, arranged axially in a cylindrical skirt of axial orientation which has the cover at its external periphery.
- This skirt is connected at one of its axial ends to a centrally perforated bottom and of transverse orientation. The bottom is directed radially inward. At its other axial end, the skirt is fixed to the steering wheel using the aforementioned fixing means.
- the pressure plate is linked in rotation by a cooperative connection of forms of the tenon-mortise type.
- the rotational connection means consist of elastic tongues elongated circumferentially in an arc of a circle or of tangential orientation.
- These tabs distributed in several groups of one or more superimposed tabs, are fixed at one of their ends to the pressure plate, for example to radial lugs thereof, and at the other of their ends to the cover , for example at a radial range thereof.
- the tongues constitute return means and ensure a return of the pressure plate towards the bottom of the cover in order to disengage the clutch, that is to say to release the friction linings from the friction disc so that they do not come to lick the friction surfaces of the flywheel and the pressure plate.
- the engagement means may consist of a plurality of coil springs or of an elastic washer with axial action of the Belleville washer type
- the declutching means may consist of a plurality of clutch levers acting on the Belleville washer to modify in a controlled manner the clamping action exerted directly or indirectly by this Belleville washer on the pressure plate.
- the engaging and declutching means belong to the same part called a diaphragm comprising a peripheral part, in the shape of a Belleville washer, extended radially inwards by a central part fragmented into radial fingers by slots. The radial fingers form the declutching levers and therefore the declutching means, while the Belleville washer with axial action forms the clutch means.
- the declutching means may consist of a false diaphragm, that is to say of a diaphragm, the peripheral part of which exerts a weak, even zero, elastic load. This can be achieved by providing this peripheral part with radial slots.
- the false diaphragm can act on one or for example two Belleville washers mounted in series.
- the said declutching means are pivoted or tilted so that they act on the engagement means for reducing and then canceling the clamping load (force) exerted by said engagement means on the pressure plate.
- the friction linings are no longer clamped between the pressure plate and the flywheel so that the torque is no longer transmitted from the first shaft to the second shaft.
- the clutch is then disengaged or disengaged. Normally the friction linings are tightened in the aforementioned manner by means of the engagement means. The clutch is therefore normally engaged or engaged.
- the friction clutch with a device to compensate for wear, in particular the friction linings and the friction faces.
- This device hereinafter called the wear take-up device, makes it possible, for example in the case of a friction clutch provided with a diaphragm, to have, during the life of the friction clutch for the position clutch engaged generally the same position for the internal end of the diaphragm fingers and a generally identical load exerted by the diaphragm on the pressure plate and the friction linings.
- the characteristic curve of the clutch release bearing remains generally identical (load exerted on the internal end of the diaphragm fingers as a function of the stroke).
- the wear take-up device comprises ramp means carried in part by a first part fixed in rotation and axially movable and in part by a second part movable in rotation and axially fixed.
- ramp means carried in part by a first part fixed in rotation and axially movable and in part by a second part movable in rotation and axially fixed.
- a trigger sensitive to the state of wear of at least the friction linings to control the relative movement between said parts.
- the first part is formed by the main part of the pressure plate and the second part by the support offered by the pressure plate to the engagement means.
- the second part Normally (clutch in the engaged position) the second part is clamped between the main part of the pressure plate and the engagement means, such as the Belleville washer of the diaphragm. No rotation of this second part is therefore possible.
- the trigger sensitive to the change in position of the pressure plate following the wear of the friction linings, makes it possible to release the second part, which can therefore rotate during the operation of disengagement of the clutch or when the clutch is in the disengaged position because the load exerted by the engagement means is low or zero. Wear of the friction linings therefore leads to an increase in the thickness of the pressure plate between its friction face and the support which it offers to the engagement means.
- One of the parts is in the form of a reaction plate providing a friction face for the friction lining concerned, while the other part consists of a support, of transverse orientation, shaped to be fixed to the first shaft.
- Second rotational connection means allowing axial movement, intervene between the reaction plate and the support so that said plate can move axially.
- the reaction plate is shaped to carry at its internal periphery part of the ramp means, while the support rotates the other part of the ramp means in association with circumferential action locking means.
- the object of the present invention is to respond to this wish economically.
- a clutch of the above-mentioned type comprising a support shaped to be fixed to a first shaft, and a reaction plate linked in rotation to the support by second rotation connection means allowing an axial displacement of the reaction plate by relative to the support
- the wear take-up device comprises, on the one hand, elastic means of compensation with axial action acting between the support and the reaction plate and, on the other hand, a blocking device disengageable with axial action carried by the reaction plate, in that the trigger acts on the blocking device so, in the event of wear of the friction linings, disengage said blocking device and allow movement of the reaction plate towards the pressure plate to compensate for said wear and in that the elastic compensation means exert a force on the reaction plate greater than the force exerted by the engagement means on the pressure plate.
- the pressure plate has a simple shape, as well as the wear take-up device, which is devoid of circumferential action locking means and ramp means. It is therefore possible to equip the friction clutch with a conventional clutch mechanism.
- the absence of ramp means makes the wear take-up device safer and more reliable since the risks of jamming due to the ramp means are eliminated.
- the reaction plate is therefore simplified since it does not have ramp means.
- the reaction plate may be in the image of the pressure plate, i.e. similar to the pressure plate, and have lugs on its outer periphery for supporting at .. 'least one releasable locking device axially acting.
- the machining of the reaction plate and the support are simplified. Thus, space is freed at the internal periphery of the reaction plate and of the support in the form of a plate, as a variant in the form of a disc, carrying a crown.
- the hub of the friction disc can penetrate the interior of the reaction plate, which is favorable for reducing the axial bulk.
- the support is also simplified since the elastic compensation means with axial action act axially between the support and the reaction plate and in an antagonistic manner with respect to the engagement means when the blocking device is disengaged.
- These elastic means economically consist of a Belleville washer or, as a variant, a diaphragm bearing, on the one hand, on its external periphery on a first boss belonging to the front face of the reaction plate, turned towards the support, and, on the other hand, at its internal periphery on a second boss carried by the support and directed towards the reaction plate.
- the first boss can be implanted overall on the same average circumference as a support, in the form of a boss, which the dorsal face of the pressure plate offers at the external periphery of the Belleville washer of a diaphragm, while the second boss is generally installed on the same average circumference as primary and secondary supports carried by the cover for pivoting mounting of the internal periphery of the Belleville washer of the diaphragm between said supports.
- the Belleville compensation washer acts in an antagonistic manner with respect to the diaphragm, the Belleville washer part of which constitutes the engagement means, and this in a precise and perfectly controlled manner. Indeed, on the one hand, the load on this Belleville washer is well controlled and, on the other hand, thanks to the implantation of the bosses, this Belleville washer acts geometrically in an antagonistic manner with respect to the diaphragm.
- the disengageable locking device with axial action is of the linear freewheel type and acts safely and reliably.
- This device can comprise two parts in relation to cylinder-piston defining between them a chamber filled with grease or any other viscous or pasty agent.
- the piston centrally carries the rod-shaped trigger acting on a valve whose seat is formed at the front end of the piston hollowed out for this purpose.
- the valve is normally closed so that normally the reaction plate cannot move axially towards the pressure plate and the bottom of the cover.
- the piston is in abutment against an integral part of the support.
- the clamping force exerted by the engagement means on the friction linings cannot move the reaction plate axially in the direction of the support, taking into account the higher force exerted by the compensating means on the reaction plate.
- This load of the compensating means is easy and controlled when it is a Belleville washer. In the event of wear, the pressure plate or the diaphragm act on the trigger to make it move back towards the support.
- the valve in the engaged clutch position, opens so that the reaction plate can move axially in the direction of the bottom of the cover in order to compensate for the wear of said friction linings.
- the displacement of the reaction plate causes, via the friction linings, a displacement of the pressure plate towards the cover so that the trigger follows the movement and that the valve closes.
- the pressure plate returns to its initial position.
- the wear take-up device is therefore simple in form, being of a safe and reliable operation.
- the cylinder is pushed by a shoulder integral with the reaction plate.
- the piston is supported, by its rear face, on a ring integral with the reaction plate.
- This ring makes it possible to stiffen the support and to form a unitary sub-assembly that can be handled and transported support - reaction plate - wear take-up device, which may belong to a double torsion damping flywheel.
- the elastic compensation means have a characteristic curve similar to that of the clutch means, being offset from it.
- the engagement and disengagement means may have any shape.
- the clutch can be of the pushed or pulled type.
- the support may belong to the second mass of a double torsion damping flywheel, of the type with elastic members with circumferential action, as described in document FR-A-2 729 199 or of the type with elastic members with radial action as described in the document FR-A-2 749 904.
- a double torsional damping flywheel is created, equipped within it with a wear take-up device comprising the support, the reaction plate, the elastic compensation means, the blocking device and the trigger according to the invention.
- This embodiment therefore makes it possible to mount a conventional clutch mechanism on a double torsion damping flywheel, the second mass of which is equipped with a wear take-up device.
- the first mass of the double torsion damping flywheel remains unchanged.
- the second mass of the latter is not modified in a profound manner since this amounts to changing the conventional reaction plate of the second mass by the support plate according to the invention.
- the flywheel according to the invention can therefore belong to the second mass of a double torsion damping flywheel and include within it a wear take-up device.
- the support is less hot than a reaction plate so that the bearing means acting between the two masses are less hot.
- FIG. 1 is a partial half-view in axial section of a friction clutch according to the invention
- FIG. 2 is a view along arrow 1 in Figure 1 without the clutch mechanism and the crown;
- FIG. 3 is a view along arrow 3 of Figure 1;
- FIG. 4 is an axial sectional view on a larger scale of the locking device of Figure 1;
- FIG. 5 is a schematic view of the clutch according to the invention.
- - Figure 6 shows the characteristic curves PI and P2 respectively of the diaphragm and the elastic compensation washer with the ordinate loads (or forces exerted) and the deflections on the abscissa;
- - Figure 7 is a view similar to Figure 1 for another variant;
- - Figure 8 is a view similar to Figure 4 for this other variant.
- FIG. 9 is an axial sectional view of a friction clutch according to the invention, equipped with a double torsional damping flywheel with elastic members with circumferential action;
- FIG. 10 is a half view in axial section on a larger scale of the friction clutch of Figure 9 ";
- FIG. 11 is an axial sectional view of a friction clutch according to the invention equipped with a double torsional damping flywheel with elastic members with radial action;
- FIG. 12 is a half view in axial section on a larger scale of the friction clutch of Figure 11;
- the friction clutch comprises in known manner a reaction plate 3, a pressure plate 7 and a friction disc 10 provided at its outer periphery with friction linings 11 intended to be tightened, when the clutch is engaged , between the friction faces 31, 21 facing each other, that the reaction plate 3 and the pressure plate 7 respectively have on the back, both of them made of cast iron.
- the cover 9 is here in stamped sheet metal, in cast iron variant, and the plate 1 in cast iron, in steel variant.
- the bottom 90 of transverse orientation is directed radially inwards.
- This support plate 1 is shaped at its internal periphery to be fixed directly ( Figures 1 to 8) or indirectly ( Figures 9 to 12) on a first shaft, while the friction disc 10 is shaped at its internal periphery to be linked in rotation to a second shaft.
- the support plate 1 is axially fixed and, when the first shaft rotates, is rotatable about the axis of axial symmetry XX ( Figures 9 to 12) of the friction clutch.
- the friction clutch is intended to equip a motor vehicle so that the support plate 1 is intended to be rigidly connected in rotation ( Figures 1 to 8) or elastic ( Figures 9 to 12) to crankshaft of the vehicle engine, constituting the first shaft, while the second shaft is the input shaft of the gearbox.
- Figures 1 to 8 the support plate 1 is intended to be rigidly connected in rotation
- Figures 9 to 12 the elastic
- crankshaft of the vehicle engine constituting the first shaft
- the second shaft is the input shaft of the gearbox.
- these shafts have not been shown, nor the internally splined hub which the friction disc has on its internal periphery for its rotational connection to the input shaft of the gearbox, as visible in document US-A-4, 195, 719.
- the clutch also includes declutching means 82 associated with the clutching means 81 for action on the clutching means 81 and canceling (release) of the force exerted by said clutching means 81 on the pressure plate 7 for tightening the friction linings 11 between trays 3.7.
- clutch means 81 and declutchers 82 belong to the same part 8, which is perforated centrally.
- This part 8 is an annular diaphragm.
- the diaphragm 8 In the free state, the diaphragm 8 has a frustoconical shape and undergoes mechanical and heat treatment operations to give it the desired shape and elasticity.
- This diaphragm 8 comprises a peripheral part 81 in the form of a Belleville washer extended radially inwards by a central part fragmented into radial fingers 82 by slots opening internally into the central opening of the diaphragm and externally, in the vicinity of the internal periphery of the Belleville washer 81, in an enlarged orifice 87.
- the slots are therefore blind.
- the clutch means are constituted by the Belleville washer 81 and the clutch means by the fingers 82 forming clutch release levers.
- the characteristic curve of the diaphragm 8 (force exerted - as a function of the deflection) depends on its thickness and on the height of its truncated cone and is visible in PI in FIG. 6 in which the deflection is shown on the abscissa (D) and on the ordinate the office exercised (C). This curve increases to a maximum, then decreases and then increases again.
- diaphragm 8 is pivotally mounted between a primary support 85 and a secondary support 84 carried by the cover 9.
- the diaphragm 8 In the clutch engaged position, the diaphragm 8 is supported by the internal periphery of its Belleville washer 81 on the primary support 85 and by the external periphery of its Belleville washer 81 on an annular boss 71, here divided into annular sectors, projecting axial by the dorsal face of the pressure plate.
- the boss 71 is directed towards the bottom 90 of the cover 9.
- the diaphragm 8 normally exerts a clamping action on the friction linings 11 to clamp them between the faces 31, 21.
- the diaphragm 8 bears on the secondary support 84.
- This change of support is carried out in a controlled manner using the declutching stop 83, which acts by pushing on the internal end of the fingers 82 of the diaphragm 8.
- the primary support 85 is produced by stamping the bottom 90 of the cover 9. Alternatively it may consist of a rod. It is the same for the secondary support 84 which is carried here by balusters 86.
- the secondary support may be constituted by the heads of the columns 86 profiled accordingly, knowing that the diaphragm 8 is interposed between the primary 85 and secondary 84 supports facing each other.
- the columns 86 are in two parts and each comprise a rivet passing through a socket engaged in an enlarged orifice 87 of the diaphragm 8.
- the secondary support 84 consists of a rolled crown, interposed between the head of each rivet and the end opposite the socket as described in the aforementioned document US 4,195,719 to which reference will be made for more details.
- this secondary support can be carried by lugs produced by cutting and folding the bottom 90 of the cover 9, said lugs each pass through an enlarged orifice 87 and are folded radially outwards at their free end, for the formation of an elbow. setting for a frustoconical crown whose external edge is rounded to form the secondary support 84.
- assembly means are provided for tilting mounting of the diaphragm 8 on the cover 9. These means comprise the primary support 85, the secondary support 84 and the posts 86 riveted to the bottom 90 or the aforementioned tabs.
- First rotational connection means 72 are provided for rotationally linking the pressure plate 7 to the cover 9 with the possibility of axial displacement. These means here consist of elastic tabs 72 distributed in several games, the number of which depends on the applications. One or more overlapping tabs can be provided for each set.
- tongues 72 are here of tangential orientation and are fixed at one of their ends each by a rivet 73 to a lug 75 circumferentially elongated that has the pressure plate 7, projecting radially outwards, at its outer periphery .
- the tongues 72 are fixed by riveting at 74 to the cover 9. More precisely, the rivet 74 is extended to form a column, the head of which forms a stop capable of cooperating with a circumferential projection 76 which the tab 75 has at the one of its circumferential ends.
- the bottom 90 of the cover 9 is extended at its outer periphery by a cylindrical skirt 92 of axial orientation. This skirt 92 is locally indented and is extended at its free end by a transverse rim 93, 94 directed radially towards the outside. It is by means of this rim 93, 94 that the cover 9, according to one characteristic, is fixed at its external periphery on the support plate 1 by means of fixing means 77 with the interposition of a closing crown. 6 between the flange 93, 94 and the external periphery of the plate 1.
- the cover 9 here surrounds the diaphragm 8 and the pressure plate 7.
- the fixing means here consist of a plurality of screws 77, the head of which rests on a radial area 93 for fixing the rim 93, 94 and crosses said area and the crown 6 in order to be screwed into the support plate 1.
- Pawns centering 78 carried by the support plate 1 are provided for center the rim 93,94 and the crown 6. The pins 78 therefore pass through holes in axial coincidence formed in the crown 6 and the pads 93.
- the rim 93.94 comprises (FIG. 3) two series of pads 93.94 offset axially.
- the above-mentioned areas 93 are used for fixing the cover 9 to the support plate 1, while the areas 94, which are closer axially to the bottom 90, are used for: fixing the tabs 72 using the balusters 74.
- two consecutive pads 93 are connected together by a pad 94 to define a first notch 79 allowing the passage of a tab 75 of the pressure plate.
- each pad 94 is perforated for the riveting of the tangential tabs 72 to the tabs 75 of the pressure plate 7.
- these elastic tongues 72 form elastic return means exerting an elastic return action on the pressure plate 7 in the direction of the bottom 90 of the cover and thus allow, when the clutch is disengaged, good release of the friction linings 11 .
- the cover 9, the diaphragm 8 and the pressure plate 7 form, thanks to the tabs 72, a unitary assembly called the clutch mechanism, the studs 74 limiting the movement towards the outside of the plate.
- pressure 7 by cooperation with the projections 76 when the clutch mechanism is in particular in the storage position, that is to say not fixed by means of its cover on the support plate 1.
- the tongues 72 are thus provided.
- the projections 76 are in abutment against the heads of the balusters 74.
- three sets of tongues 72 are provided distributed at 120 ° relative to each other. This number depends on the applications.
- the plate 1 in the embodiments of FIGS. 1 to 8 has centrally openings, one of which is not referenced is visible in FIG. 1. These openings are capable of being crossed by screws 12 allowing direct fixing of the plate 1 here at the crankshaft, so that this plate 1 is shaped at its internal periphery to be fixed to a first shaft. The plate 1 is therefore axially fixed and rotates with the vehicle engine.
- the support plate 1 is fixed axially and is shaped at its internal periphery to be connected elastically to a first mass 120 intended to be fixed to the first shaft.
- the plate 1 is thickened at its outer periphery to form an annular peripheral rim 22 of axial orientation.
- This flange 22 is here tapped and is drilled for mounting screws 77 and centering pins 78, as well as for mounting screws 67 with countersunk head for fixing the crown 6 on the free end of the flange 22.
- the rim 22 has second notches 29 as best seen in FIG. 3. These second notches 29 serve to accommodate tabs
- the support plates 1 and pressure plates 7 are also made of moldable material.
- the crown 6 makes it possible to stiffen the rim 22 by forming a bridge closing the second notches 29.
- the crown 6 also stiffens the rim 93, 94 of the cover 9 by closing the first notches 79.
- This crown 6 forms a partition separating the notches 29, 79 opposite. It will be noted that the first notches 79 are circumferentially longer than the second notches 29.
- the reaction plate 3 is linked in rotation to the support plate 1 with freedom of axial movement.
- second rotational connection means 32 with freedom of axial movement, intervene between the support plates 1 and reaction plates 3.
- the second rotation connection means 32 are like the first rotation connection means 72 and therefore consist of elastic tongues 32 of tangential orientation. These tongues 32 form second elastic return means and are fixed at one of their ends to the support plate 1 and at their other end to the lug 35, circumferentially elongated, of the reaction plate
- the tongues 32 are fixed to the plate 1 and to the lugs 35 using fastening members here with rivets, respectively 34.33.
- tongues 32 are distributed in several sets of tongues here superimposed.
- the number of sets of tongues 32 is here identical to that of the tongues 72.
- the elastic tongues 32, 72 can be in an arc of a circle.
- the tongues 32, 72 can be of radial orientation.
- rivets 33,73 are generally vis-à-vis ( Figure 3). The same applies to rivets 34.74.
- the reaction plate 3 is like the pressure plate 7 and a support plate 1 - reaction plate 3 sub-assembly is formed by the tongues 32.
- the crown 6 also belongs to this subset.
- the friction clutch according to the invention therefore comprises a flywheel in two parts, namely a reaction plate 3, dorsally offering a friction face 31 to the friction disc 10, and a support plate 1, of transverse orientation.
- This flywheel can be attached directly to the crankshaft of the vehicle engine ( Figures 1 to 8) or indirectly attached to the said crankshaft ( Figures 9 to 12).
- a wear take-up device 2.4 is mounted within the flywheel 1.3. This device makes it possible, in particular, to compensate for the wear due to the friction linings 11 and, to a lesser extent, due to the friction faces 21, 31. When said linings 11 wear out, the pressure plate 7 approaches the reaction plate 3 in so that the diaphragm position varies when the clutch is engaged.
- the purpose of the wear take-up device is to compensate for wear and maintain the position of the diaphragm 8 substantially constant when the clutch is engaged during the life of the friction clutch.
- the load exerted by the diaphragm 8 on the pressure plate 7 (clutch engaged) .. ' will also be generally constant in this clutch engaged position.
- the wear take-up device is, according to one characteristic, devoid of ramp means. It is for this reason that the reaction plate 3 is similar to the pressure plate 7.
- this plate 3 has a front support 23 in the form of a split boss like the boss 71.
- the boss 23 has the same average diameter overall as the boss 71, but is axially shorter than said boss 71.
- the boss 23 s 'extends axially projecting towards the support plate 1.
- Radially below the boss 23, the support plate 1 has a boss 24 generally of the same average diameter as the primary 85 and secondary 84 supports.
- the boss 24 extends projecting axially towards the reaction plate 3 and the bottom 90 of the cover 9.
- elastic compensation means 2 with axial action bear on the bosses 23-24. These elastic means 2 urge the reaction plate 3 towards the bottom 90 of the cover.
- the elastic means 2 act axially in the opposite direction relative to the diaphragm 8, that is to say in an antagonistic manner.
- the elastic compensation means belong to the wear take-up device and here consist of a Belleville washer 2 therefore having a characteristic curve P2 (FIG. 6) similar to that PI of the diaphragm 8.
- the washer 2 is replaced by a diaphragm allowing an air passage between the plates 1, 3.
- the Belleville washer 2 is perforated for the passage of air. The plate 3 is therefore cooled.
- the wear take-up device also comprises a trigger 41 sensitive to the state of wear of the friction linings 11 as well as to a lesser extent to the wear of the reaction and pressure plates 3, more precisely sensitive to the wear of the friction faces 21,31.
- the trigger 41 is installed on a diameter greater than that of the elastic compensation means 2.
- the trigger 41 is here controlled by the pressure plate 7 more precisely by the external periphery of the friction face 21 of the pressure plate.
- the trigger 41 is in abutment against said face 21.
- the trigger 41 is here in abutment against the lug 75 that is to say against the face of the lug 75 facing the crown 6.
- the trigger 41 is therefore in abutment a radial projection 75 directed towards the outside, which has the pressure plate 7 at its outer periphery.
- This face is here in the plane of the face 21.
- the said face can be offset axially with respect to the face 21, so that the cover 9 may not completely surround the pressure plate 7.
- the tab 75 may be shorter circumferentially and the trigger then bears on an additional projection carried by the external periphery of the pressure plate 7 and directed radially outwards.
- the trigger 41 can come into abutment against the diaphragm 8.
- This trigger 41 here consists of a cylindrical rod passing through a guide hole 61 made in the crown 6 to come into contact by its free end with the friction face 21 of the pressure plate delimiting the tab 75.
- the rod 41 by its free end may come into contact with the external periphery of the Belleville washer 81.
- a reaction stop 21 is therefore provided on one of the parts 7, 8, 9, to serve as a stop for the free end of the trigger 41.
- This reaction stop is therefore movable as a function of the wear, in particular of the linings 11. It is by means of this reaction stop 21 that wear is detected.
- the stop 21 is therefore a wear detector.
- the trigger 41 cooperates with a disengageable blocking device 4 with axial action housed here in a blind hole 5 produced in the tab 35 of the reaction plate 3.
- the hole 5 is open in the direction of the crown 6.
- the disengageable blocking device 4 is therefore carried by the reaction plate which is fixed in rotation and movable axially thanks to the tongues 32.
- the bottom 51 of the hole 5 forms a control stop for the locking device 4.
- This stop 51 is fixed in rotation and axially movable.
- This device 4 comprises two coaxial parts 42, 43 in cylinder-piston relation defining between them a cavity 44 or chamber of variable volume here filled with grease or any other pasty or viscous agent, preferably with high viscosity.
- One 42 of the parts 42, 43 is fixed and is engaged, in a complementary manner here by force, in the hole 5.
- This part 42 hereinafter called the cylinder, is hollow and serves to house the movable part 43, hereinafter called the piston.
- the cylinder 42 has a shape complementary to that of the blind hole 5.
- the piston 43 has a shape complementary to that of the cylinder, the external periphery of the piston 43 being in intimate contact with the internal bore of the cylinder, that is to say - say with the internal periphery of the cylinder.
- the piston 43 is axially movable relative to the cylinder 42.
- a seal 45 intervenes between the internal bore of the cylinder and the external periphery of the piston 43.
- the seal 45 is carried by the piston 43 having for this purpose at its outer periphery a groove for housing the seal 45, making it possible to seal the chamber 44.
- the blind hole 5 is of cylindrical shape with circular section in a square variant.
- the cylinder 42 and the piston 43 therefore have here in section a cylindrical shape with circular section in a square variant.
- the locking device 4 forms a cartridge mounted by its cylinder 42 in the hole 5.
- the movable piston 43 of the cartridge carries the trigger 41 centrally and for this purpose has a central bore 46 for guiding the trigger 41 projecting axially with respect to the piston 43 and this in the direction of the crown 6 and therefore of the pressure plate 7.
- the bore 46 and the hole 61 of the crown 6 are in axial coincidence.
- the piston 43 At its front end, directed towards the bottom 51 and the plate 1, the piston 43 carries a support 47 generally in the shape of a U, the bottom of the U forms a support for a spring 48 for setting and restoring, the other end of which presses on a valve 49 associated with the rod 41.
- the bore 46 is widened at the front at 50 at the front end of the piston 43 to form a seat 40 for the valve 49 in the form of spherical head secured to the rod 41, being here produced in one piece with the rod 41.
- the valve 49 may be a ball separate from the rod 41.
- valve 49 is able to be operated by the rod 41.
- the support 47 and the spring 48 are also housed.
- the support 47 has at the free end of each of its axially oriented branches, a fixing lug 52.
- the cavity or chamber of variable volume 44 is delimited, on the one hand, axially by the piston 43 and the transverse bottom of the cylinder 42 and, on the other hand, laterally by the cylinder skirt of the cylinder 42. Furthermore, in the vicinity of the valve 49, the rod 41 has a helical groove 53.
- Two transverse channels 54 open, on the one hand, internally, into the bore 41 in the vicinity of the front end of the portion of reduced size of the bore 41 - that is to say at the level of the seat 40 - and, on the other hand, externally in an annular groove 55 formed at the external periphery of the piston 43.
- the groove 55 is an antipollution groove and makes it possible to collect the fat passing through the groove 53 in the manner described below.
- the groove 55 is located axially between the seal 45 and the rear end of the piston 43 bearing on the crown 6.
- the support 47 is fixed here by crimping its lugs 52 to the piston 43. To do this, the large front part 50 of the bore 46 has, between the front end of the piston 43 and the seat 40, a shoulder not referenced serving as leg support
- the support 47 can be fixed by welding, screwing, etc., the support 47 and the spring 48 being housed in the piston 43 at the front end of the latter hollowed out to do this.
- the locking device 4 therefore acts axially between the reaction plate 3, which is axially movable, and a fixed part axially secured to the support plate 1, namely the crown.
- the locking device 4 can act between the reaction plate 3 and the cover 9, for example the flange
- the fixed part such as the crown 6 is offset axially in the direction of the bottom 90 of the cover 9 relative to the reaction plate 3.
- the wear take-up device 2,4 with trigger 41 operates in the following manner: In the engaged clutch position, new friction linings 11, the diaphragm 8 clamps the linings 11 between the pressure plates 7 and reaction plates 3 because the elastic compensation means 2 exert a force greater than that of the diaphragm 8.
- the tongues 32 and 72 allow the plates 3,7 to rotate with freedom of axial movement.
- the locking means 4 are locked, that is to say that the valve 49 is in abutment on its seat 4 ' 0.
- the friction linings 11 wear out the reaction plate 3 tends to move in the direction of the pressure plate 3 because the distance between the two plates 7 and 11 decrease with wear.
- reaction plate cannot move axially because of the locking device 4 then locked as shown diagrammatically in FIG. 5.
- the pressure plate 7 then acts on the trigger to approach the reaction plate 3.
- the force exerted by the diaphragm 8 on the pressure plate 7 and the trigger increases because the position of the diaphragm 8 tends to change.
- said valve leaves its seat 40 so that the cylinder pushed by the plate 3 moves and that grease can flow through the groove 53 in the channels 54 and this up to the collecting groove 55 and this without polluting the friction linings 11, which would harm the transmission of the torque.
- the reaction plate 3 moves under the action of the compensating means 2 towards the bottom 90 of the cover 9 and pushes, via the linings 11 forming wedges, the pressure plate 7 towards the bottom 90 of the cover 9.
- the rod 41 (the trigger) follows this movement so that the valve 49 closes. This is carried out in a reliable and safe manner, without risk of jamming due to the absence of ramp means facilitating the manufacture of the reaction plate 3 and the support plate 1.
- valve 49 closes when release, the trigger 41 is no longer subjected to 1 '' action of the pressure plate so that the spring 48 closes the valve.
- This plate 1 can be replaced by a thinner disk carrying at its outer periphery the flange 22.
- the clutch therefore comprises a support 1, such as a support plate, of transverse orientation, shaped to be connected to the first shaft, the support 1 being of annular shape.
- the engagement means 81 here the diaphragm, cannot move the reaction plate 3 axially, via the linings and the pressure plate 7, in the direction of the support 1 taking into account the greater reaction exerted by the elastic compensation means. It is therefore possible to normally tighten the linings 11 between the faces 21, 31, since the reaction plate 3 cannot move normally in the direction of the pressure plate 7 taking into account the presence of the locking device 4 and the fact that the piston 43 is supported by its rear end against the axially fixed crown 6 or another fixed part such as a portion of the cover 9.
- the trigger 41 (the rod) moves being guided axially by the crown 6 (the hole 61) and by the bore of the piston 43.
- the valve opens so that the reaction plate 3 is moves to the bottom 90 to compensate for wear.
- the pressure plate 7 therefore generally occupies the same position when the clutch is engaged: It is the same for the engagement and disengagement means.
- These may consist of one or more Belleville washers mounted in series and associated with a false diaphragm as visible in document FR-A-2 753 756 filed on September 6, 1996 and as mentioned above.
- use is made of a series mounting of a positive washer and of a negative Belleville washer as described in application WO 97/19275.
- the elastic compensation means 2 can in this case comprise two Belleville washers mounted in series with the interposition, for example, of a ring, like the ring 5 of the aforementioned document, between the contact zones of the two ' washers
- the engagement means may comprise a coil spring of frustoconical shape, acting between the cover and the declutching stop, capable of acting then on the declutching levers.
- the elastic compensation means can consist of a frustoconical coil spring.
- the elastic compensation means are of a shape analogous to that of the engagement means in order to have the same characteristic curve shape as these, but with a greater force for the same deflection (see FIG. 6).
- the locking device 4 comprises two coaxial parts, movable relative to one another, one of which carries the trigger 41, and capable of moving axially in one direction, one relative to the other and this disengageably under the action of the rod 41 (the trigger).
- Hole 5 is not necessarily blind.
- the cylinder 42 has at its rear end a flange 142 bearing against the rear face of the reaction plate 3 (of the ear 35 thereof), turned towards the plate pressure 7 to form the control stop and move the cylinder 42 towards the bottom 90.
- the reaction plate 3 is in two parts 130, 131 alternatively (FIG. 7), namely a support part 131 and the reaction plate 130 proper.
- a part 143 is fixedly mounted in the lug 35 and carries the valve 49, the support 47.
- This part 143 is like the piston 43 of Figures 1 to 4 and therefore has a bore 46 with a front part 50 housing the support 47, fixed by crimping, the calibration spring 48 and the valve 49 of spherical and integral shape rod 41 provided with a groove 153 opening into a collecting chamber 155 present at the rear of this part 143 valve holder.
- the piston is actually created by the reaction plate assembly 130, part 143.
- the cylinder is formed by the rim 22, the support 1 and by the support piece 131 fixed by riveting to the plate 1, radially above the screws 12.
- the plate 130 is provided with a transverse channel 154 opening internally into a chamber. 255 delimited by the plate 3 and the part 131.
- the plate 130 is linked in rotation to the support plate 1 in the same manner as in FIGS. 1 to 4, the compensation spring being identical.
- the grease in the chamber 255 prevents movement of the plate 130 under the action of the washer 2.
- the valve 49 opens and the grease is discharged into the chamber 155 closed by a metal plug 156.
- the plate 130 then moves to compensate for the wear of the linings.
- the valve 49 then closes during the declutching operation under the action of the spring 48 calibrated accordingly. In this case there is no need for crown 6.
- the piece 131 is annular and has at its axial ends respectively a fixing flange directed radially inwards for fixing, using rivets, screws or other member of the piece 131 on the support 1, said flange being in contact with the support 1, and a rim directed radially outward for axial delimitation of the chamber 255, delimited radially by the plate 130 and the part 131.
- the seals shown, in a dark manner in FIG. 7, are provided as well as a plug for closing the channel 154.
- the aforementioned reaction stop is not necessarily constituted by the tab 75 but by another projection of the pressure plate 7 or by the diaphragm 8.
- the rotational connection means 32 and 72 can, as mentioned above, be tenon-mortise type.
- the clutch can include several friction discs and several pressure plates.
- a blocking device 4 is here provided by lugs 35 of the reaction plate 3.
- Two devices 4, diametrically opposite can be provided. In general, it is sought to have a regular circumferential distribution of the locking devices in order to balance the reaction plate 3 and avoid any jamming of the triggers 4.
- the locking device 4 is generally carried by a radial projection directed towards the outside, which has the reaction plate at its external periphery like the pressure plate 7.
- This projection is in the figures the tab 35, but as a variant may consist of an additional tab, the tab 35 being circumferentially shortened.
- the structures can be reversed.
- the protrusions of the pressure 7 and reaction plate 3 then extend to the internal periphery of said plates, being directed radially inward and distinct from the legs 35.75.
- bosses 71, 23, 24, forming annular supports can be replaced by rods or any other cord.
- the clutch can be of the type pulled the outer periphery of the Belleville washer 81 then taking support on the cover, while the inner periphery of said washer
- the chamber 44 is of variable volume, the volume of this chamber decreasing with wear with transfer of grease in the channels 54 and the groove 55.
- the tongues 72.32 exert a negligible return force compared to the springs 8.2 (the clutch and compensation means).
- Elastic progressive means with axial action are usually provided between the linings 11. These have not been taken into account, here for simplicity. However, when the clutch is engaged, these means exert on the reaction plate 3 a force less than that exerted by the compensating means 2 to avoid taking up wear.
- the support 1 can be shaped at its internal periphery to be fixed to the first shaft indirectly.
- the support 1 in the form of a plate has a stepped internal bore for mounting a bearing 280 carried by the hub 180 of a first mass 120 intended to be fixed on the end of the crankshaft of the internal combustion engine.
- the first mass 120 is fixed to the crankshaft of the internal combustion engine using screws 100.
- the support 1 carries by attachment a disc 420 coupled elastically to the first mass by elastic members 320 with circumferential action as described in the document FR-A-2 729 199 to which reference will be made for more details.
- the steering wheel belongs to a double torsional damping flywheel comprising two coaxial masses 120, 1, 2 , 3, 4, 41, of axis of axial symmetry and of rotation XX mounted angularly movable one relative to the other relative to the other against elastic members 320 with circumferential action.
- the second mass comprises the support plate 1 of the reaction plate 3 and is rotatably mounted on the hub 180 of the first mass 120, here by means of a ball bearing 280 acting radially between the external periphery of the hub 180 and the internal periphery of the support plate 1 formed in favor of the central internal bore of the plate 1.
- the first mass 120 comprises a plate 200 which has at its internal periphery, in one piece, the central hub 180 and at its external periphery an annular skirt of axial orientation 220.
- the plate 200, the hub 180 and the one-piece skirt 220 are made of moldable material, here in cast iron.
- the first mass 120 is fixed to the crankshaft by means of the screws 100 passing through the hub 18 and located below the ball bearing 280.
- the second mass comprises the support plate 1 and is intended to be linked in rotation in a disengageable manner to the second shaft, namely here the input shaft of the gearbox via the friction disc 10 as mentioned above.
- the first mass delimits, for the most part a chamber 300 which can be filled with a pasty or viscous agent and in which are housed the elastic members with circumferential action 320, here in the form of coil springs of curved shape here pre-bent.
- the first mass 120 is shaped, thanks to its skirt 220, to retain radially, directly or indirectly the elastic members 220 arranged in a crown.
- the skirt 220 is hollowed out internally to present an imprint for retaining the elastic members 320.
- a chute 820 is deposited in the imprint and is therefore interposed radially between the internal periphery of the skirt 220 and the external periphery of the organs 320 to reduce wear.
- the chute is here made of high hardness steel.
- the chamber 300 is delimited for the most part by the plate 200, the skirt 220 and a disc 340 fixed here by crimping on the skirt 220.
- the disc 340 is stamped locally opposite plates 810, fixed by riveting on the plate 200, then bearing the ends of the elastic members 320 of great circumferential length.
- the plate 200 is hollowed out and the disc 340 is curved to define an annular channel for the elastic members 320.
- An internal disc 420 is fixed by rivets 4.40 to the support plate 1, hollowed out opposite the disc 340 adjacent to the plate 1 in order to reduce the axial bulk.
- the outer edge of the disc 42 has radial tabs 500 facing the plates 810 and the supports of the disc 340 to serve as a stop at the circumferential ends of the springs 320.
- the tabs 50 extend between the pads 810 and the supports of the disc 340.
- the tabs 500 enter a chamber closed internally by two sealing washers 560 arranged on either side of the disc 420.
- the washers 560 are elastic and metallic and are fixed with rivets 440 to the disc 420.
- the washers 560 are in abutment against a projecting surface of the plate 200 and against the internal periphery of the disc 340.
- the washers 560 close the chamber 300 at its internal periphery.
- the chamber 300 is partially filled here with grease and lubricates the elastic members 320 extending here each over a little less than 180 °, so that two tabs 500, two plates 810 and two diametrically opposed stampings are provided.
- a friction device 580 is provided in the center.
- This device is mounted on the hub 180 axially between the plate 200 offering a friction face and a ring 650 used for the axial setting of the inner ring of the bearing 280 fitted on the hub 180.
- a support washer for the heads of the fixing screws 100 is also used for axial setting of said inner ring.
- Rivets 660 each have a pawn-shaped head 680 penetrating into a notch 610 of a washer of friction 600 inserted axially between the plate 200 and a metal application washer 620 fixed in rotation on the hub using internal tabs (not referenced) penetrating into axial grooves (not referenced) of the hub 18.
- the rivets 660 serve fixing the sealing washers 560 to the internal disc 420.
- a disc 420 sub-assembly, washer 560 is thus formed. It is ultimately that the riveting on the support 1 using rivets 440 is carried out.
- An elastic washer with axial action here a Belleville 640 washer, is interposed axially between the ring and the washer 620 for axial tightening of the friction washer 600 between the plate 200 and the application washer 620 movable axially relative to the hub. 180, but fixed in rotation by virtue of the rotational connection produced using the internal tabs of the washers 620 engaged in the axial grooves of the hub 180.
- the pins 680 drive the washer 600 in rotation, here made of synthetic material.
- the elastic members 320 are compressed by the relative movement of the tabs 500 with respect to the plates 810 and to the disc 340.
- the washer 600 is driven by the pins 680.
- This washer rubs against the plate 200 and the washer 620, the pins 680 meshing with the notches 610.
- the support 1 has a ring 240 projecting axially and provided at its inner periphery of the groove 241 for collecting oil or fat escaping from the bearing 280 or the crankshaft.
- This plate 1 is therefore stiffened at its internal periphery thanks to the ring 240 the boss 24 extending radially below the recess made in the plate 1 for the curving of the disc 340.
- the groove 241 advantageously opens into the ventilation holes 242 produced in the plate 1.
- the ring 240 is chamfered at 243, at its base opposite a chamfer presented by the pressure plate 3 at its internal periphery.
- the chamfer 243 is connected to the groove 241.
- the disc 10 is protected and a funnel is formed between the plate 3 and the ring 240 of the reaction plate, promoting ventilation between two plates 1, 3.
- the bearing 280 is thus less hot than that of do.cument FR-A-2 729 199 because the reaction plate 3 is connected to the bearing 280 by the support plate 1 with intervention according to the invention of elastic compensation means 2 between the two plates 1, 3 separated one of the other.
- the support plate 1 always belongs to the second mass of a torsion damping flywheel as in FIGS. 9 and 10.
- the plate 1 has a ring 240 radially below the bearing boss 24 of the elastic compensation hubs 2.
- the ring 240 in all cases stiffens the support 1.
- a funnel is formed between the ring 240 and the reaction plate 3 as in FIG. 9, but the ring 240 is devoid of grooves its inner periphery.
- the elastic compensation hubs 2 are perforated for air passage between the plates 1 and 3 and ventilation.
- a second hub 300 has a stepped internal bore for mounting the ball bearing 280, the first mass 120 comprising a plate 200 in one piece at its external periphery with an annular skirt 220 of axial orientation.
- the hub 300 is made of treated steel and can alternatively form the outer ring of the bearing 280.
- the second hub 300 is therefore mounted for rotation on the hub 180, called the first hub, here by means of the ball bearing 280.
- the hub 300 is perforated at 301 for the passage of at least one tool allowing access to the fixing screw 100 of the first mass 120 or crankshaft of the engine.
- the fixing screws are therefore installed here radially above the reduced-size ball bearing 280.
- the holes 301 allow ventilation of the support plate 1.
- the second hub 300 has at its outer periphery a groove 302 as described in document FR-A-2,749,904 to which reference will be made for more details.
- This groove 302 is delimited by a cylindrical bottom of axial orientation allowing centering of the internal periphery in the form of a disc 303 of the support plate 1. More precisely, the internal bore of the disc 303 is in intimate contact with the bottom of the throat. The lateral faces of the disc 303 are in contact respectively with a web 304 of the hub 300, forming one of the sides of the groove 302, and with a friction washer 330 forming the other side of the groove.
- the washer 330 is subjected to the action of an elastic washer with axial action 340 integral in rotation with the hub 300.
- the elastic washer has at its internal periphery a transverse orientation part in which are made mooring holes through from which rivets 305 pass through the hub 300 to form pivots 306 between the plates 200, 1.
- the external periphery of the washer 340 is of frustoconical shape and is connected by a fold to its transverse part. Holes not referenced are made in the fold. Folded tabs (not referenced) from the inner periphery of the friction washer 330 penetrate the holes. The washer 330 is thus linked in rotation to the elastic washer with the possibility of axial displacement.
- the second mass of the double torsion damping flywheel comprises a torque limiter with the support 1 mounted by means of its internal disc 303 in the groove 302 of the central hub 300 with controlled tightening of the disc 303 between the wall 304 and the friction washer 330 subjected to the action of the elastic washer 340.
- the support 1 skates with respect to the hub 300 and therefore moves with respect to the latter . Skating absorbs excess torque. Under normal conditions, no relative movement occurs between the hub 300 and the support 1.
- the support 1 is mounted for rotation so controlled on the second hub 300, the bottom of the groove 302 forming a centering bearing.
- the plate 200 of the first mass carries at its external periphery pivots 307 in the form of pins fitted into the plate 200 and in an external disc 440 fixed by riveting to the skirt 220.
- the pivots 306, 307 allow the mounting of elastic members with radial action 520.
- These members 520 are compression springs and belong to cassettes each comprising a cylinder 421 with an upper articulation head 422 provided with a bearing 423 mounted on a pivot 307.
- a piston 424 is mounted inside the cylinder 421
- the piston 424 is integral with the rod 425 having at its internal periphery a lower articulation head 426, carrying a bearing 427 mounted on a lower pivot 306.
- the lower part of the cylinder is closed by a washer 428 traversed by the rod 425.
- the elastic members 520 here concentric helical springs, therefore bear at their internal periphery on the washer 428 secured to the cylinder 421 mounted for articulation by the pivots 307 on the first mass 120 and at their external periphery on the piston 424 mounted in articulation by its rod 425 with head 426 on the pivots 306 of the second hub 300.
- Some at least pivots 306 have an end pin 308 which, meshes with a friction washer 260, the pins
- the washer 260 constantly rubs against the plate 200 and drives in rotation, after taking up an angular play, a second washer 360 pinched between the plate 200 and an application washer 262 with external radial lugs (not referenced) penetrating into grooves (not referenced) formed in an additional thickness of the plate 200.
- the washer 262 is subjected to the action.
- an elastic washer with axial action here a Belleville washer 364, bearing on a closing washer 365 fixed by riveting on the plate.
- the washer 360 has tabs at its internal periphery penetrating a circumferential clearance in notches which the washer 260 has at its external periphery.
- the washer 365 is elastic and urges the washer 260 towards the plate 200.
- the washer 360 therefore intervenes delayed.
- the double flywheel therefore operates like that of document FR-A-2 749 904, with elastic radial action members 520 mounted at articulation at the external periphery of the first mass and at articulation at the internal periphery of the second mass.
- the friction device is therefore here located between the springs 420 and the plate 200 above the bearing 280.
- a torque limiter of the type of that of FIGS. 11 and 12 can replace the support plate 1 of FIGS. 9 and 10 and vice versa.
- the friction disc is of course rigid and we see in 700 its hub rigidly coupled to the linings 11.
- an unreferenced pilot bearing is mounted in the hub 180 to support the end of the second tree.
- the elastic means 2 comprise a Belleville washer or a diaphragm.
- the elastic means 2 therefore have at least one Belleville washer, knowing that a diaphragm has a Belleville washer at its outer periphery.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/194,376 US6053296A (en) | 1997-03-25 | 1998-03-25 | Friction clutch with wear take-up device, especially for motor vehicles |
DE19880565T DE19880565T1 (de) | 1997-03-25 | 1998-03-25 | Reibungskupplung mit Verschleißnachstellvorrichtung, insbesondere für Kraftfahrzeuge |
EP98917225A EP0914568A1 (fr) | 1997-03-25 | 1998-03-25 | Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR97/03628 | 1997-03-25 | ||
FR9703628A FR2762060B1 (fr) | 1997-03-25 | 1997-03-25 | Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998042994A1 true WO1998042994A1 (fr) | 1998-10-01 |
Family
ID=9505162
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR1998/000596 WO1998042994A1 (fr) | 1997-03-25 | 1998-03-25 | Embrayage a friction a dispositif de rattrapage d'usure, notamment pour vehicule automobile |
Country Status (5)
Country | Link |
---|---|
US (1) | US6053296A (fr) |
EP (1) | EP0914568A1 (fr) |
DE (1) | DE19880565T1 (fr) |
FR (1) | FR2762060B1 (fr) |
WO (1) | WO1998042994A1 (fr) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0926374A1 (fr) | 1997-12-23 | 1999-06-30 | Valeo | Embrayage à friction à dispositif de rattrapage d usure, notamment pour véhicule automobile |
EP1099877A1 (fr) * | 1999-04-26 | 2001-05-16 | Unisia Jecs Corporation | Volant cinetique d'un moteur a combustion interne |
WO2016146119A1 (fr) * | 2015-03-18 | 2016-09-22 | Schaeffler Technologies AG & Co. KG | Embrayage à friction équipé d'un dispositif de rattrapage d'usure |
EP3109497A1 (fr) * | 2015-06-26 | 2016-12-28 | Schaeffler Technologies GmbH & Co. KG | Amortisseur de vibrations torsionnelles comprenant un dispositif de reglage |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2778441B1 (fr) * | 1998-05-05 | 2001-01-19 | Valeo | Double volant amortisseur de torsion, notamment pour vehicule automobile |
FR2832776B1 (fr) * | 2001-11-26 | 2004-11-26 | Valeo | Embrayage a friction a dispositif de rattrapage d'usure, en particulier pour vehicule automobile |
DE10225991A1 (de) * | 2002-06-12 | 2003-12-24 | Sachs Race Eng Gmbh | Reibungskupplung |
DE102015201674A1 (de) * | 2014-02-07 | 2015-08-27 | Borgwarner Inc. | Selbstnachstellende kupplungsgegendruckplatte |
WO2015134219A1 (fr) * | 2014-03-06 | 2015-09-11 | Schaeffler Technologies AG & Co. KG | Embrayage double tronconique |
DE102014216594B3 (de) * | 2014-08-21 | 2015-08-06 | Schaeffler Technologies AG & Co. KG | Drehschwingungsdämpfer eines Einmassenschwungrads oder eines Zweimassenschwungrads |
JP5748086B1 (ja) | 2014-11-28 | 2015-07-15 | 昌克 ▲高▼野 | デュアルクラッチの係脱機構 |
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GB2022729A (en) * | 1978-05-26 | 1979-12-19 | Borg Warner | Automatic wear compensator spring clutches |
US4195719A (en) | 1977-07-19 | 1980-04-01 | Francisco Montoro Munoz | Construction of friction clutches |
DE4111503A1 (de) * | 1990-04-11 | 1991-10-17 | Honda Motor Co Ltd | Mehrscheibenkupplungsvorrichtung |
US5139124A (en) * | 1985-09-07 | 1992-08-18 | Luk Lamellen Und Kupplungsbau Gmbh | Apparatus for compensating for fluctuations of torque between the engine and the transmission of a motor vehicle |
WO1993007400A1 (fr) * | 1991-10-04 | 1993-04-15 | Automotive Products Plc | Embrayage a friction |
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US5404979A (en) * | 1994-05-27 | 1995-04-11 | Chrysler Corporation | Motor vehicle manual transmission modular clutch assembly |
BR9611721A (pt) * | 1995-11-17 | 1999-12-28 | Yves Jean Kemper | Sistema atuador de força controlada, embreagem automotiva, freio de fricção e processo de aplicar uma força atuante entre um membro de carga e um membro de reação |
FR2753756B1 (fr) * | 1996-09-06 | 1999-01-22 | Mecanisme d'embrayage pour embrayage a friction a faible effort de debrayage |
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1997
- 1997-03-25 FR FR9703628A patent/FR2762060B1/fr not_active Expired - Fee Related
-
1998
- 1998-03-25 DE DE19880565T patent/DE19880565T1/de not_active Withdrawn
- 1998-03-25 WO PCT/FR1998/000596 patent/WO1998042994A1/fr active Application Filing
- 1998-03-25 US US09/194,376 patent/US6053296A/en not_active Expired - Fee Related
- 1998-03-25 EP EP98917225A patent/EP0914568A1/fr not_active Withdrawn
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FR2426834A1 (fr) | 1978-05-26 | 1979-12-21 | Borg Warner | Compensateur d'usure automatique pour embrayage a ressort belleville |
US5139124A (en) * | 1985-09-07 | 1992-08-18 | Luk Lamellen Und Kupplungsbau Gmbh | Apparatus for compensating for fluctuations of torque between the engine and the transmission of a motor vehicle |
DE4111503A1 (de) * | 1990-04-11 | 1991-10-17 | Honda Motor Co Ltd | Mehrscheibenkupplungsvorrichtung |
WO1993007400A1 (fr) * | 1991-10-04 | 1993-04-15 | Automotive Products Plc | Embrayage a friction |
FR2722852A1 (fr) | 1994-07-21 | 1996-01-26 | Valeo | Mecanisme d'embrayage a dispositif de rattrapage d'usure, notamment pour vehicule automobile |
FR2729199A1 (fr) | 1995-01-11 | 1996-07-12 | Valeo | Procede de fabrication d'un volant amortisseur notamment pour vehicules automobiles |
FR2749902A1 (fr) * | 1996-06-14 | 1997-12-19 | Valeo | Procede d'assemblage et de reglage des elements d'un dispositif elastique d'amortissement |
FR2749904A1 (fr) | 1996-06-17 | 1997-12-19 | Valeo | Volant double amortisseur muni d'un limiteur de couple a montage simple |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0926374A1 (fr) | 1997-12-23 | 1999-06-30 | Valeo | Embrayage à friction à dispositif de rattrapage d usure, notamment pour véhicule automobile |
EP1099877A1 (fr) * | 1999-04-26 | 2001-05-16 | Unisia Jecs Corporation | Volant cinetique d'un moteur a combustion interne |
EP1099877A4 (fr) * | 1999-04-26 | 2005-09-21 | Unisia Jecs Corp | Volant cinetique d'un moteur a combustion interne |
WO2016146119A1 (fr) * | 2015-03-18 | 2016-09-22 | Schaeffler Technologies AG & Co. KG | Embrayage à friction équipé d'un dispositif de rattrapage d'usure |
EP3109497A1 (fr) * | 2015-06-26 | 2016-12-28 | Schaeffler Technologies GmbH & Co. KG | Amortisseur de vibrations torsionnelles comprenant un dispositif de reglage |
Also Published As
Publication number | Publication date |
---|---|
FR2762060B1 (fr) | 1999-05-14 |
DE19880565T1 (de) | 1999-07-08 |
FR2762060A1 (fr) | 1998-10-16 |
EP0914568A1 (fr) | 1999-05-12 |
US6053296A (en) | 2000-04-25 |
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