KR20040045381A - Friction clutch comprising a device for taking up wear of friction linings, in particular for a motor vehicle - Google Patents

Abstract

PURPOSE: A friction clutch is provided to relieve the demand condition for both spaces in the radial direction and the axial direction by compensating wear of friction linings with the wear take-up device. CONSTITUTION: A friction clutch is composed of a reaction plate, a friction disk(100), a pressure plate(11), a cover(12) fixed in the reaction plate, an assembling unit(13) axially operated between the cover and the pressure plate rotated and fixed to the cover, a wear compensating unit having a ramp unit(14) cooperating with a counter-ramp unit(15), and a tooth set(19) engaged with a worm(23) arranged tangentially. The ramp unit is rotated and fixed to the tooth set, and a worm driving unit is operated by wear of friction linings(101) in assembling the clutch and composed of a ratchet wheel(20) fixed to the worm. The ratchet wheel is controlled by a control tongue(36) of an elastic member(32). The elastic member is extended to a lower part(42) of the cover, and directly fixed to the cover.

Description

FRICTION CLUTCH COMPRISING A DEVICE FOR TAKING UP WEAR OF FRICTION LININGS, IN PARTICULAR FOR A MOTOR VEHICLE}

FIELD OF THE INVENTION The present invention relates to a friction clutch for automobiles, and more particularly to a clutch having a device for compensating for wear of at least one friction lining, which device acts when the lining (s) is worn in the following description. It is called a wear take-up device.

Generally, conventional friction clutches include a recoil plate belonging to a flywheel consisting of two parts to form a damping flywheel or a flexible flywheel, which is typically a first shaft which is a drive shaft, such as a crankshaft of an internal combustion engine. Is supported by its outer periphery, which is rotationally clamped on and to which at least one pressure plate is attached.

The pressure plate is rotatably fixed to the cover and the recoil plate, while being able to move axially under the action of the engaging means acting in the axial direction controlled by the separating means. This coupling means consists of a helical spring, or one or two Belleville washers mounted in series or in parallel, and is acted upon by a clutch release lever forming a separating means. In general, these coupling and disconnecting means belong to one and the same component, for example a metal diaphragm located on a cover. The diaphragm can be mounted in series or in parallel with the dish washer to aid in the separating force.

A friction disk supporting at its outer periphery the at least one friction lining, which is rotationally fixed to a shaft which is a conventional driven shaft, such as the input shaft of the gearbox, is inserted between the pressure plate and the reaction plate so that the clutch is in the engaged position. It is held between them. When the engaging means are actuated by the clutch release bearings via the separating means, the engaging means controls the axial displacement of the pressure plate. Often, the friction disk comprises an axial resilient support disk on which two friction linings are fixed on both sides. As a result, the friction disk is gradually gripped. As a variant, the support disk is rigid and, for example, fits into the friction lining at its outer periphery.

During the useful life of such a clutch, not only the friction lining (s) but also the counter elements, i.e. the pressure plate and the recoil plate, are worn, the wear of which changes in the position of the pressure plate and in the position of the axially actuating coupling means and the clutch release bearing. The change in the operating state of the separating means thus results in a shift in the gripping force between the horsepower disc and on the other hand the pressure and the recoil plate, thus affecting the force required to release the clutch. Crazy By providing a wear compensating device for such a clutch, this disadvantage is avoided, and the engagement means and the clutch release bearings, which are usually constantly positioned on the release means, occupy the same position when the clutch is in the engaged position, thus providing the shaft of the clutch Directional space requirements are reduced.

A recoil plate intended to be rotationally clamped to the drive shaft, at least one friction lining at its outer periphery, a friction disc intended to be rotationally clamped to the driven shaft, a pressure plate, a cover fixed to the recoil plate, and A friction clutch for a motor vehicle comprising an axially actuating coupling means controlled by a separating means and acting between a cover and a pressure plate on the one hand by means of the second and first stop means, the pressure plate comprising: Secured to the cover while being axially movable relative to the cover and under the action of elastic return means for returning the pressure plate axially towards the cover, the friction clutch also being positioned axially between the stop means and the pressure plate. And cooperate with counter-ramp means And a wear compensation device having a circumferentially arranged ramp means adapted for rotationally securing the tangentially arranged worm cooperatively set of teeth and rotating the worm. The means are constituted by a ratchet wheel which is actuated by wear of the friction lining (s) when the clutch is engaged and is rotatably fixed to the worm and controlled by a control tongue equipped with an elastic member. Wherein the worm and the ratchet wheel is supported by a support, the support and the elastic member is fixed to the cover and located therein, the support is a web (web), the spindle supporting the worm and the ratchet wheel ( Friction clutches for automobiles that are U-shaped with two wings suitable for supporting a spindle are known.

Such clutches are disclosed, for example, in French Patent No. 2 753 503.

It is an object of the present invention to propose a friction clutch having a device for compensating for wear of the friction lining, wherein this type of automotive friction clutch reduces the space requirement in both radial and axial directions.

According to the invention there is provided a recoil plate intended to be rotationally clamped to a drive shaft, at least one friction lining on its outer periphery, a friction disc intended to be rotationally clamped to a driven shaft, a pressure plate and the recoil plate. A cover fixed to the control means, the coupling means being controlled by the separating means and acting axially between the cover and the pressure plate on the one hand by means of the second and first stop means. A friction clutch for an automobile of the type wherein said pressure plate is rotatably fixed to said cover, while being able to move axially with respect to said cover, the action of elastic return means for returning said pressure plate axially towards said cover. Receive; The clutch further comprises a wear compensation device having ramp means, the ramp of the ramp means being arranged in a circumferential direction, axially positioned between the stop means and the pressure plate and cooperating with a counter-lamp means. Suitable for; The tooth set cooperates with tangentially disposed worms; The ramp means is rotatably fixed to the set of teeth; Means for rotationally driving the worm are provided to operate by wear of the friction lining (s) when the clutch is engaged, constituted by a ratchet wheel rotatably fixed to the worm, and having a control tongue with an elastic member. Controlled by the vehicle, the friction clutch is characterized in that the worm and the ratchet wheel are rotatably mounted around a spindle directly supported by the cover.

Advantageously, the free end of the elastic member is in the shape of a control tongue and extends generally parallel to the shaft of the clutch.

Preferably, the radially facing portion of the resilient member and the control tongue are radially in line with the opening formed in the bottom of the cover.

Advantageously, such openings allow the elastic member to be at least partially in line with the lower thickness of the cover in the axial direction.

Preferably, the elastic member is suitable for cooperating in contact with the cover by means of a radially facing portion on the outside.

Preferably, the so-called lateral arms extend to either side of the control tongue and are suitable for contacting against the radial edge of the opening constituting the control contact.

Advantageously, in its portion, which is generally parallel to the axis supporting the control tongue at the end, the resilient member comprises a cutout by creating a subpressure suitable for contacting the upper edge of the opening.

Preferably, the spindle is supported by a support fixed to the cover.

Advantageously, the support is generally U-shaped with a web and two wings suitable for supporting the spindle.

Preferably, the support is fixed to the cover by its web.

Advantageously, the axially actuating coupling means consists of a diaphragm.

Preferably, the elastic member is secured to the cover by one of the members for securing the organic articulation means of the diaphragm to the cover.

Preferably, the ratchet wheel is controlled by the diaphragm via the control tongue.

Advantageously, the ratchet wheel is controlled by an actuating device constituted by radial appendages provided on the outer periphery of the diaphragm.

Preferably, the actuating device is axially offset towards the bottom of the cover relative to the dish washer portion of the diaphragm.

Advantageously, the actuating device comprises a passageway through which the control tongue passes.

Preferably, the control tongue has a V-shaped fold and the elastic member includes an elastic lateral wing to be elastically supported by the diaphragm and to move with the diaphragm.

Advantageously, the drive device is arranged axially between the back of the control tongue and the end of the elastic lug, which is the cutout of the elastic member.

Preferably, the ramp means comprises a ramp inclined on one side and distributed in the circumferential direction, and a ring having the second stop means in the axial direction on the other side.

Advantageously, the lamp and the second stop means are substantially aligned with one another in the radial direction.

Preferably, the counter-lamp means consists of a pad intended to cooperate with the lamp of the lamp means.

Advantageously, the worm is mounted to be able to move along its axis by the action of so-called elastic compensation means.

Preferably, the cover comprises an annular skirt inclined to an axis having an opening in alignment with the worm partially received in the opening.

DETAILED DESCRIPTION Embodiments illustrated in the accompanying drawings are described to better understand the object of the present invention, which is purely illustrative and non-limiting.

1 is a partial cross-sectional view of a clutch having a wear compensation device according to the present invention;

2 is a cross-sectional view of the clutch along arrow II of FIG.

3 is a front view of the ramp means,

4 is a perspective view of the interior of a cover for receiving lamp means, worms, ratchet wheels and spiral springs;

5 is a partial perspective view of a partially cut clutch mechanism;

6 is a plan view of the contact component, FIGS. 7 and 8 are cross-sectional views of the contact component along the lines VII-VII and VIII-VIII of FIG. 6, respectively;

9 is a perspective view of the contact component,

10 is a partial side view perspectively showing the cooperation between the operating device and the elastic member;

11 is a plan view of a diaphragm with an actuating device,

12 is an enlarged view of the enlarged part XII of FIG. 11 showing the operating device;

13 is a view of a similar variant of FIG. 1, FIG.

14 is a cross-sectional view of a clutch variation according to the present invention;

15 is a partial front view of FIG. 14;

16 is a partial view of FIG. 14 at a larger scale;

17 is a front view showing the elastic member of the modification to FIGS. 14 to 16, and FIG. 18 is a side view showing the elastic member of the modification to FIGS.

<Description of the code | symbol about the principal part of drawing>

100: friction disk 101: friction lining

11: pressure plate 12: cover

13 coupling means 14 lamp means

16 lamp 17 second stop means

18: first stop means 19: teeth

Referring to the drawings, it can be seen that it is an automotive friction clutch comprising a pressure plate 11 intended to cooperate with the friction disk 100 shown in FIG. 1, and a damper for supporting the friction lining 101 at its outer periphery. It consists of a plate or a supporting disk, which cooperates with the recoil plate itself. Recoil plates (not shown) belong to a flywheel intended to be rotationally clamped to a drive shaft, such as a crankshaft of an internal combustion engine. The friction disk 100 is rotationally fixed to a driven shaft, such as the input shaft of the gearbox, by a hub supported by a damper plate at its inner circumference.

The pressure plate made of castable material, here cast iron, is an axially elastic tangential tongue (not shown) which constitutes a means for returning the pressure plate 11 towards a cover 12 made of pressed sheet metal. Rotationally fixed to the hollow shaped cover 12 in a known manner. The cover 12 comprises a transversely oriented lower portion 42 connected to a radial rim 21 for fastening to the recoil plate by means of an annular skirt 41 inclined to the axis. This rim 21 is divided into an offset region in the axial direction.

Thus, the pressure plate 11, which is rotationally fixed to the cover 12, is supported by the retaining ring 10 supported by the rivet 48 located at the inner periphery of the lower part 42 of the cover 12 and by the cover. Elastic means actuated in a controlled axial direction articulated to the cover 12 by an arcuate pressing portion 18 formed in the lower portion 42 of the 12 to provide a first stop for the diaphragm 13. 1, ie axially moveable with respect to the cover 12 under the operation of the diaphragm 13 herein, the clutch is a push type herein and the release action is the arrow of FIG. 1 shown with the clutch engaged. By actuating the end of the finger of the diaphragm 13 in the direction of (F); The diaphragm 13 is connected to the joint between the first stop 18 and the outer periphery of the retaining ring 10, which makes it possible to elastically grip the diaphragm with respect to the first stop 18. Is mounted by

In order to maintain the axially acting elastic means 12 in a position irrespective of the wear of the lining 101 of the friction disk 100 when the clutch is engaged, and the face portion referred to as the friction surface portion of the disk 100 In order to reduce wear of the pressure plate 11 and the rebound plate in contact with the lining 101, a wear compensation device is provided comprising a lamp means 14 with a lamp 16 arranged in the circumferential direction; More specifically, this ramp means 14 consists of a ring with a ramp 16 arranged in the circumferential direction and extending towards the pressure plate 11; The ring has a so-called second stop region 17 constituted by a rounded upper ridge disposed on an arc centered on the axis of the clutch on its opposite surface. Of course, the second stop region 17 may be continuous or discontinuous. This stop region 17 is located radially above the first stop region 18.

The pressure plate 11 comprises counter-lamp means comprising a counter-lamp 15 in the form of pads spaced apart from each other in the circumferential direction on its face facing towards the lower part 42 of the cover 12. The counter-lamp 15 corresponds to separating two consecutive lamps 16 in the circumferential direction, the counter-lamp 15 cooperates with the lamps 16, respectively. Intended to.

A lamp means 14 is located axially between the diaphragm 13 and the counter-lamp means such that the counter-lamp 15 receives the lamp 16 and the diaphragm 13 has a secondary stop region 17. The diaphragm 13 acts on the pressure plate 11 by cooperating with to constitute a stop means.

The set of teeth 19 is connected to the lamp means 14 by means of a rotary connecting means, which connects the set of teeth 19 and the lamp means 14 as disclosed in French Patent No. 2 784 150. It allows for relative axial movement of the two components it contains.

At their outer periphery, the ramp means 14 comprises a radial lug 44, here five radial lugs 44; Between two of these radial lugs 44, the segment 45 with the set of teeth 19 extends in the circumferential direction, and the set of teeth 19 is produced by cutting the edge of the segment 45. . The stop face of the pressure plate 11, on which the pad 15 is formed, has a cylindrical edge 28 in the circumferential direction on the outer circumference of which the ramp means 14 is centered. It has a radially oriented annular rim in intimate contact.

The end arm of the segment 45 between which the set of teeth 19 extends is thin, resilient and arcuate, so that the secondary stop region 17 of the secondary stop region 17 is here secured to the radial lug 44 by rivets. A set of teeth 19 is axially offset relative to the plane.

In terms of balance, the other three radial lugs 44 support the so-called balancing segments 55, which are arranged radially opposite to the segment 45 having the set of teeth 19.

The ramp 16 and the secondary stop means 17 are substantially in line with one another in the radial direction; Thus, the lamp means 14 is simple and very rigid in the axial direction with low inertia, and together with the segments 45 and 55 constitutes a subassembly.

The counter-lamp 15 and the cylindrical edge 28 of the pressure plate are machined from roughly cast projections.

The wear compensation device also includes a ratchet wheel having an inclined tooth and mounted to be able to rotate about a spindle 27 supporting the worm 23; The thread and pitch of the worm 23 is suitable for the set of teeth 19; The worm 23 is adapted to cooperate with the set of teeth 19 under the conditions described below.

The spindle 27 is supported by the cover 12; More specifically, the skirt 41 of the cover 12 has a radially outwardly extending portion 22 locally, which extends with a web 24 and two parallel wings. It has a U-shaped overall length with 25, 26, and the wings 25, 26 are suitable for supporting the spindle 27 by holes through which the spindle passes.

The skirt 41 has an opening 52 therein in alignment with the worm 23, which is partially received in the opening 52.

In addition, the spindle 27 is suitable for supporting a so-called contact component 30 for positioning the set of teeth 19 in the axial contact so that the set of teeth is fully positioned relative to the worm 23; To this end, the contact component 30, on the one hand, is supported by the support wings 33, 34, which, on the other hand, are supported by the spindle 27 passing through the holes of the support wings 33, 34. Includes bends 37, 38 oriented inwards and towards each other and on which the set of teeth 19 axially abuts.

The contact component 30 can be seen better in FIGS. 7-9.

The set of teeth 19 includes a radial extension 53 inwardly beyond the web 31 of the contact component, more specifically the wings 33, 34, and the teeth in both axial directions. 19) extending between the bends 37, 38 defining the fork to secure the set.

The purpose of this arrangement is to avoid the removal of the teeth of the set of teeth 19 relative to the worm, which can pass over the set of teeth 19 because of the large axial vibration, especially when the torsional stress is high, especially when the clutch When combined with a double damping flywheel, it provides compensatory operation without wear.

The contact component 30 also has a radial arm 31 positioned on the face of the engaging rim 21 of the cover 12 oriented towards the outer periphery on the wings 33, 34 and oriented towards the recoil plate. Including; The position of the contact plate 30 is thus fully defined; The same part is thus applied at the axial position of the set of teeth 19 with respect to the worm 23 and acts on the bends 37, 38 upon contact by the end arms of the segment 45.

In order to secure the spindle 27 with respect to the cover 12, the spindle 27 is provided with a cylindrical portion provided with a recessed portion 47 pressed into the wing 26 of the radial extension 22 at one of its ends. It includes a body.

The hole 43 in the other wing 25 does not fully extend out of the skirt 41 of the cover 12 so that it is positioned axially when the spindle 27 is mounted on the cover 12.

The worm 23 and the ratchet wheel 20 are herein a single component; The axial cylindrical bore 56 allows mounting of such a component on the spindle 27; Of course, the worm 23 and the ratchet wheel 20 may be separate components and are arranged such that the worm 23 and the ratchet wheel 20 are rotatably coupled to each other.

The metallic and small thickness elastic member 32 herein is a very long blade of the general form in which the fixing hole 51 is provided in the cover 12 by one of the rivets 48 for fixing the retaining ring 10. It has a blade, the blade extending along the inner surface of the lower portion 42 of the cover 12. As a variant, the blade can extend along the outer surface. The free end of the elastic member 32 is shaped as a control tongue 36 and extends generally parallel to the shaft of the clutch; The end of the control tongue 36 is narrowed so that its width is suitable for the teeth of the ratchet wheel 20; When the resilient member 32 and the ratchet wheel 20 are mounted on the cover 12, the control tongue 36 resiliently cooperates with the foot of the tooth of the ratchet wheel 20.

The radially facing portion of the elastic member 32 and the control tongue 36 are in line with the opening 40 formed in the lower portion 42 of the cover 12; This portion is slightly arcuate in a convex direction towards the opening 40, so that it is at least partially in line with the thickness of the lower portion 42 of the cover 12, thus allowing for savings in axial space requirements.

The elastic member 32 is subjected to smaller bending stresses thanks to the long length; Its mass is distributed over its entire length extending radially and is flexible; Control tongue 36 has a reduced mass and its movement is in a wide range; Good for centrifugal effect.

On both sides of the control tongue 36, so-called transverse arms 49, 50 suitable for entering the contact portion against the radial edge of the opening 40 extend laterally; Accordingly, the edges can be seen in FIG. 10 and act as control contacts and limit the movement of the control tongue 36 toward the lower portion 42 of the cover 12 as described below.

Around the spindle 27 there is a helical compression spring 46 which constitutes elastic compensation means as described below; Here, a spring 46 is located axially between the ratchet wheel 20 and the wings 34 of the contact component 30.

The ratchet wheel 20, the worm 23 and the helical spring 46 are fixed to the cover 12, and the diaphragm 13 moves relative to the cover 12; The diaphragm 13 thus comprises, on its periphery, a radial appendage referred to as the actuating device 29 (FIGS. 1 and 12) in the detachment and recombination operation, which actuating device 29 Extend radially to the outside of the dishwasher portion of the diaphragm 13 to cooperate with the control tongue 36 of the elastic member 32, while towards the lower portion 42 of the cover 12 for this dishwasher portion. Axially offset; As shown in FIG. 12, the foot of the actuating device 29 is narrowed and connected to the dish washer by a round section that limits the stress in this connection area; The elastic member 32 has a resilient lug 39 extending radially beyond the foot of the control tongue 36 by means of the U-shaped cutout; The actuating device 29 (FIG. 10) is arranged axially between the back of the control tongue 36 and the end of the resilient lug 39 which is always resiliently positioned relative to the actuating device 29, this arrangement being the control tongue. To avoid any resilience of (36); This arrangement causes the diaphragm 13 to oscillate and to recombine, which moves the control tongue 36 from right to left with respect to FIG. 1 and in cooperation with the teeth of the ratchet wheel 20. End of the ratchet causes the ratchet wheel 20 to rotate clockwise; The elasticity of the elastic member upon inclination and the inclination of the teeth of the ratchet wheel 20 mean that the control tongue 36 exceeds its teeth within the limits of deflection allowed by the control contacts defined above.

The wear compensation device described operates as follows.

1 schematically shows a coupled clutch, in which the lining 101 of the friction disc 100 is in a new state and gripped between the recoil plate (not shown) and the pressure plate 11. In this position, the control tongue 36 has its end at the foot of the tooth of the ratchet wheel 20.

When the clutch is released, the end of the finger of the diaphragm 13 acts in the direction of the arrow F and moves away from the lower portion 42 of the cover 12; The diaphragm 13 vibrates around the first stop 18 under the action of the elastic gripping force exerted by the retaining ring 10; In its movement, the outer periphery of the diaphragm 13 gradually releases each of the pressure plate 11, its operating device 29 and the control tongue 36; The end of the control tongue 36 follows an inclined ramp constituted by the teeth at the foot that was positioned in the previous step, and the teeth of the ratchet wheel 20 have an end value portion of the control tongue 36 during a new lining detachment movement. Not over; Since this is accomplished by the elastic member 32, its control tongue 36 is in contact with the control contact or cover 12.

When the lining is worn, as is known, the pressure plate 11, which is always dominated by the axial force of the diaphragm 13, is closer to the recoil plate axially fixed to the cover 12; The actuating device 29 of the diaphragm 13 thus drives the control tongue 36 closer to the recoil plate in its movement; The ratchet wheel 20 rotates around its shaft in a clockwise direction; This rotational drive of the ratchet wheel 20 leads the worm 23 to rotate about its shaft; The ramp means 14 are rotatably fixed under the influence of the diaphragm, and the worm 23 engaging the set of teeth 19 is screwed onto the set of teeth 19, as is the case. The direction of the thread of is provided likewise.

In the detachment operation involving the described wear step, the pressure plate 11 is connected to the diaphragm 13 and its lower portion by the lower stop 42 of the cover 12, the pressure plate 11 as well as the second stop region 14. The lining 101 is released by moving away from the lining 101 under the action of a tangential tongue returning towards the lamp means 14 in contact with the pad 15 by the lamp 16. The helical spring 46 actuates the dignity 23 towards the wing 25 of the radial extension 22 and moves away from it in a wear phase, ie from right to left with respect to FIG. 2; The load of the diaphragm 13 is applied to the ramp means 14, and the force that must be overcome so as to be able to rotate this ramp means 14 relative to the pressure plate 11 is the return force of the tangential tongue; If the load of the helical spring 46 is sufficient to overcome this force, the spring 46 is prevented from operating on itself by the pressure of the control tongue 36 and the worm 23 which will drive the set of teeth 19. ) Move; By cooperating with the relatively fixed pad 15 when operating them, the lamp 16 will move the pressure plate 11 away from the lower portion 42 of the cover 12, so that the working of the pressure plate 11 The axial distance between the face and the second stop region 17 of the ramp means 14 is increased and the displacement of the pressure plate 11 begins at least in part due to the wear of the lining 101. Since the load of the helical spring 46 is a function of the amount compressed by the worm 23 during the wear phase, many engagement and disconnection operations may be necessary before the play compensation device properly enters the compensation phase, which is a related component. Is a function of the relative dimensions of.

If wear is sufficient to allow the ratchet wheel 20 to rotate sufficiently so that the control tongue 36, where the return movement is defined by the control contact when the wear is returned, jumps the teeth during engagement operation, the control tongue 36 is a ratchet wheel ( 20 means to rotate and the ramp means 14 not caught by the diaphragm 13 rotates and starts to wear; At the end of the compensation operation the diaphragm 13, the ratchet wheel 20 and the control tongue 36 regain their position occupied in FIG. 1.

Of course, the retaining ring 10 may be replaced by a column having a profiled head that provides a stop opposite the first stop 18.

In a variant, the set of teeth 19 belongs to a component separate from the ramp means. This intermediate component has teeth which, on its inner circumference, enter into a recess made in an axially oriented annular rim having a ramp means past the second stop 17. Thus, the set of teeth 19 is rotatably fixed to the ramp means 14 while being movable relative to the ramp means by a tenon type connection.

FIG. 13 shows a variant of the elastic member, which is a type of elastic member 32 already described, which is generally parallel and outwardly directed to the shaft conveying at the end of the control tongue 136. A cut-out 150 by, for example, the creation of an arm 149 extending in a direction perpendicular to the control tongue 36; Its height is sufficient to come in contact with the upper edge 158 of the opening 40 formed in the lower portion 42 of the cover 12 in the detaching operation.

Here, the operating device 129 is an extension of the dish washer portion of the diaphragm 13 without an axial offset.

In the example shown, the radial extension 53 of the contact component 30 also includes a bend in line with the bends 37, 38, where the bend 137 faces the bend 37. ) Can only be seen.

14-16 illustrate clutches in which helical and ratchet wheels as well as helical springs are also carried by the support.

More precisely, the spindle 27 is supported by a support 62 made of cut and folded sheet metal, which support 62 is a web 64 and two wings 65 suitable for supporting the spindle 27. Is generally U-shaped with; The support 62 is fixed to the cover 12 by its web 64 with rivets 63.

The set of teeth 19 is supported by an annular component radially guided and centered by an axial lug 66 of the cover 12; It is rotatably coupled to the ramp means 14 by a tangential tongue 67.

The elastic member 72, better known from FIGS. 17 and 18, also has a generally elongated shape, and radially along the bottom of the cover 12, with an almost axial end 76 constituting the control tongue. Extended; Here, the diaphragm 13 is mounted with a joint on the cover 12 with a column 73, one of which is resilient by a hole 74 provided at its end opposite the control tongue 76. The member 72 is fixed to the cover 12.

The impression of the cover in line with the fixation of the column 73 makes it possible to fit the thickness of the blades in this impression, thus conventional joint columns for diaphragms are conventionally used.

The actuating device 79 is impressed to reduce its thickness as compared to the thickness of the dish washer portion of the diaphragm 13; The control contact 77 extends radially from the upper edge of the opening 40 of the cover 12; The thickness of the control contact 77 is also reduced when compared with the thickness of the stop of the cover 12; This arrangement saves axial space requirements.

The actuating device 79 comprises a passage 75 through which the control tongue 76 passes by a wing of the V-shaped fold with another wing of the V stop relative to the actuating device, the elastic lateral wing 78 being covered The elastic member 72 is elastically supported by the diaphragm 13 which moves so that it may be placed on the surface of the diaphragm 13 facing the lower part of (12).

According to the present invention, as a friction clutch having a device for compensating the wear of the friction lining, it is possible to reduce the space requirement in both radial and axial directions.

Claims (23)

A recoil plate intended to be rotationally clamped to the drive shaft, at least one friction lining 101 on its outer periphery, a friction disc 100 intended to be rotationally clamped to the driven shaft, a pressure plate 11 and And a cover 12 fixed to the recoil plate, controlled by a separating means, on the one hand and on the other hand by the second stop means 17 and the first stop means 18. A friction clutch for a vehicle of the type comprising an axially actuating engagement means 13 acting between the pressure plates 11, wherein the pressure plate 11 is rotationally fixed to the cover 12, Axially moveable with respect to the cover, under the action of elastic return means for axially returning the pressure plate (11) towards the cover (12); The clutch further comprises a wear compensation device having a ramp means 14, the ramp 16 of the ramp means 14 being arranged in the circumferential direction, the stop means 17 and the pressure plate 11. Axially located between and suitable for cooperating with the counter-lamp means 15; The set of teeth 19 cooperates with the worm 23 arranged tangentially; The ramp means (14) is rotatably fixed to the set of teeth (19); A means 20 for rotationally driving the worm 23 is provided to operate by abrasion of the friction lining (s) 101 when the clutch is engaged, and the ratchet wheel is rotatably fixed to the worm 23. In the friction clutch for automobiles, which is constituted by and controlled by control tongues 36, 136, 76 having elastic members 32, 132, 72, The elastic members 32, 132, and 72 have a form of a very long blade extending radially along one surface of the lower portion 42 of the cover 12, and are directly fixed to the cover 12. doing Friction clutch. The method of claim 1, The free ends of the resilient members 32, 132, 72 are formed as control tongues 36, 136, 76 extending generally parallel to the shaft of the clutch. Friction clutch. The method of claim 2, A portion facing radially outward of the elastic members 32, 132, 72 and the control tongues 36, 136, 76 radially with an opening 40 formed in the lower portion 42 of the cover 12. Characterized by being in a straight line Friction clutch. The method of claim 3, wherein By means of the opening 40, the elastic members 32, 132, 72 may be at least partially in line with the thickness of the lower part 42 of the cover 12 in the axial direction. Friction clutch. The method according to any one of claims 1 to 4, The elastic members 32 and 132 are adapted to cooperate with the cover 12 by means of radially facing outwards. Friction clutch. The method according to any one of claims 3 to 5, The so-called lateral arms 49, 50 extend any side of the control tongues 36, 136, 76 and are suitable for contacting against the radial edge of the opening 40 which constitutes a control contact. doing Friction clutch. The method according to any one of claims 3 to 5, At its end, which is generally parallel to the axis supporting the control tongue 136, the resilient member 132 is created with an arm 149 suitable for contacting the upper edge 158 of the opening 40. Characterized in that it comprises a notch 150 by Friction clutch. The method according to any one of claims 1 to 7, The spindle 27 is characterized by being supported by a support 62 fixed to the cover 1 Friction clutch. The method of claim 8, The support 62 is characterized in that it is generally U-shaped with a web 64 and two wings 65 suitable for supporting the spindle 27. Friction clutch. The method of claim 9, The support 62 is fixed to the cover 12 by its web 64. Friction clutch. The method according to any one of claims 1 to 10, The axially actuated coupling means is characterized in that it consists of a diaphragm 13 Friction clutch. The method of claim 11, The elastic members 32, 132, 72 are fixed to the cover 12 by one of the members 48, 73 for securing the joint means of the diaphragm 13 to the cover 12. By Friction clutch. The method according to claim 11 or 12, The ratchet wheel 20 is characterized in that it is controlled by the diaphragm 13 through the control tongue (36, 136, 76). Friction clutch. The method of claim 13, The ratchet wheel 20 is characterized in that it is controlled by the operating device (29, 129, 79, 269) constituted by radial appendages provided on the outer periphery of the diaphragm (13) Friction clutch. The method of claim 14, The actuating device 269 is characterized in that it is axially offset towards the lower part 42 of the cover 12 with respect to the dish-shaped washer part of the diaphragm 13. Friction clutch. The method of claim 14, The actuating device 79 is characterized in that it comprises a passage 75 through which the control tongue 36 passes. Friction clutch. The method of claim 16, The control tongue 76 has a V-shaped fold, the elastic member 72 includes an elastic lateral wing 78 and is elastically supported by the diaphragm 13 and the diaphragm 13 Characterized in that it is moved along with Friction clutch. The method according to claim 14 or 17, The actuating device 29 is characterized in that it is arranged axially between the back of the control tongue 36 and the end of the elastic lug 39, which is the cutout of the elastic member 32. Friction clutch. The method according to any one of claims 1 to 18, The lamp means 14 is characterized in that it consists of a ring which is inclined on the one hand and distributed in the circumferential direction and on the other hand the ring having the second stop means 17 in the axial direction. Friction clutch. The method of claim 19, The lamp 16 and the second stop means 17 are characterized in that they are almost straight in a radial direction with each other. Friction clutch. The method according to any one of claims 1 to 20, The counter-lamp means 15 are characterized in that they consist of a pad intended to cooperate with the lamp 16 of the lamp means 14. Friction clutch. The method according to any one of claims 1 to 21, The worm 23 is characterized in that it is mounted to move along its axis by the action of so-called elastic compensation means 46. Friction clutch. The method according to any one of claims 1 to 20, The cover 12 is characterized in that it comprises an annular skirt 41 inclined to the axis with the opening 52 in line with the worm 23 partially received in the opening 52. Friction clutch.