KR20030001349A - A clutch release bearing for a friction clutch, and a friction clutch having such a release bearing - Google Patents

Abstract

PURPOSE: A clutch release bearing and a friction clutch are provided to improve the reliability and lengthen the life span of a clutch release bearing receiving axial traction in the clutch released by pulling and arranged to transmit power. CONSTITUTION: A release bearing comprises a bearing(21) having two rings(22,23) and balls(24). The operating ring is engaged with an interface part(31), and activated by an operating part with the force in the bearing axial direction. The force is transmitted to the other ring of the bearing by the ball, and the ring is interlocked with a clutch release diaphragm(7). The bearing is resiliently mounted and arranged axially and radially to the interface part. A spring washer(36) is located axially between a trust support face(38) of the operating ring and a transverse support face(37) connected to the interface part. The operating ring transverse support face is engaged with the washer in the support zone located radially at a distance from the washer centering diameter.

Description

CLUTCH RELEASE BEARING FOR A FRICTION CLUTCH, AND A FRICTION CLUTCH HAVING SUCH A RELEASE BEARING}

The present invention relates to general control of a friction clutch, and more particularly to a clutch release bearing for achieving said control.

The friction clutch generally includes a recoil plate, which can be of two parts to form a damped flywheel or an elastic flywheel, which is typically a drive shaft, such as a crankshaft of an internal combustion engine of a motor vehicle, a recoil plate. Supports on its outer periphery, which is a cover plate for the attachment of at least one pressure plate.

The pressure plate is engaged with the cover plate and the recoil plate to rotate together, and at the same time axially displaceable under the deflection action of the axially acting elastic clutch engine means, which are alternately controlled by the clutch release means. The clutch engagement means may consist of one or two Belleville rings or spiral springs which are mounted in series or in parallel and then subordinate to the operation of the clutch release lever which constitutes the clutch release means. Generally, the clutch engagement means and the release clutch means consist of a common member, for example a metal diaphragm supporting on a cover plate.

The friction disc or clutch friction wheel which supports the friction liner at its outer circumference and which is rotatably coupled with a shaft which is typically a driven shaft, such as the input shaft of the gearbox of the vehicle, is the clutch engaged between the pressure plate and the recoil plate. When interposed so that they are held between them. The clutch engagement means controls the axial displacement of the pressure plate when actuated by the clutch release bearing via the clutch release means.

The friction clutch when the clutch release bearing is pulled in the approaching direction to the pressure plate and the cover plate to release the clutch is called a pull to release type. When the clutch release bearing is pressed in the direction of moving the pressure plate further away from the cover plate to release the clutch, that is, when the clutch is pushed, the clutch is called a push to release type.

Clutch release bearings typically include rolling bearings, such as roller bearings, and include inner and outer rings with rolling elements, such as between balls or rollers. One ring is arranged so that the clutch has a means for engaging such a ring with the clutch release means (e.g. diaphragm) when the clutch is of the pull-off type, and the other ring of the bearing is axially oriented on the mutual contact member. It is attached to the mutual contact member, which is adjusted to be operated by suitable actuating means for applying traction force.

Ball bearings often have sealing means for protecting the ball and its rolling trajectory. Such seals can be light and consist, for example, of simple chicanes that only provide partial protection from dust or high pressure protection against fluids. Such a seal may be a ring seal.

In this regard, the invention thus relates to a clutch release bearing for actuating a friction clutch, comprising a rolling bearing having two rings and a rolling element, one ring called the steering ring being adjusted to actuate by the steering means. Interlocked with the mutual contact means, the steering means being adapted to exert a force in the axial direction of the rolling bearing on the mutual contact member, the force being transmitted to the other ring of the bearing via the rolling element, the actuating ring or the actuating ring The other ring, referred to as this, interlocks with the clutch release means of the clutch, the rolling bearing is elastically mounted with axial and radial spacing with the mutual contact member, and the clutch release bearing is auto-centring type. ), The spring washer is a transverse contact connected to the transverse thrust plane of the steering ring of the rolling bearing and the mutual contact member Type of disposed axially between surfaces, the present invention relates to the clutch release bearing.

This type of clutch release bearing is disclosed by way of example in the specification of French Patent Application No. 99 16795, filed December 30, 1999, for example. In this arrangement, the steering ring of the bearing cooperates with the spring washer in the region of the spring washer adjacent its outer periphery. This arrangement has the risk of being loaded under load to form a conical shape, which can lead to blockage of the washer and / or damage to the seal adjacent to the washer.

The object of the present invention is to overcome this disadvantage.

According to a first aspect of the invention, a clutch release bearing for operating a friction clutch, comprising a rolling bearing having two rings and a rolling element, wherein one ring called the steering ring is operated by the steering means. Interlocked with adjustable mutual contact means, the steering means being adapted to exert a force in the axial direction of the rolling bearing on the mutual contact member, the force being transmitted to the other ring of the bearing via the rolling element, The other ring, called the actuation ring, cooperates with the clutch release means of the clutch, and the rolling bearing is elastically mounted with the mutual contact member at axial and radial intervals, and the clutch release bearing is self-centering, The spring washer is axially located between the transverse thrust surface of the steering ring of the rolling bearing and the transverse contact surface connected to the mutual contact member. In the clutch release bearing of the type arranged in this way, the transverse thrust surface of the steering ring of the rolling bearing is interlocked with the spring washer in an attachment zone radially located at the outer and inner center diameter distances of the spring washer. do.

Preferably, the transverse thrust plane of the steering ring of the rolling bearing is deflected axially outward with respect to the seal disposed transversely on the same side as the transverse thrust plane between the two rings of the rolling bearing.

Preferably, the transverse thrust plane of the steering ring of the rolling bearing has a radial dimension smaller than its own radial dimension.

In the first embodiment of the present invention, the clutch release bearing is adjusted to interlock with the friction clutch of the release type, and the steering ring of the bearing is the outer ring of the bearing.

Preferably, the outer diameter of the spring washer is larger than the outer diameter of the outer ring of the rolling bearing.

Preferably, the spring washer extends radially in a groove formed in the inner periphery of the skirt of the mutual contact member.

In a second embodiment of the release bearing, the clutch is also pulled off and the steering ring of the bearing is the inner ring of the bearing.

Preferably, the inner diameter of the spring washer is smaller than the inner diameter of the inner ring of the rolling bearing.

Preferably, the spring washer extends radially in a groove formed in the outer periphery of the central portion in the form of a skirt of the inner member.

In a third embodiment of the separating member according to the invention, the friction clutch is depressurized and the steering ring of the bearing is the outer ring of the bearing.

Preferably, the outer diameter of the spring washer is larger than the outer diameter of the outer ring of the rolling bearing.

Preferably, the spring washer extends radially in the groove formed in the inner circumference of the skirt of the mutual contact member.

In particular, in order to improve the reliability and the length of the useful life of the clutch release bearing, which is a pulled-out type and arranged for transmitting a large force, for example an especially severe axial traction in an industrial vehicle clutch, the bearing is inclined contact. It is possible to provide a clutch release bearing of this type in the form. The rolling element of the bearing transmits, for example, the axial traction on the outer ring via the mutual contact member of the release bearing to the inner ring and is disclosed in the specification of French patent application 99 16795 filed December 30, 1999. This results in an axial displacement of the outer ring relative to the inner ring when axial forces are applied on the outer ring in opposite directions.

It will be appreciated that the inclined contact rolling bearings used can support axial traction better than simple radial contact rolling bearings.

According to a second aspect of the invention, the friction clutch comprises a clutch release bearing according to the first aspect of the invention.

The clutch release or release means of the clutch consists of or is part of a diaphragm.

Other features and advantages of the invention will be apparent from the following detailed description of specific preferred embodiments of the invention, which is to be made by way of example only and with reference to the accompanying drawings.

1 is an axial sectional view of a pull-out friction clutch with a conventional clutch release bearing;

2 is an end view showing the clutch release bearing according to the present invention, applicable to the clutch shown in FIG.

3 is a view similar to FIG. 2 showing a variant embodiment of the invention,

4 is a view similar to FIGS. 2 and 3 showing the invention applied to a release bearing for a release clutch;

FIG. 5 is a view similar to FIG. 4 but showing a modified embodiment of the present invention. FIG.

Explanation of symbols for main parts of the drawings

3: cover plate 4: friction disc

5: friction liner 6: pressure plate

7: diaphragm 12: driven shaft

14 spline part 16 ball bearing

19: display stud 20: clutch release bearing

21, 121, 221: rolling bearing (ball bearing) 22, 122, 222: inner ring

23, 123, 223: outer ring 24: ball

25 coupling portion 26 thrust ring

27, 61: circular clip 29: elastic ring

31: control sleeve (member) 34: collar portion

38: transverse thrust plane 40, 166: skirt

44, 163: Lip 52: Housing

55: guide sleeve 56: clutch casing

60: shoulder 62: spring washer

63, 165: home 64: center

160: closing plate 162: dish ring

1 is a view of the entire assembly of a conventional friction clutch mechanism. This mechanism typically comprises a recoil plate 1, which in this embodiment is an engine flywheel fixed to the nose of a drive shaft 2, such as a crank shaft of an internal combustion engine. Cover plates 3, generally dish- or cloche-shaped, are attached on the periphery of the recoil plate 1 to be rotatably coupled to one another.

It is formed by a recoil space 1 and a cover plate 3 and is a component in an internal space in which the common rotational axis 13 is fixed to each other in a stacking manner coinciding with the axis of the drive shaft 2 as a component, and friction on its periphery. A friction disk 4 having a liner 5, a pressure plate 6, and an elastic force exerted on the pressure plate 6 toward the reaction plate 1, the reaction plate 1 and the pressure plate 6. There is a diaphragm 7 with a diaphragm bearing on the cover plate 3 for holding the liner 5 of the friction disk 4 in between.

The friction disk 4 is rotatably fixed to the driven shaft 12. The driven shaft is, for example, an input shaft of the gearbox and has the same shaft 13 as the reaction plate 1. More specifically, the friction disk 4 has a central hub 11 which is splined inwardly and mounted to slide on the complementary spline 14 of the drive shaft 12 so that the hub is driven shaft. Rotated with 12. The drive shaft 12 also passes through the spline 14 and has a nose 15 which is rotationally mounted centrally on the recoil plate 1 by means of a ball bearing 16.

The pressure plate 6 is elastically coupled to the cover plate 3 by tangential tongues 18 which form a return means for biasing the pressure plate 6 in the direction of the cover plate 3. do. In addition, the pressure plate 6 can be rotatably coupled with the cover plate 3 and thus displaced axially with respect to the cover plate.

The diaphragm 7 comprises a periphery 8 in the form of a dish ring, the outer periphery of which is coupled on the cover plate 3 via an interposed thrust ring 10 constituting the pivot. The inner circumference of the ring 10 is engaged on the circular contact ring 17 of the pressure plate 6. Thus, axial thrust is applied on the pressure plate 6 towards the recoil plate 1 to engage the drive shaft 2 and the driven shaft 12 when the clutch is engaged therein. The diaphragm 7 comprises a number of radial fingers 9 extending the inner circumference of the dish ring 8. In addition, the diaphragm 7 is rotatably attached to the pressure plate 6 by the display stud 19.

The clutch mechanism described so far is well known and, as is also well known, the radial fingers 9 of the diaphragm 7, in order to separate the liner 5 from the friction disk 4 to engage the clutch. It is sufficient to exert a traction in the direction of the arrow T on the free end of. A clutch mechanism of this type in which a clutch release is achieved by the action of traction on the radial finger 9 and diaphragm 7 is commonly referred to as a pull release type.

Traction force in the direction of arrow T is provided by the clutch release bearing 20. The clutch release bearing 20 comprises a rolling bearing 21 with an inclined contact. The bearing 21 has a row of inner rings 22, outer rings 23 and rolling elements 24 between these two rings. In this embodiment the rolling element 24 is a ball. Since the bearing 21 has an inclined contact, the ball 24 accurately provides the axial force exerted on the outer ring 23 to the inner ring 22 in the direction of the arrow T only by the traction force, but the outer ring ( If axial thrust P is applied to plates 1 and 6 on 23, no axial force is transmitted to inner ring 22.

Thus, the ball 24 enables the outer ring 23 to be axially displaced relative to the inner ring 22 when axial thrust P is applied to the outer ring 23.

In order to contact the inner ring 22 to the free end of the radial finger 9 of the diaphragm 7, the ring 22 is on the free end of the radial finger 9 of the diaphragm by a thrust ring 26. It is extended by the fitted coupling part. The thrust ring 26 is held axially on the coupling portion 25 by an annular coupling ring or circular clip 27 and is received in a groove 28 formed outside of the outer end of the coupling portion 25. . Ring 27 provides axial attachment to thrust ring 26.

In order to prevent all axial spacing arising in the connection between the junction 25 and the radial arm 9 of the diaphragm, the elastic ring 29, which is a dish ring here, is provided in the coupling part 25 of the inner ring 22. The free end of the radial diaphragm arm 9 in the resilient engagement portion is held against the thrust ring 26 by supporting it through its inner peripheral portion against the shoulder portion 30.

The outer ring 23 of the bearing 21 is in contact with a steering sleeve 31 which operates to interact with the actuation means (not shown). These actuating means may be mechanically shaped like a clutch release fork or hydraulically shaped like an actuating piston of a hydraulic actuator which is a receiver within a hydraulic control circuit. In addition, the actuation means may be electrically operated. The steering sleeve 31 is mounted to slide on the tubular guide sleeve 55 on the shaft 13, through which the driven shaft 12 passes. The guide sleeve 55 is fixed to the clutch casing 56. The sleeve 31 also has means (not shown) for interlocking with the above-described actuating means such that the actuating means exert its axial traction on the sleeve 31 in the direction of the arrow T.

In this case, the outer ring 23 of the bearing 21 is attached to the steering sleeve 31 by the collar piece 32. These collar pieces are metal pressed in the form of rings or sleeves, both ends of which are axially interlocked with the outer ring 23 of the bearing in a single direction and with the collar 34 of the inner sleeve 31 in the other direction. It is modified. More specifically, the collar piece 32 has a lug bent rearwardly about the collar 25 of the steering sleeve 31 on the one hand, while axially interlocking with the outer ring 23 of the bearing on the other side. A radial annular flange 35. The spring washer 36 is interposed between the transverse edge of the outer ring 23 facing the steering sleeve 31 and the transverse end thrust face 37 of the steering sleeve 31. Thereby, the ball bearing 21 is elastically mounted in the collar piece 32 with axial spacing or more precisely with axial position and radial spacing, so that the clutch release bearing 20 is automatically centered. to be.

Reference is now made to FIG. 2 which shows a variant provided by the invention for the clutch release bearing 20. As in FIG. 1, the steering ring is the outer ring 23 of the bearing 21, and the inner ring 22 is an operating ring that supports the coupling portion 25.

In this case, the transverse thrust face 38 of the steering ring 23 cooperates with the spring washer 36 in an attachment zone located radially at a distance from the outer diameter of the spring washer 36.

It is arranged between two rings 22, 23 of the bearing and one axial side of the ball 24. The transverse thrust face 38 of the steering ring 23 of the bearing is deflected axially outward with respect to the seal fitted on the same side as the thrust face 38, ie the seal 41. This deflection is achieved by machining the outer ring 23 of the bearing at the end of the bearing.

It should also be noted that the radial dimension of the transverse thrust face 38 of the steering ring or outer ring 23 of the bearing is smaller than the minimum radial dimension of the outer ring 23 itself. In addition, the outer diameter of the spring washer 36 is larger than the outer diameter of the outer bearing ring 23. A spring washer 36, which is a release washer, is located radially in a groove 39 formed on the inner circumference of the skirt 40 of the mutual contact sleeve 31. The release washer 36 may be elastically contacted on the base of the groove 39.

In this embodiment, the radial collar piece 32, which plays no role in centering the steering ring 23 between the lug 33 and the radially annular flange 35 of the collar piece 32, has a curved portion. It is press-molded so that a large diameter, that is, a diameter having an inner diameter larger than the thickness of the metal plate forming such a component, is changed. The sharp corners are limited, the clutch release force is increased or the same, and the thickness of the metal plate of the collar piece can be reduced.

Reference is now made to FIG. 3 showing the clutch release bearing 120. This bearing 120 includes a hollow annular housing 52 with a steering sleeve 31 arranged to be operated by a suitable control member such as a ball bearing 121 and a clutch release fork. The housing 52 supports the coupling element 25 and is fixed relative to the rotary outer ring 123 of the ball bearing 121. The steering sleeve 31 is adjusted to slide along the guide sleeve 55.

In this embodiment the inner ring 122 of the ball bearing 121 is axially attached to the steering sleeve 31. This ensures that an axial coupling between the ball bearing 121 and the steering sleeve 31 runs from the connection 25 to the steering sleeve 31.

In this embodiment, the housing 52 is metal pressed and is annular in shape. The housing 52 includes an axially oriented skirt 54 surrounding the outer ring 123 of the ball bearing 121 without any spacing. The skirt 54 extends at one end by an upset edge 57 extending radially towards the axis of the assembly. The upset edge 57 extends radially inwardly by a junction 58 which has a curved shape and which is inclined in the radial direction. The junction 58 is coupled to a generally grooved cylindrical portion that constitutes the coupling portion 25. The other end of the skirt 54 is initially straight and bends backwards radially inward to capture the outer ring 123 of the ball bearing 121. This rear curved end attaches a clutch release fork (not shown) during snap-fitting.

Thus, the outer ring 123 is secured to the casing 52 by a welded joint, which is captured by the upset edge 57, and the skirt 54 and its other end are also curved radially inward behind it. .

Instead of bending the end of the skirt 54 behind, it is of course also possible to axially position the outer ring 123 of the bearing 121 with a circular clip.

In this embodiment, the casing is a steering sleeve 31, supporting at its inner circumference the sliding sleeve 43 of non-friction material, which non-friction material is for providing good sliding movement along the guide sleeve 55. It is a plastic material, for example. This sliding sleeve 43 is fixed to the sleeve 31 by a forced fit, which sleeve 43 engages the lip 44 which engages in a generally trapezoidal groove 45 formed in the inner bore of the sleeve 31. Equipped.

At its outer circumference the sleeve 31 has two shoulder portions 59, 60 axially biased from each other to mount the inner ring 122 of the bearing 121. More specifically, the sleeve 31 is varied in diameter to define the shoulder portion 60. This change in diameter is formed by a groove in the area of its free end formed with the groove for mounting the circular clip 61.

Thus, a groove is formed between the shoulder portion 60 and the circular clip 61 which also forms the shoulder portion 60 to which the inner ring 122 of the ball bearing 21 is mounted. The axially acting elastic means 62, which in this embodiment is a corrugated ring, draws on the shoulder portion 60 and the inner ring of the ball bearing to deflect another portion of the inner ring 122 into contact with the circular clip 61. Support one of the parts of 122).

The inner ring 122 of the ball bearing is mounted at intervals relative to the sleeve 31 and can be radially displaced relative to the sleeve 31 under the control of the dish ring 62 with the housing 52.

Thus, the clutch release bearing is auto centered, and the bearing 121 is axially attached to the sleeve 31. In the release operation of the clutch, the traction force is transmitted to the circular clip 61 and the bearing 121 and from the bearing 121 to the coupling portion 125 and the thrust ring 26.

Thus, in this embodiment, the inner ring 122 of the ball bearing is a steering ring. The inner diameter of the corrugated washer 62 is smaller than the inner diameter of the inner sleeve 122.

In the configuration shown in FIG. 3, the spring washer 62 is radially engaged in a groove 63 formed in the outer periphery of the central portion 64 of the mutual contact member 31. This portion 64 has the shape of a sleeve.

It is of course also possible for the present invention to be applied to a clutch release bearing which is adjusted to function to actuate a pressure release friction clutch. Reference is now made to the embodiment of the release bearing 220 shown in FIG. 4. In this embodiment, the steering ring of the ball bearing 221 is the outer ring 223, which bearing has an inclined contact. The inner ring 222 of the bearing cooperates directly with the finger of the diaphragm 7.

A dish ring 162 that cooperates with the end of the outer ring 223 of the bearing is located in front of the mutual contact member or steering sleeve 31, ie on the same side of the finger of the diaphragm 7. The dish ring 162 supports the mutual contact member 31 through the closing plate 160 and supports the front of the closing plate. In this embodiment the outer circumference of the closing plate 160 is welded onto the outer circumferential shoulder 161 formed at the end of the outer skirt 166 of the member 31.

The outer diameter of the spring washer 162 is larger than the outer diameter of the outer ring 223 of the bearing 122 and extends radially in the groove 165 formed on the inner circumference of the outer skirt 166 of the member 31.

Finally, referring to FIG. 5, the closing plate 160 located at the end of the skirt 166 of the member 31 is held axially relative to the member 31 by the member of the lip 163. It is formed by upset the end of 166 and forms one side of the groove 165.

According to the present invention, the effect of improving the reliability and the length of the useful life of the clutch release bearing, especially in the case of a pull-out type and arranged for transmitting a large force, for example, a particularly severe axial traction, is applied to a clutch for an industrial vehicle. have.

Claims (15)

A clutch release bearing for operating a friction clutch, comprising a rolling bearing (21, 121, 221) having two rings (22, 122, 222; 23, 123, 223) and a rolling element (24), so-called One of the rings 23, 122, 223, called a steering ring, cooperates with an interconnecting member 31 which is adjusted to be actuated by the steering means, the steering means bearing the rolling bearing on the mutual contact member 31. Is applied to the other ring 22, 123, 223 of the bearing through the rolling element 24, the other ring being called the actuating ring and the clutch of the clutch. Interlocked with clutch release means (7), the rolling bearing is elastically mounted at intervals in the axial and radial directions with respect to the mutual contact member (31), the clutch release bearing is self-centering, spring Washers 36, 62, 162 are The clutch, disposed axially between the transverse thrust surface 38 of the steering ring 23, 122, 223 of the rolling bearing and the transverse attachment surface 37, 60, 160 connected to the mutual contact member 31. In the release bearing, The transverse thrust face 38 of the steering ring 23, 122, 223 of the rolling bearing is in an attachment zone radially located at a distance from the outer or inner center diameter of the spring washers 36, 62, 162. In the spring washer (36, 60, 160) characterized in that the interlocking Clutch release bearing. The method of claim 1, The transverse thrust surface 38 of the steering ring 23, 122, 223 of the rolling bearing is between the two rings of the rolling bearing 21, 121, 221 on the same side as the transverse thrust surface 38. Characterized in that it is deflected axially outward with respect to the seal 41 arranged in the transverse direction. Clutch release bearing. The method according to claim 1 or 2, The transverse thrust plane 38 of the steering ring 23, 122, 223 of the rolling bearing is characterized in that the radial dimension is smaller than the minimum radial dimension of the steering ring itself. Clutch release bearing. The method according to any one of claims 1 to 3, For use with a pull-out friction clutch, the steering ring of the rolling bearing is an outer ring 23 of the bearing 21. Clutch release bearing. The method of claim 4, wherein The outer diameter of the spring washer 36 is larger than the outer diameter of the outer ring 23 of the rolling bearing 21. Clutch release bearing. The method of claim 5, The spring washer 36 extends radially in a groove 39 formed in the inner circumference of the skirt 40 of the mutual contact member 31. Clutch release bearing. The method according to any one of claims 1 to 3, For use with a friction clutch of the pull-out type, the steering ring of the rolling bearing is the inner ring 122 of the bearing 121. Clutch release bearing. The method of claim 7, wherein The inner diameter of the spring washer 62 is characterized in that less than the inner diameter of the inner ring 122 of the rolling bearing 121 Clutch release bearing. The method of claim 8, The spring washer (62) is characterized in that it extends radially in the form of a skirt in the groove (63) formed in the outer peripheral portion of the central portion (64) of the mutual contact member (31). Clutch release bearing. The method according to any one of claims 1 to 3, For use with a depressurized friction clutch, the steering ring of the rolling bearing is the outer ring 223 of the bearing 221. Clutch release bearing. The method of claim 10, The outer diameter of the spring washer 162 is larger than the outer diameter of the outer ring 223 of the rolling bearing 221 Clutch release bearing. The method of claim 11, The spring washer 162 extends radially in a groove 165 formed in the inner circumference of the skirt 166 of the mutual contact member 31. Clutch release bearing. The method according to any one of claims 1 to 12, The rolling bearings (21, 121, 221) is characterized in that the form having an inclined contact portion Clutch release bearing. In the friction clutch, Claim 1 to 12 characterized in that it comprises a clutch release bearing (20, 120, 220) Friction clutch. The method of claim 14, The clutch disengaging means is formed by the diaphragm 7 of the clutch. Friction clutch.