KR100345426B1 - Liner Support Disk for Clutch Friction Wheel - Google Patents

Abstract

The present invention relates to a liner support disk comprising a tripod shaped blade 572, each liner support disk having a central support region 221A and two outer circumferential support regions 522B. A tangential bent portion 380 connects the central region 221A and the central regions 161 and 162 of the disk, while the rectangular bent portion connects the central region 221A and the outer peripheral region 522B. Connect. A friction liner is adhesively attached on the central region 221A. The present invention can be applied to automobiles.

Description

Liner support disc for clutch friction wheel

The present invention relates, in particular, to a liner support disk included in an automotive clutch friction wheel, comprising a central portion and a peripheral portion divided into radial blades, the blades receiving two friction liners. Two friction liners may be of a split type and extend on both sides of the outer circumference, each said blade being coupled to said central portion via a tangential bent portion, wherein at least one of the friction liners A liner support disc of the type comprising at least one support area which is generally parallel with the middle plane of the central part for contacting and fixing it.

Filed July 15, 1993 to manufacture a new standard liner support disk that can rotate at increased speed while reducing embedding and juddering effects and employing a cone shape. European Patent Application No. 0 579 554 discloses a liner support disk comprising a triangular blade.

More specifically, in order to form a triangular blade in this document, at least some of the blades, called triangular blades, have a central support area for contacting and securing one of the friction liners, and both sides of the central support area. It has two outer circumferential support areas thereon for contacting the other of the friction liners.

The central support region decreases in width toward the outer circumference of the liner support disk and is axially offset with respect to the center and with respect to both outer circumferential support regions.

A central support region is first coupled to the central portion of the liner support disk via a tangential bend at right angles to the radial symmetry axis of the triangular blade, and then through the circumferential bent portion oblique to the radial symmetry axis of the triangular blade. Coupled to the area.

Because of this structure, the foot portions of the blades are quite large and rigid because they can increase the support surface, increase the number of blades, and expand the central support area with a fairly wide circumferential width.

In this way, when the liner is continuous, it can have a contact surface larger than 25% of the total surface area of the back of the liner and can reduce the distance between the two central support areas.

As a result, the embedding effect by embedding the friction liner inside the pits between the two mating surfaces is reduced especially when using an organic type friction liner.

The liner support disk can rotate at increased rotational speed by further resisting the effect of centrifugal forces.

Abnormal oscillation effects (which occur in propulsion trains leading from the engine to the road wheel) that can occur as much as in high-speed torque when shifting gears or driving down hills or even at low torque in garages. Caused by vibrations of the

Such a liner support disk can reduce the wear of the friction liner and can use a conical clutch pressure plate because of the blade's structure.

It is an object of the present invention to further utilize these triangular blades.

According to the invention, the friction liner is attached directly on the central support region associated with it by adhesion.

Because of this structure, the inertia of the liner support disk can be further reduced, and the liner support disk is rotatable at a much higher rotational speed.

In this regard, the friction liner only has an effective thickness, and no excess thickness as in the case of riveting is necessary.

This is possible due to the central support area, which provides a large engagement surface area for the friction liner and can provide a substantial length of tangential bends.

In this way, the friction liner is firmly fixed on the central support area, and this fixing is very firm.

It is also possible to have the additional advantage of adhesive adhesion.

In this connection, according to the disk with the triangular blade, good axial gradual operation (gradual engagement of the friction liner between the pressure plate and the recoil plate of the clutch) is achieved during engagement of the clutch.

Due to the bends providing the axial offset, good stability of the blades and good parallelism of the friction liner are achieved. In addition, the foot of the blade is very robust, especially because of the considerable length of the tangential bend.

Typically, this progressive operation is accomplished in another way. In this regard, as disclosed in US Pat. No. 5,076,409, the friction liner is adhesively fixed on two flat disks, and a gradual operation is achieved by protrusions of elastic material interposed between the two disks.

In more detail, at least some of the protrusions join the two disks together.

In British Patent Publication No. 2 191 831, this gradual operation is achieved by a single metallic disk, the outer circumference of the single metallic disk being provided with two sets of radial lugs axially offset from each other.

The friction liner with a small engagement surface is attached onto the radial lug by a material of elastic material.

In the two solutions described above, the liner support disk has a minimum thickness and the inertia is reduced.

Nevertheless, it is necessary to use protrusions of elastic material. To avoid this, according to one feature of the invention, the liner support disk comprises two support disks which are rear contact mounted, at least one of the support disks having a triangular blade, the central support of which is supported. An apparatus is proposed in which one of the friction liners is adhesively fixed on the area and the other friction liner is adhesively fixed on the other disk.

Such a device makes it possible to reduce the inertia of the liner support disk and to minimize the thickness. Thus, the liner support disk can rotate at a very high rotational speed and also provide good support to the friction liner and impart stable axial gradual motion.

In addition, for the delivery of a given torque, these disks have a thickness thinner than that of the disk disclosed in the above-mentioned British Patent No. 2 191 831, which allows for a gradual operation.

Compared to the device disclosed in the above-mentioned US Pat. No. 5,076,409, the disc does not need to have bends in its interlocking region.

Preferably, the two liner support disks described above comprise a triangular blade with back contact mounting and an engagement interposed between the two support disks to impart a axial motion in a single direction to limit the spacing between the two support disks. Means are installed.

Said engagement means comprises, for example, a hook for limiting the gap between the two support disks.

These lugs can be arranged radially inward of the bend in the central support area, the outer support area or the support disc, for example in the tangential bend.

By this arrangement, it is possible to form a subassembly consisting of two support disks with a friction liner.

As a result, these two discs are fitted, for example, on the guide rings of the clutch friction wheel.

The hook can provide a bayonet type of fit.

In addition, the coupling means limits the separation between the two discs due to the thermal effect diffused in the clutch.

As is known, the friction liner as well as the pressure plate and the recoil plate in the clutch may reach quite high temperatures, especially during mountain driving. This causes thermal deformation in the liner support disk.

Such thermal deformation will be limited by the coupling means in a way that reduces wear of the friction liner.

Hereinafter, the present invention will be described with reference to the accompanying drawings.

1 is an axial sectional view of a liner support disk according to the invention.

2 is a cross-sectional view taken along the line 2-2 of FIG.

3 is a cross-sectional view taken along the line 3-3 of FIG.

4 is a cross-sectional view taken along line 4-4 of FIG.

5 and 6 are views similar to those of FIG. 1, showing cross-sectional views of other embodiments.

7 is a view similar to that of FIG. 2, with a partial cross-sectional view of another embodiment.

FIG. 1 shows a liner support disk having a triangular blade of the same type as the 20th degree of European Patent No. 0 579 554, for simplicity which will use the same reference numerals for elements common to the invention and the patent. .

The liner support disk is configured as a clutch friction disk for automobiles.

The liner support disk includes a central portion and an outer periphery divided into radial blades 572 for receiving friction liners 131 and 132, each blade coupled to the central portion via a tangential bend 380. And at least one central support region 221A generally contacting at least one of the friction liners and substantially parallel to the middle plane of the central portion to secure the friction liner.

To form a triangular blade, the blade 572 is in contact with at least one of the friction liners 131 and 132 and has a central support area 221A for securing the friction liner and the other of the friction liners. It has two outer circumferential support regions 522B on both sides of the central support region 221A for contact.

The central support region 221A decreases in width toward the outer peripheral portion of the liner support disk and is axially offset with respect to the central portion and the two outer peripheral support regions 522B.

The central support area 221A is first coupled to the central portion of the liner support disk via a tangential bend 380 perpendicular to the radial symmetry axis of the triangular blade, and then to the radial symmetry axis of the triangular blade. The outer circumferential bent portion 222A is coupled to the outer circumferential support region.

This bent portion 222A converges toward the outer circumferential portion of the blade. As a result, the outer circumferential support region 522B extends radially beyond the tangential bend 380.

Thus, the central support region 221A is very wide in the circumferential direction, and the tangential bend 380 is also considerably wider in the circumferential direction, so that the tangential bend of the blade 572 is very solid.

In this embodiment, the triangular blade 572 is integrated with the central portion of the disk shape. The blades 572 are alternately arranged circumferentially with a series of radial tongues 471 in the plane of the central portion of the liner support disk. This tongue 471 is integrated with the disk-shaped center part.

A portion of the outer circumferential support region 522B extends radially outwardly of the tongue 471, which has a rounded distal end partially surrounded by the outer circumferential support region 522B and is in the form of a bird wing. The central support area 221A has two lugs on its inner circumference that abut the tangential bend 380. As a result, the engagement surface of the central support area 221A is increased while the tangential bend 380 becomes very long, thereby improving the adhesion of the associated friction liner and the firmness of the blade 572.

It may be advantageous to take this structure in order to form the opening 500 in the central support region 221A by the method described below.

Due to this structure, the outer circumferential support area 522B has a firm mating surface, and the central support area 221A is the center of FIGS. 6, 14, 15 and 16 of the aforementioned European Patent No. 0 579 554. It is enlarged compared to the support area.

Of course, the liner support disk may have a shape similar to the liner support disks of FIGS. 6, 14, 15 and 16 of the aforementioned European patent.

According to the invention, the friction liner is adhesively fixed directly onto its associated central support area 221A.

In this way, the liner support disk is reduced inertia and achieves good gradual operation.

In this embodiment, the liner support disk comprises two supports (support disks) 161, 162 in a back contact relationship. The friction liners 131 and 132 are secured with an adhesive on each central support area of the support (support disk) in the manner described below. These supports (supporting discs) are arranged to be fixed to the guide ring 1 of the torsion damper by spacer bars 8 which join together two guide rings 1, 2 which are part of the torsion damper.

To this end, the spacer bar extends through a hole in the damper plate 4 of the damper.

In this embodiment, the supports (support disks) 161, 162 are elastically coupled to a hub, not shown, which hub is rotatable with the input shaft of the gearbox. Splines are formed inward for mounting on the input shaft.

The friction liners 131 and 132 are in the form of continuous circles in this embodiment and are reinforced with "KEVELAR" glass fibers, for example of an organic type such as in French Patent Publication No. 2 094 693.

The friction liners 131 and 132 are arranged to engage between the pressure plate of the clutch and the recoil plate (not shown), which are mounted on the crankshaft of the internal combustion engine to rotate it in a known manner.

Typically, circumferentially actuated resilient means (not shown) are mounted in the windows formed in opposite directions to the guide rings 1, 2 and the damper plates 4 in contact with the guide rings 1, 2.

In one variant, the supports (support discs) 161, 162 may be fixed to a damper plate secured to the hub.

For further details, reference is made, for example, to the above-mentioned European figures, in particular, FIGS. 2 to 4, 22 and 28 of the heading 0 579 554.

In this embodiment, the supports (support disks) 161 and 162 are identical and mounted in back contact with their tongues 471 in contact with each other, while the triangular blades 572 of one blade are mounted. Outer support area 522B is in contact with the outer support area of another blade.

The central support regions 221A are opposed to each other.

In this embodiment, the outer circumferential support area 522B is located in the plane of the support (support disk) 161, 162 to realize good stability in the friction liner 131, 132.

To form a subassembly consisting of supports (support disks) 161, 162 and friction liners 131, 132, a single axial direction for limiting the spacing between two supports (support disks) 161, 162. Directional actuation coupling means are provided.

In FIGS. 1 to 3 this coupling means is supported by one of the supports (support disks) 161, 162 and at least one hook arranged in contact with an associated contact surface supported by the other support (support disk). It includes.

The hook is formed by the central support region 221A, the outer circumferential support region 522B or the central portion of the supports (support disks) 161, 162, preferably near the tangential bend 380 and in the radial direction of the bend. It is supported inwardly.

In one embodiment, these coupling means comprise, for each support (support disk) 161, 162, lugs suitable for contact with each other. These lugs are part of the hook.

More specifically, in one embodiment (FIGS. 1 and 2), the joining means is adapted to bond the friction liners 131 and 132 to the respective supports (support disks) 161 and 162. Lugs 501 and 502 are each formed in the central support region 221A to be attached by a pressing operation.

These lugs 501 and 502 are formed in the opening 500 which is in the shape of a rectangular hole formed in the central support region 221A. These lugs 501 and 502 are coupled to the central support region 221A through an inclined region that forms a bent portion created from the central support region 221A, and a hole (FIG. 1) is formed to limit the stress rise. do.

In this way, lugs 501, 502, 510 are produced which extend mostly on one side of the radial axis of symmetry of triangular blades 572, with only lugs 501, 502 being associated with the associated lugs of the other support (support disk). Extends on another side of the axis of symmetry to cooperate.

Thus, lugs 501 and 502 extend parallel to central support area 221A and are axially offset toward the friction liner opposite the lug fixed on the central support area 221A.

This axial offset is achieved by the inclined areas that make up the bends. Thus, the lug 501 is cantilevered, while the rectangular opening 500 is generally parallel to the tangential bend 380.

Because of its rigidity, the opening 500 has a radius between the outer periphery of the central support region 221A and the tangential bend 380 (in this embodiment itself constitutes the tangential bend of the triangular blade 572). Direction and to the center.

The opening 500 extends symmetrically perpendicular to the radial axis of symmetry of the blade 572 between two outer circumferential bends 222A of the blade 572.

As can be appreciated, one of the supports (support disks) 161, 162 has lugs 501, 502 extending from one edge of the central support area 221A to the other edge of the central support area 221A. Other support (support disk) is the reverse.

In this way a bayonet-type fit can be provided. For example, lug 501 of one of the supports (support disk) 161, 162 is introduced into opening 500 of another support 162, 161 and then coupled with an associated lug 502 of the other support. Rotate circumferentially.

Of course, the opening 500 may be formed according to the size. In this way the subassembly is easily formed, the subassembly comprising two supports 161, 162 and two friction liners 131, 132, the axial spacing of the two friction liners being the lugs 501, 502. Is limited by cooperation.

When the subassemblies 161, 162, 131, 132 are fitted on the guide rings 1, 2, the lugs 501, 502 are engaged with each other, with the clutch separated as shown in FIG. 2.

Thus, the axial spacing between the triangular blades 572 is limited.

In these figures, lugs 501 and 502 are coplanar with outer circumferential support region 522B, which is coplanar with supports (support disks) 161 and 162.

This is made possible by the fact that the central support area 221A has a large surface area.

Of course, the lugs of the engaging means can be positioned in the outer circumferential support area 522B as shown in FIGS. 1 and 3.

Thus, lugs 503 and 504 are coupled to outer circumferential support region 522B through bend 511 and are axially offset relative to outer circumferential support region 522B but parallel to the outer circumferential support region.

In addition, a bayonet type fit may be provided. In this variant, the lugs 503 and 504 are disposed at the outer circumference of the outer circumferential support region 522B, and one lug is disposed for each outer circumferential support region. Thus, two lugs 503 and 504 are formed for each blade 572.

It will be appreciated that since the central support region 221A does not have any openings, the central support region remains the same. Thus, the friction liners 131 and 132 are adhesively attached on the increased support area.

As can be appreciated, the bend 380 causes the supports (support discs) 161, 162 to converge against each other, and the friction liners 131, 132 are arranged to move towards each other during operation of the clutch in the clutch. In addition, the blade 572 is the same as that. Due to the circumferential bends 222A, the supports (support discs) 161, 162 are deflected towards each other, and during this operation of the clutch, the blades 572 are elastically compressed to achieve the desired gradual operation. do.

Of course, the position of the lugs 503 and 504, and thus the axial offset of the lugs relative to the central support region 221A and the outer support region 522B, is such that the lugs compress the friction liners 131 and 132 in this way. Make it possible. The same applies to the lugs 501 and 502.

Of course, lugs 501 and 502 do not lie perfectly in the plane of outer circumferential support area 522B.

In such a case, as shown by the dashed lines in FIG. 2, the relief holes 520 in the friction liner 131, 132 to avoid any interference between the friction liner 131, 132 and the lugs 501, 502. ) Is enough.

All of this depends on the application.

As can be appreciated, good gradual operation is achieved.

It will be appreciated that the blade 572 may follow the tendency of the pressure plate to take a conical shape, in particular under the thermal effect attributable to the bend 380, thereby reducing wear.

It will be appreciated that the coupling means may again limit the spacing between liners 131 and 132 due to the effect of thermal deformation. This joining means limits the opening between the two supports (support disk) 161, 162.

The invention is not limited to the described embodiments.

Thus, the liner support disk may comprise only a single support disk, for example the triangular blades are arranged alternately with the radial tongue, as shown in FIG. 25 of EP 0 579 554 described above, the center of which is Supporting a friction liner for cooperating with the pressure plate of the clutch on the support area, the liner is adhesively fixed to the central support area, and there is no opening in the central support area.

The other friction liner is fixed on the tongue, preferably with an adhesive.

The subassembly can be formed by adhesively bonding the tongue, for example tongue 471, to each other.

The single support disk may comprise two sets of triangular blades arranged alternately with each other as shown in FIG. 14 of the above-mentioned European Patent No. 0 579 554.

One of the two sets of triangular blades is more rigid than the other, i.e., the blade set on the central support area, and on this other set of triangular blades a friction liner arranged to cooperate with the recoil plate of the clutch is adhesively attached. .

In a variant (Fig. 5), it is also possible to use the blade of fig. 15 of the aforementioned European Patent No. 0 579 554. This is particularly suitable when the two supports (support disks) 161, 162 are rear contact mounted and their outer support areas 221B are in contact with each other.

In that case, a very wide adhesive surface is achieved, and the supports (support disks) 161, 162 comprise very close to each other, for example 16 blades.

The liner support disk may comprise two supports (support disks) as shown in FIGS. 1 and 3, the joining means limiting the spacing between the supports (support disks) and the tangential bend 380. Is obtained by lugs 505 pressed outwardly from supports (support disks) 161 and 162 into passages or holes 506 radially inwards.

The lug 505 parallel to the plane of the central portion of the supports (support disk) 161, 162 is axially offset with respect to the plane of the central portion which is joined via the inclined bend 512.

Here, the subassembly is formed by performing the bayonet type fitting. The lug 505 of one of the supports (support disk) is joined in the hole 506 of another support (support disk) and then rotated circumferentially so that the associated lug (formed in the other support (support disk) 505 or, in a variant, with the edge of a hole 506 (and thus reduced in size) in another support (support disk).

In that case, only one of the supports (support disks) is provided with a hook which is arranged to cooperate with the contact surface supported by the other support (support disk) and is formed by the contour of the hole 506.

One of the supports (support disks) 161 and 162 does not have a triangular blade, while the other support (support disk) is for example similar to the support (support disk) of FIG.

In this case, all the gradual movements are due to the support (support disk).

The foot portion of the blade may partially include a tangential bend 380.

Of course, the number of coupling means depends on the application. In practice, only a portion (preferably at least three) of said triangular blades have hooks.

The triangular blade may be attached by riveting onto the support disk to form the outer periphery of the support disk, as in the 32nd degree of European Patent No. 0 579 554 described above.

In that case, it is also possible to provide two support disks (supports) which are joined together with the coupling means 501, 502, 510 of FIG. 1. In this case, the tongue 772 in the plane of the support disk (support) has an inclined bend at its outer circumference which limits the outer circumferential support area offset towards the central support area of the triangular blade 771. In this embodiment, these blades have tongues 725 formed in openings 726 and blocking longitudinal bends.

In all cases, the hook of one of the supports (support disk) is arranged to cooperate with an associated contact surface supported by the other support (support disk), for example by a lug to configure the hook.

In one variant (FIG. 7), a unidirectional axial actuating engagement means suitable for limiting the axial spacing between two supports (support disks) 161, 162 is a short post 1501. It may also include. These short posts are fixed by their tangential bends to one of the central support regions 221A of one of the supports (support discs) 161, 162, the shank of the short posts passing through these shanks. It extends through the other central support region 221A of the other supports (support disks) 162, 161 to have a head.

The short posts are joined by their heads on the other central support region 221A to limit the spacing between two central support regions 221A facing each other and thus between two supports (support disks). A central support region 221A having a hole for receiving the shank of the short post is arranged to slide along the shank.

As shown in FIG. 7, the relief in the friction liner 131, 132, which is adhesively attached onto the central support region 221A, to prevent interference of the head and foot of the short post with the friction liner. It is of course also necessary to form a hole.

This configuration is similar to that of FIG. 35 of European Patent No. 0 579 554 described above, except that the short post plays no role in securing the support disk.

Of course, the number of coupling means depends on the application and may be smaller than the number of triangular blades.

Consequently, to the extent that relief holes are provided in the friction liners 131, 132, the lugs 501 or 502 may cooperate directly with the edge of the opening 500 of the central support region 221A associated with the other support disk. .

Similarly, in FIG. 3, a relief hole in the friction liner 131, 132 is provided that is adhesively attached onto the central support area 221A to avoid any interference between the lugs 503, 504 and the friction liner. It is also possible.

As shown in FIG. 7, the outer circumferential support regions 522B may of course not be in contact with each other when the clutch is disengaged.

Thus, bearing is achieved during engagement of the clutch, and its engagement action corresponds to mutual engagement of the outer circumferential support area 522B.

This is possible because of the coupling means. Lugs 503, 504, 505 may be replaced by the short post 1501 of FIG. 7.

Claims (14)

A liner support disk included in an automotive clutch friction wheel, comprising: at least one support disk (first support disk) 161, 162 having a central portion and an outer periphery divided by radial blades 572, wherein the blade Is adapted to receive two friction liners 131 and 132 on both sides of the outer circumference, each blade having a radial symmetry axis and a central support area axially offset relative to the center of the support disk. 221 A and coupled to the central portion by a foot portion having a tangential bent portion 380 perpendicular to the radial axis of symmetry of the blade, wherein the central support region 221 A is provided in the Narrowed toward the outer periphery of the support disk, each blade in contact with and at least one of the friction liners 131, 132 (first friction liner); In order to secure the liner in the support disk having at least one parallel support and fixed relative to the middle region of the plane of the central portion of the supporting disk, In order to form a triangular blade 572, the support and fixation region consists of the central support region 221A, at least some of the blades 572 on their outer periphery on both sides of the central support region 221A. Having two supplemental outer circumferential support regions 522B, the outer circumferential support regions being axially offset with respect to the central support region 221A, wherein each outer circumferential support region and the central support region are radially symmetrical axes of the blades. A bent through a bent portion with respect to the bent portion, the bent portion converging toward the outer circumference of the blade, the friction liner being directly fixed by adhesion on the central support area 221A associated therewith. disk. The method of claim 1, The outer circumferential support area 522B is configured to make contact with the friction liner (second friction liner) of the other of the friction liners 131 and 132. Liner support disk. The method of claim 1, And a second support disk coupled to the first support disk, wherein the other friction liner (second friction liner) of the friction liners 131 and 132 is secured by an adhesive on the second support disk. Characterized in that Liner support disk. The method of claim 3, wherein The second support disk, like the first support disk, has a triangular blade having a central support area 221A to which the second friction liner is fixed. Liner support disk. The method of claim 4, wherein The peripheral support regions of the triangular blades are in contact with each other Liner support disk. The method of claim 4, wherein Characterized in that intervening between the support disks is a unidirectional axial actuating engagement means configured to limit the axial gap between the two support disks 161, 162. Liner support disk. The method of claim 6, The coupling means is arranged in at least part of the central support area 221A of the triangular blades. Liner support disk. The method of claim 6, The coupling means is arranged on at least a portion of the outer circumferential support area 522B of the triangular blades. Liner support disk. The method of claim 6, The coupling means is arranged in at least some of the tangential bends of the triangular blades in the support disks 161, 162. Liner support disk. The method according to any one of claims 6 to 9, Said coupling means comprising a hook Liner support disk. The method of claim 10, The hook is a lug 501, 502, 503, 504, 505 extending in parallel with one of the elements consisting of the central support region 221A, the outer circumferential support region 522B and the support disks 161, 162. And coupled to the element via a bend Liner support disk. The method of claim 11, The lugs 501 and 502 are formed in the opening 500 of the rectangular hole formed in the central support region 221A. Liner support disk. The method of claim 11, The lugs 503 and 504 are formed on the outer circumference of the outer circumferential support region 522B. Liner support disk. The method according to any one of claims 6 to 9, The coupling means consists of a short post, the foot of the short post being fixed to one of the central support regions 221A of one of the support discs 161 and 162, the shank of the short post Extending through the central support region 221A of the other support disk, the short post has a head disposed in contact with the other central support region to limit the spacing between two triangular blades of the two support disks. Characterized by Liner support disk.