KR100326785B1 - Liner support disk - Google Patents

Abstract

The present invention provides a continuous radial blade 771, 971, 1071, 1471 in the form of at least one spider web with a central portion 16, a central region 722, 922, 1022 and a longitudinal fold 724, 924, 1024. It relates to a friction liner disk comprising an outer periphery. The central region of a portion of the at least spider web shaped blades 771, 971, 1071, 1471 is oriented radially inwardly defined by openings 726, 926, 1026 in the longitudinal folds 724, 924, 1024. Central extensions 725, 915, and 1025. The friction liner disc is used in a vehicle.

Description

Liner support disc

1 is an axial sectional view of a clutch friction wheel with a liner support disk according to the invention,

2 is a partial elevation view of the liner support disk, wherein the support area is shown in cross-sectional hatching;

3 to 10 show a similarity of FIG. 2 showing a further embodiment,

11 is a cross-sectional view taken along the line 11-11 of FIG.

The above figures illustrate a liner support disk suitable for forming a vehicle clutch friction wheel portion.

These friction wheels (FIGS. 1 and 2) alternate circumferentially with a series of radial tongues 772 in the plane of the central portion 16 and the central portion 16 of the liner support disk, here at regular intervals. And an outer periphery divided by alternately arranged radial blades 771. In these figures, blade 771 and tongue 772 are integral with central portion 16.

As disclosed in EP-A-0 579 554, each blade is coupled to the central portion 16 via a longitudinal leg 724, and two blades are provided at the central support region 722 and its outer periphery. It has a peripheral support area 723.

The wide central region 722 is axially displaced with respect to the central portion and the outer circumferential support region 723.

The wide central area 722 serves to secure the friction liner 132, while the tongue 772 serves to secure the additional friction liner 131. To this end, the tongue 772 and the central area 722 of the blade 771 have a hole in this example, which in this example is formed by means of the rivet 47 (FIG. 1). 132 is formed to secure the liner support disk.

According to one feature of the invention, the holes 19 are distributed on two pitch circles having different diameters. In a variant, a part of the hole 19 is not arranged on the pitch circle to define a zig-zag shape. As another variant, fixing with an adhesive may also be employed, which may omit the fixing holes and thereby improve the strength of the blade in the following manner.

The liner support disk is provided with two annular friction liners 131, 132 mounted back to back on both sides of the central portion 16.

In this embodiment in organic form, this friction liner is continually present in the circumferential direction and reinforced by glass fibers of KELVER or others.

In clutches, liners 131 and 132 are typically tightened between a pressure plate and a reaction plate (not shown) of the clutch, while these two plates are fixed to the crankshaft so as to be rotatable with the crankshaft of the vehicle's internal combustion engine. The hub 3 is connected to the input shaft to rotate with the input shaft of the reaction plate via a splined inner bore.

In the spaced apart operation of the clutch to space the reaction plates, the friction liners 131 and 132 are separated so that the liner does not come into contact with some of the pressure plates in the separated position of the clutch.

When the clutch is in close contact, the liners 131 and 132 are tightened between the plates.

This progressive gripping action is mainly due to the triangular blade 771, in particular due to the outer circumferential support area 723 and the leg 724 of the blade.

Blade 771 has a triangular shape with three flat support regions or engagement regions 723, 722, respectively.

The flat central region 722 is in contact with the friction liner 132, which engages the pressure plate, and serves to secure the friction liner 132. This region 722 becomes narrower toward the outer periphery of the liner support disk. Thus, this area becomes wider at the inner circumference of the liner support disk.

More precisely, the liner support disk having friction liners 131, 132 is in this example motion relative to each other with respect to the action of the elastic means 5 acting circumferentially and the friction means 20 acting axially. It is part of a clutch friction disk that includes two coaxially mounted shafts.

For example, such friction wheels are disclosed in EP-A-0 579 554 and US Pat. No. 5 014 842, which are hereby incorporated by reference.

In this example, one of the coaxial portions includes two guide rings 1, 2 with the liner support disk, while the other coaxial portion is by crimping to rotate with the hub 3 or As in the case of this example, it comprises a damper plate 4 which is secured to the hub 3 by loose coupling means clearly shown in FIG. 3 of U.S. Patent No. 5 014 842.

It therefore comprises trapezoidal teeth formed on the outer periphery of these means hubs 3 and on the inner periphery of the damper plate 4, which teeth engage with each other and have a gap therebetween.

The low stiffness spring, not shown, is coupled to the cup member, each of which has its ends fitted in the slots of the hub 3 and the damper plate 4, to impart an elastic engagement between the parts.

This configuration can also be reversed, in which case the liner support disk is fixed to the damper plate 4 which is movable in rotation relative to the hub 3, while the guide ring is fixed to the hub 3.

Likewise, the liner support disk may be fixed to the damper plate 4, the damper plate is fixed to the hub 3, and the clutch friction wheel is of rigid type as disclosed in EP-A0 579 554. do.

In this example, the liner support disk is coupled to the guide ring 1 through the central portion 16 of the liner support disk, with a gap through the aperture 7 formed in the damper plate 4, and means for spacers to extend. Is fixed to the guide ring.

This spacer 8 fixes together the guide rings 1, 2 arranged on both sides of the damper plate 4.

The elastic means 5 consists in this example of a coil spring mounted in a room in a window formed so as to face each other on the guide rings 1, 2 and the damper plate 4, in its own known conventional method.

The friction means 20, together with a thrust ring installed on the guide ring 2 to rotate with the guide ring 2, by means of an axial lug attached in a hole formed in the guide ring 2, damper plate ( And a friction ring interposed axially between 4) and ring (1).

The spring is supported by the guide ring 2 and the thrust ring is pressed to contact the damper plate 4.

Regions 723 are on both sides of the central region 722 at the outer periphery of the blade 771. The region is approximately triangular in shape and is connected to the central region 722 via the bend 721, which is inclined with respect to the radial axis of symmetry of the blade 771. These bends 721 are inclined in the axial direction and are symmetrical about the radial axis.

Therefore, regions 723 and 722 are axially eccentric and parallel to each other because of axially eccentric choke 721. To be precise, the region 723 is arranged to contact the friction liner 131 which acts on the reaction plate by clutch. In this example the regions extend on the plane of the central portion 16.

The central region 722 is connected to the central portion 16 via tangentially oriented bends 724 or longitudinal bends, which in this example are perpendicular to the radial axis of symmetry of the blade. This axially inclined bend 724 constitutes the leg of the blade and displaces the region 722 axially relative to the central portion 16. The bend 724 extends symmetrically about the radial axis.

Thus, when liners 131 and 132 are compressed, region 723 deforms in the axial direction. It should be noted that the bend 724 is formed to be wide in width and quite strong. The vertical slot 224 separates the blade 771 from the tongue 772. This slot is open at the outer circumference of the liner support disk and has a circular closed end for connection of the bent portion 724 and the central portion 16.

The bent blade 771 has a reduced circumferential extension in comparison to that disclosed in EP-A-0 579 554, such that tongue 772 is formed of blade 771 according to one aspect of the present invention. It has a width in the circumferential direction close to the width. Thus, the engagement surface for each liner is located as close to each other as possible.

This is to have the largest engagement surface in the friction liners 131 and 132 in the shortest distance between the engagement surfaces.

Therefore, several blades are used. In this example, since the clutch friction wheel has a large size, the configuration is for example at least two rows of fastening members 47 of the fastening members such as rivets, screws or bolts for fixing the friction liners 131 and 132. ), At least two fixing holes 19 through which the fixing member passes are provided in at least part of the blade 771.

As a variant, it is possible to provide a single rivet with adhesive fixation or only adhesive fixation. In either case, the clutch friction wheel should have improved resistance to the effect of centrifugal forces.

Therefore, in accordance with the present invention, a liner support disk of the type described above has at least a central portion 725 of a central region 722 of a triangular blade 771 by a slot 726 formed in the longitudinal bend 724. It extends radially inward. 1 and 2, the extension portion 725 is provided with an additional hole 19, through which the fixing member 47, riveted in this example, passes. Therefore, the engagement surface for the friction liner 132 is increased, making the fixing of the liner 132 more firm.

As can be clearly seen in FIG. 2, the other fixing holes 19 are arranged at the outer circumference of the central region 722 and the blade 771.

Thus, the holes 19 for fixing the liner 132 are arranged on the same plane and are radially spaced apart from each other at a considerable distance, in this example they are arranged radially on the axis of symmetry of the blade 771. do.

According to one feature, the tongue 772 has a shape similar to that of the blade 771, so in this example the tongue is in the plane of the central portion 16 on both sides of the central region 823 and the central region 823. It has two peripheral support regions 822 at the same time.

An axially inclined and radially inclined bend 821 connects each region 822 to the outer periphery of the central region 823. The support region 822 is axially displaced towards the central region 722 of the blade 771. They may be coplanar with the blade or slightly behind the blade in the axial direction.

Two fixing holes 19 in the same plane are provided in the central region 823. These holes 19 are radially aligned on the radial symmetry axis of the tongue 772 and are located on the same pitch circle as the holes 19 of the blade 771. In some of the tongues 772, these holes are fixed for fixing to the fixed damper plate 4 by riveting the central portion 16 to the flange of the hub 3 by riveting in FIG. Aligned with the hole 119.

Of course, as in the variant shown by the broken line in FIG. 2, tongue 772 is replaced by a second set of curved triangular blades having a shape similar to blade 771 and the longitudinal bend is centered on the liner support disk. The central region can be connected to 16.

In this embodiment, the slot 726 according to the invention is V-shaped with a rounded base, with the V-shaped nipple facing the axis of the friction wheel (ie, the axis of the central portion 16). Thus, the extension 725 has a round V-shape. It constitutes an added lug that is directed approximately radially inward as in the other figures shown below.

This slot is formed in the bend 724 and extends locally in the central region 722 and a portion of the central portion 16. Thus, the bend 724 is divided into two parts, which improves the gradual tightening effect described above. The bend 724 has good mechanical strength despite having a slot provided in accordance with the present invention.

It should be noted that the extension 725 has a branched root zone, which is connected to the central zone 722 by this root zone.

This root zone reduces the risk of rupture.

The radial symmetry axis of the slot 726 coincides with the radial symmetry axis of the blade 771.

It should be understood that the good parallelism of the clutch friction wheel and the good flatness of the friction liner are due in particular to the regular spacing of the fixing holes 19 and their positions on the axis of symmetry of the tongue 772 and the blades 771.

It should also be noted that the easy manufacture of this structure is such that the disk can be accompanied by tongues and blades of different depths because of the radial displacement of the press tool obtainable.

In this example, the gap is between the two liners 131 and 132 at the position where the clutch is connected (tightened liners 131 and 132), so that the blade 771 is not entirely compressed and the liners are connected to the pressure plate. It is adapted to the shape of the reaction plate.

The triangular blade may have another shape, as disclosed in the above-mentioned European Patent Publication EP-A-0 579 554.

Thus, in FIG. 3, the triangular blade 971 has a reduced width at the outer periphery of the blade and is inclined with respect to the radial axis of symmetry of the blade and with respect to the longitudinal bend 924 perpendicular to the axis of symmetry. The bent portion 921 has a central support region 922 displaced axially with respect to the central portion 16.

As shown in FIG. 2, the central region 922 extends radially inward in the middle by a U-shaped central slot 926 formed on the longitudinal bend 924. This extension is approximately in the shape of a tongue or lug 925 having a root region connected to a reduced width central region 922, wherein the vertical end of the slot 926 is formed within the region 922 with the slot 926. It is opened by a circular hole.

Thus, lug 925 faces the axis of the assembly and has a circular free end.

The outer circumferential support area 923 is generally present in the plane of the central portion 16. This region 923 protrudes circumferentially with respect to the central region 922 such that the blade 971 is approximately T-shaped.

An advantage of this shape is that it is possible to increase the circumferential width of the tongues 972, 973 in the middle radial region of the tongues 972, 973. Thus, the tongues 972 and 973 are wider at their free ends at their radial centers and wider at the areas associated with the central portions 16.

In this example, the radial tongues 972 and 973 have different shapes. These tongues are regularly arranged alternately with the blade 971 in the circumferential direction. The free end of the tongue 972 has a reduced circumferential width and has a supplemental support area 942 connected to the main portion of the tongue via a connection bend 941, the connection bend 941 being of excellent flexibility. To have a constant width at the level of the region 942 radially displaced towards the central region 922 of the support surface of the blade 971. This bent portion 941 is widened at its base portion. In this example, the replenishment region 942 is in the plane of the region 922 of the blade 971. The region 942 may of course be located slightly later than the region 922.

Tongue 933 has a region 932 at its free end, which region 932 is connected to the major region of tongue 973 through a bent portion 931.

Bends 931 and regions 932 in the plane of central region 922 are trapezoidal in shape.

As noted, the two sets of tongues may provide an axial displacement between the regions 942 and 932 in such a way that the liner is supported during engagement of the clutch.

In this example, the central portion 16 has a fixing hole 119 for fixing the central portion 16 to the guide ring 1 or the damper plate 4 as the case may be.

It should be noted that the slot 926 is formed in the center of the bend 924 to branch the bend 924 into two, which improves the gradual tightening of the blade 971. This bend has good mechanical strength despite the presence of a slot.

It should be noted that the slot 324 separating radial tongues 972 and 973 from blade 971 has a non-linear shape due to the central widening of the tongue.

In this example, the liners 131, 132 are directly attached by adhesive on the major portions of the tongues 972, 973 and the central region 922 of the blade 971. It should be noted that the flexible extension 925 is suitable for adhesive bonding.

All of these configurations can reduce the thickness of the liners 131 and 132.

Therefore, the liners 131 and 132 have only the required thickness, as in the embodiments of FIGS. 1 and 2, no thickened portion need be provided for the rivet 47.

Thus, the inertia of the clutch friction wheel is reduced, which is advantageous for preserving the gears of the gearbox on the input shaft on which the hub 3 is mounted while the clutch is released.

In addition, the blade and tongue are reinforced because no holes are needed to receive the rivets.

Thus, by the bent portion 945 connecting the region 944 to the main portion of the tongue 972, a supplemental support region 944 axially displaced towards the region 922 can be made in the plane of the central portion 16. have.

Providing this replenishment area is accomplished by the slot 946 being approximately V-shaped and facing radially inward unlike slot 926.

Thus, radially outwardly facing tongues or lugs 944 and 945 are formed and extend symmetrically about the radial symmetry axis of tongue 972.

Of course, as in FIG. 2, provision of the replenishment support region 925 allows the replenishment holes to be provided for securing the liner 132 by rivets.

Therefore, in FIG. 4, each tongue 1072 and each triangular blade 1071 has two holes 19 through which the fixing members for liners 131 and 132 pass.

These holes are radially aligned on the radial symmetry axis of the radial tongue 1072 and the blade 1071.

One of the holes 19 is located in the region of the extension 1025 of the central region defined by the U-shaped slot 1026 formed at the center in the longitudinal bend 1024 of the blade 1071. An extension 1025 in the form of a tongue or lug is present on the plane of the central support area 1022 of the blade 1071, where the area 1022 is inclined with respect to the radial axis of symmetry of the blade 1071 ( 1024, 1021 are axially displaced relative to the central region 16.

The bent portion 1021 is connected with an outer circumferential support region 1023 approximately parallel to the bent portion 1021.

Region 1023 is generally in the plane of central region 16.

The shape of the tongue 1072 is approximately similar to the blade 1071, with the difference that the major portion of the tongue is in the same plane as the central region 16.

Accordingly, the radial tongue 1072 has two supplemental outer circumferential support regions 1122 on its outer circumference, which outer circumferential support region lies approximately in the same plane as the central region 1022 of the blade 1071.

These regions 1122 are connected to the main regions of the tongue through bends 1121, which are inclined with respect to the radial symmetry axis of the tongues 1072.

In this embodiment, the blade 1071 is widened at its outer circumference and the tongue 1072 is widened in its circumferential direction at its outer circumference.

The tongue and the triangular blade can be separated from each other and attached to the guide ring 1 or the damper plate 4 by, for example, a hole 229.

Therefore, in FIG. 5, the triangular blades 771 are alternately arranged in the circumferential direction with the radial tongue 772 having a shape similar to that of the blades 771, as shown in FIG.

In this regard, the inner periphery 316 of the tongue 772 has two holes 229 through which a fastening member such as a rivet passes through for fixing with the guide ring 1.

In this embodiment, the tongue 772 has a replenishment support region 1125 in its central portion.

This region 1125 is on the same plane as the central region of the blade 771 and is connected to the main portion 1128 of the tongue 772 via the bent portion 1124.

All of this is obtained by a slot 1126 that is approximately V shaped.

A bend 1124 having a support region 1125 in which the tip is narrowed constitutes a tongue or lug that generally faces axially toward the assembly, in contrast to the embodiment of FIG. 3.

Tongue 772 extends radially beyond its longitudinal bend toward the axis of the assembly, so that it can be secured to the guide ring using a hole 229 through which the fixing member passes.

Referring to FIG. 6, tongue 772 and blade 771 may of course be coupled to one another at their base portions.

In this case, each blade 771 is formed integrally with an integral strip 116 that is approximately annular sector shaped.

The strip 116 connects one blade 771 to one tongue 772, and in this example three fixing holes 229 for securing the guide ring 1 or the damper plate 4 by rivets. Has

5 and 6, the blades 771 and the tongues 772 are shaped symmetrically with each other because their central regions have roughly V-shaped lugs 1025, 1124, 1125 facing the axis of the assembly. Have

Lug 1025 is formed on the longitudinal bend of tongue 772 as described above. The liners 131, 132 can be secured (using the holes 19) by adhesive bonding and riveting because the lug 1025 allows such an adhesive bonding.

Of course, it is possible to separate the central portion into strips 226 with their respective circumferential ends (Fig. 7). Thereafter, a hole 229 is formed and overlaps between the tongue and the continuous blade 771.

In this embodiment the strip 226 is fixed to the guide ring 1 by means of rivets through holes 229.

The blade 771 and tongue 772 may be formed integrally, as in FIG. 2 (FIG. 8), and the apertures 19 of the blade 771 are as shown in FIGS. 5 to 7. A hole 19 associated with the tongue 772 is arranged on a pitch circle of a different (smaller) diameter from the arranged pitch circle, and a hole 119 is formed in the tongue.

As shown in Figures 5-7, the liner can be secured by adhesive bonding and riveting, which adhesive replacement replaces the second set of rivets. Tongue 772 may be composed of a triangular blade with lugs 1025.

In FIG. 9, the liner support disk comprises two attached support disks, each attachment support disk comprising a triangular shaped blade. This blade has a shape similar to that of the blade shown in FIG. 6, so that each blade is fixed on the appropriate supporting disk by the holes 229. As shown in FIG.

The support disks are fixed to each other by the spacer 8 in FIG. 1 and at the same time also by the guide ring 1.

Thus, the triangular blades are alternately aligned with the tongue 772 and are separated by slots 524 and 224. The triangular blades are mounted in series, and the friction liners 131 and 132 are adhesively fixed to the central area of the triangular blades 771.

Thus, one of the friction liners is adhesively secured to the central support area of one set of triangular blades, while the other liner is adhesively secured to the central area of another set of triangular blades.

The coupling means 501, 502 have an axial actuation in one direction and are suitable for limiting axial separation between two support disks and are arranged between the two support disks.

The spacing means are fitted at some level of the central support area of the triangular blade 771.

Therefore, in this example, similar to the blade of Fig. 2, the triangular blades 771 are regularly arranged alternately, and the triangular blades have coupling means. This coupling means comprises hooks 501 and 502. The hook includes lugs 501 and 502 extending longitudinally parallel to the central support area of a suitable support disk.

Lugs 501 and 502 are connected to the central support region via bends 510. The lug is defined in the pressed-out 500 in the form of a rectangular hole formed on the central support area.

The hooks supported by one of the disks are aligned to bond with an associated mating attachment surface supported by the other disk. The other disc supports lug 502 in the shape of lug 501.

In this respect, hooks 501, 502, 510 are provided, which extend predominantly on one side of the radial axis of symmetry of the triangular blade, with only lugs 501, 502 of the shaft for cooperating with the connecting lugs of the other disc. It is placed on both sides.

Thus, lugs 501 and 502 extend parallel to the central support area and are axially displaced towards the friction liner opposite the liner fixed on the center area of the appropriate triangular blade.

As noted, one of the disks includes at least one lug 501, 502 that extends from one edge of the central support area to the other edge of the central support area, and vice versa for the other disk.

Thus, it can provide a bayonet fit. For example, lug 501 of one of the disks is introduced into the hole 500 of the other disk and then rotates circumferentially for engagement with the connecting lugs 502 of the other disk.

Of course, the hole 500 is dimensioned accordingly.

Thus, a subassembly comprising two disks with blades 771 and tongues 772 and liners 131 and 132 is readily constructed, and axially spaced apart in cooperation with lugs 501 and 502. Limited by

This subassembly is then fitted to the guide rings 1, 2 by spacers 8.

Since the lugs 501 and 502 are engaged with each other when the clutch is released, the axial separation between the triangular blades is limited.

Lugs 501 and 502 are in substantially the same plane as the outer circumferential support area of the triangular blade in the same plane as the disc when the clutch is released.

It should be understood that the friction liners 131, 132 are secured with adhesive over a large surface area.

Of course, it is possible to provide the supplemental support area 1425 of the blade 1471 to the outer circumferential support area of the blade 1471 (see FIGS. 10 and 11).

The support region 1425 extends in the same plane as the central region 1422. In particular, the central region 1422 is connected to the outer circumferential support region 1423 in the same plane as the main portion of the tongue 1472 via the inclined bent portion 1421.

This region 1423 is connected to the supplemental support region 1425 via a bent portion 1424 that is inclined with respect to the radial axis of symmetry of the blade 1471. The area 1425 is in the same plane as the replenishment area 622 of the tongue 1472. Region 622 is defined at the free end of tongue 1472 and is approximately rectangular in shape. It is connected to the main portion of the tongue 1472 via a bend 621 similar to the bends 941 and 931 of FIG.

As in FIGS. 5-8, this tongue 1472 also has a supplemental support region 1125 that is connected to the main portion of the tongue 671 through the bend 1124.

All of these are defined by approximately V-shaped slots 1426. Thus, region 1125 is in the same plane as central region 1422.

With all these replenishment areas defining the stability area, high stability to the friction liner is obtained, which is advantageous for reducing wear. Such liners are well supported.

Of course, it is possible to adhere and fix the friction liners 131 and 132 to the tongue and the blades 771 and 772.

The invention is, of course, not limited to the above described embodiment.

The friction liners 131 and 132 may be divided. In a variant, each liner may comprise a continuous support crown in which the opening is formed to fix the friction pad in the manner disclosed in the above-mentioned European Patent Publication EP-A-0 579 554.

The legs of the blades do not have to consist solely of tangential bends, with the leg ends joining the bends to the central area of the friction wheel.

Depending on the particular application, it is also possible to omit the support areas formed in the outer periphery of the radial tongue. For example, it is possible to omit the bent portion 941 and the region 942 in FIG. 5 and to retain the region 944 and the slot 946.

It is also possible to provide two pressurized openings facing the opposite radial direction and delimiting the connecting bend supporting the supplemental support area.

All combinations are possible.

5 to 8, three supplementary support regions, two outer circumferential support regions of portion 1125 and tongue 772, are a triangular manner which is extremely advantageous for safety and for reducing liner 131 and 132 wear. It should be understood that they are closely spaced apart.

The inclined bends joining the outer circumferential support area to the central area may of course be arranged asymmetrically with respect to the radial symmetry axis of the blade. The same applies to the central region.

The supplementary support area does not necessarily have to be arranged on the radial axis of symmetry of the tongue. There may be some displacement.

In general conditions, it can be seen that in FIGS. 3 to 8, 10 and 11 the tongue provides at least one additional support area.

Thus, while compressing the liner 131, 132, each region or region 932, 822, 1122 is suitable for contacting the liner 132 to provide a reaction surface. Therefore, the above regions constitute a stable region extending in the plane of the central region 722 by the above-described bent portions 931, 821, 1131.

In a variant, these regions may fit slightly relative to the central region. Thus, the liner 131 remains completely flat.

In this regard, a liner support disk having a large support area at its outer circumference is obtained, and the friction liner 131, 132 remains in a substantially parallel plane, thereby reducing the intrusion phenomenon and the judder effect. Therefore, the liner support disk and the friction wheel can rotate at high speed, accompanied by a tendency for the pressure plate and the reaction plate to become conical. The distribution of wear in the liner is further improved.

Since the bends 724, 924, 1024, 931, 921, 821, 1121, 1021 impart high stability to the liner support disk, the liner support disk ensures good contact between the friction liners and the pressure plate and the reaction plate, It can be seen that the wear of the friction liner is reduced.

The good parallelism of the friction wheel and the good flatness of the friction liners thereof are due in particular to the regular distribution of the fixing holes 19 and their position on the axis of symmetry of the tongue and triangular blades.

In this example, there is a space between the two liners 131, 132 in the clutched position (the liners 131, 132 are braked), so that the blades are not compressed entirely so that the liner forms the pressure plate and the reaction plate. Adapt to

In FIGS. 10 and 11, it will be appreciated that the central support region 1422 has two lugs arranged on both sides of the longitudinal bend 1024 at its inner periphery. These lugs allow the support surface of region 1422 to be increased in association with lug 1025.

Thus, it is possible to adhesively fix the friction liner 132 to the region 1422.

In all cases, flexible extensions, generally present in the form of lugs 725, 925, 1025 in accordance with the present invention, allow the appropriate friction liner to be adhesively fixed.

Thus, the soluble lug is applied with an adhesive.

FIELD OF THE INVENTION The present invention relates to a liner support disc for friction liner support, which is suitable for constructing a clutch friction wheel, in particular a clutch friction wheel for use in a vehicle, comprising a central portion and an outer circumference, wherein the outer circumference receives the friction liner. Divided into radial blades, each blade being integrally connected with said central portion via a leg and generally contacting at least one of the friction liners and securing said friction liner generally. A liner support disk of the type comprising at least one support region in parallel. In the clutch friction wheel, the liner is disposed on both sides of the outer circumference.

Clutch friction wheels may experience undesirable vibrations during operation, often called judder. Such a judder effect may also occur at low torques applied during parking operation, as in high torques applied during gear shifting during driving and at start on hill roads.

Since the support area is sometimes not wide enough, an embedding effect is introduced, in which the friction liner penetrates into the hollow located between the two support surfaces of the same blade.

This causes a lack of flexibility, which is at least partly a cause of the judder effect at full load.

In addition, there is also a problem of contact with the pressure plate of the clutch.

In this regard, in the clutch, each time the clutch is engaged, the friction liner is gradually tightened between the pressure plate and the reaction plate.

The heat generated by the friction inevitably deforms the pressure plate into a conical shape, as disclosed, for example, in US Pat. No. US-A-2 902 130, and to a lesser extent, but also in the reaction plate. This happens.

Thus, the area where the friction liner is subject to pressure from the pressure plate or the reaction plate is gradually displaced toward the axis of the assembly, as a result of which the non-uniform wear efficiency of the friction liner decreases (e.g., transfer torque decrease), It may cause a judder effect.

In order to overcome this drawback and solve this problem, EP-A-0 579 554 has a central support area and two peripheral support areas on both sides of the central area. It is proposed to provide a triangular blade which is axially displaced with respect to the area and the central support area.

In one embodiment, the blades are alternately arranged circumferentially with the tongues of the first series.

In another embodiment, the blades are alternately arranged circumferentially with the blades of the second series of triangular form in the form of a first series.

The triangular blade serves to fix one of the friction liners in its central area when the friction liner is associated with the pressure plate of the clutch, while the tongue serves to fix another friction liner when the friction liner is associated with the reaction plate of the clutch. Do it.

By this configuration, the tongue or the second series of triangular blades have sufficient elasticity to accompany the tendency of the reaction plate to be conical, while the triangular blades are accompanied by the tendency of the pressure plate to be conical, with a wide contact surface. Has

In addition, the intrusion phenomenon and the juder effect are reduced, and the blade can rotate at a higher speed, thereby eliminating the bending force of the blade leg caused by the centrifugal force.

In this patent specification, the fixing of the friction liner is performed by a series of rivets arranged on the same pitch circle. Therefore, a hole for passing the rivet constituting the fixing member is provided in the triangular blade center region of the first series.

The same applies to the central region of the tongue or triangular shape.

For large size (large diameter) clutch friction wheels, when the friction liner is thin and adhered to a foil supported by rivets on the liner support disk, it provides at least two rows of rivets arranged on pitch circles having different diameter diameters. Needs to be.

In order to properly fix the friction liner, it is necessary to increase the radial depth of the central area by spacing the hole containing the rivets by approximately a radial distance, so that the hole for accommodating the fixing member is positioned. The problem arises in connection with the triangular center area.

Likewise, when adhering the friction liner on the central region, it is desirable to increase the radial size of the central region in order to support the friction liner inwardly and improve the adhesive strength.

It is an object of the present invention to provide a novel triangular blade which fulfills this requirement and can thus increase the radial size of the central region in a simple and inexpensive manner.

The central region of the triangular blade is coupled to the central portion of the liner support disk by a leg comprising at least one inclined region in the shape of a longitudinal bend perpendicular to the radial axis of symmetry of the triangular blade, in accordance with the invention. The central region of at least a portion of the triangular blades extends radially inwardly by slots formed across the longitudinal bends.

Due to the present invention, in all cases, the engagement surface of the liner mentioned is increased to increase the resistance of the liner support disk to centrifugal forces. In the central region of one triangular blade, it is possible to arrange at least two fixing holes radially spaced from each other on the same plane.

In this regard, it is possible to sufficiently provide additional holes through which the fixing member of the friction liner penetrates the extension according to the present invention. This flexible extension reduces rupture.

Thus, the associated friction liner (which may be in divided form) can be secured to the central region of the triangular blades of the first series with at least two sets of rivets or other fastening members, each radially spaced from each other.

Thus, the friction liner is firmly fixed. Such a liner may rotate at a higher speed.

Likewise, the friction liner can be fixed directly on the central area by adhesive bonding.

In this regard, the extension allows the liner to be locally fixed at an increased height, which is good for adhesion. In addition, damage due to peeling or separation is reduced because of the flexible extension.

Of course, it is possible to fix the liner with an adhesive or by riveting, leaving a hole in the prior art.

Nevertheless, it should be noted that a structure having only adhesive bonds is advantageous because it allows the thickness of the friction liner to be reduced to a usable value. In this regard, there is no need to provide an extra thickness, as in a structure fastened with a rivet. Thus, the inertia of the clutch friction wheel is reduced. The mechanical strength of the central area is increased because there is no need to provide holes for riveting. Therefore, the friction wheel can rotate at a higher speed.

The structure according to the invention is inexpensive because it does not require large deformation for the tool required to manufacture the liner support disk.

In this regard, by forming a press with a simple tool, it is sufficient to form a slot or otherwise provide two rows of fixing holes. In addition, the extension according to the invention increases the support area of the liner in which the longitudinal bend is associated without any damage to the mechanical strength.

In still another aspect of the present invention, the number of blades is increased in order to keep the distance between the connecting surfaces as small as possible to maintain the maximum supported amount of friction liner involved.

As a result, the blade has a reduced circumferential width, and it is possible to form the tongue described above, wherein the tongue is a triangular blade having two outer circumferential support areas in the plane of the center and on both sides of the center spiritual. In the form almost in the center plane.

Therefore, during elastic compression of the friction liner, the friction liner associated with the tongue is recoiled due to a new outer support area suitable for engaging with other friction liners.

Thus, the penetration effect is reduced, and the wear of the friction liner associated with the tongue becomes more uniform. In addition, because the outer circumferential support area of the tongue provides an additional mating surface, wear phenomenon in the friction liner associated with the first blade set is reduced. For other friction liners the wear becomes more uniform.

Of course, the tongue described above can be replaced with a second set of triangular blades.

In a variant, at least a portion of the tongue has at least one additional support region displaced axially towards the central region of the first set of blades at the bent joint.

The added area may be located in the tongue because it is defined by the free end or slot of the tongue. Any combination is possible.

While the penetration effect is reduced as described above, wear in the friction liner associated with the tongue is more evenly distributed due to the added support area.

According to one feature, the slot is formed locally in the central region of the triangular blade to reduce the risk of any rupture in the extension region.

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

Claims (11)

An outer periphery divided by at least one central portion 16 and at least a series of radial blades 771, 971, 1071, 1471 in triangular form, the blades being bent at the bends 721, 921, 1121, 1421. Defined by a central support region 722, 922, 1022, 1422 and two peripheral support regions 723, 923, 1023, 1423 on both sides of the central region, the peripheral region being relative to the central region. Axially displaced, the central support region is connected to the central region 16 of the liner support disk via a leg, the leg being longitudinally bent 724, 924, 1024 orthogonal to the radial axis of symmetry of the blade. A liner support disk constituting a clutch friction wheel for a vehicle, comprising an inclined region of the form The central regions 722, 922, 1022, 1422 of at least a portion of the triangular blades 771, 971, 1071, 1471 are in slots 726, 926, 1024 formed in the longitudinal bends 724, 924, 1024. Extending radially inward from the center (at 725, 925, 1025) Liner support disk. The method of claim 1, The extensions 725, 925, 1025 are in the form of lugs extending substantially radially. Liner support disk. The method according to claim 1 or 2, The slots 726, 926, 1026 define the central regions 722, 922, 1022, 1422 locally. Liner support disk. The method of claim 3, wherein The slot 726 is approximately V-shaped with a rounded base, and the V-shaped tip is directed toward the axis of the central portion 16. Liner support disk. The method of claim 3, wherein The slots 926 and 1026 are U-shaped, the base of which is directed towards the axis of the central portion 16. Liner support disk. The method of claim 5, The extension 925 is characterized in that it is U-shaped with a root region having a reduced width connecting to the central region. Liner support disk. The method of claim 1, The radial axis of symmetry of the slots 726, 926, 1026 coincides with the axis of radial symmetry of the triangular blades 771, 971, 1071, 1471. Liner support disk. The method of claim 1, The triangular blades 771 and 1071 are arranged alternately in the circumferential direction with the tongues 772 and 1072 in the form of the blades, which tongue together with the planar central regions 823 and 1023 of the central portion 16. Characterized by having two outer circumferential support regions 822, 1122 on both sides of the central region 823, 1023. Liner support disk. The method of claim 1, The triangular blade has a tongue 972 having support regions 932, 942, 944, 1125 axially displaced on the bent portions 931, 941, 621 toward the central region of the combined triangular blades 971, 1471. 973, 1472 and alternately arranged in the circumferential direction Liner support disk. The method of claim 1, The central support area of the triangular blades 771 and 1071 has at least one hole 19 through which the fixing member 47 penetrates, and the extensions 725, 925 and 1025 have additional holes through which the fixing member penetrates. Characterized in that 19 is provided Liner support disk. The method of claim 1, The extensions 725, 925, 1025 is characterized in that the coating with an adhesive Liner support disk.