JPS6213830A - Diaphragm spring clutch cover assembly - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION A. Field of Industrial Application The present invention provides a diaphragm spring clutch cover assembly comprising a pressure plate, a cover, a first annular fulcrum arrangement on the pressure plate of the diaphragm spring, and the cover. A diaphragm spring clutch cover assembly of the type (hereinafter referred to as the reference type) containing a diaphragm spring acting between a second annular fulcrum arrangement above and a second annular fulcrum arrangement.

In use, the assembly is mounted on a drive member, such as the flywheel of an automobile engine.

The driven plate is therefore connected between the pressure plate and the drive member by the load of the diaphragm spring. Typically, diaphragm springs have a plurality of radially inwardly directed fingers so that an axial actuation force exerted through a release bearing on the radially inward ends of the fingers can release the driven plate.

In clutches known in the art and containing cover assemblies of the reference type, the driven plate is a friction surface mounted on a cushion between the surfaces.
It is equipped with a cushion in the form of containing a supporting plate waiting for the surface. However, in order to simplify and reduce the production cost of the driven plate, and to reduce its inertia, driven plates have been proposed in which the cushion between the S oscillation parts is reduced or eliminated. To compensate for this lack of cushioning, it has been proposed to introduce a degree of axial flexibility or a device that provides cushioning on one of the annular supports in reference type diaphragm spring clutch assemblies. One method of providing a cushioning device within a clutch cover assembly provides a clutch arrangement that is easy to manufacture and install, yet is primarily receptive when installed in a motor vehicle. One method is disclosed in British Patent No. 1,583,403. The British patent describes a diaphragm spring clutch cover assembly of the reference type, further comprising a cushioning device in one of the annular fulcrum arrays, the cushioning device having a corrugated shape extending parallel to the axis of the diaphragm spring. and the waveform is constituted by a first series and a second series of said waveforms, wherein the first series of waveforms has a lower stiffness but a larger axial amplitude than the second series of waveforms. A diaphragm spring clutch force bar assembly containing a cushioning device formed by a single wavy ring having a corrugation is shown in Figure 1). During re-engagement of the driven plate (after disengagement) the first cushioning is by the first series and then by the second series, which ensures that the coupling load is relieved during clutch re-engagement. This ensures that the substantial range of motion of the bearing increases progressively from one end to the other.

It has been found that a wavy ring with waves of different stiffness and size is not suitable for mass production.

C.8 Problems to be Solved by the Invention The object of the present invention is to provide a reference type diaphragm clutch cover assembly as described below with reference to the drawings, in which the above-mentioned difficulties can be avoided. and at the same time the assembly can be used to form a clutch for a motor vehicle in which clutch engagement is primarily receptive and the coupling load is increased during re-engagement. It is an object of the present invention to provide a diaphragm clutch cover assembly of a reference type which can be manufactured as will be understood from the following description with reference to.

According to the present invention, a diaphragm spring clutch cover assembly is provided which includes a pressure plate, a cover, a diaphragm spring for applying a load to the pressure plate, and a first annular fulcrum arrangement on one side of the diaphragm spring. a first annular fulcrum array on the opposite side of the diaphragm spring and mounted on the cover; a diaphragm spring clutch cover assembly comprising: a cushioning device in which at least one of the fulcrum arrays includes a resilient fulcrum ring; a bearing device supporting the ring around the axis of the diaphragm spring; and portions of the ring extending into respective spaces between adjacent said bearing devices @52; and the ring is a straddling element at positions spaced around the ring, each element being at a respective said portion, and each said element padding the ring. an element providing a distance piece, said fulcrum arrangement being such that said respective portions are axially relative to the ring during movement of the diaphragm spring relative to the cover for the diaphragm spring to exert an increasing load on the pressure plate. A diaphragm spring clutch cover assembly is provided in which the distance piece is biased by a diaphragm spring to elastically deform.

Each said element straddling the fulcrum ring is substantially U
It may have a shaped cross-section and the distance piece may be a U-shaped transverse piece.

The elements may be engageable by respective stopper devices to maintain the elements in substantially the same position around the fulcrum ring.

Preferably, the fulcrum ring has at least one cutout extending therethrough, and said cutout may be supplemented by said element.

The distance between said element and an adjacent said bearing device in the circumferential direction of the fulcrum ring is less than the distance between another said element and its adjacent bearing device in the circumferential direction of the fulcrum ring. It may also be larger.

In the circumferential direction of the fulcrum ring, the distance between opposite ends of one said bearing device may be greater than the distance between opposite ends of another said bearing device.

One said element may be longer than another said element in the circumferential direction of the fulcrum ring.

The arrangement is such that an increase in the diaphragm spring load on the pressure plate after a zero or minimum load tends to cause said fulcrum ring portion to bend in an opposite second direction at said bearing device and in a first direction. axially about the ring in said first direction such that a diaphragm spring applies stress to the ring such that a diaphragm spring acts on one or more of said bends to deform the bend in the axial direction of the ring by pressing on said bend; It may also be something that causes it to be deformed.

The fulcrum ring may be provided with assistance to the deformation of the fulcrum ring or the deformation of the fulcrum ring may be controlled so that the fulcrum ring is better controlled or in a predetermined manner to reduce the chance of damage to the ring. and/or, according to a second feature of the invention, in order to make the resulting cushion deformable in such a way that it more closely matches the desired properties. a surface which is pressed against the respective said part of the ring by being biased by, said surface being convex with respect to the ring and lying on a lateral piece of said U-shaped element; at least one of said elements having a surface extending substantially circumferentially along the ring and at least a portion of said convex surface overhanging or branching progressively away from the pressure plate; A diaphragm spring clutch cover according to the first aspect of the invention may further include a diaphragm spring clutch cover according to the second aspect of the invention.

According to a third feature of the invention, in a diaphragm clutch cover assembly according to the second feature of the invention, said portion of the fulcrum ring is in contact with a convex surface during axial deformation of said portion of the fulcrum ring. Gradually, a portion of the free length of said part corresponds more closely to the convex surface, thereby extending between the adjacent said bearing device and the element having the convex surface. A reduced diaphragm clutch cover assembly is provided.

According to a fourth feature of the invention, in a diaphragm spring clutch cover assembly formed according to the third feature, said bearing device adjacent said element is a surface and a fulcrum ring is applied against said surface. and therefore as the axial deformation of the portion of the fulcrum ring increases, the portion of the fulcrum ring on the convex surface of the bearing device conforms more closely to the convex surface of the bearing device, and therefore the portion of the fulcrum ring increases in length. A diaphragm spring clutch cover assembly is provided that has a surface that further reduces friction.

According to a fifth feature of the invention, in the clutch cover according to the first feature, said bearing device adjacent to said element is convex on a fulcrum ring which faces against said surface and is convex thereon; During the axial deformation of said part of the fulcrum ring in , the part of said part which is in contact with the convex surface conforms more closely to the convex surface, thereby causing an extension between an element on said part and the convex surface. A clutch cover is provided in which the free length of said portion that resides is progressively reduced.

The gradual reduction of the free length section makes the free length section progressively more rigid and therefore progressively more resilient to deformation.

The aforementioned convex surfaces may be curved or, for example, arcuate, or biplanar or multiplanar.

The invention will now be further described, by way of example and with reference to the accompanying drawings, in which: FIG.

2. In the embodiments and operational drawings, like reference numbers refer to similar or comparable parts.

Referring to FIGS. 1-6, clutch cover assembly 2 includes a dish-shaped cover 4, a diaphragm spring 6, and an annular pressure plate 8. Referring to FIGS.

The cover 4 is a flanged rim 10 for connecting the cover assembly to a rotatably driven drive plate F (shown in dotted lines), which may be a flywheel driven by a motor vehicle engine. It has a flanged rim 10 with holes drilled at 12 to receive bolts B (only one shown). Between the drive plate F and the pressure plate 8 is a driven plate known per se, on which, if desired, it can be mounted in a substantially non-cushioned manner. It is a driven plate having a friction surface E that may be rotated. The driven plate is set at the center hub H, and the shaft spline is connected to the axis X using the driven plate in a known manner.
It has a central hub H which is axially slidably engaged on a shaft (not shown) which is rotatably driven about it (FIG. 2).

In the known manner, the diaphragm spring 6 includes a circumferential dish portion 14 integral with a release lever or finger 16 which extends inwardly in a sword-like manner, separated by a radial slot 18.

The diaphragm spring has a fulcrum arrangement 2 formed by a wire ring held in place by a cover 4.
o and an annular plate 24 which is held on the cover by 22 and rivets 26. Each fulcrum array ring 2o and 22 has a leg 28.30 or 32.34 axially returned at its end to engage into a hole 36 or 38 in the diaphragm spring 6. It is a ring that is divided into two parts.

Diaphragm springs 6 are arranged radially outside the fulcrums 20 and 22.
acts on the fulcrum array 40 on the pressure plate 8.

The pressure plate 8 is connected to the pressure plate 8 by tangential drive dots 42, each of which is bolted to the pressure plate at one end at 44 and riveted to the cover at the other end at 46. rotates around axis X together with cover 4 and drive plate F. The tangential drive stopper 42 is a stacked leaf spring.

FIG. 2 shows the clutch formed using the cover assembly 2 in a fully engaged state, with the diaphragm spring 6 under full load when the driven plate is connected to the drive plate F and the pressure plate. It is shown that it is firmly pressed between 8 and 8. This clutch is of the pressure type, with a release bearing G (known per se) stacking leaf springs 42 in seven directions relative to the cover 4, and a finger 16 biasing the pressure plate in the Y direction. The pressing of the diaphragm spring 6 is of a pressing type in which the load is released when the diaphragm spring 6 is pressed. 5 and 6, the cover assembly is shown in a fully disengaged clutch responsive position.

A fulcrum array 40 centered on the X-axis contains an annular rib 48 on the pressure plate 8 .

This rib has a flat plateau 50 from which a land 52 protrudes. The plateau has a coplanar flat surface 54 that supports a split fulcrum ring 56. The fulcrum ring 56 is made of a resilient material, such as steel wire, and is substantially flat in the unstressed state. ring 5
6 may have any desired cross-sectional shape;
In the drawings, it is shown as a circle. The lands 52 are all substantially the same and spaced apart by substantially equal spacing, and each radially outwardly includes a fulcrum ring 56.
It has a prominent bulge 57 that radially limits the. These projections from face 54 are of a smaller dimension in the axial direction than the thickness of ring 56.

A central path between the land portions 52 is a concave portion 58 extending in the circumferential direction.
and 58'. The recesses 58 are each substantially the same, whereas 58' is circumferentially longer.

Nadles 60 and 60', which may be metal, are substantially U
It is a cross section of a mold and is straddled by a ring.

The saddles 60 are all substantially the same and when the fulcrum ring 56 is substantially unstressed axially, at least one arm of each saddle is centered around its given circle with respect to the other saddles and lands 52. placed above the recess 58 so as to remain in the corresponding recess 58 with circumferentially spaced end walls 59 (FIG. 7) serving as stops for retaining the saddle in a circumferential position. It's dark. As can be seen in FIGS. 2, 3 and 6, each saddle 60 or 60' has one arm that is longer than the other.

One end of the fulcrum ring 56 has a beng 62 which is axially bent at its split and which engages a bore 64 in the base of the recess 58' to inhibit rotation of the ring.
have. Saddle 60' spans a division within ring 56 and is circumferentially longer than the other saddles 60.

Crosspiece 66 of each U-shaped portion of saddles 60 and 60'
provides a distance piece that inflates the fulcrum ring, so the diaphragm spring 6 is the distance piece 6.
It is in contact with 6.

Referring now to FIGS. 7-9 and first to FIG. 7, FIG. 7 shows that the diaphragm spring 6 is fully disengaged by applying zero or a minimum load to the distance piece 66. The situation is depicted schematically. During clutch re-engagement, the release bearing G (FIG. 2) engages the diaphragm spring 6 to apply the coupling load to the driven plate.
is allowed to move in the Z direction because it moves relatively toward the cover 4. This movement of the diaphragm spring initially causes it to press against the nadle 60, 60' in the space between the bearing lands 52, axially in the Y direction in FIG. ', 56''
Transform. The axial deformation stresses the fulcrum ring 56 and causes it to over each bearing land 52.
Provides a tendency to bend axially at 68 in the Z direction.

As one progresses from the situation in FIG. 8 to the situation in FIG. 9 to fully re-engage the clutch, the portion of the fulcrum ring 56 between the lands 52 is deformed further in the Y direction, but still more relatively. Bending 68 of the shaft in the Y direction due to contact by the diaphragm spring moving towards the cover 4
The compression of diaphragm spring 6 additionally makes the cushion of the diaphragm spring harder.

Providing the aforementioned cushion, which may be considered to some extent a two-tiered cushion, may provide a smooth engagement feature to the clutch. Therefore, as shown above,
The clutch cover assembly 2 can be used in conjunction with a driven plate having a non-cushioned friction surface to provide a self-receiving clutch engagement.

Saddles 60 and 80' may be configured to resiliently couple themselves to fulcrum ring 56. The arms of each saddle may be the same length if desired.

A portion 56' of the fulcrum ring 56 extends above each recess 58 to be hung over the gap between adjacent lands 52 towards the other side of each said recess 58.
The portion 56' is substantially a double-ended beam, that is, a double-ended beam each supported at each end by an adjacent land. The two end portions 56'' of the fulcrum ring, on the one hand in which the splitting takes place, are single-sided beams each supported at only one end by a respective land 52 adjacent to a recess 58'. Assuming the same circumferential length as the saddle 60, the connected cantilever 56'' will be less stiff than each beam 56'.

By lengthening the saddle 60', the cantilever 56
The resulting combined stiffness can be made substantially equal for each beam 56'.

The nature and stiffness of the cushioning provided can be varied from one clutch to another, i.e. in the same clutch different classes or stages of cushioning can be achieved by changing the thickness or stiffness of the fulcrum ring. , and/or (ii) by changing the distance between any two adjacent lands 52, and/or (iii)
This may be accomplished by varying the circumferential length of any saddle 60 or 60' and/or (1v) by varying the circumferential length of any surface 54.

As an alternative or addition, fulcrum arrangement 20 (FIG. 2) has in common 40, in which cover 4 spans bearing lands and fulcrum rings on these bearing lands. 40 may be substituted with one having the same features as 40, which is equipped with a bearing land and an opening for receiving the arm of the saddle.

10 to 12, in which the fingers of the diaphragm spring 6 are stretched by a release bearing for releasing the clutch. Referring to the cover assembly, the outermost fulcrum array 140 radially on the cover 4
includes a split fulcrum ring 156 above a bearing land 152 mounted on the cover. The opening 158 in the cover 4 forms a U-shaped saddle 160 whose lateral pieces are flanked by a diaphragm spring 6 .
0 arm is accepted. The condition of the cover assembly in FIG. 11 corresponds to the fully engaged position of the clutch. In FIG. 12, the pressure plate 8 has an annular fulcrum arrangement 8'. As an alternative or in addition, the fulcrum arrangement 8' may be replaced by one similar to 40 in FIGS. 1-9.

There are some difficulties in forming a perfectly flat fulcrum ring in the initial unstressed state. If such a non-flat fulcrum ring is used with a saddle mounted thereon, the fulcrum ring will remain at different points around the fulcrum ring throughout the clutch disengagement. Irregular variations occur in stressing the ring, which results in uneven distribution of the cushioning effect around the fulcrum ring.

In order to avoid or at least reduce that possibility, the modification shown in FIG. 13 can be used.

In FIG. 13, each bolt 344 is longer than the bolt 44 in FIG. Each brace 390 is generally a plate or strip that may extend radially (
end shown mounted in FIG. 13). and each brace 390 has a curved end portion 392 with a curved surface 39 convex to the diaphragm spring 6.
4 has a bent end portion 392. Brace 3 with the clutch in the fully released state
Reference numeral 90 denotes a diaphragm spring 6 which can press on the diaphragm spring which presses on the horizontal piece 66 of the saddle 60' (60) in order to preload the fulcrum ring 56. This preload may be only light. Preload is fulcrum ring 5
6 may be held flat, or in the Y direction at portions 56' and 56'' (Y, 58' and 56'' are shown in FIGS. 7 and 8).
As shown in the figure. ) may produce an initial axial deformation of the fulcrum ring, which may be only a light deformation, or may be of the same axial extent. In this manner, before the clutch enters its re-engagement from a fully disengaged condition, the fulcrum ring portions 56' and 56'' (FIG. 7) spanning the space between adjacent lands 54 will move around the fulcrum ring. are under substantially identical stress conditions to further ensure a more uniform cushioning effect at the brace 39.
The zero surface 394 is in line contact with the diaphragm spring, with the line contacts all lying in a common plane transverse to the axis of the clutch cover assembly. As previously shown, the lands 54 all lie in a common plane transverse to the axis of the clutch cover assembly. The base of the preload due to brace 390 is distance 111
d (not shown).

The clutch is then fully released between the plane of land 54 and the plane of line contact by surface 394 on the diaphragm spring.

Therefore, when the brace 390 is formed and installed so that the fulcrum ring 56 and the combined thickness of the transverse piece 66 and the bellows portion 14 of the saddle are uniform, the fulcrum ring remains flat. In this state, the clutch is held in a flat state in which it is fully released. On the other hand, if the clutch is chosen to be thinner than the above-mentioned combined thickness, the ring portions 56 and 56" (FIG. 7) will be axially can be transformed into

The braces 390 are preferably rigid so that they all apply the same or substantially the same amount of preload to the diaphragm springs, so they are not at all flexible or have very little flexibility. There is no.

The effect of preloading by brace 390 can change clutch take-up characteristics. And cushioning can only begin during clutch re-engagement. The force then exerted between the pressure plate 8 and the diaphragm spring 6 exceeds the preload. The clutch take-up characteristics can therefore be varied as desired by the preload chosen to be exerted by the brace.

While the clutch is disengaged, the brace 390 acts in conjunction with the diaphragm spring to pull back the pressure plate 8.

Therefore, the spring release strap 42 need only produce less pull than when the brace is not used, and therefore the release strap does not need to be as flexible as the brace and is therefore subject to less stress.

In a push type clutch as shown in Fig. 12,
With a brace fixed to the cover 4 and pressing on or in contact with the diaphragm spring 6; such a brace avoiding the pressing plate 8, the fulcrum ring 156 is It may be preloaded.

The clutch cover assembly shown in FIGS. 14-16 incorporates a deformation of a convex surface 70 on the underside of crosspieces 66 and 66' of U-shaped saddles 60 and 60'.

Convex surface 70 may be part of a substantially cylindrical surface. Alternatively, the convex surface 70 can have any other curved or biplanar or multiplanar convex shape.

It is believed that the provision of the convex surface 70 provides better deflection characteristics for the resilient fulcrum ring 56 during clutch re-engagement and a smoother smearing of the deformation of the ring.

When the fulcrum ring 56 is substantially undeformed as shown in FIG. 52 to a point of contact in the direction of the tangent between the fulcrum ring and the convex surface 70 of the element 6o corresponding to the fulcrum ring section 56'. ing.

As the fulcrum ring is deformed axially, each fulcrum ring portion 56' adjacent to the respective element 60 becomes more intimate with the convex surface 70 as the contact points in the tangential direction become increasingly longer line contacts. Match.

In such a position as shown in FIG. 15, the free length of each ring portion 56' becomes L2, which is shorter than Ll.

This shortening of the free length section makes it progressively more rigid. And therefore this shortening of the free length section progressively stiffens the cushion as the fulcrum ring is increasingly deformed axially towards the pressure plate 8. The cushion is further stiffened during axial compression of the curved portion 68 (FIG. 16).

In a further modification of FIGS. 17 and 18, each land 52 has a convex surface 154 against which the fulcrum ring 56 rests.

Surface 154 may be a portion of a substantially cylindrical surface or have any other curved, biplanar, or multiplanar convex shape.

FIG. 17 corresponds to the clutch in a completely disengaged state. In that state, each fulcrum ring portion 56'
contacts the corresponding surface 70 and the curved surface 154 at points substantially tangential to both sides. Each fulcrum ring section thus contains two free length sections, each of which has an angle of 13 degrees. As the fulcrum ring 56 is progressively deformed axially, these free length portions cause the rings to form a surface 70.154 where they and the fulcrum ring 56 are shown in FIG. 56'
The length of each free length portion of is reduced to L4.
Surface 70 with increasing line contact as shown in FIG.
．． 154 becomes progressively shorter by matching more closely to 154. The fulcrum ring becomes increasingly stiffer in deformation as the free length section decreases.

If desired, curved surface 70 in FIGS. 17 and 18 may be replaced by such a flat surface as on element 60 in FIGS. 1-13.

Surfaces 70 and/or 154 may be varied and may be varied from one such surface to another in the same clutch cover assembly to achieve the desired cushioning characteristics.

[Brief explanation of drawings]

FIG. 1 is a plan view of a clutch cover assembly formed in accordance with the first aspect of the invention; FIG. 2 is a plan view of a clutch cover assembly formed in accordance with the first aspect of the invention; FIG. 3 is an enlarged fragmentary view of the cover assembly shown in FIG. 2; FIG. 4 is a cross-sectional view of the cover assembly taken along the line A fragmentary sectional view on IV-IV; FIG. 5 is a graphical plan view on an enlarged scale of a fragment of the pressure plate of the assembly of FIG. 1 showing the fulcrum ring and its straddling elements; FIG. Figure 6 is a partially cross-sectional, fragmentary and graphically developed view of the diaphragm spring in the direction shown in Figure 5, including the diaphragm spring at hand; a fragmentary and graphical development comparable to FIG. 6 in the case where the pressure of the diaphragm spring is not exerted; FIG. 8 is a diagram similar to FIG. Figure 9 is a view similar to Figure 8 showing a further stage in the axial deformation of the fulcrum ring; Figure 10 is a clutch cover assembly formed according to the first feature of the invention applied to a pull-type clutch; FIG. 11 is a fragmentary top view, partially in section, of the cover assembly in FIG. 10 taken from direction XI; FIG. 12 is a fragmentary top view of another embodiment of the article; a graphical sectional view on mxi-xt in FIG. 10; and FIG. 13 is a view similar to FIG. 3 of a variation of the clutch cover assembly in FIGS. 1 to 9; It is. Figures 14, 15 and 16 show variations of the clutch cover assembly of Figures 1 to 9, which variations are formed in accordance with the second and third features of the invention. FIG. 17 is a view similar to FIGS. 7 to 9, respectively: FIG. 17 is formed by the second, third and fourth features of the invention and is completely disengaged; FIG. 18 is a fragmentary and graphical view similar to FIG. 14 of a further modification of the clutch cover assembly corresponding to the clutch in the condition; and FIG. 18 is a clutch engagement resulting in axial deformation of the fulcrum ring FIG. 18 shows the clutch cover assembly of FIG. 17 in its course. In the figure, 2: clutch cover assembly, 4: cover, 6: diaphragm spring, 8: pressure plate, 20
: Second annular fulcrum arrangement, 40: First annular fulcrum arrangement, 52:
Support device, 56: fulcrum ring, 56', 56'': part of fulcrum ring, 60: element, 6o': element, 66: distance piece.

Claims (14)

[Claims] (1) a pressure plate (8), a cover (4), a diaphragm spring (6) for applying a load to the pressure plate, and a first annular fulcrum arrangement (40) on one side of the diaphragm spring; a first annular fulcrum arrangement (40) mounted on the pressure plate; and a second annular fulcrum arrangement (20) on the opposite side of said diaphragm spring, the second annular fulcrum being mounted on the cover. a diaphragm spring clutch cover assembly comprising: an array (20), wherein said diaphragm spring acts between an array of fulcrums; a cushioning arrangement in which at least one of the fulcrum arrays contains a resilient fulcrum ring (56); Annular array bearings (
52), supporting a ring (56) about the axis of the diaphragm spring; and parts (56'), (56'') of the ring, each adjacent to said bearing device (52); parts (56'), (56'') extending into the respective spaces between the bearings (52) and elements (60) straddling the ring at positions spaced around the ring; , 60') and each element (60, 60').
′) respectively at said portions (56′), (56″), and each said element (60, 60′) provides a distance piece for padding the ring (6
0, 60'), and the fulcrum arrangement includes a pressing plate (
During the movement of the diaphragm spring (6) with respect to the cover (4) said respective parts (56'), (56'') exert an increasing load on the diaphragm spring (6).
A diaphragm spring clutch cover assembly characterized in that the distance piece (66) is biased by the diaphragm spring (6) so that the ring (66) is elastically deformed in the axial direction. (2) A clutch cover assembly according to claim 1, in which each said element (60, 60') straddling the fulcrum ring (56) has a substantially U-shaped cross section; A clutch cover assembly characterized in that the distance piece (66) is a U-shaped horizontal piece. (3) In the clutch cover assembly according to claim 1 or 2, the elements (60, 60'
) are mateable by respective stop devices (59) so as to maintain the elements in substantially the same position around the fulcrum ring (56). (4) A clutch cover assembly according to any one of claims 1 to 3, in which at least one of the elements (60, 60') includes a fulcrum ring (5).
6) A clutch cover assembly characterized by being firmly gripped toward the side. (5) A clutch cover assembly according to any one of claims 1 to 4, wherein the fulcrum ring (56) has at least one barb extending therethrough. , and said interrupt is supplemented by said element (60'). (6) In the clutch cover assembly according to any one of claims 1 to 5, one of the elements (6) in the circumferential direction of the fulcrum ring (56)
0') is longer than the other said elements (60). (7) In the clutch cover assembly according to any one of claims 1 to 6, the increase in the diaphragm spring load on the pressure plate (8) after zero or minimum load is as described above. fulcrum ring part (56') (56'')
and at the aforementioned bearing device (52) in the opposite second direction (
A diaphragm spring (6) deforms the bend (68) in the axial direction of the ring by pressing the bend in a first direction (Y). Clutch cover assembly, characterized in that it is adapted to be axially deformed about the ring (56) in said first direction (Y) so as to stress the ring in one or more ways. (8) A clutch cover assembly according to any one of claims 1 to 7, in which the brace device (390) is in contact with the diaphragm spring (6).
) in which the diaphragm spring (6) is preloaded towards the fulcrum ring. (9) In the clutch cover assembly according to any one of claims 2 to 8, the ring (56) is biased by the diaphragm spring (6). With the surface (70) pressed against each said part (56', 56'')
Regarding 6), said surface (70) is convex and said U
on the transverse piece (66) of the mold element (60, 60') and with respect to the ring (56), said convex surface (70) extending substantially circumferentially along the ring (56); and a surface (70) in which at least a portion of the convex surface (70) extends progressively away from the pressure plate.
, 60'). (10) The clutch cover assembly according to claim 9, wherein the portion (5) of the fulcrum ring (56)
Convex surface (70) during axial deformation of
The parts of said portions (56', 56'') that are in contact with the convex surface (70) more closely match the convex surface (70), thereby causing the adjacent said bearing device (52) and the convex surface ( 70) with element (6
0, 60') extending between said portions (56',
Clutch cover assembly characterized in that the free length portion (L1; L3) of 56'') is gradually reduced. (11) A clutch cover assembly according to claim 10, in which the bearing device (52) adjacent to the element (60, 60') has a surface (154). The fulcrum ring (56
) and therefore the portion (56) of the fulcrum ring (56)
′), as the axial deformation of (56″) increases, the portion of the fulcrum ring on the convex surface (154) of the bearing device (52) conforms more closely to the convex surface (154) of the bearing device (52). A clutch cover assembly having a surface that further reduces the length of said free length portion. (12) A clutch cover assembly according to any one of claims 1 to 8, in which the bearing device (52) is adjacent to the element (60, 60').
) is convex on the fulcrum ring (56) which is applied to the surface (154) and against said surface (154), and therein the axial deformation of said portions (56'), (56'') of the fulcrum ring A portion of said portions (56'), (56'') which are in contact with the convex surface (154) throughout the period are in contact with the convex surface (154).
), thereby matching said portion (56') more closely.
), (56″) on the elements (60, 60′) and the convex surface (1
54) extending between said portions (56', 56'')
Clutch cover assembly characterized in that the free length portion (L3) of ) gradually decreases. (13) In the clutch cover assembly according to any one of claims 10 to 12, the free length portion (L1; L3) gradually decreases. A clutch cover assembly characterized in that a portion of the clutch cover is gradually made more rigid against deformation. (14) In the clutch cover assembly according to any one of claims 9 to 13, the convex surfaces (70, 154) are curved, biplanar, or A clutch cover assembly characterized by its multi-plane surface.