JP2000297826A - Clutch disc - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily and inexpensively manufacture a clutch disc, to enable a structure shortened in an axial direction and to guarantee its function. SOLUTION: Friction facings 6, 6a formed on both sides of a friction facing support 3 by flatly coupling a friction material with the friction facing support 3 are molded so as to form a plurality of projecting parts 8, 8a of an axial direction. Between the projecting parts 8, 8a, each valley part 9, 9a viewed from a peripheral direction is formed. The projecting parts 8, 8a formed on both the sides of the friction facings 6, 6a support are relatively shifted and arranged viewed from the peripheral direction. When the friction facings 6, 6a are fastened in the axial direction, axial elastic deformation of the friction facing support 3 is performed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch disc, particularly for use with a motor vehicle friction clutch, which is coupled to a hub by driving (coupled to transmit driving force) and the hub. At least one friction facing support is provided, the friction facing support being provided on both sides with a friction material forming a friction facing.

[0002]

2. Description of the Related Art In the past, mass-produced clutch disks have been used, so-called "facing spring elasticity" in order to enable soft connection or fastening of corresponding friction clutches.
Is set. This facing spring elasticity is usually
It is formed by corrugated spring segments which are axially provided between two separate friction rings. In this case, the two friction rings are connected to the spring segments via rivets.

[0003] Such known arrangements are relatively labor-intensive and expensive. Furthermore, this known configuration requires a relatively large axial installation space. Furthermore, due to the large number of components required, that is to say especially due to the need for rivets, friction facings and spring segments for fixing the facings, the assembly of the corresponding clutch discs is very laborious.

[0004]

SUMMARY OF THE INVENTION It is an object of the present invention to provide an improved clutch disk of the type mentioned at the outset, in particular to provide a clutch disk which can be manufactured more simply and at a lower cost. . Furthermore, the clutch disc according to the invention allows an axially shortened structure,
It is desirable to guarantee impeccable functions. Furthermore, it is desirable for the configuration according to the invention of the friction clutch to reduce the amount of friction material used.

[0005]

SUMMARY OF THE INVENTION In order to solve this problem, in a configuration of the invention, in a clutch disk of the type mentioned at the outset, the friction material is connected in a planar manner to a friction facing support and the friction facing support is provided. Friction facings formed on both sides of the body are formed to form a plurality of axial protrusions, and valleys, recesses, or voids are formed between the protrusions when viewed in the circumferential direction. The protrusions formed on both sides of the friction facing support are arranged so as to be shifted relative to each other as viewed in the circumferential direction, and when the friction facing is tightened in the axial direction, the friction facing support is provided. Is elastically deformed in the axial direction.

[0006]

According to the present invention, the friction unit comprising the friction facing support and the friction facing material is configured to support the friction facing when the friction unit is tightened in the axial direction. The range to be deformed is also elastically deformed.

[0007] The friction facing can advantageously be glued to the friction facing support. However, for many use cases, the friction material is pressed or pressed onto the friction facing support (aupres).
sen) can also be advantageous. This means that the friction facing is formed directly on the friction facing support. That is, in such a configuration, the friction facing is not pre-fabricated as a separate component. The pressure application or press application is advantageously carried out by a hot pressing method.

For the assembly and functioning of the clutch disc, the friction facing support is formed in the form of a ring disc and has at least a substantially flat annular area, in which the friction facing is provided. If provided, it may be particularly advantageous. Advantageously, this annular area forms a ring area which extends in a continuous manner, ie an uninterrupted ring area. However, for some use cases, it may be advantageous if the ring area is divided into individual sectors as viewed in the circumferential direction. The ring range may be constituted by a plurality of components formed in a sector shape.

When the friction material is pressed onto the friction facing support, the friction facing support transfers the friction material forming the friction facing to the friction facing support, particularly in a form-fitting, ie, mating, manner. It may be particularly advantageous to have a plurality of openings and / or protrusions and / or other moldings that allow locking by engagement.

[0010] It may be advantageous for the friction facing support to have a plurality of locking areas for pivoting to another component. These fixing areas may be formed, for example, by radial brackets. These radial brackets may be integrally formed on the inner peripheral surface of the friction facing support and / or on the outer peripheral surface of the friction facing support. These radial brackets, at least at certain points, have a relatively small circumferential extension of the friction facing support to allow elastic deformation of the friction facing support area. May be. The radial bracket may in this case have, starting from a flat annular area of the friction facing support, which supports the friction facing, first a section with a small circumferential extension, and this section is , Into a wider section or base range extending in the circumferential direction. Advantageously, these radial brackets have cutouts that allow connection with another support component. These recesses are advantageously provided in this case in the widened area of the bracket.

The friction material applied to both sides of the friction facing support forms an annular friction facing which, when viewed in the circumferential direction, has a corrugated and / or stepped surface. Forming can be particularly advantageous. However, on both sides of the friction facing support, the friction facings or the friction material forming these friction facings are applied to the friction facing support in such a way as to form facing pads which are circumferentially spaced from one another. Doing so can also be advantageous.

The friction-facing pad or friction-facing section formed in a plaque-like manner is such that, with respect to each other on both sides of the friction-facing support, a facing pad provided on one side of the friction-facing support supports the other of the friction facing support. May be arranged so as to be at least approximately arranged in the range of the gap or gap existing between the two facing pads provided on the side of. The circumferential extension of the facing pads provided on both sides of the friction facing support may be coordinated with one another such that the facing pads partially overlap in the circumferential direction.

The circumferential length of the facing pad provided on both sides of the friction facing support is such that the facing pad provided on one side of the friction facing support has a friction facing support on each of the facing pads. The gap (or recess) between each two facing pads located back to back on the other side of the
It may have a smaller extension length or be coordinated with one another to have an extension length at least equal to the gap.

[0014] In another embodiment of the present invention, the facing length of the facing pad provided on both sides of the friction facing support is such that the facing pad provided on one side of the friction facing support is The facing pads may be coordinated with each other so as to have a greater extension than the gap between each two facing pads, which are located back to back on the other side of the friction facing support.

Advantageously, the friction facing support is manufactured from spring steel. The thickness of the spring steel in this case is 0.2
１．２1.2 mm, preferably 0.25-0.6 mm. For the function of the clutch disc according to the invention, the friction-facing support has, for the maximum pressing force of the friction clutch cooperating with the clutch disc, the friction-facing support on the order of 0.2-1.2 mm, preferably Can be particularly advantageous if they are designed to ensure axial spring resilience on the order of 0.4 to 0.7 mm.

In order to guarantee the good friction properties of the friction facing in the already new state, if the exposed surface is at least partially worked, for example by grinding or blasting, for example by sandblasting,
It can be particularly advantageous. Such treatment of the friction surface is particularly advantageous in friction facings formed by pressing a friction material onto a friction facing support. The partial treatment of the surface of the friction facing is desirably performed at least in an area of the surface that frictionally engages the clutch pressure plate or the counter pressure plate.

Further advantages relating to the function of the clutch disk according to the invention as well as further advantages relating to its construction are described in the embodiments described below.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below in detail with reference to the drawings.

The clutch disc 1 shown in FIGS.
Has an input part 2 which is connected to a friction facing support 3 and is drivingly connected to an output part 5 via a torsional vibration damper 4, i.e. , So that the driving force is transmitted.

The illustrated basic structure of the clutch disc 1 serves only as an example. But,
Friction facing constructed and arranged according to the invention and producing the effect according to the invention (Reibbelag)
Can be used with respect to construction in arbitrarily formed clutch discs having friction facings for tightening between the two plates. Such a clutch disk is known, for example, from DE 197 53 557 A1.
The friction facing constructed and arranged according to the invention and the components supporting this friction facing can also be used, in particular, in "rigid" clutch discs without torsional vibration dampers. Such a rigid clutch disc is known, for example, from DE-A-195 50 620.

The friction facings 6, 6a arranged on both sides of the friction facing support 3 are connected to the friction facing support 3 in a planar manner or over the entire surface. Such a connection can be effected by gluing the friction facings 6, 6a to the friction facing support 3, or by pressing the friction facing support 3 onto the friction facing support 3. Press application of facing compounds or facing mixtures, which can be provided in dry or wet form, is described, for example, in DE-A 44 31 644, DE-A-196 26 688, Germany. DE-A-196 50 451 and DE-A-197 122
The reaction can be carried out as described in the specification of JP-A No. 03. In order to improve the bonding or adhesion of the press-fitted friction facings 6, 6a, the friction facing support 3 may have a surface roughness and / or be provided with a plurality of moldings. Such a shaped part may be formed, for example, by the introduction of an axial notch, a lateral bent part, an embossed part or an axial ridge. If the friction facing support 3 has an axial cutout, the friction facings 6, 6a applied to both sides of the friction facing support 3 are firmly connected to each other via a friction material bridge or connection. obtain.

The friction material compound forming the friction facing must have a composition that allows the friction facings 6, 6a to be elastically deformed. This, on the one hand, causes cracks in the friction facing compound and / or the friction facings 6, 6a detach from the friction facing support 3, ie the connection between the friction facing support 3 and the friction facings 6, 6a is broken. It is desirable to be prevented from being performed.

That is, in the manufacturing process of the friction unit 7 formed by the friction facing support 3 and the friction facings 6, 6a, the friction facing support 3 is firmly connected to the friction facings 6, 6a.
No additional holding or fixing elements, such as rivets, are required. Therefore, regarding the assembly of the clutch disk, the friction facing support 3
And the friction facings 6, 6a form only one component. This component then only has to be assembled with the input part 2 of the clutch disc 1. For this purpose, a rivet connection 2a can be used.

For many applications, the friction-facing support 3 also has an input part 2 or a torque-transmitting part which may be connected to the output hub 5a of the clutch disc 1 radially inside and possibly torsionally. It may be advantageous if the friction facing support 3 is formed to form.

In order to ensure the resilient spring resilience required for gentle starting and transmission shifting (gear shifting), in the embodiment shown in FIGS. A plurality of protrusions 8, 8a
Are formed. These projections 8,
8a, between the valleys 9, 9a or the recessed parts 9, 9a
In this case, the axial profiling or the friction surface structures formed on both sides of the friction facing support 3 by means of the friction facings 6, 6a with respect to each other, in the axial tightening of the friction facings 6, 6a, As shown in FIG. 4, the friction facing support 3 is arranged so as to generate elastic deformation in the axial direction. That is, when the friction unit 7 is tightened, for example, between the friction surface of the flywheel and the friction surface of the pressure plate or pressure plate of the clutch,
A friction surface 10, 10a or friction facing 6, based on a convex or curved configuration of the friction surfaces 10, 10a of the protrusions or friction facing sections 8, 8a formed in a pad or plaque shape. The non-flatness or unevenness in the axial direction of 6a is reduced.

The friction facing support 3 is shown in FIGS.
As can be seen, it is advantageous if it is formed as a component 11 in the form of a ring disk. Advantageously, this component 11 itself is circumferentially closed, that is to say it extends continuously in the circumferential direction.

However, the annular region 12 of the component 11 has elongated cutouts or grooves, which are formed at least when the annular region 12 is deformed in the axial direction. It may also be advantageous to allow some internal stress reduction or some internal stress compensation. In this case, these cutouts may extend straight, bend, or extend in a zigzag or meandering manner. FIG. 5 shows several embodiments of such cutouts by means of broken lines, in which case each cutout is designated by the reference 1.
20, 121, 122, 123, 124, 125, 12
6.

As can be seen in particular from FIGS. 3 and 4, the friction-facing sections 8, 8a formed in the form of pads or plaques are provided with grooves 13 extending in the radial direction.
This groove 13 is formed in each friction facing section 8,
8a is provided in the middle. These grooves 13 can advantageously be formed in the process of pressing the friction material onto the friction facing support 3. However, these grooves 1
3 can also be formed mechanically, for example by milling or sawing. Further, the friction facings 6, 6a or the plaque-shaped friction facing sections 8, 8a forming the friction facings 6, 6a may have a different kind of groove pattern extending in a radial direction, an oblique direction, or a circumferential direction. Good. In particular, the friction facing sections 8, 8a can be provided with a large number of grooves, in which case these grooves are divided into individual areas. By providing a plurality of grooves or recesses in the friction facing sections 8, 8a, the deformability of the friction facing sections 8, 8a can be improved. In this way, cracks in the friction facing sections 8, 8a and / or detachment of the friction facing sections 8, 8a from the friction facing support 3 can be avoided or greater axial deformation and thus increased friction facings can be achieved. Spring elasticity can be enabled. The groove 13 may extend only over a partial range of the friction facing thickness of the friction facing sections 8, 8a. However, it is also possible to form the groove 13 so as to reach the thin plate of the friction facing support 3.

The friction facing support 3 has radial brackets 14 on the radial inside, which brackets 14 are disk-shaped support portions 15 of the input portion 2.
Works to fix the friction unit 7 to Bracket 1
A rivet fastening portion or a rivet connection portion 2a is provided in the range 4.

As can be seen in particular from FIGS. 3 and 4, the plaque-shaped friction facing sections 8, 8 a provided on both sides of the friction facing support 3 are viewed in the circumferential direction of the friction facing support 3. In the area of the gaps or recesses 9, 9 a provided between the two friction facing sections 8, 8 a respectively adjacent to one another, they are provided and formed in such a way that no friction material is present. However, for some use cases, it may be advantageous if there is also a certain thickness of friction material in these gaps or in the area of the gap 15 formed by the recesses 9, 9 a. As can be seen from FIG. 1, in the embodiment shown, a gap 15 is formed between each two friction facing sections 8, 8a which are circumferentially adjacent to each other in the form of a wedge. However, the side edges or surfaces of the gap 15 may extend parallel to each other or at different angles to each other. The pad-shaped friction facing sections 8, 8a may be formed in a circular or elliptical shape.
Extension length 1 in the circumferential direction of friction facing sections 8, 8a
6 is such that in the embodiment shown in FIGS. 1 to 4, the friction facing sections 8, 8a arranged on both sides of the friction facing support 3 are overlapped or overlap by a defined dimension 17. ing. That is, 1
The circumferentially extending length 16 of the two friction facing sections 8, 8a corresponds to two circumferentially adjacent friction facing sections 8; 8a, respectively, which are located back to back on the other side of the friction facing support 3. It is set to be larger than the gap (or retracted portion) 15 between them. However, the circumferential extension 16 of the friction facing sections 8, 8 a is such that the recesses or gaps 9, 9 a located back to back on the other side of the friction facing support 3.
The friction facing sections 8, 8a and the gaps 15 or the gaps 9, 9 are formed so as to be equal to or smaller than the circumferential extension length of the
It can be advantageous even if a is coordinated with each other.

The radius of curvature of the curved friction surfaces 10, 10a is of the order of 140 to 300 mm, preferably of 160 to 300 mm.
Conveniently on the order of 240 mm. However, it should be noted that this radius of curvature is an idealized radius of curvature. This is because the curved shape of the friction surfaces 10, 10a does not need to exactly match the circular sector, but may have a sinusoidal shape, for example. That is, the radius of curvature is formed to be the smallest in the middle range of the friction facing sections 8, 8a when viewed in the circumferential direction,
It is advantageous if the radius of curvature increases towards the circumferential edge region of the friction facing sections 8, 8a. It should be further noted that the curvature varies over the radial extension of the friction surfaces 10, 10a, and in this case in the region radially inside the friction surfaces 10, 10a. 10a is formed with the greatest curvature or curvature, and the friction surface 1
The curvature or curvature of 0, 10a decreases, that is, gradually decreases. That is, this means that the friction surfaces 10, 1
0a has the smallest radius of curvature on the inside in the radial direction,
And it means that it gradually increases outward in the radial direction.

Plaque-shaped friction facing sections 8, 8
a is used, these friction facing sections 8, 8 a correspond to the annular area 1 of the friction facing support 3.
It is advantageous for the two axial sides to occupy an area fraction which is in the order of 30 to 85%, preferably of the order of 50 to 80%. That is, the remaining area is occupied by the gaps or the recesses 9 and 9a.

The friction material applied to the friction facing support 3 is in the order of 3 to 20, preferably of the order of 4 to 9, with respect to the peripheral surface and the formed ridges or recesses or valleys. Advantageously, it is shaped to form a pitch. This means that, for one friction facing 6, 6a, if the friction facing 6, 6a is divided at six pitches over the entire circumference, six equally distributed friction facing sections 8, 8a or friction surfaces 10 are provided. , 10a are formed.

Due to the design according to the invention of the friction unit 7 consisting of the friction facings 6, 6a and the friction facing support 3, the following advantages are obtained: The use of friction material can be significantly reduced. This is because the axial thickness of the friction facings 6, 6a can be reduced.

As a result of the reduction in the required friction material volume, the moment of inertia of the clutch disk with the friction unit 7 according to the invention is also reduced, which is advantageous for the synchronization or switchability of the transmission or transmission. It is.

Assuming the same wear margin, the thickness 18 (FIG. 4) in the tightened state can be significantly reduced. As a result, it is possible to obtain an axial configuration space for the friction clutch to be provided between the internal combustion engine and the transmission. In extreme cases, the tightened thickness 18 of the friction unit 7 can be reduced to 2.5-3 mm. For a standard clutch disc, the axial thickness 18 is on the order of 6.5-8 mm.

[0037] Virtually all the friction material used can be consumed. Because friction facing 6,6
This is because there is no rivet head in the range a that limits or reduces the axial wear of the friction facing.

The facing compound is bonded and / or pressed to form a friction facing support 3;
A high breaking strength is obtained due to the tight bonding to the steel.

The coefficient of friction of a general-purpose friction material is related to the surface pressure; In contrast to a general-purpose clutch disc in which almost 100% of the friction surface is immediately brought into frictional contact during the engagement process of the friction clutch, which changes the surface pressure during the engagement process, according to the present invention, In the formed friction unit 7, the respectively occurring surface pressure can be relatively uniform or substantially constant. This is because the surface in frictional contact during the connection process increases. Thereby, at least equalization of the surface pressure can be obtained. Thereby, a relatively constant friction coefficient characteristic between the friction surfaces engaged with each other can be obtained. In the area of the friction surface of the friction clutch with the clutch disc,
A more constant coefficient of friction characteristic than with a general-purpose clutch disc ensures a reduced tendency to grabbing inside the friction clutch.

The temperature inside the friction facings 6, 6a can be kept at a relatively low level by good ventilation of the friction unit 7 or of the clutch disk provided with this friction unit 7;

The advantages and effects mentioned above are at least partly made possible by the embodiments described below.

In an embodiment which is not shown, the friction facing support 3 may not have a flat shape but may have a specific waveform pattern in the circumferential direction. In this case, the wave pattern may be adapted at least partially to the wave pattern or curvature of the friction facings 6, 6a. That is, for example, in the embodiment shown in FIGS. 1 to 4, the annular area 12 of the friction facing support 3 is formed by the friction surfaces 10, 1 of the two friction facings 6, 6 a.
It may have a wave pattern of 0a or a wave pattern extending at least approximately in the middle with respect to the curvature.
If this corrugated pattern has at least approximately the same size as the corrugated pattern of the friction surfaces 10, 10a, an annular area is formed when the friction facing support 3 is tightened axially between the two plates. 12 is deformed at least prone to a flat state. This means that in such a configuration of the annular area 12, the annular area 12 has a substantially flat shape as shown in FIG. 3 in a tightened state as shown in FIG. Means

Further, the annular area 12 of the friction facing support 3 has only a waveform pattern smaller than the waveform pattern or curvature of the friction surfaces 10, 10a, for example, a waveform pattern corresponding to half of the friction facing waveform pattern. If not, it can be convenient. In such a configuration, when the friction facings 6, 6a are tightened in the axial direction, the annular area 12 is first pressed towards an axially tightened flat state, and then the tightening of the friction facings 6, 6a is continued. If continued, the annular area 12
However, a reverse waveform pattern is formed.

The friction facing support 103 made of a thin plate shown in FIG.
1. The component part 111 has an annular area 112, from which a bracket 114 extending inward in the radial direction extends starting from the inner contour of the annular area 112. These brackets 114
It has a narrow range 127 when viewed in the circumferential direction, and this narrow range 127 is shifted to a circumferentially widened range 128 when viewed inward in the radial direction. In the embodiment shown, the widened area 128 extends in both circumferential directions. Notches 129 are provided in the widened area 128, and these notches 129 allow the friction facing support 103 to be riveted to the damper input portion. A friction facing compound is applied to the annular area 112. Advantageously, this annular area 112 is formed flat. As already mentioned,
At least this annular area 112 has at least one notch 120, 121, 122, 123, 124, 12
5 and 126, these cutouts being arranged preferably evenly distributed over the entire circumference.

The friction facings to be applied to both sides of the annular area 112, for example, the friction facings 6, 6a
However, if they have overlapping areas or overlapping areas (eg, dimension 17 shown in FIG. 3), the annular area 112 has a notch 130 that extends consistently in the axial direction. Can be particularly advantageous. In this case, these cutouts 130 allow a firm connection between the friction facings provided on both sides of the annular area 112. This connection can be made by a friction material forming a friction facing, in which case the friction material extends through the notch 130 and is formed integrally with the friction facing.

FIGS. 6 and 7 show sectional views of a friction unit 107 according to another variant embodiment, in which the friction unit 107 has a sectional view similar to that of FIGS. It is shown.

FIGS. 6 and 7 show that the waveform pattern of the friction facings 106, 106a or the friction surfaces 110, 110a is more exaggerated than it actually is, in order to make it easier to understand the mode of operation or function of the friction unit 107 according to the invention. It is shown in FIG. Friction surface 110, 110a
The configuration or curvature of the shape extending in a sine curve drawn in the illustrated sectional view corresponds to that described with reference to FIGS.

The pitch or interval 135 between two consecutive wave peaks 136 is such that the pitch 135 is 3 to 12 over the entire circumference of the annular area 212 of the friction facing support.
Advantageously, it is set to be present, preferably 4 to 9 times. It may be particularly advantageous if the wave patterns of the friction facings 106, 106a are formed to form 6 pitches or 8 pitches. The friction facing support 203 has a thickness of 0.3-1.5 mm, preferably 0.4-1.5 mm.
Advantageously, it is manufactured from high-strength spring steel having a thickness of 0.6 mm.

The wave peaks 136 of the friction surfaces 110 and 110a
Peaks and valleys 137 (upper saddle) (lower saddle)
Height 231 from the peak of the friction facing 1
In the new state of 06,106a, 0.4-2.5 mm
, Preferably in the order of 0.5 to 1 mm. This height difference 231 is caused by friction facing 106,
It is related to the magnitude of the diameter of 106a, where the height difference also tends to increase as the diameter increases, ie, as the clutch disc gets larger.

FIG. 6 shows the friction unit 107 in a relaxed state. In this state, the friction unit 107 has a total thickness 217 in the axial direction. The friction facings 106, 106a are each other with respect to each other.
And the other friction facings 106a;
Are formed so as to be positioned back to back. However, the wave crest 136 and the wave trough 137 positioned axially back to back may be slightly offset circumferentially with respect to each other.

Such a configuration of the friction surfaces 110, 110a allows the friction facings 106, 106a to be tightened in the axial direction between the clutch pressure plate and the counter pressure plate.
It is ensured that both the axial elastic deformation of 106a and in particular the axial elastic deformation of the annular area 212 of the friction facing support 203 (see FIG. 7). That is, when the friction unit 107 is tightened, the friction surfaces 110,
The axial waveform pattern of 110a is at least reduced, ie, at least partially eliminated.

FIG. 7 shows an idealized tightening state of the friction unit 7. However, actually, the friction surface 11
In the range of 0,110a, at least the valley 137
May still have a “residual waveform shape”. That is, this means that the friction surfaces 110 and 110a are not completely in contact with the corresponding friction surfaces provided on the pressure plate or the counter pressure plate of the friction clutch. This is shown in FIG.
7. The thickness 217 of the unfastened friction unit 107 and the thickness of the unfastened friction unit 107
The difference between the thickness 218 corresponds to the possible friction facing spring travel. Such a friction-facing spring stroke guarantees a gentle starting and a transmission or transmission change. The difference between the two thicknesses 217, 218 is of the order of 0.2 to 1.2 mm, preferably 0.3 to 0.7
Advantageously, it is on the order of mm. Thickness 21 when tightened
8 is a desired wear margin (Verschleissresse
rve). However, the arrangement according to the invention also makes it possible to form a friction unit 107 having a relatively small tightened thickness 218. This thickness 21
8 may be smaller than 5 mm in the new state of the corresponding clutch disc, in this case 2.5-3 mm
Extremely thin disk configurations having a tightened thickness 218 on the order of 10 are also possible. Large vehicles, eg 240
For vehicles with a clutch disc having an outer diameter greater than mm or an increased wear margin as required, the tightened thickness 218 is correspondingly set to a larger value, for example 7 mm or more. can do.

In connection with the embodiment shown in FIGS. 1 to 4, an embodiment not shown has been described in which the annular area 12 of the friction facing support 3 has a corrugated pattern. Annular area 212 of friction unit 107
May also have such a waveform pattern when the friction unit 107 is in a relaxed state.
That is, for example, in FIG.
However, it may have the waveform pattern shown in FIG. In this case, this waveform pattern is shifted by half of the pitch or interval 135 shown in FIG. In that case, FIG.
In the tightened state corresponding to, the annular area 212 has a substantially flat state. Further, an annular area 212
Is the height 23 of the waveform pattern of the friction surfaces 110 and 110a.
It may be advantageous to have a corrugated pattern having an axial height of less than one. In that case, the annular area 21
The second waveform pattern may simply be half the height 231. In such a configuration, the friction facings 106, 1
At the time of the axial tightening of 06a, the annular area 212 firstly
When pressed in the direction of the flattened state tightened in the axial direction and the tightening is continued, the annular area 212 obtains an inverted waveform pattern or a mirror-symmetric waveform pattern. Such a configuration includes friction facings 106, 1
There is the advantage that the shear stress can be reduced at the coupling surface existing in the area between the area 06a and the annular area 212.

In the configuration shown in FIGS. 6 and 7, the waveform patterns of the friction surfaces 110 and 110a are different in the axial direction with respect to the curved shape or geometry of the wave peak 136 and the wave trough 137. Are formed so as to be substantially equal.

In the embodiment shown in FIGS. 8 and 9, the friction facing support 303 has a flat annular area 312 to which the friction material is adhered. Or has been press-coated. This friction material forms a plaque-like area or friction facing pads 308, 308a. A space 317 is provided between two circumferentially facing friction facing pads 308, 308a, each of which is not coated with a friction material or has a small layer thickness. It is covered with. The friction facing pads 308, 308a have, in the embodiment shown, flat friction surfaces 310, 310a. As can be seen from FIG. 9, when the friction unit 307 is tightened, the area having the interval 317 is elastically deformed,
This allows a soft connection or engagement of the corresponding friction clutch. The amount of axial elastic deformation or spring travel 337 is related to the closing force of the corresponding friction clutch and the spring characteristics of the annular region 312. These two
The two characteristic quantities are advantageously matched to one another such that the spring travel 337 is on the order of 0.3 to 1.2 mm, preferably on the order of 0.4 to 0.7 mm. This value is for a clutch disc for a passenger car, and for a lorry clutch disc, this value may be set higher.

Further, the friction facing pads 308, 3
08a, the surfaces forming the friction surfaces 310, 310a are:
It may have at least one small convex curved portion as viewed in the circumferential direction.

FIG. 10 shows the structure of the friction unit 407. In this case, when viewed in the circumferential direction, the dimension 415 of the gap or void 409; 409a is determined by the plaque-shaped friction facing or the friction facing pad 40.
8,408a at least approximately coincides with the circumferential extension length 416. The friction facing pads 408, 408a arranged on both sides of the annular area 412 are positioned in the circumferential direction such that one gap or space 409a;

The embodiment shown in FIG. 11 has the same principle structure as the embodiment shown in FIG. The embodiment shown in FIG. 11 differs from the embodiment of FIG. 8 mainly in the following points. That is, in the embodiment of FIG. 11, the friction surfaces 510, 5a of the friction facing pads 508, 508a.
The surface forming 10a has a convex curvature. Such a curvature is caused by the annular area 51 of the friction unit 507.
Act on the deformed shape of No. 2.

In the friction unit 607 according to the embodiment shown in FIG. 12, a friction facing layer 638 is provided at least partially on the side of the annular area 612 opposite the individual friction facing sections 608, 608a. .
The friction facing layer 638 functions to better fix the friction facings 606 and 606a to the friction facing support 603. To this end, in the embodiment shown, a plurality of axial cutouts 630 are provided in the annular area 612, these cutouts 630 being the other of the friction facing sections 608, 608a and the friction facing support 603, respectively. Serves to form a material bridge between the friction material or friction facing layer 638 that has been press deposited on the side. The thickness of the friction material or the friction facing layer 638 depends on the friction facing layer 63.
8 is set so as not to contact the friction surfaces provided on the clutch pressure plate and the counter pressure plate when the friction unit 607 is tightened. As can be seen, the thickness of the friction facing layer 638 depends on the friction facing pad or friction facing section 60.
It is formed smaller than the thickness of 8,608a.

The friction unit 707 according to the embodiment shown in FIG. 13 is different from the embodiment shown in FIG. 6 mainly in that the wavelength 739 of the crest 736 is larger than the wavelength 740 of the trough 737.
It is different in that it is formed shorter.

In the friction unit 807 according to the embodiment shown in FIG. 14, the wavelength 840 of the trough 837 of the friction surfaces 810, 810a is changed to the wave peak 836 of the friction surfaces 810, 810a.
Is formed so as to be shorter than the wavelength 839.
As can be seen from FIG. 14, the friction surfaces 810, 810a have the smallest curvature of the friction surfaces 810, 810a in the middle area of the wave peak 836, and this curvature is the wave peak 83
6 is formed so as to gradually increase toward the edge range.

The friction unit 907 according to the embodiment shown in FIG. 15 is mainly different from the embodiment shown in FIG.
The friction facing layer 938 of friction material provided between two circumferentially facing friction facing sections 908, 908a, respectively, differs in that it has a curved outer surface 941. Based on the appropriate configuration of the friction facing layer 938 that does not participate in actual frictional engagement, the friction unit 907 during axial tightening
Can have an effect on the deformation characteristics. 12 between the individual friction facing sections 908, 908a and the friction facing layers 938 located back to back on these friction facing sections 908, 908a, respectively.
Again, a friction material bridge may be provided.

By providing a friction facing layer 938 of friction material between adjacent friction facing sections 908, 908a, the friction facing 9
The thermal properties of the annular area 912 supporting the 06,906a can also be improved. In particular, non-uniform thermal expansion of the annular region 912 can be sufficiently prevented or reduced. Thus, the annular area 9
Twelve distortions can also be avoided or at least reduced.

The friction unit according to the invention has, with regard to its axial spring characteristic, the axial residual spring resilience in the fully closed state of the friction clutch in cooperation with the respective friction clutch. (Rest
federung). The spring rate or spring constant of this residual spring elasticity is preferably 2
It may be on the order of × 10 ⁴ N / mm to 10 × 10 ⁴ / mm.

Furthermore, by providing grooves in the friction facing material, the elastic deformation characteristics of the friction unit can be changed and thus adapted to individual use cases.

Further, by appropriately distributing the waveform pattern over the entire circumference, the vibration characteristics of the friction unit can be affected.

For some use cases, it may be advantageous if the corrugated pattern of the friction surfaces, for example friction surfaces 110, 110 a, is formed such that wave peaks 136 having different heights 231 are formed. . That is, for example, two types of wave crests 136 having different heights 231 can be provided. In this case, the individual crests 136 having different heights 231 may be alternately arranged in the circumferential direction. Therefore, when the corresponding friction clutch is closed, first the large height 23
The wave crest 136 having one is used, and is then offset in time with respect to this by a small axial height 23.
The wave crest 136 having one acts.

Furthermore, the friction-facing support, for example the friction-facing support 3,103, may be formed of a plurality of parts, for example, three or four segmented thin plate parts.

The facing compound which forms the friction facing advantageously has at least small elastic properties, which allow compensation of the stresses which occur during deformation of the friction facing, so that cracks inside the friction facing are possible. In addition, breaking and / or peeling of the friction facing from the friction facing support can be avoided.

Advantageously, the friction facing compound can be admixed with at least one of the following additives: resin having a high modulus or a relatively small E-module; relatively high Rubber materials with elastic modulus,-Silicon compounds with relatively high temperature stability,-Ceramics with relatively high temperature stability,-Sintered materials with relatively high strength.

The embodiments described so far have circumferentially divided friction ranges and, between these friction ranges,
Friction units 7, 107, 307, 407, 507, at least with valleys or recesses or gaps provided at least when the friction unit is not loaded.
607, 707, 807, and 907.
However, the elastic deformation according to the invention of the friction facing support, based on the special configuration of the friction material applied to the friction facing support, means that the corrugated pattern or the unevenness of the friction surface is radial in relation to the friction facing support. It can also be done to extend. This means that in such a configuration, for example, FIGS.
It is meant to correspond to a sectional view of the friction facing support along the line.

The present invention is not limited to the above embodiment. On the contrary, many variations and modifications are possible within the framework of the arrangement disclosed herein.

[Brief description of the drawings]

FIG. 1 is a partial view of a clutch disk according to the present invention.

FIG. 2 is a sectional view taken along the line II-II in FIG.

FIG. 3 is a sectional view taken along line III-III in FIG. 1;

FIG. 4 is a sectional view showing the friction facing shown in FIG. 3 in a state where it is tightened in the axial direction.

FIG. 5 is a schematic diagram showing another embodiment of a friction facing support for use in a clutch disc according to the present invention.

FIG. 6 is a sectional view showing another embodiment of the friction unit in a relaxed state.

7 is a sectional view showing the friction unit shown in FIG. 6 in a tightened state.

FIG. 8 is a sectional view showing still another embodiment of the friction unit in a relaxed state.

FIG. 9 is a cross-sectional view showing the friction unit shown in FIG. 8 in a tightened state.

FIG. 10 is a sectional view showing still another embodiment of the friction unit.

FIG. 11 is a sectional view showing still another embodiment of the friction unit.

FIG. 12 is a sectional view showing still another embodiment of the friction unit.

FIG. 13 is a sectional view showing still another embodiment of the friction unit.

FIG. 14 is a sectional view showing still another embodiment of the friction unit.

FIG. 15 is a sectional view showing still another embodiment of the friction unit.

[Explanation of symbols]

1 clutch disc, 2 input part, 2a rivet connection part, 3 friction facing support, 4 torsional vibration damper, 5 output part, 5a output hub,
6,6a friction facing, 7 friction unit,
8,8a protrusion or friction facing section,
9, 9a valleys or recesses or voids, 1
0, 10a friction surface, 11 component, 12 annular area, 13 groove, 14 bracket, 15 support part or gap, 16 extension length, 17 dimensions,
18 thickness, 103 friction facing support,
107 friction unit, 106, 106a friction facing, 110, 110a friction surface, 111 component, 112 annular range, 114 bracket, 120, 121, 122, 123, 124, 12
5,126 notch, 127 narrow range, 129
Notch, 130 Notch, 135 spacing or pitch, 136 Wave ridge, 137 Wave valley, 203
Friction facing support, 212 annular area,
217 thickness, 218 thickness, 231 height difference,
303 friction facing support, 307 friction unit, 308, 308a friction facing pad,
310, 310a friction surface, 312 annular area, 3
17 spacing, 337 spring stroke, 407 friction unit, 408, 408a friction facing pad,
409, 409a gap or gap, 412 annular area, 415 dimensions, 416 extension length, 50
7 Friction unit, 508, 508a Friction facing pad, 510, 510a Friction surface, 512
Annular area, 603 friction facing support, 6
06,606a friction facing, 607 friction unit, 608,608a friction facing section,
612 annular area, 630 notch, 638
Friction facing layer, 707 friction unit, 73
6 Namiyama, 737 Nami, 739 wavelength,
740 wavelength, 807 friction unit, 810,
810a Friction surface, 836 Wave peak, 837 Wave peak, 839 wavelength, 840 wavelength, 906
906a friction facing, 907 friction unit, 908, 908a friction facing section, 9
12 annular area, 938 friction facing layer,
941 Outside

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Wolfgang Reich Germany Bühl-Zonharde 8 (72) Inventor Oliver Runge Bühl Beethoven Straße 2 (72) Inventor Hans-Dieter Ellison Bühl Köttenmaut, Germany G17 (72) Inventor Karl-Ludwig Kimmich Ottenhofen Schlossberg, Germany 15

Claims (21)

[Claims] 1. A clutch disc, particularly for use with an automotive friction clutch, comprising: a hub; and at least one friction facing support drivingly coupled to the hub and annularly surrounding the hub. In a type in which a friction material that forms friction facing is provided on both sides of the friction facing support, the friction material is planarly coupled to the friction facing support,
The friction facings formed on both sides of the friction facing support are formed so as to form a plurality of protrusions in the axial direction, and valleys are formed between the protrusions as viewed in the circumferential direction. The protrusions formed on both sides of the friction facing support are disposed so as to be shifted relative to each other as viewed in the circumferential direction, and when the friction facing is tightened in the axial direction, the shaft of the friction facing support is A clutch disk characterized in that elastic deformation in a direction is performed. 2. The clutch disc according to claim 1, wherein the friction facing is bonded to the friction facing support. 3. The clutch disc according to claim 1, wherein the friction material is pressed onto the friction facing support. 4. The clutch disk according to claim 3, wherein the pressing is performed by a hot pressing method. 5. The friction facing support according to claim 1, wherein the friction facing support is formed as a ring disk and has at least a substantially flat annular area, the annular area being provided with friction facing. 5. The clutch disk according to any one of the items up to 4. 6. The clutch disk according to claim 5, wherein the annular area forms a consistently extending (uninterrupted) ring area. 7. The friction facing support according to claim 1, wherein the friction facing support has a plurality of openings and / or protrusions for fixing a friction material forming the friction facing. Clutch disc. 8. The clutch disc according to claim 1, wherein the friction facing support has a plurality of fixing areas for pivoting to another component. 9. The fixing area is formed by a radial bracket, the bracket having a small circumferential extension at least at a predetermined location.
The described clutch disc. 10. The clutch disc according to claim 9, wherein the radial bracket is provided radially inside the friction facing and / or radially outside the friction facing. 11. A radial bracket defining a section of the friction facing support, starting from a flat annular area supporting the friction facing, first having a small circumferential extension length, and 2. The method according to claim 1, wherein the section transitions into a wide base region extending in the circumferential direction.
The clutch disc according to any one of claims 0 to 0. 12. The clutch disc according to claim 11, wherein a cutout for the coupling element is provided in the base area. 13. The friction material applied to both sides of the friction facing support forms an annular friction facing, the friction facing having a corrugated surface and / or stepped in a circumferential direction. The clutch disk according to any one of claims 1 to 12, which forms a surface. 14. The friction material forming a friction facing forms a facing pad circumferentially spaced from each other on both sides of the friction facing support. The clutch disc according to claim 1. 15. A facing pad provided on one side of the friction facing support, within a range of a gap (gap) existing between each two facing pads provided on the other side of the friction facing support. 15. The clutch disc of claim 14, wherein facing pads provided on opposite sides of the friction facing support are positioned relative to each other such that each is at least approximately positioned. 16. The circumferential extension of facing pads provided on both sides of the friction facing support so that the facing pads provided on both sides of the friction facing support partially overlap in the circumferential direction. The clutch disc according to claim 14 or 15, wherein the clutch disc is matched. 17. A facing pad provided on one side of the friction facing support having a gap between each two facing pads, each of which is located back to back on the other side of the friction facing support. The circumferential extension lengths of the facing pads provided on both sides of the friction facing support are coordinated with each other so as to have a small extension length or an extension length at most equal to the gap. The clutch disk according to claim 14, wherein the clutch disk is provided. 18. A facing pad provided on one side of the friction facing support, wherein the facing pad is disposed on the facing pad with a gap between each two facing pads located back to back on the other side of the friction facing support, respectively. The circumferential extension lengths of the facing pads provided on both sides of the friction facing support are coordinated with each other so that the friction extension support members also have a large extension length.
17. The clutch disk according to any one of items 1 to 16. 19. The friction facing support according to claim 19, wherein
19. The clutch disc according to claim 1, comprising a spring steel having a thickness of 1 mm, preferably a thickness of 0.25 to 0.5 mm. 20. The axial spring elasticity guaranteed by the friction facing support is in the order of 0.2 to 1.2 mm, preferably in the order of 0.4 to 0.7 mm. The clutch disk according to any one of the above. 21. A clutch disc according to claim 1, wherein the exposed surface is at least partially over-ground after press application of the friction material to the friction facing support. .