ITMI970702A1 - FRICTION GASKET IN PARTICULAR FOR A CLUTCH OR BRAKE DISK AS WELL AS A CLUTCH DISK EQUIPPED WITH IT - Google Patents

Description

DESCRIPTION

The invention relates to a friction lining, in particular for clutch plates, brakes or the like, respectively, clutch plates, brakes or the like, equipped with it. Furthermore, the invention relates to a friction lining, in particular for friction discs or brakes, for example for motor vehicles, which is substantially configured in the form of a circular ring and consists of a supporting element substantially in the form of a circular ring as well as material of friction.

Such friction linings are known according to the state of the art. Friction linings in which the friction material is applied on one side to a support element exhibit, in the case of given friction lining mixtures, a different thermal expansion and / or expansion due to moisture absorption from the friction material and from the support element. This fact can cause the friction seal, due to these expansion conditions, to deform in the shape of a vessel or cup or to rise, so that it loses its planar or flat configuration.

It is the object of the invention to provide a friction lining as well as a friction plate with a friction lining which is simply and economically manufacturable and exhibits only minimal or no twisting phenomena. Furthermore, such a friction lining in its characteristics must satisfy certain requirements concerning the bursting resistance and the rigidity, as well as concerning the friction and wear characteristics.

According to the invention, in the case of a friction lining, in particular for friction discs or brakes, for example for motor vehicles, which is substantially configured in the form of a circular ring and consists of a support element substantially in the form of a circular ring as well as from friction material, this is achieved by the fact that the friction lining consists of both the support element and the friction material substantially including this support element, the friction lining has areas of absorption or deformation for the fixing the friction lining on a fastening element, where the supporting element substantially in the form of a circular ring is arranged substantially in the center of the friction lining, considered in the axial direction.

In such a friction lining it can be advantageous for the support element to have a base region substantially in the form of a circular ring, which is arranged substantially in the center of the friction lining, considered in the axial direction.

It is also advantageous if the friction material of the friction lining, considered in the axial direction, is applied or present both in front of and behind the base region of the supporting element substantially in the form of a circular ring. With this it is obtained that the support element is arranged substantially between a front and a rear friction lining layer.

In the case of a friction lining according to the invention, it is advantageous if the expansion, considered in the axial direction, of the friction lining layer, in front of the base region of the support element is substantially equal to the expansion, considered in the axial direction, of the friction lining layer behind the support member.

Furthermore, it can be advantageous if the expansion dj, considered in the axial direction, of the friction lining layer in front of the base region of the support element is substantially greater than the expansion d2, considered in the axial direction, of the friction lining layer behind the support element. In this case it may be appropriate that the ratio between the expansion dj and the expansion d2 is in the range from 4 to 1, preferably in the range from 2 to 1. This means that the friction lining layer, which serves as the friction surface is four to one time thicker than the rear side of the friction lining.

It may be appropriate that the expansion d ^ of the friction lining layer in front of the base region of the support element, considered in the axial direction, is substantially less than the expansion d2 of the friction lining layer behind the support element, considered in the axial direction. In this case it can be advantageous for the ratio between the expansion dj and the expansion d2 to be in the range from 1 to 0.3, preferably from 1 to 0.5.

According to the inventive concept, in the case of a friction lining in particular for friction discs or brakes, for example for motor vehicles, which is substantially designed in the form of a circular ring and consists of a support element in the form of a circular ring as well as of a friction material substantially encompassing this support segment, with absorption and / or deformation zones for fixing the friction lining on a fastening element, it may be advantageous for the substantially circular ring-shaped support element to have a circular ring-shaped base region and at least one further region, which has an expansion in the axial direction, so that this region protrudes axially with respect to the circular ring-shaped base region of the support element.

Similarly, it may be suitable for the radially outer edge region of the support element in the form of a circular ring to project in an axial direction with respect to the base region of the support element. Furthermore, it may be suitable for the radially inner edge region of the support element in the form of a circular ring to project in an axial direction with respect to the base region of the support element. The radially inner or outer edge region of the support element can project with different or equal length in the axial direction.

Furthermore, it may be appropriate that in the base area of the support element in the form of a circular ring at least one area is configured convex, raised or deformed in the shape of a pot, so as to protrude with respect to the base area of the support element in the direction axial. These areas can be used for fastening, as riveting, the friction lining on a fastening element, where it is appropriate that the area has at least one opening. The bottom area can be done by softening in a suitable way.

Furthermore, it may be appropriate that at least two areas of the base region of the support element in the form of a circular ring, which project in the axial direction, are uniformly distributed, considered on the perimeter of the support element in the form of a circular ring. It may be advantageous that, in the base region of the support element in the form of a circular ring, at least one region projecting in the axial direction is configured substantially in a circular or oval shape. In particular, it may be appropriate that, in the base region of the support element in the shape of a circular ring, at least one region projecting in the axial direction is configured substantially in a polygonal shape, such as square or rectangular.

According to the inventive concept, it can be advantageous if, in the base region of the support element in the form of a circular ring, at least one region projecting in the axial direction, considered in the peripheral direction, has a contour in the shape of a circular ring. In this case, the at least one area projecting in the axial direction in the form of a circular ring should be arranged coaxially with respect to the axis of the friction lining.

It can be advantageous if openings, such as punched, perforated or perforated, are made in the base region of the support element in the form of a circular ring. Furthermore, it may be desirable if edge areas of at least one opening in the support element in the form of a circular ring are raised in the axial direction.

Furthermore, it can be advantageous if openings, such as holes, with different cross-section or with different extension are made in the base region of the support element in the form of a circular ring.

Similarly, it may be appropriate if the areas which project in an axial direction with respect to the base area in the form of a circular ring of the support element have openings.

According to the inventive concept it may be appropriate if the extension of the support element in the form of a circular ring, considered in the radial direction, is smaller than the extension of the friction lining, considered in the radial direction. Similarly, it may be appropriate if the extension of the support element, considered in the radial direction, is smaller than the radial extension of the friction lining, but greater than 1/4 of the radial extension of the friction lining. Furthermore, it may be appropriate if the extension of the support element in the form of a circular ring, considered in the radial direction, is equal to the extension of the friction lining, considered in the radial direction.

According to the invention, it is appropriate if the extension of the support element in the form of a circular ring, considered in the radial direction, is greater than the extension of the friction lining, considered in the radial direction.

According to the inventive concept it may be appropriate if the substantially circular ring-shaped support element is made of metal, such as for example steel or aluminum. Similarly, it is desirable if the substantially circular ring-shaped support element is made of plastic, such as for example fiber-reinforced plastic, for example glass-fiber reinforced.

According to a further inventive concept, in the case of a friction plate, in particular for a friction clutch, which carries on its outer perimeter at least one friction lining, with an inlet piece or part, such as a driving plate, which is possibly rotationally resistant connection with a driving disc and counter disc form the input piece of a torsional vibration damper, where a component in the form of a circular ring, such as a flange, serves as the output piece of the torsional vibration damper and transmits a torque transmissible from the output side directly, or possibly via an additional torsional vibration damper, to the clutch disc hub, where a torsional vibration damper can be provided between the flange and the clutch disc hub, for example for the range of idle operation, it may be appropriate that the friction linings of the friction plate, which serve as a piece inlet, consist of a support element and a layer of friction linings, and the support element is arranged substantially in the center of the friction lining, and the support element has areas which protrude in a radial direction with respect to a base area of the support element.

Similarly, in the case of a friction plate, in particular for motor vehicles, it can be advantageous if the friction linings of the friction plate are designed according to one of claims 1 to 27.

The invention has been illustrated in more detail with the help of the figures.

In this case:

Figure 1 shows a representation of a section of a friction plate,

figure 2a shows a section of a friction lining, figure 2b shows a section of a friction lining, figure 3 shows a view of a friction lining,

figure 4a shows a supporting element of a friction lining,

figure 4b shows a section of a support element according to figure 4a,

figure 4c shows a section of a support element according to figure 4a,

figure 4d shows a section of a support element according to figure 4a,

figure 5 shows a supporting element of a friction lining,

figure 6 shows a support element of a friction lining,

figure 7a shows a supporting element of a friction lining,

Figure 7b shows a section of a partial area of Figure 7a, Figure 7c shows a section of a partial area of Figure 7a, Figure 7d shows a representation of a detail of Figure 7a,

figure 8 shows a supporting element of a friction lining,

figure 9a shows a section of a friction lining, figure 9b shows a section of a friction lining, figure 9c shows a section of a friction lining, figure 10a shows a view of a friction lining, figure 10b shows a view of a friction lining, Figure 10c shows a section of two mo te friction linings, and

Figure 10d shows a section of two mounted friction linings.

Figure 1 shows a friction disc 1 with friction linings 2 substantially in the form of a circular ring, arranged radially externally, where two friction linings are arranged substantially coaxially with respect to each other, where the friction surfaces 2a and 2b they face away from each other in the opposite direction. The friction linings 2 are elastically connected to each other by means of springing or elastic elements, such as spring segments 3, where a fastening of the friction linings on the driving disc 4 can be ensured by means of the elastic elements, such as spring segments 3. spring segments, in their radially inner zone 3a are connected to the pad holder by means of a riveted connection 5, for example. rotation with a counter disk 6. The connection resistant to rotation between the driving disk 4 and the counter disk 6 can be obtained, for example, by means of spacers 7, which, in their outer zone 7a, 7b are subjected to a deformation of the material for fixing the driving disk and of the counter disc.

With load of force accumulators 8, which are arranged in the peripheral direction and in windows of the pad holder and counter disk, a component, such as a component 9 in the form of a circular ring, such as a flange, is arranged in such a way that the accumulators of force are housed in windows 10 of the flange. Upon rotation of the flange 9 with respect to the driving disk and the counter disk 4, 6, the force accumulators 8, considered in the perimeter direction, are stressed. In the radially inner zone of the flange 9, a further torsionall vibration damper 11 can be arranged, where the output piece of the second torsional vibration damper 11, such as an idle damper, respectively of the flange, is in connection with the output, as hub 12, of the clutch disc, where between flange 9 and hub 12 there may be a rotation play with or without stress of the force accumulators 13 of the torsional vibration damper 11.

The friction plate can also provide friction devices, such as for example friction elements, such as friction rings or friction plates 14, 15 and 16. The friction plates 14, 15 and / or 16 are stressed in the axial direction by force accumulators 17, 18, such as for example disc springs, to obtain a friction effect in the event of a relative rotation between the friction surfaces of the friction rings and the counter friction surfaces. In this case, the friction rings generally have a form-fit or force-fit connection with a bearing element, where they are rotatably formed in the region of the friction surfaces. The friction ring 15 can perform, for example with respect to the flange 9, a sliding or sliding movement, where the friction ring is normally performed integral with rotation with the cup spring 17, which engages in windows of the counter disc and is therefore held to be non-rotatable.

Figure Za shows a section of a friction lining 2 according to the invention, where the friction lining has a friction surface 2a and a surface 2c opposite the friction surface. The friction surface 2a comes into frictional engagement with a friction counter surface, where the side surface 2c of the friction lining comes into contact, for example, with a spring segment 3. The friction lining 2 is substantially made of friction material 100 and from a support element 101. The support element 101 has a zone in the form of a circular ring, such as a base zone, 102, which in the edge zones 103 and 104 is bent at an angle or bent or deformed in the axial direction . The circular ring-shaped element 102 further has openings 105, through which friction material extends or 1 in which friction material is located, where the friction material of one side 106 is joined with the friction material of the other. side 107, considered with respect to the element 102 in the form of a circular ring. For example, a friction surface of a flywheel or a clutch pressure plate can serve as the counter friction surface.

In the edge areas 103, 104 bent at an angle of the support element, openings or holes 104a can also be made, where these openings serve for joining and bonding the radially outer edge layers of the friction lining. This is advantageous since the connection or union between the friction material and the support element is usually not as good as between regions of friction material.

The radially inner and radially outer angled areas 103 and 104 of the support element 102 of the friction lining 2 can simultaneously serve as spacers. The spacer function of the elements 103 and 104 can be caused by the fact that the element 102 is inserted in an implant or device for the compression of the friction linings 1 so that the element 102 rests on the surfaces 103a and 104a and subsequently is added in a metered manner the friction material to the side 106 for this purpose. This can happen when the material of the side 107 has already been introduced before in the system. However, it can also be advantageous if the friction material comes through openings in the area 106, for example it flows.

In addition, in the circular ring-shaped element of the seal carrier 102, at least one zone 110 is formed or configured in such a way that, for example, by drawing or deforming the material, a vessel-like camber, a lift or a depression of the material. This zone is performed as an absorption or deformation zone to fix the friction lining. In the area of the cup-like or deep-drawn crown 110 there is also an opening 111, which is used to connect the friction lining 2 with a retaining element, for non-pivotally connecting the friction lining, for example with a clutch disc . A riveted connection can engage in the opening 111 of the drawn zone 110, to connect the friction lining 2 with a spring segment 3.

The element 102 in the shape of a circular ring, like the support of the gasket, is made in such a way that the area 102 in the shape of a circular ring, thanks to the spacing effect of the end areas 103 and 104, is substantially arranged in the central area of the friction lining, considered in the axial direction, so that the thickness d ^ of the friction lining layer in front of the circular ring-shaped area is substantially equal to the thickness of the friction lining layer behind the circular ring-shaped element 102 . The thickness D of the friction lining is therefore divided into the thickness dp by the thickness d2 and the material thickness d of the element 102. The thickness d1 in the new layer can be substantially equal to the thickness d2, where the thickness d ^ however can also assume be equal to one third to four times the thickness d2. The element 102 is substantially a metallic element made of steel or other metal, such as for example aluminum or non-hardened iron, or a plastic element with or without fiber reinforcement, where the thickness d is in the range between 0.1 imie 2 mm, preferably in the range from 0.2 to 1 mm. When using steel, a thickness d of 0.1 mm to 0.6 IM can be advantageous. Preferably, a thickness of the support of the gasket or of the sheet of 0.2 mm or 0.25 to 0.4 mm can be used.

It is particularly advantageous for the friction lining if the thickness d1 in the new layer is substantially equal to the thickness d2, thus ensuring that the friction lining does not deform or bump at all due to thermal expansion, or that this only occurs to a minimal extent. In case of suitable friction material, however, thickness ratios dj / dz from 4 to 0.33 are suitable.

The areas 103 and 104 bent at an angle, facing axially, also serve to increase the bending stiffness of the friction lining.

The radial extension of the friction lining, as shown in Figure 2a, can be greater than the radial extension of the circular ring-shaped element 102, such as the seal holder. In figure 2b the radial extension of the friction lining 2 is equal to the radial extension of the support of the seal 102. Similarly it can be advantageous if the support of the seal 102 for example in the radially internal area protrudes beyond the friction lining, to make it possible to the friction lining in the area of these protruding areas a fastening with for example a pad holder.

Furthermore, in Figures 2a and 2b a groove 120 can be recognized, which is made in the friction lining, in order to be able to remove rubbing dust, which forms due to abrasion of the friction lining, from the area of the friction surfaces. This groove can be made, in the case of gaskets made of compressed material, with a compression process. In addition, grooves can also be made in the radial direction.

Figure 2b shows lines 121 and 122, which in the region of the cup-shaped deformed zone 110 of the opening 111 provide a recess in the friction material of substantially circular configuration, to obtain a riveting of the gasket in the deformation zone 110. friction with a friction lining support, such as a spring segment. The free recess 121 serves to house the head of the rivet 121a.

Figure 3 shows a friction lining in one view, where the friction lining 200 is made as an element in the form of a circular ring, which has openings 201 and recesses 202 with central openings 203 distributed in the peripheral direction. The recesses 202 with central opening 203 serve to fasten, as riveting, the friction lining with a support element, such as a spring segment 3. The openings 201 serve for an opposite friction lining to be fastened, as riveted, with a support element, such as for example a spring segment, where a tool for riveting can engage through this opening 201.

The surface of the friction lining is divided into segments 204 and 205, which are divided by grooves 206 and 207. The groove 206 is a substantially circular or elliptical ring-shaped groove in the peripheral direction of the friction lining, as already indicated in the figures 2a and 2b with 120. The grooves 207 extend substantially in the radial direction, where a clockwise or counterclockwise overturning of the groove can be advantageous. The grooves serve to remove any material of the friction lining that may have formed due to wear, such as dust, from the area of the friction surfaces. The depth of the groove is only a fraction of the thickness of the friction lining layer, for example 0.5 rrm up to 2 mm.

The advantageous embodiment groove 206 is not ideally circular in shape, but at least slightly elliptical or has another shape other than a circular ring, so that the sliding rubbing powder carried therein does not rub or always wear the same surface on the friction counter surface.

Figure 4a shows a view of a gasket support 220, as a support element, which in the radially outer region 221 and in the radially inner region 222 is angled in the axial direction. The areas 221 and 222 bent at an angle, which are bent at an angle preferably in the axial direction, correspond to the areas 103 and 104 in Figures 2a and 2b. In addition, similarly cup-like convex zones 223 with a central opening 224 are distributed in the perimeter direction of element 220. In addition to these cup-like convex zones 223, openings 225 are distributed around the perimeter of the support element. gasket 220. The cup-like convex zones 223 with the central opening 224 of this zone serve for riveting the friction lining onto a friction lining support, such as a spring segment, where the openings 225 serve for the fastening and riveting of an opposite friction seal. The head of a rivet is housed in these areas.

The depth of the cup-like convex zones 223 substantially corresponds to the extension of the zones 221 and 222 bent at an angle in the axial direction, so that thanks to the depth of the zones 223 and the extension, considered in the axial direction, of the zones 221 and 222 a spacing function is ensured, which in the manufacture of the friction lining ensures that the sealing support element 220 is formed in a central region of the friction lining, considered in the axial direction.

However, the depth of the cup-like zone can also be greater or less than the axial extension of the angled zones, so that the gasket support, as a support element, rests on one side only on the cup-like zones or on the folded zones at an angle or on both, when it is on a base, as for example in a gasket press. Furthermore, on the radially outer perimeter 220a and on the radially inner perimeter 220b it is recognized that openings 226 and 227 are arranged in regular or irregular arrangement. These openings 226 and 227 serve so that the friction lining layer made of the friction lining material can form a connection between the layers of the friction lining in the axial direction to the right and left of the friction lining support. Thus a considerably better connection between the two sides can be achieved, and the element 220 can be advantageously bonded and connected with the friction lining material. The openings 226, 227 can also be arranged in the corner region.

In addition, openings 230 can be recognized in the central region of the seal carrier, which are designed correspondingly to the openings 226 and 227 and for the best connection of the friction lining layers are arranged in front and behind, respectively to the right and left of the seal holder. friction. Similarly, openings 231 can be recognized with raised edge regions, which serve so that the friction material can mesh better with the supporting element of the friction lining. The raised edge areas can be raised in such a way as to have the same axial extension as the areas 221, 222.

Figure 4b shows an area corresponding to the line I-I of Figure 4a, where the edge areas 221 and 222 are represented and the openings with edge areas 231 raised in section can be recognized. Figure 4c shows a section of Figure 4a corresponding to line II-II, where the edge areas 221 and 222 as well as the openings 227 and 226 are represented. opening 224.

Figure 4d shows a section corresponding to Figure 4a, where the section has been made along the line III-III. The edge areas 221 and 222 as well as the opening 225 are recognized.

Figure 5 shows a further embodiment of a gasket support element 300 with a radially outer edge region 301 and a radially inner edge region 302. In the radially outer edge region, openings 303, as well as openings 304 in the radially inner edge region, are formed as punched, perforated or perforated.

The convex cup-like or deep-drawn regions 310 with their central openings 311 are arranged distributed on the perimeter of the element 300, where openings 312 are also made in the central region. The cup-like areas 310 with their central openings 311 serve for fastening, such as riveting, the friction lining with a sealing support, where the openings 312 serve so that an opposite friction lining can be riveted with a support. of gasket, where the riveting punch can protrude through the opening 312.

In addition to the openings 303, 304 and 312, further openings 313, 314 and 315 are arranged, which are made for reducing the moment of inertia as well as for reducing weight in the seal holder 300. The edge areas of the openings 312 a 315 can be raised, as for example the edge areas of the openings 231 of Figure 4a, respectively 4b. These openings also serve for a better connection between the material of the friction lining layer and the support of. gasket 300.

The openings 312 to 315 can be made substantially rectangular or rectangular with rounded corners, where a trapezoid-shaped or paraileiogram-shaped opening can also be made with or without rounded corners.

Figure 6 also shows a further embodiment of a gasket support 300, which has openings 306 in the outer edge region 301 and openings 304 in the inner edge region 302. they are arranged distributed around the perimeter. The openings 312 corresponding to the openings 312 of Figure 5 have the same purpose, where these openings are also arranged distributed on the perimeter.

The openings 313 to 315 of Figure 5 in the exemplary embodiment of Figure 6 are made as smaller and subdivided apertures 320, 322, 324, 325 and 326. Furthermore, elongated openings can also be made, considered in the perimeter direction, which for example have the extension of the openings 320 and 321.

The seal supports shown in Figures 4 to 6, as support elements, serve to ensure that the friction lining is subjected to a stabilizing effect, where the material of the friction lining is arranged, as applied, substantially on both sides of the support. of the seal, and the seal support with its central zone, such as a zone in the form of a circular ring, is arranged substantially in a central zone of the friction lining. The thickness of the layer of the friction lining, which enters into frictional engagement with a friction counter-surface, such as for example the thickness d1 as shown in figure Za, can be greater than half the thickness of the friction lining, where the thickness of the element d1 support is substantially small compared to the overall thickness of the friction lining.

The thickness d1 of the gasket support, as a support element, is preferably in the range from 0.1 to 2.0 rnn, where the thickness d1 is preferably in the range from 5.0 mm to 0.5 mm. The same also applies to the thickness of the layer d2-Figure 7a shows a view of a support element 400, of a friction seal, which has a configuration substantially in the form of a circular ring. The element 400 in the form of a circular ring has a radially external edge region 401 and a radially internal edge region 402, where the edge region 401 and / or the edge region 402, considered in the axial direction, are bent at an angle or bent or deformed, so that this radially inner and / or radially outer edge region 401, 402 projects in the axial direction. In addition, in the radially outer edge region 401, openings 403 as well as openings 404 in the radially inner edge region 402 are made as drilled, punched or otherwise formed. friction with the packing support 400. Furthermore, these openings have the advantage that they reduce the mass of the packing support 400 as well as reduce the mass moment of inertia.

In the central area of the support element 400 there are openings 405, as well as 406. The openings 405, which can be made on the entire perimeter area of the element 400, serve to connect the material of the friction lining, which, considered in axial direction, is arranged, as applied, on either side of the friction lining support. The openings 406 have an embodiment in which the edge areas of these openings are raised. Such an embodiment is shown in section 7b in Figure 7b, where the raised edge areas 407 are shown in comparison with the flat base region supporting the gasket 400. The raised edge regions can be used for an increase in the surface of the element support, to achieve a better bond between the friction lining material and the support member. Furthermore, the raised edge areas of the openings 406 can be raised in such a way that the edges 407a of the raised edge areas 407 support themselves on the support element which rests flat on the lower side, i.e. the support of the gasket 400 supports itself in the areas 407a of the raised edge areas. The raised edge areas 407 with their resting areas 407a can have a spacing function, when the height of the lifting 407, considered in the axial direction, is at least equal to the height of the lifting of the edge areas 401 and / or 402.

In Figure 7a it also shows openings 408 which are made in such a way that a rivet head and a riveting tool can pass through this opening to connect or rivet a second friction lining or a further friction lining with a seal holder on a fastening element. Furthermore, zones 409 can be recognized, which have a cup-like design and show a central opening 410. The cup-like design 409 is used for fastening, for example riveting, the friction seal by means of a rivet, where the rivet head is in the area of the countersink 409 like a cup and the rivet passes through opening 410, to be connected with a fastener.

The openings 405 in a further advantageous embodiment of the gasket support 400 can be provided, like the openings 406, with raised edge regions. Furthermore, it may advantageously be advantageous for the openings 408 to have raised edge areas.

Figure 7c shows a section of the element 400 of Figure 7a along the line A-A. The radially outer edge regions 401 and 402 can be recognized, which, considered in the axial direction, are bent at an angle or deformed, so that they protrude in the axial direction with respect to the base region 400. Furthermore, the openings 403 and 404 in the region can be recognized. of the radially inner or radially outer edge of the element 400, where the openings go beyond the corner bending zone 420 and are located in the radial as well as axial zone of the element 400, 401. The zone 409, as a zone shaped like a cup or deformed, with its opening 410 shows that the depth of the cup-like zone is less than the axial extension of zones 401, 402, which is illustrated by zone T in the lower half of the figure. In this embodiment, the zone 409 serves not as a spacer but only as a fastening element. Furthermore, a configuration is possible in which the axial extension of the zone 409 is greater than the axial extension of the zones 401, 402, so that the zone 409 assumes a spacing function compared to the zones 401, 402.

Figure 7d shows a detail 7a, where an area around a cup-shaped construction 409 is represented. The support element 400, the cup-like area 409 and the central opening 410 can be recognized in the edge areas. In this embodiment, the central opening does not have a round or substantially round configuration, but it also has recesses, such as arms 421, which are substantially shaped like a star, considered in the radial direction of the opening. These arms 421 allow an execution of the zone 409 in four partial zones 422, which are essentially formed as circular segments. The subdivision of the base zone 409 of the cup-like zone into sub-zones 422 makes possible a springing effect of the segments 422, which is advantageous, when the gasket support 400 is riveted by means of rivets in the zone 409. The individual segments 422, in such an embodiment, can be stressed with different force, where it is made possible in the axial direction a slight overturning or displacement of the elements 422.

Figure 8 shows an element, such as a gasket support element 500, with a radially outer edge region 501 and a radially inner edge region 502, in which openings 503 and 504 are made.

The cup-like areas 409 of Figure 7a, which are substantially circular in shape, are connected in Figure 8 with a circular ring-shaped area 505, which is displaced, as drawn, with respect to the area 505 of the element 500 , considered in the axial direction. In the area 505, which protrudes axially with respect to the area 506, openings 507 and 508 are made as punched or perforated or drilled. spring of a clutch disc, where the openings 508 can be used for the connection, such as riveting, of an opposite friction lining.

Furthermore, ribs 510 and / or 511 can be made in the gasket support or the support element, to increase the bending rigidity of the gasket support. The lifts which can be carried out in the edge areas 501, 502 radially internal or radially external substantially in the axial direction of the friction lining, also contribute to an increase in the bending stiffness.

The lifts of the friction lining in the radially inner edge region and / or in the radially outer edge region can extend axially or be bent at an angle at an angle between 0 and 90 ° with respect to the plane of the sealing support. Similarly, the lifting can be carried out as a rib in the radially inner and / or outer edge region.

The axially projecting edge areas of the seal carrier as well as the cup-like areas, which are for example also formed on a circular ring-shaped area oriented in the peripheral direction of the friction lining, serve for the increased stiffness, such as bending stiffness, of the support member, as a seal support, where the bending stiffness of this member also determines the bending stiffness of the friction seal. Furthermore, it is advantageous if the bending stiffness takes on an increased value, since distortion problems during the operation of the friction linings, for example in the operation of a clutch disc, must be kept as low as possible.

The manufacture of such a friction lining as described above is carried out for example by the fact that a mixture of friction material is dosed in a hot press, subsequently the lining support is placed in the press and subsequently further material is dosed, first that the material with the gasket support, for example by hot pressing, is molded in its final state.

Similarly, it can be advantageous if first of all the gasket support equipped with a spacer effect is placed in the mold, then the friction material is metered, and the material during the pressing process, as a hot pressing process, also flows through holes in the area. below the seal holder.

A friction seal according to the inventive concept can be machined, such as ground, after the forming process, such as for example hot pressing process, on at least one side, such as a surface. It may also be desirable if both sides of the friction lining are ground. A friction lining according to the invention is manufactured from a mixture of friction materials consisting of different materials, for example organic and / or inorganic, such as plastics, resins, metals and fibers, such as for example glass fibers, carbon fibers. , plastic fibers, ceramic fibers. This friction material mixture is prepared by mixing the individual base substances or premixes, where residual substances, such as rubbing dust, drilling debris or pressing burrs, can also be mixed with this mixture. These residual substances can accumulate during the production or processing of friction linings, where these, if returned to the production process, do not have to be disposed of. Furthermore, processing of old workpieces, such as used and partly worn friction linings, can also take place, so that for example after a separation of reusable or non-reusable friction lining parts, the reusable parts are processed to form a powder or a granulate, and are subsequently mixed with the friction lining mixture.

The friction lining can be constructed in such a way that the friction lining layer in front of the lining support (front side) has a different material mixture than the friction lining layer behind the lining support. The friction lining layer in front of the lining support (front side) has the friction surface, and the friction lining layer behind the lining support (rear side) preferably does not serve as a friction surface.

Therefore, a material can be used for the seal mixture behind the seal carrier (rear side) which does not have to meet the high requirements regarding the coefficient of friction. This material can also preferably have a smaller thickness, so that the weight and moment of inertia of the friction lining are reduced. Similarly, the material can also be manufactured from cheaper components.

The materials of the front and rear sides of the friction lining are preferably selected in such a way that a distortion of the lining due to the effect of temperature or humidity does not substantially occur or occurs only minimally.

Depending on the choice of material, the rear side of the friction lining can also be chosen thinner or thicker than the front side. It is advantageous if the distortion characteristics of the front and rear sides of the friction lining compensate each other in such a way that no distortion of the lining results as a function of temperature or moisture content.

In the case of a friction lining according to the invention with at least one layer of friction material respectively in front of and behind a supporting element of the lining, it can be advantageous if for the side of the friction lining, which bears the friction surface, pure materials are used without residual substances.

For the side of the friction lining that does not bear the friction surface, a friction lining mixture with residual substances can be used. Such residual substances can be constituted by mixing together grinding dust, grinding burr or recycled material.

The gasket support elements, such as the gasket support plates, may have a mechanical connection between the gasket material and the support element, such as the support plate, for example by means of a shape coupling, where this Mechanical connection can be generated for example by projections or by other material connections or designs. These can be ribs and / or collars on the edge zone and / or elevations of partial zones, for example of edge zones of openings. If the material of the gasket for example is bonded, for example by proportions of resin in the mixture of the gasket support, with the support element, as a support plate, the gasket support elements, as a support plate, gasket support, can be surface treated. Thanks to this roughness, an improved connection occurs between the gasket material and the gasket carrier.

When the backing plates are fabricated, as punched, from cylindrical or non-cylindrical cylinders, a surface treatment for better adhesion of the gasket material may be advantageous. The surface of the sheets can be roughened by a chemical etching process. In addition, the surface can be roughened by a particle jet process, such as sandblasting or water jet process or by another surface removal process or deformation process.

The surface treatment by means of for example etching can suitably take place in a phosphating plant.

The friction lining is a friction lining preferably made of molded material, which is manufactured for example from a powder mixture in a mold with a hot pressing process.

Figures 9a to 9c respectively show a section of a friction lining according to the invention.

Fig. 9a, modifying the friction lining of Fig. 9b, shows a connection of the friction lining not with a rivet but with a form-fitting connection, which is formed from the material of the support member by deformation. The friction lining 600 essentially consists of a support element 603 and the two layers of friction lining 602 on the front side and 601 on the rear side of the lining. The gasket support 603 has a region 605 raised in the axial direction in the radially inner edge region 604. Furthermore, the gasket support 603 has, in the radially outer region 606, a region 607 raised in the axial direction. The radially central zone 608 has a cup-shaped formation which serves for the connection of the seal support 603 with a segment 609 of a friction disc. The segment has an opening in the connection area, in which a collar 610 is engaged, consisting of the material of the cup-shaped gasket support, which collar is again deformed, such as rimmed or folded, so that a coupling connection is formed. of shape. In the area 611 of the connection with the segment, the layer of the friction lining can be indented. Thanks to this form-fitting connection as an integrated rivet element s1 can save an additional rivet. An integrated rivet element can be performed by lifting and bending or bending the edge region of the support element or by other turning. This fixing process is not feasible with all support materials, as not all materials are deformable in the required way. In such cases, a connection can also be made with a rivet.

Figure 9b shows a section through a friction lining 620, but at another point, so that the attachment to the clutch disc segment is not shown. In the friction lining 620, for example on the front side 622 carrying the friction surface and / or on the rear side, grooves 623, 624, oriented substantially in the peripheral direction, or recesses are formed or molded. substantially in the shape of a circle or ellipse in the perimeter direction on the surface of the gasket. Several grooves can also be made next to each other. These grooves 623, 624 can be made in a closed circular shape, or the circular shapes of the grooves can be interrupted by ribs. In this case, the ribs in the area of the riveted bottoms or cup-shaped forms should be arranged for riveting or for housing the rivets or fastening means. The grooves can be made by means of a punch in the tool during the manufacturing process, whereby a centering of the support can also be achieved.

Figure 9c shows the section of a friction lining 650 with a friction lining layer 651 on the front side bearing the friction surface, and a friction lining layer 652 on the rear side. The support element 653 is arranged substantially in the center and does not have any lifting on at least one edge region, such as the radially inner edge region and / or the radially outer edge region. However, ribs 654 can be provided to increase the bending stiffness in the support member.

Figure 10a shows a view of a friction lining from the side not facing the friction surface. The friction lining 700 has a rear side 702, which forms substantially no friction surface. Openings 703 and 704 are made in the friction lining. Opening 703 with a drawn or raised area of the backing plate serves for connecting or riveting the friction lining with a fastening element, and opening 704 serves for riveting of an opposite friction seal, so that a riveting tool can pass through this opening 704. A peripheral groove 705 is made in the radially inner region of the rear side of the friction lining and a peripheral groove 706 is formed in the radially external region of the friction lining, where the perimeter groove 706 is interrupted and the perimeter groove 705 is closed . The perimeter groove 705 can also be executed interrupted and the perimeter groove 706 can also be executed closed. Advantageously, at least one interrupted or closed peripheral groove or another groove with a radial orientation can be provided in the friction lining. More than one groove can also be made in the friction lining.

Figure 10b shows a detail of a friction lining 701 from the side of the friction surface 711, where openings 703 for riveting the friction lining and 704 for the passage of tools are made in the friction lining. On the friction surface of the friction lining there are recesses or grooves 712 and 713 in the perimeter direction, where the grooves 712 and 713 in the perimeter direction can be made closed or interrupted. The creation of the grooves 705, 706 and 712, 713 entail a reduction in weight and therefore a reduction in the moment of inertia of the friction lining.

Figure 10c shows a section through an arrangement of friction linings 700, 701, which are connected with the fastening element 721 in the central zone by a deformation of the support plate 720. The central zone 722 of the deformation is carried out as an element of integrated rivet.

Figure 10d shows a connection of two friction linings 701 and 700 with a fastening element 710, which is connected with a rivet element 730 to a driving disc 711 of a clutch disc. The friction lining 700 is connected, as riveted, to the element 710 by means of the rivet element 731, where for riveting the tool passes through the free zones 704. In addition, the grooves 706, 705 and 712, 713 can be recognized.

The patent claims filed with the application are proposed formulations without prejudice to obtain wider patent protection. The Applicant reserves the right to claim still further characteristics disclosed so far only in the description and / or in the drawings.

The references used in the sub-claims refer to the further execution of the object of the main claim by means of the characteristics of the respective sub-claim; they are not to be understood as a renunciation of obtaining autonomous objective protection for the characteristics of the reference sub-claims.

However, the objects of these sub-claims also form autonomous inventions, which have a configuration independent of the objects of the previous sub-claims.

The invention is also not limited to the exemplary embodiments of the description. On the other hand, numerous variations and modifications are possible within the scope of the invention, in particular variations, elements and combinations and / or materials which are inventive for example by combining or modifying individual characteristics or elements or process steps contained in the general description and in the forms as well as in the claims and in the drawings, and by means of combinable characteristics lead to a new object or process steps or sequences of process steps, also with regard to the manufacturing, testing and working process.

Claims (31)

CLAIMS 1. Friction lining, in particular for clutch discs or brakes, for example for motor vehicles, which is substantially in the form of a circular ring and consists of a supporting element in the form of a substantially circular ring as well as a friction material including substantially this support element, the friction lining has areas of absorption or deformation for fixing the friction lining on a fastening element, where the substantially circular ring-shaped support element is arranged substantially in the center of the friction, considered in the axial direction. 2. Friction lining according to claim 1, characterized in that the support element has a base area substantially in the form of a circular ring, which is arranged substantially in the center of the friction lining, considered in the axial direction. Friction lining according to claim 1 or 2, characterized in that the friction material of the friction lining, considered in the axial direction, is applied or is present both in front of and behind the base zone, substantially in the form of a circular ring , of the support element. Friction lining according to claim 1 or 2, characterized in that, considered in the axial direction, a friction lining layer is applied in front and a friction lining layer is applied behind the support element. 5. Friction seal according to claim 1 or 2, characterized in that a layer of friction seal is applied to both sides of the support element. 6. Friction lining according to claim 4 or 5, characterized in that the extension, considered in the axial direction, of the friction lining layer in front of a base region of the support element is substantially equal to the extension, considered in the axial direction, of the friction lining layer behind the base region of the support element. 7. Friction lining according to claim 4 or 5, characterized in that the extension d1, considered in the axial direction, of the friction lining layer in front of the base region of the support element is substantially greater than the extension d2 " viewed in the axial direction, of the friction lining layer behind the base region of the support member. 8. Device according to claim 7, characterized in that the ratio between the extension d1 and the extension is in the range from 4 to 1, preferably from 2 to 1. 9. Friction lining according to claim 7, characterized in that the extension d1, considered in the axial direction, of the friction lining layer in front of the base region of the support element is substantially smaller than the extension d2 considered in axial direction, of the friction seal layer behind the support member. 10. Device according to claim 9, characterized in that the ratio between the extension d1 and the extension d2 is in the range from 1 to 0.3, preferably from 1 to 0.5. 11. Friction lining, in particular for clutch plates or brakes, for example for motor vehicles, which is substantially in the form of a circular ring and consists of a supporting element in the form of a substantially circular ring as well as a friction material substantially incorporating this support element, with deformation absorption zones for fixing the friction seal on a fastening element, characterized in that the substantially circular ring-shaped support element has a ring-shaped base zone circular and at least one further zone, which has an extension in the axial direction, so that this zone protrudes in the axial direction with respect to the base zone in the form of a circular ring of the support element. 12. Friction seal according to claim 11, characterized in that the radially outer edge region of the support element in the form of a circular ring projects axially with respect to the base region of the support element. 13. Friction seal according to claim 11, characterized in that the radially inner edge region of the support element in the form of a circular ring projects axially relative to the base region of the support element. 14. Friction seal according to claim 11, characterized in that in the base region of the support element in the form of a circular ring, at least one region is formed, as convex, raised or deformed in the shape of a cup, such that it protrudes in an axial direction with respect to the base area of the support element. 15. Friction lining according to claim 14, characterized in that at least two regions of the base region of the circular ring-shaped support element, which project in the axial direction, are uniformly distributed along the perimeter of the shaped support element of circular ring. 16. Friction seal according to claim 14, characterized in that at least one region, present in the base region of the support element in the form of a circular ring, which protrudes in the axial direction, is substantially made with a circular or oval shape. 17. Friction seal according to claim 14, characterized in that at least one area, present in the base area of the support element in the form of a circular ring, which protrudes in the axial direction, is substantially made in a polygonal shape, such as square or rectangular. 18. Friction seal according to claim 14, characterized in that at least one area, present in the base area of the support element in the form of a circular ring, which projects in the axial direction, considered in the peripheral direction, has a contour to circular ring shape. 19. Friction lining according to claim 14, characterized in that the at least one area in the form of a circular ring projecting in the axial direction is arranged coaxially with respect to the axis of the friction lining. Friction seal according to one of the preceding claims, characterized in that openings such as punched, perforated or drilled are formed in the base region of the support element in the form of a circular ring. 21. Friction lining according to one of the preceding claims, characterized in that edge regions of at least one opening in the support element in the form of a circular ring are raised in the axial direction. 22. Friction seal according to one of the preceding claims, characterized in that openings, such as holes, with different cross-section or with different extension are made in the base region of the support element in the form of a circular ring. 23. Friction seal according to one of the preceding claims, characterized in that the areas or regions, which project axially with respect to the base area in the form of a circular ring of the support element, have openings. 24. Friction lining according to one of the preceding claims, characterized in that the extension of the support element in the form of a circular ring, considered in the axial direction, is smaller than the extension of the friction lining, considered in the radial direction. 25. Friction lining according to claim 24, characterized in that the extension of the support element, considered in the radial direction, is smaller than the radial extension of the friction lining, but greater than a quarter of the radial extension of the lining of friction. 26. Friction lining according to one of the preceding claims, characterized in that the extension of the support element in the form of a circular ring, considered in the radial direction, is equal to the extension of the friction lining, considered in the radial direction. 27. Friction lining according to one of the preceding claims, characterized in that the extension of the support element in the form of a circular ring, considered in the radial direction, is greater than the extension of the friction lining, considered in the radial direction. 28. Friction seal according to one of the preceding claims, characterized in that the substantially circular ring-shaped support element is made of metal, such as for example steel or aluminum. 29. Friction lining according to one of the preceding claims, characterized in that the substantially circular ring-shaped support element is made of plastic, such as for example fiber-reinforced plastic, such as glass fibers. 30. Clutch disc, in particular for a friction clutch, which on its outer perimeter carries at least one friction lining, with an input piece, such as a driving disc, which is eventually connected integral with rotation with a counter disc, and driving disc and counter disc form the input piece of a torsional vibration damper, where a component in the form of a circular ring, such as a flange, serves as the output piece of the torsional vibration damper and transmits a transmissible torque from the output side directly or possibly via an additional torsional vibration damper at the clutch disc hub, where a torsional vibration damper can be provided between the flange and the clutch disc hub, for example for the idling range, characterized by the fact that the friction linings of the clutch disc, which serve as an input piece, are cost consisting of a support element and a layer of friction lining, and the support element is arranged substantially in the center of the friction lining, and the support element has regions, which project in a radial direction with respect to a region of base of the support element. 31. Friction plate in particular for motor vehicles, characterized in that the friction linings of the clutch plate are designed according to one of claims 1 to 29.