Method for adjusting the coefficient of friction of a friction plate and friction lamella

Abstract

A method for producing a friction lamella with a disc-shaped support lamella (5) having a first surface (6) and a second surface (7), wherein a first sintered friction coating is sintered onto the first surface (6) and a second sintered friction coating is sintered onto the second surface (7), and wherein grooves (13) are formed in the first and the second sintered friction coatings, respectively, wherein at least a portion of the grooves (13) in the first sintered friction coating are offset in the circumferential direction (12) of the support lamella (5) relative to the grooves (13) in the second sintered friction coating, wherein the coefficient of friction of the friction lamella is adjusted by the offset of the grooves, and the grooves (13) in the first sintered friction coating are produced with an area fraction between 5% and 40%, based on the total area of ​​the first sintered friction coating, and / or the grooves (13) in the second sintered friction coating are produced with an area fraction between 5% and 40%. % and 40% are produced,with respect to the total area of ​​the second dispersed friction layer, characterized in that the offset of the grooves (13) in the first dispersed friction layer to the grooves (13) in the second dispersed friction layer is made at least so large that all grooves (13) are arranged next to each other when viewed from above, so that no overlap or intersecting of the grooves (13) is formed.

Description

[0001] The invention relates to a method for adjusting the coefficient of friction of a friction plate with a carrier plate having a first surface and a second surface, wherein a first scattered sintered friction lining is sintered onto the first surface and a second scattered sintered lining is sintered onto the second surface, and wherein grooves are introduced into the first and second scattered sintered linings, wherein at least some of the grooves in the first scattered sintered lining are formed offset in the circumferential direction of the carrier plate relative to the grooves in the second scattered sintered friction lining, wherein the coefficient of friction of the friction plate is adjusted by the offset of the grooves and the grooves in the first scattered sintered friction lining are produced with an area proportion of between 5% and 40%, based on the total area of ​​the first scattered sintered friction lining and / or the grooves in the second scattered sintered friction lining are produced with an area proportion of between 5% and 40%,based on the total area of ​​the second sintered friction lining.,

[0002] The invention further relates to a friction plate comprising a disk-shaped carrier plate with a first surface and a second surface opposite thereto, wherein a first scattered sintered lining is arranged on the first surface and a second scattered sintered lining is arranged on the second surface, and wherein grooves are arranged in the first and second scattered sintered lining, and wherein grooves are arranged in the first and second scattered sintered lining, and at least some of the grooves of the first scattered sintered friction lining are arranged offset in a circumferential direction to the grooves in the second scattered sintered friction lining, and the grooves in the first scattered sintered friction lining have an area proportion of between 5% and 40%, based on the total area of ​​the first scattered sintered friction lining and / or the grooves in the second scattered sintered friction lining have an area proportion of between 5% and 40%, based on the total area of ​​the second scattered sintered friction lining.

[0003] A wide variety of friction plate designs for multi-plate friction systems are known from the state of the art. In addition to resin-bonded paper composite friction materials and carbon facings, so-called scattered sintered facings are also used. Compared to resin-bonded paper composite friction materials, these exhibit no or significantly lower compressibility and very good temperature resistance. However, the problem is that when using a defined sintered material, the coefficient of friction cannot be adapted to specific applications without changing the material.

[0004] DE 10 2009 040 129 A1 discloses a friction plate comprising a disk-shaped carrier element with a first surface and a second surface opposite thereto, wherein a first friction lining is arranged on the first surface and a second friction lining is arranged on the second surface, which are formed from a composite material comprising a resin and a fiber material, and wherein grooves are arranged in the first and second friction lining, which divide the friction linings into segments at least in areas close to the surface, wherein the segments of the first friction lining are offset by a defined offset angle with respect to the segments of the second friction lining.

[0005] DE 10 2008 012562 A1 describes a clutch plate for a multi-plate clutch operated with coolant, in the respective friction lining of which a pattern of grooves is incorporated such that the grooves run parallel to each other in two different directions and cross each other, wherein the grooves end with a closure in front of the outer edge of the clutch plate.

[0006] DE 100 15 206 A1 discloses a clutch disc comprising a hub and at least one lining carrier which is drivingly connected thereto and surrounds the hub in a ring-shaped manner, on both sides of which friction material forming friction linings is provided, which friction material is connected flatly to the friction lining carrier and is shaped such that the friction linings formed on both sides of the lining carrier form axial projections, between which - viewed in the circumferential direction - valleys are formed and the projections formed on both sides of the lining carrier - viewed in the circumferential direction - are arranged offset from one another in such a way that when the friction linings are axially clamped, an axial, elastic deformation of the lining carrier occurs.

[0007] From AT 405 494 B a method for producing a flat friction plate is known, wherein first a sintered friction lining is applied to a flat steel plate and sintered, before the sintered friction lining is compacted and calibrated while simultaneously pressing in grooves and during the calibration of the friction plate, locally limited depressions with a closed edge, for example conical or pyramid-shaped depressions, are pressed into the steel plate by the sintered friction lining, distributed over the surface of the steel plate.

[0008] DE 1 199 548 A describes a clutch plate for a multi-plate clutch, in the friction surfaces of which spiral and radial grooves for a cooling liquid are incorporated, wherein the radial grooves and the spiral grooves closed towards both the inner and outer circumference of the plate are wider than they are deep and the radial grooves are deeper and wider than the spiral grooves and the distance between the spiral grooves is smaller than the distance between the radial grooves.

[0009] AT 516 209 A1 describes a friction assembly comprising a plurality of inner plates and a plurality of outer plates, wherein the inner plates and the outer plates are arranged alternately in an axial direction, and wherein at least one freely rotatable friction ring is arranged between the inner plates and the outer plates, and wherein the inner plates and / or the outer plates are adjustable relative to one another in the axial direction to form a frictional connection with the friction rings, and the friction rings are made of at least one resin containing at least one additive or a sintered material, wherein the friction rings each have at least one compressed region and at least one non-compressed region and / or at least one region that is less compressed than the compressed region on a surface facing an inner plate and on a surface facing an outer plate.

[0010] The object of the present invention is to create a possibility with which the coefficient of friction of scattered sintered friction linings can be adjusted within certain limits.

[0011] This object is achieved with the method mentioned at the outset in that the offset of the grooves in the first scattered sintered friction lining to the grooves in the second scattered sintered friction lining is made at least large enough that all grooves are arranged next to one another when viewed from above, so that no intersection or overlap of the grooves is formed.

[0012] Furthermore, the object of the invention is achieved with the friction plate mentioned at the outset, in which the offset of the grooves in the first scattered sintered friction lining to the grooves in the second scattered sintered friction lining is at least so large that all grooves are arranged next to one another when viewed from above, so that there is no intersection or overlap of the grooves.

[0013] Surprisingly, it has been shown that even a slight offset between the grooves in the first sintered facing and the grooves in the second sintered facing causes a noticeable change in the friction behavior of the friction plate. Thus, by simply changing the manufacturing process—by rotating the grooves in the second sintered facing relative to the grooves in the first sintered facing by a defined angle in the circumferential direction—the friction coefficient of a friction plate can be adjusted within a defined range dependent on the material composition of the sintered facings. It is therefore possible to adjust a defined friction coefficient of the friction plate via the angle of the rotation itself, i.e., the absolute value of this angle. This allows the friction plate to be easily adapted to different applications of such friction plates.

[0014] According to a preferred embodiment of the method, the grooves in the first scattered sintered layer are offset in the circumferential direction relative to the grooves in the second scattered sintered layer by an angle value selected from a range of 2° to 45°. Accordingly, the friction plate has the grooves in the first scattered sintered layer offset in the circumferential direction relative to the grooves in the second scattered sintered layer by an angle value selected from a range of 2° to 45°. The aforementioned effect of the adjustability of the friction coefficient of the friction plate has been observed to be particularly pronounced in this angular range.

[0015] According to another embodiment of the method, it can be provided that at least some of the grooves in the first scattered sintered coating and / or at least some of the grooves in the second scattered sintered coating are formed in the shape of a closed polygon. According to the associated embodiment of the friction plate, it can be provided that at least some of the grooves in the first scattered sintered coating and / or at least some of the grooves in the second scattered sintered coating are formed in the shape of a closed polygon. Due to this shape of at least some of the grooves, a very large surface area of ​​the scattered sintered coating is covered by the groove, which subsequently also makes it possible to achieve a correspondingly large effect with regard to adjusting the friction coefficient of the friction plate.

[0016] As stated, the offset of the grooves in the first sintered lining relative to the grooves in the second sintered lining is intended to be at least large enough so that the grooves appear to be arranged side by side when viewed from above. This can positively influence the thermal balance of the friction plate, as the proportion of connected surfaces without grooves in the friction linings is reduced (viewed in the axial direction and relative to both friction linings arranged one behind the other in this direction). The improved cooling of the friction plate, in turn, has a positive effect on the coefficient of friction during operation of the friction plate, which is set by the groove offset.

[0017] It is further provided that the grooves in the first scattered sintered layer have a surface area between 5% and 40%, based on the total surface area of ​​the first scattered sintered layer, and / or that the grooves in the second scattered sintered layer have a surface area between 5% and 40%, based on the total surface area of ​​the second scattered sintered layer. This allows for a correspondingly fine adjustment of the friction coefficient of the friction plate.

[0018] According to a further design variant of the friction plate, it is also possible that a ratio of a groove width in mm to a lining width between the grooves on the outermost circumference of the scattered sintered linings in mm is selected from a range with a lower limit of 2:30 and an upper limit of 1:4. This allows the influence of the groove width in the friction linings on the coefficient of friction to be better taken into account.

[0019] For a better understanding of the invention, it is explained in more detail using the following figures.

[0020] They show in a simplified, schematic representation: Fig. 1 shows a section of a plate pack according to the prior art in side view; Fig. 2 a first embodiment of the friction plate in an oblique view; Fig. 3 a second design variant of the friction plate in an oblique view; Fig. 4 a section of another design variant of the friction plate.

[0021] By way of introduction, it should be noted that in the variously described embodiments, identical parts are provided with identical reference symbols or component designations. The disclosures contained throughout the description can be applied analogously to identical parts with identical reference symbols or component designations. Furthermore, the positional information chosen in the description, such as top, bottom, side, etc., refers to the directly described and illustrated figure, and these positional information must be applied analogously to the new position in the event of a change in position.

[0022] In Fig. Figure 1 shows a section of a clutch plate pack 1. The clutch plate pack 1 comprises a plurality of inner plates 2 and a plurality of outer plates 3, which can also be referred to as friction plates. The inner plates 2 are arranged in an axial direction 4, alternating with the outer plates 3. Using a corresponding actuating mechanism, the inner plates 2 can be adjusted relative to the outer plates 3 in the axial direction 4, so that a frictional connection is formed between the inner plates 2 and the outer plates 3.

[0023] The inner plates 2 have an at least approximately flat, annular support plate 5 with a first surface 6 and a second surface 7 opposite the first surface 6 in the axial direction 4. A first scattered sintered coating is arranged on the first surface 6, and a second scattered sintered coating is arranged on the second surface 7 as a friction lining 8. The inner plates 2 are therefore so-called lining plates.

[0024] The outer plates 3 also have a flat and at least approximately annular plate body 9, which, however, is free of friction linings 8 in the illustrated embodiment. The outer plates 3 are therefore the so-called counter plates, which can be brought into frictional engagement with the friction linings 8 of the inner plates 2. However, it is also possible for the friction linings 8 to be arranged on the outer plates 3, especially if no friction linings 8 are arranged on the inner plates 2.

[0025] Preferably, the support plate 5 of the inner plates 2 and / or the plate body 9 of the outer plates 3 are made of or comprise steel. However, they can also be made of another suitable material, particularly a metallic one, for example a sintered material.

[0026] This basic structure of a disk pack 1 is known from the prior art. For further details, please refer to this relevant prior art.

[0027] The disc pack 1 is part of a multi-disk friction system, for example a (wet-running) multi-disk clutch, a brake, a holding device, a differential lock, etc.

[0028] In Fig. 2 shows a first embodiment of a friction plate as used in the plate pack 1 according to Fig. 1 is or can be used. In particular, an inner plate 2 is shown. However, the friction plate can also be an outer plate 3 ( Fig. 1) be.

[0029] The friction plate is designed especially for so-called wet-running operation.

[0030] The friction plate can have at least one driver element 11, for example in the form of an internal toothing, on a radially inner end face 10.

[0031] It should be mentioned at this point that the outer plates 3 can also have at least one driver element on a radially outer end face. Therefore, if the friction plate is Fig. 2 is designed as an outer plate 3, the at least one driver element is arranged on the radially outer end face of the friction plate.

[0032] Via the driver elements 11, a rotationally fixed connection can be established with another component of the multi-disk friction system, for example a shaft in the case of the inner discs 2 or the housing of the multi-disk friction system in the case of the outer discs 3, as is known per se.

[0033] It is also possible that the inner plates 2 or the outer plates 3 are designed as so-called free-flying plates, i.e. that they do not have any such driver elements 11.

[0034] The carrier slat 5 ( Fig. 1) the friction plate is closed in a circumferential direction 12.

[0035] It should be noted at this point that in the event that the friction plate has an outer plate 3 ( Fig. 1), the following statements regarding the carrier lamella 5 can also be transferred to the lamella body 9 of the outer lamella 3, provided that this is designed according to the invention.

[0036] Preferably, the support slat 5 is formed in one piece. However, it is also possible for the support slat 5 to be composed of several interconnected segments.

[0037] As already explained, on the first surface 6 of the carrier lamella 5 ( Fig. 1) a first friction lining 8 is arranged and connected to the second surface 7. Likewise, a second friction lining 8 is arranged on the second surface 7 and connected to the carrier plate 5. As can be seen from Fig. As can be seen in Figure 2, the first and second friction linings 8 are preferably arranged on the entire first and second surfaces 6, 7 of the carrier plate 5, respectively. Furthermore, the first and second friction linings 8 preferably extend continuously in the circumferential direction 12, and are therefore preferably also annular. Thus, preferably, only a first friction lining 8 is arranged on the first surface 6 and only a second friction lining 8 is arranged on the second surface 7 of the carrier plate 5.

[0038] The first and second friction linings 8 are scatter-sintered friction linings. The scatter-sintering technology itself is known from the prior art, so reference is made here for further details of this technology. Suffice it to say that a sintering powder suitable for the friction plate is scattered onto a prepared carrier plate 5 and sintered onto the carrier plate 5. This lining is then compacted, and grooves 13 for cooling the friction plate are pressed in. The lining can then be subjected to a second sintering process. If necessary, post-treatment, e.g., calibration of the friction plate, deburring, etc., takes place.

[0039] The materials known from the state of the art for scatter sintered coatings can be used as sinter powder.

[0040] The first and second friction linings 8 are preferably made of the same sintered material. However, it is also possible for the first sintered friction lining to be made of a different material than the second sintered friction lining, for example, to vary the friction behavior of the friction plate in the two directions.

[0041] The grooves 13 in the first friction lining 8 and the grooves 13 in the second friction lining 8 (in Fig. 2 shown in dashed lines) serve to guide the oil to provide the appropriate lubrication and to dissipate heat generated by friction with a friction partner of the friction plate. These grooves 13 extend over a portion of a lining thickness 14 ( Fig. 4) the friction linings 8.

[0042] However, it is also possible for the grooves 13 to extend through the entire lining thickness 14 of the friction linings 8 up to the carrier plate 5.

[0043] It is now provided that the grooves 13 of the first friction lining 8 are arranged or formed offset by an angular value 15 in the circumferential direction 12 with respect to the position of the grooves 13 of the second friction lining 8, wherein this angular value 15 is preferably at least approximately the same for all grooves 13. However, it is also possible for the grooves 13 of the friction plate to be or are offset by different angular values ​​15. This applies both to a friction lining per se and to the first friction lining 8 compared to the second friction lining 8. It is therefore possible, for example, for the grooves 13 of the first friction lining 8 to all be arranged at the same distance from one another, whereas the distance between the grooves 13 in the second friction lining 8 varies.

[0044] As this is particularly evident from Fig. 2, the grooves 13 in the first friction lining 8 are not located above the grooves 13 in the second friction lining 8.

[0045] The angle value 15 is measured between longitudinal center axes 16 through the grooves 13 in the plane of the friction linings 8, as shown in Fig. 2 is evident.

[0046] By offsetting the grooves 13 in the second friction lining 8 relative to the grooves 13 in the first friction lining 8 by an angle of 15, the friction coefficient of the friction plate can be influenced and thus adjusted within certain limits. These limits are determined, on the one hand, by the material used to manufacture the sintered friction linings, and, on the other hand, by the friction pairing, i.e., the material from which the respective counter plates are made, i.e., in the present embodiment, the material from which the outer plates 3 ( Fig. 1) are manufactured.

[0047] As an additional effect, the offset of the grooves 13 can also influence the thermal balance of the friction plate, since the connected surface is reduced with offset grooves 13 and the good conductivity of the materials used results in lower temperatures on the friction surface. The term "smaller connected surface" means that, based on the design variant of the friction plate according to Fig. 2 the continuous surface between two grooves 13 in the first friction lining 8, which extends over at least approximately 90 °, is "interrupted" by the grooves 13 in the second friction lining 8 on the back of the friction plate, so that the continuous surface in this embodiment of the friction plate is halved, since the friction plate can be cooled better on the back by the grooves 13 shown in dashed lines in the second friction lining 8 than if these grooves 13 were not present.

[0048] According to one embodiment of the friction plate, it can be provided that the angle value 15 by which the grooves 13 in the first friction lining 8 are offset in the circumferential direction 12 with respect to the grooves 13 in the second friction lining 8 (viewed in plan view of the friction plate) can be selected from a range with a lower limit of 2° and an upper limit of 45°, in particular from a range with a lower limit of 5° and an upper limit of 30°. However, it can also be provided that this angle value 15 is selected from a range from 1° to 180° or from a range from 1° to 90° or from a range from 1° to 60°, in particular if only one groove 13 or two grooves 13 or three grooves 13 are provided per friction lining 8.

[0049] In the Fig. In the embodiment variant of the friction plate shown in Figure 2, the grooves 13 in the first and second friction lining 8 are designed as radial grooves which extend in the radial direction from the inner circumference to the outer circumference of the friction linings 8.

[0050] However, it is also possible that these grooves 13 are designed differently, as can be seen from the friction plate according to Fig. 3 is shown as an example. The grooves 13 in the two friction linings 8 are designed in the form of a closed polygon, specifically in the form of a square. As can be seen from the Fig. 3, the polygon in the first friction lining 8 is formed or arranged offset in the circumferential direction 12 of the friction plate relative to the polygon in the second friction lining 8. The Fig. However, the arrangement of the grooves 13 shown in Figure 3 is not a variant falling within the scope of protection due to the overlap.

[0051] Instead of a square, the polygon can also be a triangle or a rectangle or a hexagon or an octagon, etc.

[0052] In order to be able to use the grooves 13 for coolant guidance in this embodiment variant as well, it can be provided that further grooves 17 are arranged or formed on the polygons and branching off from these to the inner circumference or to the outer circumference of the friction linings 8, which on the one hand enable the cooling fluid to be introduced into the grooves 13 and on the other hand enable the cooling fluid to be discharged from the grooves 13.

[0053] It is also possible that such a groove 13 formed as a polygon is arranged only in one of the friction linings 8.

[0054] By way of explanation, it should be noted that the closed shape of the polygon is to be understood in the top view of the friction linings 8, as shown in Fig. 3. In other words, the closed shape of the groove 13 refers to the circumferential direction 12 of the friction plate.

[0055] Out of Fig. 3 it is further apparent that the friction linings 8 may have, in addition to the grooves 13 and optionally the grooves 17, further grooves 18, for example in the form of a waffle pattern or another pattern as is known from the prior art.

[0056] In order to further improve the adjustability of the friction coefficient of the friction plate, it is provided that the grooves 13 of the first and second friction lining 8 - viewed in plan view - are arranged at least next to one another, i.e. there is no intersection or overlap of the grooves 13.

[0057] It is further provided that the grooves 13 in the first scattered sintered friction lining have a surface area of ​​between 5% and 40%, in particular between 5% and 30%, based on the total surface area of ​​the first scattered sintered friction lining, and / or that the grooves 13 in the second scattered sintered friction lining have a surface area of ​​between 5% and 40%, in particular between 5% and 30%, based on the total surface area of ​​the second scattered sintered friction lining. The relatively large surface area of ​​the grooves 13 can further simplify the adjustability of the friction coefficient of the friction plate.

[0058] It was found that the lining thickness 14, i.e. the thickness of the friction linings 8, also influences the adjustability of the friction coefficient of the friction plate, although the reason for this is not yet known. Therefore, according to another design variant of the friction plate, it is advantageous for the defined adjustability of the friction coefficient of the friction plate if a ratio of a groove width 19 in mm, which consists of Fig. 4, to the coating thickness 14 is between 30 : 1 and 1 : 2.

[0059] Furthermore, it can be advantageous for the adjustability of the friction coefficient of the friction plate if a ratio of the groove width 19 in mm to a lining width 20 ( Fig. 2) between the grooves 13 on the outermost circumference of the sintered friction linings in mm is selected from a range with a lower limit of 2:30 and an upper limit of 1:4.

[0060] For the production of the grooves 13 and optionally the grooves 17 and / or grooves 18 in the friction linings 8, corresponding punches can be used which have this groove pattern and with which the grooves 13 and optionally the grooves 17 and / or grooves 18 can be pressed into the sintered friction linings.

[0061] The grooves 13 can be as in Fig. 4, for example, have a rectangular cross-section. However, it is also possible for the grooves 13 to have a different cross-sectional shape, for example, an inwardly tapered cross-sectional shape (e.g., a trapezoidal cross-sectional shape), a rounded cross-sectional shape, etc.

[0062] Although it is preferred that the grooves 13 in the first friction lining 8 are formed in the same shape and size as the grooves 13 in the second friction lining 8, it is also possible that the grooves 13 in the first friction lining 8 differ in shape and size from the grooves 13 in the second friction lining 8.

[0063] The exemplary embodiments show possible embodiments, whereby it should be noted at this point that combinations of the individual embodiments are also possible.

Claims

[1] Method for producing a friction plate with a disk-shaped carrier plate (5) having a first surface (6) and a second surface (7), wherein a first scattered sintered friction lining is sintered onto the first surface (6) and a second scattered sintered friction lining is sintered onto the second surface (7), and wherein grooves (13) are respectively introduced into the first and the second scattered sintered friction lining, wherein at least some of the grooves (13) in the first scattered sintered lining are formed offset in the circumferential direction (12) of the carrier plate (5) relative to the grooves (13) in the second scattered sintered friction lining, wherein the friction coefficient of the friction plate is adjusted by the offset of the grooves and the grooves (13) in the first scattered sintered friction lining are produced with an area proportion of between 5% and 40%, based on the total area of ​​the first scattered sintered friction lining and / or that the grooves (13) in the second scattered sintered friction lining are an area share between 5% and 40%,based on the total area of ​​the second scattered sintered friction lining, , characterized by that the offset of the grooves (13) in the first scatter sintered friction lining to the grooves (13) in the second scatter sintered friction lining is made at least large enough that all the grooves (13) are arranged next to one another when viewed from above, so that no intersection or overlap of the grooves (13) is formed. [2] Method according to claim 1, characterized by that the grooves (13) in the first scattered sintered friction lining are offset by an angular value (15) in the circumferential direction (12) to the grooves (13) in the second scattered sintered friction lining, which is selected from a range of 2 ° to 45 °. [3] Method according to claim 1 or 2, characterized by that at least some of the grooves (13) in the first scattered sintered friction lining and / or at least some of the grooves (13) in the second scattered sintered friction lining are formed in the form of a closed polygon. [4] Friction plate comprising a disk-shaped carrier plate (5) with a first surface (6) and a second surface (7) opposite thereto, wherein a first scattered sintered friction lining is arranged on the first surface (6) and a second scattered sintered friction lining is arranged on the second surface (7), and wherein grooves (13) are arranged in the first and second scattered sintered friction lining, and at least some of the grooves (13) of the first scattered sintered friction lining are arranged offset in a circumferential direction (12) to the grooves (13) in the second scattered sintered friction lining, and the grooves (13) in the first scattered sintered friction lining have an area proportion of between 5% and 40%, based on the total area of ​​the first scattered sintered friction lining and / or that the grooves (13) in the second scattered sintered friction lining have an area proportion of between 5% and 40%, based on the total area of ​​the second scattered sintered friction lining, characterized bythat the offset of the grooves (13) in the first scattered sintered friction lining to the grooves (13) in the second scattered sintered friction lining is at least so large that all grooves (13) are arranged next to one another when viewed in plan view, so that there is no intersection or overlap of the grooves (13). [5] Friction plate according to claim 4, characterized by that the grooves (13) in the first scattered sintered friction lining are offset by an angular value (15) in the circumferential direction (12) to the grooves (13) in the second scattered sintered friction lining, which is selected from a range of 2 ° to 45 °. [6] Friction plate according to claim 4 or 5, characterized by that at least some of the grooves (13) in the first scattered sintered friction lining and / or at least some of the grooves (13) in the second scattered sintered friction lining are formed in the form of a closed polygon. [7] Friction plate (1) according to one of claims 4 to 6, characterized bythat a ratio of a groove width (19) in mm to a lining width (20) between the grooves (13) at the outermost circumference of the scattered sintered friction linings in mm is selected from a range with a lower limit of 2:30 and an upper limit of 1:4.

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