Method for manufacturing a friction lining assembly

Abstract

The present invention relates to a method for manufacturing a friction plate for a dual clutch (1), in particular a radial dual clutch, the method comprising the steps of: providing a first friction plate ring having a first inner diameter; providing a second friction plate ring having a second outer diameter, the second outer diameter being smaller than the first inner diameter; machining the first friction plate ring and the second friction plate ring in a tool (25) for manufacturing the friction plate, characterized in that the second friction plate ring is arranged within the first friction plate ring and the second friction plate ring and the first friction plate ring are machined together in the tool (25).

Description

Technical field

[0001] The invention relates to a method for manufacturing friction plates for a dual clutch, in particular a radial dual clutch, the method comprising the steps of: providing a first friction plate ring having a first inner diameter; providing a second friction plate ring having a second outer diameter, wherein the second outer diameter is smaller than the first inner diameter; machining the first friction plate ring and the second friction plate ring in a tool for manufacturing friction plates.

[0002] The invention further relates to a friction plate assembly comprising: a first friction plate ring having a first inner diameter and a first axial ring thickness; a second friction plate ring having a second outer diameter and a second axial ring thickness, wherein the second outer diameter is smaller than the first inner diameter, and the second friction plate ring can be arranged within the first friction plate ring.

[0003] Furthermore, the invention relates to a dual clutch, in particular a radial dual clutch, the dual clutch comprising an outer friction plate group and an inner friction plate group. Background art

[0004] Radial dual clutches for dual clutch transmissions are known. For example, DE 10 2014 223 033 A1 describes a wet-running radial dual clutch which comprises a radially outer first clutch and a radially inner second clutch arranged to be rotatable about a common axis of rotation. The dual clutch has an outer friction plate support comprising outer friction plates and an inner friction plate support comprising inner friction plates. The inner friction plates (viewed in the radial direction) are arranged within the outer friction plates. Due to this arrangement, there are increased requirements for the component accuracy of the friction plates of the two friction plate groups, in particular the axial thickness of the friction plates must be within a narrower tolerance than in the case of a simple diaphragm clutch having only one friction plate group. Summary of the invention

[0005] The object of the invention is to improve the efficiency of manufacturing friction plates for a radial dual clutch and thus to improve the manufacture of the radial dual clutch.

[0006] This object is achieved in the method described at the beginning by arranging the second friction plate ring within the first friction plate ring and machining the second friction plate ring and the first friction plate ring together in a tool.

[0007] The object of the invention is furthermore achieved by means of the friction plate assembly described at the beginning, wherein the first axial ring thickness of the first friction plate ring deviates from the second axial ring thickness of the second friction plate ring by at most 0.05 mm, in particular at most 0.04 mm.

[0008] Furthermore, the object of the present invention is achieved by means of the dual clutch described at the beginning, wherein the outer friction plate group and the inner friction plate group are formed by friction plate assemblies according to the present invention, and the friction plate assemblies are manufactured according to the method according to the present invention.

[0009] Advantageously here, the manufacturing time of the friction structure assembly can be significantly shortened by the simultaneous machining or manufacturing of the outer friction plates and the inner friction plates. In addition, better utilization of the tools can thus also be achieved. Furthermore, by the simultaneous machining or manufacturing of the outer friction plates and the inner friction plates, the geometric accuracy of the two friction plates can be better coordinated with each other or the tolerances can be reduced.

[0010] In order to further improve these effects, according to an implementation variant of the present invention, it can be provided that the first and second friction plate rings are each manufactured from a carrier ring, and the friction linings are applied to the carrier ring from one side or on both sides, wherein the connection of the friction linings to the carrier rings for the first and second friction plate rings and / or the hardening of the friction linings are carried out together in a tool.

[0011] According to another implementation variant of the present invention, a press is preferably used as the tool, because the aforementioned method steps for manufacturing the outer friction plates and the inner friction plates together can be implemented more simply thereby.

[0012] According to an implementation variant, it can be provided that the compaction of the friction linings is also carried out in the press, in order to also improve the component accuracy thereby.

[0013] The first and / or second friction plate rings are preferably grooved in the tool, whereby the manufacturing depth of the friction plates using the tool can be increased again. In addition to forming cooling channels, the dimensional accuracy of the friction plates can also be improved using this step.

[0014] According to another implementation variant of the present invention, it can be provided that the first and second friction plate rings are connected to each other before being placed in the tool, whereby the joint operation of the two friction plate rings can be simplified, especially the positioning of the two friction plate rings in the tool can also be simplified.

[0015] Here, according to an implementation variant, it can be provided that at least one theoretical fracture position is provided for the connection of the first and second friction plate rings, in order to simplify the separation after machining or to prevent undesired breakouts in the area of the friction plate rings.

[0016] Advantageously here, according to an implementation variant, the connection is released in the tool, whereby a further reduction in the machining time of the friction plate rings can be achieved.

[0017] However, in order to more precisely position the friction plate ring in the tool, according to another implementation variant of the present invention, it can also be provided that a tool with an inner centering device for the second friction plate ring and an outer centering device for the first friction plate ring is used.

[0018] According to another implementation variant of the present invention, it can be provided that marks are assigned to the inner friction plate ring and the outer friction plate ring in the tool. Thus, a relative change in the installation positions of the friction plates of the friction plate group with respect to each other can be implemented more simply, and thereby tool inaccuracies, especially tool inaccuracies in terms of the flatness of the tool surface, can be compensated more simply.

[0019] It is also possible to more simply combine the individual friction plates into a friction plate group, that is, according to another implementation variant of the present invention, the first axial ring thickness of the first friction plate ring has a tolerance of at most ±0.02 mm, and / or the second axial ring thickness of the second friction plate ring has a tolerance of at most ±0.02 mm, and / or the first friction plate ring and the second friction plate ring have a tolerance of at most ±0.02 mm for flatness according to ISO 1101:2017 - 09.

[0020] According to another implementation variant of the present invention, it can be provided that the first axial ring thicknesses of all the first friction plate rings of the outer friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm, and / or the second axial ring thicknesses of all the second friction plate rings of the inner friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm, and / or the axial ring thicknesses of all the first friction plate rings of the outer friction plate group and the axial ring thicknesses of all the second friction plate rings of the inner friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm. In other words, the friction plate group can be constructed from friction plates that are very uniform in terms of thickness deviation. Description of the Drawings

[0021] To better understand the present invention, the present invention will be described in more detail with the aid of the following figures.

[0022] They are shown respectively in simplified schematic diagrams:

[0023] Figure 1 Showing a radial dual clutch;

[0024] Figure 2 Showing a partial view of a facing - type friction plate;

[0025] Figure 3 Showing the arrangement structure of outer friction plates and inner friction plates on an extrusion support;

[0026] Figure 4 Showing a press. Detailed Embodiments

[0027] First, it is stipulated that the same components in different described embodiments are provided with the same reference numerals or the same component names. Among them, the disclosure contained throughout the specification can be transferred meaningfully to the same components with the same reference numerals or the same component names. The positional descriptions selected in the specification, such as up, down, side, etc., also relate to the directly described and shown drawings, and these positional descriptions are transferred meaningfully to the new positions when the positions change.

[0028] Figure 1 A partial view of a radial dual clutch 1, in particular a radial dual clutch for a dual clutch transmission, is shown in a simplified manner. The dual clutch 1 has an outer friction plate pack 2 for the first clutch and an inner friction plate pack 3 for the second clutch. The inner friction plate pack 3 is arranged inside (below) the outer friction plate pack 2 when observed in the radial direction 4. Nevertheless, in the scope of the present invention, there is a preferred space-saving implementation variant of the dual clutch 1, that is, the inner friction plate pack 3 is arranged offset axially with respect to the outer friction plate pack.

[0029] Preferably, the outer friction plate pack 2 and the inner friction plate pack 5 have the same number of friction plates.

[0030] The outer friction plate pack 2 has at least one inner friction plate 6, in particular a plurality of inner friction plates 6, and at least one outer friction plate 7, in particular a plurality of outer friction plates 7. The inner friction plates and outer friction plates can also be referred to as friction plates. The inner friction plates 6 and the outer friction plates 7 are alternately arranged successively in the axial direction 5. Through a corresponding actuating mechanism, the inner friction plates 6 can be adjusted relative to the outer friction plates 7 in the axial direction 5, so that a frictional engagement is formed between the inner friction plates 6 and the outer friction plates 7.

[0031] The number of the inner friction plates 6 and the outer friction plates 7 can be selected, for example, respectively from the range of 1 to 20, in particular 2 to 20. Therefore, the specific numbers of the inner friction plates and the outer friction plates 6, 7 of the outer friction plate pack 2 should not be understood restrictively. Figure 1 as specifically shown in

[0032] The inner friction plate 6 has at least one driving element, for example in the form of an external tooth part, on the radially inner end face. The outer friction plate 7 also has at least one driving element, for example in the form of flags, on the radially outer end face. Through the driving elements, a non-rotating relative connection with other components of the friction structure assembly (such as the shaft or housing of the friction structure assembly) can be established, especially as is known per se through an inner friction plate support 8 (the inner friction plate 8 is arranged on the inner friction plate support) and an outer friction plate support 9 (the outer friction plate 7 is arranged on the outer friction plate support).

[0033] The inner friction plate group 3 has at least one inner friction plate 10, in particular a plurality of inner friction plates 10, and at least one outer friction plate 11, in particular a plurality of outer friction plates 11. The inner and outer friction plates can also be referred to as friction plates. The inner friction plates 10 and the outer friction plates 11 are alternately arranged successively in the axial direction 5. By means of a corresponding actuating mechanism, the inner friction plates 10 can be adjusted relative to the outer friction plates 11 in the axial direction 5, so that a frictional engagement is formed between the inner friction plates 10 and the outer friction plates 11.

[0034] The number of the inner friction plates 10 and the outer friction plates 11 of the friction plate group 3 can be selected, for example, respectively from the range of 1 to 20, in particular 2 to 20. Therefore, the specifically shown numbers of the inner friction plates 10 and the outer friction plates 11 of the friction plate group 3 should not be understood restrictively. Figure 1 in

[0035] The inner friction plate 10 has at least one driving element, for example in the form of an external tooth portion, on the axially inner end face. The outer friction plate 11 also has at least one driving element, for example in the form of a lobe, on the axially outer end face. By means of the driving elements, a non-rotational relative connection can be established with other components of the friction structure assembly (for example, the shaft or the housing of the friction structure assembly), in particular through the inner friction plate support 12 (on which the inner friction plate 10 is arranged) and the outer friction plate support 13 (on which the outer friction plate 11 is arranged) as is known per se.

[0036] This principle structure of the dual clutch 1 is known from the prior art. For other details thereof, reference is made to the relevant prior art.

[0037] The inner friction plates 6 of the outer friction plate group 2 and the inner friction plates 10 of the inner friction plate group 3 can be made of friction material or are preferably configured as so-called facing-type friction plates. The outer friction plates 7 of the outer friction plate group 2 and the outer friction plates 11 of the inner friction plate group 3 can be configured as so-called mating friction plates in this case.

[0038] However, there is also the possibility of a reverse arrangement structure, that is, the inner friction plates 6 of the outer friction plate group 2 and the inner friction plates 10 of the inner friction plate group 3 are configured as mating friction plates, while the outer friction plates 7 of the outer friction plate group 2 and the outer friction plates 11 of the inner friction plate group 3 are made of friction material or are preferably configured as facing-type friction plates.

[0039] Mating friction plates are friction plates that do not have a friction lining and are made only of metal, in particular of steel.

[0040] As can be seen from Figure 2As can be seen, a facing friction plate is a friction plate having at least one friction facing 16 on one or both sides on a support, in particular on a carrier ring 15. The friction facing 16 can be formed completely integrally. However, there is also the possibility that the friction facing 16 is formed in segments, i.e., includes a plurality of segments, which are arranged side by side circumferentially and in particular spaced apart from each other on the support. Preferably, all the friction facings 16 of a friction plate are formed identically. However, different friction facings 16 can also be provided on one friction plate.

[0041] The friction facing 16, in particular an annular friction facing, is arranged along the radially outer circumference. The friction facing 16 can be arranged as can be seen from Figure 2 directly connected to the radially outer circumference, i.e., to the peripheral surface 17 of the support, or arranged spaced apart from the radially outer circumference, i.e., radially inwardly offset.

[0042] The connection of the friction facing 16 to the support is usually effected by bonding, in particular using a resin.

[0043] The support is in particular made of a metallic material, preferably of steel.

[0044] The friction facing 16 is in particular formed by a fiber-reinforced resin (e.g., a phenolic resin), for example formed by resin-impregnated paper. If necessary, the friction facing 16 can also have friction particles, such as emery particles, etc., in and / or dispersed into the resin matrix. Such friction facings 16 are known from the prior art, and in this regard, the prior art is referred to in order to avoid repetition.

[0045] The friction facing 16 can also be a dry-running friction facing of a molding press. For this purpose, a mixture can be produced from the components of the friction facing 8, which mixture is then extruded into a pressed article in a press, if necessary in a hot press, with an increase in temperature (e.g., at a temperature between 100 °C and 190 °C).

[0046] If the friction plate is made of a friction material, the friction plate can be made of the materials described or known for the friction facing 16.

[0047] All the facing friction plates or friction plates made of a friction material provided in the dual clutch 1 can be implemented identically at least in terms of the materials or composites constituting them. All the mating friction plates of the dual clutch can also be identically constituted at least in terms of the materials constituting them. In the case of occupation on both sides of the facing friction plate, there is the possibility that the friction facing 16 of one end face is formed differently from the friction facing 16 of the second end face. In particular, this can relate to the precise configuration of the slotting of the friction facing 16, which will be described in more detail later.

[0048] Next, it will be concerned only more with the friction plate assembly 18, as can be seen in it as an implementation variant. Figure 3 As can be seen. However, the following-described implementation can be applied to all the other friction plate assemblies 18 of the dual clutch 1 (or generally denoted as the friction structure assembly). That is, all the inner friction plates 6 of the outer friction plate group 2 and all the inner friction plates 10 of the inner friction plate group 3 (each inner friction plate 6 of the outer friction plate group 2 together with the inner friction plate 10 of the inner friction plate group 3) or all the outer friction plates 7 of the outer friction plate group 2 and all the outer friction plates 11 of the inner friction plate group 2 (each outer friction plate 7 of the outer friction plate group 2 together with the outer friction plate 11 of the inner friction plate group 3) are manufactured identically.

[0049] There is also the possibility here that all the inner friction plates 6 of the outer friction plate group 2 and all the outer friction plates 11 of the inner friction plate group 3 (each inner friction plate 6 of the outer friction plate group 2 together with the outer friction plate 11 of the inner friction plate group 3) or all the outer friction plates 7 of the outer friction plate group 2 and all the inner friction plates 10 of the inner friction plate group 3 (each outer friction plate 7 of the outer friction plate group 2 together with the inner friction plate 10 of the inner friction plate group 3) are manufactured identically.

[0050] One or each friction plate assembly 18 within the scope of the present invention includes: a first friction plate ring 19 having a first inner diameter 20 and a first axial ring thickness 21 (as can be seen from Figure 4 ); a second friction plate ring 22 having a second outer diameter 23 and a second axial ring thickness 24 (as can be seen from Figure 4 ). The second outer diameter 23 of the second friction plate ring 22 is smaller than the first inner diameter 20 of the first friction plate ring 19. Thus, it is possible that, in order to manufacture the friction plate assembly 18, the second friction plate ring 22 is arranged within the first friction plate ring 19 (when observed in the radial direction 4).

[0051] Therefore, the friction plate assembly 18 is composed of or includes the friction plates formed by the first friction plate ring 19 of the outer friction plate group 2 and the friction plates formed by the second friction plate ring 22 of the inner friction plate group 3. Here, the first friction plate ring 19 can form the outer friction plate 7 or the inner friction plate 6 of the outer friction plate group 2, while the friction plate ring 22 can form the outer friction plate 11 or the inner friction plate 10 of the inner friction plate group 3. Preferably, in the friction plate assembly 18, the outer friction plates 7 of the outer friction plate group 2 are combined with the outer friction plates 11 of the inner friction plate group 3, or the inner friction plates 6 of the outer friction plate group 2 are combined with the inner friction plates 10 of the inner friction plate group 3. However, a hybrid variant of the outer friction plates 7, 11 and the inner friction plates 6, 10 is also possible.

[0052] By simultaneously manufacturing the friction discs of the outer friction disc pack 2 and the friction discs of the inner friction disc pack 3 and taking into account the adaptation of the tool 25, in particular the bearing surface 26 (on which the two friction disc rings 19, 22 are placed during manufacturing), the first axial ring thickness 21 of the first friction disc ring 19 deviates from the second axial ring thickness 24 of the second friction disc ring 22 by at most 0.05 mm, in particular at most 0.04 mm. Thus, the two friction disc rings 19, 22 have very small tolerances in terms of their theoretical dimensions.

[0053] Advantageously here, when analyzed separately using FFT (Fast Fourier Transformation), the 1st order amplitude of the thickness fluctuations has a value of at most 0.02 mm, in particular at most 0.015 mm, and, if necessary, the 2nd order amplitude of the thickness fluctuations has a value of at most 0.015 mm, in particular at most 0.01 mm.

[0054] According to an implementation variant, it can also be provided here that the first friction disc ring 19 has a tolerance of at most ±0.02 mm for the first axial ring thickness 21, and / or the second friction disc ring 22 has a tolerance of at most ±0.02 mm for the second axial ring thickness 24.

[0055] According to another implementation variant, it can be provided that the first friction disc ring 19 and the second friction disc ring 22 have a tolerance of at most ±0.02 mm for flatness in accordance with ISO 1101:2017-09. The flatness can be measured using a rotary laser, for example the rotary laser T430 from Status Pro Maschinenmesstechnik GmbH.

[0056] Thus, within the scope of the present invention, it is possible, depending on the implementation variant, to compensate for the inclination or bowl-shaped or corrugated surfaces of the tool components of the tool 25 for manufacturing the friction disc assembly 18, i.e. for a pair of friction discs, or to reduce the tolerances of the friction discs caused thereby, so that in particular the friction discs can be better used in the radial dual clutch 1, and the structural length of the outer friction disc pack 2 and the structural length of the inner friction disc pack 3 can be reduced in terms of the correspondingly observed difference in the axial direction 5 (see Figure 1 ) without costly reworking of the individual friction discs.

[0057] For the sake of completeness only, it should be noted that deviations in the theoretical geometry of the tool 25 or the inclination or bowl-shaped or wavy surfaces of the tool components are generally not visible to the naked eye.

[0058] According to a further embodiment variant of the present invention, it can be provided that the first axial ring thicknesses of all the first friction rings of the outer friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm, and / or the second axial ring thicknesses of all the second friction rings of the inner friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm, and / or the axial ring thicknesses of all the first friction rings of the outer friction plate group and the axial ring thicknesses of all the second friction rings of the inner friction plate group deviate from each other by at most 0.05 mm, especially at most 0.04 mm. Thus, the outer friction plate group 2 and the inner friction plate group 2 can be constructed or composed of friction plates which are respectively within the range of 0 mm to 0.05 mm mentioned in terms of their thickness deviation.

[0059] In order to manufacture the friction plate assembly 18 and thus the friction plates for the dual clutch 1, especially the radial dual clutch, first a first friction plate ring having a first inner diameter and a second friction plate ring having a second outer diameter are provided, wherein the second outer diameter is smaller than the first inner diameter. As long as the dimensions of the friction plate rings do not change during manufacturing, the first friction plate ring corresponds to the first friction ring 19, and the second friction plate ring corresponds to the second friction ring 22. However, as will be explained further below, this is not necessary, so the first friction plate ring and the second friction plate ring can thus also be referred to as semi-finished products.

[0060] In the tool 25, the second friction plate ring is arranged radially within the first friction plate ring, especially the second friction plate is placed on the support surface 26 of the tool 25 and then machined using the tool 25 or in the tool 25. Thus, the second friction plate ring and the first friction plate ring are machined together in the tool or using the tool 25.

[0061] As already explained, a facing-type friction plate is preferably manufactured by the method according to the present invention. According to an embodiment variant of the method, it can be provided that the first and second friction plate rings are respectively manufactured from a carrier ring 15, and the friction lining 16 is applied to the carrier ring from one side or on both sides (see Figure 2 ). For this purpose, the friction lining blank is placed on the respective carrier ring 15. The mass production of the friction lining blanks is preferably carried out before being placed on the carrier ring 15.

[0062] Then in the tool 25 (which is preferably a press 27 according to a preferred embodiment variant, see Figure 4))The connection of the friction lining blank to the respective carrier rings 15 for the first and second friction plate rings in the tool 25 can be effected. For this purpose, adhesives or other bonding agents can be used. Alternatively or additionally thereto, in the resin-bonded friction lining 16 (i.e., in particular the aforementioned friction lining 16 comprising a fibrous matrix), the resin of the friction lining 16 or the precursor of said resin can be considered. Additionally or alternatively, the resin-bonded friction lining or the friction plate can be hardened in the tool 25, i.e., the precursor of the resin is polymerized and / or crosslinked. This can be carried out with an increase in temperature and / or an increase in pressure. The temperature can depend on the respective resin here. The temperature can be, for example, between 100 °C and 250 °C. The pressure can be, for example, between 80 N / cm 2 and 5000 N / cm 2 between. The processing time in the tool 25 can be between 0.3 minutes and 10 minutes, in particular between 1 minute and 10 minutes.

[0063] As mentioned, it is preferred to use the press 27 as the tool 25. The term "tool" should be understood here in a broad sense. When the press 27 is understood as a machine, the tool 25 in the narrow sense is the support and, if necessary, the clamping tool for clamping the friction plate rings.

[0064] Using the press 27 as a tool for manufacturing the friction plate assembly 18 also has the advantage that, according to another implementation variant of the method, continuous compaction (in particular simultaneous hardening) of the friction lining 16 or the friction lining blank can thus be effected.

[0065] The compaction can be produced identically within tolerances over the entire friction lining 16. However, it can also be provided that different degrees of compaction zones are provided in a respective one or more friction linings 16.

[0066] According to another implementation variant, it can also be provided here that the first and / or second friction plate rings are grooved by compaction in the groove region in the tool 25, so that the first and / or second friction plate rings are provided with grooves 28 (see Figure 3 ). The grooves 28 are in particular for cooling the friction plates, especially when the dual clutch 1 is a wet-running dual clutch 1. The grooves 28 are used in particular to guide the coolant during frictional engagement.

[0067] It should be mentioned that the grooves 28 can also be produced without compaction of the friction lining 16.

[0068] Within the scope of the present invention, it is also possible to manufacture friction plates for a dry dual clutch 1. These friction plates are not flushed with a coolant, such as cooling oil.

[0069] In order to form the groove 28, corresponding protrusions can be provided in the bearing surface 26 of the tool 25 and / or in the upper die 29 of the press 27, which protrusions are pressed into the corresponding friction lining 16 during extrusion, especially when the resin of the friction lining 16 is hardened simultaneously.

[0070] The shape and / or arrangement of the groove 28 can be different and especially depends on the corresponding application of the dual clutch 1 or the friction plate. The groove can, for example, have a simple linear, for example radial or curved, orientation. It is also possible to produce additional patterns, such as a waffle pattern, etc.

[0071] There is also the possibility that the groove 28 of the first friction plate ring 19 is configured differently from the groove 28 of the second friction plate ring 22. This difference can relate to the geometry, such as depth, width, shape of the cross-section and / or orientation of the groove and / or the arrangement structure of the groove on the friction plate ring 19 or 22.

[0072] The first and second friction plate rings 19, 22 can be placed into the tool 25 or on the bearing surface 26 independently of one another. In this regard, it is advantageous if the tool 25 has an inner centering device 30 or inner clamping device for the second friction plate ring and an outer centering device 31 or outer clamping device for the first friction plate ring.

[0073] The inner centering device can, for example, be configured in the form of a centering mandrel onto which the second friction plate ring is inserted. Correspondingly, the outer diameter of the clamping mandrel is adapted to the inner diameter of the second friction plate ring, so that the first friction plate ring can be abutted against the clamping mandrel.

[0074] The outer centering device 31 can be formed by a plurality of abutting elements (three finger-shaped abutting elements are shown in Figure 3 where the number is non-limiting), which abutting elements extend radially inwards, and the first friction plate ring can abut against the abutting elements with its circumferential surface. The abutting elements are preferably arranged on the tool 25 so as to be evenly distributed on the circumference of the first friction plate ring.

[0075] However, according to another embodiment variant, it can also be provided that the first and second friction plate rings are connected to one another before being placed into the tool 25. Thereby, one friction plate in the two friction plate rings correspondingly centers the other friction plate ring, so that the tool 25 can thus be equipped with only one centering device, such as a centering mandrel.

[0076] The connection between the two friction plate rings can, for example, be effected by two or more connecting tabs 32. The connecting tabs 32 can be connected to the inner peripheral surface of the first friction plate ring on one side and to the outer peripheral surface of the second friction plate ring, in particular formed onto the inner peripheral surface of the first friction plate ring and the outer peripheral surface of the second friction plate ring. However, the connection between the two friction plate rings can also be configured differently.

[0077] According to an implementation variant, it can be provided that at least one theoretical breaking point 33 is assigned to the connection between the first friction plate ring and the second friction plate ring. The theoretical breaking point 33 can, for example, be configured as a groove or indentation or the like.

[0078] Instead of or in addition to this, according to another implementation variant, it can be provided that the connection is released in the tool 25. For this purpose, the tool 25 can, for example, be equipped with a cutting device, for example a cutting tool, which cuts the connection, for example the connecting tab 32, in the immediate vicinity of the peripheral surface of the friction plate ring.

[0079] According to another implementation variant, it can be provided that marks 34 are assigned to the first friction plate ring 19 and the second friction plate ring 22 in the tool 25. The marks 34 can, for example, be points, lines, indentations or the like. By means of the marks 34, the first friction plate ring 19 and the second friction plate ring 22 can be rotationally misaligned in the outer friction plate group 2 or the inner friction plate group 3. This means that the first friction plate ring 19 in the outer friction plate group 2 is arranged torsionally by a predefinable angular value, for example a value between 5° and 45°, so that the marks 34 are arranged non-aligned in the axial direction 5. The same applies to the second friction plate ring 22 and the inner friction plate group 3.

[0080] With this implementation variant, it is possible to better compensate for tool-related tolerances in the flatness and thickness of the friction plates in the finished friction plate group, since the deviations from the theoretical values always occur at the same positions on the friction plates and can therefore be compensated by the mutual torsion of the friction plates.

[0081] According to another implementation variant of the invention, it can also be provided that a tool 25, in particular a press 27, is used which has a plurality of cavities for simultaneously manufacturing a plurality of first friction plate rings 19 and a plurality of second friction plate rings 22. In this case, the marks 34 can also be used for cavity traceability. For this purpose, the marks 34 of the individual cavities can be different. However, the marks 34 can also be analyzed in connection with the position of the axial thickness deviation of the friction plate rings 19, 22. In this case, the marks 34 can also be configured identically for all cavities.

[0082] It should be noted here that, like the radial widths of the friction plate rings 19, 22, the radial distance shown in Figure 3 should not be understood restrictively between the first and second friction plate rings 19, 22.

[0083] The various embodiments illustrate or describe possible implementation variants of the dual clutch 1 or the friction plate assembly 18. Here, it should be noted that the present invention is not limited to the particularly illustrated implementation variants, but rather different combinations of the various implementation variants are also possible, and such possibilities of variation are within the capabilities of those skilled in the art working in this technical field according to the teachings of the technical process of the present invention.

[0084] The scope of protection is determined by the claims. However, the description and the drawings should be used to interpret the claims. The individual features or combinations of features from the different embodiments shown and described can themselves be independent creative solutions. The purpose based on the independent creative solutions can be derived from the description.

[0085] All descriptions of value ranges in this specification should be understood as: the value ranges together include any and all partial ranges therein. For example, the description of 1 to 10 should be understood as including together all partial ranges starting from the lower limit of 1 to the upper limit of 10, that is, all partial ranges starting with a lower limit of 1 or greater and ending with an upper limit of 10 or less, such as 1 to 1.7 or 3.2 to 8.1 or 5.5 to 10.

[0086] Finally, it should be noted that, for a better understanding of the structure of the dual clutch 1 or the friction plate assembly 18, the dual clutch or the friction plate assembly is not necessarily shown to scale.

[0087] List of Reference Numerals

[0088] 1 Dual clutch

[0089] 2 Outer friction plate group

[0090] 3 Inner friction plate group

[0091] 4 Radial direction

[0092] 5 Axial direction

[0093] 6 Inner friction plate

[0094] 7 Outer friction plate

[0095] 8 Inner friction plate support

[0096] 9 Outer friction plate support

[0097] 10 Inner friction plate

[0098] 11 Outer friction plate

[0099] 12 Inner friction plate support

[0100] 13 Outer friction plate support 14

[0102] 15 Carrier ring

[0103] 16 Friction lining

[0104] 17 Peripheral surface

[0105] 18 Friction plate assembly

[0106] 19 Friction plate ring

[0107] 20 Inner diameter

[0108] 21 Ring thickness

[0109] 22 Friction plate ring

[0110] 23 Outer diameter

[0111] 24 Ring thickness

[0112] 25 Tool

[0113] 26 Support surface

[0114] 27 Press

[0115] 28 Groove

[0116] 29 Upper punch

[0117] 30 Inner centering device

[0118] 31 Outer centering device

[0119] 32 Connecting tab

[0120] 33 Theoretical fracture position

[0121] 34 Mark

Claims

1. A method for manufacturing friction plates for a dual clutch (1), the method comprising the following steps: Providing a first friction plate ring having a first inner diameter, Providing a second friction plate ring having a second outer diameter, wherein the second outer diameter is smaller than the first inner diameter, Machining the first friction plate ring and the second friction plate ring in a tool (25) for manufacturing friction plates, Characterized in that, The second friction plate ring is disposed within the first friction plate ring, and the second friction plate ring and the first friction plate ring are machined together in the tool (25) to form a friction plate assembly (18), the friction plate assembly including a first friction plate ring (19) corresponding to the first friction plate ring and having a first axial ring thickness (21) and a second friction plate ring (22) corresponding to the second friction plate ring and having a second axial ring thickness (24), and, - The first axial ring thickness (21) of the first friction plate ring (19) has a tolerance of at most ±0.02 mm, and / or the second axial ring thickness (24) of the second friction plate ring (22) has a tolerance of at most ±0.02 mm, or - The first friction plate ring (19) and the second friction plate ring (22) have a tolerance of at most ±0.02 mm for flatness in accordance with ISO 1101:2017-09, wherein the first friction plate ring (19) and the second friction plate ring (22) are placed independently of each other on a support surface (26) of the tool (25).

2. The method according to claim 1, characterized in that, The first and second friction plate rings are each manufactured from a carrier ring (15), and a friction lining (16) or a friction lining blank is applied to the carrier ring from one side or on both sides, wherein the connection of the friction lining (16) or the friction lining blank to the carrier rings (15) for the first and second friction plate rings and / or the hardening of the friction lining (16) are carried out together in the tool (25).

3. The method according to claim 2, wherein A press (27) is used as the tool (25).

4. The method according to claim 3, wherein The compaction of the friction lining (16) is also carried out in the press (27).

5. The method according to any one of claims 1 to 4, characterized in that The first and / or second friction plate rings are slotted in the tool (25).

6. The method according to any one of claims 1 to 4, characterized in that, The first and second friction plate rings are connected to each other before being placed into the tool (25).

7. The method according to claim 6, characterized in that, At least one theoretical fracture position (33) is provided for the connection of the first and second friction plate rings.

8. The method according to claim 6, characterized in that, The connection is loosened in the tool (25).

9. The method according to any one of claims 1 to 4, characterized in that, The tool (25) has an inner centering device (30) for the second friction plate ring and an outer centering device (31) for the first friction plate ring.

10. The method according to any one of claims 1 to 4, characterized in that, Marks (34) are provided for the first friction plate ring and the second friction plate ring in the tool (25).

11. The method according to claim 1, wherein The dual clutch (1) is a radial dual clutch.

12. Friction plate assembly (18), comprising: A first friction plate ring (19) having a first inner diameter (20) and a first axial ring thickness (21); a second friction plate ring (22) having a second outer diameter (23) and a second axial ring thickness (24), wherein the second outer diameter (23) is smaller than the first inner diameter (20), and the second friction plate ring (22) can be arranged within the first friction plate ring (19), characterized in that the first axial ring thickness (21) of the first friction plate ring (19) deviates from the second axial ring thickness (24) of the second friction plate ring (22) by a maximum of 0.05 mm, and - the first axial ring thickness (21) of the first friction plate ring (19) has a tolerance of a maximum of ±0.02 mm, and / or the second axial ring thickness (24) of the second friction plate ring (22) has a tolerance of a maximum of ±0.02 mm, or - the first friction plate ring (19) and the second friction plate ring (22) have a tolerance of a maximum of ±0.02 mm for flatness in accordance with ISO 1101:2017-09, wherein the first friction plate ring (19) and the second friction plate ring (22) are placed independently of each other on a support surface (26) of a tool (25) for manufacturing friction plates.

13. The friction plate assembly (18) according to claim 12, characterized in that, The first axial ring thickness (21) of the first friction plate ring (19) deviates from the second axial ring thickness (24) of the second friction plate ring (22) by a maximum of 0.04 mm.

14. Dual clutch (1), including an outer friction plate group (2) and an inner friction plate group (3), characterized in that, The outer friction plate group (2) and the inner friction plate group (3) are formed by a friction plate assembly (18) according to one of claims 12 to 13, the friction plate assembly being manufactured according to the method according to one of claims 1 to 11.

15. The dual clutch according to claim 14, characterized in that, The first axial ring thicknesses (21) of all the first friction plate rings (19) of the outer friction plate group (2) deviate from each other by a maximum of 0.05 mm, and / or the second axial ring thicknesses (24) of all the second friction plate rings (22) of the inner friction plate group (3) deviate from each other by a maximum of 0.05 mm.

16. The dual clutch according to claim 14 or 15, characterized in that, The axial ring thicknesses of all the first friction plate rings (19) of the outer friction plate group (2) and the axial ring thicknesses (24) of all the second friction plate rings (22) of the inner friction plate group (3) deviate from each other by a maximum of 0.05 mm.

17. The dual clutch according to claim 14, characterized in that, The dual clutch (1) is a radial dual clutch.

18. The dual clutch according to claim 15, characterized in that, The first axial ring thicknesses (21) of all the first friction plate rings (19) of the outer friction plate group (2) deviate from each other by a maximum of 0.04 m.

19. The dual clutch according to claim 15, characterized in that, The second axial ring thicknesses (24) of all the second friction plate rings (22) of the inner friction plate group (3) deviate from each other by a maximum of 0.04 mm.

20. The dual clutch according to claim 16, characterized in that, The axial ring thicknesses of all the first friction plate rings (19) of the outer friction plate group (2) and the axial ring thicknesses (24) of all the second friction plate rings (22) of the inner friction plate group (3) deviate from each other by a maximum of 0.04 mm.

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