Friction clutch and method for manufacturing a squeeze plate for a friction clutch

Abstract

The invention relates to a friction clutch for a drive train with an axis of rotation, which has at least the following components: a friction disk; and a pressure plate, the pressure plate having a back side with a cam ring for receiving an axial force, the axial force being used to press the pressure plate axially against the friction disk, and the pressure plate also having a friction surface for transmitting a torque from the pressure plate to the friction disk in a friction-locking manner in a squeezed state. The friction clutch is characterized primarily in that the cam ring comprises at least one web formed integrally with the pressure plate, the web being connected to the pressure plate radially inwardly and extending radially outwardly. With the friction clutch or the manufacturing method proposed here, a separate matching with the cam ring can be achieved cost-effectively.

Description

Technical Field

[0001] The invention relates to a friction clutch for a drive train having an axis of rotation, a drive train having such a friction clutch, a motor vehicle having such a drive train, and a method for producing a pressure plate for a friction clutch. Background Art

[0002] Friction clutches for use in drive trains, for example in motor vehicles, are known from the prior art. The friction clutch intervenes in the torque change process so that the torque transmission between the input and output of the friction clutch around the rotation axis can be actively, i.e., can be controlled from the outside. In addition to complete torque transmission and complete disconnection, the friction clutch can usually also be used for speed uniformity and / or for reducing torque transmission, in which the torque is transmitted in a slipping manner. In order to transmit torque, a friction group is provided in the friction clutch, in which a compression plate with a friction surface and a corresponding friction disk can be axially pressed against each other, for example, in a manner that can be controlled by means of an operating device. For this purpose, the compression plate can be moved axially toward the friction disk. A counter-pressure plate is usually also provided so that the friction disk can be pressed between two plates (compression plate and counter-pressure plate) and frictionally contact on both sides. Here, the two plates are anti-rotation relative to the input side and the friction disk relative to the output side, or vice versa. Due to the compression force, a friction force is generated by the friction surface, and the multiplication of this friction force with the average radius of the friction surface results in a transmittable torque.

[0003] The squeeze plate must meet the high requirements for a friction surface that is as flat as possible and a high heat capacity under all operating conditions. In addition, the squeeze plate must provide a defined force application point on its back side (axially opposite to the friction surface). This is usually ensured by a so-called cam ring, which has an axial bulge forming at least one back side of the ring, and the operating device acts indirectly (or rarely directly) on the cam ring. Therefore, the squeeze plate is preferably manufactured as a cast component so far. In order to meet the ever-increasing mechanical requirements for the squeeze plate, the squeeze plate is more often manufactured from (flat) sheet materials, preferably by means of cold forming methods, such as stamping. For example, a squeeze plate with a cam ring welded on the back side is known. However, this two-step method is expensive and requires different cam rings for each cam diameter. It is also known to have a squeeze plate with a tab turned from the outside, which tabs respectively form cams for the cam ring. However, such a cam ring is limited by the position of the cam (in some cases, for example, due to the lugs extending radially outwards that are additionally required on the outer edge of the squeeze plate for connecting the leaf spring device) and only works from a minimum axial action height. In addition, known from the outside by means of gap to produce the cam of the squeeze plate. This is only possible for the squeeze plate without lugs for the leaf spring device on the outer edge of the squeeze plate, or need to be subsequently installed, for example welded lugs. Summary of the invention

[0004] Starting from this, the object of the present invention is to at least partially overcome the disadvantages known from the prior art. The features according to the invention are given by the description, for which advantageous configurations are listed. The features of the present invention can be combined in any technically meaningful manner and method, wherein the explanations from the following description and the features from the drawings can also be considered for this, which include supplementary configurations of the present invention.

[0005] The invention relates to a friction clutch for a drive train having a rotation axis, which has at least the following components:

[0006] - friction discs; and

[0007] - a pressure plate having a back side with a cam ring for receiving an axial force for pressing the pressure plate axially against the friction disk, and having a friction surface for transmitting a torque from the pressure plate to the friction disk in a frictionally locked manner in a pressed state.

[0008] The friction clutch is mainly characterized in that the cam ring includes at least one web formed integrally with the pressure plate, the web being connected to the pressure plate radially inwardly and extending radially outwardly.

[0009] Unless otherwise explicitly indicated, axial direction, radial direction or rotational direction and corresponding terms are used below with reference to the axis of rotation. Unless otherwise explicitly indicated, the ordinal numbers used in the preceding and following description serve only to distinguish clearly and do not indicate the order or sequence of the components marked. An ordinal number greater than one does not necessarily mean that further such components are present.

[0010] The friction clutch can be used for the purpose mentioned at the outset for actively disconnecting and connecting the torque transmission. For this purpose, the friction clutch comprises a friction disk, which is formed, for example (in a single friction pair) by a preferably axially fixed counter-pressure plate and has a (single) friction side for pressing against a pressure plate. Alternatively, the friction disk is a disk that can be pressed between two plates and for this purpose has a friction side on both sides in the axial direction, preferably formed by a friction lining.

[0011] In addition, a pressure plate with a friction surface is provided, wherein the friction surface can be pressed against the (corresponding) friction side of the friction disk in order to transmit torque in a friction-locking (and preferably also adhesive) manner. The rotation axis of the friction clutch is oriented normally relative to the friction surface (technically, i.e. within a predetermined tolerance range). In order to release the friction pair, i.e. to disconnect the torque transmission, the pressure plate is suspended in the friction clutch in an axially movable manner. In order to receive the corresponding pressure force, a cam ring is formed on the back side of the pressure plate (axially opposite to the friction surface). As a result, a corresponding axial force is provided for pressing the pressure plate axially against the friction disk. The cam ring is preferably provided for cooperating with a diaphragm spring or a lever spring, which is also generally referred to as a disc spring, wherein the disc spring is axially supported on a clutch cover of the friction clutch, which is rotationally fixed relative to the pressure plate (and also relative to the counterpressure plate in the case of a separated friction plate). If it is desired to axially preload the pressure plate, for example by means of a leaf spring arrangement, the pressure plate is connected to the clutch cover in a preloaded manner, for example by means of webs on the edge of the pressure plate, ie radially inside or outside, for example radially outside the friction surface of the pressure plate.

[0012] It is now proposed that the cam ring comprises at least one web which is connected to the extruded plate radially inwardly and extends radially outwardly. The web is formed integrally with the extruded plate, for example, by providing a sheet metal blank as a blank or semi-finished product, which is separated from a flat sheet metal, for example, by stamping. Therefore, the web (when using a finished extruded plate) extends from the area of ​​the friction surface (hereinafter referred to as the outer ring of the extruded plate) toward the center of the extruded plate, for example toward the axis of rotation, or also extends beyond the center. The web is then folded radially outwardly in another manufacturing step, so that the web and the outer ring overlap at least partially. The web forms an axial protrusion on the end side, that is, at the open end of the web or in the case of the open end, which is defined in terms of its radial position and its axial effective height, for example, for introducing an axial force to act on a spiral spring. From this situation, it follows that the radial position and / or the effective height can be set individually without having to change the sheet metal blank (or other type of semi-finished product). In the case of such different compression plates, only the remaining shape of the webs, for example their radially inward extension, differs with different positions of the cam ring.

[0013] It should be noted that the manufacturing method shown here is particularly economically advantageous, for example for mass production, but the extruded plate can also be produced in different ways, such as additive manufacturing, prototyping, hot forming and / or cutting. Advantages of the cam ring with at least one web are, for example, simplified shaping, one-pieceness and / or other post-processing properties.

[0014] The friction clutch proposed here can therefore be adapted to individual customer requirements by means of the individually adaptable position of the cam ring, wherein a plurality of identical components can be used simultaneously, or at least the semi-finished products for the squeeze plate can be manufactured identically and thus in large quantities. In one embodiment, tolerance compensation and / or adjustment of the friction group of the friction clutch can also be carried out by means of the webs. Likewise, if the requirements change or even errors are detected, adaptation can be carried out in a later manufacturing stage or coating stage.

[0015] Furthermore, in an advantageous embodiment of the friction clutch it is provided that the cam ring has a plurality of webs which each form a partial cam with an axial extension.

[0016] It is proposed that the cam ring has a plurality of webs, for example at least three webs, for receiving the forces in a manner that is as evenly distributed as possible. Preferably, an annular shape is formed, wherein a plurality of individual webs and / or individual ridges form individual force introduction points and / or force introduction lines on the webs. If only a single web is provided, it is designed in an annular shape or enables at least approximately annular or compensating introduction of forces into the pressure plate for the most evenly possible, frictionally locked transmission of torque.

[0017] In a preferred embodiment of the friction clutch, the part cams have different effective diameters and / or different effective heights from one another.

[0018] In this embodiment, the force intervention can be introduced into different sub-cams and / or different numbers of sub-cams in a stroke-dependent manner. Independently of this, the force intervention can be displaced relative to the friction surface in a stroke-dependent manner so that the flatness of the friction surface of the pressure plate (and possibly the flatness of the friction disk and the pressure plate) is affected as little as possible when the actuating force acting on the pressure plate increases.

[0019] In an advantageous embodiment of the friction clutch, it is further provided that the at least one web is connected to the rear side of the pressure plate in a materially bonded manner.

[0020] In this embodiment, the back side is connected to the web, i.e. the web is not connected only radially inwardly to the outer ring of the squeeze plate. This results in an additional reinforcement of the cam ring and / or the friction surface (acting on the squeeze plate). Preferably, the web is welded to the back side, particularly preferably by means of a fillet weld. Preferably, the web is connected to the back side of the squeeze plate in the region of the sub-cams, particularly preferably radially overlapping the sub-cams, by a material connection.

[0021] In an advantageous embodiment of the friction clutch, it is further provided that at least one web of the cam ring is spaced apart from the rear side of the pressure plate by a predetermined distance.

[0022] By means of the spacing from the back side of the squeeze plate, the effective height of the sub-cams of the cam ring or the associated webs can be freely set. In addition, in a preferred embodiment, the spring stiffness can be set by a predetermined spring travel, which is limited to the axial spacing from the back side of the squeeze plate, for example. This results in a force-travel-characteristic curve similar to that of a lining spring device. This makes it possible to compensate for excessive engagement speeds and / or operating forces that may cause vibrations, or conversely to achieve vibrations in order to avoid damage to the friction pair or surface. The vibration refers to the axial outward ejection of the friction pair against the engagement direction, which causes torque fluctuations that are usually undesirable. However, this is desired as a last resort and is therefore an allowed operating state of the friction group.

[0023] In a preferred embodiment of the friction clutch, a plurality of webs are provided, at least two of which are each spaced apart from the rear side of the pressure plate at different predetermined distances from one another.

[0024] In one embodiment, the series connection of the stiffness is set by means of different points of action (which can be produced, for example, by different action heights of a plurality of sub-cams on a single or different webs of the cam ring), thereby producing, for example, a desired, for example, discontinuous, force-travel characteristic curve.

[0025] According to another aspect, a drive train is provided, which has at least the following components:

[0026] - at least one driving machine;

[0027] - at least one consumer; and

[0028] - a friction clutch according to the embodiment described above,

[0029] In this case, the drive engine and the at least one consumer are releasably connected to one another in a torque-transmitting manner by means of the friction clutch.

[0030] A drive train, for example a drive train for a motor vehicle, comprises a drive machine, for example an energy conversion machine, preferably an internal combustion engine or an electric drive machine, as a (main) torque source, and at least one consumer for the torque of the drive machine, for example at least one drive wheel of the motor vehicle for its drive, an air conditioning pump and / or a generator. Furthermore, a friction clutch according to the above description is included, wherein the drive machine is detachably connected to the at least one consumer by means of the friction clutch for transmitting torque. In many applications, torque transmission can be achieved in both directions by means of the friction clutch, and inertial energy introduced by, for example, the drive wheel can be converted into electrical energy and / or can be dissipated by means of an engine brake.

[0031] Furthermore, in one embodiment, a plurality of drive engines are provided, which can be connected in series or in parallel or operated decoupled from one another by means of friction clutches, or the torques of the drive engines can be made available separately. An example is a hybrid drive consisting of an electric drive engine and an internal combustion engine, but the internal combustion engine can also be a multi-cylinder engine in which the individual cylinders (groups) can be engaged by means of friction clutches.

[0032] In order to transmit torque or disconnect transmission in a targeted manner and / or by means of a switching transmission mechanism with different transmission ratios, it is particularly advantageous to use the above-mentioned friction clutch. The friction clutch proposed here comprises a squeeze plate, which can be manufactured cost-effectively for multiple applications based on the same semi-finished product and can be matched to individual requirements at the same time.

[0033] According to a further aspect, a motor vehicle is proposed, which has at least one driven wheel and a drive train according to the above-described embodiment.

[0034] The at least one drive wheel is detachably connected to the at least one drive engine in a torque-transmitting manner for driving the motor vehicle.

[0035] Most motor vehicles currently have a front drive, so the drive engine, for example an internal combustion engine or an electric drive engine, is preferably arranged in front of the driver's cab and transversely to the main direction of travel. The installation space is particularly small in this arrangement, and it is therefore particularly advantageous to use a friction clutch of small size. The use of friction clutches in motorized two-wheeled vehicles is similarly configured, for which significantly increased power is required while maintaining the same installation space. At the same time, low costs are required.

[0036] This problem becomes more acute in passenger cars of the European compact class. The functional units used in passenger cars of the compact class are not significantly smaller than in passenger cars of the large class. However, the available installation space and cost margins are usually significantly less in compact cars. The above-mentioned drive train has a friction clutch, wherein the friction clutch or its pressure plate can be individually adapted to different configurations of the pressure plate using the same machine tool in a manufacturing process that remains as unchanged as possible and can be manufactured cost-effectively at the same time. At the same time, the required axial installation space is smaller, but at least not larger, than in known solutions.

[0037] Passenger vehicles are assigned to vehicle classes according to, for example, size, price, weight and power, wherein this definition is subject to continuous changes according to market requirements. Vehicles in the compact and microcar classes according to the European classification are assigned to the subcompact car class in the US market, and in the UK market they correspond to the supermini class or the city car class. Examples of the subcompact car class are the Volkswagen up! or the Renault Twingo. Examples of the compact car class are the Alfa Romeo Mito, the Volkswagen Polo, the Ford Ka+ or the Renault Clio. Known full hybrids in the compact car class are the BMW i3, the Audi A3 e-tron or the Toyota Yaris Hybrid.

[0038] According to another aspect, a method for manufacturing a squeeze plate for a friction clutch is provided, the method comprising at least the following steps:

[0039] i. Providing a sheet metal blank having an outer ring and at least one web extending radially inwardly from the outer ring in one piece, wherein the outer ring constitutes a friction surface and a back side when using the extruded sheet made;

[0040] ii. A sub-cam having an axially extending portion is formed on the at least one tab;

[0041] iii. folding the at least one tab radially outwardly to the back side of the outer ring; and

[0042] iv. After or during step ii and / or step iii, setting the effective diameter and effective height of the at least one sub-cam.

[0043] The manufacturing method proposed here is provided, for example, for a pressure plate of a friction clutch according to the embodiment described above. However, this is only one possible embodiment of a manufacturing method for such a pressure plate.

[0044] The extruded plate that can be produced using this manufacturing method has an outer ring, which has a friction surface on one side, with respect to which the axis of rotation of the subsequent friction clutch is (technically) oriented normally, and has a back side on the opposite side. The back side is provided for introducing an actuating force or an extrusion force. The outer ring has only the radial extension required for the friction surface, or additionally, for example, has a lug on the radial outside, for example for an axial preload mechanism, such as a leaf spring device. In some cases, the extruded plate or the sheet blank has other elements, for example, parts have been attached in intermediate steps, such as welds or milled or formed recesses. Preferably, after step i, for example simultaneously with one of steps ii to iv, any deformation that deviates from the planarity of the sheet forming the sheet blank is preferably carried out with the aid of a single tool.

[0045] First, in step i, a sheet metal blank is provided by an external supplier, for example by punching, laser cutting or water jet cutting and in some cases as a purchased part. The at least one web and in some cases other components are not yet transferred to the final position, but are connected integrally to the outer ring.

[0046] Then, steps ii and iii are performed, wherein step ii is preferably performed first. In some cases, it is advantageous for specific applications, such as adjustment or personalized reprocessing, to first perform step iii, or to perform step ii incompletely, or to repeat step ii after step iii.

[0047] In step ii, for example, the open end of the tab is rounded in order to form a run-out surface or a running surface for the spiral spring. Alternatively or additionally, a groove is formed so that a cam or cam ring (segment) with a defined run-out surface or a running surface is produced on the operating side. In one embodiment, the sub-cam is designed in such a way that a satisfactory run-out surface or a running surface is ensured even if the position of the tab and thus (within a predetermined framework) the position and, if applicable, the orientation of the sub-cam are changed in subsequent steps (for example, step iii or step iv).

[0048] In step iii, the tab is folded over so that a radial overlap with the outer ring of the extruded plate is produced. In a preferred embodiment, the tab is already transferred to its final position here, wherein preferably step ii has already been carried out. This means that, in this embodiment, step iv is integrated into step iii and in some cases into step ii. Alternatively, step iv is a subsequent adjustment step or calibration step, so that in some cases no forming takes place in step iv, but only the correct position is determined. Step iv is then a quality assurance step, which is particularly preferably already integrated into step ii and / or step iii. At least in this case, only one sampling control is sufficient for the correct manufacture of the extruded plate to ensure quality, wherein this sampling control is not regarded as step iv, but on the contrary, step iv is always required.

[0049] The manufacturing method proposed here allows the dimensions of the cam ring to be flexibly adapted to individual customer requirements, wherein standardized blanks and / or identical tools can be used for manufacturing, and for example, a single production line can be used to significantly increase the number of pieces and the pricing. In one embodiment, tolerance compensation and / or adjustment of the friction group of the friction clutch can also be carried out by means of the web, in that the manufacturing method is extended to the assembly of the friction clutch, or the pressed plate is provided in the original state by means of the manufacturing method for (optionally) re-adjusting the assembly of the friction clutch.

[0050] In addition, in an advantageous embodiment of the manufacturing method, the following steps are also included:

[0051] v. Connecting at least one of the webs to the rear side of the outer ring in a materially bonded manner.

[0052] In this embodiment, the at least one tab is connected to the back side in a materially bonded manner, i.e., for example, welded (e.g., spot welded or laser welded), brazed or adhesively bonded, thereby fixing the position of the tab in question and / or reinforcing the press plate and / or preventing wear and friction caused by relative movements between the tab and the back side of the press plate.

[0053] In addition, in an advantageous embodiment of the manufacturing method, the following steps are also included:

[0054] vi. Setting a predetermined axial spacing of at least one of the webs relative to the rear side of the outer ring.

[0055] It is proposed that the axial spacing between the respective webs relative to the back side of the outer ring is set so that a spring element with a predetermined force-travel characteristic curve is provided while fully utilizing the elasticity of the webs. In a preferred embodiment, the spring element can be compacted under load, i.e. the webs can be deformed against the back side under a predetermined axial load, for example under a compressive force and / or a vibration load, so that the spring stiffness increases rapidly (in some cases discontinuously). The compacted position of the webs is advantageous, for example, for a fully engaged state in which, i.e. when a maximum actuating force is applied, the torque is transmitted to the friction disk in an adherent manner. However, during the engagement process, for example, an uneven torque transmission or an excessively rapid increase can be compensated by vibrations. BRIEF DESCRIPTION OF THE DRAWINGS

[0056] The invention described above is explained in detail below with reference to the accompanying drawings showing preferred configurations in the context of the relevant technology. The invention is not limited in any way by the purely schematic drawings, wherein it should be noted that the drawings are not accurate to size and are not suitable for defining dimensional ratios. It is shown:

[0057] Figure 1 : A cross-sectional view of a friction clutch having a first working diameter;

[0058] Figure 2 : A cross-sectional view of a friction clutch having a second working diameter;

[0059] Figure 3 : A cross-sectional view of a friction clutch with welded tabs;

[0060] Figure 4 : A cross-sectional view of a friction clutch having spaced-apart webs;

[0061] Figure 5 : Part of the slab;

[0062] Figure 6 : Extrusion plate with spring travel;

[0063] Figure 7 : force-stroke-diagram; and

[0064] Figure 8 : Drive train in a motor vehicle with a friction clutch. DETAILED DESCRIPTION

[0065] exist Figures 1 to 4 In the figure, purely for the sake of clarity, a friction clutch 1 with a rotation axis 2 is schematically shown in cross section in a substantially identical embodiment. The friction clutch 1 or the friction group shown (pressure plate 8, friction disk 4 and counter-pressure plate 5) can be designed both as normally closed and as normally open. Here, the pressure plate 8 with a cam ring 11 is shown axially in the center, wherein the cam ring 11 is formed by means of folded-over webs 15, 16 or 17. The pressure plate has a back side 10 axially on the side of the webs 15, 16 or 17 and a (first) friction surface 13 axially opposite, which corresponds to the ring section of the pressure plate 8 represented as outer ring 9. The counter-pressure plate 5 is shown on the left side in the figure, to which the clutch cover 30 is connected in a rotationally fixed manner, here (optionally) by means of a threaded connection. The pressure plate 8 is rotationally fixed relative to the counter-pressure plate 5. The counter-pressure plate 5 is, for example, at the same time a flywheel, which can be connected to the driven shaft of the drive engine 25 (see Figure 8 ) connection. On the right side in the figure, a disc spring 32 is axially supported on the clutch cover 30 via a stepped bolt 33, which disc spring is implemented as a diaphragm spring, for example, in the normally closed configuration of the friction group. The disc spring 32 acts on the cam ring 11 of the pressure plate 8 with an effective diameter 22 and an effective height 23, which is measured here, for example, from the back side 10 of the pressure plate 8. The cam ring 11 consists of a plurality of sub-cams 19, 20 or 21, which are (optionally) designed as axially upright open ends of the corresponding webs 15, 16 or 17. The friction disk 4 is arranged here between the counterplate 5, more precisely the (second) friction surface 14 and the pressure plate 8, more precisely the (first) friction surface 13, so that the corresponding friction surface 14 can be frictionally engaged with the corresponding friction side 6 or 7 for disconnectable torque transmission. For this purpose, an axial force 12 can be introduced into the pressure plate 8 via the cam ring 11, so that the pressure plate 8 and the friction disk 4 are displaced toward the counter pressure plate 5 starting from the disengaged state of the friction clutch 1. The friction clutch 1 is then closed and the torque can be transmitted from the counter pressure plate 5 to the clutch hub 31 on the friction disk side, for example to the splice toothing for receiving the transmission input shaft (and thus then in a form-fitting manner).

[0066] exist Figure 1 and Figure 2 It can be seen from the comparison that according to Figure 2 In the embodiment of the invention, the effective diameter 22 is larger. Figure 2 The effective height 23 in the embodiment according to Figure 1 In one embodiment, the material or the size of the web 15 is generally the same. In one embodiment, different effective diameters 22 and / or different effective heights 23 are provided in a single squeeze plate 8. In another embodiment, only a single constant effective diameter 22 and / or a single constant effective height 23 is provided in the friction clutch 1.

[0067] exist Figure 3 The second tab 16 is shown, which is for example connected to the Figure 1 and / or Figure 2 Like the first web 15 , the second web is welded in the region of the second partial cam 20 to the rear side 10 of the pressing plate 8 by means of a weld seam 34 , which is designed as a fillet weld in this case.

[0068] exist Figure 4 The third connecting piece 17 is shown in FIG. Figure 1 and / or Figure 2 The third web 15 and / or the second web 16 are identical, the third web having an axial spacing 24 in the region of the third partial cam 21 relative to the rear side 10 of the pressure plate 8 .

[0069] In one embodiment, for example, Figure 1 , 2 , 3 and / or Figure 4 As shown in , the webs of a single pressure plate 8 are designed differently. In another embodiment, only a single type of web and / or a constant effective diameter 22 and / or a constant effective height 23 are provided in the friction clutch 1 .

[0070] exist Figure 5 2 shows a schematic axial top view of a plate blank 29 in detail, wherein a first web 15, a second web 16, a third web 17 and a fourth web 18 extend from the outer ring 9 toward the center, i.e. toward the axis of rotation 2, and are connected to the outer ring individually but in one piece. In addition, leaf spring lugs 35 on the outer edge of the outer ring 9 are (optionally) shown.

[0071] exist Figure 6 For example, in Figure 4As shown in , a section through the pressure plate 8 is schematically shown. In this respect, reference is made to the above description of the components of the pressure plate 8. The axial distance 24 is here simultaneously the (maximum) spring travel 36, which is elastically reduced when an axial force 12 is applied to the cam ring 11, wherein preferably the web 17 can be pressed against the back side 10 of the pressure plate 8.

[0072] exist Figure 7 A force-travel diagram is shown in FIG. Figure 6 . The ordinate is the force axis 37 and the abscissa is the travel axis 38. An exemplary force-travel characteristic curve 39 of the web 17 initially shows an approximately proportional, i.e. linear, rise with the reduction of the axial distance 24, i.e. the increase of the spring travel 36. As soon as the spring travel 36 ends due to the compaction point, the force-travel characteristic curve 39 suddenly (discontinuously here) rises sharply and tends to infinity, wherein the maximum axial force 12 is the limit in use.

[0073] exist Figure 8 Schematically shows a drive train 3 in a motor vehicle 28. The drive train 3 comprises a (single) drive engine 25 (represented here as an internal combustion engine with cylinder bores), which is provided for driving a left drive wheel 26 and a right drive wheel 27 via a transmission mechanism not explained in detail. A friction clutch 1 is provided in the drive train 3, by means of which the torque transmission to the drive wheels 26, 27 can be interrupted. The drive engine 25 of the drive train 3 is arranged transversely to the longitudinal axis 41 in front of the driver's cab 40.

[0074] With the friction clutch or the production method proposed here, individual adaptation to the cam ring can be achieved cost-effectively.

[0075] Reference numerals list

[0076] 1 Friction clutch

[0077] 2 Axis of rotation

[0078] 3 Drive system

[0079] 4 Friction disc

[0080] 5. Pressure plate

[0081] 6 First friction side

[0082] 7 Second friction side

[0083] 8 Extruded Plate

[0084] 9 Outer Ring

[0085] 10 Dorsal

[0086] 11 Cam ring

[0087] 12 Axial force

[0088] 13 First friction surface

[0089] 14 Second friction surface

[0090] 15 First joint

[0091] 16 Second joint

[0092] 17 Third joint

[0093] 18 Fourth joint

[0094] 19 First Sub-Cam

[0095] 20 Second sub-cam

[0096] 21 Third sub-cam

[0097] 22 Effective diameter

[0098] 23 Action height

[0099] 24 Axial spacing

[0100] 25 Driver

[0101] 26 Left drive wheel

[0102] 27 Right drive wheel

[0103] 28 Motor Vehicles

[0104] 29 Slab

[0105] 30 Clutch cover

[0106] 31 Clutch hub

[0107] 32 Coil Spring

[0108] 33 Step bolt

[0109] 34 Weld

[0110] 35 Leaf spring lug

[0111] 36 Spring travel

[0112] 37 Force axis

[0113] 38 Travel axis

[0114] 39 Force-travel-characteristic curve

[0115] 40 Cab

[0116] 41 Vertical axis

Claims

1. A friction clutch (1) for a drive train (3) having an axis of rotation (2), comprising at least the following components: - a friction disc (4); and a pressure plate (8) having a back side (10) with a cam ring (11) for receiving an axial force (12) for pressing the pressure plate (8) axially against the friction disk (4), and having a friction surface (13) for transmitting a torque from the pressure plate (8) to the friction disk (4) in a friction-locking manner in the pressed state, It is characterized in that The cam ring (11) comprises a plurality of webs (15, 16, 17, 18) formed integrally with the extrusion plate (8), the webs being connected to the extrusion plate (8) radially inwardly and extending radially outwardly, wherein the plurality of webs respectively constitute sub-cams (19, 20, 21) with axial extensions, wherein the sub-cams (19, 20, 21) have mutually different effective diameters (22) and / or mutually different effective heights (23), and at least one web (16) is connected to the back side (10) of the extrusion plate (8) by material locking.

2. The friction clutch (1) according to claim 1, wherein: At least one tab (18) of the cam ring (11) is spaced apart from the back side (10) of the pressure plate (8) by a predetermined distance (24).

3. The friction clutch (1) according to claim 1, wherein: At least two of the plurality of webs (18) are spaced apart from the back side (10) of the compression plate (8) at predetermined intervals (24) different from each other.

4. A drive system (3) comprising at least the following components: - at least one driving machine (25); - at least one drive wheel (26, 27); in, The drive engine (25) and the at least one drive wheel (26, 27) are detachably connected to one another in a torque-transmitting manner by means of a friction clutch (1) according to any one of claims 1 to 3.

5. A motor vehicle (28) having at least one drive wheel (26, 27) and a drive train (3) according to claim 4, in, The at least one drive wheel (26, 27) and the at least one drive engine (25) are detachably connected to each other in a torque-transmitting manner for driving the motor vehicle (28).

6. A method for manufacturing a squeeze plate (8) for a friction clutch (1), comprising at least the following steps: i. Providing a plate blank (29) having an outer ring (9) and a plurality of webs (15, 16, 17, 18) extending radially inwardly from the outer ring (9) in one piece, wherein the outer ring (9) forms a friction surface (13) and a back side (10) when the finished extruded plate (8) is used; ii. forming a sub-cam (19, 20, 21) with an axially extending portion on the plurality of tabs (15, 16, 17, 18); iii. folding the plurality of tabs (15, 16, 17, 18) radially outwardly to the back side (10) of the outer ring (9); and iv. after or during step ii and / or step iii, setting the effective diameter (22) and effective height (23) of the sub-cams (19, 20, 21) so that the sub-cams (19, 20, 21) have different effective diameters (22) and / or different effective heights (23) from each other, v. Connecting at least one of the webs (15, 16, 17, 18) to the rear side (10) of the outer ring (9) in a materially bonded manner.

7. The manufacturing method according to claim 6, further comprising the following steps: vi. Setting a predetermined axial spacing (24) of at least one of the webs relative to the back side (10) of the outer ring (9).

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