DE102015211601A1 - Friction clutch with a rotation axis for releasably connecting an output shaft with a consumer - Google Patents

Abstract

The invention relates to a friction clutch having an axis of rotation for detachably connecting an output shaft to a load, wherein the friction clutch has at least the following components: a friction pack with an axially fixed counterplate, an axially displaceable pressure plate and at least one friction disc arranged axially therebetween Counter-plate and the corresponding pressure plate in the friction pack is compressible, so that by means of the Reibpakets a torque is releasably transferable; - An actuating spring, by means of which the Reibpaket is compressible; and - a mitrotierbarer clutch cover, wherein the counter-plate is disposed axially between the clutch cover and the pressure plate and wherein the clutch cover is axially displaceable and axially fixed by means of at least one tension member with the pressure plate. The friction clutch is mainly characterized in that the at least one tension element is integrally formed by the pressure plate and / or the clutch cover. With the friction clutch proposed here, a simple, cost-effective construction is possible in which at the same time a few separate individual parts can be used.

Description

The invention relates to a friction clutch having an axis of rotation for releasably connecting an output shaft with a consumer, and a drive train, preferably for a motor vehicle.

Various configurations of friction clutches are known from the prior art, by means of which a torque releasably between an output shaft and a consumer, preferably in a motor vehicle, is transferable. For example, a configuration under the name FlexCompact is known, in which the counter-plate is arranged axially between a pressure plate and a clutch cover. The clutch cover is in this case axially fixed to the pressure plate and axially displaceable. By means of an actuating spring, the clutch cover is braced axially against the backing plate. The pressure plate is so indirectly via the clutch cover, which is connected by means of a tension element, by means of the resulting tensile force, starting from the actuating spring on the clutch cover against a arranged between the pressure plate and the counter plate friction pressed. The pressure plate, counter plate and the friction disc arranged therebetween thus form a friction packet, by means of which a torque can be transmitted. As a result of a force acting on the pressure plate contact force results in a frictional force. About the friction surfaces formed between the counter-plate and the friction disc and between the pressure plate and the friction disc multiplied by the mean radius of the friction surfaces and the friction force results in a transmissible torque. The structure of this friction clutch is particularly compact.

In the case of the FlexCompact, the counterplate has at least one (first) flange which axially bridges the axial extent of the pressure plate and the friction plate. Preferably, the at least one (first) flange with a ground disk, which is preferably formed by a so-called flex plate or a Einmassenschwungrad rotatably fixed and axially fixed connected.

Particularly preferably, the counter plate forms a plurality of radial first flanges distributed over the circumference, and the pressure plate forms a plurality of radial second flanges, which engage in the circumferential direction. As a result, a torque of the counter-plate on the pressure plate and vice versa transferable. The counter-plate is preferably, more preferably by means of the ground disc, with an output shaft of a drive unit, for example an internal combustion engine, fixed torque-transmitting connected and preferably axially mounted against this. Accordingly, preferably, the friction disc with an output shaft, preferably a transmission input shaft, fixed torque transmitting connected. Preferably, the actuating spring is a plate spring, which is indirectly or directly supported on the counter plate and is clamped against the axially displaceable clutch cover. Particularly preferred in this case also a (resilient) Abhubfeder is provided, which is axially fixedly connected to the clutch cover and by means of which the plate spring back, so towards the counter plate, supported and so when releasing the Reibpakets forms a (damped) driver.

The already reduced to very few items construction of this prior art friction clutch still has an excessive number of items, which must be mounted individually.

On this basis, the present invention has the object of at least partially overcome the disadvantages known from the prior art. The features according to the invention emerge from the independent claims, to which advantageous embodiments are indicated in the dependent claims. The features of the claims may be combined in any technically meaningful manner, and to this end, the explanations of the following description and features of the figures may be used, which include additional embodiments of the invention.

• – ein Reibpaket mit einer axial fixierten Gegenplatte, einer axial verschiebbaren Anpressplatte und zumindest einer axial dazwischen angeordneten Reibscheibe, welche zwischen der Gegenplatte und der korrespondierenden Anpressplatte im Reibpaket verpressbar ist, sodass mittels des Reibpakets ein Drehmoment lösbar übertragbar ist;
• – eine Betätigungsfeder, mittels welcher das Reibpaket verpressbar ist; und
• – ein mitrotierbarer Kupplungsdeckel,

wobei die Gegenplatte axial zwischen dem Kupplungsdeckel und der Anpressplatte angeordnet ist und wobei der Kupplungsdeckel axial verschiebbar ist und mittels zumindest eines Zugelements mit der Anpressplatte axial fixiert verbunden ist. Die Reibkupplung ist vor allem dadurch gekennzeichnet, dass das zumindest eine Zugelement von der Anpressplatte und/oder dem Kupplungsdeckel einstückig gebildet ist. The invention relates to a friction clutch having an axis of rotation for releasably connecting an output shaft to a load, wherein the friction clutch has at least the following components:

• - A friction pack with an axially fixed counter-plate, an axially displaceable pressure plate and at least one axially disposed therebetween friction, which is compressible between the counter-plate and the corresponding pressure plate in Reibpaket, so that by means of the Reibpakets a torque is releasably transferable;
• - An actuating spring, by means of which the Reibpaket is compressible; and
• - a mitrotierbarer clutch cover,

wherein the counter-plate is arranged axially between the clutch cover and the pressure plate and wherein the clutch cover is axially displaceable and is axially fixed by means of at least one tension member with the pressure plate. The friction clutch is mainly characterized in that the at least one tension element is integrally formed by the pressure plate and / or the clutch cover.

The friction clutch is configured to release a torque from an output shaft to transfer a consumer and vice versa. The counter-plate is fixed axially and forms the axial counter bearing of the friction pack, wherein the friction pack comprises a pressure plate and at least one corresponding friction disc. In the case of a plurality of friction disks, at least one intermediate plate is furthermore provided which, like the pressure plate, is also co-rotating and axially displaceable and can be pressed between two friction disks as a result of a contact force preferably introduced into the pressure plate. The counter plate, pressure plate and possibly existing intermediate plates are referred to here as friction plates. If the pressure plate is moved axially against a corresponding friction disc, the corresponding friction disc is pressed against an adjacent friction plate, for example the counter plate, so that as a result of the contact force on each friction pair, a frictional force is created, by means of which a torque from the friction plates on the at least one friction disc is transferable.

The pressure plate is axially fixed in rotation with the clutch cover and at least zugübertragend, or axially fixed, connected. Thus, a tensile force can be transmitted to the pressure plate by the clutch cover is further spaced from the counter-plate. For this purpose, an actuating spring is provided, which is preferably designed as a plate spring. The actuating spring is clamped in a configuration between the counter-plate and the clutch cover such that the first pressure plate by means of the clutch cover against the corresponding friction disc, and thus the entire friction package together, is pressed. As a result of an active actuation of the actuating spring, the actuating spring force is released and thus released the pressure plate of the corresponding friction disc. As a result, the entire friction package is released and in this state is no, or only a small (preferably negligible), torque transferable by means of the Reibpakets. In an alternative configuration, the actuating spring is biased reversed, so that the friction pack is pressed only when actively pressed and is otherwise solved. The first configuration is called normal-indented and the second configuration is called normal-disengaged.

The counterplate preferably has a plurality of first axial projections spaced apart from one another in the circumferential direction, via which the counterplate can preferably be fastened in such a way that it can transmit torque with a mass disk. The counter-plate is, preferably indirectly via the ground plate, torque-fixed connected to an output shaft of a drive unit and the friction disc with an output shaft, for example, a transmission shaft, torque-tight manner. The mass disk is particularly preferably designed as a flex plate or as a single flywheel, as described above. In another embodiment, the ground disk is a clutch side (secondary) mass flywheel of a dual mass flywheel.

The pressure plate here preferably has a plurality of radially extending and circumferentially spaced second axial projections (second flanges), which are arranged in the circumferential direction between the first axial projections (first flanges) of the counter-plate, so that the pressure plate and the counter-plate are interlocked. The torque transmission, for example, the input torque from the counter-plate to the pressure plate is supported by a concern of the respective first and second axial projections in the circumferential direction or takes place exclusively about it. Alternatively, separate components, such as at least one leaf spring and / or at least one driver, are provided for torque transmission and set up. Then, preferably, the immediately adjacent pressure-plate-side (second) and counter-plate-side (first) axial protrusions are circumferentially spaced from each other.

The pressure plate and the clutch cover are axially fixed to each other by means of at least one tension element and together displaceable. Preferably, in the configuration described above, the (second) axial projections of the pressure plate are connected to the axially displaceable clutch cover. On the clutch cover, the plate spring acts on a support point, for example a lid cam or a wire ring, with a force edge, and is preferably tilted. The support point is formed circumferentially, preferably interrupted in the circumferential direction.

The support point for the force edge of the diaphragm spring is adapted to transmit both an actuating spring force for pressing the at least one pressure plate, for example by means of tension bolts, as well as pressure forces for lifting the friction plates of the friction plates, for example by means of at least one Abhubfeder. On the back of the backing plate, for example, a cam ring is formed or arranged a wire ring on which the plate spring (with its support edge) is supported for transmitting the contact force.

This preferred normally-engaged clutch configuration is preferably disengageable by means of pressure on centrally arranged disc spring tips (actuating edge), and thus the transmission of a torque can be interrupted. In such a disengagement operation, a tensile force is applied to the support point on the clutch cover via the plate spring, so that the clutch cover in Direction (back of the) counter plate is pulled, so a distance between the back plate and the clutch cover is reduced. As a result, the friction surface of the pressure plate away from the friction surface of the backing plate and the contact pressure on the friction disc is thus solved. Preferably, the clutch cover, the pressure plate, optionally the intermediate plates and / or the counter plate are formed from sheet metal, and preferably (alone) by means of stamping and / or embossing or deep drawing.

In the configuration of the friction clutch proposed here, the at least one tension element is integrally formed by the pressure plate and / or the clutch cover. For example, the pressure plate forms a (not closed) first pot bottom and a (not closed) first pot wall, wherein the first pot bottom comprises the friction surface of the pressure plate. The first pot wall of the pressure plate extends towards the clutch cover. For example, the clutch cover forms a (not closed) second pot bottom and a (preferably not closed) second pot wall, wherein the second pot bottom, the support point for an actuating spring, preferably a plate spring comprises. The second pot wall of the clutch cover extends towards the pressure plate. A first and preferably a second pot wall is formed interrupted over the circumference. The pot wall is preferred, for example by means of deep drawing or edges, integrally formed from a sheet metal blank. The clutch cover and the pressure plate are preferably directly connected to each other by means of at least one pot wall. This eliminates long tie rods, as are customary in the prior art. A respective pot wall extends axially, preferably parallel to the axis of rotation. The pressure plate and the clutch cover are made so far as rotationally symmetrical components, that a rotation of the composite friction clutch around the rotational axis is unbalance executable. Imbalance is a friction clutch, provided that no imbalance occurs or a small imbalance with conventional imbalance masses is compensated.

• i. einen ersten Randabschnitt der Anpressplatte, welcher sich axial bis zum Kupplungsdeckel erstreckt;
• ii. einen zweiten Randabschnitt des Kupplungsdeckels, welcher sich axial bis zur Anpressplatte erstreckt; und
• iii. einen dritten Randabschnitt der Anpressplatte und einen vierten Randabschnitt des Kupplungsdeckels, wobei sich der dritte Randabschnitt und der vierte Randabschnitt axial überlappen.

According to an advantageous embodiment of the friction clutch, the tension element is formed by means of at least one of the following elements:

• i. a first edge portion of the pressure plate, which extends axially to the clutch cover;
• II. a second edge portion of the clutch cover, which extends axially to the pressure plate; and
• iii. a third edge portion of the pressure plate and a fourth edge portion of the clutch cover, wherein the third edge portion and the fourth edge portion axially overlap.

It should be pointed out in advance that the ordinal numbers of the edge sections (and pot walls) only serve to distinguish the respective embodiment in the present representation and in no way condition that edge sections of other ordinal numbers must be present. A clutch cover preferably has no second edge section if the pressure plate has a first edge section, and vice versa. However, the third edge portion causes a corresponding fourth edge portion.

In these configurations, preferably, an edge portion is an integrally formed sheet edge radially outward of a sheet metal blank, from which a pressure plate or a clutch cover is made. An edge portion is particularly preferably designed as a pot wall according to the above description. An edge portion preferably has a plurality of individual flanges, which are spaced apart in the circumferential direction. Particularly preferably, the flanges are formed with respect to their circumferential extension in such a way corresponding to mating flanges of the counter-plate that a torque transmission is made possible by a concern of the flanges on adjacent mating flanges in the circumferential direction. The mating flanges of the counterplate are adapted for connection to an output shaft, preferably by means of a flywheel.

A respective edge portion can be axially fixedly connected to the respective other partner (pressure plate or clutch cover) in the axial direction and / or in the radial direction. Preferably, an edge portion of the first configuration (i.) And the second configuration (ii.) Extends directly contacting up to a disc portion of the other partner (pressure plate or clutch cover). A disc portion is a radially extending portion of the partner between the center of the friction clutch and the respective edge portion. The center is in many cases formed by an opening for an actuating device, but at least for an output shaft, for example a transmission input shaft. In the third configuration (iii.), The edge portions of the partners overlap in a co-formed axial portion which bridges the axial distance between the friction surface of the pressure plate and the (disc) portion of the clutch cover lying in the same radius region (ring portion). Either the third edge portion is radially outward, the fourth edge portion is radially outside or these edge portions alternate (irregular or regular) from. Preferably, these edge portions are radially at least partially against each other and are based on each other or the softer, preferably radially inner, Edge portion is supported on the more stable, preferably radially outer, edge portion.

• a. eine nietartige Zapfenverbindung;
• b. einen Bajonettverschluss;
• c. eine Verstiftung, bevorzugt mit mehreren axial-diskreten Verbindungsstellen;
• d. eine Gewindepaarung, welche ein Innengewinde und ein Außengewinde an jeweils dem dritten Randabschnitt und dem vierten Randabschnitt nach der Ausführungsform iii. gemäß der obigen Beschreibung aufweist; und
• e. eine axiale und/oder radiale Klickverbindung, bevorzugt mit mehreren axial-diskreten Verbindungsstellen.

According to an advantageous embodiment of the friction clutch, the tension element has at least one of the following connecting elements for connecting the pressure plate to the clutch cover:

• a. a rivet-type pin connection;
• b. a bayonet lock;
• c. a pinning, preferably with several axially discrete joints;
• d. a thread pairing having an internal thread and an external thread at each of the third edge portion and the fourth edge portion according to the embodiment iii. according to the above description; and
• e. an axial and / or radial click connection, preferably with a plurality of axially discrete connection points.

For an embodiment with particularly few separate parts in particular integrally formed connecting elements for positive engagement and / or adhesion are preferred.

For example, a pin is formed, which extends axially or radially from one of the partners of the tension member in the region of the contacting compound. Preferably, the pin is rivet-like. That is, the open end of the pin is deformable such that it has a widening transverse to the pin axis after a suitable deformation, so that the respective partner of the tension member with its corresponding opening can not be separated. In this case, the connection is preferably set up in such a way that the partners of the tension element are pulled or pressed against each other without play. Preferably, the rivet-like pin is axially aligned, so that by means of the deformation of the pin in the axial direction a play-free connection is adjustable.

Alternatively or additionally, a pinning is provided, wherein two corresponding holes can be brought into coincidence with each other and then a pin can be guided through both holes, so that a positive connection is formed.

Preferably, the pin is held in a hole. Particularly preferably, the pin is biased by a spring in the direction of the hole axis, so that one partner is automatically connectable by pushing on the other partner by the pen is pressed by the spring into the corresponding hole of the other partner. In one embodiment, at least one partner has in the axial direction a plurality of holes, which are each arranged corresponding to a hole of the other partner. As a result, the partners are axially discrete, so with different axial distances from each other, connected to each other. As a result, for example, the biasing force of a plate spring adjustable and / or same partner for different thickness Reibpakete used.

Alternatively or additionally, a bayonet closure is provided, which can be closed by axial insertion of a partner into the other partner, preferably up to a corresponding stop, and subsequent relative rotation of the partners to one another. This allows a particularly simple installation without major tooling. In this case, further securing elements are preferably provided against an automatic release, for example a tapping or pinning according to the above description and / or a click connection.

Alternatively or additionally, a thread pairing is provided, which is arranged as an external thread circumferentially on one edge portion and corresponding internal thread circumferentially on the other edge portion of the third and fourth edge portions according to the above description. Thus, the clutch cover is screwed onto the pressure plate. In this case, further securing elements are preferably provided against an automatic release, for example a tapping or pinning according to the above description or a self-locking thread.

Alternatively or additionally, an axial and / or radial click connection, preferably with a plurality of axially discrete connection points, is provided. This has, for example, a snap hook and one or more corresponding inlets, wherein preferably by a plurality of inlets per snap hook, the axially discrete connection points are formed.

According to an advantageous embodiment of the friction clutch, the actuating spring is a disc spring, wherein the disc spring is radially fixed axially outside and radially inwardly axially actuated, wherein the spring force of the plate spring radially therebetween at a support point in the clutch cover is introduced, preferably further preferably at least one Abhubfeder is provided, by means of which the plate spring is pressed against the support point, wherein particularly preferably the at least one Abhubfeder is connected by means of a connecting element according to one embodiment according to the above description with the clutch cover and / or the pressure plate.

Particularly preferably, the disc spring is supported radially on the outside, facing away from the friction, back of the back plate, preferably by means of a wire ring or one or more cams. Preferably, a plurality of individual, more preferably tab-like, Abhubfedern distributed over the circumference.

The at least one lifting spring ensures that the clutch cover is entrained in the axial direction when the diaphragm spring is moved away from the support point. However, the at least one Abhubfeder also ensures that a sudden movement or an excessively large force when moving away the diaphragm spring from the support point on the clutch cover only delayed and / or limited to the transferable by means of at least one Abhubfeder force on the clutch cover force.

Preferably, this at least one Abhubfeder is connected by means of a connecting element with the clutch cover and / or the pressure plate, which connects the pressure plate with the clutch cover. Particularly preferably, the Abhubfeder by means of a common assembly step for connecting the partners with each other with the clutch cover and / or the pressure plate connectable. In a particularly favorable embodiment, one of the stripping springs is connected to a respective rivet-type pin of the pressure plate or the clutch cover. Such a pin of the pressure plate extends through a corresponding (first) opening in the clutch cover to a corresponding (second) opening in the Abhubfeder and is or is widened behind the openings by a, preferably cold, forming process. As a result, the clutch cover and the Abhubfeder are positively and non-positively connected at least in the axial direction with the pressure plate.

According to a further aspect of the invention, a drive train is proposed, which comprises a drive unit with an output shaft and a friction clutch according to the above description, wherein the output shaft for torque transmission by means of the friction clutch with at least one consumer is detachably connectable.

The drive train is set up to transfer a torque that is provided by a drive unit, for example an energy conversion machine, preferably an internal combustion engine or an electric motor, and output via its output shaft, for at least one consumer, ie switchable and switchable. An exemplary consumer is at least one drive wheel of a motor vehicle and / or an electric generator for the provision of electrical energy. Conversely, a recording of an inertial energy introduced, for example, by a drive wheel can also be implemented. The at least one drive wheel then forms the drive unit, wherein its inertial energy by means of the friction clutch to an electric generator for recuperation, ie for the electrical storage of the braking energy, with a suitably equipped drive train is transferable. Furthermore, in a preferred embodiment, a plurality of drive units are provided, which are connected by means of the friction clutch in series or in parallel or decoupled from each other operable, or whose torque is releasably available for use available. Examples are hybrid drives of electric motor and internal combustion engine, but also multi-cylinder engines in which individual cylinders (groups) are switchable.

In order to selectively transmit the torque and / or by means of a gearbox with different ratios or to separate a transmission, the use of the friction clutch described above is particularly advantageous because the friction clutch can be manufactured inexpensively with few components and few and safe assembly steps. In addition, bolt elements can be saved and the manufacture laid on for mass production and mass production cost-effective cold sheet metal forming.

According to a further aspect of the invention, a motor vehicle is proposed, which has at least one drive wheel which can be driven by means of a drive train according to the above description.

Most motor vehicles today have a front-wheel drive and therefore preferably arrange the drive unit, for example an internal combustion engine or an electric motor, in front of the driver's cab and transversely to the main drive direction. The space is particularly small in such an arrangement and it is therefore particularly advantageous to use a friction clutch small size. Similarly, the use of a friction clutch in motorized two-wheeled, for which a significantly increased performance is required with the same space.

This problem is exacerbated in passenger cars of the small car class according to European classification. The units used in a passenger car of the small car class are not significantly reduced compared to passenger cars larger car classes. Nevertheless, the available space for small cars is much smaller. The drive train described above has a friction clutch of particularly small size. At the same time, the friction clutch can be manufactured inexpensively with few components as well as few and safe assembly steps and is therefore particularly suitable for the low-cost range.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market. In the US market, cars of the class small cars and microcars are classified according to European classification of the class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car. Examples of the micro car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.

The above-described invention will be explained in detail in the background of the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is not limited by the purely schematic drawings in any way, it being noted that the drawings are not dimensionally accurate and are not suitable for the definition of size ratios. It is shown in

1 a conventional friction clutch in a schematic functional view;

2 a first embodiment of a friction clutch in a schematic functional view;

3 a second embodiment of a friction clutch in a schematic functional view;

4 a third embodiment of a friction clutch in a schematic functional view;

5 a fourth embodiment of a friction clutch in a schematic functional view;

6 a fifth embodiment of a friction clutch in a schematic functional view;

7 a sixth embodiment of a friction clutch in a schematic functional view;

8th a seventh embodiment of a friction clutch in a schematic functional view; and

9 : a drive train in a motor vehicle with friction clutch.

In 1 is a conventional friction clutch 1 with a rotation axis 2 shown, which for the sake of clarity, as equal as possible with the friction clutch 1 in 2 to 8th is shown and for which the same reference numerals are used. It should be pointed out that the representation is by no means a sectional view through a common sectional plane, but merely ajar from a sectional view, the basic functional assignment of the components to one another in an understandably simplified representation.

In the 1 shown friction clutch 1 has a friction package 9 on which is a counter-plate 6 , a pressure plate 7 and a friction disc interposed therebetween 8th having. The friction disc 8th is with an output shaft hub 37 rotatably fixed, so that torque from the friction disc 8th on an output shaft, for example, a transmission input shaft, (not shown) is transferable. Here is the counter plate 6 between the pressure plate 7 and a clutch cover 12 arranged. The counter plate 6 is axially fixed and, in the present example by means of a ground washer 38 , Here, a one-mass flywheel, torque transmitting with an output shaft, for example, with a crankshaft of an internal combustion engine, (not shown) rotatably fixable. Here, the rotary connection by means of a motor connection 36 the mass disk 38 accomplished.

The illustrated friction clutch 1 is a normally-engaged configuration in which an actuating spring 11 , which is designed here as a plate spring, in a friction package 9 is shown automatically pressing position, ie without the actuating spring 11 is actively activated. The actuating spring 11 has a support edge 39 on, by means of which the actuating spring 11 axially against the counter plate 6 , here by means of a wire ring 40 , (tiltable) is supported. The counter plate 6 thus forms the (axially fixed) counter bearing for the actuating spring 11 , The actuating spring 11 still has a power border 42 on, over which the actuating spring force on a support point 27 here over a lid cam, and in the opposite direction over a Abhublager 43 a lift spring 28 , in the clutch cover 12 is initiated. In the state shown here, the clutch cover 12 pressed in the illustration to the right, so from the back plate 6 spaced. As a result, the pressure plate 7 towards the counter plate 6 pulled, so the friction package 9 is compressed. The clutch cover 12 and the pressure plate 7 are by means of a tension element 10 connected axially fixed to each other, wherein the tension element 10 here from a conventional tie rod 32 is formed.

To the friction package 9 to solve, has the actuating spring 11 an operating edge 41 on, via which the action of the actuating spring force on the clutch cover 12 can be canceled. In the configuration shown here is the actuating spring 11 by means of an actuating unit, not shown, against the biasing force of the actuating spring, in the representation from right to left, depressible, so that the force edge 42 the actuating spring 11 from the support point 27 is lifted or the corresponding force is released. By means of the lifting spring 28 , which with the clutch cover 12 , here by means of the conventional tie rod 32 , Axially fixed, is the clutch cover 12 towards the counter plate 6 drawn. As a result, the force on the pressure plate 7 lifted, or an opposite force on the pressure plate 7 Applied, so the friction package 9 is solved. In this configuration are the counter plate 6 and the pressure plate 7 formed with radially extending flanges meshed with each other, so that a torque between the back plate 6 and the pressure plate 7 can be transferred via this formed toothing. In a preferred configuration, thus, the ground disk 38 , the counter plate 6 , the pressure plate 7 , the clutch cover 12 and the actuating spring 11 (preferably steamed) permanently co-rotated, with (alone) the friction disc 8th with the output shaft hub 37 only in a compressed state of the friction package 9 co-rotates.

In 2 to 8th are similar configurations of a friction clutch 1 as in 1 shown so that only the main differences are indicated here. In particular, the functional assignment of the components is Reibpaket 9 and clutch cover 12 largely the same.

In 2 is a friction clutch 1 shown at the tension element 10 from a first edge section 13 is formed, which preferably integrally with the pressure plate 7 is formed. In the present embodiment, the first edge portion extends 13 to the disc portion of the clutch cover 12 , and lies there on the clutch cover 12 at. In this particularly preferred embodiment, the first edge portion 13 In addition, a rivet-type pin on which a first pin connection 17 with the clutch cover 12 forms. In the present case this forms integral with the first edge portion 13 formed pin at the same time a Abhubfederniet 44 for axially fixing the Abhubfeder 28 on the clutch cover 12 ,

In 3 is a friction clutch 1 as in 2 shown, in which case the connecting element between the first edge portion 13 and the clutch cover 12 by means of a first bayonet catch 19 is formed. The stripping spring rivet 44 is here formed separately and preferably in one piece with the clutch cover 12 formed.

In 4 is a friction clutch 1 shown at the tension element 10 from a second edge portion 14 is formed, which preferably integrally with the clutch cover 12 is trained. The connecting element between the second edge portion 14 and the pressure plate 7 is here by means of a second bayonet closure 20 educated. The stripping spring rivet 44 is here formed separately and preferably in one piece with the clutch cover 12 formed.

In 5 is a friction clutch 1 as in 4 illustrated, in which case the connecting element between the second edge portion 14 and the pressure plate 7 by means of a second pin connection 18 is formed, in which case preferably the corresponding pin integral with the pressure plate 7 is formed. The stripping spring rivet 44 is here formed separately and preferably in one piece with the clutch cover 12 formed.

In 6 is a friction clutch 1 shown in which the tension element 10 in two parts from a third edge section 15 and a corresponding fourth edge portion 16 is formed, which has a thread pairing 24 interconnected, in this case with an internal thread 25 on the fourth edge section 16 the clutch cover 12 and a corresponding external thread 26 at the third edge section 15 the pressure plate 7 , Here, in the same embodiment, the length of the axial extent of the third edge portion 15 and the fourth edge portion 16 preferably given an axial adjustability, by which, for example, the biasing force of the actuating spring 11 is adjustable.

In 7 and 8th is a friction clutch 1 shown in which the tension element 10 also like in 6 in two parts from a third edge section 15 the pressure plate 7 and a corresponding fourth edge portion 16 the clutch cover 12 is formed. But here are the third edge section 15 and the fourth edge portion 16 by means of a pinning 21 and corresponding first axially discrete junction 22 or second axially discrete junction 23 connected to each other. In the illustrated embodiment, the pinning is 21 formed with a prestressed locking element, so that, for example, the clutch cover 12 axially on the pressure plate 7 can be pushed and the locking element is pushed back. Upon reaching a corresponding axial-discrete junction 22 or 23 engages the locking element in this and thus forms the pinning 21 , Here, too, given an axial adjustability, by which, for example, a distance between the pressure plate 7 and the clutch cover 12 adapted to the friction lining thickness of the friction disc 8th and / or plate thickness of the counter-plate 6 is adjustable in axial extent.

In 9 is a powertrain 29 comprising a drive unit 30 , shown here as an internal combustion engine, an output shaft 3 , a friction clutch 1 and a torque transmitting connected left drive wheel 4 and right drive wheel 5 , shown schematically. The powertrain 29 is here in a motor vehicle 31 arranged, wherein the drive unit 30 with its motor axis 35 transverse to the longitudinal axis 34 in front of the driver's cab 33 is arranged.

With the friction clutch proposed here, a simple, cost-effective construction is possible in which at the same time a few separate individual parts can be used.

LIST OF REFERENCE NUMBERS

1

 friction clutch

2

 the rotation axis

3

 output shaft

4

 left drive wheel

5

 right drive wheel

6

 counterplate

7

 pressure plate

8th

 friction

9

 Reibpaket

10

 tension element

11

 actuating spring

12

 clutch cover

13

 first edge section

14

 second edge section

15

 third edge section

16

 fourth edge section

17

 first pin connection

18

 second pin connection

19

 first bayonet lock

20

 second bayonet catch

21

 pinning

22

 first axially discrete junction

23

 second axially discrete junction

24

 thread pairing

25

 inner thread

26

 external thread

27

 support point

28

 Abhubfeder

29

 powertrain

30

 drive unit

31

 motor vehicle

32

 conventional tie rod

33

 cab

34

 longitudinal axis

35

 motor axis

36

 motor connection

37

 Ausgangswellennabe

38

 mass disk

39

 supporting edge

40

 wire ring

41

 operating margin

42

 force boundary

43

 Abhublager

44

 Abhubfederniet

Claims (4)

Friction clutch ( 1 ) with a rotation axis ( 2 ) for releasably connecting an output shaft ( 3 ) with a consumer ( 4 . 5 ), comprising at least the following components: - a friction package ( 9 ) with an axially fixed counter-plate ( 6 ), an axially displaceable pressure plate ( 7 ) and at least one axially interposed friction disc ( 8th ), which between the counter plate ( 6 ) and the corresponding pressure plate ( 7 ) in the friction package ( 9 ) is compressible, so that by means of the Reibpakets ( 9 ) a torque is releasably transferable; An actuating spring ( 11 ), by means of which the friction package ( 9 ) is compressible; and - a mitrotierbarer clutch cover ( 12 ), wherein the counter-plate ( 6 ) axially between the clutch cover ( 12 ) and the pressure plate ( 7 ) is arranged and wherein the clutch cover ( 12 ) is axially displaceable and by means of at least one tension element ( 10 ) with the pressure plate ( 7 ) is axially fixed, characterized in that the at least one tension element ( 10 ) from the pressure plate ( 7 ) and / or the clutch cover ( 12 ) is integrally formed. Friction clutch ( 1 ) according to claim 1, wherein the tension element ( 10 ) is formed by at least one of the following elements: i. a first edge portion ( 13 ) of the pressure plate ( 7 ), which extends axially to the clutch cover ( 12 ) extends; II. a second edge portion ( 14 ) of the clutch cover ( 12 ), which extends axially to the pressure plate ( 7 ) extends; and iii. a third edge section ( 15 ) of the pressure plate ( 7 ) and a fourth edge portion ( 16 ) of the clutch cover ( 12 ), wherein the third edge section ( 15 ) and the fourth edge section ( 16 ) overlap axially. Friction clutch ( 1 ) according to claim 1 or 2, wherein the tension element ( 10 ) by means of at least one of the following connecting elements for connecting the pressure plate ( 7 ) with the clutch cover ( 12 ): a. a rivet-type pin connection ( 17 . 18 ); b. a bayonet catch ( 19 . 20 ); c. a pinning ( 21 ), preferably with a plurality of axially discrete connection points ( 22 . 23 ); and d. a thread pairing ( 24 ), having an internal thread ( 25 ) and an external thread ( 26 ) at each of the third edge portion ( 15 ) and the fourth edge portion ( 16 ) according to the embodiment iii. according to claim 2. Friction clutch ( 1 ) according to one of the preceding claims, wherein the actuating spring ( 11 ) one Is plate spring, which is radially fixed axially fixed and radially inwardly axially actuated, wherein the spring force of the plate spring radially therebetween at a support point ( 27 ) in the clutch cover ( 12 ), wherein preferably at least one stripping spring ( 28 ) is provided, by means of which the plate spring against the support point ( 27 ) is pressed, wherein particularly preferably the at least one Abhubfeder ( 28 ) by means of a connecting element according to claim 3 with the clutch cover ( 12 ) and / or the pressure plate ( 7 ) connected is.

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