DE102014219521A1 - Space-saving radial double clutch - Google Patents

Abstract

A radial dual clutch comprises an input side and a first and a second output side, which are arranged rotatably about a common axis of rotation. Further, an outer and an inner outer plate carrier are provided, which are respectively connected to the input side, a first friction pack, which lies radially between the outer outer disk carrier and the first output side, and a second friction pack, which lies radially between the inner outer disk carrier and the second output side , The inner outer plate carrier comprises axial engagement elements, which are guided by corresponding recesses in the input side. To axially secure the inner outer disk carrier at the input side against falling out, a locking ring is further provided with a shock for positive engagement in the engagement elements of the radial outer side. In addition, the dual clutch includes a pressure pot for axially compressing the first friction pack to allow transmission of torque between the input side and the first output side, and a Belleville spring to push the pressure pot away from the friction pack, thus interrupting torque transfer between the input side and the second exit side. Axially between the input side and the plate spring is a support ring having an axial portion which bears radially on the outside of the locking ring.

Description

The invention relates to a radial double clutch. In particular, the invention relates to the attachment of an outer disk carrier on an input side of the radial double clutch.

A radial double clutch comprises an outer and an inner clutch, which are arranged radially offset from each other. One input side of the dual clutch is connected to input sides of both clutches and output sides of the clutches are provided for engagement with different shafts. The shafts may in particular comprise input shafts of a dual-clutch transmission.

Double clutches often require a particularly compact design due to their larger number of components compared to single clutches. It must be paid attention to a simple mountability of the double clutch. For example, the input side must be connected to disk carriers of both clutches, the clutches should be mountable and ideally in case of service friction elements of the clutches can be renewed as easily as possible.

On this basis, the present invention seeks to provide an improved space-saving dual clutch of the radial type. The object is solved by the subject matters of the independent claims. Subclaims indicate preferred embodiments.

For a connection device between a friction clutch and a torsional vibration damper, the torsional vibration damper has an output element and the friction clutch has an input element. The input element is connected by means of a plug-in torque-transmitting connected to the output element, wherein a clamping element is provided for backlash-free clamping of the connector.

The connecting device is intended to produce a backlash-free clamping between the friction clutch and a torsional vibration damper, for example a dual-mass flywheel. For this purpose, an output element of a torsional vibration damper is provided, which may be formed integrally with the torsional vibration damper or may constitute a separate component of the torsional vibration damper, which is designed as a connecting element for the friction clutch. Furthermore, an input element of a friction clutch is provided, which may also be an integral element of a component of the friction clutch and a separate component which is adapted for connection to the torsional vibration damper. In this case, the input element can be connected to the output element in such a way that it transmits torque, wherein this connection can be made by means of a plug connection. Such a connector is, for example, a toothing in which either the input element or the output element is inserted into the output element or input element. Thus, the input element or the output element has an outer toothing and the output element or the input element has an internal toothing. Characteristic of such a connector is that a certain amount of play is necessary to be able to fit the elements together well. In particular, in order to prevent a double fit, it is necessary for (of a plurality of) two opposing flank pairings of the plug connection (respectively) only one of the two flank pairings of the plug connection to come into contact with each other, and the flank pairing opposite the direction of rotation in each case be spaced apart, ie a clearance is present. Thus, it comes at least in a reversal of direction or at a negative acceleration to bear that this game is provided here; because this can lead to a noise. For this purpose, a clamping element is further provided, which also causes the connector is tensioned free of play. It is preferably meant that in a reversal of direction or a negative acceleration, the connector is held in position by means of the clamping element, or at least not the previously spaced (n) edge pairing (s) come (abrupt) to concern.

According to a further advantageous embodiment of the connecting device, the clamping element generates a frictional connection, and preferably comprises at least one open polygon ring. By means of the clamping element proposed here, a frictional connection is generated, which prevents a backlash-free clamping of the connector, at least in the return direction or in the negative direction of acceleration, frictionally. It is sufficient if the frictional engagement is sufficiently designed for the (maximum) applied negative accelerations. For many applications in motor vehicles, a preload of 5 to 10 Nm (Newton meters) is sufficient. Particularly preferably, this clamping element is formed by at least one open polygon ring, which is easy to assemble and can produce an effective frictional engagement with slip in the torque direction. Depending on the applied forces, it may be useful to use a plurality of open polygon rings. According to a further advantageous embodiment of the connecting device, the output element forms the receptacle for a plug-in element on the Input element of the connector and the input element arranged radially outside the receptacle abutment for the clamping element.

In this advantageous embodiment, the receptacle for a plug-in element, that is, in the case of splines, the internal teeth, formed at the output element and the plug-in element, ie the external teeth of a spline formed on the input element. Furthermore, the input element comprises a radially outwardly of the receptacle arranged after assembly of the connector abutment which surrounds the receptacle radially outwardly at least partially in the manner of a projection and thus forms a gap between the receptacle and the abutment. In this gap, the clamping element, preferably an open polygon ring, insertable. Thus, the force circle of the strain within the input member is formed as an integral component and therefore very rigidly shaped by simple means.

At a connecting device for a friction clutch and a torsional vibration damper, the torsional vibration damper on an output element and the friction clutch on an input element. The input element can be connected by means of a plug connection to transmit torque to the output element. For backlash-free clamping of the connector, a clamping element is provided.

A friction clutch for releasably connecting an output shaft to a drive train comprises an axis of rotation. In this case, the friction clutch has at least one friction pack, via which torque can be transmitted in the pressed-on state, at least one torsional vibration damper and at least one connecting device according to the above description and the input element is at least indirectly connected to the Reibpaket and the output element at least indirectly with the torsional vibration damper.

The friction clutch is adapted to releasably transfer torque from an output shaft to a drive train and vice versa. This is usually achieved via the at least one friction pack, which can be compressed axially by means of an axially displaceable, usually rotationally fixed to the output shaft, pressure plate. The pressure plate is pressed against at least one friction disc of the Reibpakets, as a result of which a frictional force arises, which multiplied by the mean radius of the friction surface results in a transmissible torque. When pressing or switching and releasing the Reibpakets arise accelerations and negative accelerations; By changing the rotational speed of the connected drive unit or rotational irregularities of the drive unit, positive and negative acceleration components may be due to the connection device of the friction clutch between the torsional vibration damper and the friction pack.

To connect the friction clutch with the torsional vibration damper, the connection device described above is provided, which allows a tension-free backlash of the connector between the Reibpaket and the torsional vibration damper. Here, the input element is at least indirectly connected to the friction pack, that is, it is formed integrally with a component of the friction pack or is added as a separate component with a component of the friction pack, for example by welding. Likewise, the output element is at least indirectly connected to the torsional vibration damper, that is, the output element is formed integrally with a component of the torsional vibration damper or added as a separate component with a component of the torsional vibration damper, for example by welding. The connecting device proposed here is at least not larger than previous connecting devices and is also set free of play in the torque transmission and thus prevents noise development. In particular, in the embodiment of the abutment disposed radially outside the receptacle on the input element, no axial extension is necessary by the coupling device of the friction coupling proposed here.

According to a further advantageous embodiment of the friction clutch, the at least one friction pack is arranged in a wet space. The wet space is preferably at least partially flooded with a liquid, in particular oil.

Especially in the case of a friction clutch with wet space, the provision of a closed clutch space limits the integration of further components, in particular of a torsional vibration damper, into the friction clutch. Additional components and components which may not be arranged in the wet room must thus be arranged outside the friction clutch wet room. With the connecting device proposed here, it is possible to achieve in a small space a solid, in particular backlash-free, connection between a torsional vibration damper and at least one Reibpaket the friction clutch, without that due to the wet space a significant increase in the friction clutch must be made. At the same time easy mounting, for example by means of a spline, obtained.

According to a further advantageous embodiment of the friction clutch, the friction clutch further comprises at least one centrifugal pendulum, which is at least indirectly connected to the input member.

In today's modern drive units, especially internal combustion engines, very slow speeds are set, which can lead to vibrations throughout the drive train, because a resonant frequency of a component is hit. In particular, for such frequency ranges, it is necessary to provide a centrifugal pendulum, which can lead to a further increase in the friction clutch. Especially with such a friction clutch, it is necessary to achieve an effective connection between the friction clutch and the torsional vibration damper. Because a centrifugal pendulum can be well integrated into the structure of a friction clutch and is designed for the frequencies of the friction clutch, but should work closely with a torsional vibration damper, it is advantageous to achieve a backlash-free connection between the torsional vibration damper and the centrifugal pendulum. With the connector with clamping element proposed here, this is particularly easy to implement without requiring additional axial space.

According to a further advantageous embodiment of the friction clutch, the centrifugal pendulum is arranged in the wet space. The wet space is preferably at least partially flooded with a liquid, in particular oil.

To arrange the centrifugal pendulum in a wet space of the friction clutch, has the advantage that the centrifugal pendulum on the one hand has an improved eradication with less mass and on the other hand requires axially smaller space. By arranging the pendulum masses in a wet room, the vibration inertia is increased counter to the direction of rotation of the coolant, wherein the rotational mass against a dry-running centrifugal pendulum can be reduced and thus the inertia of the centrifugal pendulum is reduced.

According to a further advantageous embodiment of the friction clutch is provided between the at least one friction pack and at least one of the centrifugal pendulum an intermediate element which connects the at least one centrifugal pendulum with the at least one Reibpaket torque transmitting as a separate component.

By providing an intermediate element between the at least one friction packet and the centrifugal pendulum, it is possible to gain axial space. In the prior art, the centrifugal pendulum is often additionally hooked into a pot forming a Lammellenkorb axially laterally to the slats. In this case, it is necessary due to the most required compared to the slats larger outer diameter of the centrifugal pendulum pendulum to provide a diameter extension of the pot to accommodate the centrifugal pendulum. As a result, an area is provided with a kink radially outward and another kink in the axial direction, which in itself already leads due to the necessary minimum radii of the kinks for producing such a pot to a considerable additional and mostly unused axial space. The intermediate element is now a separate component which can be connected to a lamellae-forming pot, for example by a plug connection. Thus, with a radially larger outer diameter of the centrifugal pendulum, the intermediate element must have only a bend radially inward. This already falls over the arrangement described above, a kink away. Furthermore, it is also possible to bring the remaining kink with the pot for the fins of the Reibpakets in axial overlap. Thus, space is saved.

According to a further advantageous embodiment of the friction clutch, an input disk carrier is provided in the friction package, which has a first region for receiving the input disks and a second region for receiving the input disks of a second partial clutch.

Due to the one-piece design of the input disk carrier, a good torque transmission is achieved and a single component is used, which is always acted upon by an almost constant torque due to the usual when switching to another gear change circuit of the partial clutches.

According to a further advantageous embodiment of the friction clutch, the friction clutch is a double clutch with two independently compressible friction packs.

Especially with double clutches, the space requirement is particularly large, so that a connecting element of small axial size is required. In particular, a dual clutch comprising all the embodiments described above can be made particularly small and yet meets the requirements of modern drive units, that is, it can compensate for low speeds and dampen rotational irregularities, at the same time a high transmission efficiency and low noise are achieved. Especially with the current trend, small engines with a low number of cylinders, for example, three cylinders to connect with a dual clutch with dual mass flywheel, it is necessary the just to reduce occurring rotational irregularities in order to meet the comfort requirements. At the same time a simple assembly of the components must be ensured and the noise can be prevented. This can be achieved by the play-free plug connection described above.

A motor vehicle comprises a drive unit with an output shaft, a drive train and the friction clutch described above. 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.

The installation space situation for passenger cars of the small car class according to European classification is exacerbated. 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 connecting device described above allows the use of a relatively large compared to a single clutch double clutch, which is also equipped with a centrifugal pendulum and with a separate torsional vibration damper easily and without play connectable.

Passenger cars are classified according to vehicle class according to, for example, size, price, weight, power, but this definition is subject to constant change according to the needs of the market. In the US market, vehicles 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, for example, the class City Car. Examples of the micro car class are a Volkswagen Fox or a Renault Twingo. Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.

The abovementioned, individually listed features can be combined with one another in any technologically meaningful manner and can be supplemented by explanatory facts from the description and details from the figures, wherein further embodiments of the invention are shown.

A radial double clutch according to the invention comprises an input side and a first and a second output side, which are arranged rotatably about a common axis of rotation. Further, an outer and an inner outer plate carrier are provided, which are respectively connected to the input side, a first friction pack, which lies radially between the outer outer disk carrier and the first output side, and a second friction pack, which lies radially between the inner outer disk carrier and the second output side , The inner outer plate carrier comprises axial engagement elements, which are guided by corresponding recesses in the input side. To axially secure the inner outer disk carrier at the input side against falling out, a locking ring is further provided with a shock for positive engagement in the engagement elements of the radial outer side. In addition, the dual clutch includes a pressure pot for axially compressing the first friction pack to allow transmission of torque between the input side and the first output side, and a Belleville spring to push the pressure pot away from the friction pack, thus interrupting torque transfer between the input side and the second exit side. Axially between the input side and the plate spring is a support ring having an axial portion which bears radially on the outside of the locking ring.

As a result, the support ring can simultaneously serve as an abutment for the plate spring and as a radial retaining element for the retaining ring. In particular, in cramped conditions of the double clutch so several functions can be combined in a confined space with each other by means of a simple component. The support ring may be simple and, for example, by means of a punching and pressing or embossing process tool falling from a sheet produced.

The support ring may have an axial embossment running around the axis of rotation in order to form a contact edge for the plate spring, wherein a bearing radius of the abutment edge does not exceed a predetermined extent. The predetermined dimension may be, for example, a bearing radius of about 0.5-5 mm, preferably about 1-3 mm. The smaller the bearing radius, the less the plate spring rolls when moving the pressure pot on the support ring and accordingly, a shift in the lever ratios is kept small. The force caused by the disc spring force can be kept constant so improved over the travel.

The support member may include a radial abutment member for radially centering the disc spring. Thus, the support element can take on a further task, so that a constructive margin can be increased elsewhere. For example, it is then not necessary to center the diaphragm spring radially on the input side, so that may account for about a radial abutment edge for the plate spring.

The inner outer plate carrier may have a predetermined number of axial engagement elements and the support ring may include the same number of radially outwardly facing tabs. In this case, axial portions for engagement radially on the retaining ring are provided on the tabs so that the tabs can pass through between each adjacent engagement elements. Radial and axial forces can be distributed so improved on a circumference around the axis of rotation. Due to the more uniform distribution of force, a service life or load capacity of the double clutch can be increased.

Preferably, an axial travel of the pressure pot is dimensioned so that the support ring is always pressed by the diaphragm spring against the input side. An axial securing of the support ring on the input side can thus be omitted.

The invention and the technical environment will be explained in more detail with reference to FIGS. The figures show particularly preferred embodiments, to which the invention is not limited. In particular, it should be noted that the figures and in particular the illustrated proportions are only schematic. Show it:

1 a double clutch with tensioning element and centrifugal pendulum,

2 a centrifugal pendulum with intermediate element,

3 a friction clutch with tensioning element and centrifugal pendulum,

4 a connecting device with clamping element,

5 a tension element,

6 a motor vehicle with friction clutch,

7 an enlarged view of a portion of the friction clutch of 3 .

8th the support ring of 7 in a first view and

9 the support ring of 7 and 8th in a second view.

1 shows a friction clutch 2 in which a first friction package 15 and a second friction package 16 are provided. The first rubbing package 15 includes a first pressure plate 21 and a first friction disc 23 and the second friction package 16 includes a second pressure plate 22 and a second friction disc 24 which can each be brought into frictional contact with each other, thus switchable torque in the friction packs 15 and 16 transferred to. In this embodiment, the friction packs 15 and 16 over, for example, a pressure chamber 28 operated, which on an actuator 30 acts such that a respective friction package 15 or 16 is pressed. A return spring 31 generates the necessary counterforce to create a friction package 15 or 16 to solve. That of the output shaft 13 Torque delivered is via the friction packs 15 and 16 on a first output shaft 32 or a second output shaft 33 transferable. Furthermore, a centrifugal pendulum 17 provided, which via a tab of an outer disk carrier 44 torque transmitting connected. Here is the input element 5 with the centrifugal pendulum 17 connected so that the torque through the centrifugal pendulum 17 vibration-decoupled for the predetermined repayment frequencies on the Reibpakete 15 and 16 is transmitted. The input element 5 is via a plug connection 6 with an output element 4 connected, which with a torsional vibration damper 3 connected is. The torsional vibration damper 3 in turn is with an output shaft 13 connected, so that torque from the output shaft 13 through the torsional vibration damper 3 damped on the friction clutch 2 is transmitted.

In 2 is a section of a first friction package 15 shown in which an outer disc carrier 44 with a lamellar toothing 40 is provided, in which the outer fins 38 are suspended, so that a torque from the outer disk carrier 44 on the outer fins 38 is transferable. The outer disc carrier 44 is in a mounting section 35 with an intermediate element 18 connectable, wherein the intermediate element 18 for an end stop 37 for the lamellae of the friction package 15 form. Furthermore, the intermediate element forms 18 a torque transmitting connection for the centrifugal pendulum 17 or via its torque transmission element 43 , which can also serve as a flywheel (depending on the respective net mass of the torque transmitting element). On the torque transmitting element 43 are still pendulum masses 36 provided, which is movable on the torque transmitting element 43 are suspended and thus could tear out in the event of damage. For this purpose, the intermediate element 18 In addition, a burst protection, which other components of the friction clutch 2 from damage by the pendulum masses 36 protects. The radius 46 of the outer disk carrier 40 is smaller than the outermost edge of the pendulum masses 36 , Between the outer plates 38 there are inner lamellae 39 , which with an inner disk carrier 45 are connected, which switchable via the actuator torque from the outer disk carrier 44 takes over. The components shown here are all about the axis of rotation 11 the friction clutch 2 rotatable.

In 3 is a friction clutch 2 which is a first friction package 15 and a second friction package 16 which is located in a wet room 12 are located. In essence, the structure is similar to that in the 1 , here between the centrifugal pendulum 17 a one-piece outer disc carrier 44 a separate intermediate element 18 is provided, which with the outer disk carrier 44 connected via a plug connection and a retaining ring. This saves considerable axial space.

In 4 is a detail of the arrangement as in 3 shown, in which case the clamping element 7 between the output element 4 and the abutment 10 easy to recognize. The recording 8th of the starting element 4 is designed here as an internal toothing and the plug-in element 9 of the input element 5 is designed as a corresponding external toothing, so that a torque transmission is made possible by the plurality of edge pairings in the direction of rotation. At a negative to the normal direction of rotation acceleration prevents the clamping element 7 , which is designed here as a frictionally generating polygon ring, a (sudden) rotation of the recording 8th to the plug element 9 and thus suppresses a noise. The centrifugal pendulum 17 is in the clutch bell 48 arranged the the wet room 12 the friction clutch 2 encloses, so in the wet room 12 arranged.

5 shows a polygon ring, which is a clamping element 7 can form. Due to its plurality of kinks, the polygon ring can produce a good frictional engagement with circumferential slippage, requiring only minimal space. The polygon ring forms in the installation with the abutment 10 and the recording 8th Friction points, so that a radial force is achieved by elastic deformation. The polygon ring is preferably formed from spring steel and / or allows a friction torque of 5 Nm to 10 Nm.

In 6 is a motor vehicle 19 with a drive unit 20 shown with its motor axis 27 transverse to the longitudinal axis 26 in front of the driver's cab 25 is arranged. The drive unit 20 is shown here as an internal combustion engine, which has an output shaft 13 by means of a friction clutch 2 with a purely schematically illustrated drive train 14 connected is.

With the connecting device proposed here, it is possible to achieve a noiseless connection between a friction clutch and a torsional vibration damper while at the same time being easy to install in a small installation space.

7 shows an enlarged view of a portion of the friction clutch 2 from 3 , The friction clutch 2 is as a radial double clutch 100 executed and has a rotation axis 105 on. The double clutch 100 includes an input page 110 , a first exit page 115 and a second exit side 120 around a rotation axis 105 are stored. With the input side 110 are an outer outer disc carrier 125 and an inner outer disc carrier 130 rotatably connected. An example of this is the outer outer plate carrier 125 integral with the input side 110 connected and the inner outer disc carrier 130 represents a separate component, the form-fitting with the input side 110 connected is. An outer inner plate carrier 135 is with the first exit page 115 and an inner inner disc carrier 140 with the second exit side 120 connected. Here are the inner disk carrier 135 . 140 each in one piece on the associated output pages 115 . 120 formed.

The first rubbing package 15 lies radially between the outer outer disk carrier 125 and the outer inner disc carrier 135 , In a similar way is the second friction package 16 between the inner outer disc carrier 130 and the inner inner disc carrier 140 , Will be one of the friction packages 15 . 16 axially compressed, so will a torque flow between the input side 110 and the associated output side 115 . 120 allows. For axial compression of the first friction pack 15 is the actuator 30 provided here a pressure pot 150 includes, which can be hydraulically actuated preferably axially. The pressure pot 150 may comprise an axial extension passing through an optional recess 145 in the entrance page 110 axially on the first friction pack 15 can work. To the pressure pot 150 with decreasing operating force again from the first friction package 15 Pushing away to its starting position is a diaphragm spring 155 provided, which is rotationally symmetrical to the axis of rotation 105 extends. The plate spring 155 is preferably axially opposite the pressure pot 150 by means of a ring 160 mounted, in the region of the radial outer side of the plate spring 155 lies. A radially inner region of the plate spring 155 An axial contact force acts on the input side 110 out.

The inner outer disc carrier 130 comprises a number of axial engagement elements 165 by corresponding recesses 170 in the entrance page 110 are guided. A circlip 175 grabs the out of the recesses 170 protruding engagement elements 165 one to the inner one External disk carrier 130 axially on the input side 110 secure against falling out. In one embodiment, the securing takes place by means of a press fit; In another embodiment, a positive locking is provided, wherein the engagement elements 165 have radial recesses into which the retaining ring 175 from a radially outer side, with respect to the axis of rotation 105 , engages. The circlip 175 preferably has a shock, so that it is elastically bent for mounting and axially over the engagement elements 165 can be pushed.

Under the influence of centrifugal force is the circlip 175 from the axis of rotation 105 accelerated radially outwards. To prevent unintentional loosening of the circlip 175 to prevent is a support ring 180 provided, which has a radial section 185 and an axial section 190 having. The axial section 190 is located radially on the outside of the locking ring 175 at. The radial section 185 lies axially between the plate spring 155 and the input side 110 and is thereby axially fixed. Preferably, the plate spring causes 155 a permanent bias on the radial section 185 of the support ring 180 In one embodiment, the bias voltage is independent of the axial position of the pressure pot 150 is that of a degree of actuation of the double clutch 100 can be dependent. Preferably, there is a radially inner region of the support ring 180 radially within the engagement elements 165 , At the radial section 185 of the support ring 180 recesses may be provided to the engagement elements 165 to let pass axially. If the recesses are opened on their radial outer sides, then the support ring 180 tabs 195 include, extending between adjacent engagement elements 165 extend radially outward.

8th shows the geometry of the support ring 180 in a longitudinal section through the axis of rotation 105 the double clutch 100 from 7 runs. In the illustrated variant, the mentioned recesses are for the engagement elements 165 opened radially outwards, so that tabs 195 result. At every tab 195 an axial section extends 190 , Here is the axial section 190 preferably shaped so that it has a radially inwardly acting spring force on the retaining ring 175 can exercise. To facilitate threading, an axial end of the section may be used 190 be bent radially outward.

The support ring 180 can in its radial section 185 a radial imprint 205 have a contact edge 210 for the diaphragm spring 155 to build. The edge of the investment 210 runs on a circumference around the axis of rotation 105 and has the smallest possible radius to a rolling of the plate spring 155 during actuation of the pressure pot 150 to support under as constant leverage as possible. In one embodiment, in 8th is shown, closes at a radial outer side of the embossing 205 a radial contact element 215 at. The investment element 215 extends at a predetermined angle in the axial direction and radially inward. This allows the diaphragm spring 155 on a radially outer boundary surface of the contact element 215 abut, so that the plate spring 155 with respect to the axis of rotation 105 radially mounted, in particular centered. Optionally, a radially inner boundary surface of the contact element 215 also be adapted to a corresponding shoulder of the input side 110 , as in 7 is shown to abut.

9 shows the support ring 180 of the 7 and 8th in another view. Here is the entire support ring 180 with its radially outwardly facing tabs 195 shown. The support ring 180 may preferably be made tool falling from a flat sheet in a single operation. This means that the finished support ring 180 the tool can be removed after the single operation or falls out of this. This operation may include a bending operation and a cutting operation performed together or at a predetermined offset.

LIST OF REFERENCE NUMBERS

1

 connecting device

2

 friction clutch

3

 torsional vibration dampers

4

 output element

5

 input element

6

 connector

7

 clamping element

8th

 admission

9

 plug-in element

10

 abutment

11

 axis of rotation

12

 wet room

13

 output shaft

14

 powertrain

15

 first friction package

16

 second friction package

17

 centrifugal pendulum

18

 intermediate element

19

 motor vehicle

20

 drive unit

21

 first pressure plate

22

 second pressure plate

23

 first friction disc

24

 second friction disc

25

 cab

26

 longitudinal axis

27

 motor axis

28

 pressure chamber

29

 actuator

30

 actuator

31

 Return spring

32

 first output shaft

33

 second output shaft

34

 protection section

35

 attachment section

36

 pendulum mass

37

 end stop

38

 outer fins

39

 inner fins

40

 lamellar tooth

41

 circlip

42

 recording device

43

 Torque transmission member

44

 External disk carrier

45

 Inner disk carrier

47

 radius

100

 radial double clutch

105

 axis of rotation

110

 input side

115

 first exit page

120

 second exit side

125

 outer outer plate carrier

130

 inner outer disc carrier

135

 outer inner plate carrier

140

 inner inner disc carrier

145

 recess

150

 pressure cooker

155

 Belleville spring

160

 ring

165

 engaging member

170

 recess

175

 circlip

180

 support ring

185

 radial section

190

 axial section

195

 flap

205

 radial embossing

210

 contact edge

215

 contact element

Claims (5)

Radial double clutch ( 100 ) with an input side ( 110 ) and a first ( 115 ) and a second output side ( 120 ) around a common axis of rotation ( 105 ) are rotatably arranged, wherein the double clutch ( 100 ) further comprises the following elements: - an external ( 125 ) and an inner outer disc carrier ( 130 ), each with the input side ( 110 ), - a first friction package ( 15 ), which radially between the outer outer plate carrier ( 125 ) and the first output side ( 115 ) lies; - a second friction package ( 16 ), which radially between the inner outer disc carrier ( 130 ) and the second output side ( 120 ) lies; - wherein the inner outer disc carrier ( 130 ) axial engagement elements ( 165 ) formed by corresponding recesses ( 170 ) in the input page ( 110 ) are guided; - a circlip ( 175 ) with a joint for positive engagement in the engagement elements ( 165 ) from the radial outside to the inner outer disc carrier ( 130 ) axially on the input side ( 110 ) against falling out; - a pressure pot ( 150 ) for the axial compression of the first friction packet ( 15 ) to transfer torque between the input side ( 110 ) and the first output side ( 115 ), - a disc spring ( 155 ) to the pressure pot ( 150 ) from the friction package ( 15 ) to interrupt the transmission of torque between the input side ( 110 ) and the second output side ( 120 ); - a support ring ( 180 ) axially between the input side ( 110 ) and the diaphragm spring is located; - wherein the support ring ( 180 ) an axial section ( 190 ), which radially outward on the retaining ring ( 175 ) is present. Double coupling ( 100 ) according to claim 1, wherein the support ring ( 180 ) one around the axis of rotation ( 105 ) circumferential axial imprinting ( 205 ) to a contact edge ( 210 ) for the diaphragm spring ( 155 ), and a bearing radius of the abutment edge ( 210 ) does not exceed a predetermined level. Double coupling ( 100 ) according to claim 1 or 2, wherein the support element ( 180 ) a radial contact element ( 215 ) to the plate spring ( 155 ) to center radially. Double coupling ( 100 ) according to one of the preceding claims, wherein the inner outer disc carrier ( 130 ) a predetermined number of axial engagement elements ( 165 ) and the support ring ( 180 ) the same number of radially outwardly facing tabs ( 195 ) and at the tabs ( 195 ) axial sections ( 215 ) for engagement radially on the outside of the locking ring ( 175 ) are provided so that the tabs ( 195 ) between respectively adjacent engagement elements ( 165 ). Double coupling ( 100 ) according to one of the preceding claims, wherein an axial travel of the pressure pot is dimensioned so that the support ring ( 180 ) always from the diaphragm spring ( 155 ) against the input side ( 110 ) is pressed.

Images