DE102013219400A1 - Inline coupling without center bar and floating centrifugal oil balance - Google Patents

Abstract

The invention relates to a double clutch, such as a wet-running double clutch, with an outer disk carrier on which a first radially inwardly pointing input disk set comprising at least one first input disk is attached and on which a second radially inwardly pointing input disk set comprising at least one second input disk is attached is, wherein a first output disk pack, comprising at least one first output disk, is connected, preferably toothed, to a first inner disk carrier with a first transmission input shaft, and the first input disk pack can be brought into a torque-transmitting operative relationship with the first output disk pack via a first activation unit having a piston, wherein a A second output disk pack, comprising at least one second output disk, is attached to a second inner disk carrier, the second inner disk carrier being connected to a second transmission input shaft t, which is designed concentrically to the first transmission input shaft, and the first input disk pack can be brought into a torque-transmitting operative relationship with the first output disk pack via an activation unit having a second piston, the two activation units being arranged between the input disk packs so that the lines of action of the actuating forces of the two activation units pass through The diameter range determined by the input and output disk packs run, the activation units preferably having a common central part, which is preferably arranged between a first outer disk support section and a second outer disk support section, connecting them, and preferably a wall of a centrifugal oil compensation device, both the first piston and the second piston engages axially.

Description

The invention relates to a double clutch, such as a wet-running double clutch, with an outer disk carrier, to which a first radially inwardly facing input disk set, comprising at least a first input fin, attached and to which a second radially inwardly facing input disk set comprising at least one second input fin , wherein a first output plate pack comprising at least a first output plate is attached to a first inner plate carrier, the first inner plate carrier being connected to a first transmission input shaft, preferably toothed, and the first input plate packet having the first output plate packet via a first piston having activating unit in torque-transmitting operative relationship can be brought, wherein a second output disk pack, comprising at least one second output disk, is attached to a second inner disk carrier, wherein the second Innenlame Ile carrier is connected to a second transmission input shaft which is formed concentrically to the first transmission input shaft, and the second input disk set with the second output disk set via a, having a second piston activating unit in torque-transmitting operative relationship can be brought.

The activation unit can also be referred to as activator. Under a disk pack is understood such a structure comprising at least one blade. An input fin package therefore has at least one input fin, whereas an output fin is included in at least one output fin package.

The first transmission input shaft is often formed as a solid shaft, whereas the second transmission input shaft is often formed as a hollow shaft.

The said double clutches are used in dual-clutch transmissions, which are installed in a drive train and used in motor vehicles, such as cars or trucks. Such double clutches can be designed as wet or dry double clutches, with usually double-clutch double clutches being designed as wet double clutches, ie as wet-running double clutches.

Different double wet clutches and dual clutch transmissions are known from the prior art.

From the DE 38 19 702 A1 is such a hydraulically actuated (operable) Doppelnasskupplung with axially successively arranged individual clutches known, the hydraulic actuators are arranged axially before or axially after the two individual clutches and on a same diameter or in a same diameter range as the individual clutches. Both the drive-side "cover" and the transmission-side "cover" of the clutch housing in this case have the hydraulic oil to the piston-cylinder units, so they are "built". This results in an axially elongated and complex structure.

Alternatively to this structure is from the DE 9 114 528 and DE 38 38 865 known to arrange the hydraulic actuators radially inwardly and axially overlapping with the individual clutches (ie below the Reiblamellenpakete). This results in an axially shorter space. Due to the radial nesting of actuation and disc packs, the disc packs lie on a relatively large diameter, with detrimental consequences for installation space, weight and moments of inertia.

In addition, increases in various concepts of the design effort of ÖIführung by rotating parts, and the complexity of various components. An even more compact design could be achieved in that between the two individual clutches and the two piston-cylinder units a common and firmly connected to the clutch housing coupling web is provided, as shown in US 3,424,033 or the EP 1 195 537 known.

In the structure known from these two publications, however, the common bridge requires a crosstalk between the individual clutches due to the shared support of the engagement forces of the individual clutches on the coupling web. In addition, resulting from the external output pots relatively high mass moments of inertia.

It is the object of the present invention to improve previously known double clutches and to remedy existing disadvantages. In this case, a low transmission-side output torque to be realized as an axial arrangement with Fliehölkompensation.

This object is achieved in that the two activation units are arranged between the Eingangslamellenpaketen that the action lines of the actuating forces of the two activation units extend through the determined by the input and Ausgangslamellenpaketen diameter range, wherein the activation units preferably have a common center part, preferably between a first outer disk carrier construction section and a second outer disk carrier construction section, these is arranged connecting, and the middle part preferably has an optional extension web, which is connected to a Fliehölkompensationseinrichtung.

This "inline" arrangement is particularly space-saving, is lighter compared to the currently known variants, achieves a high rigidity due to the extremely short frictional connections and is easy to reprocess. By a double piston chamber including a central web, which is thereby made possible, a force neutral outwardly acting design can be realized. Such a design has considerable cost and space advantages over conventional systems. It is particularly suitable for use in transmissions that can use only small space, for example. In front-transverse arrangements. This construction can also be used for any moments, in particular in the series application. Due to the use of common parts, assembly, production, maintenance and disassembly can be simplified. There are cost savings in all these areas.

Crosstalk is avoided. Under a crosstalk is here understood when closing the one friction clutch caused partial closing of the other friction clutch. The then occurring drag torque of each other friction clutch can be avoided while avoiding crosstalk.

When using a central part with extension web, the individual forces are so far out that no axial storage is necessary.

Only a low output-side mass moment of inertia is the result. The radial and axial dimensions can be reduced. No penetration is needed, but a direct control possible. There are no leaking joints in the moment flow to complain. When the short stator and the short rotor are obtained, the demountability is also simultaneously given. In addition, cooling between the two transmission shafts can be achieved in the same way as in the area of the fins.

The middle part can also be referred to as the piston center part, wherein the extension web can also be referred to as a central web. This allows all forces, driving forces, dynamic forces, which arise through the rotation and deflect the centrifugal oil compensation within the building, so that no external reaction forces arise. The construction is free of axial force and therefore does not require a thrust bearing.

A crosstalk between individual clutches can thus be avoided or largely reduced and moments of inertia compared to the known concepts are minimized when a double clutch is characterized in that piston-cylinder units of two friction clutches in the axial direction of the double clutch between the friction clutches and in the radial direction of the friction clutch in Diameter range of friction plates or Reiblamellenpaketen the individual clutches are arranged so that an actuating force direction of one of the piston-cylinder units in the direction of drive and an actuating force directions of the other of the piston-cylinder units point in the direction of transmission and the lines of action of the actuating forces in the diameter range of the friction plates or the Reiblamellenpakete the individual clutches are arranged. The dual clutch is also designed so that axially successively arranged and hydraulically actuated single clutches are combined for a dual-clutch transmission in a drive train of a vehicle. The drive train also has a friction clutch arranged on the drive side in the axial direction and a friction clutch arranged in the axial direction, a driven clutch housing and two piston-cylinder units, wherein the clutch housing is connected or integrally formed with externally arranged input disk carriers with respect to the friction clutches. wherein the clutch housing via an inner output disk carrier of a first of the friction clutches with a first transmission input shaft is connectable, and wherein the clutch housing via an inner output disk carrier of a second friction clutch with a second transmission input shaft is connectable.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

It is thus advantageous if the two activation units are equidistant from one another in the radial direction by a rotation axis around which they are rotatably arranged. There are then no or hardly tilting forces inside the double clutch.

When the first piston and the second piston are arranged so that the first piston acts on the first input disk set and the first output disk set of the first friction clutch and the second piston acts on the second input disk set and the second output disk set of the second friction clutch, the two clutches , which are also referred to as the first clutch K1 and second clutch K2, operated independently, d. H. getting closed.

It is advantageous if the central part forms a first pressure chamber and a second pressure chamber for receiving a control fluid, such as pressure oil, wherein the first piston bears against the first pressure chamber and the second piston bears against the second pressure chamber. A hydraulic actuation can then be effectively realized. The two pressure chambers are open in opposite directions ausstaltbar.

It is expedient if the centrifugal oil compensation device binds a first space for centrifugal oil, which is located on the axial side of the central part on which the first output disk pack is located and the centrifugal oil compensation device has a second space for centrifugal oil, which on the opposite side of the first space Middle part is located.

An advantageous embodiment is also characterized in that the Fliehölkompensationseinrichtung has a wall which is geometrically shaped so that on the one hand a part of the centrifugal oil is supplied to the Ausgangslamellenpaketen and the Eingangslamellenpaketen cooling, and on the other hand, a part of the centrifugal oil compensation device upon rotation of the individual components penetrating Fliehöl , Such a counterforce generated that this counteracts the Zentripetalkräften and possibly compensates for them. A relatively speed-independent operation of the double clutch is possible.

Further, it is advantageous if the wall on the one hand on the first piston and / or on the second piston, a relative movement between it and the respective piston permitting, but fluid passage preventing, is applied. Different receiving areas for centrifugal oil can then hold and improve the functionality of the device.

If the wall is divided into at least a first wall part and a second wall part, both of which are connected to the extension web, so the assembly can be simplified.

The variability in the assembly can be increased if the wall is riveted to the extension web or is rolled or connected via at least one support and / or locking ring.

It is also advantageous if the extension web forms an axially extending part of the wall. An integral design can then be realized.

It is useful if between the wall and the first piston and / or the wall and the second piston, a return element, such as a plate spring is arranged. Both the one friction clutch and the other friction clutch or one of the two friction clutches can then spend in a "normally open" position. The reliability is thereby increased. The reliability is further increased when the disc spring is supported on an outer disc carrier fixed component, such as the wall and / or the extension web and a protruding in the respective space for centrifugal oil nose of the respective piston.

The use of identical parts is possible if the double clutch is constructed to mirror a plane passing through the central part radial plane substantially mirror-symmetrical. However, the mirror symmetry can be interrupted in the region of the connection of the inner disk carrier to the respective transmission shafts.

It is also advantageous if the wall axially surrounds both the first piston, and the second piston and is preferably formed in several parts. The wall then extends radially inward from the middle part in the axial direction on the middle part and / or the extension web of the middle part over.

If a thrust bearing is located between the first inner disk carrier and the wall and / or a thrust bearing is located between the second inner disk carrier and the wall, a so-called "floating" centrifugal oil compensation is achieved which compensates for dynamic hydraulic forces which arise due to the rotation , The resulting resulting axial forces are quite low and arise from uneven Fliehölhaubenbefüllung. These external action forces are supported by thrust bearings on the hubs, on the housing. A hundred percent centrifugal oil compensation is possible. Also, a symmetrical structure of an axial dual clutch assembly with oiling on the outer disk carrier can be realized. The venting of a piston rear space is accessible via bores and / or passages in the middle part.

It has proven particularly expedient if the first inner disk carrier and / or the second inner disk carrier are each supported by two thrust bearings. It can be used on plain bearings or bearings, such as needle roller bearings, which reduces costs and increases longevity.

The weight of the double clutch can be reduced if the wall of the centrifugal oil compensation device is formed from sheet metal.

It is also advantageous if the wall has a first wall part, which is connected in the region of a radial plane through the middle part with a second wall part of the wall, preferably riveted. A permanent connection can then be realized.

It is also advantageous if a control fluid-conducting fluid supply device is provided on the first or second outer disc carrier construction section. Of course, such a fluid supply device may also be present on both outer disk carrier construction sections. Different materials, manufacturing processes and feeding options can then be realized. The axial double clutch arrangement in "inline" arrangement, should be applied from the outside via the plate carrier with pressure sleeve, which is then particularly easy. This is made possible by an oil supply, which transfers the pressure oil via a stator to the middle part. This central part makes it possible to transmit the contact forces directly and without deflection to the clutch plates.

In this case, it is advantageous if the fluid supply device has at least one first line which connects a stator in a fluid-conducting manner to the first pressure chamber and has at least one second line which connects the stator to the second pressure chamber in a fluid-conducting manner. Separate feeding of primary oil causing closure of the respective clutch is then achieved.

If the first line and / or the second line is incorporated in the first and preferably in the second outer disk carrier construction section in such a way that the outer disk carrier construction section forms the line, casting technology can be used in the production. A particularly resilient outer disk carrier construction section configuration is then the result.

However, the costs can be reduced if the first line and / or the second line is designed as a separate component from the outer disk carrier and is secured thereto.

It becomes particularly cost-effective if the fluid supply device has a connection part which is part of the first or preferably second outer disk carrier construction section or is a separate plastic component, the connection part ensuring the fluid connection of the stator to the first and / or second line.

It is also advantageous if the first line and / or the second line is designed as an extension of the plastic component / is. A complete plastic design can then be realized so that the primary oil can be brought to the respective pressure space via plastic guide elements.

It is also advantageous if the first line and / or the second line is a tube, preferably metallic building material, which opens into the plastic component. In this way, the combination of metallic pipes can be realized with existing plastic connector part, which brings advantages in terms of durability and cost.

It is expedient if two first lines are offset from each other by 180 ° relative to the axis of rotation.

Furthermore, it is expedient if two second lines are offset from each other by 180 ° relative to the axis of rotation. In such a 180 ° -Versetzung the forces arising out and a fast closing of the clutch can be achieved. However, it is also possible that four first lines and four second lines are used, which are each offset by 90 ° to each other.

The complexity of the dual clutch can be reduced if the first line runs directly next to the second line.

It is also advantageous if the first line and the second line are connected to Fluidleitöffnungen the middle part to supply the first piston and the second piston pressure oil.

Finally, the invention also relates to a drive train of a motor vehicle with a double clutch according to the invention.

The invention will be explained in more detail below with reference to some drawings, in which different embodiments are shown. Show it:

1 a first embodiment of a double clutch according to the invention in a longitudinal section with a central part, which has an extension web,

2 a variant of the first embodiment, in which a wall of a centrifugal oil compensation device is rolled at a radial end of the extension web,

3 another variant of the embodiment 1 in which the connection from the wall of the centrifugal oil compensating device to the extension web is achieved via two support rings and the extension web is designed to extend axially in order to include a space for centrifugal oil in the centrifugal oil compensation device,

4 a second embodiment of a double clutch, wherein, unlike in the first embodiment, no extension web is included between the piston of the first clutch (K1) and the second clutch (K2),

5 a detail of a variant of an embodiment according to 4 in which the wall of the centrifugal oil compensation device is formed in two parts and is riveted to one another,

6 a third embodiment of a dual clutch according to the invention with integrated into the outer disc carrier line for supplying control fluid to the pressure chambers in operative relationship with the piston,

7 a variant of the embodiment according to 6 in which the oil supply is ensured by a plastic inlay,

8th a view from the drive side to the transmission-side outer disk carrier design with plastic inlay 7 .

9 a second variant of the embodiment 6 with a combination of plastic inlay and piping for supplying pressurized oil to the two pressure chambers, and

10 a view from the drive side, so the side of an internal combustion engine, from the inside to the singularly illustrated outer disk carrier plastic inlay-casing combination.

The figures are merely schematic in nature and are only for the understanding of the invention. The same elements are given the same reference numerals.

In 1 is a first embodiment of a dual clutch according to the invention 1 shown. The double clutch 1 is a wet double clutch and has an outer disc carrier 2 on.

The outer disc carrier 2 splits into a first outer disk carrier construction section 3 and a second outer disc carrier structure section 4 on. Within the first outer disk carrier construction section 3 there is a first friction clutch K1, whereas radially inside the second outer disk carrier construction section, the second friction clutch K2 is located.

Between the two outer disc carrier sections 3 and 4 is a middle part 5 present, which extends radially inwardly and in an extension web 6 passes. On the radially outer side is the outer disk carrier 2 with the middle part 5 riveted so that the two outer disk carrier sections 3 and 4 and the middle part 5 drehunverschieblich are interconnected.

In the middle part 5 is a central vent 7 intended. This central vent 7 extends from the outside to an axially extending transverse opening 8th , A piston backspace 9 is vented in this way through the transverse opening and the vent.

The middle part 5 has a first pressure chamber 10 and a second pressure chamber 11 on. Compressed fluid, such as control fluid, for example. Primary oil, so about hydraulic oil, is in the two pressure chambers 10 and 11 via a fluid supply device 12 fed. The first pressure room 10 becomes axially on one side by a first piston 13 limited, wherein the second pressure chamber 11 on his first piston 13 opposite side by a second piston 14 is limited. At the first outer disk carrier construction section 3 are several radially inwardly projecting entrance lamellae 15 to an input disk pack 16 combined.

At the second outer disk carrier construction section 4 Also, inlet fins are mounted radially inwardly and combined to form an inlet fin package. While with respect to the friction clutch K1 from a first input fin 15 and a first input disk pack 16 is spoken, with respect to the friction clutch K2 from a second input fin 17 and a second input fin package 18 spoken.

The first input disk pack 16 stands with at least a first output plate 19 in operative relationship, wherein a plurality of first output fins are combined to form a first output fin package. The second entrance lamella 17 is operatively associated with a second exit louver, with a plurality of second exit louvers 21 to a second output disk pack 22 combined.

The first output disk pack 20 is on a first inner disk carrier 23 attached, wherein the second output disk pack 22 on a second inner disk carrier 24 is attached.

The first inner disk carrier 1 goes into a gearing area 25 via, which is formed by a separate component or an integrally connected thereto, ie one-piece component. A similar gearing area 26 is also radially inward on the second inner disk carrier 24 located. The gearing area 25 stands with a first transmission input shaft 27 in torque-transmitting effective contact, wherein the toothed area 26 with a second transmission input shaft 28 is in torque-contacting effective contact. The two transmission input shafts 27 and 28 are arranged concentrically with each other, to a rotation axis 29 , The first transmission input shaft 27 is therefore a solid shaft and the second transmission input shaft 28 a hollow shaft.

Coming back to the two pressure chambers 10 and 11 Let it be understood that they are part of a first activating device and a second activating device, respectively, which are the reference numerals 30 and 31 exhibit.

The first activator 30 has the first pressure chamber 10 and the first piston 13 on. The second pressure chamber 11 and the second piston 14 are part of the second activator 31 , The two clamping pistons extend radially inwardly into a centrifugal oil compensation device 32 into it. The centrifugal oil compensation device 32 has a wall 33 on. The wall 33 is symmetrical to a radial plane 34 formed and in particular formed in two parts. A first wall part 35 the wall 33 is together with the extension bar 6 and a second wall part 36 the wall 33 firmly connected, preferably via a rivet 37 ,

As in 2 It can be seen instead of using a rivet 37 also a curling be used, wherein the mutually facing ends of the first wall part 35 and the second wall part 36 not in contact with each other, preferably the distance of the wall thickness of one of the two wall parts 35 or 36 exhibit. On the radial inside are also two openings 38 in the wall 33 introduced, so one opening each 38 in the first wall part 35 and one opening each 38 in the second wall part 36 ,

Axial on both sides of the extension bar 6 Therefore, first and second spaces are formed 39 and 40 for receiving centrifugal oil, which is used for Fliehölkompensationskrafterzeugung. The geometry of the wall 33 and the piston 13 and 14 is coordinated in this regard.

In order to allow the supply of coolant to the disk sets of the friction clutches K1 and K2, the wall has 33 in the manner of a sheet, Kühlölleitabschnitte 41 on.

Between the wall 33 and the respective piston 13 and 14 are seals 42 available.

In the two rooms 39 and 40 is in each case acting as a return element disc spring 43 available. The respective disc spring 43 So acts as a return element to spend the respective friction clutch K1 with the friction clutch K2 in an open position.

Unlike in the 1 and 2 illustrated connection possibilities between the extension web 6 and the wall 33 , is in 3 presented an integrative solution, namely one in which the extension web 6 extends axially extending and a conclusion of each room 39 and 40 forms. Here are two support / retaining rings 44 used.

Coming back to 1 It should also be mentioned that radially outwardly directed grooves 45 in the pistons 13 and 14 are present, can be used in the seals, not shown.

In 4 Such an embodiment is reproduced in a modification of the first embodiment, which on an extension web 6 waived. Thus, also the axially extending transverse opening 8th be dispensed with, as already through the central vent 7 , which can be carried out in the manner of a bore, the piston rear space 9 can be vented. Many similarities come to mind, but here the focus should remain on the differences.

Such are the pistons 13 and 14 movable towards each other, such that they come into contact with each other or come into contact with each other almost. The two wall parts 35 and 36 However, here are not designed mirror-symmetrically to a transverse axis to the axis of rotation, so that the second wall part 36 directly or indirectly, the first wall part 35 embraces. The second wall part 36 bridges the two clamping pistons axially 13 and 14 ,

The term tensioning piston is used synonymously with pistons and is only intended to emphasize the exciting functionality.

In the mentioned indirect embracing the first wall part 35 through the second wall part 36 becomes an additional disk 46 used.

Unlike in the previously illustrated embodiment and the related variants, here four thrust bearings 47 used, which are the two inner disk carrier 23 and 24 store on both sides. The between the first wall part 35 and the first inner disc carrier 23 located thrust bearing 47 lies at the additional disk 46 at.

In a modification of the embodiment 4 is in 5 represented such a variant in which a Verbindungsniet 48 which geometrically to the embodiment 4 other wall parts 35 and 36 connects with each other. In the embodiments according to the 4 and 5 are the wall parts 35 and 36 always designed in the manner of sheet metal.

In the 6 to 10 is the supply of pressurized oil in the foreground. Thus, in a related first embodiment, the fluid supply device 12 formally in the second Außenlamellenträgerbauabschnitt 4 integrated, making this a first line 49 and a second line 50 formed. The second line 50 is indicated by dashed lines only in a short section. It is resorted to a sand casting with lost cores. The fluid supply device 12 points next to the lines 49 and 50 a connection part 51 on.

The connection part 51 is on a stator 52 put on so that the connections of the wires 49 and 50 with corresponding holes in the stator 52 correspond, allowing hydraulic fluid through the two lines 49 and 50 via Fluidleitöffnungen 53 and 54 , in the places of reference numerals 53 and 54 are indicated, can be supplied. The two pressure chambers 10 and 11 are thereby controllable with respect to the pressure contained therein and / or regulated. The extension of the pistons 13 and 14 can also be controlled or regulated as a result.

That the use of die-cast aluminum has certain advantages for the outer disk carrier construction section 4 has been shown in experiments.

In the in the 7 and 8th illustrated embodiment, the fluid supply device 12 formed of plastic and on the inside of the second outer disk carrier construction section 4 pressed.

In the in the 9 and 10 illustrated embodiment are lines 49 and 50 as metallic pipes 55 and 56 formed, with the stator 52 interacting connection part 51 made of plastic.

The two activating devices 30 and 31 are also referred to as activation units.

LIST OF REFERENCE NUMBERS

1

 Double coupling

2

 External disk carrier

3

 first outer disk carrier construction section

4

 second outer disk carrier construction section

5

 midsection

6

 extension web

7

 central vent

8th

 axially extending transverse opening

9

 Piston rear space

10

 first pressure chamber

11

 second pressure chamber

12

 fluid delivery device

13

 first piston

14

 second piston

15

 first entrance lamella

16

 first input disk pack

17

 second entrance lamella

18

 second input disk pack

19

 first exit lamella

20

 first output disk pack

21

 second output lamella

22

 second output disk pack

23

 first inner disk carrier

24

 second inner disk carrier

25

 toothed area

26

 toothed area

27

 first transmission input shaft

28

 second transmission input shaft

29

 axis of rotation

30

 first activating device

31

 second activator

32

 Fliehölkompensationseinrichtung

33

 wall

34

 radial plane

35

 first wall part

36

 second wall part

37

 rivet

38

 opening

39

 first room

40

 second room

41

 Kühlölleitabschnitt

42

 poetry

43

 Belleville spring

44

 Supporting / retaining ring

45

 groove

46

 additional disk

47

 thrust

48

 connecting rivet

49

 first line

50

 second line

51

 connector

52

 stator

53

 Fluidleitöffnung

54

 Fluidleitöffnung

55

 pipe

56

 pipe

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 3819702 A1 [0006]
• DE 9114528 [0007]
• DE 3838865 [0007]
• US 3424033 [0008]
• EP 1195537 [0008]

Claims (10)

Double coupling ( 1 ) like a wet double clutch, with an outer disc carrier ( 2 ), to which a first radially inwardly facing input disk set ( 16 ) comprising at least one first input plate ( 15 ) is attached and at which a second radially inwardly facing input disk set ( 18 ) comprising at least one second input fin ( 17 ), wherein a first output disk pack ( 20 ), comprising at least a first output plate ( 19 ), on a first inner disk carrier ( 23 ) with a first transmission input shaft ( 27 ), preferably toothed, and the first input disk set ( 16 ) with the first output disk pack ( 20 ) via a first, a piston ( 13 ) having activating unit ( 30 ) can be brought into torque-transmitting operative relationship, wherein a second output disk pack ( 22 ), comprising at least one second output plate ( 21 ), on a second inner disk carrier ( 24 ), wherein the second inner disk carrier ( 24 ) with a second transmission input shaft ( 28 ) connected to the first transmission input shaft ( 27 ) is concentrically formed, and the first input disk set ( 16 ) with the first output disk pack ( 20 ) via one, a second piston ( 14 ) having activating unit ( 31 ) can be brought into torque-transmitting operative relationship, characterized in that the two activation units ( 30 . 31 ) between the input disk packs ( 16 . 18 ) are arranged such that the action lines of the actuating forces of the two activation units ( 30 . 31 ) by the one of the input and output disk packs ( 16 . 18 . 20 . 22 ) have a certain diameter range, the activation units ( 30 . 31 ) preferably a common middle part ( 5 ) preferably between a first outer disk carrier construction section ( 3 ) and a second outer disk carrier construction section ( 4 ), this is arranged connecting, and preferably a wall ( 33 ) a centrifugal oil compensation device ( 32 ) both the first piston ( 13 ), as well as the second piston ( 14 ) surrounds axially. Double coupling ( 1 ) according to claim 1, characterized in that the two activation units ( 30 . 31 ) from a rotation axis ( 29 ), around which the see are rotatably arranged, are equidistant in the radial direction. Double coupling ( 1 ) according to claim 1 or 2, characterized in that the first piston ( 13 ) and the second piston ( 14 ) are arranged so that the first piston ( 13 ) on the first input disk pack ( 16 ) and the first output disk pack ( 20 ) of the first friction clutch (K1) acts and the second piston ( 14 ) on the second input disk pack ( 18 ) and the second output disk pack ( 22 ) of the second friction clutch (K2) acts. Double coupling ( 1 ) according to one of claims 1 to 3, characterized in that the middle part ( 5 ) a first pressure chamber ( 10 ) and a second pressure chamber ( 11 ) for receiving a control fluid, such as pressure oil, is formed, wherein at the first pressure chamber ( 10 ) the first piston ( 13 ) and at the second pressure chamber ( 11 ) the second piston ( 14 ) is present. Double coupling ( 1 ) according to one of claims 1 to 4, characterized in that the centrifugal oil compensation device ( 32 ) a first room ( 39 ) forms for centrifugal oil, which on the axial side of the middle part ( 5 ) is located, on which the first output disk pack ( 20 ) and the centrifugal oil compensation device ( 32 ) a second room ( 40 ) forms for centrifugal oil, which on the first room ( 39 ) opposite side of the middle part ( 5 ) is located. Double coupling ( 1 ) according to one of claims 1 to 5, characterized in that the centrifugal oil compensation device ( 32 ) a wall ( 33 ), which is geometrically shaped so that on the one hand a part of the centrifugal oil the Ausgangslamellenpaketen ( 20 . 22 ) and the input disk packs ( 16 . 18 ) is supplied coolingly, and on the other hand a part of the in the centrifugal oil compensation device ( 32 ) upon rotation of the individual components penetrating Fliehöl, so generates a counterforce that this counteracts the Zentripetalkräften and possibly compensates for this. Double coupling ( 1 ) according to claim 6, characterized in that the wall ( 33 ) is formed in several parts. Double coupling ( 1 ) according to claim 7, characterized in that between the first inner disk carrier ( 23 ) and the wall ( 33 ) an axial bearing ( 47 ) is located and / or between the second inner disk carrier ( 24 ) and the wall ( 33 ) an axial bearing ( 47 ) is located. Double coupling ( 1 ) according to one of claims 1 to 8, characterized in that the first inner disk carrier ( 23 ) and / or the second inner disk carrier ( 24 ) of two thrust bearings ( 47 ) is stored. Double coupling ( 1 ) according to one of claims 1 to 9, characterized in that the double clutch ( 1 ) to one through the middle part ( 5 ) extending radial plane ( 34 ) is constructed essentially mirror-symmetrical.

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