DE102016125264A1 - Double clutch with radially mounted disc carriers and kit of dual clutch and flywheel - Google Patents

Abstract

The invention relates to a dual clutch (1) for a drive train of a motor vehicle, with a first part clutch (2) and a second part clutch (3) for selectively transmitting torque, wherein a plurality of clutch plates (4) of each individual part clutch (2, 3) to the trapped between a respective pressure plate (5, 6) and a counter pressure plate (7, 8) for taking over a torque of a drive shaft (9) and passing to a transmission input shaft (10, 11) are arranged and prepared, wherein between the clutch plates (4) of At least one of a plate carrier (15, 16) secured against rotation, axially displaceable recorded intermediate plate (17) is present, wherein the two plate carrier (15, 16) of the first part clutch (2) and the second part clutch (3 ) are secured to a support bearing fixed component (18) via axially extending lugs (44). Furthermore, the invention relates to a kit of such a double clutch (1) and a flywheel (19).

Description

The invention relates to a dual clutch for a drive train of a motor vehicle, having a first part clutch and a second part clutch for selectively transmitting torque, wherein a plurality of clutch plates of each sub-clutch for clamping between each of a pressure plate and a reaction plate for taking over a torque of a drive shaft and passing to a Transmission input shaft are arranged and prepared, wherein between the clutch plates of the respective sub-clutch at least one of a plate carrier secured against rotation axially displaceably received intermediate plate is present. Furthermore, the invention relates to a kit of such a double clutch and a flywheel.

Double clutches are already known from the prior art. For example, the WO 2014 154 217 a dual clutch for a drive train of a motor vehicle, with two rotatably connected and at least one friction disc receiving outer carriers, wherein a first outer carrier driven in an operating state of the clutch from an output shaft of an internal combustion engine and with its at least one friction disc rotation with a first transmission input shaft driving, first inner support is connectable, and further a second outer support with its at least one friction disc rotatably connected to a second transmission input shaft driving, second inner support is connected, and with a first and second outer support rotatably relative to the transmission input shaft rotatably bearing bearing element, wherein the bearing element as a , the first and the second outer carrier is designed axially and radially bearing central warehouse.

However, the prior art always has the disadvantage that in conventional double clutches, the two plate carrier of the first sub-coupling and the second sub-coupling are welded together or that the attachment of the two plate carrier requires a large radial space.

It is therefore the object of the invention to avoid or at least mitigate the disadvantages of the prior art. In particular, a connection method is to be developed in which the two plate carriers are attached in a particularly simple and particularly space-saving manner.

The object is achieved in a generic device according to the invention in that the two disk carrier of the first sub-coupling and the second sub-coupling are attached to a support bearing fixed component about extending in the axial direction lugs.

This has the advantage that the clutch discs of the partial clutches can be made radially larger without the radial space of the entire double clutch is increased. This is possible because the plate carriers are fastened radially to the support bearing fixed component.

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

Furthermore, it is expedient if the two plate carrier are fastened / connected via a non-detachable connection to the counter-pressure plate of the first part-coupling or the second part-coupling. Since the plate carrier in operation should solve under any circumstances, it is advantageous to attach the plate carrier so that they are firmly and permanently connected to the abstützlagerfesten component, in this case, the counter-pressure plate of the second sub-coupling.

Preferably, the two plate carriers of the first sub-clutch and the second sub-clutch can be connected by a radially extending fastening means to the support bearing fixed component. This avoids that a part of the two plate carrier must extend in the radial direction to the outside, so that it can be connected via an axial attachment to the abstützlagerfesten component. This results in a considerable space savings through this connection option.

Preferably, the two plate carrier of the first part clutch and the second part clutch are riveted to the abstützlagerfesten component, pinned or screwed. Such compounds are particularly easy to assemble while offering a great resistance to loosening. The two plate carriers can also be glued to the abstützlagerfesten component.

In addition, it is advantageous if the lugs of the two disk carrier of the first sub-coupling and the second sub-coupling extend in the axial direction radially outside of the abstützlagerfesten component. Thus, the lugs can simply protrude beyond the abstützlagerfeste component without the rotational ability of the dual clutch is limited. In addition, in case of pinning or riveting it can be easily recognized at which point the noses are located.

It is also advantageous if the lugs of the first part clutch in the circumferential direction alternately to the lugs of the second part clutch are arranged, which allows the lugs of the two part clutches must not be formed overlapping and the plate carrier are still sufficiently secured.

Furthermore, it is expedient if the lugs of the two disk carrier of the first part clutch and the second part clutch are arranged on the radially same height. Since the two plate carriers are then pinned at the same height with the counter-pressure plate, the assembly of the two plate carrier can be performed in an assembly step. Also in the manufacture of the counter-pressure plate does not need to be additionally paid to the attachment of these noses, since the counter-pressure plate geometry previously used for the attachment of the noses can be used.

Preferably, the lugs can connect to the radially outer contour of the two plate carrier of the first and the second sub-coupling. This avoids that the lugs protrude radially, but it is achieved that they integrate easily into the existing structure of the plate carrier.

Moreover, it is advantageous if a radial pinning for fastening the lugs to the support bearing fixed component is arranged at the height of the lamellae toothing. It is particularly advantageous because the clutch discs can be made radially larger while maintaining the outer diameter of the dual clutch.

More preferably, the dual clutch is designed so that each clutch disc has an internal toothing, which cooperates with an external toothing of a clutch hub. The internal teeth of the clutch discs seen in the radial direction is configured differently high. It is also expedient if the internal toothing of the plurality of clutch discs cooperates with the same external toothing of the clutch hub. The external toothing of the clutch hub may have a different height range, the one area cooperating with the one clutch disk and the other area with the other clutch disk. Furthermore, the outer toothing of the clutch hub is preferably stepped and falling in a radial direction of the combustion engine-facing region in the highest. In addition, it is advantageous if the external toothing of the clutch hub is formed so that the internal toothing of a clutch disc in the axial direction radially within the other clutch disc is inserted. Advantageously, two, three, four or more clutch discs with the external teeth of the clutch hub together. It is also preferred if the geometry of the clutch discs and the clutch hub are coordinated so that they are spaced apart in any operating condition. For this purpose, a bend can be formed on the internal toothing of the one clutch disk, which is designed to keep the one clutch disk axially spaced from the other clutch disk.

A preferred embodiment is also characterized by the fact that the first sub-coupling is actuated via a pressure sleeve designed for Axialverlagern the pressure plate, and the pressure pot outside the second sub-coupling extends in the axial direction, wherein a radial outer side of at least one Drucktopfabschnittes radially further inward than at least an outer contour region of the disk carrier of the second part clutch. The pressure pot portion may merge into a radially outwardly projecting flange for attachment to the pressure plate of the first part clutch. It is advantageous if a plurality of flanges, which merge in the pressure pot sections in radially in the outer contour region of the disk carrier of the second sub-coupling, concave ribs are separated in the circumferential direction by an axially aligned recess from each other. Also, a tab of the pressure plate of the first sub-coupling can protrude radially from the disk carrier of the first sub-coupling to which the flange is attached. In addition, it is expedient if the pressure pot partially surrounds the second partial clutch. Furthermore, it is advantageous if the recesses have edges which run in the U- or V-shaped direction away from one another in the direction of the first part coupling.

The object is also achieved in that a kit from the dual clutch and a flywheel is used.

It is preferred if the flywheel has form-locking elements which cooperate positively with counter-form-locking elements, which are provided by one of the plate carrier, wherein the positive-locking elements are preferably formed as internal teeth on the flywheel and the counter-form-locking element as external teeth on the plate carrier. In this case, the external toothing of the disk carrier by the internal toothing, which is provided for receiving the pressure plate, the counter-pressure plate and / or the intermediate plate, be forcibly predetermined. It is also preferred if the internal toothing is matched to the positively predetermined external toothing. Furthermore, the disk carrier of the first sub-coupling can protrude in the axial direction into a region of the flywheel. In addition, it is expedient for the outer diameter of the disk carrier of the first partial clutch to be smaller at a first toothed region of the external toothing as at a second region of the disk carrier of the first part-coupling spaced from the first gear-toothed region. Also, the counter-pressure plate of the first part clutch may have a smaller outer diameter than the intermediate plate and / or the pressure plate of the first part clutch. Furthermore, it is advantageous if the first toothed region merges into the second toothed region in one stage. In particular, the flywheel may be formed as a two-mass flywheel.

In other words, the invention relates to a double clutch, in which the plate carrier are fixed so that radially offers a lot of space for the clutch discs with the same external space of the double clutch. Therefore, the plate carrier are fixed radially with the counter-pressure plate of the second sub-coupling, in particular pinned. The radial pinning is at the level of the lamellar toothing. The plate carriers are alternately executed with lugs on which they can be pinned. The lugs of the two plate carriers do not have to overlap.

• 1 einen Längsschnitt durch eine erfindungsgemäße Doppelkupplung mit einer ersten Teilkupplung und einer zweiten Teilkupplung in einem ersten Ausführungsbeispiel,
• 2 einen Längsschnitt durch eine Kupplungsnabe der Doppelkupplung,
• 3 einen zur 2 gedrehten Längsschnitt durch die Kupplungsnabe der Doppelkupplung,
• 4 eine zur 2 äquivalente Darstellung der Kupplungsnabe im Verschleißfall,
• 5 eine zur 4 gedrehte Längsschnittdarstellung der Kupplungsnabe im Verschleißfall,
• 6 eine perspektivische Ansicht der Doppelkupplung mit einem eine Anpressplatte der ersten Teilkupplung betätigenden Drucktopf,
• 7 eine Querschnittsdarstellung der ersten Teilkupplung,
• 8 eine zur 6 gedrehte, perspektivische Ansicht der Doppelkupplung,
• 9 einen Längsschnitt durch die erfindungsgemäße Doppelkupplung in einem zweiten Ausführungsbeispiel mit der radial verstifteten, erster Teilkupplung und der radial verstifteten zweiten Teilkupplung,
• 10 eine perspektivische Ansicht der radialen Verstiftung der ersten Teilkupplung und der zweiten Teilkupplung,
• 11 einen Längsschnitt der ersten Teilkupplung in einem dritten Ausführungsbeispiel der Doppelkupplung, und
• 12 eine perspektivische Ansicht einer Verzahnung der erfindungsgemäßen Doppelkupplung mit einem Schwungrad.

The invention will be explained below with the aid of a drawing. Show it:

• 1 a longitudinal section through a double clutch according to the invention with a first part clutch and a second part clutch in a first embodiment,
• 2 a longitudinal section through a clutch hub of the double clutch,
• 3 one to 2 rotated longitudinal section through the clutch hub of the double clutch,
• 4 one to 2 equivalent representation of the clutch hub in case of wear,
• 5 one to 4 rotated longitudinal section of the clutch hub in case of wear,
• 6 a perspective view of the double clutch with a pressure plate of the first part clutch actuated pressure pot,
• 7 a cross-sectional view of the first part clutch,
• 8th one to 6 rotated, perspective view of the double clutch,
• 9 a longitudinal section through the double clutch according to the invention in a second embodiment with the radially pinned, first part clutch and the radially pinned second part clutch,
• 10 a perspective view of the radial pinning of the first sub-coupling and the second sub-coupling,
• 11 a longitudinal section of the first part of the clutch in a third embodiment of the double clutch, and
• 12 a perspective view of a toothing of the dual clutch according to the invention with a flywheel.

The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals. The features of the individual embodiments can be interchanged.

1 shows a part of a drive train of a motor vehicle with a double clutch 1 , The double clutch consists of a first part clutch 2 and a second part clutch 3 , which are used for selectively transmitting torque. At each of the individual partial clutches 2 . 3 are several clutch discs 4 present, which are trapped between each one pressure plate 5 . 6 and a counter pressure plate 7 . 8th for taking over a torque of a drive shaft 9 and passing to a transmission input shaft 10 . 11 arranged and prepared.

In this case, each clutch disc 4 an internal toothing 12 on, over which the clutch discs 4 with an external toothing 13 a clutch hub 14 interact. The first part clutch 2 and the second part clutch 3 each have a plate carrier 15 . 16 on which is designed to the pressure plates 5 . 6 and the counter-pressure plates 7 . 8th as well as an intermediate plate 17 secured against rotation and axially displaceable record. The two plate carriers 15 . 16 the first part clutch 2 and the second part clutch 3 are on a support bearing fixed component 18 attached, as the abstützlagerfeste component 18 usually the counter pressure plate 8th the second part clutch 3 serves.

In the double clutch according to the invention 1 becomes the torque of the drive shaft 9 over a flywheel 19 on the transmission input shaft 10 . 11 transfer. For actuating the first partial clutch 2 becomes the pressure plate 5 the first part clutch 2 axially via a pressure pot designed for this purpose 20 relocated. The pressure pot 20 extends radially outside the second sub-coupling 3 in the axial direction and is via an actuator 21 , which is usually designed as a plate spring, operated. Also the second part clutch 3 is via an actuator 22 , which is also designed as a plate spring, actuated. The actuators 21 . 22 are connected via a clutch slave, not shown, and a clutch transmitter with a clutch pedal.

The 2 to 5 show an enlarged view of the clutch hub 14 the first part clutch 2 , Because the first part clutch 2 the pressure plate 5 , the intermediate plate 17 and the counterpressure plate 7 has two clutch discs 4 connected to the clutch hub. A first clutch disc 23 is disposed on the internal combustion engine side, while a second clutch disc 24 is arranged to the transmission side. The first clutch disc 23 is about friction linings 25 between the counter-pressure plate 7 and the intermediate plate 17 the first part clutch 2 jammed. In contrast, the second clutch disc 24 over friction linings 25 with the intermediate plate 17 and the pressure plate 5 the first part clutch 2 jammed.

The first clutch disc 23 is with a different gear height than the second clutch plate 24 educated. That is, the first clutch plate has a larger inner diameter and a larger inner toothing 12 having. In contrast, the second clutch disc 24 a smaller inner diameter and therefore also a less highly arranged internal toothing 12 , To the clutch hub 14 Being able to interact is also the outer toothing 13 on the clutch hub 14 gradually sloping, so that a toothed area 26 that with the first clutch disc 23 cooperates, has a larger outer diameter than a second toothed area 27 the external toothing 13 the clutch hub 14 that with the second clutch disc 24 interacts. The two toothed areas 26 . 27 have such a big difference that the internal teeth 12 the second clutch disc 24 under the first clutch disc 23 can be inserted.

In the un-worn condition, the two clutch discs 23 . 24 spaced so far apart that a bend 28 on the internal toothing 12 the second clutch disc 24 not under the internal teeth 12 the first clutch disc 23 attacks. In a worn condition (cf. 4 . 5 ), so at a wear of the friction linings 25 , attacks the bend 28 the second clutch disc 24 under the first clutch disc 23 one. Due to this structural design of the two clutch discs 23 . 24 are the discs 23 . 24 so spaced even in this state.

The axial position of the clutch hub 14 the first part clutch 2 gets hit by a stop 29 the between the first clutch disc 23 and the flywheel 19 is arranged, and a Kupplungsnabensicherungungsring 30 established. The internal toothing 12 the clutch discs 4 is designed so that the inner diameter of the clutch discs 4 larger than a support bearing safety ring 31 who is the support camp 32 holds axially.

In 6 is seen as a radial outside 33 of the pressure pot 20 the second part clutch 3 surrounds radially outside. A pressure pot section emerges 34 the radial outside 33 in an outer contour area 35 of the disk carrier 16 the second part clutch 3 one. The outer contour area 35 of the disk carrier 16 is by the inclusion of the pressure plate 6 , the counterpressure plate 8th and several intermediate plates 17 on the inside of the plate carrier 16 educated.

The pressure pot section 34 goes into a flange 36 over, with the flange 36 is designed to the pressure pot 20 to the pressure plate 5 the first part clutch 2 to tie. At the pressure pot 20 are several flanges 36 arranged in the circumferential direction, wherein the flanges 36 by an axially aligned recess 37 are separated from each other.

The flanges 36 go in the pressure pot sections 34 in ribs 38 above. Ribs 38 dive radially into the outer contour area 35 of the disk carrier 16 the second part clutch 3 one. So is an outer surface 39 the ribs 38 concave arched. The flange 36 is on a tab 39 the pressure plate 5 the first part clutch 2 attached, with the tab 39 radially out of the plate carrier 15 the first part clutch 2 protrudes. The flange 36 of the pressure pot 20 is preferably with the tab 40 the pressure plate 5 the first part clutch via a rivet 41 connected.

The pressure pot sections 34 are arranged so that they are the counter-plate 8th the second part clutch 3 in the axial direction outside overlap or in a radial recess of the counter-plate 8th succeed. The pressure pot sections 34 are about the circumference of the pressure pot 20 arranged equally distributed. The pressure pot sections 34 whose radial outside 33 radially inward than the outer contour area 35 of the disk carrier 16 the second part clutch 3 , are geometrically on the outer contour of the disk carrier 16 agreed (cf. 7 ).

As in 8th to see, the pressure pot surrounds 20 the second part clutch 3 partially closed on the side where the double clutch is actuated. The recesses 37 in the pressure pot 20 have edges 42 , the U- or V-shaped in the direction of the first part clutch 2 Run away from each other. The recesses 37 extend in the axial direction over about one third of the radial outside 33 of the pressure pot 20 so that the pressure pot 20 has a sufficiently high stability in the axial direction.

In a first embodiment of the double clutch 1 (see. 1 ) are the two plate carrier 15 . 16 the first part clutch 2 and the second part clutch 3 on the support bearing fixed component 18 , in particular the counter-pressure plate 8th the second part clutch 3 , riveted in the axial direction. In a second embodiment of the double clutch 1 (see. 9 ) become the plate carriers 15 . 16 but so on the abstützlagerfesten component 18 attached that they have a radial pinning 43 at the counterpressure plate 8th be connected. The two plate carriers 15 . 16 are therefore arranged at the same radial height.

The plate carriers 15 . 16 the first part clutch 2 and the second part clutch 3 form at their radially outermost contour subsequent noses 44 out, each the counterpressure plate 8th overlap radially outside. The noses 44 thus extend in the axial direction and can via a radially extending fastener 35 at the counterpressure plate 8th be attached. This is how the two plate carriers become 15 . 16 So over a permanent connection to the counter-pressure plate 8th attached. The noses 44 the two plate carriers 15 . 16 are arranged on the same radial height, but alternately formed in the circumferential direction, so that they do not overlap. How good in 10 to recognize, so are the noses 44 the first part clutch 2 alternating with the noses 44 the second part clutch 3 educated. The noses 44 are beyond the circumference of each disc carrier 15 . 16 arranged equally distributed. The noses 44 be with the abstützlagerfesten component 18 , in particular the counter-pressure plate 8th , riveted, pinned, screwed or glued. The noses 44 are at the counterpressure plate 8th arranged at the height of the lamellae. This allows the counter pressure plates 7 . 8th , the pressure plates 5 . 6 and the intermediate plates 17 be made radially larger.

The double clutch 1 acts with a flywheel 19 together, with the flywheel 19 Positive-locking elements has, with counter-form-locking elements, by one of the plate carrier 15 . 16 are put together, positively cooperate. The form-locking elements on the flywheel 19 are in the manner of an internal toothing 46 educated. The internal toothing 46 is on a tooth flange 47 the flywheel 19 attached. The flywheel 19 is in this embodiment as a dual mass flywheel with an integrated torsion damper 48 educated.

The counter-form-locking elements are characterized by an external toothing 49 of the disk carrier 15 educated. Here is the external toothing 49 of the disk carrier 15 through the internal toothing, which absorbs the pressure plate 5 , the counterpressure plate 7 and the intermediate plate 17 is provided, forced. The internal toothing 46 of the tooth flange 47 the flywheel 19 So it is exactly on the plate carrier 15 Voted.

The plate carrier 15 the first part clutch 2 protrudes in the axial direction in a region of the flywheel 19 into it, so that axial space can be saved. In a third embodiment of the double clutch 1 (see. 11 ) is the outer diameter of the disk carrier 15 the first part clutch 2 at a first gearing area 50 the external toothing 49 smaller than at one to the first gear area 50 axially spaced second area / gearing area 51 of the disk carrier 15 the first part clutch 2 , Due to the height difference in the gearing 49 can be an area of the first part clutch 2 under the flywheel 19 to be ordered. The external toothing 49 So it's one step 52 formed in the combustion engine-facing area. This geometric design of the disk carrier 15 the first part clutch 2 conditionally that the counter plate 7 the first part clutch 2 a smaller outer diameter than the intermediate plate 17 and / or the pressure plate 5 the first part clutch 2 having. In the perspective view of 12 is clearly seen that the internal teeth 46 the flywheel 19 in the integral with the plate carrier 15 the first part clutch formed external teeth 49 intervenes.

LIST OF REFERENCE NUMBERS

1

Double coupling

2

first part clutch

3

second part clutch

4

clutch disc

5

pressure plate

6

pressure plate

7

Platen

8th

Platen

9

drive shaft

10

Transmission input shaft

11

Transmission input shaft

12

internal gearing

13

external teeth

14

clutch

15

plate carrier

16

plate carrier

17

intermediate plate

18

support bearing fixed component

19

flywheel

20

pressure cooker

21

jig

22

jig

23

first clutch disc

24

second clutch disc

25

friction linings

26

first toothing area

27

second toothed area

28

bend

29

attack

30

Clutch hub retaining ring

31

Support bearing retaining ring

32

support bearings

33

radial outside

34

Pressure pot section

35

Outer contour region

36

flange

37

recess

38

rib

39

outer surface

40

flap

41

rivet

42

edge

43

radial pinning

44

nose

45

fastener

46

internal gearing

47

toothed flange

48

torsional vibration damper

49

external teeth

50

first toothing area

51

second area / gearing area

52

step

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

• WO 2014154217 [0002]

Claims (10)

Double clutch (1) for a drive train of a motor vehicle, with a first part clutch (2) and a second part clutch (3) for selectively transmitting torque, wherein a plurality of clutch discs (4) of each sub-clutch (2, 3) are trapped between each one Pressure plate (5, 6) and a counter-pressure plate (7, 8) for taking over a torque of a drive shaft (9) and passing to a transmission input shaft (10, 11) are arranged and prepared, wherein between the clutch discs (4) of the respective part clutch (2 , 3) at least one of a plate carrier (15, 16) secured against rotation, axially displaceable recorded intermediate plate (17) is present, characterized in that the two plate carrier (15, 16) of the first part clutch (2) and the second part clutch (3) are attached to a support bearing fixed component (18) extending in the axial direction lugs (44). Double clutch (1) to Claim 1 , characterized in that the two plate carrier (15, 16) via a non-detachable connection to the counter-pressure plate (7, 8) of the first part clutch (2) or the second part clutch (3) are attached. Double clutch (1) after one of Claims 1 or 2 , characterized in that the two plate carriers (15, 16) of the first part clutch (2) and the second part clutch (3) by a radially extending fastening means (45) on the abstützlagerfesten component (18) are connected. Double clutch (1) after one of Claims 1 to 3 , characterized in that the two plate carriers (15, 16) of the first part clutch (2) and the second part clutch (3) with the abstützlagerfesten component (18) riveted, pinned or screwed. Double clutch (1) after one of Claims 1 to 4 , characterized in that the lugs (44) of the two plate carriers (15, 16) of the first part clutch (2) and the second part clutch (3) extend in the axial direction radially outside of the abstützlagerfesten component (18). Double clutch (1) after one of Claims 1 to 5 , characterized in that the lugs (44) of the disk carrier (15) of the first part clutch (2) in the circumferential direction alternately to the lugs (44) of the disk carrier (16) of the second part clutch (3) are arranged. Double clutch (1) after one of Claims 1 to 6 , characterized in that the lugs (44) of the two plate carriers (15, 16) of the first part clutch (2) and the second part clutch (3) are arranged on the radially same height. Double clutch (1) after one of Claims 1 to 7 , characterized in that the lugs (44) adjoin the radially outermost contour of the two disk carriers (15, 16) of the first part clutch (2) and the second part clutch (3). Double clutch (1) after one of Claims 1 to 8th , characterized in that a radial pinning (43) for fixing the lugs (44) on the abstützlagerfesten component (18) is arranged at the height of the lamellar toothing. Kit of double clutch (1) according to one of Claims 1 to 9 and a flywheel (19).

Images