DE102009047953B4 - Double clutch for a dual-clutch transmission - Google Patents

Abstract

Double clutch (1) for an automatic or automated dual-clutch transmission, in particular for a transmission of a motor vehicle, with two friction clutches (K1, K2), with a housing (6), with at least one actuating piston (7, 8) and with at least one non-rotatable main piston ( 9, 10), with at least one bearing arrangement (11, 12), with at least one spring arrangement (13, 14) and with at least one disk carrier, in particular an outer disk carrier (15) and an inner disk carrier (18), wherein the friction clutches (K1, K2 ) on the one hand with a motor shaft and the other with a transmission input shaft is connected or connected, wherein the actuating piston (7, 8) on the one hand to the spring assembly (13, 14) and on the other hand on the main piston (9, 10) is supported, wherein the actuating piston ( 7, 8) relative to the spring arrangement (13, 14) is arranged co-rotating and the main piston (9, 10) relative to the housing (6) rotatably, but axially displaceably arranged , and wherein the bearing arrangement (12, 13) between the actuating piston (7, 8) and the main piston (9, 10) is arranged, wherein a support disc (19) is provided, wherein the support disc (19) on the plate carrier, in particular at the outer disk carrier (15) or on the inner disk carrier (18) is supported and the spring assembly (14) on the support disc (19) is supported, characterized in that the two friction clutches (K1, K2) have a common outer disk carrier (15), and that the housing (6) has a first motor-side housing part (6a) and a second gear-side housing part (6b) and at least one pressure chamber (24 or 25), wherein the main piston (9 or 10) is pressure-tight respectively in the pressure chamber (24 , 25) is arranged axially displaceable, wherein the housing parts (6a, 6b) substantially limit the coupling in the axial direction and extend substantially radially outwards.

Description

The invention relates to a double clutch, in particular for a transmission of a motor vehicle, with at least one friction clutch, with a housing, with at least one actuating piston and at least one non-rotatable main piston, with at least one bearing assembly, with at least one spring assembly and at least one disc carrier, in particular one Outer plate carrier and an inner disc carrier, wherein the friction clutch is connectable or connected to a motor shaft and the other with a transmission input shaft, wherein the actuating piston is supported on the one hand on the spring assembly and on the other hand on the main piston, wherein the actuating piston is arranged co-rotating relative to the spring assembly and the main piston is rotatably disposed relative to the housing but axially displaceable, and wherein the bearing assembly between the actuating piston and the main piston is arranged.

Double clutches are, for example, from the DE 10 2007 027 119 A1 known. Dual clutches divide the torque to be transmitted, namely two different transmission input shafts of a dual-clutch transmission. A first friction clutch is vzw. connectable to the first gear stage of the first transmission input shaft. The second friction clutch is connected or connectable to the second transmission input shaft, wherein the second transmission input shaft vzw. the even-numbered gear stages two, four, six, etc. and the first transmission input shaft are associated with the odd gear ratios one, three, five, etc. The friction clutches are designed in particular as wet-running friction clutches with a plurality of disks. The lamellae are stacked to disk packs, the outer disks are rotatably connected to an outer disk carrier. There are also provided two inner disk carrier with corresponding inner disks. The inner disks are each rotatably connected to one of the inner disk carrier. The outer disk carrier is connected to a clutch input shaft. The inner disc carriers are vzw. connected to the corresponding transmission input shafts.

For actuating the disk packs, an actuating piston is now provided for each friction clutch. Each actuating piston is supported on the one hand on a spring arrangement and on the other hand on a main piston.

From the DE 10 2005 027 467 A1 For example, a torque transmitting mechanism for a planetary gear in the form of a clutch is known. The planetary gear has a housing with two radially spaced pressure chambers. In each case a main piston is slidably disposed in the pressure chambers. An actuating piston is rotatably supported in each case via a thrust bearing as a bearing assembly on the main piston. The main piston is rotatably relative to the housing. The actuating pistons are rotatably arranged relative to the housing. The actuating pistons are supported by disc springs on the outer disk carriers. The outer disk carriers have through openings through which the actuating pistons engage with corresponding fingers in order to actuate the disk packs.

From the DE 197 45 344 A1 is also a generic coupling known. The clutch has a friction clutch, a rotationally fixed housing, an actuating piston and a relatively non-rotatably mounted to the housing main piston. The actuating piston is supported via a bearing arrangement on the main piston and supported on an inner disk carrier via a spring assembly. The actuating piston is arranged co-rotating relative to the inner disk carrier and the spring assembly. The inner disk carrier has Außenumfangskeilnuten, wherein inner disks engage in these Außenumfangskeilnuten. The actuating piston is formed as a thick, annular plate to obtain a stable and rigid structure. The actuating piston has an inner circumferential keyway, wherein the actuating piston engages with the inner peripheral keyway in the Außenumfangskeilnut of the inner disk carrier. Through this intervention, a rotational drive takes place with the inner disk carrier.

Furthermore, from the DE 10 2006 010 113 A1 a double clutch in radial design known in which an inner disc carrier of the inner clutch is rotatably supported on the housing via a radially inwardly directed web and is connected via another radially outwardly directed second web to the outer disk carrier of the outer clutch. An actuating piston of the outer clutch engages through the radially outer web and a spring arrangement acting on it is supported on the radially inner web.

The couplings known in the prior art are not yet optimally designed, in particular the known in the prior art inner disc carrier and the corresponding engaging actuating piston are expensive and only material intensive to produce.

The invention is therefore based on the object, such a double clutch to design and further develop, so that a rotational movement on the actuating piston in a cost-effective manner is transferable.

The disadvantages mentioned are now avoided by a support disk is provided, wherein the support disk is supported on the disk carrier, in particular on the outer disk carrier or on the inner disk carrier, and the spring assembly is supported on the support disk. The support disk is multi-functional. In particular, this support disk allows co-rotating actuating pistons to be assigned to both friction clutches of a dual clutch, wherein each of the actuating pistons can be actuated by a non-rotatable main piston. One of the two actuating pistons can then be supported in the preferred embodiment via the spring assembly directly to an outer disk carrier, wherein the other actuating piston can then be supported on the support disk. As a result, in the case of an axially adjacent arrangement of the two friction clutches of a double clutch, both actuating pistons can be supported on the housing via non-rotatable main pistons. The outer disk carrier then carries the outer disks of both friction clutches. The support disk forms vzw. a stop in the circumferential direction for the bearing with the aid of the support disk actuating piston. A rotational movement of the outer disk carrier is therefore transferable by means of the support disk on the actuating piston. The actuating piston can be manufactured so cost-effective, in particular as a sheet metal part, for example. By deep drawing. Furthermore, the support disk vzw. a radial stop for the actuating piston. As a result, the actuating piston is also radially positioned or fixed. For this purpose, the support disk vzw. at least one passage opening, in particular a plurality of passage openings, wherein the actuating piston passes through the passage opening. The actuating piston may have, for example, pressure arms or pressure fingers, wherein the pressure arms or pressure fingers are in particular adapted to the respective passage opening and pass through or pass through the passage openings. The peripheral region of the outer disk carrier has a toothing, wherein engage in the toothing the corresponding outer disk with teeth. The support disk can vzw. also have teeth on its outer circumference and thus also intervene in this toothing. Vzw. the outer disk carrier has an axial stop for the support disk, so that the support disk can also be loaded axially. The disadvantages mentioned above are therefore avoided and achieved corresponding advantages.

• 1 in schematischer, geschnittener Darstellung eine Doppelkupplung hälftig dargestellt, und
• 2 in schematischer Darstellung, eine Detaildarstellung der Doppelkupplung aus 1.

There are now a variety of ways to design the coupling according to the invention, in particular a dual clutch in an advantageous manner and further. For this purpose, reference may first be made to the claims subordinate to claim 1. In the following, a preferred embodiment of the invention will now be explained in more detail with reference to the following drawing and the associated description. In the drawing shows:

• 1 in schematic, sectional representation of a double clutch shown in half, and
• 2 in a schematic representation, a detailed representation of the double clutch 1 ,

In 1 and 2 is a coupling, in particular for a transmission of a motor vehicle. Good to see is a double clutch 1 for an unspecified, automatic or automated dual-clutch transmission.

In 1 is a first friction clutch K1 and a second friction clutch K2 clearly visible. The two friction clutches K1 and K2 are connectable to a not shown in detail motor shaft. Is recognizable in 1 right below a clutch input shaft 2 where the clutch input shaft 2 in turn can be connected according to the motor shaft. On the other hand, the first and the second friction clutch K1 and K2 connectable to a respective transmission input shaft of the dual clutch transmission. Shown in 1 only the corresponding connecting elements 3 and 4 , wherein the connecting elements 3 and 4 can be connected to the transmission input shafts.

The friction clutches K1 . K2 are vzw. as wet-running friction clutches K1 and K2 designed. The friction clutches K1 and K2 have unspecified disk packs 5 with inner disks and outer disks (not shown in detail) on. The inner disks and the outer disks are alternately to the disk packs 5 layered.

The double clutch 1 also has a housing 6 on. Shown in 1 is a motor-side housing part 6a and a transmission-side housing part 6b , The housing parts 6a . 6b Here, in essence, the coupling limit in the axial direction and extend substantially radially outward. For actuating the two friction clutches K1 and K2 is each of the friction clutches K1 . K2 an actuating piston 7 . 8th assigned. Every friction clutch K1 . K2 is also a main piston 9 . 10 assigned. The main pistons 9 . 10 are relative to the housing 6 or to the housing parts 6a . 6b arranged rotationally fixed. The actuating piston 7 is functionally effective on the main piston 9 supported. The actuating piston 8th is functionally effective on the main piston 10 supported.

The actuating pistons 7 and 8th are relative to the housing 6 and relative to the main pistons 9 . 10 rotatably arranged. Between the main piston 9 and the actuating piston 7 is a bearing assembly 11 arranged. Between the actuating piston 8th and the main piston 10 is a bearing arrangement 12 arranged. These bearing arrangements 11 . 12 are designed as a schematically illustrated release bearing.

Furthermore, the double clutch 1 for each friction clutch K1 . K2 a spring arrangement 13 respectively. 14 on. The actuating pistons 7 . 8th are relative to the respective spring arrangement 13 . 14 co-rotating arranged. The actuating piston 7 is on the one hand to the spring arrangement 13 and on the other hand at the main piston 9 over the bearing arrangement 11 supported. The actuating piston 8th is on the one hand to the spring arrangement 14 and on the other hand on the bearing assembly 12 or the main piston 10 supported.

The double clutch 1 also has at least one outer disk carrier 15 on. In the illustrated embodiment of the double clutch 1 is exactly an outer disc carrier 15 intended. Alternatively, however, a plurality of outer disk carrier, in particular two outer disk carrier may be provided, wherein in each case an outer disk carrier of one of the two friction clutches K1 . K2 then assigned.

In the illustrated embodiment of the double clutch 1 carries the outer disk carrier 15 both the outer disk of the first friction clutch K1 as well as the outer disks of the second friction clutch K2 , The outer disc carrier 15 is non-rotatable with the clutch input shaft 2 connected. The outer disc carrier 15 is in particular with the clutch input shaft 2 welded. The outer disc carrier 15 points at its peripheral area 16 a toothing, not shown, wherein the outer plates engage with corresponding teeth on its outer periphery (not shown) in this toothing. The outer plates are in this way on the outer plate carrier 15 arranged. Alternating with the outer plates each inner plates are layered. The outer disks and the inner disks together form the disk packs 5 the two friction clutches K1 and K2 , The inner disks of the first friction clutch K1 are on a first inner disk carrier 17 arranged. The inner disks of the second friction clutch K2 are on a second inner disk carrier 18 arranged. The first inner disk carrier 17 is rotationally fixed with the first connecting element 3 connected. The second inner disk carrier 18 is rotationally fixed with the second connecting element 4 connected.

The disadvantages mentioned are now avoided by a support disk 19 is provided, wherein the support disk 19 a plate carrier, here vzw. on the outer disk carrier 15 is supported, and the spring assembly 14 on the support disk 19 is supported. This has the advantage that for the second actuating piston 8th another release bearing between the second inner disc carrier 18 and the spring assembly 14 or between the spring assembly 14 and the second actuating piston 8th can be saved. The second actuating piston 8th is relative to the outer disk carrier 15 co-rotating arranged. The spring arrangement 14 is directly between the actuating piston 8th and also mitdrehenden support disk 19 supportable. To only one release bearing per friction clutch K1 . K2 get along, here is a co-rotating spring arrangement 14 required. The support disk 19 is therefore multi-functional. The support disk 19 serves for the rotary driving of the actuating piston 8th , The support disk 19 forms a stop in the circumferential direction for the actuating piston 8th , A rotational movement of the outer disk carrier 15 is by means of the support disk 19 on the actuating piston 8th transferable. The support disk 19 also forms a radial stop for the actuating piston 8th , This is the radial position of the actuating piston 8th established. This is achieved by the support disk 19 at least one passage opening 20 having. Vzw. are radially spaced a plurality of through openings 20 intended. The actuating piston 8th Now access through the access openings 20 , The actuating piston 8th has vzw. at least one, in particular a plurality of pressure arms 21 on, with the pressure arms 21 through the access openings 20 by rich. The pressure arms 21 are in particular the size of the through openings 20 customized. The pressure arms 21 extend substantially in the axial direction. The pressure arms 21 lie in particular on the radial outside 22 the passage opening 20 at. Because of the pressure arms 21 also on the peripheral sides (not shown and unspecified) of the through openings 20 abutment, is a rotational drive of the second actuating piston 8th ensured.

For actuating the first friction clutch K1 has the common outer disk carrier 15 also access openings 28 on. The first actuating piston 7 has correspondingly adapted pressure arms 29 on. The access openings 28 in turn provide a radial stop for the first actuating piston 7 These are the pressure arms 29 essentially on the outside of the passage openings 28 at. The access openings 20 or their peripheral sides serve as circumferential stops for rotational driving of the first actuating piston 7 ,

The support disk 19 engages here in particular in the not shown toothing of the outer disk carrier 15 one. For this purpose, the support disk 19 unspecified teeth on the teeth of the outer disk carrier 15 is adjusted.

Furthermore, the support disk 19 a bent area 23 on, radially outside the cranked area 23 are the pass-throughs 20 intended. Radial within the cranked area 23 is the spring arrangement 14 supported.

The outer disc carrier 15 represents an axial stop, not shown, for the support disk 19 ready. The stop is arranged and / or formed such that the support disk 19 can be loaded with an axial force. In particular, the support disk 19 the axial tension of the spring arrangement 14 take up. The axial stop for the support disk 19 may be formed, for example, as a retaining ring (not shown).

For actuating the actuating piston 7 and 8th (see. 1 ) has the housing 6 , namely here the housing part 6a and the housing part 6b , one main piston 9, 10 and one pressure chamber each 24 respectively. 25 on. The respective main piston 9 . 10 is sealing with a seal unspecified in the pressure chamber 24 . 25 guided. The housing 6 or the housing parts 6a . 6b each have one in the pressure chamber 24 . 25 opening pressure oil line 26 . 27 on. The pressure oil lines 26 . 27 are vzw. formed by drilling. The bores may in particular extend substantially in the axial direction.

At the here in the 1 and 2 illustrated preferred embodiment is the spring assembly 14 between the support disk 19 and the actuating piston 8th provided or supported, wherein the support disk 19 here in particular on the outer disk carrier 15 is arranged. Alternatively, the support disk 19 also on the inner disk carrier 18 be supported. It is crucial that the support disk 19 is supported on the respective component, with its "first blade" of the pressure arm 21 comes into contact. In the preferred embodiment shown here is as the first blade of the disk pack 5 provided an outer fin. In the event that as a lamella of the disk pack 5 an inner disk is provided, then the support disk 19 then with the inner disk carrier 18 rotatably connected, so that the corresponding rotational movement of this first blade is then equal to the rotational movement of the actuating piston 8th , The arrangement of the support disk 19 on an outer disk carrier or on an inner disk carrier is therefore dependent on the particular application and the formation of the disk set 5 ,

Now through the pressure oil lines 26 respectively. 27 a hydraulic fluid in the pressure chambers 24 . 25 pressed, so are the spring arrangements 13 . 14 compressed and the main pistons 9 . 10 with the bearing arrangement 11 . 12 and the actuating piston 7 . 8th shifted so that the lamellae packets 5 the first and the second friction clutch K1 . K2 be pressed together.

The double clutch 1 is formed in particular essentially mirror-symmetrical. The support disk 19 allows in particular the substantially symmetrical design of the double clutch 1 , The double clutch 1 has two disk sets arranged radially substantially at a height 5 on. The plate packs 5 are by a corresponding separation construction 30 axially spaced apart. The two disk packs 5 are in particular with the outer disk on the common outer disk carrier 15 arranged. Through the support disk 19 it is possible, a standing, ie a so-called main housing fixed to the housing 10 provided. The use of stationary or housing-fixed main pistons 9 . 10 allows the use of higher actuation pressures, as the pressure oil no longer via rotary feedthroughs into corresponding pressure chambers 24 . 25 must be pressed. The rotational movement of the actuating piston 7 . 8th is about the bearing arrangements 11 . 12 through the release bearing of the respective main piston 9 . 10 separated. To reset the respective actuating piston 7 . 8th become the spring arrangements 13 . 14 used as piston return elements.

The aforementioned disadvantages are therefore avoided and corresponding advantages are achieved.

LIST OF REFERENCE NUMBERS

1

Double coupling

2

Clutch input shaft

3

connecting member

4

connecting member

5

disk pack

6

casing

6a

housing part

6b

housing part

7

actuating piston

8th

actuating piston

9

main piston

10

main piston

11

bearing arrangement

12

bearing arrangement

13

spring assembly

14

spring assembly

15

External disk carrier

16

peripheral region

17

Inner disk carrier

18

Inner disk carrier

19

support disc

20

Through opening

21

pressure arm

22

outside

23

cranked area

24

pressure chamber

25

pressure chamber

26

Pressure oil line

27

Pressure oil line

28

Through opening

29

pressure arm

30

separating construction

K1

friction clutch

K2

friction clutch

Claims (9)

Double clutch (1) for an automatic or automated dual-clutch transmission, in particular for a transmission of a motor vehicle, with two friction clutches (K1, K2), with a housing (6), with at least one actuating piston (7, 8) and with at least one non-rotatable main piston ( 9, 10), with at least one bearing arrangement (11, 12), with at least one spring arrangement (13, 14) and with at least one disk carrier, in particular an outer disk carrier (15) and an inner disk carrier (18), wherein the friction clutches (K1, K2 ) on the one hand with a motor shaft and the other with a transmission input shaft is connected or connected, wherein the actuating piston (7, 8) on the one hand to the spring assembly (13, 14) and on the other hand on the main piston (9, 10) is supported, wherein the actuating piston ( 7, 8) relative to the spring arrangement (13, 14) is arranged co-rotating and the main piston (9, 10) relative to the housing (6) rotatably, but axially displaceably arranged , and wherein the bearing arrangement (12, 13) between the actuating piston (7, 8) and the main piston (9, 10) is arranged, wherein a support disc (19) is provided, wherein the support disc (19) on the plate carrier, in particular at the outer disk carrier (15) or on the inner disk carrier (18) is supported and the spring assembly (14) on the support disc (19) is supported, characterized in that the two friction clutches (K1, K2) have a common outer disk carrier (15), and that the housing (6) has a first motor-side housing part (6a) and a second gear-side housing part (6b) and at least one pressure chamber (24 or 25), wherein the main piston (9 or 10) is pressure-tight respectively in the pressure chamber (24 , 25) is arranged axially displaceable, wherein the housing parts (6a, 6b) substantially limit the coupling in the axial direction and extend substantially radially outwards. Double clutch to Claim 1 , characterized in that a rotational movement of the disk carrier (15, 18) by means of the support disk (19) on the actuating piston (8) is transferable. Double clutch to Claim 1 or 2 , characterized in that the support disc (19) has at least one passage opening (20), wherein the actuating piston (8) at least one pressure arm (21), in particular a plurality of pressure arms (21), and the respective pressure arm (21) through the respective passage opening (20). Double clutch according to one of the preceding claims, characterized in that the support disc (19) forms a stop in the circumferential direction for the actuating piston (8). Double clutch according to one of the preceding claims, characterized in that the support disc (19) engages in a toothing of the outer disc carrier (15). Double clutch according to one of the preceding claims, characterized in that the support disc (19) has a cranked region (23), wherein vzw. radially outwardly of the cranked region, the through openings (20) are provided and radially within the cranked region (23), the spring assembly (14) is supported. Double clutch according to one of the preceding claims, characterized in that the outer disk carrier (15) provides an axial stop for the support disk (19), wherein the stop is arranged and / or formed such that the support disk (19) can be loaded with an axial force. Double clutch according to one of the preceding claims, characterized in that the two friction clutches (K1, K2) are arranged side by side in the axial direction. Double clutch according to one of the preceding claims, characterized in that the housing (6) at least one in the pressure chamber (24, 25) opening, in particular axially extending pressure oil line (26, 27), wherein vzw. the pressure oil line (26 or 27) is designed as a bore.

Images