DE102011006029B4 - Sealing arrangement for wet running double clutch - Google Patents

Abstract

Coupling, in particular double clutch, for the arrangement in a drive train of a motor vehicle between a drive unit and a transmission for transmitting a torque from the drive unit to the transmission, with at least one first multi-plate clutch arrangement (2) which has a transmission-side plate carrier (5; 6) and a drive-side plate carrier (7; 8), the clutch arrangement (2) being actuable by means of an actuating piston (16) which can be pressurized, the piston neck (19) of which is connected in a rotationally fixed manner to an oil supply hub (4) and which is a pressure chamber (24 ) facing first effective area and a second effective area facing a pressure equalization space (27), the pressure equalizing space (27) being connected essentially radially from the second effective area of the actuating piston (16), the oil supply hub (4) and one connected to the oil supply hub (4) extending wall (40) is formed and via a Sealing arrangement is sealed, the sealing arrangement having a seal carrier (42) with a first groove (44) formed therein and a seal (43) insertable into the first groove (44), characterized in that the piston neck extends axially and the oil feed hub radially and that the first groove (44) with the first seal (43) inserted therein provides a seal with respect to the wall (40), and the seal carrier (42) further has a second groove (47) which is connected to the oil supply hub ( 4) facing side of the seal carrier (42) and into which a seal (46) can be inserted, which provides a seal with respect to the piston neck (19) connected to the oil supply hub (4).

Description

The invention relates to a clutch device, in particular a double clutch device for the arrangement in a drive train of a motor vehicle between a drive unit and a transmission for transmitting a torque from the drive unit to the transmission, according to the preamble of patent claim 1.

From the EP 1 780 435 A2 a double clutch device is known in radial design, which is provided for the arrangement in a drive train of a motor vehicle between a drive unit and a transmission. The clutch device has a first clutch arrangement assigned to a first transmission input shaft of the transmission and a second clutch arrangement assigned to a second transmission input shaft of the transmission, by means of which the torque transmission between the drive unit and the transmission takes place. The first transmission input shaft is designed as a hollow shaft and the second transmission input shaft is surrounded by the first transmission shaft. The two clutch arrangements are associated with disk packs which can be actuated by means of hydraulically activatable actuating pistons, the actuating pistons each being assigned a pressure compensation chamber. The plate pack includes an inner plate carrier and an outer plate carrier, for the non-rotatable arrangement of the inner and outer plates. Cooling oil flows through the clutch plates for cooling, the cooling oil reaching the clutch plates via the pressure compensation chamber. The oil-bearing pressure compensation chambers are secured against oil loss by sealing elements. Further prior art is from, for example DE 10 2008 018 715 A1 . DE 197 00 635 A1 or DE 10 2005 044 227 A1 known.

A disadvantage of this prior art, however, is that the known sealing elements can form leaks when the clutch is actuated, as a result of which the oil pressure serving to cool the lamellae decreases. However, a reduction in the oil pressure in the pressure compensation chamber increases the drag torque when the clutch is released, since the oil pressure present in the pressure compensation chamber counteracts the oil pressure with which the pressure chamber is acted upon and which serves to shift the actuating piston. The seals previously used to seal the pressure compensation spaces are also technically complex to assemble and therefore expensive to manufacture.

It is therefore an object of the present invention to provide a sealing arrangement which is structurally simpler to manufacture and which also seals the pressure compensation chamber in a resistant manner against leaks.

The object is achieved by a coupling device with the features of patent claim 1.

The invention is based on the idea of providing, instead of the vulcanized seals used hitherto, a seal arrangement for a coupling device which comprises a seal carrier which at least in regions corresponds in shape and scope to the inner contour of a pressure compensation chamber and which seals the pressure compensation chamber to the outside at least in regions. According to the invention, a first groove is provided in the seal carrier, into which a seal can be inserted, which seals the seal carrier against leakage-proof against a wall enclosing the pressure compensation chamber.

With regard to their elasticity, the seal carrier and the seal inserted into the first groove of the seal carrier are preferably designed in such a way that the seal carrier together with the seal is axially displaceable relative to the wall of the pressure compensation space. Due to the seal that can be inserted into the first groove, the pressure compensation space is sealed against leakage from the wall.

Furthermore, it can prove to be advantageous to design both the seal carrier and the seal that can be inserted into the first groove in such a way that their sealing ability is independent of the temperature of the oil in the pressure compensation chamber. Another advantage of the seal arrangement is that it is possible to dispense with the technically complex vulcanization of the seal to an actuating piston and the internal guidance of the seal carrier in the pressure compensation chamber is significantly improved.

According to a further preferred embodiment of the invention, the seal carrier has a contact surface corresponding to a second active surface of the actuating piston and is preferably designed to be clamped onto a piston neck of the actuating piston. In this way, the seal carrier is captively attached to a piston neck of the actuating piston, as a result of which the internal volume of the pressure compensation space can be maximized.

In a further preferred embodiment of the invention it is provided that the first groove with the first seal inserted therein provides a seal with respect to the wall of the pressure compensation space and the seal carrier has a second groove which is formed on the side of the seal carrier facing an oil supply hub and in which a further seal can be inserted, which is connected to that with the oil supply hub Piston neck provides an additional seal. The first and the second groove are designed in such a way that they hold the associated seal in a captive manner even when the seal carrier moves axially in relation to the oil supply hub, a leak-proof seal being nevertheless ensured.

In a further advantageous embodiment of the invention, it is provided that a reset element is arranged in the pressure compensation chamber, which returns the actuating piston to its starting position when the clutch is not actuated or when the clutch is released, and that the seal carrier is designed to radially encompass the reset element on its outer circumference. The restoring element can be designed, for example, as a spring assembly. The advantage of this design is that the coupling device can be made radially (and preferably also axially) narrower than the oil supply hub, since the seal carrier and the restoring element are arranged in one another and are radially equally spaced from the oil supply hub. The seal carrier is preferably designed in this way that it can follow the axial length change of the restoring element while maintaining its sealability.

For this purpose, a preferred embodiment of the invention provides that the restoring element is designed as a coil spring package and the seal carrier has a receptacle that supports the coil spring package.

In addition, it is provided that the receptacle in the seal carrier is designed as an essentially annular recess. The shape of the recess can be adapted to the outer circumference of the coil spring. However, the ring shape of the recess is only an example and is in no way intended exclusively. Instead of a coil spring package, any other technical solution for a restoring element is also conceivable, on the outer contour of which the recess can be adapted.

According to a further preferred embodiment of the invention, it is provided that the receptacle in the seal carrier is designed as a pocket, each of which receives a coil spring of the coil spring package. Depending on the size and scope of the drive unit and the gearbox, the coupling device can be reinforced by installing additional pockets for additional coil spring packages.

In addition, it can be provided that the at least one coil spring assembly is supported on the wall on the side facing away from the seal carrier. Both the wall and the seal carrier are designed in such a way that they each provide the coil spring assembly with sufficient support surface axially when the coil spring is compressed and expanded, when the clutch is closed and when the clutch is released.

According to a further preferred embodiment of the invention, the pressure chamber can be delimited by a first active surface of the actuating piston and a gear-side disk carrier, a sealing arrangement which can be clamped onto the disk carrier and having a second seal carrier and a seal connected to the second seal carrier being provided between the actuating piston and the disk carrier , wherein the seal is preferably glued on.

The seal carrier itself can be made of plastic or any other suitable material.

The embodiments of the invention prove to be advantageous since the pressure space of the coupling device can additionally be secured against oil loss and thus against undesired towing of the coupling device, which significantly increases the service life and the ease of use of the coupling device.

Further advantages and advantageous embodiments are defined in the subclaims, the description and the drawings.

The invention is to be explained in more detail below by way of example, without restricting generality, using an exemplary embodiment shown in the drawings.

• 1: Eine schematische Schnittansicht durch ein erstes bevorzugtes Ausführungsbeispiel einer Doppelkupplungseinrichtung mit der erfindungsgemäßen Dichtungsanordnung und
• 2: eine vergrößerte Darstellung der in 1 gezeigten erfindungsgemäßen Dichtungsanordnung.

Show it:

• 1 : A schematic sectional view through a first preferred embodiment of a double clutch device with the sealing arrangement according to the invention and
• 2 : an enlarged view of the in 1 shown sealing arrangement according to the invention.

In the following figures, elements with the same function are each numbered with the same reference numerals.

1 and sections 2 show a double clutch 1 with an inner clutch assembly 2 and an outer clutch assembly 3 , The clutch assemblies 2 and 3 are designed as multi-plate clutches, each with an inner plate carrier 5 . 6 and an outer disk carrier 7 . 8th have, which on the lamellar carriers 5 . 6 and 7 . 8th arranged slats 9 . 11 , and 10 . 12 interlock and form lamella packs.

The outer disk carrier 7 is torsion-proof with a driver 13 the double clutch 1 connected, which in turn is rotatably connected to an output shaft of a drive unit, not shown, so that via the driver 13 torque during operation from the drive unit to the double clutch 1 is initiated. Because both the outer disk carrier 7 the outer clutch assembly 2 as well as the outer disk carrier 8th the inner coupling device 3 non-rotatable with an oil feed hub 4 are connected, the torque is via the driver 13 also on the inner clutch assembly 3 initiated.

The inner disk carriers are on the transmission side 5 . 6 rotationally fixed by means of, for example, a toothing with a transmission input shaft in each case 14 . 15 connected, the inner disk carrier 6 the inner clutch assembly 3 with the first transmission input shaft designed as a hollow shaft 15 connected is. The transmission input shaft designed as a hollow shaft 15 surrounds a second transmission input shaft 14 which in turn with the inner disk carrier 5 the outer coupling device 2 is rotatably connected. If the clutch is brought into frictional engagement, the torque of the drive unit is either via the first clutch arrangement 2 or the second clutch arrangement 3 transferred by the appropriate slats 10 . 12 , respectively. 9 . 11 be brought into frictional engagement.

In this way, the outer disc carrier 7 . 8th a drive-side clutch part and through the inner plate carrier 5 . 6 a transmission-side coupling part is formed.

In order to bring the plates into frictional engagement, each clutch arrangement is 2 . 3 one actuating piston each 16 . 17 assigned, which acts on the plate packs with a force acting in the axial direction. The actuating piston 16 . 17 are pressure rooms 24 . 25 assigned to form the axial force on the actuating piston 16 . 17 be pressurized with fluid. This pressure fluid is through holes in the oil feed hub 11 fed. The pressure fluid advantageously also serves as cooling oil for the multi-plate clutch, the cooling oil flow being the double clutch 1 Flows in an essentially radial direction from the inside to the outside. Additionally or alternatively, the cooling oil can also be between the oil feed hub 4 and the outer transmission input shaft 15 be fed.

To the clutch assembly 2 . 3 reset elements are to be solved 20 . 22 provided that in the case shown here as a plate spring 20 and coil spring 22 are trained. The reset elements 20 . 22 outgoing force acts on the pressure chamber 24 respectively. 25 on the actuating piston 16 respectively. 17 counteracting pressure. There is no more fluid in the pressure chamber 24 . 25 supplied, i.e. the pressure in the pressure chamber 24 respectively. 25 reduced, causes the pressure of the respective reset element 20 . 22 releasing the multi-plate clutch assembly 2 . 3 by an axial displacement of the actuating pistons 16 . 17 in the direction of the transmission (not shown).

The pressure room 25 of the actuating piston 17 is through the actuating piston 17 whose piston neck 18 and a clutch housing cover 30 delimited the wet area of the clutch assembly 3 concludes. On his from the piston neck 18 the opposite end is the pressure chamber 25 via a sealing element 31 sealed at the top. Between the actuating piston 17 and the transmission-side outside of the transmission-side plate carrier 7 is a pressure equalization room 28 arranged by another sealing element 33 is sealed radially outwards. The pressure room 24 of the actuating piston 16 is from the outer disk carrier 7 and the actuating piston 16 limited. The pressure chamber ends radially on the inside 24 on the oil feed hub 4 , An associated pressure equalization room 27 is radially outwards via a seal carrier 42 sealed and by the actuating piston 16 , the oil feed hub 4 and one with the oil feed hub 4 connected, essentially radially extending wall 40 limited.

All or only some of the sealing elements shown here 31 . 33 . 35 . 36 . 42 . 43 can be designed as seals according to the invention. In the following, however, the innovative sealing concept is exemplified with regard to the sealing elements of the inner multi-plate clutch arrangement 2 described. It shows 2 For an improved understanding an enlarged view of the relevant components.

As in 2 are recognizable between the actuating piston 16 and the outer disk carrier 7 and to seal the pressure compensation chamber 27 Exemplary embodiments of the novel sealing concept are shown.

Within the pressure equalization room 27 a seal arrangement is shown, the first seal carrier 42 and a seal 43 has, which in one, in the seal carrier 42 trained first groove 44 is inserted. The seal carrier 42 is the shape and scope of the actuating piston 16 modeled. Furthermore, the seal carrier 42 a recess at its radially inner end 47 on into which a seal 46 is introduced, which is a seal between the actuating piston 16 and the seal carrier 42 creates and the pressure compensation space 27 seals. That in the pressure equalization room 27 arranged reset element 22 that the actuating piston 16 the multi-plate clutch arrangement 2 when the clutch device is not actuated 1 leads back to a starting position, is in the 1 and 2 formed as a coil spring package. In the sectional view of the 1 and 2 only a single coil spring is visible due to the illustration.

How 2 can still be seen, grips the seal carrier 42 the reset element 22 radially on its outer circumference, so that the restoring element 22 is supported radially outwards. The seal carrier can do this 42 have an annular recess. In addition, the seal carrier 42 also have individual pockets, each of which is used to hold a coil spring of a coil spring package. Concerning. The advantages of using a coil spring are on the parallel application, published under DE 10 2011 006 027 A1 (Sign of the applicant: 003719-DE-NP), which is hereby fully incorporated into this application.

For sealing the pressure chamber 24 is a second seal carrier 35 provided the the pressure room 24 on the of the oil supply hub 4 seals the opposite side. At the end of the second seal carrier 35 that the pressure room 24 is facing is on the seal carrier 35 additionally a seal 36 attached, which can be glued, for example. The seals 35 . 36 can on the outer disk carrier 7 be pinched. The seal 36 is in 2 designed as a sealing ring with a circumferential nose 37 in a groove 38 of the actuating piston 16 intervenes.

A particular advantage of the inventive sealing concept described here is that the sealing elements no longer have to be vulcanized in an additional time-consuming step, but can be pushed onto the seal carrier in a time-saving manner, so that the manufacturing process can be accelerated.

LIST OF REFERENCE NUMBERS

1

Dual clutch assembly

2

Multi-plate clutch arrangement

3

Multi-plate clutch arrangement

4

Ölzuführnabe

5

Inner disk carrier

6

Inner disk carrier

7

External disk carrier

8th

External disk carrier

9

Clutch plates on the drive side

10

Clutch plates on the drive side

11

Clutch plates on the transmission side

12

Clutch plates on the transmission side

13

takeaway

14

Transmission input shaft

15

Transmission input shaft

16

actuating piston

17

actuating piston

18

tang

19

tang

20

Return element

22

Return element

24

pressure chamber

25

pressure chamber

27

Centrifugal compensation chamber

28

Centrifugal compensation chamber

30

Clutch cover

31

sealing element

33

sealing element

35

second seal carrier

36

poetry

37

nose

38

groove

40

wall

42

seal carrier

43

poetry

44

groove

46

All-round seal

47

recess

Claims (9)

Coupling, in particular double clutch, for the arrangement in a drive train of a motor vehicle between a drive unit and a transmission for transmitting a torque from the drive unit to the transmission, with at least one first multi-plate clutch arrangement (2) which has a transmission-side plate carrier (5; 6) and a drive-side plate carrier (7; 8), the clutch arrangement (2) being actuable by means of an actuating piston (16) which can be pressurized, the piston neck (19) of which is connected in a rotationally fixed manner to an oil supply hub (4) and which is a pressure chamber (24 ) facing first effective area and a second effective area facing a pressure equalization space (27), the pressure equalizing space (27) from the second Active surface of the actuating piston (16), the oil feed hub (4) and a substantially radially extending wall (40) connected to the oil feed hub (4) is formed and is sealed by a seal arrangement, the seal arrangement comprising a seal carrier (42) with a first groove (44) formed therein and a seal (43) which can be inserted into the first groove (44), characterized in that the piston neck extends axially and radially surrounds the oil supply hub, and in that the first groove (44) with the first groove inserted therein Seal (43) provides a seal with respect to the wall (40), and the seal carrier (42) further has a second groove (47) which is formed on the side of the seal carrier (42) facing the oil supply hub (4) and into which one Seal (46) can be inserted, which provides a seal with respect to the piston neck (19) connected to the oil supply hub (4). Clutch after Claim 1 , wherein the seal carrier (42) has a contact surface corresponding to the second active surface of the actuating piston (16), and is preferably designed to be clamped onto the piston neck (19). Coupling according to one of the preceding claims, wherein a return element (22) is further arranged in the pressure compensation space (27), which guides the actuating piston (16) into its initial position when not actuated, and the seal carrier (42) is designed for this purpose, the reset element (22 ) to grip radially around its outer circumference. Clutch after Claim 3 , wherein the restoring element (22) is designed as a coil spring package, and the seal carrier (42) has a receptacle that supports the coil spring package. Clutch after Claim 4 , wherein the receptacle is designed as an essentially annular recess in the seal carrier (42). Clutch after Claim 4 , wherein the receptacle is designed as pockets that each receive a coil spring of the coil spring package. Clutch after Claim 4 . 5 or 6 , wherein the coil spring assembly is supported on the side facing away from the seal carrier (42) on the wall (40). Coupling according to one of the preceding claims, wherein the pressure chamber (24) is delimited by the first active surface of the actuating piston (16) and the drive-side disk carrier (7), wherein between the actuating piston (16) and the disk carrier (7) a on the disk carrier (7) Clampable seal arrangement is provided, which has a second seal carrier (35) and a seal (36) connected to the second seal carrier (35), the seal (36) preferably being glued on. Coupling according to one of the preceding claims, wherein at least one of the seal carriers (42; 35) is made of plastic.

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