DE102011006029A1 - Dual clutch device used for motor vehicle, has actuating piston whose pressure equalization chamber wall is connected to oil supply hub - Google Patents

Abstract

The device (1) has a multi-plate clutch assembly (2) that is operated through an actuating piston (16). The neck region (19) of actuating piston is provided with an oil supply hub (4). A pressure equalization chamber is formed on the surface of actuating piston. The radially extending wall of pressure equalization chamber of piston is connected to the oil supply hub. A gasket is inserted into the grooves of seal carrier.

Description

The invention relates to a coupling 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 is a double clutch device of the radial type known, which is provided for the arrangement in a drive train of a motor vehicle between a drive unit and a transmission. The coupling 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 which the torque transmission takes place between the drive unit and the transmission. In this case, the first transmission input shaft is formed as a hollow shaft and the second transmission input shaft surrounded by the first transmission shaft. The two clutch assemblies are assigned disc packs which can be actuated by means of hydraulically activatable actuating piston, wherein the actuating piston is associated with a respective pressure compensation chamber. The disk set comprises in each case an inner disk carrier and an outer disk carrier for the rotationally fixed arrangement of the inner and outer disks. Cooling oil flows through the clutch plates for cooling, whereby the cooling oil reaches the clutch plates via the pressure equalization chamber. The oil-carrying pressure compensation chambers are secured against oil loss by sealing elements.

A disadvantage of this prior art, however, is that the known sealing elements can form leaks in the course of the actuation of the clutch, whereby the oil pressure serving the finned cooling decreases. A reduction in the oil pressure in the pressure compensation chamber, however, increases the drag torque when releasing the clutch, since the voltage applied in the pressure compensation chamber oil pressure counteracts the oil pressure, which is applied to the pressure chamber and which serves for the displacement of the actuating piston. The seals previously used to seal the pressure compensation chambers are also technically expensive to assemble and thus expensive to manufacture.

Object of the present invention is therefore to provide a seal assembly that is structurally simpler to manufacture and also seals the pressure compensation chamber resistant to leaks.

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

The invention is based on the idea of providing a sealing arrangement for a coupling device comprising a seal carrier which at least partially corresponds in shape and extent to the inner contour of a pressure equalization chamber and which at least partially seals the pressure compensation chamber to the outside. 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 leaks relative to a wall enclosing the pressure equalization chamber.

Preferably, with regard to their elasticity, the seal carrier and the seal inserted into the first groove of the seal carrier are designed such that the seal carrier together with the seal against the wall of the pressure compensation chamber is axially displaceable. Due to the insertable into the first groove seal the pressure compensation chamber against the wall is sealed leak-proof.

Furthermore, it may prove advantageous to design both the seal carrier and the seal which can be inserted into the first groove in such a way that its sealing capability is independent of the temperature of the oil present in the pressure equalization chamber. Another advantage of the sealing arrangement is that it is possible to dispense with a technically complex scorching of the seal on an actuating piston and the internal guide of the seal carrier is significantly improved in the pressure compensation chamber.

According to a further preferred embodiment of the invention, the seal carrier has a, corresponding to a second effective surface of the actuating piston contact surface and is preferably adapted to be clamped onto a piston neck of the actuating piston. The seal carrier is captively secured in this way to a piston neck of the actuating piston, whereby the internal volume of the pressure compensation chamber 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 chamber and the seal carrier has a second groove which is formed on the side of the seal carrier facing an oil feed hub and in a further seal can be inserted opposite to that connected to the oil supply hub Piston neck provides an additional seal. The first and the second groove are formed so that they hold their respective associated seal captive even with axial movement of the seal carrier with respect to the Ölzuführnabe, yet a leak-proof seal is guaranteed.

In a further advantageous embodiment of the invention it is provided that in the pressure compensation chamber, a restoring element is arranged, which returns the actuating piston in non-actuation or when releasing the clutch in its initial position and that the seal carrier is adapted to engage around the restoring element on its outer circumference radially. The return element may be formed, for example, as a spring assembly. The advantage of this construction is that the coupling device can be made narrower relative to the oil supply hub radially (and preferably also axially), since the seal carrier and the return element are arranged in one another and radially equidistant from the oil supply hub. The seal carrier is preferably designed so that it can follow the axial change in length of the return element while maintaining its sealing ability.

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

In addition, it is provided that the receptacle is formed in the seal carrier as a substantially 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 meant to be exemplary only and in no way exclusive. Instead of a helical spring package, any other technical solution for a restoring element is conceivable, on the outer contour of the recess is adaptable.

According to a further preferred embodiment of the invention it is provided that the receptacle is formed in the seal carrier as a pocket, which receives in each case a coil spring of the coil spring assembly. Depending on the size and scope of the drive unit and the transmission, the coupling device can be reinforced by additional pockets for additional coil spring assemblies are installed.

In addition, it may be provided that the at least one coil spring assembly is supported on the side facing away from the seal carrier on the wall. Both the wall and the seal carrier are designed so that they provide the coil spring assembly in compression and expansion of the coil spring when closing and when releasing the clutch axially each have a sufficient support surface.

According to a further preferred embodiment of the invention, the pressure chamber may be delimited by a first active surface of the actuating piston and a gear-side plate carrier, wherein between the actuating piston and plate carrier a clampable on the plate carrier seal assembly is provided which has a second seal carrier and a seal associated with the second seal carrier , wherein the seal is preferably glued.

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

The embodiments of the invention prove to be advantageous, since the pressure chamber of the coupling device is additionally securable against oil loss and thus against undesired dragging of the coupling device, which substantially increases the service life and ease of operation of the coupling device.

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

In the following, the invention will be explained by way of example, without limitation of generality, with reference to an embodiment shown in the drawings.

Show it:

1 : A schematic sectional view through a first preferred embodiment of a dual clutch device with the seal assembly according to the invention and

2 : an enlarged view of the in 1 shown sealing arrangement according to the invention.

In the following figures, functionally equivalent elements are numbered with the same reference numerals.

1 and in part 2 show a double clutch 1 with an internal coupling arrangement 2 and an outer clutch assembly 3 , The clutch arrangements 2 and 3 are designed as multi-plate clutches, each having an inner disc carrier 5 . 6 and an outer disc carrier 7 . 8th having, on the disc carriers 5 . 6 and 7 . 8th arranged slats 9 . 11 , and 10 . 12 interlock and form each disk packs.

The outer disc carrier 7 is torsionally with a driver 13 the double clutch 1 connected in turn rotatably connected to an output shaft of a drive unit, not shown, so that over the driver 13 During operation, a torque from the drive unit in the double clutch 1 is initiated. Because both the outer disk carrier 7 the outer clutch assembly 2 as well as the outer disc carrier 8th the inner coupling device 3 rotatably with an oil supply hub 4 are connected, the torque on the driver 13 also on the inner clutch assembly 3 initiated.

Transmission side are the inner disk carrier 5 . 6 rotatably by means of, for example, a toothing, each with a transmission input shaft 14 . 15 connected, wherein the inner disk carrier 6 the inner clutch assembly 3 with the first formed as a hollow shaft transmission input shaft 15 connected is. The trained as a hollow shaft transmission input shaft 15 surrounds a second transmission input shaft 14 , in turn, with the inner disk carrier 5 the outer coupling device 2 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 assembly 3 transferred by the appropriate slats 10 . 12 , respectively. 9 . 11 be brought into frictional engagement.

This is done by the outer disk carrier 7 . 8th a drive-side coupling part and by the inner disk carrier 5 . 6 a transmission-side coupling part is formed.

In order to bring the slats in frictional engagement is each clutch assembly 2 . 3 one actuating piston each 16 . 17 assigned, which acts on the disk sets with a force acting in the axial direction force. The actuating piston 16 . 17 are pressure chambers 24 . 25 associated with, for forming the axial force on the actuating piston 16 . 17 be pressurized with pressurized fluid. This pressure fluid is through holes in the oil supply hub 11 fed. Advantageously, the pressurized fluid also serves as a cooling oil for the multi-plate clutch, wherein the cooling oil flow the dual clutch 1 flows in a substantially radial direction from the inside to the outside. Additionally or alternatively, the cooling oil may also be between the oil supply hub 4 and the outer transmission input shaft 15 be supplied.

To the clutch assembly 2 . 3 to solve, are reset elements 20 . 22 provided in the case shown here as a plate spring 20 and coil spring 22 are formed. The of the reset elements 20 . 22 Outgoing force affects that of the pressure chamber 24 respectively. 25 on the actuating piston 16 respectively. 17 counteracting pressure. Will no more fluid the pressure chamber 24 . 25 supplied, so the pressure in the pressure chamber 24 respectively. 25 reduces, causes the pressure of the respective return element 20 . 22 the release of the multi-plate clutch assembly 2 . 3 by an axial displacement of the actuating piston 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 space of the clutch assembly 3 concludes. At his from the neck of the flask 18 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 compensation room 28 arranged by another sealing element 33 is sealed radially outward. The pressure room 24 of the actuating piston 16 is from the outer disk carrier 7 and the actuating piston 16 limited. Radially inside the pressure chamber ends 24 at the oil supply hub 4 , An associated pressure compensation room 27 is radially outward over a seal carrier 42 sealed and from the actuating piston 16 , the oil feed hub 4 and one with the oil supply hub 4 connected, substantially radially extending wall 40 limited.

All or even only one 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 with regard to the sealing elements of the inner multi-plate clutch arrangement becomes exemplary 2 described. It shows 2 for a better understanding an enlarged view of the relevant components.

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

Within the pressure compensation room 27 a seal assembly is shown, which is a first seal carrier 42 and a seal 43 which, in one, in the seal carrier 42 trained first groove 44 is inserted. The seal carrier 42 is in shape and size of the actuating piston 16 modeled. Furthermore, the seal carrier 42 at its radially inner end a recess 47 in 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 room 27 seals. That in the pressure equalization room 27 arranged return element 22 that the actuating piston 16 the multi-plate clutch assembly 2 when not operating the coupling device 1 in a starting position, is in the 1 and 2 designed as a coil spring package. In the sectional view of 1 and 2 However, due to the illustration, only a single coil spring is visible.

As 2 can still be seen, embraces the seal carrier 42 the reset element 22 radially on its outer periphery, so that the return element 22 supported radially outwards. For this purpose, the seal carrier 42 have an annular recess. In addition, the seal carrier 42 Also have individual pockets that each serve to receive a coil spring of a coil spring package. Concerning. the advantages of using a coil spring is to refer to the co-pending application 003719, which is hereby incorporated in full in this application.

For sealing the pressure chamber 24 is a second seal carrier 35 provided the pressure room 24 on the from the oil supply hub 4 side turned away seals. At the end of the second seal carrier 35 that the pressure room 24 is facing, is on the seal carrier 35 in addition a seal 36 attached, which may be glued example. The seals 35 . 36 can on the outer disc carrier 7 be clamped. 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 need to be vulcanized in an additional time-consuming step, but can be postponed time-saving on the seal carrier, 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

Circumferential seal

47

recess

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

• EP 1780435 A2 [0002]

Claims (10)

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 (US Pat. 2 ), a transmission-side plate carrier ( 5 ; 6 ) and a drive-side plate carrier ( 7 ; 8th ), wherein the coupling arrangement ( 2 ) by means of a pressurizable actuating piston ( 16 ) is operable, the piston neck ( 19 ) rotatably with an oil feed hub ( 4 ), and one of a pressurizable pressure chamber ( 24 ) facing first effective area and a pressure equalization space ( 27 ) facing the second effective surface, wherein the pressure compensation space ( 27 ) of the second effective surface of the actuating piston ( 16 ), the oil feed hub ( 4 ) and one with the oil supply hub ( 4 ) are connected in a substantially radially extending wall ( 40 ) is formed and sealed by a seal assembly, characterized in that the seal assembly is a seal carrier ( 42 ) having a first groove formed therein ( 44 ) and one in the first groove ( 44 ) insertable seal ( 43 ) having. Coupling according to claim 1, wherein the seal carrier ( 42 ) one of the second effective surface of the actuating piston ( 16 ) has corresponding contact surface, and is preferably adapted to the piston neck ( 19 ) to be clamped. Coupling according to claim 1 or 2, wherein the first groove ( 44 ) with the first seal inserted therein ( 43 ) a seal with respect to the wall ( 40 ), and preferably the seal carrier ( 42 ), a second groove ( 47 ), which at the oil supply hub ( 4 ) facing side of the seal carrier ( 42 ) is formed and into which a seal ( 46 ) which can be inserted, which has a seal with respect to the oil feed hub ( 4 ) connected piston neck ( 19 ). Coupling according to one of the preceding claims, wherein in the pressure compensation chamber ( 27 ) a reset element ( 22 ) is arranged, which the actuating piston ( 16 ) when not in its initial position ( 48 ), and wherein the seal carrier ( 42 ) is designed to the reset element ( 22 ) to encompass radially on its outer circumference. Coupling according to claim 4, wherein the return element ( 22 ) is designed as a helical spring package, and the seal carrier ( 42 ) Has a coil spring assembly supporting the support. Coupling according to claim 5, wherein the receptacle as a substantially annular recess in the seal carrier ( 42 ) is trained. Clutch according to claim 5, wherein the receptacle is formed as a pocket, each receiving a coil spring of the coil spring assembly. A coupling according to claim 5, 6 or 7, wherein the coil spring assembly is mounted on the seal carrier (10). 42 ) facing away from the wall ( 40 ) is supported. Coupling according to one of the preceding claims, wherein the pressure chamber ( 24 ) of the first effective area of the actuating piston ( 16 ) and the drive-side plate carrier ( 7 ) is limited, wherein between actuating piston ( 16 ) and lamb carrier ( 7 ) one on the plate carrier ( 7 ) is provided with a clampable seal arrangement, which has a second seal carrier ( 35 ) and one with the second seal carrier ( 35 ) connected seal ( 36 ), wherein preferably the seal ( 36 ) is glued. Coupling according to one of the preceding claims, wherein at least one of the seal carrier ( 42 ; 35 ) is made of plastic.

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