DE102013203016A1 - Clutch - Google Patents

Abstract

The invention relates to clutch release bearings, as used, for example, for actuating shifting clutches in motor vehicles. To ensure the compensation of an angular misalignment between, for example, a shift clutch (3) and a gearbox, for release arrangements that have a central release or central axial adjuster (9), the end (12) of the piston (10) of the axial adjuster facing the shift clutch 3 is specified (9) with a first shoulder (13.1) and the flange (8.2) of the standing inner bearing ring (8.2) with a second shoulder (13.2), at least one of the two shoulders (13) in physical contact being rounded or crowned Has contour.

Description

Field of the invention

The invention is concerned with a clutch release bearing, as used for example for the actuation of shift disconnect couplings in motor vehicles. A particular aspect of the invention is directed to the angle compensation between the transmission input shaft and the disconnect clutch or the output shaft of the drive unit.

In the prior art it is known to provide in the drive train between the transmission and drive unit, a shift disconnect clutch, which interrupts the power flow in the drive train. Generally, this is realized in such a way that a frictional engagement between the friction partners of the shift disconnect clutch is canceled by an axial movement of an axial adjuster. IE this is solved so that a clutch release bearing between the gearbox and gearshift clutch is provided, which comprises an inner bearing ring, an outer bearing ring and rolling elements, wherein the outer bearing ring is arranged coaxially to the inner bearing ring and the rolling elements in the annular space between the two bearing rings of the Unroll bearing races provided raceways. Essentially, two types of clutch release bearings are distinguished. Thus, there are release bearings having a fixed inner bearing ring and a peripheral outer bearing ring, and those having a circumferential inner bearing ring and a stationary outer bearing ring. Both versions have in common that the respective rotating bearing ring is in operative connection with a diaphragm spring belonging to the shift disconnect clutch and the axial movement of the respective axial adjuster required for the separation of the clutch and transmitted via the diaphragm spring to the clutch via the respective stationary, thus non-rotating Bearing ring is initiated. Arrangements that have a stationary outer bearing ring, usually with the clutch pedal operatively connected and acting on the outer surface of the outer bearing ring lever systems. Standing inner bearing rings, which find application in so-called dual-clutch transmissions applications are usually hydraulically driven by a central axial adjuster is arranged concentrically to the axis of rotation. Such concepts, to which the present application relates, are known as Concentric Slave Cylinder (CSC) systems or Zentralausrücker. Such central Axialversteller generally have a pressure chamber into which a pressure line opens, and which is closed by a piston. This piston is operatively connected to the stationary inner bearing ring and, when extended, causes axial movement of the clutch release bearing or disconnection of the shift disconnect clutch. Since the drive unit, the shift disconnect clutch and the gearbox are integral components that have all their tolerances fluctuating dimensions, it can not be ruled out that after assembly to a radial offset and an angular offset between the drive unit and the gearbox which usually also the clutch release bearing is attached comes. Radial misalignment is generally addressed by providing self-centering. This will be - like in DE 19912432 shown - the stationary bearing ring provided with a flange which engages radially movable in a groove of another, also stationary component.

An angular misalignment which results in a non-uniform and therefore disadvantageous load life of the release bearing is generally addressed by allowing the release bearing to accommodate the given angular misalignment. In DE 19912432 in which the stationary bearing ring is driven by a Zentralausrücker, this is solved so that the rotating outer bearing ring is provided a segment which is in physical contact with the outer bearing ring and on which also in operative connection with the diaphragm spring of the disconnect clutch flange is trained. In this case, the segment has a complementary contour to the rounded contour of the outer bearing ring, whereby tilting of the segment relative to the outer bearing ring is possible to compensate for an angular offset. In order to exclude a lifting of the segment from the outer bearing ring, the segment is clamped to the outer bearing ring.

The use of this segment inevitably increases the axial extent of the release bearing. In addition, the mobility for compensating the angular offset is limited by the clamping of the outer bearing ring with the segment. Furthermore, special precautions must be taken to exclude a wear-increasing co-rotation of the segment at least when disengaging.

Object of the invention

Therefore, the invention has for its object to provide a clutch release bearing, which is very compact and allows compensation of a large angular offset.

Summary of the invention

This object is achieved with the features specified in claim 1. Advantageous education and Further developments of the invention are the claims 2 to 5 can be removed.

If a first shoulder is provided at the end of the piston which points in the direction of the flange of the inner bearing ring, a second shoulder is provided on the side of the flange of the inner bearing ring pointing in the direction of the axial adjuster, each shoulder has a contact surface, with which the first shoulder is in physical contact with the second shoulder, and at least one of the contact surfaces has a convex contour, the angle compensation is completely displaced into the interior of the clutch release bearing, whereby space is saved. In addition, the danger is prevented by the displacement of the angle compensation to the inner stationary bearing ring that it can come under the effect of rotation of the diaphragm spring when disengaged to co-rotation of the angle compensation element.

Is the flange of the inner bearing ring on the piston of the axial adjuster radially slidably connected by a ring member is provided, which has a groove, in which engages the free edge of the flange, and a spring which is supported on the flange and one of the walls of the groove , Radial compensation and also the angle compensation is realized by only one component, which has advantages in the design of release bearings, as even with variants, the standard components such as bearing rings can remain unchanged.

A further component reduction or simplification is given when the ring element either forms the second shoulder itself or receives it.

The cohesion is improved when the ring member has at its edge facing away from the flange of the inner bearing ring spring tongues, which rest on the side of the first shoulder, which faces away from the flange of the inner bearing ring.

The free mobility of the two, the angle compensation ensuring shoulders is not limited if the free ends of the spring tongues are provided with spherical, projecting in the direction of the axis of rotation abutment surfaces and when the spring tongues come into physical contact exclusively with the contact surfaces with the side of the first shoulder, which faces away from the flange of the inner bearing ring.

Brief description of the figures

Show it:

1 a central axial adjuster in its structural environment;

2 a clutch release bearing in detail;

3 a detail A according to 2 ;

4 a variant of detail A according to 3 ;

5 another variant; and

6 a side view of a ring element according to 2 and 3 ,

Detailed description of the figures

The invention will now be described in more detail with reference to FIGS.

In 1 the periphery is illustrated in more detail in the clutch release bearing 1 be used. This periphery, which corresponds to the installation situation in a motor vehicle, is essentially a hydraulic actuator 2 and a clutch 3 educated. Will the clutch pedal 2.1 Pressed, pressure in the connecting line 2.2 built and to one within the clutch release bearing 1 arranged piston of a centric to the axis of rotation R lying Axververstellers transferred (everything in 1 not shown).

The shift disconnect clutch 3 is essentially made of a printing plate 3.1 , a flywheel 3.2 , a friction disc 03.03 and a diaphragm spring 3.4 educated. Will now by the effect of the pressure built up the outer bearing ring 4 of the clutch release bearing 1 by means of the action of the central axial adjuster in the 1 to the right against the outer bearing ring 4 fitting diaphragm spring 3.4 moves, the pressure plate rises 3.1 from the friction disc 03.03 off and over the flywheel 3.2 on the wave 3.5 transmitted power flow is interrupted (everything in 1 Not shown).

Details of the clutch release bearing 1 are 2 removable. It is clear from the illustration according to 2 removable, that the clutch release bearing 1 from an outer bearing ring 4 , an inner bearing ring 5 and rolling elements 6 is formed, wherein the rolling elements 6 between the races 4 . 5 on of the races 4 . 5 provided careers 7.1 . 7.2 roll.

To provide a sufficient Abstützflache for the diaphragm spring 3.4 on the rotating outer bearing ring 4 is this with a flange 8.1 provided, which extends in the direction of the axis of rotation R.

The inner bearing ring 5 , which frames an annulus RR, has a flange 8.2 on, which also extends in the direction of the axis of rotation R.

The connection of the inner bearing ring 5 to the central axial adjuster 9 is now related to 3 explained in more detail.

The central axial adjuster 9 , which with the supply line 2.2 is connected, is annular and is arranged and fixed concentrically to the axis of rotation R. Integral part of the central axial adjuster 9 is a piston 10 who has a pressure room 11 in which the supply line 2.2 opens, closes. Will now by pressing the clutch pedal 2.1 ( 1 ) Pressure builds up, the piston moves 10 from the pressure room 11 out (indicated in 3 by the arrow P).

The inner bearing ring 4 facing the end 12 of the piston 10 is with a first shoulder 13.1 Mistake.

The flange 8.2 of the inner bearing ring 5 engages in a groove 14 a, which extends from an axially extending ring element 15 provided. To fix the flange 8.2 in the groove 14 is a plate spring 16 provided, which is in the groove 14 supports and the flange 8.2 against one of the walls 17 the groove 14 suppressed. This type of axial fixing causes a radial displacement of the shaft 3.5 ( 1 ) and the flywheel 3.2 ( 1 ) This offset by a radial movement of the flange 8.2 in the groove 14 is compensated.

In addition, the ring element 15 , which is formed of sheet metal, with a second shoulder 13.2 connected, extending from the flange 8.2 in the direction of the axial adjuster 9 extends. This shoulder 13.2 is with a contact surface 18.1 provided, which has a convex or curved contour, wherein the zenith Z of the curvature points in the direction of the axis of rotation R and with the newly formed contact surface 18.2 the first shoulder 13.1 is in physical contact.

For connection of inner bearing ring 5 and axial adjuster 9 are on the edge 19 of the ring element 15 moving in the direction of the central axial adjuster 9 points, spring tongues 20 are provided, which is the first shoulder 8.1 embrace when they are on this - as well as in 3 shown - are snapped. So that the spring tongues 20 an also known as angular displacement relative movement between the two shoulders 8.1 . 8.2 or their contact surfaces 18.1 . 18.2 do not hinder, are the spring tongues 20 at their free ends 21 with projecting in the direction of the rotation axis R, spherical or rounded projections formed 22 provided on the side of the shoulder 13.1 abut the inner bearing ring 5 turned away.

A side view of a ring element 15 corresponding 3 is in 6 illustrated in more detail. This representation is removable, the groove 14 is circumferential and the edge 19 evenly with spring tongues 20 understand is.

The variant according to 4 differs from the design according to 3 in that there is no ring element 15 between the flange 8.2 and the second shoulder 13.2 is provided and instead the shoulder 13.2 directly on the flange 8.2 is trained. Only for the sake of completeness, it should be stated that to reduce the number of components, the shoulder 13.2 and the flange 8.2 can also form an integral unit. The connection between the flange 8.2 and the shoulder 13.1 is also made from a simply shaped ring element 15 formed, which on the shoulder 13.2 postponed and fixed in this position. The spring tongues 20 are substantially straight, although the angle at which the straight spring tongues 20 on the contact surface 18.3 the shoulder 13.1 from which angle is different, under which also just contact surface 18.3 runs.

The execution according to 5 differs from the design according to 3 merely by helping to improve the mobility of the shoulders 13.1 . 13.2 also the contact area 18.2 the shoulder 13.1 with which this with the shoulder 13.2 is in physical contact, has a crowned or rounded profile.

Shall be the mobility of the shoulders 13.1 . 13.2 can be further improved, in another - not shown - embodiment, one or both contact surfaces 18.1 . 18.2 be coated with a sliding coating, for example made of Teflon.

LIST OF REFERENCE NUMBERS

1

 Clutch

2

actuator

2.1

 clutch pedal

2.2

 interconnectors

3

 Disconnectable clutch

3.1

 printing plate

3.2

 flywheel

3.3

 friction

3.4

 diaphragm spring

3.5

 wave

4

 outer bearing ring

5

 inner bearing ring

6

rolling elements

7.1, 7.2

 raceways

8.1, 8.2

 flange

9

axiers

10

 piston

11

 pressure chamber

12

The End

13.1, 13.2

shoulder

14

groove

15

 ring element

16

 Belleville spring

17

 wall

18.1,18.2

 contact area

19

 edge

20

spring tongues

21

 free ends

22

 projections

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 19912432 [0002, 0003]

Claims (5)

Clutch release bearing with an outer, rotating bearing ring ( 4 ), who has a career ( 7.1 ) and a flange ( 8.1 ), with an inner, stationary bearing ring ( 5 ), who has a career ( 7.2 ) and a flange ( 8.2 ), with a plurality of rolling elements ( 6 ), which depends on the bearing rings ( 7.1 . 7.2 ) provided careers ( 8.1 . 8.2 ), and with a central axial adjuster ( 9 ) located within one of the inner bearing ring ( 5 rimmed annular space RR is arranged and the via a piston ( 10 ) with the flange ( 8.2 ) of the inner bearing ring ( 5 ) is in operative connection, characterized in that at the end ( 12 ) of the piston ( 10 ), which in the direction of the flange ( 8.2 ) of the inner bearing ring ( 5 ), a first shoulder ( 13.1 ) is provided that on the side of the flange ( 8.2 ) of the inner bearing ring ( 5 ), which in the direction of the axial adjuster ( 9 ), a second shoulder ( 13.2 ) is provided that each shoulder ( 13.1 . 13.2 ) a contact surface ( 18.1 . 18.2 ), with which the first shoulder ( 13.1 ) with the second shoulder ( 13.2 ) is in physical contact, and that at least one of the contact surfaces ( 18.1 . 18.2 ) has a convex contour. Clutch release bearing according to claim 1, characterized in that the flange ( 8.2 ) of the inner bearing ring ( 5 ) on the piston ( 10 ) of the central axial adjuster ( 9 ) is radially slidably connected by a ring element ( 15 ) is provided, which a groove ( 14 ), in which the free edge of the flange ( 8.2 ) engages, and by a plate spring ( 16 ) located on the flange ( 8.2 ) and one of the walls ( 17 ) of the groove ( 14 ) is supported. Clutch release bearing according to claim 2, characterized in that the ring element ( 15 ) either the second shoulder ( 13.2 ) or absorbs them. Clutch release bearing according to claim 3, characterized in that the ring element ( 15 ) at its the flange ( 8.2 ) of the inner bearing ring ( 5 ) facing away from the edge ( 20 ) Spring tongues ( 20 ), which on the side of the first shoulder ( 13.1 ), which the flange ( 8.2 ) of the inner bearing ring ( 5 ) are turned away Clutch release bearing according to claim 4, characterized in that the free ends ( 21 ) of the spring tongues ( 20 ) with crowned, in the direction of the axis of rotation R projecting contact surfaces ( 22 ) and that the spring tongues ( 20 ) exclusively with the contact surfaces ( 22 ) with the side of the first shoulder ( 13.1 ) come into physical contact with the flange ( 8.2 ) of the inner bearing ring ( 5 ) is turned away.

Images