DE102008060585B4 - Arrangement for actuating a clutch - Google Patents

Abstract

Arrangement for actuating a clutch (10), in particular a friction clutch in a drive train of a motor vehicle, having a hydraulic release device comprising a slave cylinder (4) with a torque support (21) engaging in a bearing (22) fixed to the housing, the torque support (21) in the tangential direction about a longitudinal axis (23) of the actuated clutch (10) against rotation about the longitudinal axis (23), wherein the bearing (22) comprises a spring-damper element, in which the torque support (21 ), wherein the spring-damper element has a receptacle for a hydraulic line (28) and the receptacle is formed in an elastomer (25), characterized by a clamp (29), which the elastomer (25) in the region of the receptacle clamped so that the hydraulic line (28) is receivable secured in the receptacle and wherein the clip (29) on the torque support (21) is fixed.

Description

The present invention relates to an arrangement for actuating a clutch, in particular a friction clutch in a drive train of a motor vehicle, comprising a hydraulic release device comprising a slave cylinder with a torque support which engages in a housing fixed bearing, the torque support in the tangential direction about a longitudinal axis of the to be actuated clutch bearing against rotation about the longitudinal axis, wherein the bearing has a spring-damper element in which the torque support is mounted.

From the DE 101 38 722 A1 is a clutch-proof release for a friction clutch in a motor vehicle known. The clutch-proof releaser has a central slave cylinder (CSC) which is designed to be clutch-proof. This means that the supporting forces of the slave cylinder are absorbed by the clutch housing, for example by the clutch cover. However, in this support usually the releaser or the slave cylinder is mounted so that it can still rotate about the clutch axis. To limit this possibility of movement, it is known to support the slave cylinder fixed to the housing in the circumferential direction. In this case, the nozzle for connection to the pressure line can be used as a torque support for the slave cylinder. However, such a torque support has been found to be disadvantageous because the inclusion of the nozzle in a housing-fixed bearing over the lifetime of the clutch had an increasing game.

Another problem is that the pressure line, i. the hydraulic line is exposed to operate the releaser, displacements and vibrations. This is particularly disadvantageous in that the hydraulic line or pressure line can be performed within the clutch or within the clutch housing over a longer distance without support. This can lead to damage to the hydraulic line.

An object of the invention is to improve known from the prior art arrangements for the actuation of clutches, in particular, a reliable and durable torque support of the releaser or a reliable and durable storage of hydraulic power should be ensured.

The object is achieved by an arrangement for actuating a clutch, in particular a friction clutch in a drive train of a motor vehicle, with a hydraulic release comprising a slave cylinder with a torque support which engages in a housing fixed bearing, the torque support in the tangential direction about a longitudinal axis the clutch to be actuated bears against rotation about the longitudinal axis, wherein the bearing has a spring-damper element, in which the torque support is mounted, characterized in that the spring-damper element has a receptacle for a hydraulic line. The clutch is preferably part of a drive train, in particular for a motor vehicle, with a rotationally connected to the drive unit coupling, which means that a clutch housing of the clutch is rotationally connected to a drive unit of the motor vehicle. The drive unit may be an electric machine or an internal combustion engine. The release is preferably a Zentralausrücker. This is on the DE 101 38 722 A1 directed. A cover-resistant release mechanism offers the advantage that forces on the crankshaft and in particular forces on axial bearings of the crankshaft are avoided. In connection with the invention, a cover-resistant release mechanism has the advantage that the forces arising during operation of the release mechanism can largely be absorbed within the coupling. The longitudinal axis of the coupling is preferably a longitudinal axis of a drive or an output shaft of the clutch. The storage takes place in the circumferential direction to the longitudinal axis, ie tangentially, wherein the torque support is preferably mounted exclusively by the spring-damper element. The receptacle for the hydraulic line in the spring-damper element has the advantage that the hydraulic line can be stored elastic and damped, so that a storage can be ensured, which makes damage to the hydraulic line unlikely. The spring-damper element has the advantage that a permanent storage of the torque support is ensured and at the same time power peaks are mitigated, so that there is no or only a very small wear in the torque support.

In addition, the spring-damper element comprises an elastomer, wherein the receptacle is formed in the elastomer. An elastomer offers the advantage of an elastic and at the same time damping storage, so that a largely wear-free storage is possible. This affects both the hydraulic line and the torque support. Due to the damping properties of the elastomer resonant vibrations can be avoided. Preferably, the torque support in the bearing is stored exclusively in one or more elastomers. This means that there are no other direct connections between a fixed bearing mounting of the bearing and the torque support, except by the elastomer. Preferred elastomers are PEEK ( Polyetheretherketone) or POM (polyoxymethylene), although many other elastomers can be used.

The arrangement for actuating a clutch further comprises a clamp, which clamps the elastomer in the region of the receptacle, so that the hydraulic line is secured in the receptacle can be received. It is possible, for example, to compress the two above-mentioned hooks by the clamp or to fix them by the clamp so that they can not move apart so that a release of the hydraulic line can be ruled out. Advantageous embodiments of the invention have on the outside of the hook-shaped formations bevels, which a placement of the clip "from above", i. from the insertion side, through which the hydraulic line is inserted into the hook, allows. The clip then forces this bevels, so that a sliding apart of the hook and a release of the hydraulic line are not possible.

The clamp is attached to the torque support, wherein the attachment is carried out advantageously detachable. In this case, the receptacle on the elastomer is preferably arranged in the vicinity of the point at which the torque support engages in the elastomer in order to ensure the smallest possible relative movements between the clip and the receptacle. The torque support may also be referred to as a housing attachment, since it is arranged on a housing of the central release. The clip is preferably secured to the torque support with a screw or bolt. This offers the advantage of easy mounting of the hydraulic line in the receptacle or a slight replacement of the hydraulic line.

Advantageously, the receptacle has a geometry which allows snapping the hydraulic line in the receptacle. Thus, taking advantage of the elastic properties of an elastomer a simple recording can be created, which allows at least a provisional fixation of the hydraulic line. Depending on the design of a snap-in device for the hydraulic line, the fixation of the hydraulic line in the snap-in receptacle can also be designed such that a permanent fixation of the hydraulic line in the receptacle is provided. A suitable snap-in device may comprise, for example, two hook-shaped formations which engage or enclose the hydraulic line on both sides when the hydraulic line is inserted. In this case, it should be understood that the two hooks do not have to completely cover the hydraulic line, but at the top, i. at the insertion side of the recording, can leave a gap.

Preferably, the bearing has a housing-fixed holding part on which the spring-damper element is mounted. The housing-fixed holding part is preferably a sheet metal part, which is adapted to support the spring-damper element or the elastomer. The holding part preferably has two plate-shaped or nose-shaped formations, between which or on which the elastomer is arranged. The plates or noses can engage in the elastomer or absorb the elastomer between them. In this case, the plates are arranged so that they are circumferentially spaced and receive in the circumferential direction between them at least a majority of the elastomer. The holding part can also be fastened outside the clutch bell.

Preferably, the holding part is designed so that it exits from a clutch bell of the clutch in an assembled state in which the assembly is mounted in the clutch. This offers the advantage that the holding part or the retaining plate can be easily mounted because the fixing points are outside the clutch bell. Preferably, the holding part for this purpose has two holding arms, which emerge from the clutch bell. Advantageously, a fixing of the holding part is made with screws on a housing of the coupling. The protruding from the clutch bell retaining arms offer the advantage that the fixation of the holding part does not have to be "blind" within the clutch. Such a formed holding part forms an independent object of the invention, which can be used in conjunction with an elastomer for supporting the torque support, wherein the elastomer may or may not have a receptacle for a hydraulic line.

Advantageously, the torque support is supported by the elastomer such that forces applied to the bearing by the torque support in the circumferential direction substantially produce a normal force load on the elastomer. In this case, "in the circumferential direction" in the circumferential direction with respect to the axis of the clutch, ie an axis of a drive or output shaft of the clutch. The forces applied circumferentially to the bearing are the typical forces of the torque support, ie those forces resulting from a rotation of the slave cylinder about the axis. Normal forces are compressive or tensile forces, which essentially means that in the case of an elastomer having a spatial extent, for example an elastomer having a cuboid-like shape, it can not be ruled out that, depending on the absorption of the elastomer in the bearing, low thrust forces in addition to the normal forces can arise. It is preferred that predominantly normal forces arise if forces of the Torque support in the circumferential direction are absorbed by the bearing.

Preferably, the torque support is supported by the elastomer such that forces applied to the bearing by the torque support in the axial or radial direction substantially produce a thrust load on the elastomer. Again, in the axial or radial direction, it is meant that forces are applied to the bearing or the elastomer with respect to the coupling axially or radially by the torque support. "Essentially" again means that in reality no pure shear loading of the elastomer is to be expected. This depends on the force input of the bearing forces in the elastomer or in the elastomers. Said feature is advantageously combined with the feature that the forces applied circumferentially to the bearing substantially produce a normal force load on the elastomer. For this purpose, an elastomer block or a plurality of elastomer blocks is preferably arranged so that they are arranged between two force introduction points in the tangential direction, that is, that the force introduction points are tangentially spaced with respect to the axis of the coupling. The force introduction points are preferably fixed to the housing and may be the plates of the holding part. It is possible to provide only an elastomer in which the torque support is enclosed.

Advantageously, the elastomer has recesses arranged in the elastomer so as to reduce the flexural rigidity of the elastomer in at least one direction. In this way, thrust transmissions in the elastomer should be avoided. The thrust forces result preferably mainly from radial or axial displacements of the torque support. Such shifts should be possible in the camp largely without compulsion. For this purpose, the elastomer may have cuts or cuts, which reduce bending stiffness in the appropriate direction. The cuts can be designed as grooves or as recesses. The cuts are preferably made so as to reduce as little as possible the stiffness of the elastomer for receiving the bearing forces of the torque supports in the circumferential direction, while reducing the stiffness of the elastomer for absorbing axial or radial forces.

Advantageously, the elastomer has recesses which are suitable for receiving the torque support or the holding part in the elastomer. The torque support is preferably received in the tangential direction substantially centrally in the elastomer and the plates or tabs of the holding part outside, so that the plates or lugs of the holding part receive the elastomer like a clamp, the plates or noses can also engage in the elastomer , This offers the advantage of an elastic and damped mounting of the torque support.

Preferably, the torque support is permanently connected to the spring-damper element. It is particularly preferred if the torque support is vulcanized into the elastomer. This offers the advantage of a particularly simple and durable construction.

• 1 eine schematische Darstellung eines Beispiels für ein hydraulisches Kraftübertragungssystem, bei dem eine Anordnung zur Betätigung einer Kupplung eingesetzt werden kann;
• 2 schematisch eine Anordnung zur Betätigung einer Kupplung;
• 3 eine Skizze, die eine Einzelheit der 2 genauer zeigt;
• 4 schematisch eine Einzelheit der 2 in vergrößerter Darstellung;
• 5 schematisch eine Einzelheit der Anordnung der 2 vergrößert;
• 6 den Elastomer der 2 schematisch in einer vergrößerten Ansicht;
• 7 den Elastomer der 2 schematisch aus einer anderen Blickrichtung als in der 6;
• 8 schematisch das Halteteil der Anordnung der 2; und
• 9 die Klammer der Anordnung der 2 in einer schematischen Ansicht.

In the following, embodiments of the invention will be explained with reference to the accompanying drawings. Showing:

• 1 a schematic representation of an example of a hydraulic power transmission system, in which an arrangement for actuating a clutch can be used;
• 2 schematically an arrangement for actuating a clutch;
• 3 a sketch that is a detail of 2 shows more exactly;
• 4 schematically a detail of 2 in an enlarged view;
• 5 schematically a detail of the arrangement of 2 increased;
• 6 the elastomer of 2 schematically in an enlarged view;
• 7 the elastomer of 2 schematically from a different perspective than in the 6 ;
• 8th schematically the holding part of the arrangement of 2 ; and
• 9 the bracket of the arrangement of 2 in a schematic view.

In the 1 an example of a hydraulic power transmission system is shown in which an arrangement is used to actuate a clutch. It can be used both a hydraulic system, as well as an electrical or mechanical. The hydraulic power transmission system is a hydraulic clutch actuator 1 for a motor vehicle. The clutch operation 1 includes a master cylinder 2 by a hydraulic pressure line 3 with a slave cylinder 4 is in fluid communication. The slave cylinder 4 is designed as a central annular slave cylinder (CSC). In an annular slave cylinder housing 5 is an annular slave cylinder piston 6 stored. The annular slave cylinder 4 and the annular slave cylinder piston 6 close a turn annular pressure chamber 7 one. The slave cylinder 4 is about a release bearing 8th stored and operated a disc spring 9 , The plate spring 9 is used to actuate a clutch 10th

This clutch 10 includes among other parts the diaphragm spring 9 , a printing plate 11 , a counter pressure plate 12 and a clutch disc 13 , The plate spring 9 is biased so that these in biasing the pressure plate 11 on the counter pressure plate 12 presses while the non-rotatably connected to a transmission input shaft clutch disc 13 between the pressure plate 11 and the counterpressure plate 12 clamps. For this purpose, the pressure plate 11 and the counter-pressure plate 12 rotatably connected to a crankshaft of an internal combustion engine, not shown here as drive unit of a motor vehicle. When pressurizing the slave cylinder 4 is therefore the diaphragm spring 9 moved so that they counter to their biasing direction, the contact pressure of the printing plate 11 in the direction of the pressure plate 12 reduces and thus a frictional connection between the clutch disc 13 on the one hand and the pressure plate 11 and the counterpressure plate 12 on the other hand solves

The master cylinder 2 of the 1 includes a master cylinder piston 14 that by means of a clutch pedal 15 over a push rod 16 is pressed. A master cylinder housing 17 of the master cylinder 2 and the master cylinder piston arranged movably therein 14 close a pressure chamber 18 one. In pressureless systems is with the pressure chamber 18 a back-up tank 19 hydraulically connected. An advantageous for certain embodiments in the pressure line 3 arranged hydraulic valve 20 serves to quick return movements of the clutch pedal 15 in their effect on the hydraulic clutch actuation 1 to limit. As a result, high Einkuppelgeschwindigkeiten when operating the clutch 10 avoided.

The hydraulic clutch operation 1 with the clutch 10 further includes a torque support 21 which are in a warehouse 22 intervenes. Like all other parts of the hydraulic clutch control 1 also are the torque support 21 and the camp 22 shown here only very schematically. The warehouse 22 serves to torque support 21 in a tangential direction about a longitudinal axis 23 the clutch 10 to store. The arrangement for actuating the clutch 10 includes, among other things, the slave cylinder and the torque support 21 with the warehouse 22 ,

In the 2 an arrangement is shown, wherein a part of the slave cylinder 4 of the 1 is shown. Generally be in the 2 the same reference numerals as used in Fig. 1 for the same or similar parts.

At the slave cylinder 4 is a torque support 21 arranged. This torque support 21 is in a warehouse 22 stored, the basis of the 2 is described. The warehouse 22 includes an elastomer 25 into which the torque support 21 engages, and a housing-fixed sheet metal part 26 , The elastomer 25 is through the housing-fixed sheet metal part 26 held. The housing-fixed sheet metal part 26 is designed so that it has two arms 27 having, which are designed such that it consists of a clutch bell of the coupling 1 emerge, leaving a fixation of the two arms 27 is possible on a housing of the coupling. The fixation to the housing is made by a screw on each of the arms 27 of the sheet metal part 26 , Furthermore, in the 2 a hydraulic line 28 shown which the hydraulic valve 20 of the 1 with the slave cylinder 4 combines. The hydraulic line 28 is in the elastomer 25 recorded in a recording, which is based on the 4 and 5 will be explained in more detail. For fixing the hydraulic line 28 in the inclusion of the elastomer 25 is at the torque support 21 a clamp 29 attached, which is an emergence of the hydraulic line 28 prevented from the recording. The clip 29 Can with a screw or a bolt on the torque support 21 be attached.

In the 3 are some parts that are in the 2 are shown enlarged, again like reference numerals designate like or similar parts. To explain the 3 is essentially on the 2 directed. In addition, in the 3 still the edge 30 a coupling housing to see where the sheet metal part 26 with the arm 27 is attached.

In the 4 are in turn parts of 2 shown enlarged. In particular, in the 4 a connection 35 the hydraulic line 28 on the slave cylinder 4 shown. In relation to the others in the 4 Parts shown will refer to the description of 2 and 3 referenced, again like reference numerals designate like parts.

In the 5 is the storage of the torque support 21 in the elastomer 25 shown in more detail. Again, like reference numerals designate like parts as in FIGS 1 to 4 and the corresponding descriptions. The clip 29 and the hydraulic line 28 are opposite the 4 omitted for clarity.

The torque support 21 engages in the elastomer 25 one. Near the point of application of the torque support 21 in the elastomer 25 has the elastomer 25 a receptacle for the hydraulic line 28 (in the 5 not shown). The recording includes two clip arms 37 which the hydraulic line 28 enclose on both sides. By bending the clamp arms apart 37 can the hydraulic line 28 be recorded in the recording. The advantage of this storage of the hydraulic line 28 is that due to the flexibility and the damping properties of the elastomer 25 a wear-free or at least low-wear storage of the hydraulic line 28 is guaranteed in the recording. This also relieves one in the 4 shown connection 35 the hydraulic line 28 on the slave cylinder 4 ,

The 6 shows the elastomer 25 of the 2 to 5 in an enlarged, perspective view. Again, the staple arms 37 the receptacle for the hydraulic line 28 to recognize. Furthermore, in the 6 Cuts in the elastomer 25 shown. The incisions are as horizontal grooves 38 executed. The cuts cause the bending stiffness of the elastomer 25 decreases. It should be noted that the torque support 21 a fixation of the rotational degree of freedom of the slave cylinder 4 around the longitudinal axis 23 to reach the clutch. This means that the roughly cuboidal elastomer 25 which is an elongated extension in the tangential direction with respect to the longitudinal axis 23 has the coupling, in the tangential direction as possible sprung and damped fixation of the torque support 21 should ensure. In contrast, radial and axial displacements of the torque support 21 remain largely free of constraints. This is achieved by using the elastomer 25 is provided with an elongated extension in the tangential direction, wherein the torque support 21 in the middle between the two tangentially spaced ends of the elastomer 25 in the elastomer 25 is included. The elastomer 25 has in the tangential direction of its elongated extent, which is at least twice as large as its width and height in the radial and in the axial direction, so that in the radial direction and in the axial direction a bending load of the elastomer 25 occurs if an axial or radial movement of the torque support 21 is present. Through the cuts, ie the horizontal grooves 38 , that is achieved that the rigidity of the bearing 22 with the elastomer 25 is substantially larger in the tangential direction than in the axial or in the radial direction.

Furthermore, in the 6 two slots 40 shown, which are intended to have two plate-shaped formations 45 of the sheet metal part 26 take. This will make the elastomer 25 on the sheet metal part 26 supported. The formations 45 are designed like noses with rounded corners to push the elastomer 25 on the formations 45 to facilitate. Preferably, the formations 45 and the slots 40 designed so that the elastomer 25 accurately fitting and with a slight press fit on the formations 45 can be arranged.

The 7 shows the elastomer 25 in a perspective view, the view of the 7 the elastomer 25 from a different side than the view shows 6 , Again, like reference numerals designate like parts as in FIGS 1 to 6 , Furthermore, in the view of 7 a receiving opening 41 for the torque support 21 to see. The receiving opening 41 is in the middle of the elastomer 25 arranged. The clamp arms 37 the receptacle for the hydraulic line 28 are next to the reception opening 41 arranged a relative displacement between the recording with the clip arms 37 on the one hand and the receiving opening 41 On the other hand, to keep as low as possible. This serves to loads the hydraulic line 28 (in 7 not shown).

In the 7 can also be seen that the staple arms 37 the receptacle for the hydraulic line 28 outside two sloping surfaces 43 or bevels 43 exhibit. Through the sloping surfaces 43 it is possible when putting on the clip 29 on the clamp arms 37 the staple arms 37 compress. The clip 29 is shaped accordingly and will be described in more detail in connection with FIG. 9.

In the 8th is the sheet metal part 26 of the 2 shown alone. Again, the two arms 27 to see with which an attachment of the sheet metal part 26 outside a clutch bell is possible. Furthermore, the sheet metal part 26 shaped so that it can be used within a coupling housing. For holding the elastomer 25 (in 8th not shown), the sheet metal part 26 two plate-shaped formations 45 or noses 45 on which in the slots 40 of the elastomer 25 intervention.

In the 9 is schematically the bracket 29 shown in perspective in an enlarged view. The clip 29 comes with a bolt or a screw that passes through a through hole 47 the bracket 29 is guided, at the torque support 21 attached. Furthermore, it can be seen that the bracket 29 has a clamp arm, which is attached to the sloping surfaces 43 the staple arms 37 ( 7 ) is adjusted so that the staple arms 37 when putting on the clip 29 be compressed so that the hydraulic line 28 (please refer 2 ) in the inclusion of the elastomer 25 is fixed.

LIST OF REFERENCE NUMBERS

1

clutch Control

2

Master cylinder

3

pressure line

4

slave cylinder

5

Slave cylinder housing

6

Slave cylinder piston

7

pressure chamber

8th

release bearing

9

Belleville spring

10

clutch

11

printing plate

12

Platen

13

clutch disc

14

Master cylinder piston

15

clutch pedal

16

pushrod

17

Master cylinder housing

18

pressure chamber

19

An expansion reservoir

20

Hydraulic valve

21

torque support

22

camp

23

longitudinal axis

25

elastomer

26

sheet metal part

27

poor

28

hydraulic line

29

clip

30

edge

35

connection

37

clip arms

38

Horizontal grooves

40

insertion openings

41

receiving opening

43

Sloping surfaces

45

Plate-shaped formations

47

Through opening

Claims (9)

Arrangement for actuating a clutch (10), in particular a friction clutch in a drive train of a motor vehicle, having a hydraulic release device comprising a slave cylinder (4) with a torque support (21) engaging in a bearing (22) fixed to the housing, the torque support (21) in the tangential direction about a longitudinal axis (23) of the actuated clutch (10) against rotation about the longitudinal axis (23), wherein the bearing (22) comprises a spring-damper element, in which the torque support (21 ), wherein the spring-damper element has a receptacle for a hydraulic line (28) and the receptacle is formed in an elastomer (25), characterized by a clamp (29), which the elastomer (25) in the region of the receptacle clamped so that the hydraulic line (28) is receivable secured in the receptacle and wherein the clip (29) is fixed to the torque support (21). Arrangement according to Claim 1 , characterized in that the receptacle has a geometry which allows snapping the hydraulic line (28) in the receptacle. Arrangement according to one of the preceding claims, characterized in that the bearing (22) has a housing-fixed holding part (26) in which the spring-damper element is mounted. Arrangement according to Claim 3 characterized in that the holding member (26) is adapted to exit from a clutch bell of the clutch (10) in an assembled condition where the assembly is mounted. Arrangement according to one of Claims 1 to 4 characterized in that the torque support (21) is journaled with the elastomer (25) such that forces applied by the torque support (21) circumferentially to the bearing (22) produce substantially a normal force load on the elastomer (25). Arrangement according to one of Claims 1 to 5 , characterized in that the torque support (21) is mounted with the elastomer (25) that by the torque support (21) in the radial or axial direction on the bearing (22) applied forces substantially a thrust load and / or bending load of the elastomer (25). Arrangement according to one of Claims 1 to 6 , characterized in that the elastomer (25) has cuts which are thus in the elastomer are arranged so that the bending stiffness of the elastomer (25) is reduced in at least one direction. Arrangement according to one of Claims 3 to 7 , characterized in that the elastomer (25) has recesses which are suitable for receiving the torque support (21) and / or the holding part (26) in the elastomer (25). Arrangement according to Claim 3 . 4 or 8th , characterized in that the holding part (26) is fastened outside the clutch bell.

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