DE102017120036A1 - Actuator with multistage spring characteristic and clutch actuator with actuator - Google Patents

Abstract

The invention relates to an actuator (1) for a clutch actuating device of a motor vehicle, having a housing (2), a housing (2) slidably received and the housing (2) a pressure chamber (3) limiting the main piston (4), a Displacement position of the main piston (4) adjusting motor (5) and a displaceable accumulator piston (6) having pressure medium reservoir (7), wherein the pressure medium reservoir (7) is arranged and designed so that in at least one displacement position of the main piston (4) between the Main piston (4) and a slave cylinder port (8) of the housing (2) limited pressure chamber (3) from a master cylinder connection (9) of the housing (2) separated and the pressure medium reservoir (7) with the master cylinder connection (9) is connected, and wherein the Accumulator piston (6) against its a volume of the pressure medium reservoir (7) enlarging extension direction by means of a spring device (10) is supported, wherein e ine spring characteristic (11) of the spring device (10) is formed in several stages. In addition, the invention relates to a clutch actuating device with this actuator (1).

Description

The invention relates to an actuator for a clutch actuation device of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with a housing, a slidably received in the housing and the housing a pressure chamber limiting main piston, a displacement position of the main piston adjusting motor and a a pressure medium reservoir having a displaceable accumulator piston, the pressure medium reservoir being arranged and configured such that in at least one displacement position of the main piston the pressure space bounded between the main piston and a slave cylinder port of the housing is separated from a master cylinder port of the housing and the pressure medium reservoir is connected to the master cylinder port, and wherein the accumulator piston is supported / prestressed by means of a spring device, counter to its extension direction, which enlarges a volume of the pressure medium reservoir. Furthermore, the invention relates to a clutch actuating device for a motor vehicle with this actuator.

Generic prior art is with the DE 10 2016 217 826 B3 disclosed. Herein an actuator of a friction clutch with such an actuator is disclosed.

Furthermore, the applicant is state of the art in the form of DE 10 2016 205 310 B3 known. Herein is disclosed an actuator with a volume constant storage chamber.

Thus, actuators are already known according to the preamble of claim 1, which are used in operation in actuators, in a hydraulic path between a slave cylinder and a master cylinder. In operation, the actuator allows in particular the so-called "sailing function", by means of which the drive motor of the motor vehicle can be switched off by disengaging the clutch during (off) rolling (no gas is given). For this purpose, the actuator is activated during (off) rolling of the motor vehicle and the main piston is displaced in such a way that the actuator acts fluidically / hydraulically on the slave cylinder such that the corresponding clutch is open.

As a disadvantage, however, it has been found in known embodiments that in the activated state of the actuator, i. in the at least one shift position of the main piston, a pedal force characteristic influenced by the pressure medium reservoir may be greatly affected by the usual pedal force characteristic as it occurs in a conventional operation of the clutch (when master cylinder connection is connected to the pressure chamber and thus to the slave cylinder and thus the clutch pedal via hydraulic Distance adjusting to disengaging element, such as disc spring, the clutch acts) differs. This in turn means loss of comfort on the part of the driver on the clutch pedal.

It is therefore an object of the present invention to overcome the known from the prior art disadvantages and in particular to provide an actuator for a hydraulic path between a slave cylinder and a master cylinder available, which affects the operating comfort of a clutch pedal as little as possible.

This is inventively achieved in that a spring characteristic (i.e., a force-displacement characteristic) of the spring device is formed in multiple stages (preferably at least two stages).

Such a multi-stage design makes it possible, even in the activated state of the actuator, to simulate, as far as possible, a realistic pedal force characteristic for disengaging the clutch on the part of the clutch pedal. A difference in the forces acting on the clutch pedal between a normal clutch operation, in which the slave cylinder is operated directly above the master cylinder, and a support operation, in which the activated actuator actuates the slave cylinder, is thus significantly reduced.

Further advantageous embodiments are claimed with the subclaims and explained in more detail below.

It is advantageous if the pressure medium reservoir is continuously / permanently / inseparably connected (i.e., independent of the displacement position of the main piston) to the master cylinder connection.

If the spring device is designed in such a way that the spring characteristic crosses a clutch characteristic, which preferably runs in a wave shape, after its (first) maximum (in a degressive range), the spring characteristic is particularly closely matched to the clutch characteristic.

The spring device expediently has a plurality of, preferably two, spring units arranged in series with one another. As a result, the spring device is particularly inexpensive to produce compared to when the characteristic would be generated by a further plate spring.

In this regard, it is also advantageous if the spring device comprises a first spring unit and a second spring unit, wherein the spring units are designed and matched to one another are that the second spring unit is compressed when the first spring unit is fully compressed, acts on the second spring unit via a mechanical stop or the two spring units reach the same level of force. The first spring unit is thus softer than the second spring unit, so that a defined spring characteristic, which is aligned as close as possible to the clutch characteristic is generated.

If the first spring unit is designed as a multi-part spring assembly, this can be implemented in a particularly space-saving manner in the illustrated embodiment. It is also advantageous if the second spring unit is additionally or alternatively designed as a multi-part spring assembly.

In this connection, it is particularly expedient for the spring assembly to have a plurality of plate-shaped spring segments (preferably in the form of leaf / plate springs) which are preferably supported axially (ie arranged in series) or arranged in parallel. The individual spring segments are preferably coordinated so that they compress at the same time under pressure.

If the first spring unit and / or second spring unit has a pressure spring or a plurality of pressure springs (arranged in series or parallel to one another), wherein the respective compression spring is preferably designed as a helical compression spring, the structure of the spring device is further simplified.

Furthermore, it is advantageous if a piston seal of the accumulator piston is designed such that it forms a (swinging) of the spring device damping (targeted) friction to their relatively movable components out. As a result, the ease of use of the actuator is further improved.

If there is a stop defining a maximum compression position of the first spring unit, the reliability of the actuator is further increased.

In this regard, it is furthermore particularly advantageous if a further stop (preferably housing-fixed end stop or predetermined by the displaced storage piston) is provided for the second spring unit.

Furthermore, it is advantageous if, in the usual way, the main piston has a piston displaceable by means of the motor and a floating piston component which is displaceably received on the piston retainer and relative to the piston retainer.

The pressure chamber is preferably connected to the master cylinder connection and / or the slave cylinder connection as a function of the position of the piston receiver and of the floating piston component. However, the pressure chamber is always / permanently connected to the slave cylinder connection.

Furthermore, the invention relates to a clutch actuation device for a motor vehicle, having the actuator according to the invention according to at least one of the embodiments described above, a slave cylinder connected to the slave cylinder port (fluidic / hydraulic) and a slave cylinder connected to the master cylinder (fluidic / hydraulic) master cylinder.

In other words, according to the invention, therefore, an actuator also referred to as "MT + -arctor" is implemented with a two-stage spring characteristic in order to improve the ride comfort for the driver. A two-stage spring characteristic is produced by providing a first spring (first spring unit) with a first spring ramp and a second spring (second spring unit) which is prestressed and generates a second spring ramp. In addition, the two-stage spring characteristic crosses a clutch characteristic.

The invention will now be explained in more detail with reference to figures.

• 1 eine schematische Detaildarstellung eines erfindungsgemäßen Aktors nach einem bevorzugten Ausführungsbeispiel im Bereich eines Druckmittelreservoirs, wobei ein Speicherkolben sowie eine den Speicherkolben bei seiner Verschiebung in Ausfahrrichtung elastisch abstützende Federeinrichtung veranschaulicht sind,
• 2 ein Diagramm, aus dem eine durch die Federeinrichtung des Druckmittelreservoirs bewirkte Speicherkennlinie sowie eine zum Ausrücken eines Ausrückelementes der Kupplung definierte Kupplungskennlinie veranschaulicht sind,
• 3 ein Diagramm, das alleine die Kupplungskennlinie nach 2 zeigt,
• 4 ein Diagramm, das ausschließlich eine durch die Federeinrichtung bewirkte Federkennlinie zeigt,
• 5 ein Diagramm, das wiederum die Federkennlinie sowie die Kupplungskennlinie mit auftretender Hysterese zeigt,
• 6 eine Prinzipdarstellung, die in ihrem oberen Teil die Federkennlinie, ähnlich zu 4, und in einem unteren Teil drei ähnlich zu 1 umgesetzte jeweils in dem oberen Teil einen der markierten Zustände repräsentierende Detaildarstellungen des Druckmittelreservoirs samt Speicherkolben und Federienrichtung dargestellt sind, und
• 7 eine Längsschnittdarstellung des gesamten Aktors, wie er in den 1 und 6 schematisch abgebildet ist, sodass eine Übersicht über den Aufbau des Aktors gegeben ist.

Show it:

• 1 a schematic detail of an actuator according to the invention according to a preferred embodiment in the region of a pressure medium reservoir, wherein a storage piston and the storage piston in its displacement in the extension direction elastically supporting spring means are illustrated,
• 2 a diagram illustrating a storage characteristic caused by the spring device of the pressure medium reservoir as well as a clutch characteristic curve defined for disengaging a disengagement element of the clutch,
• 3 a diagram that alone the clutch characteristic after 2 shows,
• 4 a diagram which shows only a spring characteristic caused by the spring device,
• 5 a diagram which in turn shows the spring characteristic as well as the clutch characteristic with occurring hysteresis,
• 6 a schematic diagram, in its upper part, the spring characteristic, similar to 4 , and in a lower part three similar to 1 converted in each case in the upper part one of the marked states representing detailed representations of the pressure medium reservoir, including storage piston and Federienrichtung are shown, and
• 7 a longitudinal sectional view of the entire actuator, as in the 1 and 6 is shown schematically, so that an overview of the structure of the actuator is given.

The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals.

In 1 is an inventive actuator 1 partially illustrated. The entire actuator structure corresponds in particular to the structure of the actuator, as it appears from the published patents with the official license plate DE 10 2016 217 826 B3 and DE10 2016 205 310 B3 disclosed and known. The embodiments of the actuator disclosed herein are thus incorporated by reference as being incorporated herein.

As in connection with 1 to recognize is the actor 1 in turn used in a fluidic (here hydraulic) distance between a master cylinder and a slave cylinder of a (fluidic / hydraulic) clutch actuator. The master cylinder can be actuated in the usual way by means of a clutch pedal of a motor vehicle; the slave cylinder acts on a disengagement element in the form of a plate spring, actuating on a clutch, preferably a friction clutch, of the motor vehicle. The housing 2 is with a master cylinder connection 9 in which, in operation, the master cylinder is connected fluidically, in this case hydraulically, and a slave cylinder connection 8th to which the slave cylinder is fluidly / hydraulically connected during operation. The actor 1 is in the hydraulic path in series with the master cylinder and the slave cylinder, namely arranged between these two cylinders.

The actor 1 is also particularly good in its construction 7 recognizable. The actor 1 has a housing 2 in which a main piston 4 is recorded on. The main piston 4 has a piston receiver 26 and a floating piston / floating piston component 27 on. The piston receiver 26 of the main piston 4 is by means of an electric motor 5 / an electric motor (coupled via a spindle drive) axially displaceable in the housing 2 stored. The housing 2 implemented as a fixed component. The floating-piston component 27 is in turn relative to the piston 26 in the longitudinal / axial direction of the piston 26 on the piston actuator 26 slidably mounted.

A pressure room 3 that by the main piston 4 and the case 2 limited / defined, as in 7 is clearly visible during operation over the slave cylinder connection 8th hydraulically connected to the slave cylinder. The master cylinder connection 9 is, however, dependent on the displacement position of the main piston 4 optionally from the pressure room 3 / Slave cylinder connection 8th disconnected or connected to this. The actor 1 is designed so that the master cylinder connection 9 in a first displacement position of the main piston 4 , in actuator actuation position / with activated actuator 1 , from the slave cylinder connection 8th is separated and in a second displacement position of the main piston 4 , in a driver actuation position, with the slave cylinder connection 8th (fluidic / hydraulic) is connected. In the first displacement position thus brings the actor alone 1 / the main piston 4 the necessary pressure for actuating the clutch, whereas in the second displacement position the driver (via the clutch pedal) alone or after oversteer by the floating piston component 27 of the main piston 4 from the actor 1 apply the pressure to actuate the clutch.

To one between the master cylinder and the actuator 1 located fluid / hydraulic fluid in the first displacement position of the main piston 4 is in the actuator without causing loss of comfort on the part of the clutch pedal 1 a variable in its volume pressure medium reservoir 7 (also called memory / storage chamber) exists, which also in 1 and can be seen in detail. The pressure medium reservoir 7 serves to, in the first displacement position of the main piston 4 , ie with disconnected master cylinder connection 9 from the pressure room 3 , for the driver on the part of the clutch pedal as close as possible to the ideal clutch characteristic 12 lying ( 3 ) simulated (pedal) force characteristic (also referred to as storage characteristic curve). For this purpose, the pressure medium reservoir according to the invention 7 with a sliding storage piston 6 provided, wherein the accumulator piston 6 against its extension direction by a spring device 10 is elastically supported. The spring device 10 is inventively designed such that it has a multi-level, here a two-stage, spring characteristic 11 ( 4 ) depicts / achieves. The spring device 10 consists of two spring units 21 . 22 ,

Also, the pressure medium reservoir 7 Always / permanently in operation a hydraulic connection with the master cylinder connection 9 and thus with the master cylinder. The available volume in the pressure medium reservoir 7 is always in operation from the position / position / displacement position of the main piston 4 (and thus in turn of the position of the Kolbennehmers 26 as well as the Floating piston component 27 ) depends on / is through the main piston 4 limited / defined, as in connection with 7 is also comprehensible.

The storage piston 6 is basically relative to the housing 2 and to the main piston 4 slidable in the actuator 1 added. The functioning of the pressure medium reservoir 7 including accumulator piston 6 is in the 6 illustrated. In the upper part of the illustration after 6 is a spring characteristic 11 as done by the spring device 10 is generated. The spring characteristic 11 is illustrated as a force (F) path (x) characteristic. This spring characteristic 11 corresponds to the in 4 also shown spring characteristic 11 , wherein the spring characteristic 11 in 6 has a more realistic shifted starting point ("0"). The background to the location of this starting point is that before the spring device 10 / the spring units 21 . 22 is / are compressed, the accumulator piston 6 First, a certain "free travel" has to start, which inter alia by an initial compressing / deforming a piston seal 23 of the accumulator piston 6 caused. The spring characteristic 11 influenced in the second displacement position of the main piston 4 decisively acting on the clutch pedal (pedal) force characteristic / memory characteristic. The lower part of the illustration after 6 shows the at the marked places ( 0 , a, b) of the diagram converted positions / positions of the accumulator piston 6 ,

At the point "0" of the spring characteristic 11 (lower left partial representation in 6 ) is the storage piston 6 in a retracted position (rest position / initial position), which is why the spring device 10 is maximally relaxed or in the defined preload. A first spring unit 21 the spring device 10 is with a first axial end on a flange of a first connecting pot 24 (Also referred to as the first auxiliary piston), the displacement-proof with the accumulator piston 6 coupled, supported. With a first end remote from the second axial end is the first spring unit 21 on a second connection pot 25 (also referred to as second auxiliary piston) supported. At the second connection pot 25 is at the same time with a first axial end a second spring unit 22 supported. A second axial end of the second spring unit 22 is again supported on the housing. The spring units 21 . 22 are thus connected in series relative to each other and tension the accumulator piston 6 together in the same axial direction, namely against its extension / in its retraction before. In the illustrated retracted position of the accumulator piston 6 takes the pressure medium reservoir 7 a minimal volume of fluid. The spring units 21 . 22 are biased by a certain amount and are due to corresponding housing-fixed rest stops 14a respectively. 14c . 14b (via the connection pots 12 respectively. 13 ) at.

As in connection with the spring characteristic 11 recognizable, is the spring device 10 designed such that along a displacement path of the accumulator piston 6 from the retracted position to its extended position, ie at an inflow of the hydraulic fluid in the pressure medium reservoir 7 and thus with an increase in the volume of the pressure medium reservoir 7 , first the first spring unit 21 compressed / compressed. According to the lower middle partial view in 6 is the one in the spring characteristic 11 marked point "a" then reached when the first spring unit 21 compressed to a certain extent and the first connecting pot 24 on the second connecting pot 25 axially abutting. For this purpose, the first connecting pot forms 24 a stop 20 out in the point "a" in contact with the second connection pot 25 is. The second spring unit 22 In this embodiment, it remains fully extended / uncompressed between the point "0" and the point "a". In principle, however, it is also contemplated in other embodiments, the second spring unit 22 perform differently and at a same level of force as the first spring unit 21 already in the displacement between the points "a" and "0" to compress.

In this embodiment, only when compressed first spring unit 21 (defined by the location of the stop 20 ) the second spring unit 22 (lower right partial representation in 6 ) is compressed according to the displacement range between the point "a" and the point "b". Then the volume of the pressure medium reservoir 7 further enlarged. Finally, the point "b" is reached, in which the spring units 21 and 22 are completely compressed (maximum compression position of the spring device 10 ). The spring units 21 and 22 are then in turn preferably by means of an end stop, which is not shown here for clarity sake, fixed to the housing or by the position of the accumulator piston 6 supported and the accumulator piston 6 has reached his (maximum) extended position.

The first spring unit 21 preferably consists of a spring assembly, such as a plate spring package or a leaf spring package, whereas the second spring unit 22 preferably designed as a compression spring, such as a helical compression spring. However, it is also implemented in other versions, the first spring unit 21 and / or the second spring unit 22 implement with a single or multi-part compression spring / compression spring arrangement. At the first spring unit 21 it is advantageous to provide these with at least two, more preferably with three compression springs. Also the second spring unit 22 is preferred with multiple, such as two or three, compression springs Mistake. The compression springs of the respective spring unit 21 . 22 are then more preferably arranged in series / axially stacked / serial or parallel to each other.

In conjunction with the 2 and 5 it can be seen that by the formation of the spring device 10 the resulting spring characteristic 11 results. The spring characteristic 11 It reproduces the ideal clutch characteristic relatively exactly, so that no significant loss of comfort can be perceived by the driver. The on the clutch pedal in the first displacement position of the main piston 4 applied force characteristic (also referred to as a memory characteristic) corresponds essentially to the course of this spring characteristic 11 In practice, other influencing factors influence the course of the force curve. The spring characteristic 11 cuts an ideal force characteristic (clutch characteristic 12 ) according to their maximum 13 , ie after their first maximum seen from a zero point of the displacement path. In 5 the corresponding characteristics are illustrated with the existing in practice hysteresis.

In addition, it is intended a piston seal 23 of the accumulator piston 6 that the pressure medium reservoir 7 seals to the environment, specifically with a friction to the relatively-displaceable components of the accumulator piston 6 namely the housing 2 or the main piston 4 , to provide. This friction serves to damp vibration of certain pressure fluctuation peaks.

In other words, is thus by the thought of the invention, a two-stage spring characteristic 11 defined, so that the (resulting) storage curve as close as possible to the ideal clutch characteristic 12 located. Due to the crossover (in the point 19 ) of the characteristics 11 . 12 becomes a stability problem due to seal friction on the seal 23 avoided.

Thus results from the spring characteristic 11 also a multi-level memory characteristic. A first spring (first spring unit 21 ) describes a first spring ramp 15 (between point "0" and "a" in 6 ). The first spring ramp 15 allows a progressive load increase up to a knee / break point 16 , The first spring 21 can be designed in the form of a multi-part spring assembly. A bias 17 this first spring 21 assures the advantage that the 0 position of the first spring 21 on the way back (see hysteresis due to seal friction in 5 ). A second spring (second spring unit 22 ) is also biased in their installation and is then further compressed when the first spring ramp 15 has reached its preload level (at break point 16 ). The second spring 22 converted second spring ramp 18 / Spring characteristic is essentially the same level of force as the max. Coupling force, as indicated by the clutch characteristic 12 is predetermined. The second spring 22 may be formed in the form of a compression spring for cost reasons. Thus, the characteristic is 6 rising and crossing the clutch characteristic 12 (at the crossroads 19 . 2 ) in the degressive range of the clutch characteristic 12 , At a handover, the floating piston builds (floating piston component 27 ) and the accumulator piston 6 to a vibration system that can lead to instability due to the spring characteristic. The seal friction (in particular by the seal 23 ) are therefore designed so that these frictions are sufficient to keep the system stable.

Thus, a coupling of single feathers 21 . 22 implemented with (different) spring characteristics, so that the combination of the spring characteristics (in the resulting spring characteristic 11 ) on the clutch pedal (in the form of a force characteristic / storage curve) as the clutch characteristic 12 feels. Under clutch characteristic 12 is in particular the characteristic occurring at the clutch pedal (F (x) or F (V)) with the actuator 1 to understand at rest. The spring characteristic (F (x)) is in the actuator 1 provided. As a memory characteristic is the characteristic occurring at the clutch pedal characteristic (F (x) or F (V)) with at least partially actuated actuator 1 (Actuator not at rest) understood. The memory characteristic curve is dependent on the degree of actuation (position) of the actuator 1 , It is a set of curves. According to the invention, the spring characteristic 11 stages. That is, the spring characteristic 11 consists of sections which are described by different polynomials. Especially with a kink (break point 16 ) and discontinuous derivative. A first section of the spring characteristic 11 describes the free travel (before the point "0"), without a spring 21 . 22 is pressed. In the right picture in 6 is a block situation between the spring 21 and the spring 22 described. Here, a corresponding stop can be provided.

The memory characteristic is in real case in the clutch characteristic 12 after the transfer point of the MT + -activator 1 via ( 2 ). The storage characteristic essentially results from the spring characteristic 11 ( 4 ) by means of hydraulic transmission, friction, over-center spring on the pedal and the pedal transmission.

LIST OF REFERENCE NUMBERS

1

actuator

2

casing

3

pressure chamber

4

main piston

5

engine

6

accumulator piston

7

Pressure fluid reservoir

8th

Slave cylinder connection

9

Master cylinder connection

10

spring means

11

Spring characteristic

12

Clutch characteristic

13

maximum

14a, 14c

first rest stop

14b

second rest stop

15

first spring ramp

16

inflection point

17

bias point

18

second spring ramp

19

intersection

20

attack

21

first spring unit

22

second spring unit

23

piston seal

24

first connection pot

25

second connecting pot

26

piston takers

27

Floating piston component

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 102016217826 B3 [0002, 0027]
• DE 102016205310 B3 [0003, 0027]

Claims (10)

Actuator (1) for a clutch actuating device of a motor vehicle, comprising a housing (2), a main piston (4) displaceably received in the housing (2) and defining a pressure chamber (3) with the housing (2), a displacement position of the main piston ( 4) adjusting motor (5) and a displaceable accumulator piston (6) having pressure medium reservoir (7), wherein the pressure medium reservoir (7) is arranged and designed so that in at least one displacement position of the main piston (4) between the main piston (4) and a slave cylinder connection (8) of the housing (2) delimited pressure chamber (3) separated from a master cylinder connection (9) of the housing (2) and the pressure medium reservoir (7) with the master cylinder connection (9) is connected, and wherein the accumulator piston (6) contrary to its extension of a volume of the pressure medium reservoir (7) extending extension direction by means of a spring device (10), characterized in that a F ederkennlinie (11) of the spring device (10) is formed multi-level. Actuator (1) to Claim 1 , characterized in that the spring device (10) is formed such that the spring characteristic (11) crosses a clutch characteristic (12) to its maximum (13). Actuator (1) according to one of Claims 1 and 2 , characterized in that the spring device (10) has a plurality of spring units (21, 22) arranged in series with one another. Actuator (1) according to one of Claims 1 to 3 characterized in that the spring means (10) comprises a first spring unit (21) and a second spring unit (22), wherein the spring units (21, 22) are designed and matched to one another such that the second spring unit (22) is compressed, when the first spring unit (21) is fully compressed, acts on the second spring unit (22) via a mechanical stop (20) or the two spring units (21, 22) reach the same level of force. Actuator (1) to Claim 4 , characterized in that the first spring unit (21) and / or the second spring unit (22) is designed as a multi-part spring assembly. Actuator (1) to Claim 5 , characterized in that the spring assembly comprises a plurality of mutually supported plate-shaped spring segments. Actuator (1) according to one of Claims 4 to 6 , characterized in that the first spring unit (21) and / or the second spring unit (22) comprises a compression spring or a plurality of compression springs. Actuator (1) to Claim 6 or 7 , characterized in that a piston seal (23) of the accumulator piston (6) is designed such that it forms a swinging of the spring means (10) damping friction to their relatively movable components (2) out. Actuator (1) according to one of Claims 4 to 8th , characterized in that there is a stop (20) defining a maximum compression position of the first spring unit (21). A clutch actuating device for a motor vehicle, having an actuator (1) according to one of Claims 1 to 9 , a slave cylinder connected to the slave cylinder connection (8) and a master cylinder connected to the master cylinder connection (9).

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