DE102015110186A1 - Actuator for a clutch, in particular a motor vehicle - Google Patents

Abstract

The present invention relates to an actuator (10) for a clutch, in particular for a motor vehicle, comprising at least one output member (14) of the actuator to act on control means of the clutch (E), said output member (14) movable between at least a first axial rest position (P1) and a loaded second axial working position (P2), which varies depending on the wear of the clutch (E) with respect to a stationary reference (12), a controlled motor (18) to drive means (20) cooperating with at least one actuator (22) acting on said output member (14), support means (36) comprising at least one support spring (38) exerting an assisting force on a support member (40) movable between an end rest position defined by first stop means (42) and an end support ngsposition, which is defined by second stop means (44) and to which the supporting force claimed said support member (40) is mounted, wherein the support member (40) in movement with the actuating member (22) by means of complementary connecting means (62, 64 ) permitting adjustment of the relative position of the support member (40) with respect to the actuator (22) in one direction only to reduce wear in response to the second axial operating position (P2) of the output member (14) under load to compensate for the clutch (E).

Description

The present invention relates to the field of actuators, in particular a clutch actuator of a motor vehicle.

More particularly, the present invention relates to an actuator for adjusting stroke or wear for a motor vehicle clutch which acts directly or not directly on control means associated with the clutch, such as at least one clutch release bearing.

When the actuator has assisting means, also called "force-balancing", the actuator generally comprises a support spring acting on a cam or ramp connected to the output member of the actuator to move the output member into, for example, the actuator to load the direction corresponding to the opening of the clutch when the clutch is of the "normally closed" type.

The assist spring approximately equalizes the resisting force provided by a return spring of the clutch, generally a diaphragm spring, so that the force to be delivered by the motor for actuating the clutch is then reduced to a minimum value.

It is to be remembered that a clutch in which the position of the diaphragm spring by default corresponds to an engaged state is generally called "normally closed", while a clutch in which the rest position of the diaphragm spring is normally in a disengaged state "normally open , This latter "normally open" type of clutch being used in particular in a vehicle incorporating an automated manual transmission.

In a clutch, the wear of the friction linings by a displacement of the control means, such as the clutch release bearing, and therefore the output member of the actuator, by a change in the axial stroke of this output member and a more or less strong change in the operating force, of the Actuator is to provide to effect a change in state of the clutch.

According to the prior art, numerous lifting or wear adjusting systems are known, which are generally integrated in the coupling in order to compensate for the wear of the friction linings in the course of its occurrence such that the wear does not affect the position of the control means and the axial stroke of the output member of the actuator more influenced.

However, such known devices are relatively complex, and their operation often proves to be quite inaccurate and hardly reliable in use.

Another solution is to adjust the axial position of the output member of the actuator depending on the wear of the clutch and in particular the friction linings, the adjustment is achieved in particular by means of variable length, which, integrated in the actuator, the displacement the control means, such as the clutch release bearing, which is due to the wear of the clutch compensate.

In such a solution, the ability to adapt the power assist means to the manufacturing tolerances and wear of the clutch remains a delicate issue, because the moment that the actuator motor encounters depends on the good relative setting of the assist and clutch characteristics which determines, in particular, the performance of the actuator and the design and life of its components.

The document WO-2007/138216 describes a stroke adjustment actuator, particularly for a motor vehicle clutch, which includes a motor that translates a movable member that acts on an output member of the actuator, such as a shaft, to effect the opening and closing of the clutch.

Advantageously, such an actuator is applicable to the control of a normally-closed type clutch as well as a normally-open type clutch.

The movable part consists of a screw-nut system that allows adjusting the length in both directions to compensate for the tolerances and in particular the wear of the clutch, substantially the wear of the friction linings.

In the kinematic chain of the actuator, the screw-nut system is inserted just upstream of the output member, and the adjustment of the length depending on the wear occurs in a stroke range of the movable member which does not affect the state of the coupling, for example, in the range which corresponds to over-disengaging in a clutch of the normally open type.

The adjustment of the length is made selectively at the request of a computer, in particular depending on information transmitted to the computer by one or more sensors, such as a predefined position value for a position sensor corresponding to the grinding point of the clutch.

According to a first possibility, such an adjustment of the support with respect to the grinding point, which is estimated by the computer, can be achieved, but this grinding point can vary in particular depending on the temperature of the coupling.

In addition, the relationship between the position of the grinding point and the load of the clutch in the engaged state, that is, when the assist force in the case of a clutch of the normally open type must be highest, numerous uncertainties, in particular related to the scatters and with the variation of the force of the diaphragm spring and the return tabs of the pressure plate with the wear, as well as the different tolerances in the progressiveness and in the rigidity of the components of the clutch.

According to a second possibility, the setting of the support for a high transmittable torque value can be achieved. However, the uncertainty in the value of the friction coefficient of the clutch in this case adds to the adjustment of the support.

In the document WO-2007/138216 the adjustment is made step by step with the screw-nut system and one step at a time for a return path of the movable part. As a result, the initial setting at start-up for a first use of the actuator may require a large number of steps, and therefore a long time to execute on the assembly line, depending on the tolerances.

In addition, the adjustment is made in the actuator when the clutch is in its disengaged state and occasionally, while the engine of the vehicle equipped with it is turned off, that is under the conditions in which the movement noise exiting the actuator, especially for the driver is perceptible. For this reason, certain vehicle manufacturers require that the adjustment be made with the engine running and when the clutch is in its engaged state so as not to be noticeable to the driver of the vehicle.

The document FR 2 564 920 describes wear adjusting means (or adjuster) of an actuator for controlling a normally-closed type clutch.

The operating principle of the actuator described in this document, however, only applies to a normally closed type coupling. The rest position (which corresponds to a force equal to zero and the engaged state) and the useful stroke of the clutch are each connected in such a way that the adjustment concept is not applicable to a normally open clutch in which the rest position remains unchanged regardless of the wear of the clutch.

As a result, such an actuator has the disadvantage that it can not be standardized and used for different applications, in particular in a hybrid vehicle comprising three clutches, one normally-closed type clutch and two normally-open type clutches.

The adjustment of the assist force is also achieved mechanically with respect to the rest position of the clutch, that is, while the clutch load is minimal, and therefore not when the actuation force is maximum, where the assist force would prove most useful.

The object of the present invention is to provide an actuator for a clutch, which is particularly simple and compact and which allows to overcome the disadvantages of the actuators of the prior art.

More particularly, the present invention aims to propose an actuator incorporating assisting means which selectively provide an assisting force to passively assist the actuation force to achieve efficient operation and, at the same time, reduced power consumption of the engine, said actuator is compatible with all types of coupling, normally open or closed.

The present invention also aims to propose an actuator that can be quickly adjusted, in particular to perform the original adjustment of the actuator on the assembly line, and its Einstellmanöver can be performed noiseless, while the clutch occupies the engaged state (and wherein the engine running in such a way that it is imperceptible to the driver).

• – ein Ausgangsorgan des Stellantriebs, um auf Steuermittel der Kupplung einzuwirken, um einen Zustandswechsel der Kupplung mindestens zwischen einem gekuppelten Zustand und einem ausgekuppelten Zustand zu bewirken, wobei das Ausgangsorgan zwischen mindestens einer ersten axialen Ruheposition und einer unter Last stehenden zweiten axialen Arbeitsposition beweglich montiert ist, die in Bezug auf eine stationäre Referenz in Abhängigkeit von dem Verschleiß der Kupplung variiert,
• – einen selektiv gesteuerten Motor, um zugeordnete Antriebsmittel zu verlagern, die mit mindestens einem Betätigungsorgan zusammenwirken, das auf das besagte Ausgangsorgan einwirkt,
• – Unterstützungsmittel, die mindestens eine Unterstützungsfeder aufweisen, die über Anlegemittel eine Unterstützungskraft auf ein Unterstützungsorgan ausübt, das beweglich zwischen einer End-Ruhestellung, die von ersten Anschlagmitteln definiert ist, und einer End-Unterstützungsposition, die von zweiten Anschlagmitteln definiert ist und zu der die besagte Unterstützungskraft das besagte Unterstützungsorgan beansprucht, montiert ist, wobei das besagte Unterstützungsorgan in Bewegung mit dem besagten Betätigungsorgan über komplementäre Verbindungsmittel verbunden ist, die in einer nur einseitig gerichteten Weise die Einstellung der relativen Position des Unterstützungsorgans in Bezug auf das Betätigungsorgan erlauben, um in Abhängigkeit von der zweiten axialen Arbeitsposition unter Last des Ausgangsorgans den Verschleiß der Kupplung auszugleichen.

With this aim, the invention proposes an actuator for a clutch, in particular for a motor vehicle, which comprises at least the following:

• - An output member of the actuator to act on control means of the clutch to cause a state change of the clutch at least between a coupled state and a disengaged state, wherein the output member is movably mounted between at least a first axial rest position and a second axial working position under load that varies with respect to a stationary reference depending on the wear of the clutch,
• A selectively controlled motor to displace associated drive means cooperating with at least one actuator which acts on said output member,
• Support means comprising at least one support spring which, via apply means, applies an assist force to a support member movably between an end rest position defined by first stop means and an end support position defined by second stop means and to which said supportive force claimed said support member is mounted, said support member is connected in movement with said actuator via complementary connecting means which allow in a unidirectional manner, the adjustment of the relative position of the support member with respect to the actuator in dependence From the second axial working position under load of the output member to compensate for the wear of the clutch.

Advantageously, the actuator according to the invention can be associated with any coupling, with a simple coupling or a double coupling and regardless of its type, a normally open coupling as well as a normally closed coupling.

Advantageously, the actuator may be used in the control of a normally-open clutch to effect a change from the disengaged state to the engaged state, as well as to a normally-closed clutch to effect the change from the engaged state to the disengaged state, conversely ,

Advantageously, the actuator comprises assisting means providing a maximum assisting force when the resisting force opposed by the diaphragm spring of the coupling is maximum.

Compared with the prior art actuators, the complementary connecting means constituting the adjusting means, thanks to which the adjustment is made which allows the wear of the coupling to be compensated, not downstream of the motor and the support means and upstream of the output member, i.e. "in Series "arranged.

The actuator is adapted to readjust the wear of the clutch when the resistance force counteracted by the diaphragm spring of the clutch is substantially maximum, the readjustment advantageously taking place on a linear and rising part of the clutch characteristic corresponding to the maximum force. he follows.

Advantageously, the actuator according to the invention is adjustable depending on the tolerances and the wear of the coupling by simple and robust strategies by selectively using the motor of the actuator, a controlled force, called over-force exerted, which is greater than the force normally required for coupling ,

Advantageously, different readjustment strategies may be used, in particular initially, on the assembly line of the manual transmission or the vehicle, according to conditions defined by the manufacturer of the vehicle or later, during the life of the vehicle.

In the case of strategies over the life of the vehicle, the readjustment may be made periodically at a given predefined interval that is sufficiently long for the onset of wear or only when effective wear is detected.

The readjustment may also be carried out under conditions favorable for achieving good repeatability of wear detection, in particular the following conditions: an estimated temperature of the engine or clutch which is within a certain range of values, a clutch speed which is moderate or zero or according to the acoustical conditions or availability of the actuator while the engine of the vehicle is stopped or running.

The over-force generated by the motor of the actuator is achieved, for example, by gradually applying a current to the motor until a predefined setpoint is reached, or by communicating a certain kinetic energy (speed) to the motor to a predefined engaged position.

• – belegt das Ausgangsorgan die unter Last stehende zweite Arbeitsposition, wenn die Kupplung des normalerweise offenen Typs im eingekuppelten Zustand ist;
• – ist der Stellantrieb angepasst, um eine normalerweise offene Kupplung zu steuern;
• – ist der Stellantrieb angepasst, um eine normalerweise geschlossene Kupplung zu steuern;
• – umfasst der Stellantrieb ein Gehäuse, das, indem es die ersten und zweiten Anschlagmittel trägt, die stationäre Referenz bildet, in Bezug auf welche die zweite axiale Arbeitsposition variiert;
• – sind Vorspannungsmittel zwischen dem besagten Betätigungsorgan und dem besagten Ausgangsorgan angeordnet;
• – umfassen die besagten Antriebsmittel Mittel zum Umwandeln einer Drehbewegung des Motors in eine Verschiebungsbewegung, die auf das Betätigungsorgan übertragen wird;
• – umfassen die zum Motor gehörenden Antriebsmittel zumindest eine Kugelumlaufspindel und einen Schlitten, wobei der drehende Antrieb der Kugelumlaufspindel durch den Motor die verschiebende Bewegung des Schlittens bewirkt, der in Bewegung mit dem Betätigungsorgan verbunden ist;
• – ist das Betätigungsorgan um eine Rotationsachse drehbeweglich montiert;
• – ist das Unterstützungsorgan um die Rotationsachse des Betätigungsorgans drehbeweglich montiert;
• – bestehen die Mittel zum Anlegen der Unterstützungskraft, die von der Unterstützungsfeder geliefert wird, an das Unterstützungsorgan aus einem System Walze und Nocken;
• – umfassen die komplementären Verbindungsmittel Rücklauf-Verhinderungsmittel, die eingreifen, um das Einstellen der relativen Position des Betätigungsorgans in Bezug zu dem Unterstützungsorgan in einer einseitig gerichteten Weise zu erlauben;
• – umfassen die Rücklauf-Verhinderungsmittel mindestens ein Sperrklinkensystem;
• – beschränken die ersten Anschlagmittel einerseits den Hub des Unterstützungsorgans zu der End-Ruheposition und, andererseits, den Hub des Ausgangsorgans zu der axialen Ruheposition und des Betätigungsorgans über die komplementären Verbindungsmittel und die Unterstützungsmittel, wodurch der Rücklaufhub des Motors in die Richtung, die dem Rücklauf des Unterstützungsorgans zu der End-Ruheposition, und des Ausgangsorgans zu der axialen Ruheposition entspricht, ein verringerter Hub ist;
• – umfassen die komplementären Verbindungsmittel des Unterstützungsorgans und des Betätigungsorgans Eingriffsmittel, die aus mindestens einer ersten Verzahnung, welche von einem ersten Teil getragen wird, das fest mit dem Betätigungsorgan verbunden ist, und aus einer zweiten Verzahnung bestehen, welche von einem zweiten Teil getragen wird, das in Bewegung verbunden mit dem und beweglich in Bezug zu dem Unterstützungsorgan montiert ist;
• – wird der Motor gesteuert, um selektiv unter bestimmten Bedingungen eine Überkraft auszuüben, um es zu erlauben, den Verschleiß der Kupplung auszugleichen;
• – sind das Betätigungsorgan und/oder das Unterstützungsorgan translatorisch beweglich montiert;
• – ist der Stellantrieb geeignet, eine Kupplung, einfach oder doppelt, des normalerweise offenen Typs zu steuern, insbesondere eine Kupplung, die ein Kraftfahrzeug ausstattet, welches ein automatisches Schaltgetriebe umfasst.

According to other features of the invention:

• - the output element occupies the second working position under load when the normally open type clutch is in the engaged state;
• - The actuator is adapted to control a normally open coupling;
• - The actuator is adapted to control a normally closed clutch;
• The actuator comprises a housing which, by supporting the first and second stop means, constitutes the stationary reference with respect to which the second axial working position varies;
• - Biasing means are arranged between said actuator and said output member;
• - The said drive means comprise means for converting a rotational movement of the motor in a sliding movement, which is transmitted to the actuator;
• The drive means belonging to the motor comprise at least one ball screw and a slide, wherein the rotary drive of the ball screw by the motor causes the sliding movement of the carriage, which is connected in movement with the actuator;
• - The actuator is rotatably mounted about an axis of rotation;
• - The support member is rotatably mounted about the axis of rotation of the actuator;
• The means for applying the assisting force supplied by the support spring to the support member consist of a roller and cam system;
• The complementary connecting means comprise return preventing means which engage to allow adjustment of the relative position of the actuating member with respect to the support member in a unidirectional manner;
• The return-preventing means comprise at least one pawl system;
• The first stop means limit, on the one hand, the stroke of the support member to the end rest position and, on the other hand, the stroke of the output member to the axial rest position and of the actuator via the complementary connecting means and the support means, whereby the return stroke of the engine in the direction leading to the return the support member to the end rest position, and the output member corresponds to the axial rest position, is a reduced stroke;
• The complementary connection means of the support member and the actuator comprise engagement means consisting of at least a first toothing carried by a first part fixedly connected to the actuator and a second toothing supported by a second part; which is mounted in movement with and movably mounted with respect to the support member;
• - The motor is controlled to selectively exert a positive force under certain conditions, to allow to compensate for the wear of the clutch;
• - The actuator and / or the support member are mounted translationally movable;
• - The actuator is adapted to control a clutch, single or double, of the normally open type, in particular a clutch that equips a motor vehicle, which includes an automatic transmission.

Other features and advantages of the invention will become apparent upon reading the following detailed description, which should be understood by reference to the accompanying drawings, in which:

the 1 and 2 are three-quarter perspective views illustrating an actuator for a clutch according to an embodiment of the invention and each showing the actuator with and without housing,

3 is a sectional view taken along a plane with a vertical orientation, which passes through the axis of rotation A, the actuator according to the 1 and 2 without the housing,

4 is an end view in the axial direction, the actuator according to the 1 and 2 without the housing,

the 5 to 9 axial sectional views are that the actuator according to the 1 to 4 represent and show different operating states and operating positions,

10 is a schematic view illustrating an embodiment of the actuator according to the invention.

In the following description and in the claims, the terms "front" and "rear", "top" and "bottom", "right" and "left" are used with reference to the orientations longitudinal, vertical and for the sake of understanding across the tripod (L, V, T) shown on the figures and according to the definitions given in the description.

The longitudinal alignment according to the tripod (L, V, T) therefore corresponds to a general axial operating direction of the actuator.

On the 1 and 2 became an actuator 10 for a clutch E (not shown in detail) in particular of a motor vehicle.

The actuator 10 includes a housing 12 , which generally has a parallelepiped shape and in the interior of which at least a part of the components is arranged.

As in 1 shown, extends at least a part of an output member 14 of the actuator 10 outside of said housing 12 ,

Preferably, the actuator comprises 10 a protective bellows 15 who is the source organ 14 belongs. The protective bellows 15 is at one of its axial ends with a 16 the surfaces of the housing 12 connected, said vertical surface 16 from the parent organ 14 is crossed, and at the other of its ends it is with the parent organ 14 connected. The protective bellows 15 surrounds the output organ 14 and has a general accordion fold shape that allows its length to vary axially when the output organ 14 is moved.

Preferably, the starting organ 14 the actuator a shaft whose free end is adapted to control means (not shown) of the clutch E act.

The control means of a clutch E may be implemented in different ways depending on the applications.

As a non-limiting example, such mechanical type of control means includes a fork which is pivotally mounted between its two ends, one end thereof being connected to the output member 14 is connected to be actuated selectively by the actuator, and the other of its ends is adapted to act on a clutch release bearing to control against the restoring force exerted by a diaphragm spring of the clutch E, a state change of said clutch E.

As a variant, the control means are hydraulic and comprise at least one sensor, to which the output member 14 acting, and a slave, which, connected to the encoder by hydraulic connection means, integrates a stop adapted to act on the coupling, in particular the free end of the fingers of a diaphragm spring, to change the state of the clutch between the engaged and disengaged To effect state.

The initial organ 14 is adapted to cause a change in state of the clutch E between at least one engaged state and a disengaged state, generally via such control means of mechanical and / or hydraulic type.

The initial organ 14 is between at least a first axial rest position (P1), which in 6 and a second axial operating position (P2) under load, shown in FIG 6 shown is movably mounted.

The second axial working position under load (P2) of the output member 14 varies depending on the wear of the clutch E, in particular on the wear of the friction linings.

The clutch E is in this embodiment, a normally open clutch, so that the output member 14 the actuator occupies the said second axial working position under load (P2) in the engaged state.

In the course of wear, which occurs in the clutch E, the second axial working position varies under load (P2) of the output member 14 in terms of a stationary reference.

The actuator 10 includes a motor 18 which is selectively controlled to associated drive means 20 to relocate, especially in 2 are visible.

Preferably, the stationary reference consists of a vertical front surface 16 of the motor 18 , which determines a reference position P on 6 is shown, or as a variant, it consists of the housing 12 , in particular from one of its vertical surfaces.

Preferably, the engine is 18 a rotating motor, but especially not exclusively an electric motor. As in the 1 and 2 shown includes the engine 18 at least one plug in the upper part 19 for his power supply.

Preferably, the engine is 18 on the housing 12 fastened, for example by means of screws (not shown), with fixing lugs of the engine 18 co-operate, of which, as in the 1 and 2 shown here are four present, which are circumferentially on the body of the engine 18 are distributed.

As a variant, the engine 18 a linear motor.

As a variant, the engine 18 operated by a force of the hydraulic or pneumatic type.

To good performance of the engine 18 to achieve, for example, a short reaction time, or even to avoid heating, becomes the engine 18 advantageously used in a torque range (or current range) in which the motor has the best performance, where the operating efficiency is optimal.

The motor 18 Generally, beyond this torque range (or current range) for which the operation is optimal, it has an area where the motor is located 18 Although lower power is available, but remains available to provide an overforce, generally to improve the accelerations of the engine or to overcome a torque peak, and in particular in the invention to achieve an adjustment, as described in detail with reference to the 5 to 9 is explained.

Advantageously, the engine 18 suitable to be controlled to selectively exert an over-force to the actuator of the invention 10 allow to compensate for the wear of the clutch, the over-force is applied under certain conditions, in particular depending on one or more parameters.

These parameters are, for example, zero speed of the engine of the clutch and the actuator 10 equipped vehicle, a given distance traveled by the vehicle, a given temperature of the engine, etc.

Advantageously, the actuator performs 10 an adjustment if and only if there is a wear of the coupling.

The drive means 20 coming from the engine 18 be actuated, act with at least one actuator 22 that on the initial organ 14 interacts, together.

The drive means 20 comprise means for converting the movement, for example for converting the rotational movement of the motor 18 in a displacement movement, to the actuator 22 is transmitted.

As in 2 shown, include the drive means 20 that with the engine 18 associated with at least one ball screw 24 and a sled 26 , wherein the rotating drive of the ball screw 24 through the engine 18 the displacement movement of the carriage 26 causes.

As a variant, the drive means exist 20 of other mechanical equivalent means advantageously adapted to carry out a motion conversion, such as a nut / bolt system, a system comprising a cam or at least one lever, a connecting rod crank system, a gear system.

When the ball screw 24 rotatably driven by the motor, the carriage moves 26 axially along the longitudinal direction as a function of the direction of rotation in the one direction or in the other direction between at least one rear and one front position.

The sled 26 includes eluent 28 that with an axial path 30 interact, the eluents 28 For example, consist of two rollers, which are in the upper part of the carriage 26 , which is formed as a "U", are arranged.

Preferably, the web becomes 30 from the bottom surface of a part 31 formed firmly with the housing 12 connected as a variant directly to the housing 12 belongs.

The sled 26 is in motion with the actuator 22 connected.

The actuator 22 is formed of a lever which is rotatably mounted for rotation about a transversely extending axis A, wherein the axis A stationary and fixed to the housing 12 of the actuator 10 connected is.

The lever 22 , which forms the actuator, comprises two lateral plates, starting from the axis of rotation A, which is arranged at its lower end, globally vertically in the direction of the drive means 20 and globally parallel to each other delimit a space between them.

Preferably, the carriage comprises 26 two drive arm 32 which are transverse, with respect to the main body of the carriage 26 projecting, extend and which are suitable, the operating lever 22 to drive positively.

Every drive arm 32 of the sled 26 includes a role 33 , which is intended to rotatably drive the lever 20 to allow the axis A, when the carriage 26 that of the engine 18 is moved, moves axially translationally.

Preferably, each of the plates of the operating lever 22 an upper end formed as a "Y", the upper legs between each other a receptacle 34 delimit, inside which one of the drive arms 32 fits.

Every shot 34 is delimited by a "V" -shaped web, the roll 33 of drive arm 32 along the direction of movement of the carriage 26 interacts with one or the other part.

The actuator 10 includes supportive means 36 that have at least one support spring 38 comprising, by means of applying means an assisting force on a supportive body 40 exercises.

The support organ 40 is movable between an end rest position, the first stop means 42 is defined, and an end support position, the second stop means 44 is defined, and to which the supporting body 40 is claimed by the support force mounted.

The support means 36 are in a box 45 next to the case 12 of the actuator 10 housed, with the support spring 38 with one of its ends against a surface with vertical transverse orientation of the housing 45 is in support and at the other rear of their ends the support organ 40 claimed by the application means.

The first and second stop means 42 . 44 are advantageously from the housing 12 of the actuator 10 carried.

Preferably, the application means comprise at least one axial support 46 that includes at least one front part to which the supporting spring 38 is mounted, and a rear part comprising an annular collar which, by extending radially on a diameter which is larger than that of the front part, a support side 48 includes.

The rear end of the support spring 38 comes axially against the surface 48 the buttock of the wearer 46 to the edition, whereby the rear part two wings 50 comprising axially extending rearwardly from the annular collar.

The application means comprise a system with cam and roller to the support force on the support member 40 to transfer, wherein the system at least one application roller 52 and a reaction roller 54 includes that with the carrier 46 through a transverse shaft 56 are connected, the ends axially in the wings 50 are blocked.

The support organ 40 is rotatably mounted to the rotation axis A movable. Preferably, the support organ 40 formed by a lever which, like the lever forming the actuator 22 , is movably mounted at its lower end about the axis of rotation A.

The support lever 40 includes a part 58 , which forms a tracking device, with the application roller 52 the support means 36 interacts.

The support lever 40 includes a claw 60 which, by projecting axially projecting rearwardly, is intended to engage with the second stop means 44 co.

The support organ 40 is in shift with the actuator 22 connected via complementary connecting means, which adjust the relative position of the support organ 40 in relation to the actuator 22 in only one direction to allow in response to the second axial working position under load (P2) of the output member 14 compensate for the wear of the clutch.

The complementary connection means comprise at least a first connection part 62 firmly with the lever 22 , which forms the actuator, is connected.

The first connection part 62 is located inside the room, which is transverse to the two panels holding the operating lever 22 form, is limited.

The first connection part 62 is intended to be engaged by a second connector 64 to be connected, this second connecting part 64 in relocation with the support organ 40 connected is.

The first connection part 62 generally has an arcuate shape and includes a concave bottom surface 65 , which is aligned with the axis of rotation A.

A first gearing 66 is from the first connection part 62 worn, right here in the lower surface 65 arranged, and a second gearing 68 leading to the first gearing 66 is complementary, is from the second connecting part 64 carried.

Advantageously, the complementary connecting means comprise return preventing means which engage to adjust the relative position of the actuator 22 in relation to the supporting body 40 to allow in one direction only.

Preferably, the return protection means consist of at least one pawl system or other equivalent blocking means.

The second gearing 68 is from the second connection part 64 worn in a recording of the support organ 40 is movably mounted, wherein the second connecting part 64 from an elastic organ 70 , this in 3 is visible, is claimed so that such a pawl system is formed.

The second connecting part 64 is between a retracted and an engaged position of the second toothing 68 to which the elastic organ 70 the second connecting part 64 automatically reset, movably mounted.

The elastic organ 70 is between the bottom of the support of the support organ 40 and the second connection part 64 whose lower part is the organ 70 claimed so that the first and second teeth 66 and 68 interact to the actuator 22 and the support organ 40 arranged in relocation, arranged.

The retracted position allows relative movement of the first gearing 66 in relation to the second gearing 68 and consequently the actuator 72 in relation to the supporting body 40 ,

The retracted position is achieved when, since the actuator 22 and the support organ 40 are rotationally driven, the claw 60 the support organ with the second stop 44 comes into contact.

The first connection part 62 firmly with the operating lever 22 is not blocked, so that the first gearing 66 therefore with a ramp effect the second gearing 68 against the elastic organ 70 claimed to allow the movement of the one relative to the other by a given number of teeth, which corresponds to the wear of the clutch to be compensated.

Preferably, the actuator comprises 10 biasing 72 between the actuator 22 and the source organ 14 are arranged.

Advantageously, such biasing means allow 72 in particular, the compound of the parent organ 14 of the actuator 10 with the control means of the clutch E easier.

Advantageously, the biasing means allow it 72 to recreate any existing game and the starting organ 14 to keep in contact with the control means of the clutch E.

As in the 2 and 4 shown, include the biasing means 72 at least one bias spring 74 one end on an intermediate part 76 , which generally has a "U" bow shape, is in circulation.

Preferably, the other end of the biasing spring is located 74 on a collar, a spacer 78 includes axially on the back.

The intermediate part 76 the biasing agent 72 is always in motion with the output member 14 of the actuator 10 and with the actuator 22 connected. The axial front part of the intermediate part 76 is at the axial rear end of the shaft 14 and the rear axial part formed of two legs of the "U" enclosing it from the outside, with the actuator 22 coupled.

The intermediate part 76 includes for its connection to the actuator 22 on each of his thighs a shrinkage 80 , The shrinkage 80 penetrates across a hole 82 holding each plate, which is the actuator 22 forms, includes.

The preload spring 74 is therefore axially between the output member 14 and the actuator 22 of the actuator 10 inserted.

Below is the functioning of the actuator 10 according to the first embodiment, with reference to the 1 to 4 described in more detail.

In 5 became the components of the actuator 10 in the respective positions that are taken by one and the other when the actuator 10 as supplied, prior to its assembly, to associate it with a clutch E by being connected to the control means of the clutch, as well as showing its commissioning.

In this delivery condition, the actuator occupies 22 an end position which is offset axially forward, the disengaged state and the retracted position of the carriage 26 the drive means 20 equivalent.

The support organ 40 is in a stable position over his claw 60 in support against the second stop means 44 ,

The support spring 38 has its maximum length and takes over the system with cam and roller 52 . 54 the support organ 40 with a maximum support force indicated by an arrow F in 5 is shown.

As in 5 shown points the spring 38 axially its maximum length, for which the force F is minimal, but since the action distance X with respect to the axis A is maximum, the assisting moment C (corresponding to the product of the force F with the distance X) is on the lever, the support organ 40 is also maximum, which is why the support is maximum.

Compared to 5 is in 7 the action distance X with respect to the axis A is minimal.

The support spring 38 therefore occupies a stable position such that any risk of involuntary release of the spring 38 is eliminated.

The initial organ 14 of the actuator 10 is in an axial forward end position, beyond the disengaged state, which allows the organ 14 without excessive force to connect with the control means, such as a fork, the clutch E.

Advantageously, it allows preloading spring 74 , the initial organ 14 with the control means of the clutch to connect without excessive force, while at the same time, however, a sufficient force is applied to readjust any existing game and the output member 14 to keep in contact with the control means of the clutch E.

In 6 became the components of the actuator 10 in the respective positions that occupy the one and the other, when the actuator 10 , which is associated with a clutch E, is used (in the engaged new state) for the first time.

The actuator 10 is controlled to act on the clutch E against the resistance force that opposes these and in particular the diaphragm spring of the clutch E, and until reaching a balance.

The motor 18 drives the ball screw 24 rotatory, indicating an axial movement of the carriage 26 according to a track, during which the carriage 26 the drive means 20 the actuator 22 that is, clockwise about the axis of rotation A, from the first stop means 42 to the second stop means 44 , pans, takes along.

When the actuator 22 is driven in a rotational manner, the support organ remains 40 in the attack against the second stop means 44 motionless, so that therefore a relative displacement between the actuator 22 and the supporting body 40 occurs.

The first gearing 66 of the first part 62 that with the actuator 22 connected, moves with respect to the second gearing 68 that from the second part 64 is worn, which is vertical to the retracted position against the elastic organ 70 is pushed back.

During the movement of the first part 62 has the first gearing 66 for each tooth, an inclined surface forming a ramp adjacent to the surface of the second toothing 68 with which it interacts, applies a force greater than the restoring force exerted by the elastic organ 70 is applied to the relative movement of the actuator 22 in relation to the supporting body 40 to achieve.

Advantageously, the initial setting takes place during the commissioning of the actuator 10 in a single movement of the actuator 22 that alone by the engine 18 without the help of the support 36 is driven.

The commissioning of the actuator 10 is easy and fast, especially without requiring any learning.

Advantageously, the commissioning of the actuator 10 regardless of the state of the engine of the motor vehicle equipped with the clutch E, including when the engine is stopped.

The sled 26 is then axially in the reverse direction of the engine 18 moved to take the position on 7 is shown, in the course of this return path drives the actuator 22 the support body 40 by engagement, resulting in the positive engagement between the first gearing 66 and the second gearing 68 results.

The support organ 40 leaves the end support position, that of the second stop means 44 is defined, and is by the drive means 20 coming from the engine 18 are driven to the final resting position, that of the first stop means 42 is deferred. During the return path, the support organ compresses 40 the support spring 38 axially.

The first disengagement involves the components of the actuator 10 originally in the in 7 positions shown.

The motor 18 again drives the ball screw 24 rotatory and thereby causes the displacement of the part 26 in the execution, the part 26 via drive arms 32 the actuator 22 rotatory about the axis A drives.

The support organ 40 is also driven in rotation about the axis A, by the actuator 22 accompanying him in his movement and giving him the support that comes from the support funds 36 , in particular the support spring 38 is delivered.

In the direction of movement are the support organ 40 and the actuator 22 connected in movement by engagement, more specifically based on the first and second teeth 66 and 68 belonging to the complementary liaison.

The first and the second connecting part 62 and 64 , each one of the first and second gears 66 and 68 carry, namely function like a pawl system, the support organ 40 and the actuator 22 connects in one direction.

Advantageously, the engine 18 in this maneuver by the supporting force, which is the supportive means 36 the support body 40 deliver, supported.

In the 8th and 9 In each case, the components of the actuator were engaged and disengaged 10 when the maximum wear compensation capacity of the clutch has been used.

As in the 8th and 9 shown was the maximum relative movement between the first gearing 66 and the second gearing 68 the complementary bonding agent 62 and 64 used.

As in 9 shown, the moving part occupied by the part 26 and the actuator 22 is formed, an axial end position of the housing 12 which is opposite, is demarcated.

The embodiment described with reference to FIGS 1 to 9 is given by way of example and not limitation.

In 10 was schematically a variant of the actuator according to the invention 10 shown.

Compared with those in the 1 to 9 described embodiment, shows 10 a variant of the invention, in which in particular the movements of the organs are linear.

Advantageously, the actuating member 22 and the support organ 40 mounted translationally movable.

Preferably, the actuator according to this variant is adapted to control a clutch, single or double, of the normally open type, in particular a clutch E, which equips a motor vehicle comprising an automatic transmission.

Advantageously, the actuator is therefore suitable, for example, to act on the control means of the clutch E, which comprises hydraulic connection means. The hydraulic connection means are for example between the output member 14 of the actuator 10 and the clutch E arranged.

Depending on the application, the hydraulic connection means comprise at least one transmitter and one receiver, which are preferably each of the concentric type.

The actuator according to the invention 10 is in no way on the control of a normally open clutch E, as in the embodiment of the 1 to 9 or the variant of 10 is described limited.

Advantageously, the starting element occupies 14 the second operating position under load P2 when the clutch E of the normally open type is in the engaged state.

As a variant not shown is the actuator 10 able to control a normally closed clutch E. For this purpose, the actuating force must be a constantly increasing force on the second axial working position under load P2 of the output member 14 Beyond that, and the wear of the clutch E must be the movement from the second axial working position under load P2 of the output member 14 effect in the direction of actuation, that is, on the previous second axial working position under load P2, from the output member 14 is occupied, out.

In such a variant, the output member occupied 14 the second working position under load P2 when the normally-open type clutch E is in the disengaged state.

In 10 For example, the first axial rest position (P1) and the second axial rest position under load (P2) were respectively represented in the new state corresponding to the letter "N" and after wear of the clutch corresponding to the letter "U".

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

• WO 2007/138216 [0011, 0019]
• FR 2564920 [0021]

Claims (15)

Actuator ( 10 ) for a clutch (E), in particular for a motor vehicle, comprising at least: - an output element ( 14 ) of the actuator to act on control means of the clutch (E) to cause a state change of the clutch (E) at least between a coupled state and a disengaged state, wherein the output member ( 14 ) is movably mounted between at least a first axial rest position (P1) and a second axial operating position (P2) under load which is dependent on the wear of the clutch (E) with respect to a stationary reference (P1). 12 ) is variable, - a selectively controlled engine ( 18 ) to associated drive means ( 20 ) with at least one actuator ( 22 ) interacting with the parent organ ( 14 ), - support ( 36 ) containing at least one support spring ( 38 ), which are mediated by means of application ( 52 . 54 . 58 ) an assisting force on a supporting body ( 40 ) movably between an end rest position, which is supported by first stop means ( 42 ) and an end support position defined by second stop means ( 44 ) and to which the supporting force supports the 40 ) is mounted, wherein the support member ( 40 ) in motion with the actuator ( 22 ) with the intermediation of complementary liaison ( 62 . 64 ), which determines the adjustment of the relative position of the 40 ) with respect to the actuator ( 22 ) in one direction only, in order to produce a function of the second axial working position (P2) of the output member under load (P2). 14 ) compensate the wear of the clutch (E). Actuator according to claim 1, characterized in that the actuator ( 10 ) is adapted to control a normally open coupling (E). Actuator according to claim 1 or 2, characterized in that the actuator ( 10 ) a housing ( 12 ), which, by holding the first and second stop means ( 42 . 44 ), which forms a stationary reference with respect to which the second axial working position (P2) varies. Actuator according to one of claims 1 to 3, characterized in that biasing means ( 72 ) between the actuator ( 22 ) and the parent organ ( 14 ) are arranged. Actuator according to one of claims 1 to 4, characterized in that the drive means ( 20 ) Means for converting a rotary motion of the motor ( 18 ) in a translatory movement, which on the actuator ( 22 ) is transmitted. Actuator according to claim 4, characterized in that the motor ( 18 ) associated drive means ( 20 ) at least one ball screw ( 24 ) and a sledge ( 26 ), wherein the rotary drive of the ball screw ( 24 ) by the engine ( 18 ) the translational movement of the carriage ( 26 ) which is in movement with the actuator ( 22 ) connected is. Actuator according to one of the preceding claims, characterized in that the actuating member ( 22 ) is mounted rotatably about a rotation axis (A). Actuator according to claim 7, characterized in that the support member ( 40 ) about the axis of rotation (A) of the actuator ( 22 ) is mounted rotatably. Actuator according to one of the preceding claims, characterized in that the means for applying the of the support spring ( 38 ) to the supporting body ( 40 ) from a roller and cam system ( 52 . 54 . 58 ) consist. Actuator according to one of the preceding claims, characterized in that the complementary connecting means ( 62 . 64 ) Comprise return-preventing means which engage to adjust the relative position of the actuator ( 22 ) in relation to the supporting body ( 40 ) only in one direction. Actuator according to claim 10, characterized in that the return-preventing means comprise at least one pawl system. Actuator according to claim 1, characterized in that the first stop means ( 42 ) on the one hand, the hub of the supporting body ( 40 ) to the end rest position and, on the other hand, the stroke of the parent organ ( 14 ) to the axial rest position (P1) and the actuator ( 22 ) mediating the complementary connection means ( 62 . 64 ) and the support ( 36 ), whereby the return stroke of the engine ( 18 ) in the direction of the return of the supporting body ( 40 ) to the end rest position and the output member to the axial rest position (P1) is a reduced stroke. Actuator according to one of the preceding claims, characterized in that the complementary connecting means ( 62 . 64 ) of the supporting body ( 40 ) and the actuator ( 22 ) Comprise intervention means consisting of at least a first gearing ( 66 ), which from a first part ( 62 ), which is fixed to the actuator ( 22 ) and a second gearing ( 68 ) formed by a second part ( 64 ), which is in motion connected to the supporting body ( 40 ) and is mounted relative to this movable. Actuator according to one of the preceding claims, characterized in that the engine ( 18 ) is controlled to selectively exert an excess force under certain conditions to allow the compensation of the wear of the clutch (E). Actuator according to claim 1, characterized in that the actuating member ( 22 ) and / or the supporting body ( 40 ) are mounted translationally displaceable.

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