• 专利附录
  • 专利说明
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    • 专利摘要:
    The present invention relates to an actuator (10) for a clutch, especially a motor vehicle, comprising at least one actuator output member (14) for acting on control means of said clutch (E), said member (14). with a movable mounting between at least a first axial position (P1) of rest and a second position (P2) axially working under load which, relative to a reference (12) fixed, varies depending on the wear of the clutch (E), a motor (18) controlled to move driving means (20) which cooperate with at least one actuating member (22) acting on said output member (14), means (36) assistance device comprising an assistance spring (38) which exerts an assist force on a support member (40) which is movably mounted between an extreme rest position defined by first abutment means (42) and an extreme assist position defined by second (44) abutment means and wherein said assisting force urges said assisting member (40), said assisting member (40) being movably connected to said actuating member (22) via connecting means (62, 64) enabling , unidirectionally, the adjustment of the relative position of the member (40) of assistance relative to the actuating member (22) for, depending on the second position (P2) axially working under load of the output member (14) compensates for the wear of the clutch (E).
    公开号:FR3022966A1
    申请号:FR1456011
    申请日:2014-06-26
    公开日:2016-01-01
    发明作者:Herve Maurel
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to the field of actuators, in particular a clutch actuator of a motor vehicle.
    [0002] The present invention relates more particularly to a stroke or wear compensating actuator for a motor vehicle clutch acting, directly or indirectly, on associated control means of the clutch, such as at least one clutch abutment. When the actuator comprises assistance means, also called "force compensation", the actuator then generally comprises an assistance spring which acts on a cam or an inclined ramp connected to the output member of the actuator. actuator for biasing said output member, for example in the direction corresponding to the opening of the clutch when the clutch is of the "normally closed" type.
    [0003] The assisting spring approximately balances the resisting force provided by a clutch return spring, usually a diaphragm, so that the force to be supplied by the engine for the actuation of the clutch is then reduced to a minimum. minimum value. It is recalled that a clutch in which the position of the diaphragm by default corresponds to an engaged state is generally called "normally closed" whereas a clutch in which the position of rest of the diaphragm by default corresponds to a disengaged state is called "normally open ", the latter type of clutch" normally open "being used in particular in a vehicle with a robotized gearbox. In a clutch, the wear of the friction linings results in a displacement of the control means, such as the clutch abutment, and therefore of the output member of the actuator, by a modification of the axial stroke of the clutch. this output member and a more or less significant modification of the control force to be delivered by the actuator to cause a change of state of the clutch. Numerous stroke or wear retrofit systems which are generally integrated with the clutch to compensate for the wear of the friction linings as it occurs, are known from the state of the art. way that said wear no longer affects the position of the control means and the axial stroke of the output member of the actuator. Such known devices are, however, relatively complex and their operation often proves to be imprecise and unreliable in use. Another solution is to adjust the axial position of the output member of the actuator according to the wear of the clutch and more particularly the friction linings, the adjustment being obtained in particular by means of length variable which, integrated with the actuator, compensate the displacement of control means, such as the clutch stop, due to wear of the clutch. In such a solution, the ability of the force assistance means to adapt to manufacturing tolerances and wear of the clutch remains a delicate point since the torque seen by the actuator motor depends on the correct timing. relative assistance and clutch curves, which in particular determines the performance of the actuator as well as the dimensioning and the lifetime of its components. Document WO-2007/138216 discloses a stroke-compensating actuator, in particular for a motor vehicle clutch, comprising a motor driving in translation a moving element acting on an output member of the actuator, such as a rod. , to cause the opening and closing of the clutch. Advantageously, such an actuator is applicable to the control of a clutch of normally closed type, such as a clutch of the normally open type. The moving equipment is constituted by a screw-nut system allowing adjustment of the length in both directions to compensate for the tolerances and more particularly the wear of the clutch, essentially 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 as a function of the wear is carried out in a running range of the moving element. which does not affect the state of the clutch, for example the range corresponding to an over-clutch in a clutch of normally open type. The length is adjusted selectively at the request of a computer, in particular according to information transmitted to the computer by one or more sensors, such as a predefined position value for a position sensor and corresponding to the licking the clutch. According to a first possibility, such a setting of assistance can be obtained in relation to the licking point estimated by the computer, this licking point is however likely to vary, depending in particular on the temperature of the clutch. In addition, the relationship between the position of the licking point and the force of the clutch in the engaged position, that is when the assistance effort must be greatest in the case of a clutch normally open type, 15 presents numerous uncertainties which are linked in particular to the dispersions and the variation of the force of the diaphragm, as well as the return tongues of the pressure plate with the wear, the different tolerances on the progressivity as on the stiffness of the components of the diaphragm. 'clutch. According to a second possibility, the setting of the assistance can be obtained in relation to a high transmissible torque value. However, the uncertainty on the value of the coefficient of friction of the clutch comes in this case to add to the setting of assistance. In the document WO-2007/138216, the adjustment with the screw-nut system is carried out step by step and at a rate of one step for a round trip of the moving equipment. Consequently, the initial setting during commissioning for a first use of the actuator may require, according to tolerances, a large number of steps and therefore require a significant time to be performed on the line of 'assembly. In addition, the adjustment within the actuator is effected when the clutch takes its disengaged state and sometimes while the engine of the equipped vehicle is off, that is to say under conditions for which the noise of displacement from the actuator is particularly noticeable by the driver. This is the reason why some vehicle manufacturers require that the adjustment is done with the engine running and when the clutch is in its engaged state, in particular to be imperceptible to the driver of the vehicle.
    [0004] The document FR-2.564.920 describes means of catch-up of wear (or catch-up) of an actuator for the control of a clutch of normally closed type. The principle of operation of the actuator described in this document, however, applies only to a clutch of normally closed type. Indeed, the rest position (corresponding to a zero effort and the engaged state) and the useful stroke of the clutch are respectively linked so that this catch-up principle is not applicable to a clutch normally open type in which the rest position remains the same regardless of the wear of the clutch.
    [0005] Therefore, such an actuator has the disadvantage of not being standardized and used for different applications and particularly with a hybrid vehicle having three clutches, respectively a normally closed type clutch and two clutches of normally open type.
    [0006] The setting of the assist force is also obtained mechanically in relation to the rest position of the clutch, ie when the clutch force is minimal and therefore not when the actuating force is at a maximum where the assistance effort would be the most useful. The object of the present invention is to provide a clutch actuator which is particularly simple and compact and makes it possible to solve the disadvantages of actuators of the state of the art. The present invention is particularly intended to provide an actuator that integrates assistance means selectively delivering an assistance effort to passively assist in the actuation to obtain a high performance operation while having a reduced energy consumption of motor, said actuator being compatible with all types of clutch, normally open or closed.
    [0007] Another object of the present invention is to propose an actuator which is quick to adjust, in particular to carry out the initial adjustment of the actuator on the assembly line and whose adjustment maneuver can be carried out silently while the clutch occupies the state engaged (and that the engine is running so as to be imperceptible to the driver). For this purpose, the invention proposes an actuator for a clutch, particularly a motor vehicle, comprising at least: an actuator output member for acting on control means of said clutch in order to cause a change of state of the clutch enters at least one engaged state and a disengaged state, said output member being movably mounted between at least a first axial position of rest and a second axial working position under load which, with respect to a fixed reference, varies in according to the wear of the clutch, - a selectively controlled motor for moving associated drive means which cooperate with at least one actuating member acting on said output member, - assistance means comprising at least an assistance spring which, by means of application means, exerts an assisting force on an assistance member which is movably mounted between an extreme rest position defined by r first stop means and an end support position defined by second abutment means and towards which said assistance force urges said assistance member, said assistance member being linked in displacement to said actuating member by by means of complementary connection means 25 allowing, unidirectionally, the adjustment of the relative position of the assistance member with respect to the actuating member for, depending on the second axial working position under load of the output member, compensate for the wear of the clutch. Advantageously, the actuator according to the invention is capable of being associated with any clutch, a simple clutch or a double clutch, and whatever the type, a clutch normally open as a clutch normally closed.
    [0008] Advantageously, the actuator is applicable to the control of a clutch normally open to cause a change of the disengaged state to the engaged state, as to that of a clutch normally closed to, conversely, cause the change of the state engaged to the disengaged state. Advantageously, the actuator comprises assistance means which deliver a maximum assistance force when the resisting force opposite the diaphragm of the clutch is maximum. In comparison with the actuators of the state of the art, the complementary connecting means forming the catching means by means of which adjustment is made to compensate for the wear of the clutch are not arranged downstream of the engine and assistance means and upstream of the output member, that is to say "in series". The actuator is able to compensate for the wear of the clutch when the resisting force which is opposed to it by the diaphragm of the clutch is substantially maximal, said catching taking place advantageously on a linear and increasing part of the curve. of the clutch corresponding to said maximum effort. Advantageously, the actuator according to the invention is adjustable as a function of the tolerances and the wear of the clutch, by simple and robust strategies, by selectively exerting, with the aid of the motor of the actuator, a controlled effort, said over-effort, which is greater than the effort normally required to engage advantageously, different retrofit strategies can be implemented, especially initially on the assembly line of the 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 during the life of the vehicle, the catch-up can be carried out periodically, at a given predetermined interval and sufficiently long so that a wear could have appeared or only when an effective wear is detected. The catch-up can still be performed under conditions that are favorable for obtaining a good repeatability of the wear detection, in particular conditions such as: an estimated engine or clutch temperature situated in a determined value range , a clutch rotation speed that is moderate or zero or, depending on the acoustic constraints or availability of the actuator, when the vehicle engine is stopped or rotating. Said over-effort generated by the motor of the actuator is for example obtained by progressively applying a current to the motor until a predetermined setpoint is reached or by communicating a certain kinetic energy (speed) to the motor up to a predefined engaged position. According to other characteristics of the invention: the output member occupies said second working position under load when the clutch of the normally open type is in the engaged state; the actuator is able to control a normally open clutch; the actuator is able to control a normally closed clutch; the actuator comprises a casing which, bearing the first and second abutment means, constitutes said fixed reference with respect to which the second axial working position varies; - Preloading means are arranged between said actuating member and said output member; said drive means comprise means for transforming a rotational movement of the motor into a translation movement transmitted to the actuating member. - The drive means associated with the motor comprise at least one ball screw and a carriage, the rotation drive of said ball screw by the motor causing the translational movement of said carriage 30 which is linked in displacement to the body actuation; - The actuating member is rotatably mounted about an axis of rotation; - The assistance member is rotatably mounted about the axis of rotation of the actuating member; the means of application to the assistance member of the assistance force delivered by the assistance spring consist of a roller and cam system; - The complementary connection means comprise non-return means which intervene to allow the adjustment of the relative position of the actuating member relative to the support member, unidirectionally; Said non-return means comprise at least one ratchet system; the first stop means limit, on the one hand, the stroke of the assistance member towards the extreme rest position and, on the other hand, the stroke of the output member towards the axial position of rest and of the actuating member 15 via the complementary connecting means and the assistance means, whereby the motor return stroke, in the direction corresponding to the return of the assistance member to the end position of rest and the output member to the axial position of rest, is a reduced stroke. The complementary connecting means of the assistance member and the actuating member comprise meshing means consisting of at least one first toothing carried by a first piece integral with the actuating member and a second toothing carried by a second piece which is movably connected and mounted movably with respect to said assist member; - The engine is controlled to selectively exert an over-effort under specified conditions, to allow to compensate for the wear of the clutch; the actuating member and / or the assistance member are mounted movably in translation; the actuator is capable of controlling a clutch, single or double, of normally open type, in particular a clutch fitted to a motor vehicle comprising a robotized gearbox.
    [0009] Other features and advantages of the invention will appear during the reading of the detailed description which follows for the understanding of which reference will be made to the appended drawings in which: FIGS. 1 and 2 are three-quarter views in perspective which represent an actuator for a clutch according to an embodiment of the invention and which respectively illustrate said actuator with and without its housing; - Figure 3 is a sectional view along a vertical orientation plane passing through the axis A of rotation, which represents the actuator according to Figures 1 and 2 without the housing; - Figure 4 is an end view in the axial direction which shows the actuator according to Figures 1 and 2, without the housing; - Figures 5 to 9 are axial sectional views which show the actuator according to Figures 1 to 4 and which illustrate different states and operating positions; - Figure 10 is a schematic view showing an alternative embodiment of the actuator according to the invention. In the remainder of the description and the claims, the terms "before" and "backward", "upper" and "lower", "right" and "left" will be used in a nonlimiting manner and in order to facilitate understanding thereof. with reference to the longitudinal, vertical and transverse orientations of the trihedron (L, V, T) shown in the figures and according to the definitions given in the description.
    [0010] The longitudinal orientation according to the trihedron (L, V, T) thus corresponds to a general axial direction of actuation of the actuator. FIGS. 1 and 2 show an actuator 10 for a clutch E (not shown in detail), in particular of a motor vehicle.
    [0011] The actuator 10 comprises a housing 12 having generally a parallelepipedal shape and within which are arranged at least a portion of the components.
    [0012] As illustrated in FIG. 1, at least a portion of an actuator output member 14 extends outside of said casing 12. Preferably, the actuator 10 comprises an associated protection bellows 15 said output member 14. The bellows 15 of protection is connected at one of its axial ends to one 16 of the faces of the casing 12, said vertical face 16 being traversed by said output member 14, and connected at the other end thereof to said member 14 out. The bellows 15 of protection surrounds the output member 14 and has a generally accordion shape for axially varying the length when the output member 14 is moved. Preferably, the output member 14 of the actuator is a rod whose free end is able to act on control means (not shown) of the clutch E. The control means of a clutch E are likely to be achieved in different ways depending on the applications. By way of non-limiting example, such mechanical control means comprise a fork which is pivotally mounted between its two ends, one of its ends being connected to the output member 14 in order to be selectively manipulated by the actuator 10 and the other of its ends being able to act on a disengagement stop to control, against the restoring force exerted by a diaphragm of the clutch E, a change of state of said clutch E. In a variant, the control means are of hydraulic type and comprise at least one transmitter on which said output member 14 acts and a receiver which, connected to the transmitter by hydraulic connection means, integrates a stop able to act on the clutch, in particular on the free end of the fingers of a diaphragm, in order to cause a change of state of the clutch between the engaged and disengaged states. The output member 14 is adapted to cause a change of state of the clutch E between at least one engaged state and a disengaged state, generally via such mechanical and / or hydraulic type control means. The output member 14 is movably mounted between at least a first axial position (P1) of rest illustrated in FIG. 6 and a second axial working position (P2) under load shown in FIG. 6. The second position (P2) axial working under load of the output member 14 varies depending on the wear of the clutch E, in particular the wear of the friction linings. The clutch E is in this embodiment a normally open clutch so that the output member 14 of the actuator occupies said second axial working position (P2) under load is in the engaged state. As and when wear occurs in the clutch E, the second axial position (P2) working under load of the output member 14 varies with respect to a fixed reference. The actuator 10 comprises a motor 18 which is selectively controlled to move associated driving means 20 more particularly visible in FIG. 2. Preferably, said fixed reference is constituted by a front vertical face 16 of the motor 18 which determines a reference position P illustrated in Figure 6 or alternatively constituted by the housing 12, in particular one vertical of its faces. Preferably, the motor 18 is a rotary motor, in particular but not exclusively a motor of the electric type. As illustrated in Figures 1 and 2, the motor 18 has in the upper part at least one connector 19 for its power supply. Preferably, the motor 18 is fixed to the casing 12, for example by means of screws (not shown) which cooperate with fastening tabs of the motor 18 which, as illustrated in FIGS. 1 and 2, are here four in number distributed circumferentially on the body of the motor 18. In a variant, the motor 18 is a linear motor.
    [0013] Alternatively, the motor 18 is moved by a force of the hydraulic or pneumatic type. To obtain good performance of the motor 18, such as a low response time or to avoid overheating, the motor 18 is advantageously used in a range of torque (or current) in which the motor has the best efficiency, where the efficiency in operation is optimal. The motor 18 generally has, beyond this range of torque (or current) for which the operation is optimal, a range in which the motor 18 has a lower performance but is still available to deliver an over-effort, generally to improve the acceleration of the engine or to spend a torque peak, more particularly in the invention to obtain a catch-up as explained in detail with reference to Figures 5 to 9. Advantageously, the motor 18 is able to be controlled to selectively exercise a -effort to allow the actuator 10 according to the invention to compensate for the wear of the clutch, said over-effort being applied under specified conditions, in particular according to one or more parameters. These parameters are for example a zero speed of the vehicle engine equipped with the clutch and the actuator 10, a given distance traveled by the vehicle, a given engine temperature, etc. Advantageously, the actuator 10 makes a retrofit if and only if there is wear of the clutch. The drive means 20 driven by the motor 18 cooperate with at least one actuating member 22 acting on said output member 14. The drive means 20 comprise means for transforming the movement, for example of transforming the rotational movement of the motor 18 into a translation movement which is transmitted to the actuating member 22. As illustrated in FIG. 2, the drive means 20 associated with the motor 18 comprise at least one ball screw 24 and a carriage 26, the rotation drive of said ball screw 24 by the motor 18 causing the translational displacement of said carriage 26. In a variant, the drive means 20 consist of other equivalent mechanical means, advantageously capable of performing a movement transformation, such as a screw-nut system, a system comprising a cam or at least one lever, a crank-handle system, a gear system. When the ball screw 24 is rotated by the motor 18, the carriage 26 moves axially in the longitudinal direction in one direction or the other depending on the direction of rotation, between at least one retracted position and an advanced position. . The carriage 26 comprises rolling means 28 which cooperate with an axial track 30, the rolling means 28 being for example formed by two rollers arranged in the upper part of the carriage 26 10 shaped as a "U". Preferably, the track 30 is formed by the underside of a part 31 which is integral with the casing 12, alternatively directly belonging to the casing 12. The carriage 26 is connected in displacement to the actuating member 22. The actuating member 22 is formed by a lever which is rotatably mounted about an axis A which extends transversely, said axis A being fixed and integral with the housing 12 of the actuator 10. The lever 22 forming the actuating member comprises two side plates which, from the axis A of rotation arranged at their lower end, 20 extend generally vertically towards the drive means and which, generally parallel, delimit transversely between them an area. Preferably, the carriage 26 comprises two drive arms 32 which extend transversely, projecting from the main body of the carriage 26, and which are capable of driving the actuating lever 22 by cooperation of shapes. Each drive arm 32 of the carriage 26 comprises a roller 33 intended to allow the rotation of the lever 22 about the axis A when the carriage 26, driven by the motor 18, moves axially 30 in translation. Preferably, each of the plates of the actuating lever 22 has an upper end shaped as "Y" whose upper limbs delimit between them a housing 34 inside which engages one of the arms 32 drive. Each housing 34 is delimited by a track in "V" with one part or the other of which cooperates the wheel 33 of the arm 32 in the direction of movement of the carriage 26. The actuator 10 comprises means 36 of assistance comprising at least one assistance spring 38 which, through means of application, exerts an assistance effort on a support member. The support member 40 is movably mounted between an extreme rest position defined by first stop means 42 and an end assistance position defined by second stop means 44 and towards which said support member 40 is solicited by the assistance effort. The assistance means 36 are housed in a housing 45 adjacent to the casing 12 of the actuator 10, said support spring 38 being in abutment with one end of its ends against a transverse vertical face of the housing 45 and urging, at the other rear of its ends, the support member 40 via said application means. The first and second stop means 42, 44 are advantageously carried by the casing 12 of the actuator 10. Preferably, the application means comprise at least one axial support 46 comprising at least one front part around which is mounted said assist spring 38 and a rear portion having an annular flange which, radially extending over a diameter greater than that of the front portion, has a bearing face 48. The rear end of the support spring 38 comes axially in abutment against said face 48 of the rear portion of the support 46, which rear portion comprises two wings 50 which extend axially rearwardly from said annular flange. The application means comprise a cam and roller system for transmitting the assistance force to the assistance member 40, said system comprising at least one application roller 52 and a reaction roller 54 which are connected to the support 46 by a transverse shaft 56 whose ends are axially locked in the wings 50. The support member 40 is rotatably mounted about the axis A of rotation. Preferably, said assistance member 40 is formed by a lever which, like the lever 22 forming the actuating member, is movably mounted at its lower end about the axis A of rotation. The lever 40 of assistance comprises a portion 58 forming a follower with which cooperates the roller 52 of application of the means 36 of assistance. The assisting lever 40 comprises a tab 60 which, projecting axially towards the rear, is intended to cooperate with the second means 44 of abutment. The assistance member 40 is linked in displacement to said actuating member 22 by means of complementary connection means which allow, in a unidirectional manner, the adjustment of the relative position of the support member 40 with respect to the actuating member 22 for, depending on the second axial position (P2) working under load of the output member 14, compensating for the wear of the clutch. The complementary connection means comprise at least a first connecting piece 62 which is integral with the lever 22 forming the actuating member. The first connecting piece 62 is arranged inside the space delimited transversely by the two plates forming said actuating lever 22. The first connecting piece 62 is intended to be linked by meshing with a second connecting piece 64, which second connecting piece 64 is linked in displacement with the support member 40. The first connecting piece 62 generally has an arc shape and has a concave lower face 65 oriented towards the axis A of rotation. A first toothing 66 is carried by the first connecting piece 62, here provided directly in said lower face 65, and a second toothing 68, complementary to the first toothing 66, is carried by said second connecting piece 64.
    [0014] Advantageously, the complementary connection means comprise non-return means which intervene to allow the adjustment of the relative position of the actuating member 22 relative to the support member 40, in a unidirectional manner.
    [0015] Preferably, said non-return means are formed by at least one ratchet system or other equivalent locking means. The second toothing 68 is carried by the second connecting piece 64 which is mounted movably in a housing of the support member 40, said second connecting piece 64 being biased by an elastic member 70, visible in FIG. to form such a ratchet system. The second connecting piece 64 is movably mounted between a retracted position and an engaged position of the second toothing 68 towards which said elastic member 70 automatically recalls said second connecting piece 64.
    [0016] The elastic member 70 is arranged between the bottom of the housing of the support member 40 and the second connecting piece 64, the member 70 urges the lower part so that, in the engaged position, the first and second set of teeth 66 and 68 cooperate together to link in motion the actuating member 22 and the assisting member 40.
    [0017] The retracted position allows a relative movement of the first toothing 66 with respect to the second toothing 68, and consequently of the actuating member 22 with respect to the support member 40. The retracted position is obtained when, the actuating member 22 and the assisting member 40 being rotated, the lug 60 of the assisting member 40 comes into contact with the second stop 44. Indeed, the first piece 62 of connection secured to the actuating lever 22 is in turn not blocked so that the first toothing 66 then applies, with a ramp effect, the second toothing 68 against the elastic member 70 in order to allow the displacement relative to each other of a given number of teeth corresponding to the wear of the clutch to be compensated.
    [0018] Preferably, the actuator 10 comprises means 72 for precharging which are arranged between the actuating member 22 and the output member 14. Advantageously, such preloading means 72 make it possible, in particular, to facilitate the connection of the actuator output member 14 with the clutch control means E. Advantageously, the preloading means 72 make it possible to make up any existing game. and keeping said output member 14 in contact with the control means of said clutch E.
    [0019] As illustrated in FIGS. 2 and 4, the preloading means 72 comprise at least one preloading spring 74, one end of which bears on an intermediate piece 76 which generally has a U-shaped stirrup shape. Preferably, the other end of the preloading spring 74 bears on a flange which axially comprises a spacer 78 at its rear. The intermediate piece 76 of the precharge means 72 is respectively linked in displacement with the outlet member 14. of the actuator 10 and the actuating member 22. The forward axial portion of the intermediate piece 76 is coupled to the rear axial end of the rod 14 and the rear axial portion, formed by two branches of the "U" which surround it from the outside, to the member 22 of actuation. The intermediate piece 76 comprises, for its connection with said actuating member 22, a stamped 80 on each of its branches. Said stamped member 80 penetrates transversely into a hole 82 that each plate comprises forming said actuating member 22. The preload spring 74 is thus interposed axially between the output member 14 and the actuator member 22 of the actuator 10. The operation of the actuator 10 according to the first embodiment of FIG. embodiment which has just been described with reference to FIGS. 1 to 4. FIG. 5 shows the components of the actuator 10 in the positions respectively occupied by each other when the actuator 10 is in the delivery state, prior to its assembly to associate it with a clutch E by connecting it to the control means of said clutch and its commissioning. In this state of delivery, the actuating member 22 occupies an extreme position, offset axially before, corresponding to the disengaged state and the retracted position of the carriage 26 of the drive means. The support member 40 is in a stable position, supported by means of its lug 60 against the second means 44 abutment. The assisting spring 38 has its maximum length and urges 10 through the cam and roller system 52, 54 the assist member 40 with maximum assist effort, which is illustrated by an arrow F on FIG. 5. As illustrated in FIG. 5, the spring 38 has axially its maximum length for which the force F is minimal, but the distance X of action with respect to the axis A then being maximum, the torque C assistance (corresponding to the product of the force F by the distance X) on the lever forming the support member 40 is also maximum thanks to which assistance is maximum. As compared with FIG. 5, the distance X of action with respect to the axis A is minimal in FIG. 7. The assistance spring 38 then occupies a stable position so that any risk of unexpected release of the spring 38 is deleted. The output member 14 of the actuator 10 is in an extreme axial forward position, beyond the disengaged state, for connecting without undue effort said member 14 to the control means, such as a fork, the Advantageously, the preloading spring 74 makes it possible to connect the output member 14 to the clutch control means without undue effort while, however, exerting a sufficient force to catch any existing game and maintain said output member 14. in contact with the control means of said clutch E. It is shown in Figure 6, the components of the actuator 10 in the positions respectively occupied by each other when the actuator 10 associated with a clutch E (in the new geared state) is used for the first time. The actuator 10 is controlled to act on the clutch E against the resisting force opposed thereto, and more particularly by the diaphragm of said clutch E, until an equilibrium is reached. 'established. The motor 18 rotates the ball screw 24 which causes the carriage 26 to move axially in a forward path in which the carriage 26 of the drive means 20 carries with it the actuating member 22 which pivots around it. the axis A of rotation in the clockwise direction, from the first stop means 42 to the second stop means 44. When the actuating member 22 is thus rotated, the assisting member 40 abuts against said second abutment means 44 remains stationary thereto, so that a relative movement then occurs between the member 22 of the abutment. actuation and the assistance member 40. The first toothing 66 of the first piece 62 connected to the actuating member 22 moves relative to the second toothing 68 carried by the second piece 64 which is pushed vertically towards the retracted position 20 against the member 70 elastic. During the displacement of the first piece 62, the first toothing 66 has for each tooth an inclined ramp-like face which will apply on the face of the second toothing 68 with which it cooperates a force greater than the restoring force exerted by the elastic member 70 to obtain the relative displacement of the actuating member 22 relative to the support member 40. Advantageously, the initial setting of the actuator 10 is carried out in a single movement of the actuating member 22 driven by the single motor 18, without the aid of the assistance means 36. The commissioning of the actuator 10 is carried out simply and quickly, in particular without requiring any training.
    [0020] Advantageously, the commissioning of the actuator 10 may be performed independently of the state of the engine of the motor vehicle equipped with the clutch E, including when said engine is stopped.
    [0021] The carriage 26 is then moved axially in the opposite direction by the motor 18 to occupy the position shown in FIG. 7, during this return path the actuating member 22 drives the assisting member 40 by meshing, which results from the cooperation of shapes between the first toothing 66 and the second toothing 68.
    [0022] The assistance member 40 leaves the end assistance position defined by the second stop means 44 and is returned by the drive means 20 moved by the motor 18 to the end rest position defined by the first means 42 of stop. During the return path, the support member 40 will axially compress the assistance spring 38.
    [0023] During the first disengagement, the components of the actuator 10 are initially in the positions shown in Figure 7. The motor 18 again rotates the ball screw 24 and in doing so causes the translation of the carriage 26 in the forward direction , said carriage 26 driving, via the arms 32 drive, the member 22 for actuating in rotation about the axis A. The support member 40 is also rotated about the axis A, accompanying the actuating member 22 in its movement and transmitting the assistance force delivered by the means 36 of assistance, including the spring 38 assistance.
    [0024] In the direction of travel to go, the support member 40 and the actuating member 22 are linked in motion by meshing, more precisely via the first and second sets of teeth 66 and 68 belonging to the complementary connection means. Indeed, the first and second connecting pieces 62 and 64, each carrying one of said first and second sets of teeth 66 and 68, then function as a ratchet system which together displaces the support member 40 and the member 22 together. unidirectional operation.
    [0025] Advantageously, the engine 18 is during this maneuver assisted by the assistance effort that delivers the assistance means 36 to the support member 40. In FIGS. 8 and 9, respectively in the engaged state and the disengaged state, the components of the actuator 10 are shown when the maximum wear compensation capacity of the clutch has been used. As illustrated in FIGS. 8 and 9, the maximum relative displacement between the first toothing 66 and the second toothing 68 of the complementary connection means 62 and 64 has been used.
    [0026] As shown in Figure 9, the movable assembly formed by the carriage 26 and the actuating member 22 occupy an extreme axial position delimited by the housing 12 located vis-à-vis. The embodiment which has just been described with reference to FIGS. 1 to 9 is given by way of nonlimiting example.
    [0027] FIG. 10 shows diagrammatically an alternative embodiment of the actuator 10 according to the invention. In comparison with the embodiment described in FIGS. 1 to 9, FIG. 10 illustrates a variant of the invention in which in particular the movements of the members are linear.
    [0028] Advantageously, the actuating member 22 and the assisting member 40 are movably mounted in translation. Preferably, an actuator according to this variant is able to control a clutch, single or double, of normally open type, in particular a clutch E equipping a motor vehicle having a robotized gearbox. Advantageously, the actuator is then for example able to act on the control means of the clutch E having hydraulic connection means. Said hydraulic connection means are for example arranged between the output member 14 of the actuator 10 and said clutch E.
    [0029] According to the applications, the hydraulic connection means comprise at least one emitter and a receiver, which are preferably respectively concentric type.
    [0030] The actuator 10 according to the invention is not limited to the control of a clutch E normally open, as described in the embodiment of Figures 1 to 9 or the variant of Figure 10. Advantageously, the body 14 output occupies said second position P2 working under load when the normally open type clutch E is in the engaged state. In variant not shown, the actuator 10 is able to control a clutch E normally closed. To do this, the actuating force must be a continually increasing force beyond the second axial position P2 working under load of the output member 14 and the wear of the clutch E cause the displacement of the second axial position P2 working under load of the output member 14 in the direction of actuation, that is to say beyond the second axial position P2 working under the previous load occupied by the member 14 Release.
    [0031] In such a variant, the output member 14 of the actuator 10 then occupies said second position P2 under load when the clutch E, of normally closed type, is in the disengaged state. FIG. 10 shows the first axial position (P1) of rest and the second position (P2) of working under load, respectively in new condition corresponding to the letter "N" and after wear of the clutch which corresponds to the letter "U".
    权利要求:
    Claims (15)
    [0001]
    REVENDICATIONS1. Actuator (10) for a clutch (E), in particular for a motor vehicle, comprising at least: an actuator output member (14) for acting on control means of said clutch (E) in order to cause a change in state of the clutch (E) between at least one engaged state and a disengaged state, said output member (14) being movably mounted between at least a first axial position (P1) and a second axial position (P2). load-operated workbench which, in relation to a fixed reference (12), varies according to the wear of the clutch (E), - a motor (18) selectively controlled to move associated drive means (20) which cooperate with at least one actuating member (22) acting on said output member (14), - assistance means (36) comprising at least one assist spring (38) which, via means (52, 54, 58) for application, exerts an assisting force on a support member (40) which is mob mounted between an extreme rest position defined by first abutment means (42) and an end assistance position defined by second (44) abutment means and towards which said assisting force urges said member (40) to assistance, said assist member (40) being movably connected to said actuating member (22) by means of complementary connecting means (62, 64) for unidirectionally adjusting the relative position of the means (40) for assisting with the actuating member (22) for, as a function of the second axial working position (P2) under load of the output member (14), compensating for wear clutch (E).
    [0002]
    2. Actuator according to claim 1, characterized in that the actuator (10) is adapted to control a clutch (E) normally open.
    [0003]
    3. Actuator according to one of claims 1 or 2, characterized in that the actuator (10) comprises a housing (12) which, bearing the first and second stop means (42, 44) constitutes said fixed reference relative at which the second axial position (P2) of work varies.
    [0004]
    4. Actuator according to any one of claims 1 to 3, characterized in that means (72) for precharging are arranged between said actuating member (22) and said member (14) output.
    [0005]
    5. Actuator according to any one of claims 1 to 4, characterized in that said means (20) for driving comprises means for transforming a rotational movement of the motor (18) into a translation movement transmitted to the actuating member (22).
    [0006]
    6. Actuator according to claim 4, characterized in that the drive means (20) associated with the motor (18) comprise at least one screw (24) ball and a carriage (26), the rotational drive of said screw (24) ball by the motor (18) causing the translational movement of said carriage (26) which is connected in motion to the member (22) actuation.
    [0007]
    7. Actuator according to any one of the preceding claims, characterized in that the actuating member (22) is rotatably mounted about an axis (A) of rotation.
    [0008]
    8. Actuator according to claim 7, characterized in that the member (40) of assistance is rotatably mounted about the axis (A) of rotation of the actuating member (22).
    [0009]
    9. Actuator according to any one of the preceding claims, characterized in that the means of application to the member (40) for assisting the assistance effort delivered by the spring (38) assistance are constituted by a roller and cam system (52, 54, 58).
    [0010]
    10. Actuator according to any one of the preceding claims, characterized in that the complementary means (62, 64) of connection comprise non-return means which intervene to allow the adjustment of the relative position of the member (22) d actuation relative to the support member (40) unidirectionally.
    [0011]
    11. Actuator according to claim 10, characterized in that said non-return means comprise at least one ratchet system.
    [0012]
    12. Actuator according to claim 1, characterized in that the first stop means (42) limit on the one hand the stroke of the member (40) assistance to the extreme rest position and, secondly, the stroke of the output member (14) towards the axial rest position (P1) and the actuating member (22) via the complementary connecting means (62, 64) and means (36) ), whereby the return stroke of the motor (18), in the direction corresponding to the return of the member (40) assistance to the end position of the rest and the output member to the position (P1) axial rest, is a reduced stroke.
    [0013]
    13. Actuator according to any one of the preceding claims, characterized in that the complementary means (62, 64) for connecting the member (40) of assistance and the member (22) actuation comprise means meshing consisting of at least one first toothing (66) carried by a first piece (62) integral with the actuating member (22) and a second toothing (68) carried by a second piece (64) which is linked in displacement and movably mounted relative to said support member (40).
    [0014]
    14. Actuator according to any one of the preceding claims, characterized in that the motor (18) is controlled to selectively exert an over-effort under specified conditions, in order to compensate for the wear of the clutch (E). .
    [0015]
    15. An actuator according to claim 1, characterized in that the member (22) for actuating and / or the member (40) of assistance are mounted movable in translation.
    类似技术:
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    同族专利:
    公开号 | 公开日
    KR20160001668A|2016-01-06|
    CN105221593B|2019-04-12|
    CN105221593A|2016-01-06|
    FR3022966B1|2016-06-10|
    DE102015110186A1|2015-12-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2564920A2|1984-05-28|1985-11-29|Valeo|Device for taking up wear for the control of a coupling device such as a clutch.|
    FR2790806A1|1999-03-08|2000-09-15|Valeo|CONTROL DEVICE FOR COUPLING MEANS WITH VARIABLE EFFORT MODERATION|
    WO2005028900A1|2003-09-24|2005-03-31|Aktiebolaget Skf|Actuator unit with incorporated device to compensate for wear on the clutch|
    FR2901587A1|2006-05-29|2007-11-30|Valeo Embrayages|Force compensation type push rod`s course adjustment actuator for controlling motor vehicle clutch, has course adjustment assembly displaced in translation by motor along adjustment stroke positions and driving unit drive strokes|WO2017207917A1|2016-06-03|2017-12-07|Valeo Embrayages|Actuator for a clutch, notably for a motor vehicle|DE2160278C2|1971-12-04|1982-04-08|Volkswagenwerk Ag, 3180 Wolfsburg|Self-adjusting actuator for a motor vehicle clutch|
    FR2753660B1|1996-09-25|1999-03-05|FRICTION CLUTCH WITH ELECTROMECHANICAL ACTUATOR, ESPECIALLY FOR A MOTOR VEHICLE|
    JP2003194101A|2001-12-27|2003-07-09|Exedy Corp|Clutch connecting and disconnecting device|US10704613B2|2016-07-20|2020-07-07|Gkn Automotive Ltd.|Actuator assembly and clutch assembly|
    JP6460413B2|2016-08-26|2019-01-30|トヨタ自動車株式会社|Lithium ion secondary battery and battery pack|
    KR20180069941A|2016-12-15|2018-06-26|현대자동차주식회사|Clutch actuator|
    CN108050169B|2017-12-03|2019-10-18|中国直升机设计研究所|A kind of manipulation apparatus for adjusting force|
    EP3755916B1|2018-06-13|2022-01-26|KA Group AG|Electrically driven clutch actuator|
    KR20200001800A|2018-06-28|2020-01-07|발레오 앙브라이아쥐|Clutch actuator|
    KR20200011722A|2018-07-25|2020-02-04|현대자동차주식회사|Wear Compensation Device of Clutch Actuator|
    KR102119711B1|2018-09-21|2020-06-05|현대트랜시스 주식회사|Clutch actuator|
    KR102106571B1|2018-09-21|2020-05-04|현대트랜시스 주식회사|Load compensating device of gear actuator|
    KR102168563B1|2018-11-29|2020-10-22|주식회사평화발레오|Wear compensation apparatus for clutch actuator|
    KR102209980B1|2019-07-31|2021-02-03|주식회사평화발레오|Clutch actuator for car|
    法律状态:
    2015-06-30| PLFP| Fee payment|Year of fee payment: 2 |
    2016-01-01| PLSC| Search report ready|Effective date: 20160101 |
    2016-07-08| PLFP| Fee payment|Year of fee payment: 3 |
    2017-06-30| PLFP| Fee payment|Year of fee payment: 4 |
    2018-06-27| PLFP| Fee payment|Year of fee payment: 5 |
    2020-06-30| PLFP| Fee payment|Year of fee payment: 7 |
    2021-06-30| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1456011A|FR3022966B1|2014-06-26|2014-06-26|ACTUATOR FOR A CLUTCH, IN PARTICULAR A MOTOR VEHICLE|FR1456011A| FR3022966B1|2014-06-26|2014-06-26|ACTUATOR FOR A CLUTCH, IN PARTICULAR A MOTOR VEHICLE|
    KR1020150089636A| KR20160001668A|2014-06-26|2015-06-24|Actuator for a clutch of a motor vehicle|
    DE102015110186.6A| DE102015110186A1|2014-06-26|2015-06-24|Actuator for a clutch, in particular a motor vehicle|
    CN201510362810.6A| CN105221593B|2014-06-26|2015-06-26|For clutch particularly for the actuator of the clutch of motor vehicles|
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