WO2008119911A1 - Clutch control device - Google Patents
Clutch control device Download PDFInfo
- Publication number
- WO2008119911A1 WO2008119911A1 PCT/FR2008/050339 FR2008050339W WO2008119911A1 WO 2008119911 A1 WO2008119911 A1 WO 2008119911A1 FR 2008050339 W FR2008050339 W FR 2008050339W WO 2008119911 A1 WO2008119911 A1 WO 2008119911A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- core
- stop
- actuator
- clutch
- latch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Ceased
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
Definitions
- the invention relates to a device for controlling a clutch, in particular for a motor vehicle, comprising an actuator with an electric motor connected by coupling means to a movable member of the clutch for opening and closing the clutch. clutch, this device also comprising means for locking the coupling means in a service position authorizing the control of the clutch by the actuator, and electromagnetic means for controlling the locking means.
- a device of this type is already described in patent application FR06.50248 of the applicant.
- this device is the annular spring or diaphragm of the clutch which brings the movable member of the clutch to the rest position in the event of power supply failure of the actuator, and it is a spring return link associated with a coupling connecting the actuator to the clutch which causes this coupling to go into a position where the actuator is decoupled from the clutch.
- the coupling used in this device comprises a toothed wheel movable by electromagnetic means in a service position where it provides the coupling between the actuator and the clutch, the toothed wheel being returned to a decoupling position by its return spring. when the electromagnetic means are no longer excited.
- the present invention is intended to improve this device by improving the decoupling of the actuator and the clutch in case of power failure, reducing the cost and size of the means used for this purpose and optimizing the use, size and power of the electromagnetic means controlling the coupling and decoupling of the actuator and the clutch.
- the invention also aims to accelerate the return of this device in the rest position or safety in case of power failure.
- a clutch control device in particular for a motor vehicle, comprising an electric motor actuator connected by coupling means to a movable member of the clutch to ensure the opening and closing of the clutch.
- clutch locking means of the coupling means in an active position allowing control of the clutch by the actuator, and electromagnetic means for controlling the locking means
- the electromagnetic control means comprise a core mobile associated with a return spring and axially displaceable inside a movable stop on which the locking means rest, this stop being movable by the core between a locking position and a release position of the locking means and the return spring urging the core from a service position to a rest position allowing the release of the means s of locking and decoupling of the actuator and the clutch, the stroke of the core from its operating position to its rest position comprising a first part where it has no action on the stop, and a second part where it moves the stop to its release position of the locking means, the core coming to hit the stop at the end of the first part of its race.
- the first part of the race of the core is an acceleration or momentum race during which the core acquires a kinetic energy that it transfers to the stop when it hits it, which allows to move the stop of its operating position despite the load exerted on it by the locking means which maintain the coupling means of the actuator and the clutch in the service position. Thanks to this transfer of kinetic energy, it is possible to associate a weaker return spring with the movable core of the electromagnetic control means and it is also possible to use means electromagnetic devices that are less powerful, less cumbersome and consume less energy.
- the decoupling of the actuator and the clutch is ensured more rapidly, which also makes it possible to reduce the clutch more rapidly to a predetermined safety position (corresponding, for example, to its closing).
- the locking means comprise a slidably guided latch in a passage of a casing perpendicular to the longitudinal axis of the actuator, the latch cooperating with a first end with the coupling means and by a second end with the stop traversed by the movable core.
- This lock comprises at its first end an axial locking tooth of the coupling means in an active position.
- the coupling means comprise an epicyclic gear train mounted in the casing between the output shaft of the actuator motor and a movable member of the clutch, which is gear comprising an outer ring (or a planet carrier), guided in rotation in the housing and immobilized by the first end of the lock.
- the outer cylindrical surface of this ring gear or the planet carrier comprises at least one receiving orifice of the axial tooth of the lock and this axial tooth and the orifice of the ring have, in a circumferential direction about the axis of the actuator, opposite faces which are respectively substantially radial and oblique with respect to a radial direction, the inclination of the oblique faces of the tooth and the orifice facilitating the ejection of the tooth out of the orifice for a direction of rotation of the crown.
- the second end of the lock comprises two bearing faces on the abutment mentioned above, a first bearing face being flat and perpendicular to the axis of the lock to be applied on a flat part of the outer cylindrical surface of the abutment, the second bearing face being inclined on the axis of the bolt forming an obtuse angle with the first bearing face and being intended to be applied on a complementary inclined face of one end of the stop so that this stop can push the lock in its locking position of the crown, when the stop is moved to its service position.
- this stop is tubular and contains a preload spring which is supported on a projection of the core and urges the stop to its operating position.
- the axial displacement of the abutment on the core is limited by means such as, for example, washers integral with the core, and by a shoulder of the casing on which the abutment is supported. operating position, this casing comprising a first cylindrical passage for receiving and guiding the abutment and a second cylindrical passage for receiving and guiding the bolt, the first cylindrical passage being parallel to the axis of the actuator, the second passage cylindrical being perpendicular to the axis of the actuator and connecting the first passage to said coupling means.
- the first part of the stroke of the core, up to the percussion on the stop, is equal to the stroke of the abutment between the aforementioned means integral with the core, and is at least equal to or greater than 70% of the total stroke of the core , to optimize the use of the return spring of the core and reduce the power, mass and cost of the electromagnetic control means.
- the second part of the race of the core is at least equal to the application length of the first bearing surface of the lock on the flat of the stop.
- this second part of the race of the core makes it possible to bring the inclined face of the abutment to the level of the inclined bearing face of the lock, the inclinations of these faces being determined so that the thrust of the latch on the stop brings the stop in the rest position, the latch being itself pushed into the inactive position by the outer ring of the epicyclic gear train of the coupling means.
- the sum of the first and the second part of the race of the core is substantially equal to the total stroke of the core, to optimize the use of the return spring of the core.
- the actuator comprises a unidirectional permanent brake, comprising a freewheel mechanism connected to the electric motor shaft of the actuator and to a constant torque brake connected to the housing of the actuator. actuator.
- This unidirectional permanent brake is advantageously mounted on one end of the shaft of the electric motor which is opposite to the end of this shaft connected to the coupling means, and it is integrated with the actuator.
- the action of this brake adds to the frictional torque in the electric motor of the actuator and keeps the load of the actuator in a given position, without the electric motor of the actuator is powered.
- This brake is particularly useful in the case where force compensation means are associated with the actuator to balance the force developed by the annular diaphragm of the clutch.
- FIG. 2 is a partial schematic cross sectional view along line N-II of Figure 1;
- FIGS. 3 to 8 are views corresponding to Figures 1 and 2 respectively and illustrate different operating positions of the device according to the invention
- - Figure 9 is a partial schematic view in axial section illustrating an additional feature of the device according to the invention.
- the device of FIGS. 1 and 2 is intended for the control of a clutch of a conventional type for a motor vehicle, in which a clutch disc carrying friction linings is clamped between a reaction plate driven in rotation by the crankshaft. an internal combustion engine, and a pressure plate biased towards the clutch closing position by an annular diaphragm.
- a clutch abutment makes it possible to act on this diaphragm for the opening of the clutch, this stop being itself moved between two extreme positions, corresponding to the opening and closing of the clutch respectively, by means associated with a clutch pedal or by a controlled actuator of any type. All these elements, which are well known to those skilled in the art and do not form part of the invention, are recalled here only to facilitate the understanding of the invention.
- the device of Figures 1 and 2 essentially comprises an actuator 10 with an electric motor whose output shaft 12 is connected by coupling means 14 to a clutch abutment (not shown) of a clutch of the aforementioned type.
- the coupling means 14 comprise an epicyclic gear train gearbox housed in a housing 16 on which the actuator 10 is fixed.
- the epicyclic gear train of the coupling means 14 comprises an outer ring 18 of cylindrical shape (or a planet carrier) housed in a bore of the casing 16 and which must be immobilized in rotation in this bore so that the rotation the output shaft 12 of the motor is transmitted by means of movement transformation to the disengagement stop.
- the outer ring 18 is free to rotate in the bore of the housing 16, no torque transmission is ensured between the shaft 12 and the clutch release bearing, the latter then being completely decoupled from the actuator 10.
- the immobilization in rotation of the ring gear 18 in the casing 16 is ensured by a cylindrical lock 20 which is guided in translation in a cylindrical passage 22 of the casing 16 in a direction perpendicular to the axis of rotation of the shaft 12 and the ring 18, this latch 20 cooperating with the ring 18 by a first end having an axial tooth 24 intended to be engaged in a hole or a corresponding slot 25 of the ring 18 to immobilize it in rotation.
- the other end of the latch 22 bears against a mobile stop 26 of cylindrical shape, for example, which is slidably mounted in a bore 28 of the housing 16 whose axis is parallel to the axis of rotation of the shaft 12 and perpendicular to the bolt axis 20.
- the abutment 26 is traversed axially by a cylindrical rod 30 integral with the movable core 32 of an electromagnet 34 whose body is screwed into the open end of the bore 28, the electromagnet 34 thus being parallel to the actuator 10 and adjacent thereto.
- the free end of the cylindrical rod 30 carries a washer 36 which is a means for moving the movable stop 26 to a rest position when the electromagnet 34 is not supplied with electrical energy.
- the end of the core 32 opposite the abutment 26 is associated with a nonlinear return spring 38, for example of conical helical shape which is supported by one end on the body of the electromagnet 34 and by its another end on the core 32, to push the latter in the direction opposite to the stop 26.
- the displacement of the core 32 in this direction is limited by a circlip 40 integral with the rod 30 and coming to rest on the end of the body 34 of the electromagnet screwed into the bore 28.
- a washer 42 for example of rubber, is mounted on this end of the body of the electromagnet to dampen the shock of the circlip 40 at the end of the race.
- the circlip 40 is also intended to be applied via a washer 44 on the corresponding end of the stop 26 to maintain this stop in a service position when the electromagnet 34 is supplied with electrical energy, this operating position is also defined by pressing the abutment 26 on a shoulder 46 of the bore 28, the side opposite to the electromagnet.
- the stop 26, which is traversed freely by the cylindrical rod 30, contains a preload spring 48, one end of which bears on the washer 44 and the aforementioned circlip 40 and whose opposite end rests on a shoulder of the axial passage. of this stop in which the rod 30 extends, for purposes which will be explained below.
- the end of the lock 20 which is in contact with the stop 26, comprises two bearing faces on this stop, a first bearing face 50 being flat and perpendicular to the axis of the lock and being applied on a flat surface 52 the outer cylindrical surface of the abutment 26, the second bearing surface 54 of the latch 20 being oblique with respect to the axis of the latch and being intended to be applied on a corresponding oblique face 56 of the abutment 26.
- the first plane bearing face 50 of the latch 20 is formed on the side of the latch which is opposite the electromagnet 34, while the flat portion 52 of the latch is formed on the side of the abutment 26 which is located on the side of the electromagnet 34.
- the inclined bearing face 54 of the lock is formed on the latch side which is located on the side of the electromagnet 34, while the inclined bearing face 56 of the stop 26 is formed on the side of this stop which is located opposite the electromagnet 34.
- These inclined faces 54 and 56 of the latch and the stop are cylindrical surfaces while the two other bearing faces 50 and 52 of the latch and the stop are planar.
- the axial tooth 24 of the latch 20 which is engaged in the orifice or the slot 25 of the ring 18, comprises a substantially radial face and an opposite face oblique with respect to a radial direction, the radial face of the tooth 24 being applied on a radial wall of the orifice 25 while the oblique face of the tooth 24 is applied to an oblique wall corresponding to the orifice 25 so that the rotation of the ring 18 in the direction of clockwise in Figure 2 about the axis of the shaft 12 tends to push the tooth 24 and therefore the lock 20 to the top on this figure.
- the walls of the orifice 25 are flat or involute in a circle.
- the ring gear 18 may comprise two diametrically opposite orifices or slots 25 or a different number of these orifices or slots regularly distributed over the periphery of the ring gear 18.
- the operation of this device is as follows:
- the core 32 When the electromagnet 34 is supplied with electrical energy, the core 32 is moved to the right in FIG. 1 until it abuts inside the body of the electromagnet, the movable stop 26 being then pushed to the right by the circlip 40 and the washer 44 and bearing on the shoulder 46 of the bore 28.
- the movable core 32 is returned to its rest position by its return spring 38 as shown in FIG. 3, the circlip 40 carried by the rod 30 and the washer 44 deviates from the movable stop 26 which remains stuck in the bore 28 by the latch 20, and the end washer 36 carried by the end of the rod 30 is close to the movable stop 26 until it hits the latter with a certain speed in the position shown in FIG. 3.
- the restoring force developed by the spring 38 is determined to follow the force curve of the electromagnet with a the most constant distance possible.
- the kinetic energy that is applied by the washer 36 to the movable stop 26 is sufficient to move it to the left in FIG. 3 until the flat portion 52 of this movable stopper escapes from the flat bearing face 50 of the lock 20, the connection angle of the bearing faces 50 and 54 of the lock then being at the beginning of the inclined face 56 of the movable stop and starting to slide on this inclined face (position shown in Figure 5).
- the sliding of the end of the lock 20 on the inclined face 56 of the movable stop results from the thrust exerted by the inclined wall of the orifice 25 of the ring 18 on the inclined face of the axial tooth 24 of the lock 20 and has the effect of pushing the movable stop to the left in Figure 5, to the full unlocking position shown in Figure 7.
- the movable stop 26 In this position, the movable stop 26 is brought to the maximum of the body of the electromagnet, and the lock 20 has been pushed upward enough so that its axial tooth 24 is disengaged from the orifice 25 of the ring 18 and releases the latter, which is then free to rotate and decouples the actuator 10 of the clutch.
- the movable core 32 of the electromagnet is in its rest position, the circlip 40 being applied to the damping washer 42 by the end of the body of the electromagnet 34.
- the preload spring 48 of the movable stop 26 is compressed in this position and thus urges this stop to the right in FIG. 7, so that the inclined face 56 of the abutment 20 remains in abutment on the inclined face 54 of the latch 20, which makes it possible to maintain the angular positions of the abutment 26 and the latch 20 in their respective guides.
- the first part of the return stroke of the movable core 32 which corresponds to the distance traveled by the end washer 36 between the position shown in FIG. 1 and that represented in FIG. 3, is equal to the travel of the stop 26 between the circlip 40 and the washer 36 and is preferably relatively large compared to the total stroke of the core 32, to optimize the use of the return spring 38 of the movable core and thus reduce the power, mass and cost
- this first part of the travel of the mobile core may have a value greater than 70% of the total travel of the mobile core.
- the second part of this stroke corresponds to the distance that the movable stop 26 must travel to pass from its locking position shown in Figures 1 and 3 to its position in Figure 5 where it begins to allow the movement of the lock 20 upwards.
- This second part of the stroke of the core 32 is approximately equal to the length of application of the flat bearing face 50 of the lock 20 on the flat part 52 of the abutment 26.
- This second portion of travel is advantageously reduced and for example less than 30% of the total stroke of the movable core 32 to reduce the unlocking energy and therefore the size of the electromagnet. It is also preferable that the sum of the first part and the second part of the stroke of the core 32 represents all or almost all of the stroke of this core, for optimum use of the return spring 38 of this core . At the end of the second part of the stroke of the movable core, it is no longer the return spring 38 which acts on the movable stop 26 to move it towards its actual unlocking position shown in Figure 7, it is the latch 20 which is itself pushed up by the torque applied to the ring 18, and which will finish moving the movable stop 26 in its position unlocking.
- the movable core 32 When the electromagnet 34 is again supplied with electrical energy, the movable core 32 is biased from its rest position shown in FIG. 7 to its locking position shown in FIG. 1, but the movable stop 26 is blocked by the lock. 20 and can not move to its position of Figure 1.
- the electric motor of the actuator 10 When the electric motor of the actuator 10 is itself supplied with electrical energy, it rotates the ring 18 inside the housing until an orifice 25 of this ring is aligned with the tooth 24 of the lock 20, the movable stop 26 can then push the lock 20 down and return to its locking position shown in Figures 1 and 2.
- This brake 60 is advantageously mounted on the end of the shaft 12 opposite to that connected to the coupling means 14, the brake being mounted inside the cover of the actuator 10 and comprising a freewheel mechanism 62 connecting the end of the shaft 12 to a brake disc 64 clamped between fittings 66 biased towards one another by springs 68 bearing on fixed parts of the actuator 10, these fittings 66 being themselves immobilized in rotation by means of pins or the like 70 integral with the housing of the actuator.
- the brake 60 associated with the output shaft 12 of the electric motor of the actuator avoids continuously supplying the motor to maintain the position of the actuator load.
- the integration of this brake in the actuator reduces the bulk and facilitates assembly.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
L'invention concerne un dispositif de commande d'un embrayage, en particulier pour véhicule automobile, comprenant un actionneur à moteur électrique relié par des moyens de couplage à un organe mobile de l'embrayage pour assurer l'ouverture et la fermeture de l'embrayage, ce dispositif comprenant également des moyens de verrouillage des moyens de couplage dans une position de service autorisant la commande de l'embrayage par l'actionneur, et des moyens électromagnétiques de commande des moyens de verrouillage. The invention relates to a device for controlling a clutch, in particular for a motor vehicle, comprising an actuator with an electric motor connected by coupling means to a movable member of the clutch for opening and closing the clutch. clutch, this device also comprising means for locking the coupling means in a service position authorizing the control of the clutch by the actuator, and electromagnetic means for controlling the locking means.
Un dispositif de ce type est déjà décrit dans la demande de brevet FR06.50248 de la déposante. Dans ce dispositif, c'est le ressort ou diaphragme annulaire de l'embrayage qui ramène l'organe mobile de l'embrayage en position de repos en cas de coupure de l'alimentation électrique de l'actionneur, et c'est un ressort de rappel associé à un accouplement reliant l'actionneur à l'embrayage qui fait passer cet accouplement dans une position où l'actionneur est découplé de l'embrayage. L'accouplement utilisé dans ce dispositif comprend une roue dentée déplaçable par des moyens électromagnétiques dans une position de service où elle assure le couplage entre l'actionneur et l'embrayage, cette roue dentée étant ramenée dans une position de découplage par son ressort de rappel quand les moyens électromagnétiques ne sont plus excités.A device of this type is already described in patent application FR06.50248 of the applicant. In this device, it is the annular spring or diaphragm of the clutch which brings the movable member of the clutch to the rest position in the event of power supply failure of the actuator, and it is a spring return link associated with a coupling connecting the actuator to the clutch which causes this coupling to go into a position where the actuator is decoupled from the clutch. The coupling used in this device comprises a toothed wheel movable by electromagnetic means in a service position where it provides the coupling between the actuator and the clutch, the toothed wheel being returned to a decoupling position by its return spring. when the electromagnetic means are no longer excited.
La présente invention a notamment pour but de perfectionner ce dispositif en améliorant le découplage de l'actionneur et de l'embrayage en cas de coupure de l'alimentation électrique, en réduisant le coût et l'encombrement des moyens utilisés à cet effet et en optimisant l'utilisation, l'encombrement et la puissance des moyens électromagnétiques commandant le couplage et le découplage de l'actionneur et de l'embrayage. L'invention a également pour but d'accélérer le retour de ce dispositif en position de repos ou de sécurité en cas de coupure de l'alimentation électrique.The present invention is intended to improve this device by improving the decoupling of the actuator and the clutch in case of power failure, reducing the cost and size of the means used for this purpose and optimizing the use, size and power of the electromagnetic means controlling the coupling and decoupling of the actuator and the clutch. The invention also aims to accelerate the return of this device in the rest position or safety in case of power failure.
Elle propose à cet effet un dispositif de commande d'un embrayage, en particulier pour véhicule automobile, comprenant un actionneur à moteur électrique relié par des moyens de couplage à un organe mobile de l'embrayage pour assurer l'ouverture et la fermeture de l'embrayage, des moyens de verrouillage des moyens de couplage dans une position active autorisant la commande de l'embrayage par l'actionneur, et des moyens électromagnétiques de commande des moyens de verrouillage, caractérisé en ce que les moyens électromagnétiques de commande comprennent un noyau mobile associé à un ressort de rappel et axialement déplaçable à l'intérieur d'une butée mobile sur laquelle s'appuient les moyens de verrouillage, cette butée étant déplaçable par le noyau entre une position de blocage et une position de libération des moyens de verrouillage et le ressort de rappel sollicitant le noyau d'une position de service vers une position de repos permettant la libération des moyens de verrouillage et le découplage de l'actionneur et de l'embrayage, la course du noyau de sa position de service vers sa position de repos comprenant une première partie où il n'a pas d'action sur la butée, et une seconde partie où il déplace la butée vers sa position de libération des moyens de verrouillage, le noyau venant percuter la butée à la fin de la première partie de sa course.It proposes for this purpose a clutch control device, in particular for a motor vehicle, comprising an electric motor actuator connected by coupling means to a movable member of the clutch to ensure the opening and closing of the clutch. clutch, locking means of the coupling means in an active position allowing control of the clutch by the actuator, and electromagnetic means for controlling the locking means, characterized in that the electromagnetic control means comprise a core mobile associated with a return spring and axially displaceable inside a movable stop on which the locking means rest, this stop being movable by the core between a locking position and a release position of the locking means and the return spring urging the core from a service position to a rest position allowing the release of the means s of locking and decoupling of the actuator and the clutch, the stroke of the core from its operating position to its rest position comprising a first part where it has no action on the stop, and a second part where it moves the stop to its release position of the locking means, the core coming to hit the stop at the end of the first part of its race.
Dans le dispositif selon l'invention, la première partie de la course du noyau est une course d'accélération ou d'élan au cours de laquelle le noyau acquiert une énergie cinétique qu'il transfère à la butée quand il la percute, ce qui permet d'écarter la butée de sa position de service malgré la charge exercée sur elle par les moyens de verrouillage qui maintiennent les moyens de couplage de l'actionneur et de l'embrayage en position de service. Grâce à ce transfert d'énergie cinétique, on peut associer un ressort de rappel moins puissant au noyau mobile des moyens électromagnétiques de commande et on peut aussi utiliser des moyens électromagnétiques qui sont moins puissants, moins encombrants et qui consomment moins d'énergie.In the device according to the invention, the first part of the race of the core is an acceleration or momentum race during which the core acquires a kinetic energy that it transfers to the stop when it hits it, which allows to move the stop of its operating position despite the load exerted on it by the locking means which maintain the coupling means of the actuator and the clutch in the service position. Thanks to this transfer of kinetic energy, it is possible to associate a weaker return spring with the movable core of the electromagnetic control means and it is also possible to use means electromagnetic devices that are less powerful, less cumbersome and consume less energy.
Corollairement, le découplage de l'actionneur et de l'embrayage est assuré de façon plus rapide, ce qui permet aussi de ramener plus rapidement l'embrayage dans une position prédéterminée de sécurité (correspondant par exemple à sa fermeture).As a corollary, the decoupling of the actuator and the clutch is ensured more rapidly, which also makes it possible to reduce the clutch more rapidly to a predetermined safety position (corresponding, for example, to its closing).
Selon une autre caractéristique de l'invention, les moyens de verrouillage comprennent un verrou guidé en coulissement dans un passage d'un carter perpendiculaire à l'axe longitudinal de l'actionneur, le verrou coopérant par une première extrémité avec les moyens de couplage et par une seconde extrémité avec la butée traversée par le noyau mobile.According to another characteristic of the invention, the locking means comprise a slidably guided latch in a passage of a casing perpendicular to the longitudinal axis of the actuator, the latch cooperating with a first end with the coupling means and by a second end with the stop traversed by the movable core.
Ce verrou comprend à sa première extrémité une dent axiale d'immobilisation des moyens de couplage dans une position active.This lock comprises at its first end an axial locking tooth of the coupling means in an active position.
Dans un mode de réalisation préféré de l'invention, les moyens de couplage comprennent un train d'engrenages épicycloïdal monté dans le carter entre l'arbre de sortie du moteur de l'actionneur et un organe mobile de l'embrayage, ce train d'engrenages comportant une couronne extérieure (ou un porte-satellites), guidée en rotation dans le carter et immobilisée par la première extrémité du verrou. La surface cylindrique extérieure de cette couronne ou du porte- satellites comprend au moins un orifice de réception de la dent axiale du verrou et cette dent axiale et l'orifice de la couronne ont, dans une direction circonférentielle autour de l'axe de l'actionneur, des faces opposées qui sont respectivement sensiblement radiales et obliques par rapport à une direction radiale, l'inclinaison des faces obliques de la dent et de l'orifice facilitant l'éjection de la dent hors de l'orifice pour un sens de rotation de la couronne.In a preferred embodiment of the invention, the coupling means comprise an epicyclic gear train mounted in the casing between the output shaft of the actuator motor and a movable member of the clutch, which is gear comprising an outer ring (or a planet carrier), guided in rotation in the housing and immobilized by the first end of the lock. The outer cylindrical surface of this ring gear or the planet carrier comprises at least one receiving orifice of the axial tooth of the lock and this axial tooth and the orifice of the ring have, in a circumferential direction about the axis of the actuator, opposite faces which are respectively substantially radial and oblique with respect to a radial direction, the inclination of the oblique faces of the tooth and the orifice facilitating the ejection of the tooth out of the orifice for a direction of rotation of the crown.
La seconde extrémité du verrou comprend deux faces d'appui sur la butée précitée, une première face d'appui étant plane et perpendiculaire à l'axe du verrou pour s'appliquer sur un méplat de la surface cylindrique extérieure de la butée, la seconde face d'appui étant inclinée sur l'axe du verrou en formant un angle obtus avec la première face d'appui et étant destinée à s'appliquer sur une face inclinée complémentaire d'une extrémité de la butée afin que cette butée puisse repousser le verrou dans sa position de verrouillage de la couronne, quand la butée est déplacée vers sa position de service.The second end of the lock comprises two bearing faces on the abutment mentioned above, a first bearing face being flat and perpendicular to the axis of the lock to be applied on a flat part of the outer cylindrical surface of the abutment, the second bearing face being inclined on the axis of the bolt forming an obtuse angle with the first bearing face and being intended to be applied on a complementary inclined face of one end of the stop so that this stop can push the lock in its locking position of the crown, when the stop is moved to its service position.
Avantageusement, cette butée est tubulaire et contient un ressort de précharge qui s'appuie sur une saillie du noyau et sollicite la butée vers sa position de service.Advantageously, this stop is tubular and contains a preload spring which is supported on a projection of the core and urges the stop to its operating position.
Cela permet de maintenir toujours la butée en contact avec la seconde extrémité du verrou et donc de conserver une orientation déterminée de la butée et du verrou autour de leurs axes respectifs.This makes it possible to keep the abutment always in contact with the second end of the lock and thus to maintain a determined orientation of the abutment and the lock around their respective axes.
Selon encore une autre caractéristique de l'invention, le déplacement axial de la butée sur le noyau est limité par des moyens, tels par exemple que des rondelles, solidaires du noyau, et par un épaulement du carter sur lequel s'appuie la butée en position de service, ce carter comprenant un premier passage cylindrique de réception et de guidage de la butée et un second passage cylindrique de réception et de guidage du verrou, le premier passage cylindrique étant parallèle à l'axe de l'actionneur, le second passage cylindrique étant perpendiculaire à l'axe de l'actionneur et reliant le premier passage aux moyens de couplage précités.According to yet another characteristic of the invention, the axial displacement of the abutment on the core is limited by means such as, for example, washers integral with the core, and by a shoulder of the casing on which the abutment is supported. operating position, this casing comprising a first cylindrical passage for receiving and guiding the abutment and a second cylindrical passage for receiving and guiding the bolt, the first cylindrical passage being parallel to the axis of the actuator, the second passage cylindrical being perpendicular to the axis of the actuator and connecting the first passage to said coupling means.
La première partie de la course du noyau, jusqu'à la percussion sur la butée, est égale à la course de la butée entre les moyens précités solidaires du noyau, et est au moins égale ou supérieure à 70 % de la course totale du noyau, pour optimiser l'utilisation du ressort de rappel du noyau et réduire la puissance, la masse et le coût des moyens électromagnétiques de commande.The first part of the stroke of the core, up to the percussion on the stop, is equal to the stroke of the abutment between the aforementioned means integral with the core, and is at least equal to or greater than 70% of the total stroke of the core , to optimize the use of the return spring of the core and reduce the power, mass and cost of the electromagnetic control means.
La deuxième partie de la course du noyau est au moins égale à la longueur d'application de la première face d'appui du verrou sur le méplat de la butée. Ainsi, cette deuxième partie de la course du noyau permet d'amener la face inclinée de la butée au niveau de la face d'appui inclinée du verrou, les inclinaisons de ces faces étant déterminées pour que la poussée du verrou sur la butée ramène la butée en position de repos, le verrou étant lui-même repoussé en position inactive par la couronne extérieure du train d'engrenages épicycloïdal des moyens de couplage. Avantageusement, la somme de la première et de la deuxième partie de la course du noyau est sensiblement égale à la course totale du noyau, pour optimiser l'utilisation du ressort de rappel du noyau.The second part of the race of the core is at least equal to the application length of the first bearing surface of the lock on the flat of the stop. Thus, this second part of the race of the core makes it possible to bring the inclined face of the abutment to the level of the inclined bearing face of the lock, the inclinations of these faces being determined so that the thrust of the latch on the stop brings the stop in the rest position, the latch being itself pushed into the inactive position by the outer ring of the epicyclic gear train of the coupling means. Advantageously, the sum of the first and the second part of the race of the core is substantially equal to the total stroke of the core, to optimize the use of the return spring of the core.
Selon encore une autre caractéristique de l'invention, l'actionneur comprend un frein permanent unidirectionnel, comportant un mécanisme de roue libre relié à l'arbre du moteur électrique de l'actionneur et à un frein de couple constant lié au boîtier de l'actionneur.According to yet another characteristic of the invention, the actuator comprises a unidirectional permanent brake, comprising a freewheel mechanism connected to the electric motor shaft of the actuator and to a constant torque brake connected to the housing of the actuator. actuator.
Ce frein permanent unidirectionnel est avantageusement monté sur une extrémité de l'arbre du moteur électrique qui est opposée à l'extrémité de cet arbre reliée aux moyens de couplage, et il est intégré à l'actionneur. L'action de ce frein s'ajoute aux couples de frottement dans le moteur électrique de l'actionneur et permet de maintenir la charge de l'actionneur dans une position donnée, sans que le moteur électrique de l'actionneur soit alimenté. Ce frein est particulièrement utile dans le cas où des moyens de compensation d'effort sont associés à l'actionneur pour équilibrer la force développée par le diaphragme annulaire de l'embrayage. L'invention sera mieux comprise et d'autres caractéristiques, détails et avantages de celle-ci apparaîtront plus clairement à la lecture de la description qui suit, faite à titre d'exemple en référence aux dessins annexés dans lesquels : - la figure 1 est une vue schématique partielle en coupe axiale d'un dispositif de commande selon l'invention ;This unidirectional permanent brake is advantageously mounted on one end of the shaft of the electric motor which is opposite to the end of this shaft connected to the coupling means, and it is integrated with the actuator. The action of this brake adds to the frictional torque in the electric motor of the actuator and keeps the load of the actuator in a given position, without the electric motor of the actuator is powered. This brake is particularly useful in the case where force compensation means are associated with the actuator to balance the force developed by the annular diaphragm of the clutch. The invention will be better understood and other characteristics, details and advantages thereof will appear more clearly on reading the description which follows, given by way of example with reference to the accompanying drawings, in which: FIG. a partial schematic view in axial section of a control device according to the invention;
- la figure 2 est une vue schématique partielle en coupe transversale selon la ligne N-Il de la figure 1 ;- Figure 2 is a partial schematic cross sectional view along line N-II of Figure 1;
- les figures 3 à 8 sont des vues correspondant aux figures 1 et 2 respectivement et illustrent différentes positions de fonctionnement du dispositif selon l'invention ; - la figure 9 est une vue schématique partielle en coupe axiale illustrant une caractéristique supplémentaire du dispositif selon l'invention.- Figures 3 to 8 are views corresponding to Figures 1 and 2 respectively and illustrate different operating positions of the device according to the invention; - Figure 9 is a partial schematic view in axial section illustrating an additional feature of the device according to the invention.
Le dispositif des figures 1 et 2 est destiné à la commande d'un embrayage d'un type classique pour véhicule automobile, dans lequel un disque d'embrayage portant des garnitures de friction est serré entre un plateau de réaction entraîné en rotation par le vilebrequin d'un moteur à combustion interne, et un plateau de pression sollicité vers la position de fermeture de l'embrayage par un diaphragme annulaire. Une butée de débrayage permet d'agir sur ce diaphragme pour l'ouverture de l'embrayage, cette butée étant elle-même déplacée entre deux positions extrêmes, correspondant à l'ouverture et à la fermeture de l'embrayage respectivement, par des moyens associés à une pédale d'embrayage ou par un actionneur commandé d'un type quelconque. Tous ces éléments, qui sont bien connus de l'homme du métier et ne font pas partie de l'invention, ne sont rappelés ici que pour faciliter la compréhension de l'invention.The device of FIGS. 1 and 2 is intended for the control of a clutch of a conventional type for a motor vehicle, in which a clutch disc carrying friction linings is clamped between a reaction plate driven in rotation by the crankshaft. an internal combustion engine, and a pressure plate biased towards the clutch closing position by an annular diaphragm. A clutch abutment makes it possible to act on this diaphragm for the opening of the clutch, this stop being itself moved between two extreme positions, corresponding to the opening and closing of the clutch respectively, by means associated with a clutch pedal or by a controlled actuator of any type. All these elements, which are well known to those skilled in the art and do not form part of the invention, are recalled here only to facilitate the understanding of the invention.
Le dispositif des figures 1 et 2 comprend essentiellement un actionneur 10 à moteur électrique dont l'arbre de sortie 12 est relié par des moyens de couplage 14 à une butée d'embrayage (non représentée) d'un embrayage du type précité.The device of Figures 1 and 2 essentially comprises an actuator 10 with an electric motor whose output shaft 12 is connected by coupling means 14 to a clutch abutment (not shown) of a clutch of the aforementioned type.
Les moyens de couplage 14 comprennent dans cet exemple un réducteur à train d'engrenages épicycloïdal, logé dans un carter 16 sur lequel est fixé l'actionneur 10.In this example, the coupling means 14 comprise an epicyclic gear train gearbox housed in a housing 16 on which the actuator 10 is fixed.
Le train d'engrenages épicycloïdal des moyens de couplage 14 comprend une couronne extérieure 18, de forme cylindrique, (ou un porte- satellites), logée dans un alésage du carter 16 et qui doit être immobilisée en rotation dans cet alésage pour que la rotation de l'arbre 12 de sortie du moteur soit transmise par des moyens de transformation de mouvement à la butée de débrayage. Lorsque la couronne extérieure 18 est libre en rotation dans l'alésage du carter 16, aucune transmission de couple n'est assurée entre l'arbre 12 et la butée de débrayage, celle-ci étant alors totalement découplée de l'actionneur 10.The epicyclic gear train of the coupling means 14 comprises an outer ring 18 of cylindrical shape (or a planet carrier) housed in a bore of the casing 16 and which must be immobilized in rotation in this bore so that the rotation the output shaft 12 of the motor is transmitted by means of movement transformation to the disengagement stop. When the outer ring 18 is free to rotate in the bore of the housing 16, no torque transmission is ensured between the shaft 12 and the clutch release bearing, the latter then being completely decoupled from the actuator 10.
L'immobilisation en rotation de la couronne 18 dans le carter 16 est assurée par un verrou cylindrique 20 qui est guidé en translation dans un passage cylindrique 22 du carter 16 dans une direction perpendiculaire à l'axe de rotation de l'arbre 12 et de la couronne 18, ce verrou 20 coopérant avec la couronne 18 par une première extrémité comportant une dent axiale 24 destinée à être engagée dans un orifice ou une fente correspondante 25 de la couronne 18 pour l'immobiliser en rotation. L'autre extrémité du verrou 22 est en appui sur une butée mobile 26 de forme par exemple cylindrique, qui est montée coulissante dans un alésage 28 du carter 16 dont l'axe est parallèle à l'axe de rotation de l'arbre 12 et perpendiculaire à l'axe du verrou 20.The immobilization in rotation of the ring gear 18 in the casing 16 is ensured by a cylindrical lock 20 which is guided in translation in a cylindrical passage 22 of the casing 16 in a direction perpendicular to the axis of rotation of the shaft 12 and the ring 18, this latch 20 cooperating with the ring 18 by a first end having an axial tooth 24 intended to be engaged in a hole or a corresponding slot 25 of the ring 18 to immobilize it in rotation. The other end of the latch 22 bears against a mobile stop 26 of cylindrical shape, for example, which is slidably mounted in a bore 28 of the housing 16 whose axis is parallel to the axis of rotation of the shaft 12 and perpendicular to the bolt axis 20.
La butée 26 est traversée axialement par une tige cylindrique 30 solidaire du noyau mobile 32 d'un électro-aimant 34 dont le corps est monté par vissage dans l'extrémité ouverte de l'alésage 28, l'électro-aimant 34 étant ainsi parallèle à l'actionneur 10 et voisin de celui-ci.The abutment 26 is traversed axially by a cylindrical rod 30 integral with the movable core 32 of an electromagnet 34 whose body is screwed into the open end of the bore 28, the electromagnet 34 thus being parallel to the actuator 10 and adjacent thereto.
L'extrémité libre de la tige cylindrique 30 porte une rondelle 36 qui constitue un moyen de déplacement de la butée mobile 26 vers une position de repos lorsque l'électro-aimant 34 n'est pas alimenté en énergie électrique. L'extrémité du noyau 32 à l'opposé de la butée 26 est associée à un ressort de rappel 38 non linéaire, par exemple de forme hélicoïdale conique qui prend appui par une extrémité sur le corps de l'électro-aimant 34 et par son autre extrémité sur le noyau 32, pour repousser celui-ci dans la direction opposée à la butée 26.The free end of the cylindrical rod 30 carries a washer 36 which is a means for moving the movable stop 26 to a rest position when the electromagnet 34 is not supplied with electrical energy. The end of the core 32 opposite the abutment 26 is associated with a nonlinear return spring 38, for example of conical helical shape which is supported by one end on the body of the electromagnet 34 and by its another end on the core 32, to push the latter in the direction opposite to the stop 26.
Le déplacement du noyau 32 dans cette direction est limité par un circlip 40 solidaire de la tige 30 et venant s'appliquer sur l'extrémité du corps 34 de l'électro-aimant vissé dans l'alésage 28.The displacement of the core 32 in this direction is limited by a circlip 40 integral with the rod 30 and coming to rest on the end of the body 34 of the electromagnet screwed into the bore 28.
Une rondelle 42, par exemple en caoutchouc, est montée sur cette extrémité du corps de l'électro-aimant pour amortir le choc du circlip 40 en fin de course. Le circlip 40 est destiné également à s'appliquer par l'intermédiaire d'une rondelle 44 sur l'extrémité correspondante de la butée 26 pour maintenir cette butée dans une position de service lorsque l'électro-aimant 34 est alimenté en énergie électrique, cette position de service étant également définie par appui de la butée 26 sur un épaulement 46 de l'alésage 28, du côté opposé à l'électro-aimant.A washer 42, for example of rubber, is mounted on this end of the body of the electromagnet to dampen the shock of the circlip 40 at the end of the race. The circlip 40 is also intended to be applied via a washer 44 on the corresponding end of the stop 26 to maintain this stop in a service position when the electromagnet 34 is supplied with electrical energy, this operating position is also defined by pressing the abutment 26 on a shoulder 46 of the bore 28, the side opposite to the electromagnet.
La butée 26, qui est traversée librement par la tige cylindrique 30, contient un ressort de précharge 48 dont une extrémité s'appuie sur la rondelle 44 et le circlip 40 précité et dont l'extrémité opposée s'appuie sur un épaulement du passage axial de cette butée dans lequel s'étend la tige 30, à des fins qui seront expliquées ci-dessous.The stop 26, which is traversed freely by the cylindrical rod 30, contains a preload spring 48, one end of which bears on the washer 44 and the aforementioned circlip 40 and whose opposite end rests on a shoulder of the axial passage. of this stop in which the rod 30 extends, for purposes which will be explained below.
L'extrémité du verrou 20 qui est au contact de la butée 26, comprend deux faces d'appui sur cette butée, une première face d'appui 50 étant plane et perpendiculaire à l'axe du verrou et s'appliquant sur un méplat 52 de la surface cylindrique externe de la butée 26, la seconde face d'appui 54 du verrou 20 étant oblique par rapport à l'axe du verrou et étant destinée à s'appliquer sur une face oblique correspondante 56 de la butée 26.The end of the lock 20 which is in contact with the stop 26, comprises two bearing faces on this stop, a first bearing face 50 being flat and perpendicular to the axis of the lock and being applied on a flat surface 52 the outer cylindrical surface of the abutment 26, the second bearing surface 54 of the latch 20 being oblique with respect to the axis of the latch and being intended to be applied on a corresponding oblique face 56 of the abutment 26.
La première face d'appui plane 50 du verrou 20 est formée sur le côté du verrou qui est à l'opposé de l'électro-aimant 34, tandis que le méplat 52 du verrou est formé sur le côté du la butée 26 qui est situé du côté de l'électro-aimant 34. La face d'appui inclinée 54 du verrou est formée du côté du verrou qui est situé du côté de l'électro-aimant 34, tandis que la face d'appui inclinée 56 de la butée 26 est formée du côté de cette butée qui est situé à l'opposé de l'électro-aimant 34. Ces faces inclinées 54 et 56 du verrou et de la butée sont des surfaces cylindriques tandis que les deux autres faces d'appui 50 et 52 du verrou et de la butée sont planes.The first plane bearing face 50 of the latch 20 is formed on the side of the latch which is opposite the electromagnet 34, while the flat portion 52 of the latch is formed on the side of the abutment 26 which is located on the side of the electromagnet 34. The inclined bearing face 54 of the lock is formed on the latch side which is located on the side of the electromagnet 34, while the inclined bearing face 56 of the stop 26 is formed on the side of this stop which is located opposite the electromagnet 34. These inclined faces 54 and 56 of the latch and the stop are cylindrical surfaces while the two other bearing faces 50 and 52 of the latch and the stop are planar.
La dent axiale 24 du verrou 20 qui est engagée dans l'orifice ou la fente 25 de la couronne 18, comprend une face sensiblement radiale et une face opposée oblique par rapport à une direction radiale, la face radiale de la dent 24 étant appliquée sur une paroi radiale de l'orifice 25 tandis que la face oblique de la dent 24 est appliquée sur une paroi oblique correspondante de l'orifice 25 de telle sorte que la rotation de la couronne 18 dans le sens des aiguilles d'une montre en figure 2 autour de l'axe de l'arbre 12 tende à repousser la dent 24 et donc le verrou 20 vers le haut sur cette figure. Les parois de l'orifice 25 sont planes ou en développante de cercle.The axial tooth 24 of the latch 20 which is engaged in the orifice or the slot 25 of the ring 18, comprises a substantially radial face and an opposite face oblique with respect to a radial direction, the radial face of the tooth 24 being applied on a radial wall of the orifice 25 while the oblique face of the tooth 24 is applied to an oblique wall corresponding to the orifice 25 so that the rotation of the ring 18 in the direction of clockwise in Figure 2 about the axis of the shaft 12 tends to push the tooth 24 and therefore the lock 20 to the top on this figure. The walls of the orifice 25 are flat or involute in a circle.
Comme représenté en figure 2, la couronne 18 peut comporter deux orifices ou fentes 25 diamétralement opposés ou un nombre différent de ces orifices ou fentes régulièrement répartis sur la périphérie de la couronne 18. Le fonctionnement de ce dispositif est le suivant :As shown in FIG. 2, the ring gear 18 may comprise two diametrically opposite orifices or slots 25 or a different number of these orifices or slots regularly distributed over the periphery of the ring gear 18. The operation of this device is as follows:
Lorsque l'électro-aimant 34 est alimenté en énergie électrique, le noyau 32 est déplacé vers la droite en figure 1 jusqu'à venir en butée à l'intérieur du corps de l'électro-aimant, la butée mobile 26 étant alors poussée vers la droite par le circlip 40 et la rondelle 44 et venant en appui sur l'épaulement 46 de l'alésage 28.When the electromagnet 34 is supplied with electrical energy, the core 32 is moved to the right in FIG. 1 until it abuts inside the body of the electromagnet, the movable stop 26 being then pushed to the right by the circlip 40 and the washer 44 and bearing on the shoulder 46 of the bore 28.
Dans cette position, le ressort de rappel 38 du noyau 32 est comprimé au maximum, le ressort de précharge 48 de la butée mobile 26 est également comprimé et tend à pousser cette butée en appui sur l'épaulement 46 et la rondelle 36 portée par l'extrémité libre de la tige 30 est écartée de la butée 26.In this position, the return spring 38 of the core 32 is compressed to the maximum, the preload spring 48 of the movable stop 26 is also compressed and tends to push this abutment bearing on the shoulder 46 and the washer 36 carried by the free end of the rod 30 is spaced from the abutment 26.
Dans cette position de la butée mobile 26, qui est sa position de service ou de verrouillage, le méplat 52 de sa surface extérieure est en appui sur la face plane 50 de l'extrémité du verrou 20, dont la dent axiale 24 est engagée dans un orifice 25 de la couronne extérieure 18 des moyens de couplage 14 comme représenté en figure 2, la couronne 18 étant ainsi immobilisée en rotation et permettant la commande de l'embrayage au moyen du moteur électrique de l'actionneur 1.In this position of the movable stop 26, which is its operating or locking position, the flat portion 52 of its outer surface bears on the flat face 50 of the end of the lock 20, whose axial tooth 24 is engaged in an orifice 25 of the outer ring 18 of the coupling means 14 as shown in FIG. 2, the ring gear being thus immobilized in rotation and allowing the control of the clutch by means of the electric motor of the actuator 1.
Dans cette position, si la couronne 18 est sollicitée en rotation dans le sens des aiguilles d'une montre en figure 2, le verrou 20 qui est en appui par sa face plane 50 sur le méplat 52 de la butée mobile 26, ne peut être déplacé vers le haut et libérer la couronne 18, la poussée du verrou 20 sur la butée mobile 26 ayant pour effet de coincer cette butée dans sa position de service à l'intérieur de l'alésage 28 du carter.In this position, if the ring gear 18 is urged in rotation clockwise in FIG. 2, the latch 20 which is supported by its flat face 50 on the flat part 52 of the movable stop 26, can not be moved upward and release the crown 18, the lock thrust 20 on the movable stop 26 having the effect of jamming this stop in its operating position inside the bore 28 of the housing.
Si alors l'alimentation électrique de l'électro-aimant 34 est coupée, de façon volontaire ou en cas de panne, le noyau mobile 32 est ramené vers sa position de repos par son ressort de rappel 38 comme représenté en figure 3, le circlip 40 porté par la tige 30 et la rondelle 44 s'écarte de la butée mobile 26 qui reste coincée dans l'alésage 28 par le verrou 20, et la rondelle d'extrémité 36 portée par l'extrémité de la tige 30 se rapproche de la butée mobile 26 jusqu'à venir percuter celle-ci avec une certaine vitesse dans la position représentée en figure 3. La force de rappel développée par le ressort 38 est déterminée pour suivre la courbe d'effort de l'électro- aimant avec un écart le plus constant possible.If then the power supply of the electromagnet 34 is cut off, voluntarily or in case of failure, the movable core 32 is returned to its rest position by its return spring 38 as shown in FIG. 3, the circlip 40 carried by the rod 30 and the washer 44 deviates from the movable stop 26 which remains stuck in the bore 28 by the latch 20, and the end washer 36 carried by the end of the rod 30 is close to the movable stop 26 until it hits the latter with a certain speed in the position shown in FIG. 3. The restoring force developed by the spring 38 is determined to follow the force curve of the electromagnet with a the most constant distance possible.
L'énergie cinétique qui est appliquée par la rondelle 36 à la butée mobile 26 est suffisante pour déplacer celle-ci vers la gauche en figure 3 jusqu'à ce que le méplat 52 de cette butée mobile échappe à la face plane d'appui 50 du verrou 20, l'angle de raccordement des faces d'appui 50 et 54 du verrou se trouvant alors au début de la face inclinée 56 de la butée mobile et commençant à glisser sur cette face inclinée (position représentée en figure 5). Le glissement de l'extrémité du verrou 20 sur la face inclinée 56 de la butée mobile résulte de la poussée exercée par la paroi inclinée de l'orifice 25 de la couronne 18 sur la face inclinée de la dent axiale 24 du verrou 20 et a pour effet de repousser la butée mobile vers la gauche en figure 5, jusque dans la position de déverrouillage complet représentée en figure 7. Dans cette position, la butée mobile 26 est rapprochée au maximum du corps de l'électro-aimant, et le verrou 20 a été repoussé vers le haut suffisamment pour que sa dent axiale 24 soit dégagée de l'orifice 25 de la couronne 18 et libère celle-ci, qui est alors libre en rotation et découple l'actionneur 10 de l'embrayage. Le noyau mobile 32 de l'électro-aimant est dans sa position de repos, le circlip 40 étant appliqué sur la rondelle d'amortissement 42 portée par l'extrémité du corps de l'électro-aimant 34. Le ressort de précharge 48 de la butée mobile 26 est comprimé dans cette position et sollicite donc cette butée vers la droite en figure 7, de telle sorte que la face inclinée 56 de la butée 20 reste en appui sur la face inclinée 54 du verrou 20, ce qui permet de conserver les positions angulaires de la butée 26 et du verrou 20 dans leurs guidages respectifs.The kinetic energy that is applied by the washer 36 to the movable stop 26 is sufficient to move it to the left in FIG. 3 until the flat portion 52 of this movable stopper escapes from the flat bearing face 50 of the lock 20, the connection angle of the bearing faces 50 and 54 of the lock then being at the beginning of the inclined face 56 of the movable stop and starting to slide on this inclined face (position shown in Figure 5). The sliding of the end of the lock 20 on the inclined face 56 of the movable stop results from the thrust exerted by the inclined wall of the orifice 25 of the ring 18 on the inclined face of the axial tooth 24 of the lock 20 and has the effect of pushing the movable stop to the left in Figure 5, to the full unlocking position shown in Figure 7. In this position, the movable stop 26 is brought to the maximum of the body of the electromagnet, and the lock 20 has been pushed upward enough so that its axial tooth 24 is disengaged from the orifice 25 of the ring 18 and releases the latter, which is then free to rotate and decouples the actuator 10 of the clutch. The movable core 32 of the electromagnet is in its rest position, the circlip 40 being applied to the damping washer 42 by the end of the body of the electromagnet 34. The preload spring 48 of the movable stop 26 is compressed in this position and thus urges this stop to the right in FIG. 7, so that the inclined face 56 of the abutment 20 remains in abutment on the inclined face 54 of the latch 20, which makes it possible to maintain the angular positions of the abutment 26 and the latch 20 in their respective guides.
La première partie de la course de retour du noyau mobile 32, qui correspond à la distance parcourue par la rondelle d'extrémité 36 entre la position représentée en figure 1 et celle représentée en figure 3, est égale à la course de la butée 26 entre le circlip 40 et la rondelle 36 et est de préférence relativement grande par rapport à la course totale du noyau 32, afin d'optimiser l'utilisation du ressort de rappel 38 du noyau mobile et donc de réduire la puissance, la masse et le coût de l'électro-aimant 34. En pratique, cette première partie de la course du noyau mobile pourra avoir une valeur supérieure à 70 % de la course totale du noyau mobile.The first part of the return stroke of the movable core 32, which corresponds to the distance traveled by the end washer 36 between the position shown in FIG. 1 and that represented in FIG. 3, is equal to the travel of the stop 26 between the circlip 40 and the washer 36 and is preferably relatively large compared to the total stroke of the core 32, to optimize the use of the return spring 38 of the movable core and thus reduce the power, mass and cost In practice, this first part of the travel of the mobile core may have a value greater than 70% of the total travel of the mobile core.
La deuxième partie de cette course correspond à la distance que doit parcourir la butée mobile 26 pour passer de sa position de verrouillage représentée aux figures 1 et 3 à sa position de la figure 5 où elle commence à permettre le déplacement du verrou 20 vers le haut. Cette deuxième partie de la course du noyau 32 est approximativement égale à la longueur d'application de la face plane d'appui 50 du verrou 20 sur le méplat 52 de la butée 26.The second part of this stroke corresponds to the distance that the movable stop 26 must travel to pass from its locking position shown in Figures 1 and 3 to its position in Figure 5 where it begins to allow the movement of the lock 20 upwards. . This second part of the stroke of the core 32 is approximately equal to the length of application of the flat bearing face 50 of the lock 20 on the flat part 52 of the abutment 26.
Cette deuxième partie de course est avantageusement réduite et par exemple inférieure à 30 % de la course totale du noyau mobile 32 afin de réduire l'énergie de déverrouillage et donc la dimension de l'électro-aimant. Il est par ailleurs préférable que la somme de la première partie et de la deuxième partie de la course du noyau 32 représente la totalité ou la quasi-totalité de la course de ce noyau, pour une utilisation optimale du ressort de rappel 38 de ce noyau. A la fin de la seconde partie de la course du noyau mobile, ce n'est plus le ressort de rappel 38 qui agit sur la butée mobile 26 pour la déplacer vers sa position de déverrouillage effectif représentée en figure 7, c'est le verrou 20 qui est lui-même poussé vers le haut par le couple de rotation appliqué à la couronne 18, et qui va finir de déplacer la butée mobile 26 dans sa position de déverrouillage. Lorsque l'électro-aimant 34 est à nouveau alimenté en énergie électrique, le noyau mobile 32 est sollicité de sa position de repos représenté en figure 7 vers sa position de verrouillage représentée en figure 1 , mais la butée mobile 26 est bloquée par le verrou 20 et ne peut se déplacer vers sa position de la figure 1. Lorsque le moteur électrique de l'actionneur 10 est lui-même alimenté en énergie électrique, il fait tourner la couronne 18 à l'intérieur du carter jusqu'à ce qu'un orifice 25 de cette couronne se trouve aligné avec la dent 24 du verrou 20, la butée mobile 26 pouvant alors repousser le verrou 20 vers le bas et retrouver sa position de verrouillage représentée aux figures 1 et 2. Comme on l'a représenté schématiquement dans la variante de réalisation de la figure 9, il peut être avantageux d'associer un frein permanent unidirectionnel à l'arbre 12 du moteur électrique de l'actionneur 10.This second portion of travel is advantageously reduced and for example less than 30% of the total stroke of the movable core 32 to reduce the unlocking energy and therefore the size of the electromagnet. It is also preferable that the sum of the first part and the second part of the stroke of the core 32 represents all or almost all of the stroke of this core, for optimum use of the return spring 38 of this core . At the end of the second part of the stroke of the movable core, it is no longer the return spring 38 which acts on the movable stop 26 to move it towards its actual unlocking position shown in Figure 7, it is the latch 20 which is itself pushed up by the torque applied to the ring 18, and which will finish moving the movable stop 26 in its position unlocking. When the electromagnet 34 is again supplied with electrical energy, the movable core 32 is biased from its rest position shown in FIG. 7 to its locking position shown in FIG. 1, but the movable stop 26 is blocked by the lock. 20 and can not move to its position of Figure 1. When the electric motor of the actuator 10 is itself supplied with electrical energy, it rotates the ring 18 inside the housing until an orifice 25 of this ring is aligned with the tooth 24 of the lock 20, the movable stop 26 can then push the lock 20 down and return to its locking position shown in Figures 1 and 2. As schematically shown in the variant embodiment of FIG. 9, it may be advantageous to associate a unidirectional permanent brake with the shaft 12 of the electric motor of the actuator 10.
Ce frein 60 est avantageusement monté sur l'extrémité de l'arbre 12 opposée à celle reliée aux moyens de couplage 14, le frein étant monté à l'intérieur du capot de l'actionneur 10 et comprenant un mécanisme de roue libre 62 reliant l'extrémité de l'arbre 12 à un disque de frein 64 serré entre des garnitures 66 sollicitées l'une vers l'autre par des ressorts 68 prenant appui sur des parties fixes de l'actionneur 10, ces garnitures 66 étant elles- mêmes immobilisées en rotation au moyen de goupilles ou analogue 70 solidaires du boîtier de l'actionneur.This brake 60 is advantageously mounted on the end of the shaft 12 opposite to that connected to the coupling means 14, the brake being mounted inside the cover of the actuator 10 and comprising a freewheel mechanism 62 connecting the end of the shaft 12 to a brake disc 64 clamped between fittings 66 biased towards one another by springs 68 bearing on fixed parts of the actuator 10, these fittings 66 being themselves immobilized in rotation by means of pins or the like 70 integral with the housing of the actuator.
Le frein 60 associé à l'arbre 12 de sortie du moteur électrique de l'actionneur évite d'alimenter en permanence ce moteur pour maintenir en position la charge de l'actionneur. L'intégration de ce frein dans l'actionneur réduit l'encombrement et facilite le montage. The brake 60 associated with the output shaft 12 of the electric motor of the actuator avoids continuously supplying the motor to maintain the position of the actuator load. The integration of this brake in the actuator reduces the bulk and facilitates assembly.
Claims
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE112008000559T DE112008000559T5 (en) | 2007-03-02 | 2008-02-28 | Control device for a clutch |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR0701516 | 2007-03-02 | ||
| FR0701516A FR2913258B1 (en) | 2007-03-02 | 2007-03-02 | DEVICE FOR CONTROLLING A CLUTCH. |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2008119911A1 true WO2008119911A1 (en) | 2008-10-09 |
Family
ID=38577447
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/FR2008/050339 Ceased WO2008119911A1 (en) | 2007-03-02 | 2008-02-28 | Clutch control device |
Country Status (3)
| Country | Link |
|---|---|
| DE (1) | DE112008000559T5 (en) |
| FR (1) | FR2913258B1 (en) |
| WO (1) | WO2008119911A1 (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2807488A1 (en) * | 2000-04-07 | 2001-10-12 | Gkn Viscodrive Gmbh | Axial adjusting device for operating multi-plate clutch includes pressure disc rotationally secured by releasable anti-rotation means comprising axially movable bolt which engages in and releases from pawls |
| WO2003050437A2 (en) * | 2001-12-13 | 2003-06-19 | Skf Industrie S.P.A. | Screw actuator with locking mechanism |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR650248A (en) | 1927-09-09 | 1929-01-07 | Universal soap device |
-
2007
- 2007-03-02 FR FR0701516A patent/FR2913258B1/en active Active
-
2008
- 2008-02-28 WO PCT/FR2008/050339 patent/WO2008119911A1/en not_active Ceased
- 2008-02-28 DE DE112008000559T patent/DE112008000559T5/en not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2807488A1 (en) * | 2000-04-07 | 2001-10-12 | Gkn Viscodrive Gmbh | Axial adjusting device for operating multi-plate clutch includes pressure disc rotationally secured by releasable anti-rotation means comprising axially movable bolt which engages in and releases from pawls |
| WO2003050437A2 (en) * | 2001-12-13 | 2003-06-19 | Skf Industrie S.P.A. | Screw actuator with locking mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112008000559T5 (en) | 2010-01-07 |
| FR2913258A1 (en) | 2008-09-05 |
| FR2913258B1 (en) | 2009-05-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| FR3078990A1 (en) | OPENING CONTROL WITH MECHANICAL REASSEMBLY | |
| FR2813648A1 (en) | RATCHET FREE WHEEL DEVICE | |
| FR2793527A1 (en) | Motor for electric starter used with internal combustion engines, utilizes a planetary reduction gear formed integrally with the armature | |
| EP1324466B1 (en) | Disc brake and torque transmission device | |
| FR2984433A1 (en) | CLUTCH WITH RETRACTION OF WEAR, IN PARTICULAR FOR MOTOR VEHICLE | |
| WO2014106714A1 (en) | Gearbox for a self-propelled device such as a lawnmower | |
| FR2657051A1 (en) | CLUTCH OPERATING DEVICE. | |
| WO2016055637A1 (en) | Clutch device | |
| FR2706190A1 (en) | Rotational transmission device | |
| EP0511067A1 (en) | Controlled viscous fluid transmission device particularly for motor vehicles | |
| WO2008119911A1 (en) | Clutch control device | |
| EP4380810B1 (en) | Powertrain for a hybrid propulsion or traction motor vehicle comprising a mechanism for blocking the combustion engine | |
| FR2913257A1 (en) | Clutch controlling device for motor vehicle, has lock for maintaining gear with respect to motor body when coupling unit is in active position, and permitting free rotation of gear with respect to body when unit is in uncoupled position | |
| EP1003982A1 (en) | Friction clutch with wear take-up device, in particular for motor vehicle | |
| WO2003081752A1 (en) | Device with disc braking and torque transmission | |
| EP1478844B1 (en) | Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear | |
| FR2902073A1 (en) | Transmission device for bicycle, has slip clutch rotatably coupling planetary shaft with planet carrier, and overrunning clutch mounted on planet carrier, so that rotation of carrier is in same direction as that of rotation of shaft | |
| FR2667276A1 (en) | Clutch control system - has rotating part which drives release lever with wear take up system between movable and activating parts | |
| FR2661960A1 (en) | ASSEMBLY OF A FRICTION CLUTCH COVER. | |
| FR2742205A1 (en) | GEAR GAME RETRAPING DEVICE | |
| WO2017207917A1 (en) | Actuator for a clutch, notably for a motor vehicle | |
| CA2132549A1 (en) | Device for actuating a clutch on a gear box or the like | |
| FR2778707A1 (en) | Friction clutch for motor vehicle, with wear compensation | |
| FR3136266A3 (en) | One-way clutch device and method | |
| FR3134862A1 (en) | CLUTCH DISC WITH FREEWHEEL DEVICE INCLUDING TWO RAMP SYSTEMS |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 08762174 Country of ref document: EP Kind code of ref document: A1 |
|
| WWE | Wipo information: entry into national phase |
Ref document number: 1120080005591 Country of ref document: DE |
|
| RET | De translation (de og part 6b) |
Ref document number: 112008000559 Country of ref document: DE Date of ref document: 20100107 Kind code of ref document: P |
|
| 122 | Ep: pct application non-entry in european phase |
Ref document number: 08762174 Country of ref document: EP Kind code of ref document: A1 |