FR2785690A1 - Control element arrangement for automated vehicle coupling e.g. automated gearbox of braking system, has compensation force arrangement, and adapter that adapts control element arrangement to varying operating conditions - Google Patents

Abstract

The arrangement has a control drive (14) mounted on a housing (12) and that engages a movably mounted drive element (16), a driven element (20) that engages the drive element in a first coupling region and that interacts with an element to be driven in a second coupling region. A compensation force arrangement (28) acts on the housing in a third coupling region and on the drive element in a fourth coupling region. An adapter arrangement (50) adapts the control element arrangement to varying operating conditions.

Description

The present invention relates to an actuator in particular for controlling an automatic vehicle clutch, applicable to an automatic gearbox or for serving as a brake actuator or similar means comprising: a motor carried by a casing and acting on an element
drive to move it, the element
drive being carried movably in a range
of support relative to the casing depending on the action
by the motor, an output element acting through a coupling zone
(first coupling zone) on the drive element and
by its other coupling zone (second coupling zone)
on the member to be operated and if necessary, a force compensator which acts through a coupling zone
(third coupling zone) on the casing and by another
coupling zone (fourth coupling zone) on the element
drive.

 Such an actuator is known for example according to document DE 196 00 471 A1 used to actuate a friction clutch. Such friction clutches generally include a membrane spring as a force accumulator which urges a pressure plate and which must be driven in its released position relative to its operating position so that the actuator can execute the declutching operations. To effect this transition, the actuator must provide a predetermined force.

 It is known that in particular in the case of friction clutches of motor vehicles, the operating states or the operating characteristics change during use. Thus, for example, the wear of the friction linings of a clutch disc can modify the mounting position of the force accumulator and thus its force characteristic. As a result, for a force characteristic remaining the same, the actuator modifies the declutching operations and in the extreme case, it can no longer execute them correctly. To avoid this, the document DE 196 00 471 A1 combines an actuator and a friction clutch with an automatic device for compensating for wear. This means that the variable operating characteristics in the clutch (induced by wear or the like) are automatically compensated in the clutch so that the actuator ensures with a constant actuation characteristic by cooperating with the clutch. friction adapted to variable clutch characteristics so that the clutch and disengage operations to be performed have an almost constant characteristic.

 If such measures are not taken, there is a risk that the displacement of the operating range of the actuator will produce greater wear therein and that the motor itself will require more energy to modify the clutch and clutch durations. clutch as has already been mentioned, with the consequence of a modification of the whole of the characteristic of the operation of the clutch.

 Another way to avoid such annoying consequences is to use hydraulic clutch actuators also comprising a wear compensation device. In addition, it is possible in the case of electromechanical actuators, to use electric motors with higher power and higher gear ratio.

All this however leads to higher costs and a more complex structure of these systems.

 This is why, the present invention aims to develop an actuator which can be advantageously used in conjunction with a device to be operated and which has variable operating characteristics during operating time.

 This problem is solved according to the invention by an actuator, in particular for actuating an automatic vehicle clutch, applicable to an automatic gearbox, or as a brake actuator or the like of the type defined above, characterized by an adapter which adapts the actuator to changes in operating condition.

 This means that there is no longer any need to compensate for the modifications directly in the device to be maneuvered because the actuator according to the invention itself allows adaptation to such measures. In particular, in the application to friction clutches of motor vehicles, existing clutches can be used without the relatively complicated wear compensation devices and due to the adaptation measures undertaken directly inside the actuator , regardless of the state of wear or operation of the friction clutch, clutch and clutch release operations with constant characteristics.

 According to an advantageous characteristic, the adapter provides them. adaptation measures to influence the actuator components.

By way of example according to advantageous characteristics, the adapter can be produced to: a) modify a compensating force generated by the compensation
force sator or / and, b) modify the position of the first coupling zone by
relative to the drive element, c) modify the position of the second coupling zone by
relative to the member to be operated or / and, the casing or / and, d) modify the position, of the third coupling zone by
report to the housing or / and modify the force compensator
or / and, e) modify a position of the fourth coupling zone by
relation to the drive element and / or the compensator
by force or / and, f) move the fourth coupling zone with respect to
the driving element in the execution of an operation
maneuver using the actuator and / or, g) change the position of the support area relative to the
crankcase and / or engine.

 It is thus recognized that, ultimately, at the level of all the moving or cooperating components in the actuator, displacement or sliding measures are taken in order to be able to modify the force or output characteristic of the actuator according to the invention, by proceeding as desired.

 Thus, advantageously the force compensator comprises a force generator with elastic spring effect and the adapter can modify the state of prestressing of the force generator.

 For this, the adapter can modify and in particular shorten the distance between two stressing zones of the force generator, this distance being measured in the longitudinal direction of the force compensator.

 In addition, the force characteristic can be influenced by modifying, by the adapter, the distance between the third coupling zone and the fourth coupling zone.

 For this, advantageously, the adapter displaces the third coupling zone with respect to the casing essentially in a longitudinal direction of the force compensator by moving it away from the fourth coupling zone or vice versa.

 As a variant, or in addition, it is possible that, according to another advantageous characteristic, the adapter displaces (brings closer or apart) the fourth coupling zone with respect to the motor essentially in a longitudinal direction of the force compensator with respect to the third range of coupling.

 It is also possible for the adapter to modify a position of the third coupling range with respect to the casing essentially in a direction transverse to the longitudinal direction of the force compensator.

 In this case, as a variant or in addition, the adapter modifies a position of the fourth coupling range relative to the motor essentially transversely to the longitudinal direction of the force compensator.

 All of these means or measures ultimately result in modifying the position of the force compensator in the actuator in order to adapt the operating characteristic of the compensator to the variable states of the device to be operated.

 For this, for example, the adapter modifies the distance between the first coupling zone of the coupling zone and / or an angular position of the first coupling zone with respect to a reference angle position defined on the motor. .

 It is also possible for the adapter to modify the position of the second coupling area essentially in a longitudinal direction of the output element relative to the member to be operated and / or the casing.

 At the second coupling zone, adaptation measures can be taken so that the adapter device modifies a position of the second coupling range essentially transversely to a longitudinal direction of the output element relative to the housing. and / or the organ to be operated.

 Another possibility of action is characterized in that the drive element is a drive wheel or a drive wheel segment engaged with a motor wheel rotating about an axis of rotation and the adapter. displaces an axis of rotation defining the bearing zone of the drive element with an essentially constant distance relative to the axis of rotation of the motor wheel relative to the casing or the motor.

 For this, according to another advantageous characteristic, the adapter comprises a sliding device which slides an assembly receiving the drive element along a guide path substantially essentially concentrically surrounding the axis of rotation of the wheel of the engine.

 In summary, in the actuator according to the invention, the adapter advantageously comprises a displacement device which displaces a component comprising the respective coupling range or forming a bearing range with respect to the associated component. Thus, it should be noted that the expression associated component designates the component or the assembly at the level of which a certain coupling or bearing zone is supported, that is to say a zone with which this coupling zone is connected either directly to generate a force, or with the interposition of a certain support device or force transmission.

 For example, according to an advantageous characteristic, the sliding device comprises at least one threaded rod driven in rotation and carried relative to the coupling or bearing pad or of the corresponding component, and the corresponding component or the components which form or comprise the zone. bearing or coupling is or are provided with a nut-forming element which moves in the longitudinal direction of the threaded rod when the latter is rotated.

 In this case, there will be a high displacement efficiency if at least one threaded rod is oriented with its longitudinal direction in a direction in which we want to move the coupling or bearing area relative to the corresponding component.

 In addition, at least one threaded rod is coupled by a lever device or a device articulated to the corresponding component or to the coupling or bearing area.

According to another development of the invention: * the sliding device comprises a first component of
inclined surfaces rotated about an axis by
relative to the coupling or bearing area or components
corresponding health, this component having a first on
oblique face extending in a helix relative to
the axis of rotation, 'as well as a second component of inclined surfaces not ro
relative to the associated component or to the neck area
range or level, this second component having a second
oblique surface extending in a helical line by
relative to the axis of rotation of the first surface component
at an angle, * preferably, by relative rotation between the first and
the second surface in the form of a helix, we modify
the length of the assembly formed by the first and second
component of surfaces.

 This is accomplished in a simple manner in that the first and second oblique surfaces form an exterior or interior thread surface.

 In addition, according to an advantageous characteristic, the first and the second oblique surface have an angular extension at most equal to 360 relative to the axis of rotation.

 In this case, it is not essential that the respective oblique surfaces are helical surfaces, but they can also extend radially inwardly relative to their axis of rotation up to this.

According to another variant of the invention: 'the sliding device comprises a unit of pathways
guidance coupled to the coupling zone or bearing zone or
to the associated component as well as a guided unit, in engagement
with a guide path of the guide path unit, * and to create the guide movement, the path unit
or / and the guided unit is driven according to a
rotational or / and linear movement.

 For example, according to another characteristic, the guideway unit comprises a guide groove extending essentially in a helix or eccentrically with respect to an axis of rotation and the guided unit comprises a guide pin penetrating into the groove guide.

 This embodiment is particularly advantageous because it allows guidance in both directions.

 Alternatively the guideway unit comprises a guide cam with an eccentric cam surface and the guided unit comprises a cam follower.

 It is also possible that the guideway unit has a wedge device.

 According to another development of the actuator according to the invention, the sliding device comprises a coupling opening device coupled to the coupling zone or bearing zone or to an associated component, this device having a variable opening section, and the corresponding component or the coupling or bearing area comprises a support element penetrating into the coupling opening device with a variable opening section, of a support element which follows the section variation.

 It is also possible that the sliding device comprises a rack coupled to the coupling or bearing zone or to the corresponding component, as well as a pinion or a screw wheel or the like, driven in rotation and meshing with the rack or the component. associated or the coupling or bearing area.

 It is possible to use linear drive units, in particular linear electric motors or linear magnetic motors which are coupled to the coupling or bearing region on the one hand and to the component for the sliding device on the other hand.

 It is also possible for the sliding device to comprise a bimetal device, a shape memory device or similar means coupled on one side to the coupling zone or bearing zone and on the other side to the associated component, as well as a control unit preferably a heating unit to influence the shape of the bimetal device, that of the shape memory alloy device or the like.

 The actuator according to the invention can also be characterized in that for the execution of the operations of my work the position of the fourth coupling zone varies with respect to the drive element. In such an embodiment, according to another advantageous embodiment, the sliding device can modify the relative modification characteristic between the fourth coupling zone and the support zone of the drive element.

The present invention will be described below in more detail with the aid of preferred embodiments shown in the accompanying drawings in which: * Figure 1 is a side view of an actuator in a
open housing, * figures 2 to 5 show longitudinal sections
spring compensator materials in which the step
the compensating spring preload is variable, * Figures 6 and 7 show schematic views of the com
spring thinker in which the angular position is
variable, * Figures 8 and 9 show schematic views of com
spring thinkers in which one of the ranges of
coupling can be moved, FIG. 10 is a schematic view of part of
the actuator in which the position of the axis of rota
tion of the drive element can be modified, * Figures 11 to 15 show schematic views of a
spring compensator which allows to modify the position
of one of the zones of coupling by a lever system, 'Figures 16 and 17 are schematic views of a com
spring thinker in which the state of prestressing of the
spring can be modified by a lever system, FIG. 18 is a schematic view of a compensator with
spring in which the state of spring preload
can be modified by a screw drive, * Figure 19 is a view corresponding to that of the fi
gure 18 whose screw drive allows to modify the
angular position of the spring compensator, * Figures 20 and 21 each show a compensator with
spring in which you can change the position of a
compensation spring coupling area, using
oblique surfaces which cooperate, 'Figure 22 is a view corresponding to that of the fi
gure 21 in which the device with oblique surfaces
allows to modify the angular position of the compensator
spring, 'Figure 23 shows a device with a mistletoe groove
helical dage to change the position, 'Figures 24 and 25 each show a drive to
cam surfaces for changing the position of
one of the coupling zones of the spring compensator, * Figures 26 to 29 show neck wedge devices
smoothing allowing to modify the position of one of the
coupling zones of the spring compensator, * Figures 30 and 31 show an opening device in
diaphragm shape for changing the position of
one of the spring compensator coupling zones, * Figures 32 and 33 show a rack and pinion device
used to modify the position of one of the
coupling of the spring compensator, * Figures 34 and 35 show a device with a li
or magnetic to change the position of a com
spring thinker, Figures 36 and 37 show an alloy device with
shape memory which allows you to modify a precon-
drag or the position of a spring compensator, 'Figure 38 shows a guide device for
modify the position variation characteristic of the
spring-loaded compensator with respect to the entry element
during the execution of the maneuver, * Figures 39 and 40 show another embodiment
a guideway device that changes the position
tion of a spring compensator.

 FIG. 1 shows an actuator generally bearing the reference 10. The actuator 10 comprises a casing 12 equipped with a motor 14, for example an electric motor. The casing 12 further carries a toothed segment 16 pivoting about an axis of rotation A1; this segment meshes with a toothing not shown with a pinion provided on the electric motor 14 or on a reduction mechanism and the electric motor 14 can drive it to pivot around the axis of rotation A1.

 An output element 20 is coupled to the drive element, i.e. to the gear wheel segment 16 at a first coupling area 22, i.e. to an area coupling the output element 20. Thus, a pivoting movement of the toothed wheel segment 16 is converted into a translational movement of the rod-shaped output element 20. By its other coupling zone 24, that is to say a second coupling zone 24 which is only shown diagrammatically in FIG. 1, the output element 20 according to FIG. 1 acts on a sensor cylinder 26 which provides a hydraulic actuating force applied to a member to be actuated. It should be noted that there may be different possibilities here for emitting this actuating force.

Instead of the hydraulic force transmission, one can also provide a mechanical transmission; Isolation output 20 can also act directly on the member to be actuated, for example the diaphragm spring of a friction clutch or a spring pad.

 Between the casing 12 and the toothed wheel segment 16, there is a compensator 28 with a compensator spring 30 generally produced as a helical compression spring.

The compensating spring 30 is supported with its respective stress zones 32, 34 by transmission elements 36, 38 on the casing 12 or on the toothed wheel segment 16.

At the level of the transmission element 36, there is provided a coupling zone 40 hereinafter called the third coupling zone 40 for the spring compensator 28; at the level of the transmission element 38, there is provided another coupling zone 42 hereinafter called the fourth coupling zone 42 for the spring compensator 28. In each of the coupling zones 40, 42 in which the spring compensator 28 rests against the casing 12 or the toothed pinion segment 16, the spring compensator 28 can pivot in a very different and known manner with the casing 12 or the toothed wheel segment 16, for example by means of bearing devices.

 It appears that a longitudinal axis or a longitudinal direction L1 of the spring compensator 28 in the basic position shown in FIG. 1 of the actuator does not intersect the axis of rotation Ai of the toothed wheel segment 16. If the electric motor 14 is powered from this basic state, for example to disengage a clutch by creating a pushing force, then the toothed wheel segment 16 is driven clockwise to turn around the axis of rotation A1; the outlet element 20 is then slid to the left according to FIG. 1 and creates hydraulic pressure in the sensor cylinder 26.

By this sliding movement, the longitudinal axis or the longitudinal direction L1 of the spring compensator 28 approaches the axis of rotation A1 and acts in this approximation range, first of all against the electric motor 14.

Once the longitudinal axis L1 has passed beyond the axis of rotation A1, the spring compensator 28 acts in the same direction as the electric motor 14 and creates an additional torque around the axis of rotation A1 pushing the toothed wheel segment 16 in a clockwise direction. The force characteristic of the spring compensator 28 can preferably be adjusted to compensate for a force characteristic of the member which, for example, acts on the diaphragm spring of the clutch. In this case, the electric motor 14 will only have to provide the force serving to set the whole system in motion and to keep it in motion against the friction forces produced.

 As already indicated above, in particular in systems subject to wear, the difficulty is that their operating characteristics and thus also their actuation characteristics vary during their period of use. According to the present invention, it is provided for this that the actuator 10 can be adapted by various means described later, to such actuation characteristics, variable to provide such modified actuation forces or degrees or amplitudes of actuation modified. This means that the state in which the member to be operated is detected and, depending on this detection result, different adaptation means are taken inside the actuator 10 according to the invention to hold account of this state thus entered. For example, in the case of clutch linings subject to wear, the resulting change in the mounting position and thus in the spring characteristic of the diaphragm spring is detected so that the electric motor 14 receives a higher intensity current to execute the clutching and disengaging operations. When this is observed, the adaptation measures described below can be taken to again create an actuation characteristic corresponding to a new clutch, by lowering the intensity of the current. Another state which is detected and ultimately leads to the execution of adaptation measures, would be a failure of the electric motor 14 directly in the actuator. In this case also, one can use the adaptation measures which will be described later without the electric motors 14 generating in emergency operation, an actuating force by the actuator according to the invention.

 It is thus recognized that in the sense of the present invention, the possibly modified operating conditions include not only the operating conditions at the level of a device to be maneuvered, but also the conditions or operating states existing directly in the actuator 10 and which could eventually lead to the fact that, without carrying out adaptations, the desired operating function could no longer be fulfilled.

 Before describing the various embodiments with reference to FIGS. 2 to 40, making it possible to carry out the adaptations indicated above, the following will be described below and with reference to FIG. 1, the ranges in which such measurements could occur .

 First of all, it is possible to modify the position of the spring compensator 28 with respect to the casing 12 or with respect to the toothed wheel segment 26. For this, one can for example as indicated by the arrow P1, place the spring compensator 28 in the third coupling range 40 in the direction of the longitudinal axis L1 or / and essentially transversely to this longitudinal axis L1.

The coupling pad 40 of the spring compensator 28 can itself be moved. It is correspondingly possible, as indicated by arrow P2, to modify the position of the spring compensator 28 at the coupling pad 42 either in the longitudinal direction thereof and / or essentially transversely to this longitudinal direction. L1. In this case, it is also possible to modify the position of the coupling area 42 of the spring compensator 28. Another possibility of adaptation consists in modifying the stress zones 32, 34 in the spring compensator 28 to thereby modify the state of prestressing of the compensating spring 30. In addition, it is possible to act on the spring compensator 28 for example on the toothed pinion segment 16 to modify the relative position between the fourth coupling range 42 and the axis of rotation A1 of the toothed wheel segment 16 during the pivoting movement of this segment 16. In this case, to carry out the adaptation measures, the degree of variation or the characteristic of variation of this relative position can be influenced.

 The description of the measures to be taken for the spring compensator 28 already shows that these measures are often nested. Thus, a displacement at the level of the fourth coupling zone 42 transversely to the longitudinal direction L1 obviously also leads to a modification of position, in particular a modification of the angular position of the spring compensator 28 at the level of the third coupling zone 40.

 Other adaptation measures can be carried out by modifying the relative position between the first coupling zone 22 of the output element 20 relative to the axis of rotation A1 of the toothed wheel segment 16. This is how for example one can modify the nested distance B1 and / or one can modify the relative angular position as indicated by the arrow P3. In this case, the line B1 drawn as an arrow can serve as a reference position or zero position and an angular displacement can be defined in the direction of the arrow P3 relative to this reference position.

 According to other adaptation measures, at the second coupling range 24, it is possible to modify the point of attack or the landing zone 12 and with a longitudinal direction L2 represented in FIG. 1.

 Another adaptation measure can be carried out at the level of the gear wheel segment 16. In FIG. 1, the reference A2 designates the axis of rotation of the gear wheel which, driven by the electric motor 14, meshes with the gear segment. toothed wheel 16 and pivots it around the axis A ,. The toothed wheel segment 16 can be slid for a constant distance between the axes Al and A2 (this is necessary to maintain the state of engagement) so as to modify the position of the axis A1 relative to that of the casing 12 .

 It is obviously also possible to combine the different adaptation measures.

 Different embodiments of displacement devices will be described below; these different embodiments make it possible to act on different components of the actuator 10 to intervene in the direction of adaptation measurement. Mainly, the execution of adaptation measures will be described at the level of the spring compensator 28. It is clear that the various displacement devices described can be used for example to slide the first support zone 22 relative to the segment. gear 16 or the second coupling zone 24 relative to the member to be operated or the like clutch.

 FIG. 2 shows a first variant of the displacement device 50 produced here as an adapter device and serving to modify the state of prestressing of the compensating spring 30 of the compensator 28. It can be seen that the compensating spring 30 is supported on the one hand on the transmission element 36 and on the other hand on the sliding support element 52. The support element 52 is integrally connected to a nut 54 carried by a threaded rod 56. The threaded rod 56 is rotatably mounted in a bearing 58 of the transmission element 38 and is rotated by a rotational drive means for example an electric motor 60. The motor 60 is integral in rotation with the transmission element 36 but it can slide in the direction axial, that is to say in the longitudinal direction of the compensating spring 30 so that it can move by the relative sliding between the two telescopic transmission elements 36, 38 in Isolémen t transmission 36. When the motor 60 is supplied and the threaded rod 56 is rotated, it follows that the support element 52 held integrally in rotation with the nut 54 in the slots 62,64 of l the transmission element 38 moves in the longitudinal direction of the threaded rod 56 and thus modifies the state of prestressing of the compensating spring 30.

It also changes the intensity of the force applied to the toothed wheel segment 16 by the spring compensator 28.

It should be noted that the bearing 58 receives the threaded rod 56 so as to let it rotate while blocking it axially.

 Figure 3 shows a variant of the previous embodiment. In this case, the motor 60 is fixed in the transmission element 36 and the threaded rod 56 is supported axially on the transmission element 36. By supplying the motor 60 which may be constituted by a stepping motor, a DC motor or the like, the state of prestressing of the compensating spring 30 is again modified by increasing or decreasing, for example, the prestressing force.

It should be noted that in this embodiment, all the components of the displacement device 50 necessary to modify the prestressing force, are housed inside the transmission element 36 on the side of the casing. In the case of a fixed mounted motor, the threaded rod 56 does not have to receive support, it suffices to guide it.

 Figure 4 shows another alternative embodiment. This variant includes the displacement device 50, the transmission element 38 crossed here by the threaded rod 56 in an internal threading zone 66. The threaded rod 56 is supported on the toothed wheel segment 16 and thus forms the fourth zone coupling 42. The motor 60 is again mounted in the transmission element 36 and slides freely in the axial direction while being locked in rotation. When the motor 60 is powered and it turns the threaded rod 56 as indicated by the arrow, the external thread of the threaded rod 56 and the internal thread segment 66 of the transmission element 38 cooperate so that this element 38 performs a telescopic axial movement relative to the transmission element 36 which modifies the state of prestressing of the compensating spring 30.

 Figure 5 shows another variant. In this variant, the threaded rod 56 passes through the actuating element 36 and is thus supported by a third bearing zone against the casing 12. The motor 60 is housed in the transmission element 36, that is to say ie in a cylindrical segment thereof while being housed therein in rotation but sliding axially. When the motor 60 is supplied with power and it rotates the threaded rod 56, the axial displacement of the transmission element 36 then produced, displaces the two ends 32, 34 of the spring with respect to each other by spreading or bringing them together to modify the state of prestressing.

 Figures 6 and 7 each show a threaded rod device for changing the angular position and thus if necessary the axial length of the spring compensator 28. In Figure 6, the motor 60 is fixed to the housing 12 as a component associated with the coupling zone 40 of the transmission element 36; the motor carries the threaded rod 56 so that it is essentially directed transverse to the longitudinal direction of the spring compensator 28. When the motor 60 is supplied, the coupling zone 40 can be moved relative to the casing 12 essentially transversely to the longitudinal direction of the spring compensator 28 which can on the one hand modify the length of this spring compensator 28 and thus modify the state of prestressing and on the other hand modify the conditions of the angle of attack of the spring compensator 28 with respect to the gear wheel segment 16, that is to say modify the ratio of the lever arms. Thus, the action of the torque of the toothed wheel segment 16 generated by the spring compensator 28 is adjusted.

 In the embodiment of FIG. 7, the motor 60 is fixed relative to or on the toothed wheel segment 16 which in this case constitutes the compensator associated with the coupling zone 42. The threaded rod 56 is then engaged with a nut provided at the fourth coupling zone and it thus displaces this fourth coupling zone 42 essentially in the direction transverse to the longitudinal direction of the spring compensator 28 along the toothed wheel segment 16. In this case also by modifying the mounting position of the spring compensator 28 both with respect to the casing 12 and with respect to the toothed wheel segment 16, not only the prestressing conditions are modified but also the conditions of torque action between the spring compensator 28 and the gear wheel segment 16.

 It should be noted that such an adjustment between a coupling zone or a component associated with it, can obviously also be provided at the level of the first support zone 22 or of the second support zone 24 in FIG. 1, that is to say between the output element 20 and the toothed wheel segment 16 or between the components to bias the member to be operated. Here it must be ensured that for the electric motor to be provided or fixed in the area of the various components, it is necessary to be able to install power supply lines.

It should also be noted that, in particular the embodiment shown in FIGS. 6 and 7 and making it possible to modify the lever arm ratios, a displacement device according to the invention can be used to create the emergency operating conditions mentioned above. If we again consider FIG. 1 for this purpose, and if we assume that in the basic state represented in this figure, the electric motor 14 breaks down or has a fault, we can then execute an operation actuation, that is to say to rotate the toothed wheel segment 16 clockwise even if the position of the spring compensator 28 is changed so that its longitudinal axis L1 is raised again above the axis of rotation A1 and then exerts an effective torque on the gear wheel segment 16. This displacement of the longitudinal axis
L1 can be produced as described above with reference to FIGS. 6 and 7. The return of the toothed wheel segment 16 to the position shown in FIG. 1 can in fact be obtained in this way by putting the longitudinal axis L1 of the spring compensator 28 back to the position shown in Figure 1; under these conditions, for example, in an application to a friction clutch of a motor vehicle, there will be an additional restoring force created by an appropriate force accumulator. To assist the prestressing of the compensating spring 30 or / and to modify the position of the axis of rotation, it is possible to proceed in the manner described below.

 The embodiment of FIG. 8 shows a displacement device 50 mounted so as to cooperate between the third coupling zone 40 of the spring compensator 28 and the casing 12. This device 50 comprises a motor 60 and a threaded rod driven in rotation by this engine. This rod is engaged at the third coupling zone 40 with a threaded orifice or nut 54 provided on the transmission element 36. By supplying the motor 60, the third coupling zone 40 can be moved relative to the casing 12 by removing it or bringing it closer to the casing; this creates a modification of the prestressing conditions of the compensating spring 30. It is also possible to act on the behavior of the spring to have a pivoting connection either at the third coupling zone 40, that is to say in the connection zone between the transmission element 36 and the threaded rod 56 or in the connection range between the motor 60 and the casing 12.

 FIG. 9 shows an alternative embodiment in which the displacement device 50 is provided between the fourth coupling zone 42 of the transmission element 38 of the spring compensator 28 and the toothed wheel segment 16 but its construction is practically identical to that shown in Figure 8 and described on this occasion.

 The use of a threaded rod mechanism can also be used to move the position of the bearing zone formed or defined by the axis of rotation A1 of the toothed wheel segment 16 in the casing 12. For this, as shown in FIG. 10, one or two pieces 70 in the form of plates provided on the casing form a movement path 72 of constant radius (r) relative to the axis of rotation A2 of the toothed wheel or of the screw wheel or the like meshing with the gear wheel segment 16. This or these guide paths 72 receive a component carrying the gear wheel segment 16 in rotation guided by at least one segment. This component further meshes with the threaded rod 56 through an opening with an internal thread or a nut or the like. The threaded rod is rotated by the motor 60. In the present case, the motor 60 is pivotally mounted on the casing 12. When the motor 60 is driven, the threaded rod 56 must be turned so that the distance between the component 74 and the motor 60 varies and that consequently this component 74 moves with the axis of rotation A1 of the toothed wheel segment 60 along the guide path 72. It follows that for an engagement produced at the same time between the toothed wheel segment 16 and the toothed wheel which drives the latter, the position of the bearing range of the toothed wheel segment 16 varies in the casing; this makes it possible to modify on the one hand the ratio of the lever arms between the toothed wheel segment 16 and the spring compensator 28 and on the other hand the ratio of the lever arms between the toothed segment 16 and the output element 20 .

 FIG. 11 shows an embodiment in which the spring compensator 28 is pivotally connected in the third coupling zone 40 with the first end segment 76 of a lever 78. A second end 80 of the lever 78 is connected pivotally to the housing 12.

Between the first and second ends 76.80, the lever is engaged by a screw connection with the threaded rod 56 via an orifice with internal thread or a nut 54 pivotally provided thereon; the threaded rod 56 is rotated by the motor 60 itself mounted to pivot relative to the casing 12. By supplying the motor 60 and under the effect of the induced rotation of the threaded rod 56, the first end zone is moved 76 of the lever 78 relative to the casing 12 by moving it apart or bringing it closer so that the third coupling zone 40 is also displaced relative to the casing 12 (approaching or moving away) thus producing the expansion or tensioning of the compensating spring 30.

 FIG. 12 shows a variant of the embodiment of FIG. 11 in which the lever 78 is pivotally mounted on the toothed wheel segment 16 and the fourth coupling zone 42 is coupled on transmission isolation 38 with the first end zone 76 of the lever 78 at the level of a cavity 79. It is possible in principle in this case to mount the motor 60 itself pivoting on the toothed wheel segment 16 or that the motor 60 is pivotally mounted in the casing 12. It the result would be that for a pivoting movement of the toothed wheel segment 16, in addition to the position variation produced in any case of the spring compensator 28 relative to the toothed wheel segment, there would also be a displacement of the lever 78 relative to the toothed wheel segment 60 and thus a displacement of the fourth coupling zone 42 relative to the toothed wheel segment 16 with as a consequence a modification of the state of prestressing of the compensating spring 30 .

 FIG. 13 shows an embodiment in which, using the lever 78, the third coupling zone 40 can be displaced essentially in the transverse direction relative to the longitudinal direction of the spring compensator 28 along the casing 12. For this, the lever 78 has a cavity 82 in the form of an oblong hole in its end region 76. This oblong hole causes a guide pin 84 of the transmission element 36. By turning the threaded rod 56 and due to the tilting caused by lever 78, we arrive at the movement mentioned. It should be noted that a corresponding arrangement can also be provided on or at the level of the fourth coupling zone 42 on the toothed wheel segment 16.

 In the various embodiments of the lever described, it is also possible to influence the different support points of the levers, that is to say the points of connection of the different components with the levers or the bearing points of the levers to modify the characteristic of the force. It should be noted once again here that these embodiments in which levers are used can also be applied within the ranges initially described to generate modifications influencing the zones, for example the second coupling zone or the first coupling zone or for example also at the mounting of the sensor cylinder 26 on the housing 12 to move the cylinder 26 relative to the housing 12. It is also possible to use the embodiments of the levers in connection with a guide path along which the slide is component 74 shown in FIG. 10 and receiving the gear wheel segment 16 in rotation.

 FIG. 14 shows an embodiment in which the displacement device 50 comprises a toggle mechanism 86. This toggle mechanism 86 comprises two arm segments 88, 90 pivoting with respect to each other.

The arm segment 88 is articulated to the casing 12 and the arm segment 90 is connected to a sliding rod 92 slidably housed in its longitudinal direction in the casing 12; this rod is coupled to the third coupling zone 40 to the spring compensator 28. At the pivoting connection between the two arm segments 88, 90, the threaded rod 56 cooperates with an orifice with internal thread or a nut element connected to the arm segments 88.90. By turning the threaded rod 56, the respective angular position of the arm segments 88, 90 is modified so that the sliding rod 92 and thus also the third coupling zone 40 move relative to the casing 12.

 An identical arrangement is obviously possible as a variant and in addition also in the region of the toothed wheel segment 16.

 FIG. 15 shows the use of the toggle mechanism 86 for laterally sliding the third coupling zone 40 relative to the casing 12. It can be seen that the arm segment 90 acts directly on the transmission element 36 and slides this transversely to the longitudinal direction of the spring compensator 28 when the threaded rod 56 rotates. In this embodiment, the motor 60 can be fixed to the casing 12; alternatively or in addition, it is also possible to press the threaded rod 56 as shown on the casing 12. This arrangement also transposes to the fourth coupling pad 42, that is to say to the toothed wheel segment 16 or to slide the first and second coupling zone with respect to the bearing zone defined by the axis of rotation A1, with respect to the casing 12. In this case, care must be taken to have a guide path or guide curve like that shown in Figure 10.

 To modify the action ratios, it is possible in this case to move the screwing zone between the threaded rod 56 and the toggle mechanism 86 outside the zone of coupling of the two arm segments 88, 90 and to move this area on one of the arm segments 88.90. In addition, in all of the lever variants shown, it is possible to adapt the shape of the levers to the necessary force ratio, that is to say that the levers can optionally be bent, folded or bent.

 In the embodiment in FIG. 16, a lever 94 is pivotally mounted on the casing 12. This lever acts in an intermediate zone by a connecting element 90 on the transmission range 32 of the compensating spring 30. The engine 60, c that is to say the threaded rod 56 driven in rotation by the motor is pivotally coupled by an internal thread element 96 engaged with the threaded rod 56 and with the lever 94 to slide the transmission zone 32 of the compensating spring 30 essentially in its longitudinal direction. Under these conditions, either the motor 60 is carried directly by the casing 12, or the threaded rod 56 can be pressed in rotation by its free end in the casing 12. It should be noted that it is also possible here to come into the positions as those indicated by the references 60 ', 56', 96 ', that is to say that in this case, the drive unit comprising the components 60', 56 ', 96' acts at the level of the the free end of the lever 94 which certainly makes it possible to create good conditions for the lever arm on one side and which however also makes it possible to support the race, whereas in the first case, there is a reduction in the race.

 FIG. 17 shows a variant of the embodiment shown in FIG. 16 in which the lever 94 is practically supported at the level of the housing 12 against which the spring compensator 28 bears with its support zone 40. For the rest, the embodiment shown in FIG. 17 corresponds essentially to that of FIG. 16. In this case, there are also two positioning possibilities for the sliding device 50 comprising the motor, the threaded rod and the internal thread element as described with reference to Figure 16.

 In the embodiment of FIG. 18, the motor 60 is again fixed to the casing 12 and its output shaft carries a straight gear 102. The straight gear 102 meshes with a straight gear 104 adapted by its orifice threaded on an external thread 106. The external thread 106 is supported by the casing 12 and comprises a guide slot 108 in which slides a guide pin forming the third coupling zone 40 or stud of the transmission element 36, the sliding in the longitudinal direction of the spring compensator 28.

 The rotation of the right wheel 102 and thus of the right wheel 104 results in the meshing of the internal and external toothing of the right wheel 104 the displacement of the spring compensator 28 in the longitudinal direction; it follows that the third coupling zone 40 moves relative to the casing 12 and relaxes or tends the compensating spring 30. If in the present case one wanted to associate the element with external thread 106 and if necessary also the wheel tooth 104 at the spring compensator 28, the fulcrum 40 ′ of the external threaded element 106 should be considered as the third coupling zone. It should be noted that it is possible to have a corresponding embodiment at the level of the connection between the spring compensator 28 and the toothed wheel segment 16. It appears that the toothed wheel 102 has a much greater length than the toothed wheel 104. This even allows during axial sliding of the toothed wheel 104 to keep the '' between the gear wheels 102,104.

 FIG. 19 shows such an arrangement for modifying the angular position of the spring compensator 28.

In this embodiment, the toothed wheel 104 rotates in a slot 108 of the casing but cannot slide in the longitudinal direction of the element with external thread 108.

When the toothed wheel 102 rotates and thus drives the toothed wheel 104, the external thread element 106 moves relative to the casing 12 and thus also slides the third coupling zone 40.

 In the embodiment of FIG. 20, the toothed wheel 102 is coupled to a first element with oblique surfaces 112 by the toothed wheel 104; this element 112 can thus essentially rotate around an axis of rotation A5 corresponding to the longitudinal axis L1 of the spring compensator 20. The first biased surface element 112 comprises, as shown in FIG. 21, a first biased surface 114 , produced by a propeller, which extends around the axis of rotation A5 in an extension range corresponding practically to 360. A second element with oblique surfaces 116 is associated with the transmission element 36 with a second oblique surface 118, this element not rotating relative to the element 36. In the basic position represented in FIG. 20, one of the surfaces formed by the two elements with biased surfaces 112,118 is in the minimal state since the two elements are nested axially, almost completely like a toothing. If the toothed wheel 102 rotates the wheel 104 and thus the first element with biased surfaces 112, the two biased surfaces 114,118 slide relative to each other so that the axial length of the unit formed by these two elements 112,116 increases, thus spreading the coupling zone 40 relative to the casing 12. In this case, the bearing zone 40 ′ which rotates the first element of oblique surfaces 114 on the casing 12 could be considered to be third coupling zone if the inclined surface elements 114,116 were to be associated again with the spring compensator 28.

 FIG. 22 shows the use of such a biased surface device for modifying the angular position of the spring compensator 28. The axis of rotation of the first biased surface element is located essentially transversely to the longitudinal axis of the compensator with spring 28. It is also noted in this case that it is possible to have a corresponding embodiment at the level of the fourth coupling zone 42.

 It should be noted that in this embodiment, there will in principle be no force which could bring the surface elements biased 112,116 for a corresponding relative position of rotation. This is why an additional, opposing force component can be provided, for example in the form of a spring providing a force F shortening the assembly formed by the two oblique surface elements 112, 116.

 Figure 23 shows another embodiment which, using two components rotating relative to each other, creates an axial extension like that used in the embodiment of Figures 20 and 22. In the case present, a component 120 which is for example driven in rotation by the toothed wheel 104, has a guide groove 122 in its wall, this groove receiving a guide pin 124 of a component 126 cooperating telescopically with the component 120. When component 120 is in rotation (or optionally in addition or alternatively component 126), the axial length is shortened with the consequence of the displacement of the assemblies coupled to these components, one relative to the other as shown in Figures 20 to 22.

 FIG. 24 shows an embodiment creating a sliding force by a cam element 130 with a cam surface 132 eccentric with respect to the axis of rotation A3. This cam element 130 acts on a sliding element 134 slidably housed in its longitudinal direction in the casing 12. The rotation of the cam element 130 also rotatably mounted in the housing 12 displaces the sliding element 134 essentially transversely to the longitudinal direction of the spring compensator 28 and thus drives the third coupling zone 40. In this case, there is again provided a device generating an opposing force which, when the cams 130 are rotated in the opposite direction, generates an opposing force F which can lift the spring compensator 28 according to FIG. 24.

 FIG. 25 shows the use of the cam element 130 for sliding the third coupling zone 40 essentially in the longitudinal direction of the spring compensator 28. This sliding causes the tensioning of the compensator spring 30, which makes it possible to modify The effect of force on the toothed wheel segment 16.

 FIG. 26 shows the sliding rod element 134 provided with an inclined surface 136 coming against an inclined surface 138 complementary to a wedge-shaped element 140. The wedge-shaped element 140 is movable by a linear motor of known type for example a threaded rod device like that described above or a rack device, relative to the casing 12 essentially transversely to the longitudinal direction of the spring compensator 28 so that by sliding the surfaces at an angle 136,138 l one with respect to the other, the sliding rod element 134 slides in its longitudinal direction relative to the casing 12 and again moves the third coupling zone 40 relative to the second coupling zone 42 by moving it apart or in bringing it closer.

 Figure 27 shows the use of this device to move the third coupling zone 40 essentially trans

 In the embodiment of FIG. 28, Sliding rod isolation 134 carries a conical element 142 whose conical surface is in abutment against two elements with oblique surfaces 144,146 movable relative to the casing 12. By the common displacement of these two elements 144,146 relative to each other (in the direction of approximation or spacing), by the reciprocal sliding of the oblique surfaces, the conical element 142 is moved to the right or to the left according to FIG. 28 and the sliding rod element 134 moves in the casing 12, in its longitudinal direction as well as in the longitudinal direction of the spring compensator 28.

 FIG. 29 shows the use of this device for moving the coupling zone 40 essentially transversely to the longitudinal direction of the spring compensator 28. In this case, too, an opposing force F is required to return the coupling zone 40 towards the top according to FIG. 29 when the two oblique surface elements 144, 146 are separated.

 FIG. 30 also shows a tensioned cable 148, for example a steel cable or the like, wound around the cone segment 142 and of which a turn 150 forms a diaphragm opening in which the cone element 142 penetrates. By stretching the cable 148 , the section of this opening is reduced so that the cone element 142 is pushed to the right according to FIG. 30 and displaces the third coupling zone 40 towards the second coupling zone 42. This diaphragm-shaped opening can also be produced by a mechanical diaphragm such as, for example, those of a camera.

 FIG. 31 shows such an arrangement for sliding the third coupling zone essentially transversely to the longitudinal direction of the spring compensator 28. In this case, too, an opposing force F is required to return the coupling zone 40 upwards according to the Figure 31 if necessary or desired.

 In FIG. 32, the third coupling zone 40 is moved by means of a rack 152 sliding in the housing 12 in the longitudinal direction or along the longitudinal axis of the spring compensator 28; the rack 152 meshes with a drive pinion 154 rotated by a motor not shown. FIG. 33 shows this embodiment serving to move the third coupling zone 40 essentially in the direction transverse to the longitudinal direction of the spring compensator 28. It should be noted that in this pinion / rack arrangement, instead of the pinion, it is possible to also use a screw wheel or the like.

 According to FIG. 34, the third coupling zone 40 is displaced by a linear drive essentially in the longitudinal direction of the spring compensator 28.

This linear drive can for example be a magnetic linear drive with a coil fixed relative to the casing and a core sliding in or through the coil.

In this case also, it is possible to envisage the use of a generally known linear electric motor or of a linear drive device with polar claws.

 According to FIG. 35, this sliding device 50 comprising a linear drive is used to move the third coupling zone 40 essentially in the direction transverse to the longitudinal direction of the spring compensator 28. According to the embodiment of the linear drive depending on whether Whether or not a force is generated in the two directions of movement, it will be necessary, if necessary, to create a restoring force.

 According to FIG. 36, the spring compensator 28 comprises, as sliding device 50, a helical element made of a shape memory alloy or of a bimetal. This element 160 bears on one side against the transmission element 36 and on the other side against a coupling element 158, the latter here forms the third coupling zone 40 or carries the latter. The coupling element 158 comprises a latching rod 164 penetrating into a complementary latching orifice 166 of the transmission element 36 to allow relative movement between these two components only if by heating by the heating installation 162 , the element 160 begins to modify its shape and in particular begins to expand. This avoids having to constantly energize the heater for adaptation measures. The axial extension of the element 160 produced by this heating effect or if necessary the shortening of the element 160 then makes it possible to move the two elements 36,158 relative to one another (in the direction of bringing together or the spacing) with the consequence of modifying the prestressing position of the compensating spring 30.

 FIG. 37 shows the use of such a device for the lateral displacement of the third coupling zone 40 with respect to the longitudinal axis or with respect to the longitudinal direction of the spring compensator 28.

The helically wound element, made of a shape memory alloy or a bi-metal, bears at one end against the casing 12 and at its other end against the sliding rod element 134; the latching rod 164 is then fixed to the casing 12 and the latching effect is created relative to the sliding rod element 134.

 In these embodiments, it could in principle also be envisaged to produce this element in shape memory alloy directly as a heating element or as a heating wire so that by the electrical supply and without requiring a heating element, it is possible to heat this element 160 and deploy or shorten it axially according to the shape memory.

 FIG. 38 shows an embodiment in which the sliding rod element 134 is slidably mounted in the casing 12, that is to say in an opening provided therein, essentially in the direction transverse to the axis longitudinal of the spring compensator 28. At one end, as already indicated above, the sliding rod element 134 is coupled to the transmission element 36; its other end is connected by a guide rod 172 or similar means, in engagement with a guide path or a guide groove 170 provided in a rotating disc part 168. The guide groove 170 is eccentric with respect to the 'axis of rotation A4 of the disk 168; thus, the rotation of the disc 168 controlled by a motor or the like, leads the guide rod 172 into the guide groove 170 which moves the sliding rod 134 in isolation relative to the casing 12.

 FIG. 39 shows this embodiment for the sliding of the third coupling zone 40 relative to the fourth coupling zone 42.

 It should be noted once again that all of the embodiments shown in FIGS. 14 to 39 and acting between the casing 12 and the spring compensator 28 can also act between the toothed wheel segment 16 and the spring compensator 28. It is It is also clear that these sliding devices, produced or acting differently, can also be used to create a relative movement for example between the output element 20 and the toothed wheel segment 16, the sensor cylinder 26 and the casing 12 as well as the 'output element 20 and the part actuated by it, for example a diaphragm spring of a clutch or the like. The use of these sliding devices to move the axis of rotation A1 of the toothed wheel segment 16 relative to the casing 12 is also possible and in this case, as already indicated, it is necessary to provide guide tracks to obtain a determined sliding of this toothed wheel segment 16.

 FIG. 40 shows another embodiment of the actuator 10 according to the invention; this embodiment essentially corresponds to that already described with the aid of FIG. 1. In the embodiment of FIG. 40, the toothed wheel segment 16 has an oblong hole 182 in which rests in sliding the spring compensator 28 at the fourth coupling zone 42. For this, the spring compensator 28 may include a guide rod or a guide stud 184 at its second transmission element 38. This guide stud 184 penetrates into a cavity or opening 186 in the form of a curved oblong hole in a disc part 188. The disc part 188 is guided in a movable rectilinear direction in the direction of an arrow P3.

A nut element 180 is fixed on the disc part 188 receiving a threaded rod 56 itself rotated by a screw drive or the like by the electric motor 60. This means that a rotation of the threaded rod 56 causes the disc-shaped part 188 to move in the view in FIG. 40 in one direction or the other in the longitudinal direction of the threaded rod 56.

 This maneuver performed by the actuator 10 drives transmission isolation 38 by the toothed wheel segment 16 which then rotates, via the stud 184 so that this stud 184 follows the cavity or the opening 186 of the disc part. 188 and can also slide in the opening in the form of an oblong hole 182. This in principle means that this operation also modifies the relative position of the fourth coupling zone 42 with respect to the toothed wheel segment 16, in particular the distance from the axis of rotation A1. The possibility of sliding the disc part 188 makes it possible to modify the amplitude or the nature of the position modification between the third coupling zone 40 and the toothed wheel segment 16. This can be done on the one hand by the form of the cavity 186 and on the other hand by the degree of sliding of the disc part 188. It is thus possible to influence the characteristic of the force generated by the actuator according to the invention.

 It appears that in the actuator according to the invention, there can be a large number of variants. By carrying out such modifications, it is possible to adjust the operating characteristic of the actuator 10, that is to say the characteristic of the force emitted or the characteristic over time. This makes it possible to adapt the actuator 10 according to the invention in a very simple manner to changes in operating conditions or even as described, in order to carry out emergency functions. It is also possible to detect operating conditions which change by detecting the current supplying the motor 14 and by defining according to the intensity of the current which flows, whether or not to make modifications. As a variant, it is also possible, thanks to separate sensors, to enter a certain characteristic or a certain operating state, for example a state of wear of a clutch disc or else to transmit a signal to a control device. so that, depending on this, necessary adaptations are carried out according to the different possibilities of adaptation. It should be noted once again, that the actuator according to the invention makes it possible to undertake, at the same time, modification measures in the most different ranges in that in all the desired ranges, the displacement devices can be integrated. or the sliding devices described and located essentially in relation to the spring compensator 28.

 In the foregoing, reference has often been made to the fact that the sliding device makes it possible to move a coupling range with respect to the associated components, for example moving it away from them. Considering the spring compensator 28, it appears that one can move a coupling range in the direction of the longitudinal axis L, of the spring compensator 28 obviously also causing a modification of the state of prestressing of the spring 30. This displacement of a coupling range of the spring compensator 28 also modifies the total length for example shortens it so that the interval between this coupling range of the spring compensator 28 and the corresponding component for example the housing 12, can receive another set, for example lever or wedge mechanisms as shown. If one wanted to associate with all the volume become free of the components of the spring compensator filling the volume thus released and not the corresponding components, that is to say for example the casing, such a modification would ultimately lead to the modification Also indicated according to the invention is the state of spring preload. The support of the spring compensator against the casing or another associated component could be done by the assembly filling the gap and which can then include the coupling zone.

Claims (1)

1) Actuator in particular for controlling an automatic vehicle clutch, applicable to an automatic gearbox or for serving as a brake actuator or similar means comprising: a motor (14) carried by a casing (12) and acting on an element of drive (16) for moving the latter, Drive isolation (16) being carried movably in a support range (A1) relative to the casing (12) depending on the action by the motor (14) , * an output element (20) acting by a range neck region (22) (first coupling region 22) on the drive element (16) and by its other coupling region (24) (second region coupling 24) on the member (26) to be engaged and if necessary, a force compensator (28) which acts by a coupling zone (40) (third coupling zone 40) on the housing (12) and by another coupling zone (42) (fourth coupling zone 42) on the drive element (16), characterized by a adapter (50) which adapts the actuator (10) to changes in operating condition. 2) Actuator according to claim 1, characterized in that the adapter (50) ensures the adaptation measures to influence the components (20,28,16) of the actuator (10). 3) Actuator according to any one of claims 1 or 2, characterized in that the adapter (50) is designed to: a) modify a compensating force generated by the force compensator (28) or / and, b ) modify the position of the first coupling zone (20) relative to the drive element (16), c) modify the position of the second coupling zone (24) relative to the member to be operated (26 ) or / and, the casing (12) or / and, d) modifying the position of the third coupling zone (40) relative to the casing (12) or / and modifying the force compensator (28) or / and, e) modifying a position of the fourth coupling zone (42) relative to the drive element (16) or / and the force compensator (28) or / and, f) moving the fourth coupling zone (42 ) relative to the drive element (16) in the execution of an operating operation using the actuator (10) and / or, g) modifying the position of the support area (A1) by rap port to the casing (12) or / and to the motor (14). 4) Actuator according to claim 3, characterized in that the force compensator (28) comprises a force generator (30) with elastic spring effect and the adapter (50) can modify the state of prestressing of the force generator (30). 5) Actuator according to claim 4, characterized in that the adapter (50) can modify and in particular shorten the distance between two stressing zones (32,34) of the force generator (30), this distance being measured in the direction longitudinal of the force compensator (28). 6) Actuator according to one of claims 3 to 5 characterized in that the adapter (50) changes the distance between the third coupling zone (40) and the fourth coupling zone (42). 7) Actuator according to claim 6, characterized in that the adapter (50) moves the third coupling zone (40) relative to the casing (12) essentially in a longitudinal direction (L1) of the force compensator (28) in moving it away from the fourth coupling zone (42) or vice versa. 8) Actuator according to any one of claims 6 or 7, characterized in that the adapter (50) displaces (brings closer or apart) the fourth coupling zone (42) relative to the motor (16) essentially in a longitudinal direction (L1) of the force compensator (28) relative to the third coupling range (40). 9) Actuator according to any one of claims 3 to 8, characterized in that the adapter (50) modifies a position of the third coupling range (40) relative to the casing (12) essentially in a direction transverse to the longitudinal direction (L1) of the force compensator (28). 10) Actuator according to any one of claims 3 to 9, characterized in that the adapter (50) modifies a position of the fourth coupling range (42) relative to the motor (16) essentially transversely to the longitudinal direction ( L1) of the force compensator (28). 11) Actuator according to any one of claims 3 to 10, characterized in that the adapter (50) modifies the distance between the first coupling zone (22) of the bearing zone (A1) and / or an angular position of the first coupling zone (22) with respect to a reference angle position defined on the motor (16). 12) Actuator according to any one of claims 3 to 11, characterized in that the adapter (50) modifies the position of the second coupling pad (24) essentially in a longitudinal direction (L2) of the element outlet (20) relative to the member (26) to be operated or / and the casing (12). 13) Actuator according to any one of claims 3 to 12, characterized in that the adapter device (50) modifies a position of the second coupling pad (24) essentially transversely relative to a longitudinal direction (L2) of the outlet element (20) relative to the casing (12) and / or the member (26) to be actuated. 14) Actuator according to any one of claims 3 to 13, characterized in that the drive element (16) is a drive wheel or a drive wheel segment (16) engaged with a wheel of the motor (14) rotating around an axis of rotation (A2) and the adapter (50) displaces an axis of rotation (A1) defining the bearing region (A1) of the drive element (16) with a distance (r) essentially constant relative to the axis of rotation (A2) of the motor wheel (14) relative to the casing (12) or to the motor (14). 15) Actuator according to claim 14, characterized in that the adapter (50) comprises a sliding device (50) which slides an assembly (74) receiving the drive element (16) along a guide path (72) essentially concentrically surrounding the axis of rotation (A2) of the motor wheel (14). 16) Actuator according to any one of claims 1 to 15, characterized in that the adapter (50) comprises a sliding device (50) which displaces a component forming or comprising a range neck area (40) or a range of bearing (A1) with respect to an associated component. 17) Actuator according to claim 16, characterized in that the sliding device (50) comprises at least one threaded rod (56) driven in rotation and carried relative to the coupling or bearing pad (40) or of the corresponding component (12), and the corresponding component (12) or the components which form or comprise the bearing or coupling zone (40) is provided with a nut element (54) which moves in the longitudinal direction of the threaded rod (56) when the latter is rotated. 18) Actuator according to claim 17, characterized in that at least one threaded rod (56) is oriented with its longitudinal direction in a direction in which one wants to move the coupling zone (40) or bearing with respect to the corresponding component (12). 19) Actuator according to any one of claims 17 or 18, characterized in that at least one threaded rod (56) is coupled by a lever device or an articulated device (78,86) to the corresponding component (12) or to the coupling (40) or bearing area. 20) Actuator according to any one of claims 16 to 19, characterized in that the sliding device (50) comprises a first component of inclined surfaces (104, 112) driven in rotation about an axis (A5) relative to the coupling zone (40) or bearing or corresponding components, this component having a first oblique surface (114) extending in a helix relative to the axis of rotation (As), * as well as a second component of inclined surfaces (106,  116) not rotatable with respect to the associated component or to the  coupling zone (40) or bearing, this second component  having a second oblique surface (118) extending sui  vant a helical path relative to the axis of rotation  (A5) of the first component with oblique surfaces (112), * preferably, by relative rotation between the first and  the second oblique surface (114, 118) in the form of a helix,  the length of the assembly formed by the first is modified and  of the second surface component (112,116).  21) Actuator according to claim 20, characterized in that the first and the second oblique surface form an external or internal thread surface.  22) Actuator according to claim 20 or 21, characterized in that the first and the second oblique surface (112,116) have an angular extension at most equal to 360 relative to the axis of rotation (As).  23) Actuator according to any one of claims 16 to 22, characterized in that * the sliding device (50) comprises a che unit  guide mins (120,130,140,144,146,168) coupled to  the coupling zone (40) or bearing zone or to the component  associated (12) as well as a guided unit (126,134,134), in  taken with a guide path (122,132,170) of the unit  with guide tracks (120,130,140,144,146,168), * and to create the guide movement, the track unit  guide (120,130,140,144,146,168) or / and the unit  guided (126,134,134) is driven by a movement  of rotation and / or linear.  24) Actuator according to claim 23, characterized in that the guideway unit (120,130,168) has a guide groove (122,170) extending essentially helically or eccentrically with respect to an axis of rotation and the guided unit (126,134) includes a guide pin (124,172) extending into the guide groove (122, 170).  25) Actuator according to claim 23, characterized in that the guideway unit (130) comprises a guide cam (130) with an eccentric cam surface (132) and the guided unit (134) comprises a follower cams (134).  26) Actuator according to claim 23, characterized in that the guide unit (140,144,146) comprises a wedge-shaped device (140,144,146).  27) Actuator according to any one of claims 16 to 26, characterized in that 'the sliding device (50) comprises a device  with coupling opening (148,150) coupled to the zone of  coupling (40) or bearing zone or to an associated component  (12), this device having a variable opening section  and, 'the corresponding component (12) or the coupling zone  (40) or bearing comprises a penetrating support element  in the coupling opening device (148,150) with  a variable opening section, a support element which  follows the section variation.  28) Actuator according to any one of claims 16 to 27, characterized in that the sliding device (50) comprises a rack (152) coupled to the coupling (40) or bearing zone or to the corresponding component (12), as well as a pinion or a screw wheel (154) or similar means, driven in rotation and meshing with the rack (152) or the associated component (12) or the coupling (40) or bearing zone.  29) Actuator according to any one of claims 16 to 28, characterized in that the sliding device (50) comprises a linear drive unit (156) in particular a linear electric motor or a linear magnetic motor (156), coupled on one side to the coupling zone (40) or bearing zone and on the other side to the associated component (12).  30) Actuator according to any one of claims 16 to 29, characterized in that the sliding device comprises a bimetal device, a shape memory device (160) or similar means necked on one side to the coupling zone (40) or bearing area and on the other side to the associated component (12), as well as a control unit (162) preferably a heating unit (162) to influence the shape of the bimetal device, that of the device to shape memory alloy (160) or the like.  31) Actuator according to any one of claims 16 to 30, characterized in that the position of the fourth coupling zone (42) of the force compensator (28) relative to the drive element (16) can be modified by the movement of the drive element (16), induced by the motor (14) and the sliding device (50,56,188) makes it possible to modify the characteristic of variation of relative position between the fourth coupling zone (42 ) and the support zone (A1) of the drive element (16).