FR2749636A1 - ACTUATING DEVICE - Google Patents

Abstract

The invention relates to an actuating device 1 for controlling a mechanism located in the drive train of a vehicle, for example for switching and / or selecting the transmission ratios of a gearbox and / or for the actuation of a torque transmission system 2. The actuation device comprises a drive unit 3, a transmission mechanism, as well as an output element in conjunction with the drive unit, at least one spring 25 being provided to stress this output element.

Description

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  The present invention relates to an actuating device for controlling an actuable mechanism, such as for example a transmission or a torque transmission system, located in the motor train of a vehicle, this device comprising a drive unit. drive and an output element, operably connected to this unit via a drive link, and furthermore at least one energy accumulator by means of which a force can act directly or

  indirectly on the output element.

  Actuating devices of this type are known from German Offenlegungsschrift DE-OS 195 04 847. Among these actuating devices used with torque transmission systems, there has been described an actuating device which comprises an energy accumulator producing dynamic assistance and which is arranged to act linearly so that there is a relationship

  linear between the actuating stroke and the force exerted.

  The object of the present invention is to create an actuating device of the aforementioned type, which produces a modulation of force rate, such as, for example, a modulation of the pace of force as a function of the stroke, for the force exerted on the output element, which provides dynamic assistance of a drive motor in at least one direction of operation. In addition, the object of the invention is to create a device of the aforementioned type which can be arranged in an advantageous manner as regards the volume of space, the cost and the material costs. Another object of the invention is to create a device which has a

  improved operating capacity.

  This result is achieved according to the invention with actuating devices of the aforementioned type in that a force-engageable element is permanently operatively connected with the drive connection by means of a geometry contour. spatial, as for example

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  a cam profile, a cam device or a particular cam, and that the force exerted by the energy accumulator, which is provided in number at least equal to the unit, acts on the output element via the spatial geometry contour of the element. In addition, according to the invention, in an actuating device for controlling a control element that can be actuated, for example for switching or selecting transmission ratios of a transmission or for actuation of the torque transmission system located in the motor train of a vehicle, it is provided that the actuating device comprises a drive unit, possibly a transmission mechanism and an output element permanently connected to this via a drive connection, and also at least one energy accumulator biasing the output element, and it is advisable that a force-biasable element is spatial geometry, such as for example a cam disk, a cam profile and / or a particular cam, in the drive link between the drive unit e t the output element and that the force exerted by the energy accumulator, provided in number at least equal to the unit, acts on the element

  output via the spatial geometry contour.

  Furthermore, it is advantageous for the force-biasing member having a spatially geometric contour, such as a cam disk, a cam profile, or a particular cam, to be biased by the energy accumulator provided. in a number at least equal to unity, in the region of the geometrically geometric contour such that a force is transmitted to the output element from the energy accumulator and through the contour to

spatial geometry.

  According to another characteristic of the invention, it is advantageously provided that the force-biasable element having the spatial geometry contour such as a cam disk, a cam profile, a cam track, or a particular cam, an element that is set in motion upon actuation of the actuatable control element. For an actuating device, it is advisable that, during a dynamic stressing of the contour that can be urged by a force and during a movement of the element having the contour that can be biased by a force, a dynamic modulation of the action of the force exerted on the output element by the energy accumulator. In addition, it is advisable that the member having the force-biasing contour move in at least one direction upon actuation.

of the control element.

  Also, it is advisable that the member having the force-biasable contour can be moved in a linear direction and / or in a circular motion and / or in an axial direction and / or in a

  radial direction and / or in a circumferential direction.

  According to another characteristic of the invention, it is advantageous that the outline of the element, with spatial geometry and which can be biased by a force, is oriented in a linear direction and / or in an axial direction and / or in a direction radial and / or in a circumferential direction. 3 () In an exemplary embodiment of the present invention, it is advantageous that the force exerted by the energy accumulator, provided at the number at least equal to unity, on the contour of the element, with spatial geometry and can be biased by a force, essentially oriented in a linear direction and / or in an axial direction and / or in a radial direction and / or

a circumferential direction.

  In addition, it is advisable that the modulation of the contour of the spatially-geometric and force-responsive element be essentially oriented in a linear direction and / or in an axial direction and / or in a radial direction and or in a circumferential direction. It is advantageous that, during a dynamic stressing of the contour for example by means of a energy accumulator provided in number at least equal to one unit, the action of the force is carried out at least in the essential in the direction of

  the output element or in the opposite direction.

  In addition, it is advisable that, during a dynamic stressing of the contour for example by means of a energy accumulator provided in a number at least equal to unity, a division of the force exerted takes place at least in essentially in the direction of an actuating movement of the output member and / or in a direction perpendicular to that

actuating movement.

  Also, it is advantageous that a transmission mechanism is operatively disposed in the drive connection between the drive unit and the output member. It is advisable that the space geometry element having the force-biased contour is operably connected to the drive system, with an element located in the drive link, or with

the output element.

  Further, it is expedient that the space-constrained, force-responsive contour member has a cam disk, a cam track, or a particular rotatable cam having a one-dimensional or two-dimensional profile. Further, it is advisable that the spatially geometrically contoured and force-responsive member has a cam disk and a cam track or cam, arranged with a one-dimensional or two-dimensional and moveable profile.

linearly or axially.

  According to another characteristic of the invention, it is advantageous that the element having the geometrically contoured contour and being able to be biased by a force comprises a cam disk, a cam track or a particular cam.

  arranged with a three-dimensional profile.

  Also, it is advantageous that the energy accumulator, provided in a number at least equal to unity and which forces the spatial geometry contour by a force, comprises a sliding shoe, a roller and / or a bearing by which the energy accumulator leans against the

contour.

  In addition, according to another advantageous characteristic of the invention, the energy accumulator, provided in number at least equal to the unit solicits an organ, such as for example a lever, which is supported in a first zone with the possibility of displacement and which comprises in a second zone a sliding shoe, a roller or a bearing, which

  solicits the outline of the spatial geometry element.

  In addition, it is advisable that the energy accumulator, provided in number at least equal to unity, solicits an element which is supported by means of a linear guide and which furthermore comprises the contour of the element spatial geometry. In this regard, it is furthermore advantageous that the energy accumulator, provided in a number at least equal to 3 () the unit, solicits a clip-like element, which is supported in an area with the possibility of displacement and who

  solicits the outline of the spatial geometry element.

  It is advantageous that the energy accumulator, provided in a number at least equal to unity, solicits the element having the spatial geometry contour, for example in the zone of a

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  bearing, as on a trunnion arranged in a non-centered manner, the output member then pressing against an area of the

contour with spatial geometry.

  Also, it is advisable that the energy accumulator provided in a number at least equal to unity, solicits the element having the spatial geometry contour, for example in the area of a bearing, such as a trunnion disposed so non-centered, in which case an element biasing the output member bears against an area of the geometry contour

Space.

  In addition, it is advantageous for the support against the geometrically contoured contour and / or the stressing of the geometrically-shaped contour to be effected with sliding effect,

gyration or rolling.

  According to another characteristic of the invention, it is advisable for the drive unit to be an electric motor, an electromagnetic unit or an electromechanical unit. Also, it is advisable that the drive unit is a pressure actuated drive unit, such as a hydraulic, hydropneumatic drive unit.

or pneumatic.

  In addition, it is advisable that the action of the force acting on the output element of the actuating device is modulated, in relation to the movement of the geometrically contoured contour and the dynamic stress of this contour, in function of the actuating stroke of said

output element.

  Also, it is advantageous for dynamic assistance to occur at least in part of the race

  actuating the output element.

  According to another alternative embodiment of the present invention, it is advantageous for the dynamic assistance to undergo, if necessary, a sign change at

during the actuation race.

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  According to another characteristic of the invention, in an actuating device providing control of a control element that can be actuated, for example for switching and / or selecting the transmission ratios of a transmission and / or for an actuation of a torque transmission system, located in the drive train of a vehicle, there is provided a drive unit and optionally a transmission mechanism, and an output element operatively connected to the same; ci via a drive connection and can be actuated by a energy accumulator, provided in number at least equal to the unit, and it is advantageous that, during the action exerted by the accumulator of energy on the output element, this

  Accumulator operates as a low dead center spring.

  In this respect, it is particularly advantageous that two energy accumulators are located in mutually opposite positions and that they solicit the element of

  output each acting as a low dead center spring.

  Also, it is advantageous that the energy accumulator, provided in number at least equal to unity, is arranged as a low dead center spring, so that a first end zone is pivotally mounted on the output element and that the second extreme zone is

  mounted pivotally for example on the housing.

  According to another feature of the invention, it is advisable, for the control of a control element that can be actuated, for example for switching and / or selection of the transmission ratio of a transmission and / or for an actuation of a system 3 () torque, located in the drive train of a vehicle, the actuating device comprises a drive unit and, if appropriate, a transmission mechanism as well as an output element operably connected via a drive link so as to be actuable by at least two energy accumulators and is

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  advantage that, during the action exerted by the two aforementioned energy accumulators on the output element, these two energy accumulators are arranged as

  energy accumulators acting in series.

  In addition, it is advisable that at least one accumulator

  of energy is a prestressed energy accumulator.

  In addition, it is advisable that the energy accumulator, provided in the number at least equal to unity, is a spring, such as a pressure spring, an elastic blade, a loop spring or an elastic member formed of a metal, a rubber-like material or a plastics material. Also, it is sensible that the element having the spatial geometry contour is formed of a metal or a

plastic material.

  It is also advantageous for the element having the spatial geometry contour to form a single piece.

  with a component of the transmission.

  Also, it is advisable that the element having the spatial geometry contour forms one and the same piece

with the output element.

  In a variant of the invention, it is advantageous for the element having the spatial geometry contour to form a single piece with an element situated in the functional link existing between the drive unit and

the output element.

  In addition, it is advisable that the element having the spatial geometry contour is connected to an element located in the functional link existing between the unit.

  3 () and the output element.

  Other features and advantages of the invention

  will be highlighted in the following description, given

  by way of nonlimiting example, with reference to the appended drawings, in which: FIG. 1 represents an actuating device,

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  FIG. 2 shows an actuating device, FIG. 3 represents an actuating device, FIG. 4 represents a compensation device, FIG. 4 a represents a compensation device, FIG. Figure 5a shows a compensation device, Figure 5b represents a compensation device, Figure 6a represents a compensation device, Figure 6b represents a compensation device, Figure 6c represents a device. Figure 7a shows a compensation device; Figure 7b represents a compensation device; Figure 8a represents a compensation device; Figure 8b represents a compensation device; and Figure 9 represents another device. 10 is a cam disk, FIG. 11 is a cam disk, and FIG. diagram, - figure 13 represents a diagram, - figure 14 shows a part of an actuating device,

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  FIG. 14a shows an arrangement of energy accumulators, FIG. 14b shows an arrangement of energy accumulators, FIG. 15a shows an arrangement of energy accumulators, FIG. 15b shows a disposition of energy accumulators, FIG. energy accumulators; FIG. 16 represents an actuating device; and FIG. 17 represents another actuating device. FIG. 1 represents an actuating device 1 for producing an automated actuation, for example of a J5 torque transmission system 2 and / or an automated commutation of the reports of a transmission in the engine train of a vehicle, comprising a drive motor, a torque transmission system and a transmission. The torque transmission system can be engaged or disengaged automatically by means of this device and with the aid of a control unit or the torque that can be transmitted by the torque transmission system can be controlled in a targeted manner . The transmission can be a manually or automatically switchable transmission and, in the case of an automatically switchable transmission, the reports can be engaged, changed or exited in a targeted manner using the device. The reports can be ordered successively or in any sequence in

  function of the kinematics of the device.

  The actuating device 1 for automated actuation of a torque transmission system and / or a transmission, comprises a drive unit 3, which can be embodied for example in the form of an electric motor. The drive unit of the actuator may also be provided as an electromagnetic unit or as an agent operated unit.

  pressure, in particular a hydraulic or pneumatic unit.

  The embodiment of Figure 1 shows a housing 4 of the actuating device 1, wherein is housed the electric motor 3, the output shaft 5 of the motor being supported at 6, 6a and 7. The electric motor 3 can also be mounted externally on the housing 4 and in this case, the output shaft 5 of the motor enters the housing 4 through an opening provided therein. The polar housing 3a of the electric motor 3 is connected to the casing 4 of the device, for example by bolting, riveting or by means of a fitting connection. In this case, for example, the output shaft of the motor

  to ensure that a drive link is established.

  A transmission mechanism may be arranged after the output shaft of the motor so that the driving movement, such as a rotational movement of the output shaft of the electric motor, can be converted for example into another form of transmission. movement. The exemplary embodiment of FIG. 1 represents a worm gear transmission mechanism following which a transmission mechanism is arranged.

crank.

  It is provided, preferably in an area between the bearings 6 and 7, a worm connected to the output shaft 5 of the engine, at least in substantially non-rotating manner. This worm is not shown in Figure 1, but it is part of a worm transmission mechanism. This worm is engaged

with a tangent wheel 8.

  In place of a worm drive mechanism, however, other transmission mechanisms can be used, such as planetary gear transmissions, spur gear transmissions, bevel gears, transmissions with

  threaded spindle or other transmissions.

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  The worm drives the tangent wheel 8 which is rotatably mounted about the axis 9. In addition, through the journal 10, a crank shaft 11 is connected to the tangent wheel so as to solicit or actuate a piston 12 of a pressure-actuatable actuating cylinder of the actuating device. The element 11, like a crank shaft, can be drivingly connected to a piston 12 of a pressure actuated cylinder, such as a hydraulic emitter cylinder, and can be controlled by means of an axial shift of the piston. piston 12 of the emitter cylinder, the axial position of the piston 14 of a receiver cylinder, such as a hydraulic receiver cylinder 15. The pressure medium transmission channel 12, 13, 14 can be arranged as a hydraulic or

like a pneumatic way.

  The connection between the crank pin 11 and the piston 12 of the emitter cylinder can be created by means of a connecting system 16, which is arranged in the manner of a ball joint or a universal joint and which is furthermore realized so that, during an assembly, a

  assembly is facilitated by means of interlocking.

  The outlet portion 17 of the hydraulic slave cylinder serves as an outlet part for the actuating device which, in this embodiment, acts on a release fork 18 so that the axial position of a disengaging bearing 19 can be adjusted or changed to engage or disengage the clutch in a targeted way

  or to set a target value transmittable torque.

  The torque transmission system 2 has been shown in the form of a friction clutch comprising a pressure plate 20, a clutch disc 21, an annular spring 22, which is mounted on a steering wheel 23, the cover of clutch being designated by 24. The clutch bearing 19 actuates the annular spring 22 during a

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  axial movement, which produces a clutch or disengagement of the clutch. The friction clutch may be a clutch with automatic wear compensation adjustment. In addition, the torque transmission system can be a disk clutch or a bridging clutch of a

  torque converter, or another clutch.

  The friction clutch can be a dry friction clutch or a friction clutch

  operating in a wet process in a fluid.

  The transmission of the vehicle can be arranged in the form of a manually commutated transmission or in the form of an automated switching transmission. In addition, the transmission may be an automatic transmission, such as an automatic range transmission, and a continuously adjustable transmission, such as a cone-shaped and infinitely adjustable drive-type transmission. The actuating device can be used for clutching and / or disengaging a torque transmission system or for effecting a gear shift.

  transmission in a transmission of the aforementioned types.

  Actuation of the clutch by means of the clutching fork 18 is effected in opposition to the force of the annular spring 22 serving as energy accumulator. The disengaging means may be for example a

central disengagement.

  Inside the actuating device 1, at least one energy accumulator 25 is provided which rests on one of its ends on the component 26, which in turn rests against the part 27 of the casing , the other end of the energy accumulator resting on the component 28, which is connected axially fixedly to the crank shaft 11 by means of a fixing ring 29. With this arrangement of the energy accumulator, it is possible to exercise with the help of the energy accumulator assistance

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  dynamic on the crank operated by the drive unit. The force exerted by the energy accumulator acts in opposition or in cooperation with the energy accumulator of the clutch. The direction of application of the force of the energy accumulator 25 to the crank shaft or to an output element may be

  modulated according to the actuating stroke.

  The energy accumulator 25 is arranged essentially coaxially with the axis of the crank shaft 11 and it assists the movement of the crank shaft 11 in the disengagement direction and / or in the clutch direction of the crank shaft. torque transmission system. By appropriately selecting the prestressing of the energy accumulator 25, for example a helical spring, it is possible to obtain that the energy accumulator exerts, over a part of the actuating stroke of the component 11, a force which produces the disengagement operation while, on another part of the axial stroke, a force is produced which opposes the disengagement process. Thus, it is possible to provide a

  change of direction of action of the force on the crank.

  The actuating device 1 further comprises a spatial geometry element 30, which carries or is provided with a cam profile and which is non-rotatably connected to the tangent wheel 8. The connection of the element 30 with the tangent wheel 8 can be created via a snap connection, which thus establishes a non-rotating connection, or by bolting, or by riveting. In addition, the element 30 can form a single piece with the tangent wheel 8. Advantageously, the tangent wheel 8 can be manufactured in the form of a plastic injection molded part, in which case the element 30 can be made with its one-piece cam profile in the injection molding process or it can be injection molded with the tangent wheel. The component can, however, also be

made of a metal.

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  The member 30 carrying a cam profile is biased by a force so that, through the cam profile, this force is exerted on an output member of the actuator. The modulation of the cam profile makes it possible to modulate the dynamic loading as a function of the actuating stroke or of the actuating movement. The energy accumulator 50 exerts its force on the cam profile directly or indirectly, as

  example via a lever provided with rollers.

  The cam profile divides the force acting on it into a partial force oriented in the direction of movement and a partial force oriented perpendicular to the direction of movement, in which case the partial force oriented in the direction of movement produces a force assist. strength

  i 5 or force compensation.

  FIG. 2 shows an actuating device provided with a drive unit 101, such as an electric motor, comprising an output shaft 102, after which a transmission mechanism, such as a screw transmission mechanism, is arranged. without end, this end screw is not shown in Figure 2. The worm is engaged with a tangent wheel 103, which causes a

  output member 105 via a crank 104.

  The crank 104 is supported in an area 106 while the

  tangent wheel is rotatably mounted in an area 107.

  The motor shaft 102 is supported by means of

bearings 110 and 111.

  A space geometry element 120 is non-rotatably connected to the tangent wheel 103, this element 120 having an outline 121, such as a cam profile or a cam disk. A lever member 123 is pivotally mounted in the region 122 of the member 130 while a roller 125 is rotatably mounted in the region 124 of the member 130. A energy accumulator 126 biases the lever 123 so that the roller 125 is

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  pushed against the contour or the profile 121 of the element 120.

  The energy accumulator is supported by support members and 131 so that it can not escape, these support members being arranged so that they engage in the axial opening central of the energy accumulator, as a pressure spring. Because of this commitment, the energy accumulator is disposed in the essential without

  possibility of translation or without possibility of loss.

  The force produced by the energy accumulator 126 and which is transmitted via the lever 123 and the roller 125 to the contour 121, is divided at the point of application and in accordance with the conventional parallelogram of decomposition of forces into a component a force acting in a radial direction and a force component acting in a conferring direction. The radially oriented force component acts centrally on the axis 107. The force component oriented in a circumferential direction produces a dynamic bias on the crank 104 and therefore on the output member 105. The force assist or the force compensation thus obtained for the actuating force acting on the output element 105 may be modulated as a function of the movement by the cam profile 121 of the spatial geometry element 120, such as a cam disk or a particular cam. The radially and circumferentially acting force components exert an action on a spinning cam disc. In a general manner, the force acting on the cam profile divides into a component oriented substantially parallel to the direction of movement or actuation and also into a component oriented substantially perpendicular to the direction of movement.

  direction of movement or actuation.

  Due to the cam control of the force action or the force compensation of the compensating spring, it is possible to obtain a force compensation or

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  well a compensating moment that depend in the essentials

the intended application.

  In the exemplary embodiment shown in FIG. 2, there is provided a spring 126 fixed on the casing and acting, directly or indirectly via the lever 123, on a cam profile 121, provided on the tangent wheel When the spacing of the contact area between the spring and the cam profile relative to the axis of rotation 107 of the tangent wheel changes, a torque acts in a circumferential direction. The cam profile may be arranged such that the torque exerted opposes the torque generated by the actuating force on the output element or assists the torque. By means of a cam-controlled compensation spring, it is possible, thanks to a modulation of the cam profile, to limit the compensation effect, if any, in certain parts of the adjustable stroke and in this respect this problem can be solved by making it possible in the angle of rotation of the cam profile 121, a variation of the radius of the cam profile is only possible in portions of said angle. In other parts of this angle of rotation, provision can be made for

invariant radius.

  The arrangement of the cam profile allows targeted modulation of the force that is exerted or produced in the direction of the actuating movement. The effect of the force can be adjusted, for example, so that it acts in one direction in the entire actuating stroke or that it changes direction at least once in the actuating stroke. Also, the size of the acting force

  can be modulated in the actuating stroke.

  As a spatial geometry contour, such as for example a cam disk or a cam profile or a modulated surface connected to a cam disk or to a particular cam, is meant for example a surface such as the 121 shown in FIG. figure 2. This surface comprises

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  a component oriented in an axial direction and a component oriented in a circumferential direction, the modulation of the surface or the cam profile being effected by means of a modulation of the radius as a function of the angle of rotation. The dynamic bias is essentially produced in a radial direction so that a division of the force into a circumferential component and a radial component is obtained. The circumferential component of the force exerted by the energy accumulator on the surface then advantageously produces dynamic assistance of the drive system. It is also advantageous, as shown in FIGS. 6a and 6b, for the surface to comprise a circumferentially oriented component and a radially oriented component, and for the modulation of the surface to take place in an axial direction as a function of the rotation angle of the surface. whereby a force acting in an axial direction produces under the effect of a decomposition a force component oriented in the circumferential direction and a force component oriented in the axial direction, the circumferential component of the force producing an assistance of the system. drive. The feature described above is advantageously applicable to training systems

  having elements undergoing a circular motion.

  In devices comprising elements undergoing a linear movement, as is for example the case of the device of FIGS. 4 to 5b, it is advantageous that the surface of the contour with spatial geometry, such as for example a cam profile or a disk forming a cam or a particular cam, has a component oriented in a radial direction and a component oriented in an axial direction, the modulation of the surface being effected so that a spacing relative to the axis of movement or a radius starting from the axis of movement is modulated according to the axial direction. We thus obtain an action

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  force on for example a linkage in the direction of movement, in which case a decomposition of the force is

  produced by the surface of the cam profile.

  FIG. 3 represents an exemplary embodiment corresponding to FIG. 2, the energy accumulator 200 then being constituted by an element in the form of an elastic blade which is fixed by means of fastening means 201 on the casing 202. On the branch 203 of the energy accumulator is rotatably mounted a roller 205 in the zone of the support 204 so that the energy accumulator 200 pushes the roller 205 against the cam profile 206 of the Spatial Geometry Element 207. The cam track or cam profile on the contour 206 of the element 207 is modulated in a radial direction as the element 207 rotates in a circumferential direction. It is thus possible to obtain a force modulation which produces a force assist or a force compensation on the corresponding element, such as

the output element 210.

  FIG. 4 shows a part of a force compensation system belonging to an actuating device and in which a force produced by a energy accumulator is transmitted to an output element via a cam profile . The force compensation device may produce force compensation or force assistance with respect to the output element

  depending on the direction of the applied force.

  The force compensation device comprises a member 300 which is mobile in axial translation and which is driven by a drive unit 301, comprising, for example, an electric motor and a transmission mechanism. The axially displaceable member 300 includes in an area 302 a contour or cam profile 303 which, when viewed in an axial direction, has a periphery, radius, or spacing that is modulated. The element 304 is further connected to an actuatable element, in which case the dynamic assistance of

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  the element 302 acts as a dynamic assistance for the actuation of the actuatable element. The dynamic biasing of the modulated zones 303 is performed such that a first bent lever 305 is pivotally mounted in a zone 311 and a second lever 306 is also mounted in the zone 311; there is then provided between the receiving zones 305a and 306a a energy accumulator 307 which exerts pressure on the receiving zones 305a and 306a. A roller 308 is rotatably mounted in the zone 305a. On an end part of the lever 305 is mounted another roller 309 so as to be rotatable about the pivot 310. Under the effect of the dynamic loading of the energy accumulator 307 in the zones 305a and 306a, there is a thrust of the rollers 308 and 309 against the modulated path 303 of the element 302, so that a dynamic boosting effect is produced by the energy accumulator on the element 302 or the element 304 Via the cam channel or the modulation of the zone 302, 303, assistance or compensation is obtained.

  the force required for actuation.

  Figure 4a schematically shows a drive device 301, which drives the element 300 for example through a transmission mechanism. The element 300 comprises a zone 302 which is provided with a cam track or a cam profile 303. The cam profile is urged by a roller 308, 309, the roller being rotatably mounted in a front portion a sliding shoe 320, 321. The energy accumulators 322, 323 are received in an extreme zone of the sliding shoes and they are supported by their second end zone against the housing. The sliding shoes 320, 321 are supported with the possibility of sliding by guide rails 324, 325. The dynamic loading of the cam profile 303 is produced by the energy accumulators by

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  by means of the rollers 303, 309 so that a force is exerted on the element 302 as well as on the outlet portion 330 of the element 300. Under the effect of the modulation of the cam profile 303 as a function of the axial dimension of the element 300, it is possible to obtain a dynamic solicitation of

  the element 303 which is a function of the race.

  FIG. 4b represents another variant embodiment where a drive system 303 actuates the element 300, for example by means of an electric motor and a transmission mechanism, this element 300 comprising in a zone 302 a cam profile 303. In addition, the element 300 is provided with a biasing zone 330 which acts on an actuating element for controlling a torque transmission system for a transmission. The biasing of the cam 303 of the element 302 is produced by the intervention of a lever arm 335, pivotally mounted on a pivot 336 which is integral with the housing. The lever arm 335 is biased by the energy accumulator 337 which is connected by one of its end zones designated 337a, with the lever arm while its other end zone 337b is integral with the housing. Under the effect of the dynamic loading, the roller 308, which is rotatably mounted in the zone 340, is applied against the cam profile 303 so that the energy accumulator applies a force to the cam profile and to the cam. the output member 330 through the arm of

lever and roller.

  Sa represents an element 350 which is displaceable in axial translation and which can be controlled and driven by a drive unit in the zone 351. This element 350 is connected to an element 352, forming a single unit.

  and even piece with him or being fixed on this element.

  The element 352 comprises a modulated bearing surface 353a, 353b.

  In an area 354, the lever arms 355 and 356 are rotatably mounted about an axis of rotation.

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  rotation and they comprise receiving areas 355a and 356a each receiving an energy accumulator 357 so that these energy accumulators push the elements 355, 356 towards each other. In the receiving zones 360 and 361 there are rollers 362 and 363 between which the element 352 is mounted. The rollers 362 and 363 roll on the contour 353a, 353b so that, under the effect of the force exerted by the accumulator of energy on the receiving zones of the lever, the rollers are pushed against the contour 353a, 353b so as to urge the element 352. As a result, a force produced by the energy accumulator 357 is transmitted via lever arms and rollers to the cam track and from this cam track 353a, 353b to the element

352 and then to the element 350.

  Figure 5b shows the arrangement of Figure 5a in a plan view made in correspondence with the arrow 370 of Figure 5a. One can see the element 350 which is biased in an area 351 and which actuates in an area 371 an actuatable element. The figure highlights the receiving zones 355a, 356a as well as the lever arms 355 and 356. In addition, the figure shows the roller 360 which urges the element 352 by

  via the cam track 353b.

  Fig. 6a shows a part of an actuating device of a torque transmission system or a transmission (400); there is provided an element 402 rotatable about an axis 401 and which can be driven by a drive unit. The element 402 may for example be the tangent wheel 8 of Figure 1 or another actuatable element, such as a toothed wheel. A member 404 bearing a cam profile 404 is attached to the actuatable member 402, which cam profile is also directly connected to or formed on the member 402. The cam profile 404 of the member 403 is modulated in an axial direction and, considering a direction

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  circumferential, the axial spacing of the modulated surface

404 varies.

  The energy accumulator 405 is fixed on the housing side by one of its ends 405a, a pin 405c penetrating into the central zone of the energy accumulator and thus maintaining the latter in a fixed position. The end zone 405b of the energy accumulator is connected via a receiving zone 405d to a lever 406 so that the force of the energy accumulator 405 is transmitted via the lever 406 and the roller 407, to the cam surface or to the cam disk 404 and then to the output member 402. The lever 406 is rotatably mounted in a zone 406a and the roller 407 is rotatably mounted in an area 406b. The force exerted by the energy accumulator 405 is transmitted, via the lever 406 and the roller 407, substantially in an axial direction to the cam profile 404, so that the element 402 is biased by a force in a circumferential direction. The arrangement of FIG. 6a thus produces an assistance force which is exerted in one direction

  circumferential with respect to axis 401.

  FIG. 6b further shows an arrangement 410 for a force assist or a force compensation for an actuating device of a torque transmission system or a transmission, the element 412 being mounted so as to be able to turn around axis 411; this element 412 can be rotated for example by means of a drive unit. The element 412 can be arranged for example in the form of a tangent wheel, such as

  designated by the reference numeral 8 in FIG.

  The element 413 is connected to the element 412 or forms a single piece with it, the element 413 being an element essentially having a cylinder shape and having on its outer periphery a cam profile , as a modulated edge in an axial direction. The cam profile

24 2749636

  414 is held by one of its ends 416a and with the aid of retaining means 416b on the housing 419 while its other end 416c is hooked on a lever with a retaining means 416d. The lever 417 is pivotally mounted in a zone 417a and a roller 418 is provided in a zone 417b which bears in an axial direction against an area of the curved surface 413 of the cam profile 414 and transmits a force of the energy accumulator at the element 412. The force produced by the energy accumulator 416 is oriented in an axial direction and, through the biasing of the cam profile, a conversion effect occurs. on the force exerted in the direction

  circumferential element 412.

  Fig. 6c shows an element producing a force compensation, or a force reduction, or a force assist for an actuating device of a torque transmission system or a transmission; an element 432 is disposed coaxially with an axis 431 and can

  be rotated by means of a drive unit.

  The element 433, of substantially cylindrical shape, is connected to the element 432 or forms a single piece with

  this, the element 433 carrying a cam profile 434.

  The energy accumulator 435 is held at one of its sides 435a against the housing by means of the retaining means 439 and, in a zone 435b, a biasing of a pusher 436 which is guided linearly by means of guides 438a and 438b. The pusher 436 comprises, in one of its axial end zones, a roller or a sliding part which urges the cam track or the cam disc 434 of the element 433 so as to produce a force assist for the accumulator. energy 435 to the element 432. The guides 438a and 438b can operate by sliding or via

of a bearing.

  FIG. 7a shows a rotary element 500, which is mounted to rotate coaxially with the axis 501 and which

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  can be driven, via the shaft 502, by means of a driving element or an intermediate transmission mechanism. The peripheral zone 503 of the element 500 is modulated, considering it in a circumferential direction, in a radial direction, so that the peripheral zone 503 can provide, in the manner

  a cam disk, a modulated control of the mechanism.

  The journal 504, including the axis 505, is connected to the element 500 being in particular fixed thereon, so that the pin 504 moves on a circular path 506 during a rotation of the element 500. The energy accumulator 507 is held on the housing by the retaining means 508, which enters an end zone 507a of the central passage of the energy accumulator and thus prevents

  translation or escape of this energy accumulator.

  In the end zone 507b, the energy accumulator is received by a retaining means 509, which comprises lugs 510a and 510b which provide a guide, by means of the trunnion 504, to a rotary bearing of the element 509. , as a receiving area. When the energy accumulator is installed in such a way that a pulling and pulling stress can be exerted on the energy accumulator or can be produced from it, then it is possible to obtain a better transmission of the force of the energy accumulator to the element 500 via the trunnion and in this respect, it is possible to obtain a sign change and a functional modulation of action

  the strength of the energy accumulator on the element 500.

  The output element 511 is arranged as a pusher which comprises at its end part 511a a rotary roller 512 which

  rests against a border zone 503 of the element 500.

  Under the effect of the modulation, produced as a function of the angle of rotation, of the force exerted by the energy accumulator on the element 500 and also under the effect of the modulation of radius, produced as a function of the angle of rotation,

26 2749636

  the element 500, it is possible to obtain a force compensation or a modulation of the action of the force exerted

on element 511.

  FIGS. 7a and 7b show a variant of a cam-controlled compensation spring and a spring

  at low dead point or high dead point provided on a pusher.

  According to this variant, on the one hand, a spring is fixed eccentrically on a rotating disk and, under the effect of its preload, it can produce a torque with respect to the center of rotation of the disk, and on the other hand, an actuation of the clutch can be produced by means of a biasing of a cam profile provided on the disc. In this case, the characteristic curve of the disengaging force can be adapted in the best possible way, by means of the arrangement of the cam profile, to the compensation characteristic curve of the compensation spring. The compensation characteristic curve may comprise, in wide areas of actuation, a variation of force that is very close to the characteristic curve representing the disengaging force of a clutch. The disengaging force produces a torque acting on the cam disk. The relationship between the two quantities can be defined, with simplification as regards the freedom of friction, by the following formula: Mcharge = Fbunching dr / d (p = Fclutch clutch / d (P In this formula, Mcharge represents the moment produced by the disengaging force, r represents the spacing of the point of application of the force exerted by the cam disk relative to the pusher for actuation of the clutch while the angle of rotation of the cam disk is present. The variations of r correspond to the variations occurring for an actuating stroke S. When an opposing force acts during a

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  Actuation of the clutch, energy is transmitted from the compensation spring to the rotating disk. During an inversion of the actuation, that is to say during movements of the pusher in the direction of application of forces, the energy produced in return by the clutch spring can again be stored in the compensation spring, which can lead to a reduction in the load of the drive element, such as an electric motor. In another variant, zones 520 can be provided on the edge of the cam disc which cause a blocking because, in order to obtain a support, the roller of the pusher 511 reaches a zone 520 provided for this purpose and which makes it necessary to increase in the strength to get out

] 5 of this area.

  Fig. 8a shows an arrangement producing a force compensation or a force assist for an actuating device of a torque transmission system and / or a transmission, in which case the substantially disk-shaped member 600 is rotatably mounted about the axis 601. The member 600 is driven through the drive shaft, shown as the drive link 602, such that a motion of rotation of the element 600 is carried out in a targeted manner. The periphery of the element 600 is arranged as a cam disk and modulated in radius, this disk having in a first angular zone 604 and in a second angular zone 605 a radius that can vary with the angle of rotation while it comprises a constant radius in another zone

  3 () angular 606 possibly provided.

  Against the disk-shaped curb region 603 is a roller 607, which is rotatably mounted by means of the journal 608 in an area of the pusher 609, the driving force being transmitted to the pusher 609 from the element. 602 via element 600 and roller

28 2749636

  607. Under the effect of the rotation of the element 600 and the modulation of the radius, there is an axial movement of the element 609 for an actuation of a torque transmission system and / or for a selection or a gearshift in a transmission. For force assistance, there is provided an energy accumulator 610, such as a loop spring, arranged so that one of its ends 610a is fixed to the housing, being engaged for example in a retaining zone of the 611. The other end zone of the 610b spring

  can be connected by conjugation of shapes with the element 600.

  The form-conjugate connection may be designed such that it is established in any position or angular orientation of the element 600 or, however, so that there is a free stroke angle, in which the energy accumulator will not be biased during a rotation of the element 600. The zone 612, which is highlighted in FIG. 8b, is arranged as such a free stroke zone, which means that the cavity 612 in which is received the end 610b of the loop spring 610 will produce a dynamic spring solicitation only after

  the crossing of a free stroke angle.

  This angular position 613 corresponds for example to the angular range in which the radius modulation is zero, which means that the angular range 613 corresponds to

  in Figure 8b at the angular range 606.

  A device corresponding to FIGS. 8a and 8b can be used for example to produce a force compensation by means of a compensation spring for clutch actuation by means of a cam disk, which is driven for example by an actuator with an electric motor. This is advantageous in the case of automation of the clutch operations and operation of the transmission by means of two actuators with electric motors. In this case, a maneuvering body fulfills the

29 2749636

  partial functions of clutch control and ratio switching while the second operating member performs the partial function of selecting reports. In addition, it is also possible to involve other divisions of the clutch control operations, command switching and selection in the transmission; in this regard, the selection process is to operate the transmission between the switching channels and the switching process is to operate the transmission within the switching channels. To achieve a comfortable clutch release and re-engagement of the torque transmission system, it is necessary to be able to quickly open an automated clutch and to be able to close it in a targeted manner, in which case the opening of the clutch can be carried out more quickly or more slowly depending on the vehicle's operating condition while closing the clutch must also be performed more quickly or slowly depending on the vehicle's operating status or operating parameters. The biasing of the actuating member is generally very large when opening the clutch because, when closing the clutch, the energy stored in the clutch spring is released. For example, in the case of an annular spring clutch, the

  disengagement spring is constituted by this annular spring.

  Because the duration of actuation increases with the biasing of the operating member, it is advisable that this operating member can be assisted, during an opening of the clutch, by an energy accumulator.

additional.

  When the electric motor operating member must fulfill, for example, the clutch control and switching functions, it can cause, for example by means of an irreversible transmission mechanism,

  a cam disk which is divided into three zones.

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  In a first zone, for example in the angular range 605, the clutch is open, in a second zone, the clutch is kept open, as for example in the angular range 606, and in a third zone, the clutch S is closed again, as for example in the angular range 604. In the case of a cam disk whose stroke increases or decreases linearly or whose stroke increases or decreases in correspondence with another function of the rotation angle or displacement that is selected in a targeted way, it is necessary to involve a driving torque that is proportional to the curve

clutch characteristic.

  In combination with a linearly operating compensation spring, the load torque initially has a negative value when the clutch is opened. Such a linearly operating compensation spring for controlling the torque transmission system has been represented for example in FIG. 1 by being designated by the reference 25. Due to the provision of an irreversible transmission mechanism in the transmission member maneuver, the spring can not accelerate the actuator, or it can not sufficiently strongly, so that this operating member can operate, in this case, virtually empty. In the second zone of the cam disk, where the actuator controls the switching, the clutch is kept open. The compensation spring then operates forcefully in its free travel range. In the third zone, in which the clutch is closed, the energy stored in the disengagement spring of the clutch is released, so that the load torque initially takes a negative value. Due to the irreversibility of the operating member or the transmission mechanism of the latter, the operating member operates substantially free of charge in this case. On about two-thirds of the total disengagement stroke, the actuating force is

* 3 1 2749636

  virtually zero. In this range, the clutch will be frequently actuated to control the transmissible torque, which is the case for example in different operating states, such as during a clutch or a clutch before or after report switching processes or well in

  control situations with corrective torque adjustment.

  In this respect, a corrective torque adjustment corresponds to a control of the torque transmission system in relation to the available torque on the drive side, which depends on the existing motor torque, minus secondary equipment torques, such as for example an installation

air conditioning.

  Because the actuation in such a range is carried out virtually without force intervention, the operating member can quickly adjust, with low energy consumption, the torque that can be transmitted by the clutch. By means of the cam profile 603 of the disk 600, however, it is also possible to obtain other actuation characteristic curves. Until a complete closure of the clutch, the operating member must operate in opposition to the compensation spring until it is again armed. The cam disk may also be arranged in the form of a cam profile located on the periphery or on the front side of a cylinder. In place of a cam disk, however, it is possible to use any type of transmission mechanism operating non-uniformly with stopping or moving phases. The compensation spring can be fixed in the housing by being hinged to the cam disk but however, it can also be fixed to the disk with

articulation in the housing.

  The incorporation of a torsion spring, such as a loop spring, which is actuated by means of a cam disk during opening and closing of the clutch, corresponds to an advantageous implementation of

32 2749636

  the invention. When closing the clutch, the compensation spring is loaded and the energy stored in the clutch spring is converted into a preload of the compensation spring. When the clutch is opened, the compensation spring causes the actuating member to exert a pressure or a load on the clutch spring. In the angular range of the cam disk in which the operating member performs a switching operation, or for example a selection operation, the clutch is kept open and the spring of

  compensation is relaxed and is no longer solicited.

  Figure 9 shows schematically an actuator 700 having a housing 701 in which or on which is installed the drive unit 702, as an electric motor. The output shaft 703 of this motor is connected, via a worm 704, to a tangential wheel 705 to actuate the output member 706, such as a pusher or an actuating crank. For force compensation, a cam disk 707, having a modulated surface 708, is non-rotatably connected to the tangent wheel 705, with at least one energy accumulator 709, 710 biasing the disk 707. Due to the modulation of the cam disk or the cam track 708, there is a modulation of the dynamic bias exerted by

  the energy accumulator on the output element 706.

  FIG. 10 also highlights this arrangement, where the contour 750 of circular shape represents the outer radius of the tangent wheel, for example wheel 705. The

  contour 751 corresponds to the contour of the cam disk 708.

  The arrow 752 represents the line of action of the force exerted by the energy accumulator on the disc 751. The radius r, designated 753, represents the spacing from the center of the tangent wheel 750 and the angle pdesigned by 754, corresponds to the angle of rotation. The arrow 755 highlights the actuating force that acts on the element of

33 2749636

  output and the radius R, designated 756, defines the spacing of the point of application of the actuating force relative to the center of rotation 757. The compensation effect exerted by the compensation spring, which acts on the disk forming cam in correspondence with the arrow 752, is then defined by the relation: Mcompensation = dr / d (p.Fressort.In an alternative embodiment, the energy accumulator, which produces the force 752, can be arranged as a bending spring or an elastic blade or as a spring acting by

via a lever.

  Fig. 11 shows an arrangement of a cam disk 800, which is used in an actuator for combined operation of a clutch and a transmission. At an angle of rotation of 360, there is a disengagement operation, a switching operation and a re-engagement operation of the clutch. From point 801, where the clutch is closed, the cam disk is actuated automatically in the direction of the arrow 802, to obtain a force modulation as a function of the actuating stroke or the operating angle. At the beginning of the actuation, when the clutch is closed, the energy accumulator 803 is applied by its roller 804 in the zone 801 against the disk forming a cam.

to solicit the latter.

  In the angular range 805, the clutch is disengaged while the angular range 806 causes a ratio switching operation; in a first half of this angular range, a ratio is output, a dead point condition is reached at 807, and in the second half of the angular range 806, another gear is engaged before, in the angular range 808, the clutch is engaged again. Areas designated 809 and 810, respectively, can be used for point domain maintenance

  dead, or closing clutch.

3 4 2749636

  FIG. 12 shows a modulation of radius R as a function of the angle of a cam disk such as that represented in FIG. 11. For the angle θ, the radius has a maximum or substantially maximum value and, as as indicated by the curves 900 or 901, one can obtain a maximum or a minimum in correspondence with a stopping phase. From the angle 0 to the angle 90, the radius modulation can decrease in correspondence with the curves 902a, 902b or 902c and a minimum is obtained for 90. From 90 to 180, the modulation of radius [O increases again and in the transition zone of 180, one can have a minimum of 903 attributable to a stopping phase or a maximum of 904 before a minimum is reached for the angular position of 270. From 270 to 360, the radius modulation increases again. In the range from 0 to 90, the clutch is actuated, in which case the clutch is closed while for substantially 90 the clutch is open. From 90 to 180, there is a ratio switching operation, for 180 a neutral condition is obtained and 180 to 270, a ratio switching operation occurs before, from 270 to 360

the clutch is closed again.

  Figure 13 shows the effect of compensation on the forces or torques produced during an actuation of the clutch and a switching operation. The curve 950 corresponds to the first part (p 1 of the clutch force characteristic curve, between the points (p1 and p2 of the characteristic curve there is an output of the ratio corresponding to the curve portion 950a; angle between (p2 and (p3 and corresponding to the curve portion 950b, there is a ratio engagement process and, in the angular range between (p3 and <p4 and corresponding to the curve portion 950c, there is The profile of the curve 951 corresponds to the compensating force or torque, so the compensation in the range 951a is negative, at the point (pl,

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  a sign change occurs so that the compensation becomes positive, in the range between pl and p2 and in correspondence with the curve portion 951a, the compensation is positive, in the angular range between p2 and p3 and in correspondence with the curve portion 951d, the compensation is negative, at T3 there is again a sign change and, in the angular range between (p3 and p4 and in correspondence with the curve portion 951c, the compensation becomes positive. The solid line designated 952 represents the resultant force or moment resulting respectively in the sum of the clutch or switching actuating forces 950 and the compensating forces 951. It is realized that it occurs at the same time. total a significant reduction in maximum values compared to simple clutch actuation and switching forces that are represented in 950. In the angular range included between 0 and pl, a reduction in the clutch actuating force is recorded whereas, in the angular range between 1pl and p2, an increase in this force is recorded in correspondence with the curve profile 952a, before, in the angular range between y2 and p3, there is a decrease in switching forces. The maximum, indicated in 954, occurs as a result of synchronization and unlocking processes; in this respect the maximum that is designated by 955 occurs under the effect of a ratio commitment process during a switch while the maximum forces 956 occurs

  under the effect of contact with a stop in the transmission.

  In the angular range between p3 and p4, the characteristic curve representing the clutch force is reduced from profile 950c to profile 952c. In total, we obtain a reduction in the values of the forces

  clutch actuation and switching.

  FIG. 14 represents a portion of an operating member such as that corresponding to FIG. 1,

36 2749636

  comprising a tangent wheel 1001, an element such as an operating crank 1002 and a set of energy accumulators 1003. This set of energy accumulators 1003 has, unlike the energy accumulator 25 of the 1, a series arrangement of two energy accumulators 1004 and 1005, which makes it possible to obtain a two-step characteristic curve by the fact that the energy accumulator 1004, like a spring, is a softer spring the energy accumulator 1005. The element 1006 serves as a stop for the creation of a prestressing. Due to the arrangement of energy accumulators having different stiffnesses, it is possible to obtain a characteristic curve which has several steps representing the action

the compensation force.

  FIGS. 14a and 14b show exemplary embodiments relating to sets of two energy accumulators, but it should be noted that an assembly comprising more than two energy accumulators may be advantageous for

  create a characteristic curve with several steps.

  The energy accumulator 1050 is held in a support 1051 and this energy accumulator 1050 can be prestressed. The energy accumulator 1052 acts via the element 1053 on the energy accumulator 1050 which can be prestressed, so that, during axial loading of the element 1054, an initial biasing the energy accumulator 1052 which deforms until the effect of the preload is counterbalanced and then also the accumulator

1050 energy is compressed.

  Fig. 14b shows an alternative embodiment in which the element 1055 disposed between the energy accumulators 1050 and 1052 is arranged in the form of a pot so that the axial installation space can be used more favorably. In the case where the actuating stroke is sufficiently small, and when such a form of construction

37 2749636

  permits. In cases where a large axial actuation stroke occurs, it is advantageous to adopt a

  variant such as that of Figure 14a.

  Element 1051 is arranged as a pot-shaped element while element 1055 has an at least pot-shaped section. The springs of FIGS. 14a and 14b, which may be prestressed, may have a smaller stiffness than the

non-prestressed springs.

  FIG. 15 represents an exemplary embodiment of a compensation spring system for an actuating device of a torque transmission system and / or a transmission; it is provided inside a casing 1100 at least one set of springs 1101a, 110lb, which is mounted on a pivot support 1102 and 1103 in a fixed position in the casing but nevertheless with possibility of pivoting and which is in further pivotally connected to a driven member 1106 via another link 1104, 1105. The member 1106 includes a drive portion 1106a so that axial movement of that member may occur. , while its output portion 1106b biases an output element to produce its actuation. Under the effect of the axial displacement of the element 1106, the hinge zones 1104 and 1105 move in an axial direction while the hinge zones 1102 and 1103 remain in fixed positions, which produces a relative movement of the hinge regions 1104 and 1105. elements biasing the energy accumulators 1110 and 1111, so that a force can be exerted axially by the energy accumulators on the element 1106. The energy accumulators 1110 and 1111 are arranged so that, at least in a position, as a limit position, they exert a force only in a direction perpendicular to the axis of movement of the element 1106. When a shift of the element 1106, a component of the force exerted by the springs on element 1106 is however produced in the direction of movement of this

38 2749636

  This force can however also act in the opposite direction and in this case a force component acts in the direction of the axis of displacement. This arrangement is shown diagrammatically in FIG. 15b where the element 1120 is arranged so as to be able to move, in which case the energy accumulators 1121 and 1122 are held both on the housing side and on the element 1120. are subjected to prestressing, for example in a limit position corresponding to the representation of the springs 1120 and 1121. When actuating the element 1120 in an axial direction, the attachment point 1123 is shifted in an axial direction until at point 124, so that the force exerted by the energy accumulators 1121 and 1122 is also oriented in an axial direction. The arrangement of the energy accumulators can be chosen such that, in an end zone, a dead point is reached in such a way that the energy accumulators no longer act as top-dead springs. In addition, it can also be advantageous for the energy accumulators to act as top dead springs, so that an axial force is obtained at the limit of the actuating stroke. This axial force does not occur when the springs are in the neutral position at the end of the actuating stroke. Fig. 16 shows an actuating device 1200 comprising a drive unit 1201, such as an electric motor. This electric motor 1201 drives a shaft 1202, which is supported and positioned in an axial direction in the zone 1203 by means of the element 1204. In addition, the shaft 12302 is maintained in the zone 1203 via a opening or guide 1205 provided in the wall 1206 of the housing. The worm gear 1207 is substantially non-rotatably connected to the shaft 1202. The worm gear 1207 is engaged with the tangential wheel 1208, which is supported by a bearing in an area of the axis 1209. The tangent wheel 1208 is

39 2749636

  associated with a toothed wheel 1210, or this toothed wheel forms a single piece with the tangent wheel. The toothing of the toothed wheel 1210 drives a rack 1211, which actuates a piston 1213 of an emitter cylinder 1214, as a hydraulic emitter cylinder. The rack 1211 is held in the radial direction of the toothed wheel 1206, at the

  means of the roller 1212 or by means of a support.

  The tangent wheel 1208, where a disk connected thereto, such as for example the gear wheel 1210, comprises a cam profile which is directly or indirectly solicited by a energy accumulator 1219. This energy accumulator 1219 is disposed between a receiving zone provided in the housing 1206 and a receiving zone provided on a lever 1217, this lever 1217 being rotatably mounted in the bearing 1218. In addition, the lever is equipped with a roller 1216 which is rotatably mounted in the zone 1222. This roller rolls on the contour of the cam profile 1215 and it thus solicits this cam profile producing, in connection with the design of this cam profile, a shape acting on the output element of the device , this force depending on a distance or a position on the cam profile. There is provided on the housing 1206 a receiving zone 1220 and on the lever 1217 a receiving zone 1221 which engage respectively in ends of the energy accumulator, such as a coil spring, so as to maintain this energy accumulator. in its position and / or to create an anti-loss attachment for it. Figure 17 shows another advantageous arrangement

  an actuating device 1300 according to the invention.

  This device 1300 comprises a drive unit 1301 which can be arranged as an electric motor. This electric motor 1301 drives a shaft, such as the motor shaft 1302, which is held in a zone 1303 by means of a bearing or a bearing. The shaft 1302 is non-rotatably connected to a worm 1304 which is engaged with

2749636

  a tangent wheel 1305. The tangent wheel 1305 has a contour or a cam profile 1306 against which a sliding or rotating element rests, such as a roller 1307 or, for example, a sliding shoe. The roller 1307 is disposed on the lever or on the crank 1308, which is connected with the piston 1309 of the pressure-actuated emitter cylinder 1310, like a hydraulic cylinder. The roller 1307 is rotatably mounted in the bearing 1311. In addition, a lever 1312 is articulated in the region of the bearing 1311, and is also articulated in the zone 1313. The lever arm 1313 produces a movement of the connecting rod 1308 and during a solicitation of the rotating contour 1306 when the gear 1305 rotates. It is thus possible to obtain a stroke modulation of the piston of the emitter cylinder as a function of the rotational movement of the tangent wheel, or in a general way, as a function of the

actuating movement.

  The embodiments of FIGS. 16 and 17 represent variants. Advantageously, the motor axis, like a shaft, is arranged parallel to the axis of the actuating crank or the pusher of the output element. In addition, the tangent wheel may be located in the same plane as the motor shaft, in which case the operating crank or the pusher may be located in this plane

or outside this plane.

  The present invention furthermore relates to the earlier German patent application of 196 22 641, the content of which expressly corresponds to the disclosure content.

of the present patent application.

  ) The claims filed with the patent application

  are drafting proposals with no prejudicial effect for obtaining patent protection. The Applicant still reserves the right to claim other features highlighted so far only in the

description and / or drawings.

4 1 2749636

  Attachments used in the claims

  of the subject matter of the main claim by the characteristics of the corresponding secondary claim, but should not be considered as a waiver of the

  characteristics of related secondary claims.

  The objects of these secondary claims

  also constitute particular inventions that are

  of an independent design of the objects of the claims

previous secondary.

  The invention is also not limited to the examples

  embodiments given in the description. On the contrary, in

  Within the scope of the invention, it is possible to envisage numerous variations and modifications, in particular variations, elements and combinations and / or materials which are inventive, for example by combination or modification of certain features or elements, or operating steps, which have been described in relation to those described in the

  general description, the embodiments and the

  claims and which are contained in the drawings in

  leading, by a combination of features to a new object, or to new process steps, or to new sequences of process steps, so far as also relates to methods of making, controlling and placing

implemented.

42 2749636

Claims (30)

  1 - Actuating device for controlling a control element that can be actuated, for example for switching and / or selecting transmission ratios of a transmission and / or for actuating a transmission system torque, located in the motor train of a vehicle, this actuating device comprising a drive unit and possibly a transmission mechanism, and an output element operatively connected to said unit via a driving connection, and furthermore at least one energy accumulator being provided for biasing the output element, an actuating device characterized in that an element which can be force-biased and provided with a contour with spatial geometry, such as for example a cam profile or a cam disk, or a particular cam, is permanently operatively connected with the drive link and the drive e exerted by the energy accumulator, provided in number at least equal to the unit, acts on the output element via the geometry contour space of said element.   2 - Actuating device for controlling a control element that can be actuated, for example for switching and / or selecting the transmission ratio of a transmission and / or for actuating a transmission system torque, located in the motor train of a vehicle, said actuating device comprising a drive unit, and optionally, a 3) transmission mechanism, and an output element operatively connected to said unit via of a drive link and furthermore at least one energy storage device being provided for biasing the output element, said operating device being characterized in that an element able to be biased by a force and having a contour to 43 2749636   spatial geometry, such as a cam disk, a cam profile and / or a particular cam, and disposed in the drive link between the drive unit and the output member and the force exerted by the energy accumulator provided in number at least equal to unity, acts on the output element via the spatial geometry contour.   3 - Device according to one of claims 1 and 2,   characterized in that the force-biasable element having a spatial geometry contour such as a cam disk, a cam profile or a particular cam is biased by the energy accumulator, which is less than unity in a region of the spatial geometry contour, such that a force exerted by the energy accumulator acts on the output element by   via the contour with spatial geometry.   4 - Actuating device according to one of   Claims 1 to 3, characterized in that the element   being biased by a force and having the spatial geometry contour, such as a cam disk, a cam profile, a cam track, or a particular cam, is an element that is set in motion upon actuation of the element of actuable control.   - Actuating device according to one of   Claims 1 to 4, characterized in that, in a   dynamic stressing of the contour that can be biased by a force and during a movement of the element having the contour that can be biased by a force, there is a dynamic modulation of the action of the force exerted by   the energy accumulator on the output element.   6 - Actuating device according to one of   Claims 1 to 5, characterized in that the element having the   contour which can be urged by a force, when actuated by the control element, a movement in at least one direction.   Actuating device according to Claim 6, characterized in that the element having the force-displaceable contour is displaceable in a linear direction and / or in a circular motion and / or in an axial direction and / or in a radial direction and / or in a circumferential direction.   8 - Actuating device according to one of   Claims 1 to 7, characterized in that the outline,   spatial geometry and which can be biased by a force, the element is oriented in a linear direction and / or in an axial direction and / or in a radial direction and / or   in a circumferential direction.   9 - Actuating device according to one of   Claims 1 to 8, characterized in that the force exerted   by the energy accumulator, provided in a number at least equal to unity, on the geometrically contoured and force-responsive contour of the element, is oriented substantially in a linear direction and / or in an axial direction and / or in a radial direction and / or in a circumferential direction.   - Actuating device according to one of   Claims 1 to 9, characterized in that the modulation of   The geometrically space-incident, force-responsive contour of the element is produced substantially in a linear direction and / or in an axial direction and / or in a radial direction and / or in a circumferential direction. 11 - Actuating device according to one of   Claims 6 to 10, characterized in that in a   dynamic stressing of the contour, for example by an energy accumulator, provided in number at least equal to unity, the action of the force is carried out at least substantially in the direction of the output element or in the the opposite direction. è2749636   12 - Actuating device according to one of   Claims 1 to 11, characterized in that at a   dynamic stressing of the contour, for example by a energy accumulator provided in number at least equal to unity, a division of the force exerted takes place at least essentially in the direction of an actuating movement of the output element and / or in one direction   perpendicular to this actuating movement.   13 - Actuating device according to one of   Claims 1 to 12, characterized in that a mechanism   transmission is arranged to act in the drive link between the drive unit and the output member. 14 - Actuating device according to one of   Claims 1 to 13, characterized in that the element   spatial geometry and having the force-biased contour is in operative connection with the drive unit, with a member provided in the link   drive or with the output element.   15 - Actuating device according to one of   Claims 1 to 14, characterized in that the element having   the space geometrically contourable and force-engageable contour includes a cam disk, a cam track or a particular cam, rotatable and having a profile one-dimensional or two-dimensional.   16 - Actuating device according to one of   Claims 1 to 15, characterized in that the element having   the spatially geometrically contoured and force-engageable contour comprises a cam disk, a cam track, or a particular cam having a one-dimensional profile or   two-dimensional and movable linearly or axially.   17 - Actuating device according to one of   Claims 1 to 16, characterized in that the element having   an outline with spatial geometry that can be solicited by 46 2749636   a force, includes a cam disk, a cam track   or a particular cam, with a three-dimensional profile.   18 - Actuating device according to one of   Claims 1 to 17, characterized in that the accumulator   of energy, provided in number at least equal to the unit and dynamically soliciting the contour with spatial geometry, comprises a sliding shoe, a roller and / or a bearing, by which the energy accumulator bears against the contour. 19 - Actuating device according to one of   Claims 1 to 18, characterized in that the accumulator   a predicted power in number at least equal to unity, solicits an organ, such as for example a lever, which is mounted with the possibility of displacement in a first zone and which comprises, in a second zone, a sliding shoe, a roller or a bearing, which solicits the contour with geometry space of the element.   - Actuating device according to one of   Claims 1 to 19, characterized in that the accumulator   of energy, provided in number at least equal to unity, solicits an element, which is supported by means of a linear guide and which further comprises the geometrically contoured contour of the element.   21 - Actuating device according to one of   Claims 1 to 20, characterized in that the accumulator   energy supply, provided in number at least equal to the unit, solicits a clip-like element, which is mounted in a zone with the possibility of displacement and which solicits the contour to   spatial geometry of the element.   3 () 22 - Actuating device according to one of   Claims 1 to 21, characterized in that the accumulator   of energy, provided in number at least equal to unity, solicits the element having a spatial geometry contour for example in the area of a bearing, such as a trunnion disposed so 47 2749636   not centered, the output element leaning against an area of the contour with spatial geometry.   23 - Actuating device according to one of   Claims 1 to 22, characterized in that the accumulator   of energy, provided in number at least equal to the unit, solicits the element having a spatial geometry contour for example in the area of a bearing, such as a trunnion arranged in a non-centered manner, an element soliciting the element Release   leaning against an area of the contour with spatial geometry.   24 - Actuating device according to one of   Claims 1 to 23, characterized in that the support against the   contour with spatial geometry and / or the solicitation of the spatial geometry contour is / are carried out with effect of   sliding, gyrating or rolling.   25 - Actuating device according to one of   Claims 1 to 24, characterized in that the unit   drive is an electric motor, a unit   electromagnetic or an electromechanical unit.   26 - Actuating device according to one of the   Claims 1 to 25, characterized in that the unit   is a drive unit actuated by pressure medium, such as a hydraulic drive unit, hydropneumatic or pneumatic.   27 - Actuating device according to one of the   Claims 1 to 26, characterized in that the action of the   force exerted on the output element of the actuating device is modulated, in relation to the movement of the spatial geometry contour and the dynamic stress of this contour, as a function of the actuating stroke of said output element.   28 - Operating device according to one of   claims 1 to 27, characterized in that the assistance of   force is produced at least in part of the race   actuating the output element. 48 2749636   29 - Actuating device according to one of   claims 1 to 28, characterized in that the assistance of   force undergoes, if necessary, a change of sign during the actuation stroke.   Actuating device for controlling an actuatable control element, for example for switching and / or selecting transmission ratios of a transmission and / or for actuating a torque transmission system, located in the motor train of a vehicle, said actuating device comprising a drive unit, and possibly a transmission mechanism, and an output element operatively connected to said unit via a link drive, and also at least one energy accumulator that can bias the output element, characterized in that the force exerted by the energy accumulator, provided in number at least equal to the unit, acts on the output element, this energy accumulator being disposed   so as to act as a low dead center spring.   31 - Actuating device according to claim, characterized in that there are provided two energy accumulators, located in mutually opposed positions and urging the output element, each acting as a spring at low dead point.   32 - Actuating device according to claim, characterized in that the energy accumulator, provided in number at least equal to the unit, is arranged as a low dead center spring, in that a first extreme zone is pivotally mounted on the output member and in that the second end zone is pivotally mounted by example on the crankcase.   33 - Actuating device, in particular according to one   Claims 1 to 32, for controlling an element of   control operable, for example for switching and / or selection of the transmission ratio 49 2749636   of a transmission and / or for an actuation of a torque transmission system, located in the motor train of a vehicle, this actuating device comprising a drive unit and, if appropriate, a transmission mechanism, and an output element operably connected to said unit via a drive connection, and also at least two energy accumulators which can bias the output element, characterized in that the force exerted by the energy accumulators provided in number at least equal to two, acts on the output element, these two energy accumulators being arranged as energy accumulators operating in series.   34 - Actuating device according to one of   Claims 1 to 33, characterized in that the accumulator   of energy, provided in a number at least equal to unity, is a   pre-stressed energy accumulator.   - Actuating device according to one of   Claims 1 to 34, characterized in that the accumulator   of energy, provided in number at least equal to unity, is a spring, such as a pressure spring, an elastic blade, a loop spring or an elastic element formed of a metal, a material similar to rubber or plastic. 36 - Actuating device according to one of   Claims 1 to 35, characterized in that the element having   the spatial geometry contour is formed of a metal or a plastic material.   37 - Actuating device according to one of the   Claims 1 to 36, characterized in that the element having   the spatial geomatric outline forms one and the same piece   with a component of the transmission.   38 - Actuating device according to one of the   Claims 1 to 37, characterized in that the element having 2749636   the spatial geometry contour forms one and the same piece with the output element.   39 - Actuating device according to one of   Claims 1 to 38, characterized in that the element having   the spatial geometry contour forms a single piece with a functionally arranged element between the unit   drive and the output element.   - Actuating device according to one of   Claims 1 to 39, characterized in that the element having   the spatial geometry contour is connected to a member operably disposed between the drive unit and the output member.