WO2016188732A1 - Convertisseur de caractéristique muni d'un disque à cames et d'un poussoir présentant un positionnement minimisant la force transversale et servant à actionner un embrayage - Google Patents

Convertisseur de caractéristique muni d'un disque à cames et d'un poussoir présentant un positionnement minimisant la force transversale et servant à actionner un embrayage Download PDF

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Publication number
WO2016188732A1
WO2016188732A1 PCT/EP2016/060393 EP2016060393W WO2016188732A1 WO 2016188732 A1 WO2016188732 A1 WO 2016188732A1 EP 2016060393 W EP2016060393 W EP 2016060393W WO 2016188732 A1 WO2016188732 A1 WO 2016188732A1
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WO
WIPO (PCT)
Prior art keywords
actuating
rotation
axis
plunger
converter
Prior art date
Application number
PCT/EP2016/060393
Other languages
German (de)
English (en)
Inventor
Peter Bolz
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2016188732A1 publication Critical patent/WO2016188732A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
    • F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
    • F16H53/06—Cam-followers

Definitions

  • the present invention relates to a characteristic converter for actuating a cylinder, in particular a master cylinder of a clutch of a motor vehicle, having an actuating disk, which is rotatable about an axis of rotation in and against a rotational direction, and is provided for actuating a plunger which is displaceable in and against a displacement direction is, wherein the actuating disk has a cross-sectional contour, which in an operating region in which the plunger rests against the actuation disk when actuated, has a steadily increasing center distance from the axis of rotation.
  • the present invention also relates to an actuator assembly comprising such a tag converter and a tell drive for automatically driving the tag converter.
  • the present invention relates to a clutch, in particular of a motor vehicle, with such a tag converter.
  • Dry clutches in a motor vehicle are actuated by a motor vehicle driver via a hydraulic master cylinder and a hydraulic slave cylinder, or with cables. Dry clutches are also known in which the actuation is automated. In automated dry clutches, the master cylinder of the system is actuated by a gear by an electric motor.
  • Such transmissions usually comprise an identification converter having a first stage with a helical or helical gear, and a second stage, the the rotational movement of the first stage in a linear movement, such as a plunger, converts.
  • the second stage often includes crank mechanisms or spindle drives. But there are also cams usable.
  • the publication DE 60 2004 01 1 168 T2 discloses an electromechanical actuator with a cam-like actuator which drives a member for actuating the master cylinder.
  • the member has the shape of a cylindrical member which is slidable in the direction of its own axis. By moving the member a slide is moved, which is housed in a hydraulic cartridge. As a result, a liquid is displaced in a tube attached to the cartridge.
  • the object of the present invention is to provide an identifier converter for actuating a cylinder, in particular a clutch of a motor vehicle, which converts a rotational movement into a linear movement with little loss, as well as a clutch with such an identifier converter.
  • the object is achieved with an identifier converter for actuating a cylinder.
  • the cylinder is preferably a hydraulic cylinder.
  • the invention is also suitable for actuating a pneumatic cylinder.
  • the cylinder is a master cylinder of a clutch of a motor vehicle. But is also preferred the operation of a pump.
  • the identification converter has an actuating disk, which is rotatable about an axis of rotation in and against a direction of rotation. In addition, it has a plunger which is displaceable in and against a displacement direction.
  • the actuating disk is provided for displacing the plunger.
  • the plunger is provided for actuating the cylinder.
  • the actuating disk has a cross-sectional contour which, in an actuating region in which the tappet rests on the actuating disk in a contact region when actuated, has at least partially a steadily increasing axial spacing relative to the axis of rotation.
  • the identification converter is characterized in that the contact area is punctiform or linear, and that in the operating area in which the cross-sectional contour has a steadily increasing center distance to the axis of rotation, a maximum curve of the
  • the plunger When turning the actuating disk in this operating range, the plunger is therefore at the maximum curve on the actuating disk.
  • the maximum curve is the point or linear contact area in which the local slope of the cross-sectional contour is just zero.
  • no force acts tangentially on the actuating disk in this operating range.
  • no lateral force caused by such a tangential force acts on the plunger.
  • the plunger is therefore lossy displaced, and the identifier converter low-loss operable. It is preferred that the plunger extends along an axis of action 31 along which it is displaced in the direction of displacement when the actuating disk is rotated.
  • Cross-sectional contour to the axis of rotation is formed monotonically rising.
  • the contact area can therefore be determined by forming the mathematical derivative of the cross-sectional contour.
  • the increase in the axial distance increases steadily.
  • the contact area of this embodiment can be determined by forming the second mathematical derivative of the cross-sectional contour.
  • the plunger is accelerated when rotating the actuating disk in this operating range.
  • Cross-sectional contour partially has a decreasing center distance to the axis of rotation, so that the plunger is decelerated when moving, or has a constant center distance to the axis of rotation, so that it remains in its position.
  • the cross-sectional contour is preferably continuous at least everywhere, preferably smooth.
  • the cross-sectional contour has a steadily increasing center distance to the axis of rotation in the entire operating range.
  • it is formed monotonically increasing in the entire operating range.
  • the contact area in the entire operating range is a maximum of the curve
  • the increase in the axial distance in the operating area is substantially the same everywhere.
  • the plunger is moved in the entire operating range at substantially constant speed.
  • the plunger preferably extends parallel to a first spatial direction extending in a radial direction of the axis of rotation, and is furthermore preferably spaced therefrom by an offset. It is therefore not aligned with the axis of rotation, but its axis of action is offset by the offset to the axis of rotation.
  • an embodiment is preferred in which the increase in the axial distance in the operating region is steadily increasing. As a result, the plunger is accelerated throughout the operating range.
  • the plunger extends at an angle> 0 ° to the first spatial direction, and is spaced from the offset in the contact region thereof.
  • a return torque acts on the actuating disk.
  • the plunger is loaded only in the direction of its axis of action, ie in the direction of displacement. Overall, almost no reaction forces act on the plunger in the actuation area. The plunger is thereby not only displaceable loss, but the storage of the plunger is much easier possible, and there are no complex multi-joint arrangements required.
  • the actuating disk preferably has an actuating surface in the actuating region, against which the plunger rests.
  • the actuating surface preferably extends transversely to the axis of action of the plunger, or to the direction of displacement.
  • the displacement direction extends transversely to the axis of rotation.
  • the displacement direction and the actuating surface extend at an angle of> 0 ° to the axis of rotation.
  • an actuating element is arranged on the plunger, which has a rolling-off means, which is rotatable about a rolling axis in and against a rolling direction.
  • the rolling-off means rolls when turning the actuating disk on the actuating surface.
  • the actuating disc is a cam disc with the actuating portion and an actuating stop.
  • the actuation region preferably extends from an actuation start to an actuation end. It is preferred that the actuation stop is formed by a contour which is rectilinear in cross-section and connects the actuation end to the actuation start. At the actuating stop, the cross-sectional contour of the actuating disk therefore extends in a jump shape.
  • the object is further achieved with an actuating arrangement for a cylinder, for example for a master cylinder of a clutch of a motor vehicle.
  • the actuating arrangement has such a detection converter, as well as a Versteilantrieb for automatically driving the identification converter. It is preferred that an output axis of the Versteilantriebs is arranged transversely to the axis of rotation. As a result, the actuator assembly is very flat / compact buildable. Depending on the space requirements but other arrangements are preferred. Particularly preferably, the output axis has an angle to the radial direction of the axis of rotation. As a result, the position of the Versteilantriebs is adjustable relative to the identifier converter.
  • the object is further achieved with a clutch, in particular a motor vehicle, with such a tag converter.
  • Fig. 1 shows in (a) schematically a first embodiment of a
  • FIG. 3 shows in (a) an actuating disk for an identification transformer according to the invention, and in (b) a table of values, and
  • FIG. 4 shows in (a) an actuating arrangement with an identifier converter according to the invention, and in (b) a detail of the actuating arrangement of FIG. 4 (a).
  • Fig. 1 (a) schematically shows a prior art ID converter 1.
  • the identifier converter 1 has an actuating disk 2, which is rotatably mounted in and against a direction of rotation 63 about a rotation axis 6.
  • the actuating disk 2 is a cam disk, which has a cross-sectional contour 20, with an actuating region 21 and an actuating stop 22.
  • the actuating region 21 extends from an actuating start 21 1 to an actuating end 212. In the illustrated embodiment, a distance A 2 increases
  • the cross-sectional contour 20 runs monotonously in the operating area. and smooth.
  • the actuating start 21 1 and the operating end 212 are connected to each other in a straight line.
  • the actuating disk 2 therefore has there a cross-sectional contour 20 with a jump.
  • the identifier converter 1 comprises a plunger 3, which is mounted displaceably in a first bearing 41 in and against a displacement direction 30.
  • the plunger 3 extends along an axis of action 31 and in a radial direction 62 of the axis of rotation 6. It is therefore aligned with the axis of rotation 6, so that its axis of action 31, the axis of rotation 6 intersects.
  • the displacement direction 30 therefore extends in the radial direction 62.
  • a spherical actuating element 7 is fixed, which is displaceable with the plunger 3 in and against the displacement direction 30.
  • the actuating element 7 is located in the operating region 21 on the actuating disk 2.
  • the plunger 3 When turning the actuating disk 2, the plunger 3, preferably against a spring force, according to the cross-sectional contour 20 of the actuating disk 2 is moved in the direction of displacement 30. Since the distance A 2 of the cross-sectional contour 20 from the axis of rotation 6 in the embodiment of the actuating disk shown here in the entire operating range 21 steadily increases, the plunger 3 is continuously displaced in the direction of displacement 30.
  • the identifier converter 1 therefore converts a rotational movement into a linear movement. In this case, a torque of the actuating disk 2 is converted into a counterforce F of the plunger 3.
  • the reaction force R acts on the actuation element 7, which effects the counterforce F of the plunger 3.
  • the reaction force R has an NEN effective angle ß to the radial direction 62.
  • the effective angle ⁇ corresponds to a pitch angle ⁇ of the cross-sectional contour 20 in the contact region P of the plunger 3, in which this rests against the actuating disk 2.
  • the reaction force R acting on the actuating disk 2 therefore has a tangential force component RR and an axial force component RA.
  • the axial force component RA acts in a first spatial direction x, which extends in a radial direction 62 of the axis of rotation 6.
  • the radial direction 62 in which the first spatial direction x extends, is referred to below as the first radial direction.
  • the terms first radial direction and first spatial direction x are used synonymously below.
  • the tangential force component RR acts in a second spatial direction y transversely to the first spatial direction y.
  • the second spatial direction also extends in a radial direction 62 of the axis of rotation.
  • the radial direction 62, in which the second spatial direction y extends, is referred to below as the second radial direction.
  • the terms second radial direction and second spatial direction y are used synonymously below.
  • the plunger 3 is aligned with the axis of rotation 6. Its axis of action 31 therefore intersects the axis of rotation 6. It extends in the first spatial direction x.
  • the displacement direction 30 is therefore the first radial direction x.
  • the pitch angle ß of the cross-sectional contour 20 in the contact area P of the plunger 3 acts on the plunger 3 not only an axial force FA in the direction 30, but also a transverse force FR transverse to the displacement direction 30.
  • the lateral force FR is greater, the greater the effective angle ß and / or the smaller the axial distance A 2 of the cross-sectional contour 20 from the axis of rotation 6.
  • the lateral force FR must be supported in the first bearing 41.
  • the lateral force FR must be applied by the actuating disk 2. It therefore causes a loss of power, since this proportion of the applied force can not be used for moving the plunger 3.
  • Direction of rotation 63 is rotated about its axis of rotation 6.
  • the contact area P shifts along the actuating surface 210 of the actuating disk 2 (or along the cross-sectional contour 20).
  • it is displaced from a basic position G, in which it is arranged approximately at the actuation start 21 1 of the actuation region 21, into an adjustment position V, in which it is displaced along the actuation region 21 in the direction of the actuation end 212.
  • the plunger 3 is moved in the direction of displacement 30.
  • a cylinder 9 for example, a master cylinder of a clutch (not shown) of a motor vehicle (not shown) is actuated.
  • the plunger 3 is operated against a restoring force, in particular a spring (not shown). As a result, it is pushed back against the direction of displacement 30 when the actuating disk 2 is rotated counter to the direction of rotation 63.
  • FIG. 1 (a) shows the identification converter 1 in the adjustment position V.
  • FIG. 1 (b) shows an actuation arrangement 100 with a further embodiment of a prior art identification converter 1 in the basic position G.
  • the identifier converter of FIG. 1 (b) differs from that of FIG. 1 (a) by the actuating element 7 fastened to the tappet.
  • the actuating element 7 of the identifier converter 1 of FIG. 1 (b) has an offset.
  • rolling means 71 with a rolling surface 70 which extends in the axial direction 61 of the axis of rotation 6.
  • the actuating disk 2 has an actuating surface 210 which extends in the axial direction 61 of the axis of rotation 6.
  • An axial distance A 2 of the actuating surface 2 from the axis of rotation 6 increases steadily.
  • the actuating disk 2 has a cross-sectional contour 20 which, analogously to that of the actuating disk 2 of FIG. 1 (a), permits a continuous displacement of the tappet 3.
  • the unrolling means 71 abuts against the actuating surface 210 of the actuating disk 2 along a linear contact area P.
  • the unrolling means 71 abuts against the actuating surface 210 of the actuating disk 2 along a linear contact area P.
  • the actuator disk 2 is driven by means of a Versteilantriebs 8, a
  • Output shaft 810 with a toothing 814 (see Fig. 4 (a)).
  • the output shaft 810 extends in an output direction 81 1 concentrically about an output axis 81.
  • the actuating disk 2 is arranged rotationally fixed to the drive wheel 27.
  • the drive wheel 27 has a counter-toothing 271 (see Fig. 4 (a)), which is formed corresponding to the toothing of the output shaft 810 and in engagement therewith. It is rotatably mounted about the axis of rotation 6. Preferably, it is arranged transversely to the axis of rotation 6. When rotating the output shaft 810 in a drive direction 813, therefore, the drive wheel 27 and the actuating disk 2 are simultaneously rotated in the rotational direction 63.
  • Fig. 1 (b) also shows a housing 10 with an interior 1 1, in which the identifier converter 1 is arranged.
  • the first camp 41, in which the Plunger 3 is mounted here is formed by a bushing which extends in the direction of displacement 30 and is arranged in the housing 10.
  • FIG. 2 shows a first embodiment of an identifier converter 1 according to the invention schematically.
  • the identifier converter 1 has the actuating disk 2 rotatable in and counter to the direction of rotation 63 about the axis of rotation 6, as well as the plunger 3 displaceable in and against the displacement direction 30.
  • the plunger 3 is mounted in the first bearing 41.
  • the actuating disk 2 of the identifier converter 1 has a cross-sectional contour 20 in the entire actuating region 21, with a continuously increasing center distance A 2 relative to the axis of rotation 6. Namely, the cross-sectional contour 20 is designed to increase monotonously.
  • the plunger 3 is in the contact area P on the actuating disk 2, which is formed point-like or linear-shaped. In addition, the contact area P is the maximum curve of the cross-sectional contour 20.
  • the effective angle ⁇ (see FIG. 1 a) in the contact region is just 0 °. Therefore, at the actuation Disc 2 no tangential force component RR of the reaction force R on the plunger 3, but only the axial force component RA. Therefore, the plunger 3 can be moved in this arrangement with little loss in and against the sliding direction 30. In addition, no or at least virtually no transverse force FR (see Fig. 1 a) must be collected in the bearing 41 of the plunger 3. For storing the plunger 3, therefore, a cost-effective bearing 41, in particular a cost-saving socket can be used.
  • FIG. 2 shows the axial force FA of the plunger 3, directed counter to the reaction force R.
  • the plunger 3 extends parallel to the first spatial direction x, and therefore parallel to the first radial direction x of the axis of rotation 6. He is not aligned with the axis of rotation 6 out. Instead, it is offset by an offset ⁇ to the first radial direction x. Therefore, its axis of action 31 does not intersect the axis of rotation 6.
  • the contact area P is displaced along the cross-sectional contour 20 in the direction of rotation 63 of the axis of rotation 6.
  • 2 shows the identifier converter 1 in an adjustment position V, in which the abutment region P is displaced towards the actuating end 212. Since the axial distance A 2 of the cross-sectional contour 20 increases steadily in the operating region 21, the plunger 3 is displaced in the adjustment position V by an adjustment ⁇ in the direction 30.
  • Fig. 3 shows in (a) an actuating disk 2 for an identifier converter 1 according to the invention, and in (b) a table of values. It clarifies the determination of the contact area P for the inventive identifier converter 1 by forming the mathematical derivative of
  • Cross-sectional contour 20 The axis of rotation 6 of the actuating disk 2 is arranged in a zero point (0,0) of a coordinate cross whose axes extend in the first spatial direction x and in the second spatial direction y. A path in [mm] is shown on the axes / spatial directions x, y.
  • the actuating disk 2 is shown rotated in different directions of rotation um, which are each spaced by 30 ° from each other, about its axis of rotation 6 in the direction of rotation 63.
  • the actuating stop 22 extends in the first spatial direction x.
  • the value table shows a calculated result of the calculation of an optimal position of the plunger 3.
  • the mathematically determined value in which the cross-sectional contour 20 has its maximum curve is designated here by P, since this position is used according to the invention as a contact region P. It is visible that the Kurvenmaximunn P shifts approximately along a line L in the direction of displacement 30 upon rotation of the actuating disk. In the arrangement of the plunger 3 in the direction of the line L this is therefore always arranged approximately at the maximum curve P.
  • the line L is spaced by the offset ⁇ from the first spatial direction. In the basic position G, the plunger 3 is therefore spaced apart from the actuation start 21 1 by the offset ⁇ .
  • the table of values can be taken that the adjustment ⁇ , by which the axial distance A 2 of the contact area P increases when turning the actuating disk 2, slightly larger. Due to the only slight change of the plunger 3 is still arranged here substantially parallel to the first spatial direction x. Therefore, although slight tangential forces RR act on the plunger 3. However, these are small enough to allow a cost-effective storage 41 of the plunger 3.
  • FIG. 4 shows an actuating arrangement 100 with such an identifier converter 1 according to the invention.
  • a housing 10 of the actuator assembly 100 is shown open, so that the identifier converter 1 in the interior 1 1 of the housing 10 is visible.
  • the actuating arrangement 100 has the adjusting drive 8.
  • the plunger 3 component 9 in particular the cylinder on.
  • the cylinder 9 is here a hydraulic cylinder and comprises a tappet guide 91 and a cartridge 92.
  • the identifier converter 1 has the actuating disk 2, which is rotatable in and against the direction of rotation 93 about the axis of rotation 6.
  • the actuation disk 2 has the actuation region 21 and the actuation stop 22. In the actuation region 21, the cross-sectional contour 20 rises steadily from the actuation start 21 1 to the actuation end 212.
  • the bolt 28 cooperates with a groove (not shown) in the housing 10 of the tag converter 1, with a slot end (not shown) serving as a stop for the pin 28.
  • the actuating disk 2 is driven by means of Versteilantriebs 8, which has an output shaft 810 which extends in the driven direction 81 1 and in and against the drive direction 813 to a
  • Output shaft 81 is rotatable.
  • a worm gear 814 is arranged as positive engagement means, which is in engagement with a counter toothing 271 of the drive wheel 27.
  • Fig. 4 (a) shows only a section of the drive wheel 27 in dashed lines.
  • the drive wheel 27 When rotating the output shaft 810 in the drive direction 813, the drive wheel 27 is driven in the direction of rotation 63, so that the actuating disk 2 rotates about the axis of rotation 6 in the direction of rotation 63.
  • a rolling element 7 which is arranged around a Abrollachse 72 in and against a rolling direction 723 rotatably mounted on the plunger 3.
  • the rolling element 7 rotates when turning the actuating disk 2 in a rolling direction 723 opposite to the direction of rotation 63 of the actuating disk 2. It rests in the contact area P on the actuating disk 2.
  • the plunger 3 is therefore guided here in an inner space 50 of a linear guide frame 5.
  • the guide frame 5 has on opposite longitudinal sides 541, 542 each have a guide groove 53, in which a corresponding to the guide groove 53 formed guide web 33, which is arranged on opposite longitudinal sides 341, 342 of the plunger 3, engages.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un convertisseur de caractéristique (1) servant à actionner un cylindre, en particulier un maître-cylindre d'un embrayage d'un véhicule automobile. Le convertisseur de caractéristique comprend un disque d'actionnement, qui peut tourner autour d'un axe de rotation (6) dans une direction de rotation (63, 93) et dans le sens opposé à cette dernière et qui sert à actionner un poussoir, qui peut être coulissé dans une direction de coulissement (30) et dans le sens opposé à cette dernière. Le disque d'actionnement présente un contour de section transversale (20, 210), qui présente dans une zone d'actionnement, dans laquelle le poussoir repose sur le disque d'actionnement dans une zone d'appui lors de l'actionnement, au moins en partie une distance axiale (A1, A2) par rapport à l'axe de rotation (6), laquelle est en augmentation constante. La zone d'appui est réalisée de manière à présenter une forme de point ou de ligne et constitue, dans la zone d'actionnement, dans laquelle la distance axiale (A1, A2) par rapport à l'axe de rotation (6) est en augmentation constante, un maximum de courbe du contour de section transversale (20, 210). L'invention concerne de plus un ensemble d'actionnement, qui comprend un convertisseur de caractéristique (1) de ce type et un entraînement d'ajustement (8) servant à entraîner de manière automatique le convertisseur de caractéristique (1). L'invention concerne par ailleurs un embrayage, en particulier d'un véhicule automobile, muni d'un convertisseur de caractéristique (1) de ce type.
PCT/EP2016/060393 2015-05-26 2016-05-10 Convertisseur de caractéristique muni d'un disque à cames et d'un poussoir présentant un positionnement minimisant la force transversale et servant à actionner un embrayage WO2016188732A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015209611.4A DE102015209611A1 (de) 2015-05-26 2015-05-26 Kennungswandler mit Kurvenscheibe und Querkraft- minimiert positioniertem Stößel zur Betätigung einer Kupplung
DE102015209611.4 2015-05-26

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WO2016188732A1 true WO2016188732A1 (fr) 2016-12-01

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US20180163710A1 (en) * 2016-12-08 2018-06-14 KNAUER Wissenschaftliche Gerãte GMBH Cam mechanism for the implementation of a variable stroke
CN108869564A (zh) * 2017-05-15 2018-11-23 罗伯特·博世有限公司 用于操纵车辆离合器的致动器

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WO2020225943A1 (fr) * 2019-05-07 2020-11-12 日本精工株式会社 Dispositif de came, dispositif de fabrication de pièce, dispositif de fabrication de palier, procédé de fabrication de pièce, procédé de fabrication de machine et procédé de miniaturisation de dispositif de came

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FR1381162A (fr) * 1963-11-18 1964-12-04 Dispositif hydraulique de commande de direction
DE1750322B1 (de) * 1968-04-20 1971-01-14 Messerschmitt Boelkow Blohm Vorrichtung zum Umformen einer linearen in eine kreisfoermige Bewegung,und umgekehrt
DE602004011168T2 (de) 2003-10-31 2008-12-24 Sila Holding Industriale S.P.A., Nichelino Elektromechanischer Aktuator für eine Kupplung eines Kraftfahrzeugs
EP2431626A1 (fr) * 2010-09-16 2012-03-21 Univance Corporation Dispositif de commande d'embrayage
EP2503174A1 (fr) * 2009-11-19 2012-09-26 Aisin Seiki Kabushiki Kaisha Actionneur d'embrayage
WO2015082137A1 (fr) * 2013-12-05 2015-06-11 Robert Bosch Gmbh Organe de commande s'encliquetant en position maximale pour actionner un actionneur hydraulique d'embrayage et embrayage à commande électrique

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FR1381162A (fr) * 1963-11-18 1964-12-04 Dispositif hydraulique de commande de direction
DE1750322B1 (de) * 1968-04-20 1971-01-14 Messerschmitt Boelkow Blohm Vorrichtung zum Umformen einer linearen in eine kreisfoermige Bewegung,und umgekehrt
DE602004011168T2 (de) 2003-10-31 2008-12-24 Sila Holding Industriale S.P.A., Nichelino Elektromechanischer Aktuator für eine Kupplung eines Kraftfahrzeugs
EP2503174A1 (fr) * 2009-11-19 2012-09-26 Aisin Seiki Kabushiki Kaisha Actionneur d'embrayage
EP2431626A1 (fr) * 2010-09-16 2012-03-21 Univance Corporation Dispositif de commande d'embrayage
WO2015082137A1 (fr) * 2013-12-05 2015-06-11 Robert Bosch Gmbh Organe de commande s'encliquetant en position maximale pour actionner un actionneur hydraulique d'embrayage et embrayage à commande électrique

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180163710A1 (en) * 2016-12-08 2018-06-14 KNAUER Wissenschaftliche Gerãte GMBH Cam mechanism for the implementation of a variable stroke
US10907623B2 (en) * 2016-12-08 2021-02-02 KNAUER Wissenschaftliche Geräte GmbH Cam mechanism for the implementation of a variable stroke
CN108869564A (zh) * 2017-05-15 2018-11-23 罗伯特·博世有限公司 用于操纵车辆离合器的致动器

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