EP2192604B1 - Dateneingabevorrichtung mit verbesserter Anschlagcharakteristik - Google Patents

Dateneingabevorrichtung mit verbesserter Anschlagcharakteristik Download PDF

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Publication number
EP2192604B1
EP2192604B1 EP09177528.8A EP09177528A EP2192604B1 EP 2192604 B1 EP2192604 B1 EP 2192604B1 EP 09177528 A EP09177528 A EP 09177528A EP 2192604 B1 EP2192604 B1 EP 2192604B1
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EP
European Patent Office
Prior art keywords
stem
rod
force
cam
switch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP09177528.8A
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English (en)
French (fr)
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EP2192604A1 (de
Inventor
Jean-Louis Bigand
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Thales SA
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Thales SA
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Publication of EP2192604A1 publication Critical patent/EP2192604A1/de
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Publication of EP2192604B1 publication Critical patent/EP2192604B1/de
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    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H25/00—Switches with compound movement of handle or other operating part
    • H01H25/06—Operating part movable both angularly and rectilinearly, the rectilinear movement being along the axis of angular movement
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/50—Driving mechanisms, i.e. for transmitting driving force to the contacts with indexing or locating means, e.g. indexing by ball and spring
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H15/00—Switches having rectilinearly-movable operating part or parts adapted for actuation in opposite directions, e.g. slide switch
    • H01H15/24—Switches having rectilinearly-movable operating part or parts adapted for actuation in opposite directions, e.g. slide switch having a single operating part only protruding from one side of the switch casing for alternate pushing and pulling

Definitions

  • the invention relates to a data input device being made by means of a switch actuated by a rod.
  • the invention finds particular utility for a rod that can be pulled or pushed around an equilibrium position.
  • the two movements of the rod, pull and push allow each to enter a datum.
  • the switch is usually placed at one end of the rod.
  • An operator pulls or pushes the rod, causing the operation of the corresponding switch.
  • the rod may also allow the operation of a rotary encoder around the axis of translation of the rod.
  • the data from the rotary encoder can be optically encoded in an electronic part of the device.
  • a tactile sensation whose main function is to ensure that the electrical release of the switch is ensured after the passage of a peak effort.
  • the deflection can be important, for example greater than one millimeter.
  • Such devices are found in the aeronautical industry and more particularly in aircraft dashboards. The safety of the flight of the aircraft may depend on the data input made by means of the device. This is why many manufacturers impose severe constraints in the tactile feedback that a pilot must feel when operating the device.
  • a ball cooperating with the rod More specifically, on the rod is formed a cam comprising an inclined pan followed by a plane parallel to the axis of movement of the rod.
  • the ball can move perpendicular to the axis of movement of the rod by relying on the cam by means of a spring.
  • the stem At rest, the stem is in a position of equilibrium. This position is maintained by a return spring capable of compressing along the axis of movement of the rod. In this equilibrium position, the ball is in contact with the cam at the bottom of the inclined face.
  • the ball rises on the inclined pan by compressing its spring until reaching the parallel plane.
  • the force exerted by the ball on the cam is added to that exerted by the return spring of the rod.
  • the force added by the ball brought back to the axis
  • the displacement of the rod is practically nil, with the friction close, and the only effort that the operator must overcome is that generated by the return spring of the rod.
  • the ball is in contact with the inclined pan, it exerts an axial component of force on the rod. This axial component, added to the force generated by the return spring, forms a peak effort that the operator must overcome by operating the rod.
  • the accuracy of these systems depends in particular on the diameter of the ball and its position on the inclined pan at the equilibrium position, which imposes tight tolerances of realization.
  • the peak of effort depends on the diameter of the ball, the force exerted by the spring of the ball and the slope of the inclined face.
  • the slope of the return curve of the rod depends on the stiffness of the return spring and the friction force of the ball on the cam.
  • the subject of the invention is a data input device according to claim 1.
  • the slope is defined as a surface angularly offset from the direction of movement of the rod.
  • the orientation of the angle is such that the force exerted by the circular element on the rod opposes the displacement of the rod from its equilibrium position.
  • the slope is also defined as a surface angularly offset from the direction of movement of the rod.
  • the orientation of the angle of the slope is reversed relative to that of the slope so that the force exerted by the circular element on the rod tends to facilitate the displacement of the rod from its position. balance.
  • the invention makes it possible to ensure that the movement of the rod can not be stopped physically before the switch is triggered.
  • a data input device comprising a switch allowing the input of the data, a rod movable in translation relative to a housing and a return spring allowing the rod to return to a equilibrium position where the rod is not maneuvered.
  • the displacement in translation of the rod makes it possible to manipulate the switch.
  • the invention can be implemented in a rotator where a rotational movement of the rod allows to operate the switch.
  • the rod is rotatable relative to the housing and the rotation of the rod makes it possible to enter a datum represented by the angular position of the rod.
  • the switch will not be described.
  • the rod serves as an intermediary between the operator and the moving part of the switch.
  • the switch is for example a push button operated in translation.
  • the switch may also be an optical encoder comprising a mask integral with the rod and movable between a transmitter and a detection cell, the transmitter and the detection cell being integral with the housing.
  • the use of an optical encoder the advantage of not producing stress on the rod. The only forces between the housing and the stem come from the different constituent elements of the invention.
  • the rod is secured to the moving part of the push button and an operator exerts a force on the rod. This effort is transmitted to the mobile part.
  • the invention allows a net movement of the moving part and thus improves the reliability of the data input made by the operation of the switch.
  • the device comprises means for modulating a force exerted by the return spring in order to define a peak force at a point of the stroke of the rod beyond which the switch is maneuvered;
  • the figure 1 allows to illustrate this peak of effort. More specifically, the figure 1 represents an example of curve 10 defining the force FO to be applied on the rod, ordinate, as a function of displacement or stroke D of the latter carried on the abscissa.
  • the electrical contact of the switch must be made after the peak of effort 11 and before the end of the race.
  • the part of the race where the switch is operated is represented by dimension 19.
  • the figure 2 schematically represents the forces exerted on the rod when it is in equilibrium position.
  • the device comprises a cam 20 integral with the rod 21 and a circular element 22 capable of moving substantially perpendicular to the displacement of the rod 21.
  • the displacement of the rod 21 is in translation along an axis 23.
  • the element circular 22 is held in abutment against the cam 20 by means of a spring 24.
  • the cam 20 comprises a slope 25, a high point 26 and a slope 27 on which relies successively the circular element 22 when the rod 21 is operated from its equilibrium position to a position where the switch is operated.
  • the circular element 22 may be rigid: a spherical ball or a cylinder whose axis is perpendicular to the plane of the figure 2 .
  • a cylindrical shape makes it possible to better distribute the force exerted by the circular element 22 against the cam 20 and thus to reduce the wear on the cam 20 and the circular element 22.
  • the circular element and the resilient means holding the circular element in pressure against the cam 20 can be made by means of a single mechanical part such as an elastic ring.
  • the circular outer shape of the ring is in contact with the cam 20 and the elasticity of the ring makes it possible to keep it bearing against the cam 20 throughout the movement of the rod 21.
  • the device also comprises a return spring 29 opposing the displacement of the rod 21 and can therefore be compressed along the axis 23.
  • a return spring 29 opposing the displacement of the rod 21 and can therefore be compressed along the axis 23. In the equilibrium position, the rod is in abutment against the housing 28, the return spring 29 is compressed so as to hold the rod 21 against the housing 28 and the circular element 22 bears on the slope 25.
  • the radial component can also be cashed by a second assembly formed of a cam, a circular element and a spring.
  • This second set is arranged in the data input device symmetrically to the first assembly formed of the cam 20, the circular element 22 and the spring 24 shown on the drawing. figure 2 .
  • the symmetry of the two sets is made with respect to the axis 23.
  • the sum of the axial and radial components exerted by the circular element 22 on the rod 21 is substantially perpendicular to a plane tangential to the cam 20 at the point of contact between the circular element 22 and the cam 20. In this decomposition we do not take into account the friction that could be taken into account in a finer modeling.
  • the circular element 22 reaches the high point 26.
  • This high point is the junction between the slope 25 and the slope 27.
  • the effort FC changes direction to move towards the right of the figure 2 .
  • the figure 3 represents the position of the rod 21 after the passage of the rod 21 around the high point 26.
  • the depth of displacement 14 corresponds to the passage of the circular element around the high point 26.
  • the change of direction of the effort FC allows The recess may appear in the curve 10 between the force peak 11 and the minimum 13. This recess corresponds to the passage of the circular element 22 at the level of the high point 26.
  • the forces FC and FR evolve linearly as a function of the respective compression of the springs 24 and 29, which corresponds to the linear portion 16 of the curve 10.
  • the slope of the linear part 16 can be adapted by changing the inclination of the slope 27 and thus ensure that the effort value 17 is lower, or even significantly lower than that of the effort peak 11 while remaining positive to allow the return of the rod 21 to its equilibrium position if the effort exerted by the operator FO is released.
  • the dimensions of the cam 20 are defined such that an effort FO exerted on the rod 21 throughout a portion 19 of the stroke of the rod 21, part where the switch is operated, is less than the effort peak 11.
  • the depth of displacement 14 is substantially equal to the radius of the circular element 22 multiplied by the sine of the angle of the slope 25 with respect to the axis 23.
  • the depth of the displacement is elongated by the radius of the circular element 22 multiplied by the sine of the angle of the slope 27 relative to the axis 23. It is thus possible for the same depth of displacement 14 reduce the radius of the circular element 22, which reduces the size of the device.
  • the presence of the slope 27 allows a greater hollow force 15 due to the reversal of the FC effort. Without slope 27, there is simply a cancellation of the force FC when the circular element 22 reaches the flat surface parallel to the axis 23. It is thus possible for a hollow of the given force 15 to reduce the force exerted. by the spring 24 by implementing the invention. This reduction in effort makes it possible to reduce the wear on the cam 20 and the circular element 22. It is also possible to use softer and less expensive materials. In one embodiment of the invention, it has for example been possible to replace a metal cam 20 with a cam 20 made of plastic material while maintaining the same service life of the device, for example a lifetime measured in number of maneuvers.
  • the circular element 22 rests on the cam 20 at a junction 30 between the slope 25 and the high point 26.
  • the force FC is oriented in the opposite direction to the effort FO, from where a major effort to overcome by the operator to take off the rod 21 of its abutment against the housing 28.
  • the force FC decreases. This makes it possible to reduce strongly, or even to suppress, the first part 12 of the displacement of the rod 21.
  • he is required to exert an almost equal effort at the peak of effort 11. This causes a depression of the rod 21 coinciding almost with the beginning of its movement and thus an improvement in the reliability of the operation of the switch.
  • the device may include a second switch.
  • the means for modulating the effort make it possible to create a second peak of effort in the stroke of the rod beyond which the second switch is operated.
  • This variant is explained using the Figures 4 to 4f .
  • the device comprises only one circular element 22 that can move along a cam 40 comprising two slopes 25a and 25b, two high points 26a and 26b and two against slopes 27a and 27b on which the element relies successively circular 22 when the rod 21 is operated from its equilibrium position.
  • the zones 25a, 26a and 27a of the cam 40 are similar to the zones 25, 26 and 27 already described and the zones 25b, 26b and 27b serve to support the circular element 22 when the rod 21 moves towards a position where the second switch is operated.
  • the figure 4f represents an enlarged view of the cam 40 alone.
  • the two slopes, 25a and 25b, the two high points 26a and 26b and the two against slopes 27a and 27b are respectively symmetrical with respect to the same point of the cam 40, located between the two slopes 25a and 25b.
  • the equilibrium position of the rod 21 is obtained when the circular element 22 is simultaneously supported on the two slopes 25a and 25b. It is not necessarily necessary to provide an abutment against the housing 28 to maintain the rod 21 against its equilibrium position.
  • the figure 4 represents a curve of the force FO, ordinate, expressed in newtons and exerted on the rod 21 by the operator as a function of the displacement of the rod 21 on the abscissa and expressed in millimeters.
  • the curve illustrates the movement of the rod 21 in only one direction from the equilibrium position.
  • the circular element 22 bears on the slope 25a and is slightly off the slope 25b.
  • the force FO has a value of the order of 9.5N corresponding to the effort peak 11.
  • the circular element 22 bears on the cam 40 at a junction 30a between the slope 25a and the high point 26a.
  • the curve of the figure 4 decreases to reach a value of the order of 7.5N at the point where the circular element 22 completely leaves the slope 25a to follow the high point 26a.
  • This zone of the cam 40 formed by the high point 26a is for example a small surface substantially parallel to the axis 23 of displacement of the rod 21.
  • the circular element 22 bears on the cam 40 at a junction 41a between the high point 26a and the slope 27a.
  • the force FC increases in absolute value from a zero value, when the circular element 22 bears on the high point 26a, up to a maximum value, when the circular element 22 completely leaves the necessary point 26a. to follow the slope 27a.
  • the effort FO then has a value of the order of 6.5N. Beyond this point, the circular element 22 follows the slope 27a and the curve of the figure 4 is linear and increasing as in part 16 of curve 10.
  • the origin of the displacements of the rod 21 is the equilibrium position of the rod 21 and the curve represented figure 4 allows to deduce a symmetrical curve when the circular element 22 follows the zones 25b, 26b and 27b of the ramp when the rod 21 is moved by the operator in the direction of the negative abscissa.
  • the peak force 11 is here obtained from the equilibrium position, because the circular element 22 bears against the junction 30a.
  • the figure 5 represents a graph obtained for a device with two switches that can be maneuvered in translation around a position of balance defined by a single return spring that can be compressed or stretched.
  • This equilibrium position can also be defined by means of two pre-loaded and antagonistic springs. Both springs bear on both the housing 28 and the rod 21. At the equilibrium position the forces exerted by each of the springs are equal in absolute value and opposite in direction.
  • This graph defines the curve 10 as for the figures 1 and 4 with the abscissa the stroke of the rod 21 and ordinate the force FO to be applied to the rod 21 to move it.
  • Curve 10 is symmetrical with respect to the origin of the reference of this graph.
  • a curve 50 representing the return force FR is a straight line passing through the origin of the marker. The curve is obtained either with a return spring or with two opposing springs whose stiffness or stiffness are constant.
  • This embodiment makes it possible to define two peaks of forces 11, one negative and the other positive, both placed on the vertical axis as for the figure 4 but has several disadvantages.
  • the minimums 13 of the first and third quadrants are close to the horizontal axis of the graph.
  • the wear of the device can degrade the shape of the curve 10 and if a minimum 13 was to pass on the other side of the horizontal axis, the rod 21 would no longer return to its equilibrium position.
  • the equilibrium position is defined when the circular element 22 is in simultaneous support on the two slopes 25a and 25b, it is necessary to adjust the setting of the spring or return springs so that at this position of balance the curve 50 passes well by the origin of the marker. In other words, at the equilibrium position, the spring or springs must not apply any force on the rod 21.
  • the figure 6 illustrates a solution to these disadvantages.
  • the device comprises two return spring 60 and 61.
  • the two return springs 60 and 61 are arranged in such a way that only one of the return springs 60 or 61 is compressed when the rod 21 leaves its equilibrium position. another return spring 60 or 61 remaining in the state of the equilibrium position.
  • the two springs 60 and 61 operate independently of one another.
  • the device comprises a support piece 62 that can move relative to the rod 21 and relative to the housing 28. In the equilibrium position, the support piece 62 is supported against the housing 28 and against the rod 21.
  • the first return spring 60 bears between the housing 28 and the support piece 62 and the second return spring 61 bears between the rod 21 and the support piece 62. Both springs 60 and 61 exert a force on the support piece 62 in the same direction.
  • the equilibrium position does not depend on the tension of the return springs 60 and 61.
  • the equilibrium position is defined by the support of rigid mechanical parts against each other, namely the support piece 62 on the against the rod 21 and against the housing 28.
  • the displacement of the rod 21 is in translation along the axis 23 to manipulate the two switches.
  • the support piece 62 is a piece of revolution in the form of a washer traversed by the rod 21 and can move in translation along the rod 21 in a bore 63 of axis 23 of the housing 28. At the position of equilibrium, the support piece 62 bears against a bottom 64 of the bore 63. In this same position, the support piece 62 bears against a shoulder 65 of the rod 21.
  • the two springs 60 and 61 are helical. They are mounted concentrically around the axis 23.
  • the bore 63 is partially closed by a cover 66 on which the spring 60 bears by a first of its ends 60a, possibly via a washer 67.
  • a second end 60b of the spring 60 bears against the support piece 62.
  • the rod 21 passes through the washer 67 and the cover 66.
  • the spring 61 bears against a first end 61a against a washer 68
  • a second end 61b of the spring 61 bears against the bearing piece 62.
  • the washer 68 is secured to the rod 21 by means of a circlip 69 disposed in a groove 70 of the rod 21.
  • the support piece 62 may comprise a tubular extension 71 to limit the displacement of the support piece 62 in the bore 63.
  • the extension 71 can abut against the washer 67 to limit the displacement of the rod 21 in the direction "push" P.
  • the support piece 62 rest against the shoulder 65.
  • the washers 62 and 68 both follow the movement of the rod 21.
  • the spring 61 does not deform when the operator pushes on the rod 21.
  • the cam 40 secured to the rod 21, the circular element 22 and the spring 24 both sliding in a radial housing 75 of the cover 66 are also shown.
  • the spring 24 disappears and only the elastic ring is located in the housing 75.
  • the precise definition of the equilibrium position achieved by means of the two return springs 60 and 61 is complementary to the means for modulating the force of the return springs 60 and 61, means implementing the cam 40 and the element circular 22. It is of course possible to implement the precise definition of the equilibrium position without means for modulating the force of the return springs 60 and 61.
  • the figure 7 represents the axial components of the various efforts involved in the exemplary embodiment defined in the figure 6 .
  • the curve 50 representing the return force FR as a function of the stroke of the rod 21, is linear in each of the quadrants where it is present. The linearity is due to the stiffness of each spring 60 and 61.
  • the two springs 60 and 61 have the same stiffness and the slope of the curve 50 is the same for both quadrants. It is of course possible to use springs 60 and 61 having different stiffnesses which would lead to different slopes in each of the quadrants where the curve 50 is present.
  • curve 50 of the figure 7 includes a jump at the vertical axis.
  • the y-intercept has a positive value 80.
  • the ordinate at the origin has a negative value 81.
  • the two ordinates at the origin 80 and 81 represent the calibration or preload of the return spring 60 or 61 corresponding. This is a force that the return springs 60 and 61 exert when the device is at its equilibrium position. This calibration can be equal or different for the two return springs 60 and 61. This calibration makes it possible to increase the values of the stress peaks 11 and the minimums 13 of each quadrant and more generally to shift the curves 10.
  • a curve 82 representing the variation of the force FC as a function of the stroke is also shown.
  • the curve 82 corresponds to the evolution of the effort FC explained by means of the Figures 2 and 3 .
  • the value of the force FC is positive.
  • the effort FC is zero and when the circular element 22 is in contact with the slope 27, the value of the effort FC is negative.
  • a curve 83 shows the evolution of a friction force FF of the circular element 22 during its displacement along the cam 40 away from the balance position.
  • the value of the force FF has the same sign the force FR when the cam 40 moves away from the equilibrium position.
  • the sign of the value of the force FF is reversed when the cam returns to the equilibrium position. To avoid overloading the figure 7 only the positive FF friction force has been shown.
  • the effort FO that the operator must exert on the rod 21 to move it is equal to the sum of the forces FR, FC and FF.
  • the curve 10 shown is the force FO when the rod moves away from the equilibrium position. Because of the negative sign of the friction force FF, the curve 10, not shown here, would approach the horizontal axis when the rod 21 returns to the equilibrium position.
  • the setting of the return springs 60 and 61 may take into account the friction force FF to prevent the minimums 13 have values too low, which could cause the non-return of the rod to the equilibrium position.

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  • Push-Button Switches (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)

Claims (10)

  1. Dateneingabevorrichtung, umfassend
    • einen Schalter, der die Eingabe der Daten ermöglicht,
    • einen Stift (21), der in Bezug auf ein Gehäuse (28) mobil ist, wobei der Stift (21) ermöglicht, den Schalter zu betätigen,
    • eine Rückholfeder, die dem Stift (21) ermöglicht, in eine Gleichgewichtsposition zurückzukehren, wo der Stift (21) nicht betätigt wird, und
    • Mittel zum Modulieren einer Kraft, die von der Rückholfeder ausgeübt wird, um eine Kraftspitze (11) an einem Punkt des Verlaufs des Stifts (21) zu definieren, über den hinaus der Schalter betätigt wird,
    wobei die Mittel zum Modulieren der Kraft umfassen
    • ein kreisförmiges Element (22), das sich im Wesentlichen senkrecht zur Verlagerung des Stifts (21) verlagern kann,
    • eine Nocke (20, 40), die fest mit dem Stift (21) verbunden ist,
    • elastische Mittel (24), die das kreisförmige Element (22) gegen die Nocke (20, 40) gedrückt halten,
    die Nocke (20, 40) umfassend eine Steigung (25, 25a), einen oberen Punkt (26, 26a) und eine Gegensteigung (27, 27a), an denen sich aufeinanderfolgend das kreisförmige Element (22) abstützt, wenn der Stift (21) aus seiner Gleichgewichtsposition zu einer Position betätigt wird, wo der Schalter betätigt wird, dadurch gekennzeichnet, dass wenn der Stift (21) in seiner Gleichgewichtsposition ist, sich das kreisförmige Element (22) an der Nocke (20, 40) auf Höhe eines Übergangs (30, 30a) zwischen der Steigung (25, 25a) und dem oberen Punkt (26, 26a) abstützt,
    und dass die Kraftspitze (11) bereits in der Gleichgewichtsposition erlangt wird, und dass eine Kraft (FO), die auf den Stift (21) ausgeübt werden muss, um ihn zu verlagern, über die Gleichgewichtsposition hinaus abnimmt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Abmessungen der Nocke (20, 40) derart definiert sind, dass die Kraft (FO), die auf den Stift (21) entlang eines Abschnitts (19) des Verlaufs des Stifts (21) ausgeübt wird, d. h. des Abschnitts (19), wo der Schalter betätigt wird, niedriger als die Kraftspitze (11) ist.
  3. Vorrichtung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass sie einen zweiten Schalter umfasst, dass die Mittel zum Modulieren der Kraft ermöglichen, eine zweite Kraftspitze im Verlauf des Stifts (21) zu erzeugen, über die hinaus der zweite Schalter betätigt wird, und dass die Nocke (40) eine zweite Steigung (25b), einen zweiten oberen Punkt (26b) und eine zweite Gegensteigung (27b) umfasst, an denen sich aufeinanderfolgend das kreisförmige Element (22) abstützt, wenn der Stift (21) aus seiner Gleichgewichtsposition zu einer Position betätigt wird, wo der zweite Schalter betätigt wird.
  4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die erste und zweite Steigung (25a, 25b), der erste und zweite obere Punkt (26a, 26b), sowie die erste und zweite Gegensteigung (27a 27b) jeweils symmetrisch in Bezug auf denselben Punkt der Nocke (40) sind.
  5. Vorrichtung nach einem der Ansprüche 3 oder 4, dadurch gekennzeichnet, dass die Kraftspitzen am selben Punkt des Verlaufs des Stifts (21) erlangt werden.
  6. Vorrichtung nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass sie eine zweite Rückholfeder (61) umfasst, und dass die zwei Rückholfedern (60, 61) derart angeordnet sind, dass nur eine der Rückholfedern (60, 61) komprimiert wird, wenn der Stift seine Gleichgewichtsposition verlässt, und die andere Rückholfeder im Zustand der Gleichgewichtsposition bleibt.
  7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, dass sie ein Stützteil (62) umfasst, das sich in Bezug auf den Stift (21) und in Bezug auf das Gehäuse (28) verlagern kann, dass sich das Stützteil (62) in der Gleichgewichtsposition gegen das Gehäuse (28) und gegen den Stift (21) abstützt, dass die erste Rückholfeder (60) sich zwischen dem Gehäuse (28) und dem Stützteil (62) abstützt, und dass die zweite Rückholfeder (61) sich zwischen dem Stift (21) und dem Stützteil (62) abstützt, und dass die zwei Rückholfedern (60, 61) eine Kraft (FR) auf das Stützteil (62) in derselben Richtung ausüben.
  8. Vorrichtung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass eine Übertragungsverlagerung des Stifts (21) in Bezug auf das Gehäuse (28) die Schalterbetätigung ermöglicht.
  9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass der Stift (21) in der Drehung mobil in Bezug auf das Gehäuse ist und dass die Drehung des Stifts ermöglicht, ein Datenelement einzugeben, das durch die Winkelposition des Stifts (21) dargestellt wird.
  10. Vorrichtung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass das kreisförmige Element und die elastischen Mittel, die das kreisförmige Element gegen die Nocke (20, 40) gedrückt halten, durch einen elastischen Ring gebildet sind, der sich in einer Aufnahme (75) des Gehäuses (28) befindet.
EP09177528.8A 2008-11-28 2009-11-30 Dateneingabevorrichtung mit verbesserter Anschlagcharakteristik Not-in-force EP2192604B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0806704A FR2939236B1 (fr) 2008-11-28 2008-11-28 Dispositif d'entree de donnee a sensation tactile amelioree

Publications (2)

Publication Number Publication Date
EP2192604A1 EP2192604A1 (de) 2010-06-02
EP2192604B1 true EP2192604B1 (de) 2017-10-25

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EP09177528.8A Not-in-force EP2192604B1 (de) 2008-11-28 2009-11-30 Dateneingabevorrichtung mit verbesserter Anschlagcharakteristik

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Country Link
US (1) US8242400B2 (de)
EP (1) EP2192604B1 (de)
CN (1) CN101876857B (de)
FR (1) FR2939236B1 (de)

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CN103871767A (zh) * 2014-03-18 2014-06-18 苏州佳世达电通有限公司 按键、电子装置及该电子装置的组装方法
CN108417437A (zh) * 2018-03-28 2018-08-17 南方电网科学研究院有限责任公司 一种用于直流断路器分合闸保持的凸轮保持机构

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EP0004544A2 (de) * 1978-04-10 1979-10-17 Mannesmann Demag AG Schaltelement mit Raststellen

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DE3834390C1 (de) * 1988-10-10 1989-12-07 Leopold Kostal Gmbh & Co Kg, 5880 Luedenscheid, De
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JPH11134972A (ja) * 1997-10-28 1999-05-21 Matsushita Electric Works Ltd 遅れスイッチ
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FR2859783B1 (fr) * 2003-09-16 2005-11-18 Thales Sa Organe de manoeuvre
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EP0004544A2 (de) * 1978-04-10 1979-10-17 Mannesmann Demag AG Schaltelement mit Raststellen

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Publication number Publication date
US8242400B2 (en) 2012-08-14
FR2939236B1 (fr) 2011-04-29
EP2192604A1 (de) 2010-06-02
US20100133079A1 (en) 2010-06-03
CN101876857B (zh) 2013-05-29
FR2939236A1 (fr) 2010-06-04
CN101876857A (zh) 2010-11-03

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