EP1941326B1 - Chronometerhemmung für uhrenstück - Google Patents

Chronometerhemmung für uhrenstück Download PDF

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Publication number
EP1941326B1
EP1941326B1 EP06806882A EP06806882A EP1941326B1 EP 1941326 B1 EP1941326 B1 EP 1941326B1 EP 06806882 A EP06806882 A EP 06806882A EP 06806882 A EP06806882 A EP 06806882A EP 1941326 B1 EP1941326 B1 EP 1941326B1
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EP
European Patent Office
Prior art keywords
pallet
axis
detent
impulse
escape wheel
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EP06806882A
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English (en)
French (fr)
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EP1941326A2 (de
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Jean-François Mojon
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Individual
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Individual
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Publication of EP1941326A2 publication Critical patent/EP1941326A2/de
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/063—Balance construction

Definitions

  • the present invention relates to a detent escapement for a timepiece, of the type comprising a toothed escape wheel and a rocker respectively pivoted on a first and a second axis.
  • the escapement according to the invention also comprises an expansion bearing a pallet of rest intended to cooperate with a first tooth of the escape wheel, along a certain length of penetration, to block it in a rest phase .
  • the trigger is rotatably mounted on a third axis to be able to release the first tooth in a disengagement phase.
  • a pulse pallet integral with the balance by presenting a movement coaxial with oscillations of the balance, is intended to cooperate with a second tooth of the escape wheel to receive a pulse of the latter after the rest phase.
  • This document describes an exhaust structure comprising a detent having the shape of a rocker pivoted at one of its ends.
  • This escapement comprises a pendulum bearing small and large trays on its axis, the small plate carrying a release pallet for rotating the trigger, while the large plate carries a notch performing the function of a pulse pallet, arranged so as to cooperate with the teeth of an escape wheel.
  • the trigger comprises, moreover, a rest pallet intended to interact with the teeth of the escapement wheel to block the latter during periods of free oscillation of the balance.
  • the trigger To allow the pivoting of the trigger, it carries an elongated spring, which is secured to the trigger in the region of its end by which it pivots and whose free end is located on the trajectory of the pallet of clearance of the small plate.
  • the latter acts on the spring, in a first direction of rotation of the balance, to rotate the trigger and allow the escape wheel to turn one step, while it simply crosses the spring by elastic deformation of the latter, in the other direction of rotation of the balance.
  • a main object of the present invention is to provide an alternative structure of exhaust escapement to obtain a high efficiency and increased impact safety against the known mechanisms of the prior art.
  • the invention relates to an expansion escapement of the type mentioned above, characterized in that it further comprises a limitation plate, coaxial and integral in rotation of the balance, having a periphery comprising a substantially circular main portion and a cutout arranged to be positioned opposite the pallet of rest in the disengagement phase.
  • the main portion is dimensioned so as to define a safety distance, separating the pallet of rest from the main circular portion when positioned facing one another, less than the length of penetration of the pallet of rest on the first tooth of the escape wheel.
  • the amplitude of the pivoting movements of the trigger is limited, in case of shock, directly by the interaction of the pallet of rest and the limiting plate, without it being necessary to provide additional elements. to ensure this function.
  • the efficiency and the reliability of the escapement according to the present invention are sufficient to allow their implementation in timepieces of small dimensions, in particular because the escape wheel can not be released due to shock intervening outside the clearance phase.
  • the above purpose is achieved while limiting the size of the exhaust to allow its implementation in timepieces of small dimensions, such as wristwatches.
  • the line defined by the third axis of the trigger and the pallet rest is substantially perpendicular to the center line, which reduces the size of the exhaust significantly.
  • the escapement comprises a release pallet secured to the beam by being coaxial thereto, while the trigger carries a spring, a portion of which is disposed in the path of the release pallet.
  • the balance has a small and a large additional trays, both integral with the beam and centered on the second axis, the small plate carrying the release pallet while the large plate carries the pulse pallet.
  • the pulse pallet is carried directly by the limiting plate, the latter then also fulfilling the function of the large conventional tray.
  • the pulse pallet has a pulse surface located at a distance from the second axis less than or equal to the mean radius of the limiting plate and that the periphery of the latter also has a recess. next to the impulse surface to make it accessible. The cutout is then formed on the opposite side of the pulse pallet with reference to the recess, to allow the release of the pallet rest when the release pallet rotates the trigger.
  • the escapement also comprises an anti-gallop device, that is to say to limit the rotation of the escape wheel to a single pitch at each oscillation of the pendulum.
  • FIG. 1 represents a simplified perspective view of the detent escapement according to a first preferred embodiment of the present invention, a part of its constituent elements being torn off to make some others visible;
  • the figure 2a represents a simplified top view of the visible detent escapement on the figure 1 in a first phase of its operation
  • the figure 2b represents a view similar to that of the figure 2a in a second phase of operation
  • the Figure 2c represents a view similar to that of the figure 2a in a third phase of operation
  • the figure 2d represents a view similar to that of the figure 2a in a fourth phase of operation
  • FIG. 3 represents a simplified perspective view of a detail of the exhaust according to a further embodiment
  • FIGS. 4a and 4b are simplified top views of a second construction detail of the escapement, respectively according to first and second preferred embodiments, and
  • FIG. 5 is a simplified perspective view of the detent escapement according to a further preferred embodiment of the present invention, some of its constituent elements being torn off to make some others visible.
  • the figure 1 is a simplified perspective view of the basic building elements of a detent escapement according to a preferred embodiment of the present invention. Some of these elements, normally hidden, have been made visible to expose the general principle of operation.
  • This escapement for a timepiece is intended to be integrated with a watch movement (not shown) comprising in particular a source of mechanical energy, such as a mainspring.
  • a watch movement (not shown) comprising in particular a source of mechanical energy, such as a mainspring.
  • the exhaust is connected to this energy source, via a gear train, by an escape wheel 1.
  • the escape wheel 1 is of conventional type and is represented here with fifteen teeth 2, for illustrative non-limiting. It is intended to be mounted on the watch movement by a pivot 3 defining its axis of rotation X1.
  • the escapement also includes a rocker of which only the location of the pivot 4 is shown schematically for the sake of clarity.
  • the balance is rotatably mounted relative to a second axis, referenced X2 on the figure 1 .
  • a large plate 5 and a small plate 6 are integral with the shaft 4 of the beam by being coaxial.
  • the small plate is visible in the figures thanks to the fact that a portion of the large plate has been omitted for the purposes of this presentation.
  • the large plate 5 carries a pulse pallet 7 whose end having the impulse surface is located at a distance from the axis X2 equal to the general radius of the large plate 5.
  • the impulse surface is made accessible by cutting the large plate forming a recess 8 facing this surface.
  • the small plate 6 carries a release pallet 9, one end of which is arranged projecting with respect to the periphery of the small plate.
  • the angular position of the clearance pallet is predefined with reference to the position of the impulse pallet on the large plate and the skilled person will not encounter any particular difficulty to adjust the relative positions of these two pallets.
  • the exhaust comprises an expansion 11 rotatably mounted with reference to a third axis, referenced X3 on the figure 1 .
  • a spiral spring 12 is fixed by its outer end 13 to the watch movement, while its inner end (not visible) is integral with the trigger 11.
  • the trigger 11 comprises a rectilinear main arm 14 whose central region is mounted on a pivot 15 of axis X3.
  • the main arm carries a cotter pin 16 at a first end 17, while its second end 18 is extended by a bend, itself followed by a short straight portion 19 extending in a direction substantially perpendicular to the direction of the arm main.
  • the spiral spring 12 acts on the main arm 14 of the trigger 11 to return the latter in a predefined angular orientation to the means of positioning a pin 20, integral with the watch movement and intended to cooperate with a flattened on the first end 17 of the trigger. It may be possible to connect the pin to the watch movement by means of an eccentric to allow an adjustable positioning, in a known manner.
  • the trigger 11 carries a pallet of rest 21 mounted in the region of the second end 18 of the main arm and intended to cooperate with the teeth 2 of the escape wheel, as it appears on the figure 1 .
  • the trigger also carries a stop 22 of substantially semi-cylindrical shape at the free end of the rectilinear portion 19, in other words, near the small plate 6.
  • An expansion spring 23, of generally rectilinear shape, is arranged on the trigger 11 so as to have a first end 24 housed in the slot of the cotter pin 16 and its second end 25 disposed in abutment against the flat portion of the stopper 22 It may be noted that the second end 25 has a small angle to the general direction of the spring 23 in a conventional manner.
  • the short rectilinear portion 19 comprises a finger 26 extending from the central portion of the portion 19, in a direction substantially tangential to the periphery of the small plate 6, and finished in a point.
  • the function of this finger 26 will be explained below in connection with the detailed description of the operation of the exhaust which has just been described.
  • the main stages of the kinematics of this escapement are conventional insofar as they include a rest phase, during which the escape wheel is blocked and the balance carries free oscillation arcs, a release phase during which the escape wheel is released to transmit a pulse to the beam, and a blockage of the escape wheel initiating a new rest phase during which the balance resumes its free oscillation.
  • the figure 2a is a top view of the exhaust shown on the figure 1 , the configuration and the relative positions of its different constituent elements being identical to those of the figure 1 .
  • the rest pallet 21 is arranged to cooperate with the teeth 2 of the escape wheel, more precisely with the tooth 200 at the moment represented on the figure 2a .
  • the escape wheel 1 undergoes a permanent force tending to turn it, clockwise, because of its kinematic connection with the energy source of the movement.
  • the interaction of its tooth 200 with the rest pallet 21 ensures its locking in the position of the trigger shown on the figure 2a .
  • the pendulum completes a free oscillation arc in the direction indicated by the arrow F, at the instant shown, because the release pallet 9 carried by the small plate 6 comes into contact with the end 25 of the expansion spring. 23.
  • the pulse pallet 7, carried by the large plate 5 is positioned in the region of a tooth 201 adjacent to the tooth 200 but still located out of range of the pulse pallet.
  • the teeth 200 and 201 are located on either side of this line of centers L.
  • these teeth are the two teeth of the escape wheel 1 closest to the axis X1 of rotation of the balance.
  • this particular feature contributes to reducing the impact of disturbances related to the inertia of the trigger on the pendulum oscillations.
  • the finger 26 of the trigger is disposed opposite a flat 28 of the periphery of the small plate 6, formed by a cutout thereof.
  • the rest pallet 21 is located opposite a cutout 29 formed in the periphery (partially represented in the form of a broken line) of the large plate 5 on the opposite side to that of the recess 8, with reference to the position of the impulse pallet 7.
  • the figure 2b represents the escape a brief moment after that of the figure 2a , when it is at the end of the release phase.
  • the rest pallet 21 leaves the tooth 200 of the escape wheel to release the latter, the movement of the pallet rest being made possible, in the particular case shown, because of the presence of cutting 29 of the large tray.
  • This feature will be explained in more detail in relation to the description of the figure 2d .
  • the finger 26 of the trigger follows the same movement as the rest pallet approaching the small plate 6, such a movement of the finger being possible due to the presence of the flat portion 28 of the small plate.
  • the Figure 2c represents the device of the preceding figures at the beginning of the pulse phase.
  • the rest pallet has left the tooth 200 by releasing the escape wheel 1, the latter thus being driven in a rotational movement by the energy source of the watch movement, in the direction opposite to that indicated by the arrow F.
  • the clearance pallet 9 has crossed the spring 23 by pivoting the trigger 11 and the beam starts a new arc free oscillation.
  • the trigger 11 being simultaneously relieved of the force previously exerted by the release pallet, it is thus subject only to the restoring force of its spiral spring 12 which tends to bring its second end 18 towards the escape wheel 1.
  • the rest pallet 21 then moves away from the large plate 5 while the finger 26 moves away from the small plate 6.
  • the impulse pallet 7 leaves the trajectory of the tooth 201 by simultaneous rotation of the pendulum and the escape wheel, as shown in FIG. figure 2d . It can be noted that both the pulse pallet and the tooth 201 cross the line of centers L during the pulse phase.
  • the rest pallet 21 is located at a distance from the axis X1 greater than the maximum radius of the large plate 5 while the finger 26 is located at a distance from the axis X1 greater than the maximum radius of the small plate 6 .
  • the clearance pallet 9 meets again the end 25 of the expansion spring 23 which, in this sense, can deform to disengage from the abutment 22 of the trigger and, thus allow the passage of the clearance pallet with a minimum of disturbance of the movement of the balance.
  • the crossing of the spring by the release pallet is preferably optimized by the completion of a rounded at the edge of the pallet which lifts the spring during the downward arc.
  • the spring 23 rests against the abutment 22 as soon as its end 25 is released by the release pallet 9.
  • the pendulum then ends its ascending arc before making a new downward arc to find itself in the situation represented on the figure 2a , with the difference that the escape wheel 1 has turned one step in the direction of clockwise rotation.
  • the figure 2d illustrates that the average radius of the large tray 5 is preferably chosen such that the periphery of the tray defines a stop for the pallet rest 21 during the rest phases.
  • the safety distance separating the pallet from the large platform is preferably less than the penetration length of the pallet rest on the tooth of the escape wheel.
  • the implementation of the present invention is also not limited to the use of a release pad associated with an expansion spring.
  • a release pad associated with an expansion spring By way of example, one could alternatively envisage a structure such as that described in the patent application EP 1 544 689 A1 already mentioned in the prior art.
  • the device disclosed in this document should then be adapted to take account of the fact that the rest pallet and the part of the trigger which cooperates with the small plate are located on the same side of the trigger with reference to the axis of rotation X3 of the latter.
  • the finger acting on the trigger should be disposed near the small plate, while the guide curve ensuring the return of the pallet rest towards the escape wheel should face the axis of rotation X1 of the pendulum, being arranged at a distance from the small plateau.
  • FIG 3 is a perspective view showing an anti-gallop system complementary to the device described above to enhance the level of security of the latter. Only the essential elements to the understanding of this system have been represented on this figure.
  • the anti-gallop system comprises a rocker 40 comprising a fork 41 and pivotally mounted on the watch movement, near the small plate 6.
  • the pivoting amplitude of the rocker is limited by two stops 42, intended to cooperate with end 43 of the rocker farthest from the small plateau.
  • the flip-flop 40 further comprises two inclined planes 44 arranged to cooperate with a jumper 45 to define two stable positions of the flip-flop corresponding to the stop positions.
  • the fork 41 is arranged sufficiently close to the small plate to be able to interact with the clearance pallet 9.
  • the pallet exerts pressure on the inner surface of the fork to tilt the lever 40 from one end position to the other.
  • the fork 41 defines two stops for the small plate in case of galloping, or rebate, to prevent the balance to make more than one turn around its axis X1 pivoting.
  • FIGS. 4a and 4b represent particular embodiments of the spring for recalling the trigger in a predefined position, thus providing alternatives to the spiral spring 12 which has been previously described in connection with the main mode.
  • the spring is formed of a piece with the trigger. Therefore, the latter is shown alone on the Figures 4a and 4b , the other constituents of the exhaust being in accordance with what has been explained above.
  • the figure 4a represents a first expansion variant 100 comprising a straight spring 101 extending in a rectilinear direction from the central region of the trigger, near its axis of rotation X3.
  • a stop 102 integral with the watch movement and intended to prevent the rotation of the free end 103 of the spring in the disengagement phase to return the trigger to its position of rest, that is to say in the position it occupies during the rest phases of the escape wheel 1.
  • the figure 4b represents a second expansion variant 110 comprising a spring 111 of sinuous shape.
  • the spring 111 has a first end 112 integral with the central region of the trigger 110, while its second end 113 is fixed on the watch movement by any suitable means, such as for example by a hole 114 made directly in its end 113 and, intended to cooperate with a screw or an eccentric to allow adjustment of the restoring force (not visible).
  • the figure 5 represents a simplified perspective view, similar to that of the figure 1 of the detent escapement according to a further preferred embodiment of the present invention. Part of the components of the exhaust is torn to make some others visible.
  • the large plate 50 has a disk shape, of smaller radius than the large plate 5 of the first embodiment, and comprises a notch in which is housed the pulse pallet 7. Due to its reduced diameter, the large plate 50 does not fulfill the plateau function limitation but simply provides the support function for the pulse pallet, conventionally.
  • a limiting plate 51 is provided to fulfill this function in the present embodiment. It is mounted coaxial to small 6 and large trays 50, being integral with the pendulum. It has a periphery of which a main portion 52 is of circular shape, while a cutout 29 is formed in a predefined angular position with reference to the position of the impulse pallet 7, in a manner similar to that described in FIG. relationship with the first embodiment.
  • the mean radius of the limiting plate 51 is chosen such that the periphery of the latter is situated at a safety distance less than the penetration length of the pallet 21 on the teeth of the escape wheel 1 outside. of the clearance phase.
  • the cutout 29 is positioned facing the pallet of rest during the disengagement phase to allow the pivoting of the trigger 11.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Transmission Devices (AREA)
  • Steering Controls (AREA)
  • Dental Preparations (AREA)
  • Adhesives Or Adhesive Processes (AREA)
  • Electric Clocks (AREA)
  • Axle Suspensions And Sidecars For Cycles (AREA)
  • Ladders (AREA)

Claims (12)

  1. Chronometerhemmung für Uhrenstück, aufweisend
    ein gezahntes Hemmungsrad (1), das über eine erste Achse (X1) dreht,
    eine Unruh, die über eine zweite Achse (X2) dreht und zu der eine Antriebspalette (7) koaxial und verbunden ist,
    eine Auslösung (11, 100, 110), die eine Ruhepalette (21) trägt, die dazu bestimmt ist, mit einem ersten Zahn (200) des Hemmungsrads gemäß einer bestimmten Eindringlänge zusammenzuwirken, um den ersten Zahn in einer Ruhephase zu blockieren,
    wobei die Auslösung über eine dritte Achse (X3) dreht, um in der Lage zu sein, den ersten Zahn (200) in einer Auslösephase freizugeben,
    wobei die Antriebspalette (7) dazu bestimmt ist, mit einem zweiten Zahn (201) des Hemmungsrads zusammenzuwirken, um einen Antrieb von diesem nach der Auslösephase zu erhalten,
    wobei der erste (200) und der zweite (201) Zahn benachbart sind und auf einer und der anderen Seite einer Zentrumsgeraden (L) angeordnet, die die erste (X1) und zweite (X2) Achse in der Ruhephase verbindet,
    dadurch gekennzeichnet, dass sie weiterhin eine zur Unruh koaxiale, mit ihr in Rotation verbundene Begrenzungsscheibe (5, 51) umfasst, die eine Peripherie aufweist, die einen etwa kreisförmigen Hauptabschnitt (52) sowie einen Ausschnitt (29) aufweist, der derart ausgebildet ist, dass er in der Auslösephase gegenüber der Ruhepalette positioniert ist; und
    dadurch, dass der Hauptabschnitt (52) derart dimensioniert ist, um einen Sicherheitsabstand zu definieren, der die Ruhepalette von dem kreisförmigen Hauptabschnitt trennt, wenn sie gegenüberliegend positioniert sind, der kleiner ist als die Eindringlänge.
  2. Hemmung nach Anspruch 1, dadurch gekennzeichnet, dass sie eine zusätzliche große und kleine Scheibe (50, 6) umfasst, die beide mit der Unruh verbunden sind und über der zweiten Achse (X2) zentriert, wobei die kleine Scheibe (6) eine Auslösepalette (9) trägt, wogegen die große Scheibe (50) die Antriebspalette (7) trägt, wobei die Auslösung (11, 100, 110) eine Feder (23) trägt, von der ein Abschnitt (25) auf der Bahn der Auslösepalette (9) angeordnet ist.
  3. Hemmung nach Anspruch 2, dadurch gekennzeichnet, dass die Begrenzungsscheibe (51) einen Durchmesser aufweist, der größer ist als die jeweiligen Durchmesser der kleinen und großen Scheibe (50, 6).
  4. Hemmung nach Anspruch 1, dadurch gekennzeichnet, dass sie eine kleine Scheibe (6) umfasst, die mit der Unruh verbunden ist und über der zweiten Achse (X2) zentriert, die eine Auslösepalette (9) trägt, wobei die Auslösung (11, 100, 110) eine Feder (23) trägt, von der ein Abschnitt (25) auf der Bahn der Auslösepalette (9) angeordnet ist, und dadurch, dass die Antriebspalette (7) von der Begrenzungsscheibe (5) getragen wird.
  5. Hemmung nach Anspruch 4, dadurch gekennzeichnet, dass die Antriebspalette (7) eine Antriebsfläche aufweist, die sich in einem Abstand von der zweiten Achse (X2) befindet, der kleiner oder gleich dem mittleren Radius der Begrenzungsscheibe (5) ist, und dadurch, dass die Peripherie der Begrenzungsscheibe (5) weiterhin eine Aussparung (8) aufweist, die gegenüber der Antriebsfläche eingearbeitet ist, um diese zugänglich zu machen, wobei der Ausschnitt (29) auf der gegenüberliegenden Seite der Antriebspalette (7) in bezug auf die Aussparung eingearbeitet ist.
  6. Hemmung nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass die Auslösung (11, 100, 110) einen Hauptarm (14) umfasst, der über die dritte Achse (X3) durch einen zentralen Bereich drehend angeordnet ist und an dessen erstem Ende (17) die Feder (23) befestigt ist, wogegen die Ruhepalette (21) auf seinem zweiten Ende (18) befestigt ist,
    wobei der Hauptarm nach seinem zweiten Ende durch ein Knie verlängert ist, das selbst durch einen kurzen Abschnitt (19) verlängert ist, der einen Anschlag (22) für den Abschnitt (25) der Feder (23) trägt, der sich auf der Bahn der Auslösepalette befindet,
    wobei der kurze Abschnitt (19) weiterhin einen Finger (26) trägt, der sich in eine Richtung erstreckt, die etwa Tangente zur Peripherie der kleinen Scheibe (6) ist, wobei der Winkel, der den Finger von der kleinen Scheibe bezugnehmend auf die dritte Achse X3 trennt, kleiner ist als der Winkel, der der Eindringlänge der Ruhepalette (21) auf dem ersten Zahn (200) des Hemmungsrads (1) entspricht, und
    dadurch, dass die kleine Scheibe (6) einen verstümmelten Abschnitt (28) auf ihrer Peripherie aufweist, der derart ausgebildet ist, dass er dem Finger gegenüberliegt, wenn die Auslösepalette (9) im Kontakt mit der Feder (23) angeordnet ist.
  7. Hemmung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Ausschnitt (29) ab einer Region des Hauptabschnitts (52) der Peripherie der Begrenzungsscheibe (5, 51), die von der Antriebspalette (7) entfernt ist, einen ersten kurzen Abschnitt mit einer gebogenen Kontur aufweist, gefolgt von einer ersten Rampe, die länger ist als der erste Abschnitt, etwa geradlinig und sich in Richtung der Antriebspalette (7) bis zum Hauptabschnitt erstreckt.
  8. Hemmung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie elastische Mittel (12, 101, 111) umfasst, die ausgebildet sind, um eine Kraft auf die Auslösung (11, 100, 110) auszuüben, die dazu neigt, die Ruhepalette (21) in den Bereich einzuführen, der zwei nebeneinanderliegende Zähne des Hemmungsrads (1) trennt, wobei die elastischen Mittel mit der Auslösung von einem Teil gebildet werden.
  9. Hemmung nach Anspruch 8, dadurch gekennzeichnet, dass die elastischen Mittel eine Feder (111) in einer gewundenen Form umfassen, von der ein erstes Ende (112) mit der Auslösung (110) verbunden ist, wogegen ihr zweites Ende (113) in bezug auf die Auslösung eine feste vordefinierte Position aufweist.
  10. Hemmung nach einem der Ansprüche 2 bis 9, dadurch gekennzeichnet, dass sie weiterhin eine Anti-Galopp-Wippe (40) umfasst, die zwischen zwei stabilen Extrempositionen gemäß einer Achse parallel zur zweiten Achse drehbar ist und mindestens eine Kontaktfläche aufweist, die derart ausgebildet ist, um mit der Auslösepalette (9) zusammenzuwirken, damit die Anti-Galopp-Wippe von einer Extremposition in die andere dreht.
  11. Uhrwerk für Uhrenstück, eine Hemmung nach einem der vorhergehenden Ansprüche umfassend, eine Energiequelle und ein Übersetzungsgetriebe, das die kinematische Verbindung zwischen der Energiequelle und dem Hemmungsrad der Hemmung gewährleistet.
  12. Uhrenstück, das ein Uhrwerk nach Anspruch 11 umfasst.
EP06806882A 2005-09-30 2006-09-29 Chronometerhemmung für uhrenstück Active EP1941326B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06806882A EP1941326B1 (de) 2005-09-30 2006-09-29 Chronometerhemmung für uhrenstück

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP05109056A EP1770452A1 (de) 2005-09-30 2005-09-30 Chronometerhemmung für Uhren
EP06806882A EP1941326B1 (de) 2005-09-30 2006-09-29 Chronometerhemmung für uhrenstück
PCT/EP2006/066884 WO2007039558A2 (fr) 2005-09-30 2006-09-29 Echappement a detente pour piece d'horlogerie

Publications (2)

Publication Number Publication Date
EP1941326A2 EP1941326A2 (de) 2008-07-09
EP1941326B1 true EP1941326B1 (de) 2009-04-22

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Application Number Title Priority Date Filing Date
EP05109056A Withdrawn EP1770452A1 (de) 2005-09-30 2005-09-30 Chronometerhemmung für Uhren
EP06806882A Active EP1941326B1 (de) 2005-09-30 2006-09-29 Chronometerhemmung für uhrenstück

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EP05109056A Withdrawn EP1770452A1 (de) 2005-09-30 2005-09-30 Chronometerhemmung für Uhren

Country Status (10)

Country Link
US (1) US7458717B2 (de)
EP (2) EP1770452A1 (de)
JP (1) JP4898814B2 (de)
CN (1) CN101278240B (de)
AT (1) ATE429666T1 (de)
DE (1) DE602006006464D1 (de)
ES (1) ES2326340T3 (de)
HK (1) HK1118344A1 (de)
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EP2706416B1 (de) 2012-09-07 2015-11-18 The Swatch Group Research and Development Ltd Flexibler Anker mit konstanter Kraft
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EP2887157B1 (de) * 2013-12-23 2018-02-07 The Swatch Group Research and Development Ltd. Optimierte uhrhemmung
EP2947522B1 (de) 2014-05-20 2017-05-03 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Uhranker für mechanischen Oszillator, und Mechanismus zur Zeitauslösung der Uhr
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RU2408042C2 (ru) 2010-12-27
CN101278240B (zh) 2010-06-02
US7458717B2 (en) 2008-12-02
DE602006006464D1 (de) 2009-06-04
ATE429666T1 (de) 2009-05-15
WO2007039558A2 (fr) 2007-04-12
EP1941326A2 (de) 2008-07-09
JP4898814B2 (ja) 2012-03-21
HK1118344A1 (de) 2009-02-06
US20080219103A1 (en) 2008-09-11
ES2326340T3 (es) 2009-10-07
RU2008117152A (ru) 2009-11-10
CN101278240A (zh) 2008-10-01
EP1770452A1 (de) 2007-04-04
JP2009510425A (ja) 2009-03-12
WO2007039558A3 (fr) 2007-06-28

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