EP3598243B1 - Uhrmechanismus mit organ, das sich in sprüngen bewegt - Google Patents

Uhrmechanismus mit organ, das sich in sprüngen bewegt Download PDF

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Publication number
EP3598243B1
EP3598243B1 EP18184530.6A EP18184530A EP3598243B1 EP 3598243 B1 EP3598243 B1 EP 3598243B1 EP 18184530 A EP18184530 A EP 18184530A EP 3598243 B1 EP3598243 B1 EP 3598243B1
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EP
European Patent Office
Prior art keywords
actuating spring
timepiece mechanism
winding
hub
elastic
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EP18184530.6A
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English (en)
French (fr)
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EP3598243A1 (de
Inventor
Samuel Tanner
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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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
    • G04B19/00—Indicating the time by visual means
    • G04B19/02—Back-gearing arrangements between gear train and hands
    • 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
    • G04B19/00—Indicating the time by visual means
    • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/24306—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator combination of different shapes, e.g. bands and discs, discs and drums
    • G04B19/2432—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement

Definitions

  • the present invention relates to a jumping organ watch mechanism, in particular for the instantaneous display of a temporal quantity such as the date.
  • Instantaneous display mechanisms comprising a snail cam against which a rocker rests under the action of a return spring applied against the rocker are known in watchmaking.
  • the return spring is a V-shaped, U-shaped or spiral leaf.
  • the lever slides from the lower part to the upper part of the cam, which gradually arms the return spring, then the lever drops from said upper part to said lower part, this sudden movement, considered instantaneous, being used to actuate an indicator such as a needle associated with a scale or a disk bearing indications and cooperating with a window.
  • Patent applications CH 702137 and EP 2241944 describe such mechanisms for a minute counter.
  • the present invention aims to remedy this drawback or at least to attenuate it and to this end proposes a watch mechanism comprising a motor member, a regulating member for regulating the motor member, a jumping member, an actuating spring, a or several gears between the driving member and the actuating spring and a winding and blocking device allowing continuous winding of the actuating spring by the driving member via the gear(s) and periodic disarming of the spring actuation, the actuation spring causing the jumping member to make a jump each time it is unwinded, characterized in that the actuation spring is a spring with non-linear behavior which produces, between a winding angle ⁇ a and a winding angle ⁇ b separated by at least 10°, an elastic return moment which does not vary by more than 10%, and in that the actuating spring is pre-wound with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ], the clockwork mechanism was nt arranged so that, during its
  • the present invention also proposes a timepiece, such as a clock, a wristwatch or a pocket watch, comprising this timepiece mechanism.
  • the figure 1 is a block diagram of a timepiece mechanism 1 according to the invention, with a jumping member, for a timepiece such as a clock, a wristwatch or a pocket watch.
  • the watch mechanism 1 forms or is part of a watch movement. It comprises a drive member 2, a gear train 3 driven by the drive member 2, a winding and locking device 4 actuated by the gear train 3 and a flexible wheel 5 actuated by the winding and locking device 4.
  • the driving member 2 is typically in the form of one or more barrel springs housed in one or more respective barrels.
  • the rotation of the gear train 3 and of the barrel or barrels is regulated in a conventional manner by a regulating member 6, for example with escapement and balance-spring.
  • Motor member 2, gear train 3 and regulator member 6 are conventional and will therefore not be described in more detail.
  • the winding and blocking device 4 is shown in picture 2 . It comprises a winding wheel set 7, a blocking wheel set 8 and a moving frame 9.
  • a wheel 10 of the winding wheel set 7 meshes with the gear train 3 and is continuously driven by the latter.
  • a star wheel 11 of the winding mobile 7, coaxial with and integral in rotation with the wheel 10, is located in a first closed contour opening 12 of the mobile frame 9 and constitutes a rotary drive member cooperating with two drive elements 13 diametrically opposed formed in the wall of the opening 12.
  • a star 14 of the blocking mobile 8 is located in a second opening with a closed outline 15 of the mobile frame 9 and constitutes a rotary blocking member cooperating with two stop elements 16 diametrically opposite formed in the wall of the opening 15.
  • This star 14 is coaxial with and integral in rotation with a pinion 17 forming part of the mobile blocking device 8.
  • the mobile frame 9 is guided in translation along the double arrow F by a device flexible guide 18 with which it preferably forms a single piece.
  • the mobile frame 9 could however be guided in rotation.
  • the assembly 9, 11, 14 forms a blocking device of the type described in patent applications PCT/IB2018/052645 and PCT/IB2018/052646 of the applicant which are incorporated in the present application by reference.
  • the flexible wheel 5 is shown in figures 2 and 3 . It comprises a hub 19 which is coaxial and integral in rotation with the winding mobile 7, a rim 20 and elastic arms or blades 21 uniformly distributed around the hub 19 and connecting the hub 19 to the rim 20.
  • the rim 20 is thus suspended from the hub 19, and guided in rotation with respect to the hub 19, by the elastic arms 21.
  • the latter together form an actuating spring 22 capable of storing mechanical energy by stretching (by a rotation of the hub 19 with respect to to the serge 20 in one direction, namely the clockwise direction of the picture 2 or 3 ) and restore it by relaxing (by rotating the rim 20 relative to the hub 19 in the Same direction).
  • the flexible wheel 5 further comprises an external toothing 23 secured to the rim 20. This toothing 23 meshes with the pinion 17 of the blocking mobile 8.
  • the flexible wheel 5 is preferably in one piece. It is for example made of metal, alloy, silicon (typically coated with silicon oxide), plastic, mineral glass or metallic glass. It can be produced by machining or by the LIGA technique, in particular in the case where it is made of a metal or alloy, by deep reactive ion etching called DRIE, in particular in the case where it is made of silicon, by molding, in particular in the case where it is made of plastic or metallic glass, or by laser cutting, in particular in the case where it is made of mineral glass.
  • DRIE deep reactive ion etching
  • a display disc 24 is fixed, for example glued, to the rim 20.
  • the display disc 24 is a date display disc bearing two series of indications “1” to “31 » and the rim 20 and the display disc 24 perform together in a jumping manner, with one jump per day, one turn in two months.
  • the indications carried by the display disk 24 are successively visible through an aperture of a dial of the timepiece.
  • the display disc 24 could be one piece with the flexible wheel 5.
  • the operation of the clockwork mechanism 1 is as follows.
  • the winding mobile 7 and with it the hub 19 rotate continuously, according to a rhythm determined by the oscillations of the regulating member 6, in the clockwise direction of the picture 2 under the action of the motor member 2 exerted via the gear train 3. In doing so, they continuously arm the actuating spring 22. Most of the time, the blocking mobile 8, which is under tension due to the torque the actuating spring 22, is blocked by one of the stop elements 16 against which rests on one of the branches of star 14, which keeps rim 20 stationary and therefore the torque delivery end of actuating spring 22.
  • the rim 20 is released periodically at times which are determined by the meeting between the star 11 of the winding mobile 7 and each of the drive elements 13. As soon as a branch of the star 11 comes into contact with the one of the drive elements 13, it cooperates with the latter to move the mobile frame 9 in order to disengage the star wheel 14 of the locking mobile 8 from the stop element 16 against which it was resting. Under the action of the actuating spring 22, the rim 20 and the blocking mobile 8 begin to rotate abruptly until another branch of the star 14 comes to rest on the other element of stop 16. During this sudden movement, considered instantaneous with respect to the movement of the gear train 3 and the winding mobile 7, the indication visible through the aperture is replaced by the following one and the actuating spring 22 is partially disarmed.
  • the different gear ratios in the watch mechanism 1 and the number of branches of each of the stars 11 and 14 are chosen so that the actuating spring 22 accumulates between two successive unwindings (two successive jumps of the serge 20) the same quantity of energy than that released at each disarming.
  • the watch mechanism 1 as described above and illustrated in figure 1 and 2 is an example of implementation. Many variations are possible.
  • the clockwork mechanism 1 could be adapted to cause the display disk 24 to display a quantity other than the date, such as the month, the day of the week, the hour, the minute or the second.
  • the winding mobile 7 could be kinematically connected to the hub 19 in a way other than by being integral in rotation with the latter, for example by means of one or more gears.
  • the blocking mobile 8 could be kinematically connected to the rim 20 by more than one gear.
  • Another one modification could consist in making the driving member 2 mesh directly with the wheel 10.
  • the winding and blocking device 4 is advantageous in particular for protecting the watch mechanism 1 against shocks and for reducing friction, as explained in the patent applications PCT/IB2018/052645 and PCT/IB2018/052646 .
  • the jumping member of watch mechanism 1 could be constituted by hub 19.
  • Hub 19 would then be coaxial and integral in rotation with blocking wheel set 8 while that pinion 17 which meshes with toothing 23 carried by rim 20 would be coaxial and integral in rotation with winding mobile 7.
  • the number of branches of each of stars 11 and 14 would be adapted accordingly.
  • the needle can, for example, being a dead seconds hand.
  • the elastic arms 21 which constitute the actuating spring 22 are specially shaped to improve the constancy of the torque or elastic return moment exerted by this actuating spring 22, and therefore the constancy of the torque necessary to continuously arm this actuating spring 22, and thus improve the regularity of the oscillations of the regulating member 6.
  • the insulated flexible wheel 5 shown in picture 3 has, due to the shape of its elastic arms 21, a privileged direction of rotation of its rim 20 with respect to its hub 19, this direction being defined as that which allows, from its state of rest, the greatest displacement relative angle of its rim 20 with respect to its hub 19. This preferred direction of rotation is clockwise at the picture 3 .
  • the actuating spring 22 deforms to exert a restoring moment M( ⁇ ) depending on the position ⁇ of the rim 20 relative to the hub 19, tending to cause the rim 20 to pivot relative to the hub 19 in the opposite direction to the winding direction, that is to say in the opposite direction to the privileged direction of rotation, thus tending to make it return to its resting state.
  • the actuating spring 22 is designed, in particular by its shape, to exert, in the flexible wheel 5, an elastic return moment M( ⁇ ) that is substantially constant over a range of angular positions [ ⁇ a , ⁇ b ] of the serge 20 with respect to hub 19 by at least 10°, preferably by at least 15°, preferably by at least 20°, preferably by at least 25°.
  • “Substantially constant” moment is understood to mean a moment not varying by more than 10%, preferably 5%, more preferably 3%, typically 1.5%, it being understood that this percentage can be further reduced.
  • the actuating spring 22 is pre-armed with a value ⁇ arm included in the range [ ⁇ a , ⁇ b ] and the gear ratios and the numbers of branches of the stars 11 and 14 are chosen so that the winding angle ⁇ remains in this range during operation of said mechanism, so that the elastic return moment remains substantially constant.
  • Each unwinding of the actuating spring 22 brings the winding angle ⁇ back to the value ⁇ arm .
  • the elastic arms 21 can be shaped by topological optimization by applying the teaching of the publication "Design of adjustable constant-force forceps for robot-assisted surgical manipulation", Chao-Chieh Lan et al., 2011 IEEE International Conference on Robotics and Automation, Shanghai International Conference Center, May 9-13, 2011, China.
  • the topological optimization discussed in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic arms.
  • each of the elastic arms 21 of the actuating spring 22 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the flexible wheel 5 to be designed as well as the constraint “( M max -M min )/((M max +M min )/2) ⁇ 0.05” sought.
  • the inequality “(M max -M min )/((M max +M min )/2) ⁇ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range [ ⁇ a_5% , ⁇ b_5% ].
  • this flexible wheel 5 comprising three elastic arms 21 distributed uniformly around the hub 19.
  • This flexible wheel 5 corresponds to that shown in the figures.
  • the dimensions of this flexible wheel 5 are as follows: Gear head diameter: 26.12mm Outside diameter of the hub: 4mm Inner diameter of the serge: 20mm Height : 0.2mm Thickness of the elastic arms: 90 ⁇ m Curvilinear length of each arm: 9.82mm
  • control points Q 0 , Q 1 , Q 2 , Q 3 , Q 4 , Q 5 , Q 6 were used.
  • the coordinates of these control points are shown in Table 1 below.
  • ⁇ i> ⁇ u>Table 1 Coordinates of control points Q ⁇ sub>0 ⁇ /sub> to Q ⁇ sub>6 ⁇ /sub>. ⁇ /u> ⁇ /i> Variables x-coordinates [mm] y-coordinates [mm] Q 0 1.51325 1.30775 Q1 3.7465 3,238 Q2 5,625 -1.1825 Q3 6.875 0.907 Q4 7.5 2.06575 Q5 8.75 0 Q6 10 0
  • the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bézier curve of order 4 based on control points Q 3 to Q 6 .
  • the graph of the figure 5 shows the geometry of the external diameter of the hub 19, of the internal diameter of the rim 20 and of one of the elastic arms 21 of the flexible wheel 5 that the applicant has designed, the geometry of said arm being defined by a curve passing through the set of point coordinates defined in Table 2 above. This graph is produced in an orthonormal frame.
  • the figure 6 represents the results of a simulation of the evolution of the elastic return moment of the flexible wheel 5 isolated thus produced as a function of the angular position ⁇ of its rim 20 with respect to its hub 19.
  • the simulation carried out considers the insulated flexible wheel 5 made of silicon coated with a layer of silicon oxide 3 ⁇ m thick, but any suitable material can be used.
  • materials such as Nivaflex ® 45/18 (alloy based on cobalt, nickel and chromium), CK101 (unalloyed structural steel) or other alloys, plastic, mineral glasses or metallic glasses, for example Vitreloy 1b, are also suitable and make it possible to obtain flexible wheels whose elastic return moment is substantially constant over the same angular ranges [ ⁇ a , ⁇ b ].
  • the angular operating range allowing the delivery of a substantially constant moment being a constant linked to the shape of the elastic arms 21, the operating angle ⁇ b must be less than the angle ⁇ lim corresponding to the limit before yielding or rupture of the actuating spring 22. This makes it possible to define the maximum thickness that it is possible to achieve on the arms.
  • Table 3 gives, by way of indication, the values ⁇ a_y% , ⁇ b_y% and ⁇ (range of angular positions at substantially constant moment) associated with the flexible wheel 5 produced by the applicant as a function of the percentage of constancy y considered as well as the associated torque values M min and M max .
  • the figure 7 shows different curves representative of a normalized moment of force M( ⁇ ) exerted by the flexible wheel 5 isolated as a function of the angular position ⁇ of its rim 20 with respect to its hub 19 (winding angle) for different section variations elastic arms 21.
  • the highest curve, denoted by A1 corresponds to elastic arms 21 of constant section and thickness of 30 ⁇ m.
  • the curves located below the curve A1 correspond to elastic arms 21 whose thickness decreases linearly from the hub 19 to the serge 20, the thickness at the point of junction with the hub 19 being 30 ⁇ m for each curve, the thickness at the point of junction with the serge 20 being 29 ⁇ m for the curve A2, 28 ⁇ m for the curve A3 and 27 ⁇ m for the curve A4.
  • An improvement in consistency is observed for curves A2, A3 and A4 compared to curve A1 over a range of angles of reinforcement of length greater than 15°.
  • the figure 8 shows two curves B1 and B2 representative of a normalized moment of force M( ⁇ ) exerted by the flexible wheel 5 isolated as a function of the angular position ⁇ of its rim 20 with respect to its hub 19 (winding angle) for different shapes of section of the elastic arms 21.
  • the highest curve, B1 corresponds to elastic arms 21 of constant section and thickness of 30 ⁇ m.
  • Curve B2 corresponds to elastic arms 21 whose thickness decreases linearly from the hub 19 to the middle of the arm then increases linearly from the middle of the arm to the serge 20, the thickness at the junction points with the hub 19 and with the serge 20 being 30 ⁇ m, the thickness in the middle of the arm being 29 ⁇ m.
  • the elastic arms 21 have a variable section
  • this typically varies in a strictly monotonous manner (it increases or decreases without interruption but not necessarily linearly) over at least one continuous portion of the elastic arm representing 10% , preferably 20%, preferably 30%, preferably 40%, of the (curvilinear) length of the elastic arm.
  • the variation of the section is also chosen to improve the constancy of the elastic restoring moment over the range [ ⁇ a , ⁇ b ] compared to elastic arms of the same shape as the arms 21 but of constant section.
  • the elastic arms 21 can in particular take a form as described in the article “Functional joint mechanisms with constant torque outputs”, Mechanism and machine theory 62 (2013) 166-181, Chia-Wen Hou et al.
  • the height, length, thickness and/or material of the elastic arms 21, or even the inclination of the elastic arms 21 relative to the hub 19 (in the plane of the flexible wheel 5), can also be modified to adjust the value of the substantially constant elastic restoring moment.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
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Claims (15)

  1. Uhrmechanismus (1), der ein Antriebsorgan (2), ein Regulierorgan (6) zum Regulieren des Antriebsorgans (2), ein springendes Organ (20, 24), eine Betätigungsfeder (22), eine oder mehrere Getriebe (3, 10) zwischen dem Antriebsorgan (2) und der Betätigungsfeder (22) und eine Spannungs- und Blockiervorrichtung (4) umfasst, die dazu gestaltet ist, eine kontinuierliche Spannung der Betätigungsfeder (22) durch das Antriebsorgan (2) über das oder die Getriebe (3, 10) und ein periodisches Entspannen der Betätigungsfeder (22) zu ermöglichen, wobei die Betätigungsfeder (22) dazu gestaltet ist, zu bewirken, dass das springende Organ (20, 24) bei jeder seiner Entspannungen einen Sprung ausführt, wobei die Betätigungsfeder (22) mindestens einen elastischen Arm (21) umfasst, dadurch gekennzeichnet, dass der oder jeder elastische Arm (21) eine gewundene Form aufweist, dadurch, dass die Betätigungsfeder (22) eine Feder mit nichtlinearem Verhalten ist, die zwischen einem Spannungswinkel θa und einem Spannungswinkel θb, die um mindestens 10° getrennt sind, ein elastisches Rückzugsmoment erzeugt, das sich um nicht mehr als 10 % verändert, und dadurch, dass die Betätigungsfeder (22) um einen Wert θarm vorgespannt ist, der in dem Bereich [θa, θb] enthalten ist, wobei der Uhrmechanismus (1) derart gestaltet ist, dass während seines Betriebs der Spannungswinkel der Betätigungsfeder (22) im Bereich [θa, θb] bleibt.
  2. Uhrmechanismus (1) nach Anspruch 1, dadurch gekennzeichnet, dass das elastische Rückzugsmoment, das von der Betätigungsfeder (22) erzeugt wird, sich in dem Bereich [θa, θb] um nicht mehr als 5 %, vorzugsweise um nicht mehr als 3 %, vorzugsweise um nicht mehr als 1,5 % verändert.
  3. Uhrmechanismus (1) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Spannungswinkel θa und θb um mindestens 15°, vorzugsweise mindestens 20°, vorzugsweise mindestens 25° getrennt sind.
  4. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Betätigungsfeder (22) mehrere der elastischen Arme (21) umfasst, die gleichmäßig winklig verteilt sind.
  5. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die geometrische Form des oder jedes elastischen Arms (21) eine Bezierkurve oder eine Folge von Bezierkurven ist.
  6. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der oder jeder elastische Arm (21) einen veränderlichen Querschnitt aufweist, dessen Veränderung derart ausgewählt ist, dass die Konstanz des elastischen Rückzugsmoments im Bereich [θa, θb] in Bezug auf einen elastischen Arm mit der gleichen Form aber konstantem Querschnitt verbessert ist.
  7. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass er ein flexibles Rad (5) umfasst, das eine Nabe (19), einen Fußkreis (20) und die Betätigungsfeder (22) umfasst, welche die Nabe (19) mit dem Fußkreis (20) verbindet, und dadurch, dass das springende Organ den Fußkreis (20) oder die Nabe (19) umfasst.
  8. Uhrmechanismus (1) nach Anspruch 7, dadurch gekennzeichnet, dass das flexible Rad (5) einstückig ist.
  9. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Spannungs- und Blockiervorrichtung (4) ein bewegliches Organ (9), ein drehbares Mitnehmerorgan (11), das kinematisch mit dem Antriebsorgan (2) und mit einem Spannungsende der Betätigungsfeder (22) verbunden ist und dazu gestaltet ist, das bewegliche Organ (9) zu verlagern, und ein drehbares Blockierorgan (14) umfasst, das kinematisch mit einem Momentabgabeende der Betätigungsfeder (22) und mit dem springenden Organ (20, 24) verbunden ist, wobei das drehbare Blockierorgan (14) durch das bewegliche Organ (9) blockiert wird und periodisch durch die Verlagerungen des beweglichen Organs (9), die von dem drehbaren Antriebsorgan (11) bewirkt werden, entsperrt wird.
  10. Uhrmechanismus (1) nach Anspruch 9, dadurch gekennzeichnet, dass das bewegliche Organ (9) translatorisch beweglich ist.
  11. Uhrmechanismus (1) nach Anspruch 9 oder 10, dadurch gekennzeichnet, dass das bewegliche Organ (9) eine erste und eine zweite Öffnung mit geschlossenem Umriss (12, 15) ist, mit deren Wänden das drehbare Mitnehmerorgan (11) beziehungsweise das drehbare Blockierorgan (14) zusammenwirken.
  12. Uhrmechanismus (1) nach einem der Ansprüche 9 bis 11, wenn abhängig von Anspruch 7 oder 8, dadurch gekennzeichnet, dass das springende Organ (20, 24) den Fußkreis (20) umfasst und die Nabe (19) drehfest mit dem drehbaren Mitnehmerorgan (11) verbunden ist.
  13. Uhrmechanismus (1) nach einem der Ansprüche 9 bis 11, wenn abhängig von Anspruch 7 oder 8, dadurch gekennzeichnet, dass das springende Organ die Nabe (19) umfasst, die drehfest mit dem Blockierorgan (14) ist.
  14. Uhrmechanismus (1) nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass das springende Organ (20, 24) ein Anzeigeorgan (24) umfasst.
  15. Uhr, die einen Uhrmechanismus (1) nach einem der Ansprüche 1 bis 14 umfasst.
EP18184530.6A 2018-07-19 2018-07-19 Uhrmechanismus mit organ, das sich in sprüngen bewegt Active EP3598243B1 (de)

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EP18184530.6A EP3598243B1 (de) 2018-07-19 2018-07-19 Uhrmechanismus mit organ, das sich in sprüngen bewegt

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EP3598243A1 EP3598243A1 (de) 2020-01-22
EP3598243B1 true EP3598243B1 (de) 2022-10-19

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Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH718066A2 (fr) 2020-11-17 2022-05-31 Patek Philippe Sa Geneve Organe horloger comprenant au moins une lame ressort.
EP4248277A1 (de) 2020-11-17 2023-09-27 Patek Philippe SA Genève Verfahren zur herstellung eines federblattes eines uhrenelements und besagtes federblatt

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH1046070A4 (de) 1970-07-10 1972-02-29
CH702137B1 (fr) 2007-02-05 2011-05-13 Patek Philippe Sa Geneve Dispositif d'entraînement et de réglage d'un compteur instantané et pièce d'horlogerie comportant un tel dispositif.
CH700753B1 (fr) 2009-04-15 2014-03-14 Patek Philippe Sa Geneve Mécanisme de compteur instantané et came escargot pour un tel mécanisme.
CN103097965B (zh) * 2010-07-19 2015-05-13 尼瓦洛克斯-法尔股份有限公司 具有弹性枢轴的振荡机构和用于传递能量的可动元件
ES2661863T3 (es) 2013-04-30 2018-04-04 Audemars Piguet (Renaud Et Papi) Sa Mecanismo de salto instantáneo para pieza de relojería

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