EP2869138A2 - Spiralfeder für Regulierorgan einer mechanischen Armbanduhr, mit einer solchen Spiralfeder ausgestattetes Regulierorgan und Herstellungsverfahren einer solchen Spiralfeder - Google Patents

Spiralfeder für Regulierorgan einer mechanischen Armbanduhr, mit einer solchen Spiralfeder ausgestattetes Regulierorgan und Herstellungsverfahren einer solchen Spiralfeder Download PDF

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Publication number
EP2869138A2
EP2869138A2 EP20140181326 EP14181326A EP2869138A2 EP 2869138 A2 EP2869138 A2 EP 2869138A2 EP 20140181326 EP20140181326 EP 20140181326 EP 14181326 A EP14181326 A EP 14181326A EP 2869138 A2 EP2869138 A2 EP 2869138A2
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EP
European Patent Office
Prior art keywords
spiral
hairspring
point
center
function
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EP20140181326
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English (en)
French (fr)
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EP2869138A3 (de
EP2869138B1 (de
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Stéphane von Gunten
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Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
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Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
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Publication of EP2869138A3 publication Critical patent/EP2869138A3/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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/066—Manufacture of the spiral spring
    • 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
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/22—Compensation of mechanisms for stabilising frequency for the effect of variations of temperature
    • G04B17/222—Compensation of mechanisms for stabilising frequency for the effect of variations of temperature with balances

Definitions

  • the present invention relates to a spiral for a mechanical watch regulating member, a regulating member provided with such a spiral, and a method for producing such a spiral.
  • the movements of mechanical watches are most often regulated by a regulating member comprising a balance and a hairspring.
  • the outer end of the hairspring is attached to the rooster with the peg while the inner end is connected to the axis of the pendulum with the ferrule.
  • the center of gravity of the spiral moves during successive expansions and contractions, so that it does not correspond in every moment with the center of rotation of the spiral on the axis of the balance.
  • the distance between the center of gravity and the center of rotation creates an unbalance, which induces a lateral pressure (that is to say radial) on the axis of the balance and on the pivots of this axis. This unbalance and resulting lateral pressure on the axis disturb isochronism.
  • planar spirals sometimes referred to as flat spirals
  • photolithography or ion etching processes There is therefore an interest in obtaining planar spirals (sometimes referred to as flat spirals), less bulky and easier to perform with photolithography or ion etching processes.
  • WO2012152843 discloses a hairspring comprising a number of through holes or blind holes to increase the area of the oxidizable surface, while maintaining the rigidity of the hairspring.
  • the spiral has a terminal curve that allows the center of gravity of the spiral to be on the axis of the balance. The shape of this curve is not specified, nor its effect on the lateral pressure on the axis of the balance.
  • CH327796 proposes to modify the section of a portion of the spiral blade, for example by folding, in order to increase its rigidity and to obtain a concentric development of the spiral.
  • FR1588702 proposes to extend the outer end of the spiral with a resilient element more rigid than the spring.
  • CH701846 describes a flat hairspring whose rigidity of the blade decreases progressively over more than 360 ° from a point situated between its inner end and its second turn and between its outer end and the penultimate turn.
  • CH692532 proposes to modify the rigidity of a portion of the hairspring through additional heat treatment, which however has the disadvantage of increasing the cost of manufacture.
  • US209642 discloses a flat horological spiral whose thickness is modulated in order to modify the flexibility of the turns and thus improve the isochronism.
  • US3782169 suggests to change the thickness at certain points of the spiral, for example on the outer turn, to adjust its rigidity and therefore the frequency of the oscillator.
  • EP1431844 describes a hairspring that has a variable pitch on one side to achieve a constant oscillation. This document does not describe how this irregular step improves the regularity of the oscillation and does not explain how this spiral must be sized.
  • EP1473604 discloses an analytical method for sizing a spiral spring having a blade portion stiffened by increasing its thickness in the plane of the hairspring. This method, however, is based on a number of approximations.
  • EP1605323 discloses a watch movement hairspring whose outer circumferential turn has a plurality of elbows 1-, 17, 18 and a plurality of reinforcements 19, 20, 21.
  • WO2013034962 describes a spiral comprising an outer turn of variable thickness, arranged to compensate at least partially the variation of the movement of the movement according to the oscillation amplitude of the balance.
  • US2011292770 discloses a silicon balance spring having a portion of its wave-shaped outer curve, to improve the oscillation of the hairspring.
  • the utility model DE202012103893U describes another spiral having a stiffened outer turn due to a reinforced thickness portion.
  • the rigid portion of these spirals constitutes a "dead" zone that is practically undeformed during contractions and expansions of the spiral.
  • the outer coil therefore most often comprises a succession of zones with variable rigidity. The calculation of the deformations of such a spiral with variable stiffness is particularly difficult to perform, so that the shape of these spirals is most often approximations.
  • variable stiffness of the spirals is most often obtained thanks to a variable thickness of the spiral blade in the spiral plane.
  • machining or folding operations that make the manufacturing process more expensive are thus avoided.
  • an outer coating for example a coating of silicon dioxide to compensate for variations as a function of the temperature of the Young's modulus of the spiral .
  • Perfect compensation is only possible when the relationship between the thickness of the coating and that of the core is chosen precisely.
  • the thickness of the layer of dioxide produced by heating is however constant while the thickness of the core varies in the case of a spiral of varying thickness. This results in a Young's modulus stiffened portions of the outer coil which depends on the temperature, and thus an imperfect compensation of unbalance when this temperature varies.
  • the stiffness variation of the outer coil is also sometimes obtained by means of one or more elbows.
  • a portion in which the spiral suddenly changes direction for example a portion in which the local radius of curvature is less than one tenth of the maximum radius of the spiral.
  • Such elbows are difficult to obtain by folding in the case of metal spirals.
  • the presence of such elbows creates zones of internal tension which may, during deformation of the spiral, weaken it or even cause it to break.
  • An object of the present invention is therefore to provide a planar hairspring for a timepiece regulating member whose isochronism is improved compared to the spirals of the prior art.
  • Another object is to propose a planar hairspring for a timepiece regulating organ whose center of gravity does not move or little and substantially corresponds to the center of rotation of the hairspring.
  • Another goal is to propose a plan spiral different from the existing plan spirals.
  • Another object is to propose a planar hairspring for a timepiece regulating member that can be optimized and calculated more easily and more precisely than the existing hairsprings.
  • Another aim is to propose a planar hairspring for a clock-adjusting organ whose thickness of the blade in the plane of the hairspring is substantially constant.
  • Another aim is to propose a planar hairspring for a timepiece regulating organ whose variation of rigidity of the blade comes essentially from the variable radius of curvature, but not from a variation of section or materials.
  • a spiral thickness is considered to be substantially constant if the variations are mainly due to the process of manufacturing.
  • a spiral thickness is also considered substantially constant if the thickness variations do not exceed +/- 10%.
  • the section of the outer turn is considered constant if the variations are due mainly to the manufacturing process.
  • a turn section is also considered to be substantially constant if surface variations do not exceed +/- 10%.
  • the coefficient of proportionality between the distance ( ⁇ ) and the angular position ( ⁇ ) is positive in the case of turns whose radius increases counterclockwise, and negative in the case of turns of increasing radius in the clockwise direction.
  • This solution has the advantage of reducing the lateral pressure on the axis of the balance without requiring a spiral in several planes and without requiring changes in the thickness of the spiral.
  • the reduction is determined with respect to the pressure that would be exerted if the outer turn was made in such a way that the distance between each point of this outer turn and the center of rotation of the hairspring varies linearly as a function of the angular position of this point when the hairspring is at rest.
  • the inner turns and the outer turn are all in the same plane, which allows, in the case of a silicon spiral, to produce it by photolithography. Independently of the material, this characteristic of planar spirals also makes it possible to reduce the bulk.
  • This solution also makes it possible to produce a hairspring whose return torque depends on the amplitude of oscillation, so as to compensate, for example, for the delay due to the exhaust at small amplitudes.
  • the displacements of the center of gravity of the spiral are compensated thanks to the geometrical shape of the last turn at least.
  • the nonlinear function which determines the shape of the last turn can be obtained by successive approximations, by means of a simulation software, taking into account the different conditions (or constraints) expressed in the claims and in the description.
  • the invention therefore results from a choice of unexpected conditions to define the shape of the last turn of a spiral.
  • Conventional scrolls are usually not designed to respect this unusual set of conditions, and nothing a priori makes it possible to determine whether a functional spiral can be achieved in compliance with these conditions.
  • the non-linear function ⁇ f 2 ( ⁇ ) is advantageously chosen so that the displacement of the center of gravity of the last turn during work of the hairspring at least partially offsets the displacement of the center of gravity of said other turns.
  • the center of gravity tends to move away from the peak when the spiral expands, and to get closer to it when the hairspring contracts.
  • the shape of the last turn it is for example possible to make a hairspring in which the center of gravity of the last turn tends to approach the peak during the expansion of the hairspring.
  • the outer turn tends to reduce the overall center of gravity of the spiral on the center of rotation of the balance.
  • the invention also relates to a planar hairspring intended to be mounted on the balance shaft of a mechanical watch regulating member, the hairspring being formed of a blade of substantially constant thickness in the plane of the spiral, the spiral having several internal turns in which the distance ( ⁇ ) between each point and the center of rotation of the hairspring varies according to a substantially linear function as a function of the angular position ( ⁇ ) of the point when the hairspring is at rest; and an outer turn in which the distance ( ⁇ ) between each point (M) of the last turn and the center of rotation increases and then decreases according to the angular position ( ⁇ ) of the point when the hairspring is at rest.
  • the point of the spiral furthest from the center of rotation is thus distinct from the outer end, and distinct from the point of attachment to the peak.
  • the nonlinear function f 2 therefore comprises a maximum, or in any case a local maximum, at a distance from its end; it grows then decreases. It can also include a point of inflection.
  • the last turn of the spiral is advantageously devoid of bends, that is to say devoid of portions in which the local radius of curvature is less than 10% of the maximum radius of the spiral.
  • the local radius of curvature of the last turn varies at rest in a ratio of 1 to 10 at most, preferably in a ratio of 1 to 5 at most, for example in a ratio of 1 to 2 at most. . This avoids the accumulation of tension in the bent areas, which allows for a stronger spiral.
  • the maximum of the function f 2 is advantageously at least 180 ° of the peak when the hairspring is at rest. So, this point away important center is far from the peak and is not likely to collide with the peak when working the spiral or shocks.
  • the linear distance between the maximum of the function f 2 and the outer end of the hairspring moves during work of the hairspring.
  • This linear distance (measured along the hairspring) can preferably decrease during the expansion of the hairspring.
  • the angular distance between the point of inflection and the outer end of the hairspring moves during work of the hairspring.
  • the maximum is preferably at least 210 °, preferably at least 270 ° of the peak when the hairspring is at rest.
  • This angular distance between the point of maximum radius and the outer end of the hairspring decreases during at least a portion of the expansion of the hairspring, so as to bring the point of maximum radius of the position to 180 ° of the pin, so to away from the piton.
  • the nonlinear function f 2 is preferably a continuous function.
  • the derivative of this non-linear function is preferably a continuous function. This makes it possible to obtain a concentric and progressive deformation of the turns, without discontinuity.
  • the invention thus also relates to a hairspring for a watch movement regulating member mechanical device in which the shape of at least one external turn is calculated so as to obtain a restoring torque C 'which depends on the amplitude according to a non-linear function, so as to compensate for the delay due to the small amplitude escapement respectively to compensate the advance at large amplitudes.
  • the shape is chosen so that the average of the torque exerted by the hairspring depends on the amplitude. This means that the hairspring will be stiffer than a conventional hairspring at small amplitudes, and then progressively less rigid than a conventional hairspring at large amplitudes.
  • the shape of the outer coil of the spiral is therefore chosen according to the exhaust.
  • the subject of the invention is also a mechanical watch regulating member comprising an escapement and a spiral formed of a blade of substantially constant thickness in the plane of the spiral, the spiral comprising several internal turns S 1 , S 2 ,. S N-1 for which the distance between each point and the center of rotation of the hairspring varies linearly as a function of the angular position of this point when the hairspring is at rest; the hairspring further comprising an outer turn for which the distance between each point and said center of rotation is a non-linear function of the angular position of the point when the hairspring is at rest; said non-linear function being adapted as a function of the exhaust, so as to reduce the lateral pressure exerted by the spring on the balance shaft when the hairspring is mounted on this axis and / or in order to compensate for the delay due to the exhaust at low amplitudes.
  • This solution therefore makes it possible to propose a regulating member in which the external curve of the spiral is modified with respect to a conventional Archimedes spiral taking into account the exhaust, so as to reduce the pressure on the axis and / or to compensate the drifts due to the exhaust.
  • the spiral 1 illustrated in the figures is a planar spiral, that is to say that all its turns S 1 , S 2 , ... S N-1 , S N are in the same plane. It can therefore be produced by LIGA, DRIE deep etching, laser etching or lithographic etching from a wafer based on silicon, diamond, glass, carbon, etc., or by winding a strip metal, for example Elinvar or Fe / Ni / Cr alloy for example. Spirals formed of several materials, for example silicon-based silicon or diamond-based silicon.
  • the inner end of the hairspring is intended to be mounted on the axis of a not shown beam by means of a shell 10.
  • the shell is integrated in the hairspring.
  • the invention however also applies to spirals without built-in ferrule.
  • the outer end of the hairspring is intended to be fixed to the unrepresented cock by means of a pin 11.
  • the pin is represented here by a pellet coming from one piece to the rest of the hairspring. Nevertheless, it is obvious that the end of the spiral can be made to constant thickness or take other forms according to the desired construction for its attachment to the peak.
  • the regulating member incorporating the hairspring according to the invention may include racket pins which pinch the hairspring at an adjustable distance from the end, in order to adjust the active length of the hairspring and thus to adjust the oscillation frequency of the hairspring. regulating organ.
  • the thickness of the hairspring 1 in the plane of the hairspring is substantially constant.
  • the spiral section is preferably rectangular and substantially constant between the inner end and the outer end. The computer modeling of the spiral deformations is thus simplified and can be performed without having to resort to approximations or simplifications.
  • the rigidity of the hairspring is determined in particular by its section, its length and the Young's modulus of the material used.
  • the hairspring comprises a core in a first material and a heat-compensating envelope in a second material.
  • the core is silicon-based and the envelope is made of silicon dioxide produced by thermal oxidation.
  • the heat compensating envelope compensates for variations in the Young's modulus of the core as the temperature varies.
  • the proportion between the core and the thermocompensator envelope is constant throughout the spiral.
  • the apparent Young's modulus is thus constant throughout the hairspring and for the entire thermocompensated temperature range.
  • the entire length of the hairspring acts as a return spring; there is no dead zone with reduced deformability.
  • the internal turns of the spiral S 1 to S N-1 are spiral Archimedes, so that the distance ⁇ between each point M of these turns and the center of rotation 100 of the spiral is substantially proportional to the angular position ⁇ from this point M when the hairspring is at rest.
  • all the turns of the spiral except the last turn S N on the outside are Archimedean spiral. It is also possible to provide a hairspring in which only certain internal turns are spiral Archimedes, for example the turns S 1 to S N-2 , or the turns S 2 to S N-1 , etc.
  • At least the outer turn S N is modified and does not correspond to an Archimedean spiral.
  • this function f 2 is a non-linear function of the angular position ( ⁇ ) of the point when the hairspring is at rest.
  • the function f 2 is chosen so as to reduce the lateral pressure exerted by the hairspring on the balance shaft when the hairspring 1 rotates about this axis.
  • the function f 2 can also be chosen so that the return torque exerted by the spiral varies as a function of the rotation angle (and therefore the amplitude) of the spiral; the dependence is preferably nonlinear so as to compensate for the delay due to the small amplitude escape.
  • the hairspring can be slightly stiffer at small amplitudes, respectively slightly less rigid at large amplitudes, which makes it possible to compensate for the imperfections of the exhaust.
  • the function f 2 so that the average of the torque exerted during the contraction and during the expansion, for a given angle of rotation, makes it possible to compensate for the imperfections of the escapement.
  • Geometric shapes that fulfill this first condition and / or second condition can be obtained analytically by a system of equations by placing the condition that the unbalance of the hairspring must be minimal regardless of the angular position of the ferrule 10 and the balance.
  • a second condition is preferably that the function f 2 must be continuous.
  • a third condition is that the derived from the function f 2 must be continuous, the fourth condition is preferably that the restoring torque exerted by the spiral on the axis of the balance is proportional to the angle of rotation.
  • this system of equation is simpler to solve than if the rigidity is variable. It is therefore not necessary to resort to approximations to solve it so that it is possible to arrive by analytical calculation to an optimal solution.
  • Geometric shapes that fulfill these different conditions can also be obtained, more simply, by successive approximations by means of a simulation software which makes it possible to estimate the unbalance and / or the lateral pressure on the axis of the balance according to the chosen shape and the angular position of the axis of the balance.
  • This solution has the advantage of reducing the lateral pressure (that is to say radial) on the axis of the balance without requiring spirals in several planes and without requiring changes in the thickness or composition of the spiral.
  • this solution makes it possible to produce a hairspring in which the return torque does not vary linearly as a function of the angle of rotation.
  • a hairspring that would be more rigid at small amplitudes than a conventional hairspring in which the torque varies linearly with amplitude, so as to increase the return torque and therefore the frequency of oscillations. to small amplitudes, and thus compensate the delay due to the exhaust.
  • rack pins not shown can be moved to change the active length of the hairspring and thus finely adjust the step.
  • Geometric shapes that fulfill these different conditions can also be obtained by successive approximations using a simulation software that estimates the return torque exerted as a function of the angular position of the balance, so as to exert the torque that allows in combination with a given escape to obtain an improved isochronism whatever the amplitude of the oscillations of the balance.
  • the non-linear function ⁇ f 2 ( ⁇ ) is advantageously chosen so that the displacement of the center of gravity of the last turn S N during the work of the hairspring 1 at least partially compensates for the displacement of the center of gravity of the other turns S 1 at S N-1 .
  • the nonlinear function f 2 comprises a maximum 13, that is to say a point where the radius ⁇ decreases when the angular position ⁇ increases in absolute value by moving towards the outside of the hairspring. .
  • the point of maximum diameter 13 is advantageously at least 180 ° in absolute value of the peak 11 when the spiral is at rest. Thus, this point at a significant distance from the center is far from the peak and does not risk colliding with the peak when working the spiral or shocks.
  • the linear distance d between the point of maximum radius 13 and the outer end of the hairspring 11 moves during work of the hairspring.
  • This linear distance d (measured along the hairspring) may preferably decrease during the expansion of the hairspring, so that the point of inflection approaches the end of the hairspring.
  • the angular distance ⁇ between the point of maximum radius 13 and the outer end of the hairspring 11 moves during the work of the hairspring.
  • the point of maximum radius is preferably at least 210 °, preferably at least 270 ° of the peak when the hairspring 1 is at rest.
  • This angular distance ⁇ between the point of maximum radius and the outer end of the hairspring decreases during at least part of the expansion of the hairspring.
  • the point of maximum radius 13 is thus almost opposite to the peak 11, or in any case at an angular distance between 120 and 240 ° of the peak, and therefore at a great distance from the peak.
  • This makes it possible to move the center of gravity of the last turn opposite the peak, and to compensate the displacement in the direction of the peak of the center of gravity of the assembly formed by the other turns during the expansion of the hairspring.
  • This also allows to move the point of maximum radius 13 of the piton during the expansion of the spiral.
  • the function f 2 is preferably a continuous nonlinear function.
  • the derivative of this function is preferably a continuous function. This makes it possible to obtain a concentric and progressive deformation of the turns, without discontinuity, and therefore a restoring moment exerted by the spiral on the axis of the balance which varies according to the rotation angle of the spiral, without discontinuities.
  • the Figures 2 to 11 show the shape of the hairspring in different successive angular positions of the balance shaft. In particular, the displacement of the point of maximum radius 13 is observed.
  • the shape of the last turn S N is optimized so as to avoid the risk of contact with the peak 11 and / or the penultimate turn S N-1 .
  • the present invention also relates to a mechanical watch regulator member comprising a spiral formed of a blade of substantially constant thickness in the plane of the spiral, for example a spiral as described above, and a matching exhaust.
  • the escapement comprises for example a Swiss anchor and an anchor wheel.
  • the spiral is made according to the escapement, and comprises several internal spirals S 1 , S 2 , .., S N-1 spiral Archimedes, and an outer turn for which the distance ⁇ between each point and the center of rotation 100 is a nonlinear function f 2 of the angular position ⁇ of the point when the hairspring is at rest.
  • This function is chosen according to the exhaust, so as to reduce the lateral pressure exerted by the spiral on the axis of balance when the spiral is mounted on this axis and / or to compensate for the delay due to the exhaust at low amplitudes.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Metallurgy (AREA)
  • Manufacturing & Machinery (AREA)
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EP14181326.1A 2013-08-19 2014-08-18 Spiralfeder für Regulierorgan einer mechanischen Armbanduhr, mit einer solchen Spiralfeder ausgestattetes Regulierorgan und Herstellungsverfahren einer solchen Spiralfeder Active EP2869138B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH01408/13A CH708429A1 (fr) 2013-08-19 2013-08-19 Spiral pour organe réglant de montre mécanique, organe régulateur muni d'un tel spiral, et procédé de réalisation d'un tel spiral.

Publications (3)

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EP2869138A2 true EP2869138A2 (de) 2015-05-06
EP2869138A3 EP2869138A3 (de) 2016-03-09
EP2869138B1 EP2869138B1 (de) 2017-10-04

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Cited By (4)

* Cited by examiner, † Cited by third party
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JP2017083438A (ja) * 2015-10-22 2017-05-18 ウーテーアー・エス・アー・マニファクチュール・オロロジェール・スイス 一定の断面を有する小型ヒゲゼンマイ
JP2017083435A (ja) * 2015-10-22 2017-05-18 ウーテーアー・エス・アー・マニファクチュール・オロロジェール・スイス 可変する断面を有する小型ヒゲゼンマイ
CN115070394A (zh) * 2022-07-07 2022-09-20 昆山隆正机电科技有限公司 一种游丝与内圈固定座自动组装机
CN118151513A (zh) * 2024-03-27 2024-06-07 深圳市宇珀黄金钟表科技有限公司 机械表的摆轮和游丝稳定性检测方法、装置和计算机设备

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EP4332686A1 (de) * 2022-08-30 2024-03-06 ETA SA Manufacture Horlogère Suisse Spiralfeder für eine spiralunruh-einheit einer uhrwerke

Citations (13)

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Publication number Priority date Publication date Assignee Title
US209642A (en) 1878-11-05 Improvement in balance-springs for time-keepers
CH327796A (fr) 1954-02-22 1958-02-15 Horlogerie Suisse S A Asuag Spiral plat
FR1588702A (de) 1967-11-09 1970-04-17
US3782169A (en) 1969-07-11 1974-01-01 Fab D Assortiments Reunies Regulating the frequency of an oscillatory system including a balance and a coiled spring
CH692532A5 (fr) 1997-10-21 2002-07-15 Ebauchesfabrik Eta Ag Procédé de fabrication d'un spiral de balancier pour mouvement d'horlogerie.
EP1431844A1 (de) 2002-12-19 2004-06-23 SFT Services SA Vorrichtung für das Regelelement eines Uhrwerks
EP1473604A1 (de) 2003-04-29 2004-11-03 Patek Philippe S.A. Unruh und fläche Spiralfeder für Uhrwerk
EP1605323A2 (de) 2004-04-13 2005-12-14 Coredem S.A. Spiralfeder für mechanisches Uhrwerk
CH701846A1 (fr) 2009-09-21 2011-03-31 Rolex Sa Spiral plat pour balancier d'horlogerie et ensemble balancier-spiral.
US20110292770A1 (en) 2009-02-06 2011-12-01 Petra Damasko Mechanical oscillating system for clocks and functional element for clocks
DE202012103893U1 (de) 2011-10-21 2012-10-25 Petra Damasko Schwingsystem für mechanische Uhrwerke
WO2012152843A1 (fr) 2011-05-09 2012-11-15 Lvmh Swiss Manufactures Sa Ressort spiral en silicium pour montre mecanique
WO2013034962A1 (fr) 2011-09-07 2013-03-14 Patek Philippe Sa Geneve Mouvement d'horlogerie à balancier-spiral

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US209642A (en) 1878-11-05 Improvement in balance-springs for time-keepers
CH327796A (fr) 1954-02-22 1958-02-15 Horlogerie Suisse S A Asuag Spiral plat
FR1588702A (de) 1967-11-09 1970-04-17
US3782169A (en) 1969-07-11 1974-01-01 Fab D Assortiments Reunies Regulating the frequency of an oscillatory system including a balance and a coiled spring
CH692532A5 (fr) 1997-10-21 2002-07-15 Ebauchesfabrik Eta Ag Procédé de fabrication d'un spiral de balancier pour mouvement d'horlogerie.
EP1431844A1 (de) 2002-12-19 2004-06-23 SFT Services SA Vorrichtung für das Regelelement eines Uhrwerks
EP1473604A1 (de) 2003-04-29 2004-11-03 Patek Philippe S.A. Unruh und fläche Spiralfeder für Uhrwerk
EP1605323A2 (de) 2004-04-13 2005-12-14 Coredem S.A. Spiralfeder für mechanisches Uhrwerk
US20110292770A1 (en) 2009-02-06 2011-12-01 Petra Damasko Mechanical oscillating system for clocks and functional element for clocks
CH701846A1 (fr) 2009-09-21 2011-03-31 Rolex Sa Spiral plat pour balancier d'horlogerie et ensemble balancier-spiral.
WO2012152843A1 (fr) 2011-05-09 2012-11-15 Lvmh Swiss Manufactures Sa Ressort spiral en silicium pour montre mecanique
WO2013034962A1 (fr) 2011-09-07 2013-03-14 Patek Philippe Sa Geneve Mouvement d'horlogerie à balancier-spiral
DE202012103893U1 (de) 2011-10-21 2012-10-25 Petra Damasko Schwingsystem für mechanische Uhrwerke

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017083438A (ja) * 2015-10-22 2017-05-18 ウーテーアー・エス・アー・マニファクチュール・オロロジェール・スイス 一定の断面を有する小型ヒゲゼンマイ
JP2017083435A (ja) * 2015-10-22 2017-05-18 ウーテーアー・エス・アー・マニファクチュール・オロロジェール・スイス 可変する断面を有する小型ヒゲゼンマイ
CN115070394A (zh) * 2022-07-07 2022-09-20 昆山隆正机电科技有限公司 一种游丝与内圈固定座自动组装机
CN118151513A (zh) * 2024-03-27 2024-06-07 深圳市宇珀黄金钟表科技有限公司 机械表的摆轮和游丝稳定性检测方法、装置和计算机设备

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CH708429A1 (fr) 2015-02-27
EP2869138B1 (de) 2017-10-04

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