EP4191346B1 - Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif - Google Patents

Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif Download PDF

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Publication number
EP4191346B1
EP4191346B1 EP21212441.6A EP21212441A EP4191346B1 EP 4191346 B1 EP4191346 B1 EP 4191346B1 EP 21212441 A EP21212441 A EP 21212441A EP 4191346 B1 EP4191346 B1 EP 4191346B1
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EP
European Patent Office
Prior art keywords
resonator mechanism
flexible
pivot
resonator
modulus
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.)
Active
Application number
EP21212441.6A
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German (de)
English (en)
French (fr)
Other versions
EP4191346A1 (fr
Inventor
Gianni Di Domenico
Mohammad Hussein Kahrobaiyan
Dominique Lechot
Pascal Winkler
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Swatch Group Research and Development SA
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Swatch Group Research and Development SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Swatch Group Research and Development SA filed Critical Swatch Group Research and Development SA
Priority to EP21212441.6A priority Critical patent/EP4191346B1/fr
Priority to US17/812,456 priority patent/US20230176522A1/en
Priority to JP2022134701A priority patent/JP7407250B2/ja
Priority to CN202211089846.8A priority patent/CN116224741A/zh
Publication of EP4191346A1 publication Critical patent/EP4191346A1/fr
Application granted granted Critical
Publication of EP4191346B1 publication Critical patent/EP4191346B1/fr
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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
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • 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
    • 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
    • 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
    • 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings
    • 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
    • G04B43/00—Protecting clockworks by shields or other means against external influences, e.g. magnetic fields
    • G04B43/002—Component shock protection arrangements

Definitions

  • the invention relates to a clockwork resonator mechanism, comprising a structure and an anchoring block from which is suspended at least one inertial element arranged to oscillate according to a first degree of freedom in rotation RZ around a pivot axis extending in a first direction Z, said inertial element being subjected to restoring forces exerted by a flexible pivot comprising a plurality of substantially longitudinal elastic blades, each fixed, at a first end to said anchoring block, and at a second end to said element inertial, each said elastic blade being deformable essentially in an XY plane perpendicular to said first direction Z, the structure carrying this anchoring block by a flexible suspension which allows the mobility of the anchoring block according to five degrees of freedom.
  • the invention also relates to a clock oscillator comprising at least one such resonator mechanism.
  • the invention also relates to a clock movement comprising at least one such oscillator and/or such a resonator mechanism.
  • the invention also relates to a watch comprising such a clock movement, and/or such an oscillator, and/or such a resonator mechanism.
  • the invention relates to the field of watchmaking resonators, and particularly those which include elastic blades acting as return means for the operation of the oscillator, and the shock protection of such mechanisms with flexible guides.
  • a way to achieve this anti-shock was presented in the application CH 715526 on behalf of ETA Manufacture Horlogère Suisse.
  • a flexible structure (called anti-shock) is inserted between the flexible pivot and the plate which allows the movements of the balance according to all degrees of freedom (translations X, Y, Z and rotations X, Y) except the rotation Z of the balance which is authorized by the flexible pivot, and mechanical stops are added to limit the travel of the balance wheel.
  • this anti-shock allows the balance to move to the mechanical stops, while preserving the flexible silicon pivot from breakage.
  • the rigidity of the shock absorber is high enough so that the balance does not touch the mechanical stops.
  • the shock absorber and the flexible pivot are made in a single monolithic silicon piece. This has advantages in terms of simplicity of manufacturing and assembly.
  • silicon is a fragile material, so much so that, during very violent shocks, the part may break because the maximum stress is exceeded.
  • Shock resistance also depends on this torsional rigidity; in fact, during out-of-plane impacts, the stress suffered by the blades quickly reaches levels very high values, which reduces the distance that the part can travel before giving way.
  • Shock absorbers for timepieces come in many variations. However, their main purpose is to protect the fragile pivots of the axis, and not the elastic elements, such as conventionally the spiral spring.
  • the document EP3054357A1 in the name of ETA Manufacture Horlogère Suisse SA describes a watch oscillator comprising a structure and distinct primary resonators, temporally and geometrically phase-shifted, each comprising a mass recalled towards the structure by an elastic return means.
  • This oscillator comprises coupling means for the interaction of the primary resonators, comprising motor means for driving in movement a mobile which comprises drive and guide means arranged to drive and guide a control means articulated with transmission means , each articulated, at a distance from the control means, with a mass of a primary resonator.
  • the primary resonators and the mobile are arranged in such a way that the axes of the joints of any two of the primary resonators and the articulation axis of the control means are never coplanar.
  • the document EP3035127A1 in the name of SWATCH GROUP RESEARCH & DEVELOPMENT Ltd describes a watchmaking oscillator comprising a resonator constituted by a tuning fork which comprises at least two oscillating mobile parts, fixed to a connecting element by flexible elements whose geometry determines a virtual pivot axis of determined position relative to a plate, and around which the respective movable part oscillates, the center of mass of which coincides in the rest position with the respective virtual pivot axis.
  • the flexible elements are made up of crossed elastic blades at a distance from each other in two parallel planes, including the projections of the directions on one of the planes parallel intersect at the level of the virtual pivot axis of the mobile part.
  • New mechanism architectures make it possible to maximize the quality factor of a resonator, through the use of flexible guidance with the use of an anchor escapement with a very small lifting angle, according to application CH01544/16 in the name of ETA Manufacture Horlogère Suisse and its derivatives, the lessons of which can be directly used in the present invention, and whose resonator can be further improved with regard to its sensitivity to shocks, according to certain particular directions. This is therefore to protect the blades from breakage in the event of impact.
  • the anti-shock systems proposed to date for resonators with flexible guides protect the shock blades in certain directions only, but not in all directions, or that they present the defect of allowing the blade to move slightly. embedding of the flexible pivot according to its oscillation rotation, which should be avoided as much as possible.
  • Application CH00518/18 or application EP18168765.8 in the name of ETA Manufacture Horlogère Suisse describes a watch resonator mechanism, comprising a structure carrying, by a flexible suspension, an anchoring block from which is suspended an inertial element oscillating according to a first degree of freedom in rotation RZ, under the action of restoring forces exerted by a flexible pivot comprising first elastic blades each fixed to said inertial element and to said anchoring block, the flexible suspension being arranged to allow a certain mobility of the anchoring block according to all other degrees of freedom that the first degree of freedom in rotation RZ according to which only the inertial element is mobile to avoid any disturbance of its oscillation, and the rigidity of the suspension according to the first degree of freedom in rotation RZ is very much greater than the rigidity of the pivot flexible according to this same first degree of freedom in rotation RZ.
  • the invention aims to optimize the shock protection of such an oscillator, while ensuring the required torsional rigidities of the suspension, in particular for a resonator mechanism according to CH00518/18 or the request EP18168765.8 in the name of ETA Manufacture Horlogère Suisse, or for a similar resonator with flexible guides.
  • a good rotary resonator with flexible guidance which constitutes a flexible pivot and defines a virtual pivot axis, must be both very flexible for oscillation rotation according to a first degree of freedom in rotation RZ, and also very rigid according to the other degrees of freedom (X, Y, Z, RX, RY) so as to avoid parasitic movements of the center of mass of the resonator. Indeed, such parasitic movements can cause walking errors if the orientation of the resonator changes in the gravity field (we speak of a position error).
  • the suspension of the pivot embedding must be very rigid depending on the degree of freedom of the oscillation, so as not to disturb the isochronism of the resonator, and not to dissipate energy via movements due to reaction forces.
  • the invention proposes to produce an improved shock absorber for a flexible guided oscillator, to better manage the torsional rigidities of the suspension, and consequently to limit the out-of-plane movement stroke of the blades of a blade resonator, and therefore to ensure better performance of the system.
  • the invention relates to a blade resonator mechanism according to claim 1.
  • the invention also relates to a clock oscillator comprising at least one such resonator mechanism.
  • the invention also relates to a clock movement comprising at least one such resonator mechanism.
  • the invention also relates to a watch comprising such a clock movement, and/or such a resonator mechanism.
  • the invention relates to a clockwork resonator mechanism, which constitutes a variant of the resonators described in application CH00518/18, or application EP18168765.8 in the name of ETA Manufacture Horlogère Congress, or the request CH 715526 or request EP 3561607 in the name of ETA Manufacture Horlogère Congress, whose characteristics a person skilled in the art will know how to combine with those specific to the present invention.
  • the invention is based on the observation that silicon (or silicon and/or silicon oxide) is the most suitable material for the flexible pivot, but not for the shock absorber. Indeed, in order to fulfill its anti-shock role, the structure must be capable of large deformations with high accumulation of elastic energy. Some metallic materials are more suitable than silicon for this function. For example, NiP material is more suitable than silicon. Indeed, the Young's modulus is 90GPa for NiP compared to 150GPa for Si, and the maximum stress is 1700MPa for NiP compared to 1000MPa for Si. This means that the maximum authorized deformation is three times greater for NiP than for the If.
  • the invention therefore consists of making the pivot in a first material, in particular silicon or equivalent, and of making the anti-shock in a second material, in particular nickel phosphorus NiP or equivalent, this second material having very different physical properties from the first material .
  • This resonator mechanism 100 of clockwork comprises, as visible on the figure 1 , a structure 1 and an anchoring block 30, from which is suspended at least one inertial element 2 which is arranged to oscillate according to a first degree of freedom in rotation RZ around a pivot axis D extending in a first direction Z.
  • This inertial element 2 is subjected to restoring forces exerted by a flexible pivot 200 comprising a plurality of substantially longitudinal elastic blades 3, each fixed, at a first end to the anchoring block 30, and at a second end to the inertial element 2.
  • Each elastic blade 3 is deformable essentially in a plane XY perpendicular to the first direction Z.
  • the resonator mechanism 100 is a composite assembly made from at least two distinct materials, and which comprises, on the one hand, the flexible pivot 200, which is made from a first material characterized by a first Young's modulus E1 and by a first elastic limit Sigma1 and by a first toughness G1, and on the other hand the flexible suspension 300, which is made of a second material characterized by a second Young's modulus E2 and by a second elastic limit Sigma2 and by a second toughness G2.
  • a high G toughness means that the part is able to store more elastic energy before breaking.
  • the value of the second toughness G2 is greater than ten times the value of the first toughness G1. Even more particularly, the value of the second toughness G2 is greater than eighty times the value of the first toughness G1. This is the case when the first material is silicon and/or silicon oxide, and when the second material is NiP, the G2/G1 ratio is close to 100;
  • the Sigma2/E2 ratio is at least twice the Sigma1/E1 ratio.
  • the value of the first Young's modulus E1 is greater than or equal to 1.5 times the value of the second Young's modulus E2.
  • the value of the second elastic limit Sigma2 is greater than or equal to 1.5 times the value of the first elastic limit Sigma1
  • At least one inertial element 2 is integral with the flexible pivot 200.
  • the flexible suspension 300 is integral with the structure 1.
  • the flexible pivot 200 is removable relative to the flexible suspension 300.
  • the flexible suspension 300 comprises gripper elements, in particular jaws 939, to immobilize the flexible pivot 200.
  • these jaws 939 constitute the gripping elements of an elastic gripper 930.
  • Figure 3 shows under the mark 938 the rest position of this clamp.
  • the flexible suspension 300 comprises at least one pocket 933 which is capable of receiving glue to immobilize the flexible pivot 200.
  • the junction between the flexible suspension 300 and the flexible pivot 200 is made on the anchoring block 30, which preferably includes reliefs 309 of a shape complementary to the profile of the elements 939.
  • the clamp 930 is suspended from an intermediate mass 305, which is itself suspended from the structure 1 or from another intermediate mass 303.
  • This elastic assembly has the advantage of minimizing the added mass.
  • the Sigma2/E2 ratio is at least three times the Sigma1/E1 ratio.
  • the first material is silicon and/or silicon oxide.
  • the second material is nickel-phosphorus NiP.
  • the toughness of silicon is almost 100 times lower than that of all nickel alloys.
  • a couple with the first material which is silicon and/or a silicon oxide, and the second material which is nickel-phosphorus NiP, is particularly advantageous for the desired anti-shock application
  • the dissipation (losses) of the NiP is larger than that of silicon, which constitutes an additional advantage.
  • nickel phosphorus NiP can have a sigma elastic limit / Young E modulus ratio which is sufficiently high to meet the conditions of the invention.
  • nickel phosphorus NiP has the major advantage of being able to be shaped precisely with the “LIGA” method (Lithography Galvano-Abformung), with perfect geometry and tight tolerances perfectly compatible with the requirements. watchmakers.
  • the flexible suspension 300 is advantageously, but not limited to, made from a nickel-phosphorus NiP board with a thickness of between 180 and 420 micrometers.
  • FIG. 3 describes the assembly of the flexible pivot 200 with the flexible suspension 300, and shows the assembly area in detail, and also describes the assembly procedure.
  • the assembly is done in three stages: firstly the elastic clamp 930 (in particular in NiP) is moved aside in order to be able to insert the anchoring block 30 (in particular in silicon) in the jaws 939; then the clamp 930 is released so that its jaws 939 grip and block the reliefs 309 of the anchoring block 30; finally, only if necessary, glue is inserted into at least one pocket 933 between the clamp 930 and the anchoring block 30.
  • the elastic clamp 930 in particular in NiP
  • the anchoring block 30 in particular in silicon
  • the 930 elastic clamp is designed so that the clamping force is significant. It is therefore important to ensure that the Hertzian pressure does not exceed the maximum stress at the contact between the jaw 939 and the relief 309 of the silicon anchoring block 30. For this reason, the shape of the jaw 939 matches that of relief 309, so that the difference in radius of curvature is as small as possible. The fact of giving a certain flexibility to the jaw 939 allows it to deform slightly to accommodate possible geometric errors between the clamp 930 and the anchoring block 30.
  • the pocket 933 provided for the glue is made up, on the one hand of at least one wide zone where it is easy to insert the glue, as well as on the other hand at least one narrower zone which helps in the distribution of the glue. glue by capillary action.
  • Using the torsional flexibility of a translation table makes it possible to better manage the torsional rigidities of the suspension. To do this, we orient the blades of the XY tables so that the direction of greatest torsional flexibility targets the axis of rotation of the resonator. Their torsional flexibility is managed by bringing the blades closer to each other.
  • the flexible suspension 300 comprises, advantageously, between the anchoring block 30 and a first intermediate mass 303, which is fixed to the structure 1 directly or via a flexible plate 301 in the first direction Z, a transverse translation table 32 with flexible guidance, and which comprises transverse blades 320 or transverse flexible rods 1320, rectilinear and extending in the second direction X and in symmetry around a transverse axis D2 crossing the pivot axis D .
  • the flexible suspension 300 further comprises, between the anchoring block 30 and a second intermediate mass 305, a longitudinal translation table 31 with flexible guidance, and which comprises longitudinal blades 310 or longitudinal flexible rods, rectilinear and extending in the third direction Y and in symmetry around a longitudinal axis D1 crossing the pivot axis D.
  • the table transverse translation 32 with flexible guidance comprises transverse blades 320 or transverse flexible rods, rectilinear and extending in the second direction X and in symmetry around the transverse axis D2 crossing the pivot axis D.
  • the longitudinal axis D1 crosses the transverse axis D2, and in particular the longitudinal axis D1, the transverse axis D2, and the pivot axis D are concurrent.
  • the longitudinal translation table 31 and the transverse translation table 32 each comprise at least two flexible blades or rods, each blade or rod being characterized by its thickness in the second direction according to the third direction Y or vice versa, by its height according to the first direction Z, and by its length according to the direction in which the blade or rod extends, the length being at least five times greater than the height, the height being at least as great as the thickness, and more particularly at least five times greater than this thickness, and more particularly still at least seven times greater than this thickness.
  • the transverse translation table 32 comprises at least two transverse flexible blades or rods, parallel to each other and of the same length.
  • THE figures 1 And 4 illustrate a variant close to the invention with four parallel transverse blades, and, more particularly, each consisting of two half-blades arranged on two superimposed levels, and extending in the extension of one another in the first direction Z. These half-blades can be either entirely free with respect to each other, or else joined together by gluing or the like, or by growth of SiO 2 in the case of an execution in silicon, or the like.
  • the longitudinal translation table 31, when it exists since it is optional, can obey the same construction principle.
  • FIG 6 illustrates a variant with flexible rods, grouped in two levels of two rods, of substantially square section; another variation has circular flexible rods. The number, arrangement, and section of these blades or rods may vary without departing from the present invention.
  • the blades or transverse rods of the transverse translation table 32 have a first plane of symmetry, which is parallel to the transverse axis D2, and which passes through the pivot axis D.
  • the blades or transverse rods of the transverse translation table 32 have a second plane of symmetry, which is parallel to the transverse axis D2, and orthogonal to the pivot axis D.
  • the blades or transverse rods of the transverse translation table 32 have a third plane of symmetry, which is perpendicular to the transverse axis D2, and parallel to the pivot axis D.
  • the blades or transverse rods of the transverse translation table 32 extend over at least two levels parallel to each other, each level being perpendicular to the pivot axis D.
  • the arrangement of the blades or transverse rods of the transverse translation table 32 is identical on each of the levels.
  • the transverse blades or rectilinear flexible rods 320 are flat blades whose height is at least five times greater than their thickness.
  • transverse blades or rectilinear flexible rods 320 are rods of square or circular section whose height is equal to the thickness.
  • the longitudinal translation table 31 comprises at least two longitudinal flexible blades or rods, parallel to each other and of the same length.
  • the blades or longitudinal rods of the longitudinal translation table 31 have a first plane of symmetry, which is parallel to the longitudinal axis D1, and which passes through the pivot axis D.
  • the blades or longitudinal rods of the longitudinal translation table 31 have a second plane of symmetry, which is parallel to the longitudinal axis D1, and orthogonal to the pivot axis D.
  • the blades or longitudinal rods of the longitudinal translation table 31 have a third plane of symmetry, which is perpendicular to the longitudinal axis D1, and parallel to the pivot axis D.
  • the blades or transverse rods of the longitudinal translation table 31 extend over at least two levels parallel to each other, each level being perpendicular to the pivot axis D.
  • the arrangement of the blades or transverse rods of the longitudinal translation table 31 is identical on each of the levels.
  • the longitudinal blades or rectilinear flexible rods 310 are flat blades whose height is at least five times greater than their thickness.
  • the longitudinal blades or rectilinear flexible rods 310 are rods of square or circular section whose height equals the thickness.
  • the resonator mechanism 100 comprises axial stop means comprising at least a first upper axial stop and a second lower axial stop to limit the translational travel of the inertial element 2 at least in the first direction Z, the means axial stop being arranged to cooperate in stop support with the inertial element 2 for the protection of the longitudinal blades 3 at least against axial shocks in the first direction Z, and the second plane of symmetry is substantially equidistant from the first axial stop 7 and the second axial stop 8.
  • the resonator mechanism 100 comprises a plate fixed on the structure 1 or in one piece with it, comprising at least one flexible blade 302 extending in a plane perpendicular to the pivot axis D and fixed to the first intermediate mass 303, and which is arranged to allow mobility of the first intermediate mass 303 in the first direction Z.
  • the plate 301 comprises at least two such coplanar flexible blades.
  • Such a plate 301 is however optional if the height of the blades of the translation tables XY is low compared to the height of the flexible blades 3, in particular less than a third of the height of the flexible blades 3, and in particular if these translation tables include flexible rods as on the Figure 6 .
  • the technology used for manufacturing makes it possible to obtain two distinct blades in the height of a silicon wafer, which promotes the torsional flexibility of the table without softening it for translation.
  • the resonator mechanism 100 can thus advantageously comprise at least two superimposed elementary assemblies, which each group together a level of the anchoring block 30, and/or a base of the at least one inertial element 2, and of the flexible pivot 200 or the flexible suspension 300 which always form a composite assembly, and/or the first intermediate mass 303, and/or the transverse translation table 32, and/or a breakable element used only during assembly and destroyed before the oscillator is put into service; each elementary assembly can be assembled with at least one other elementary assembly by bonding or the like, by mechanical assembly, or by growth of SiO 2 in the case of an execution in silicon, or the like.
  • such an elementary assembly also comprises at least one level of the second intermediate mass 305 and/or of the longitudinal translation table 31.
  • the invention also relates to a clockwork oscillator mechanism 500 comprising such a clockwork resonator mechanism 100, and an escapement mechanism 400, arranged to cooperate with one another.
  • the invention also relates to a clock movement 1000 comprising at least one such oscillator mechanism 500 and/or at least one resonator mechanism 100.
  • the invention also relates to a watch 2000 comprising at least one such movement 1000 and/or at least one oscillator mechanism 500 and/or at least one such resonator mechanism 100.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)
  • Electric Clocks (AREA)
EP21212441.6A 2021-12-06 2021-12-06 Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif Active EP4191346B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP21212441.6A EP4191346B1 (fr) 2021-12-06 2021-12-06 Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif
US17/812,456 US20230176522A1 (en) 2021-12-06 2022-07-14 Shock protection of a resonator mechanism with rotary flexure bearing
JP2022134701A JP7407250B2 (ja) 2021-12-06 2022-08-26 回転たわみ軸受を有する共振器機構の衝撃保護
CN202211089846.8A CN116224741A (zh) 2021-12-06 2022-09-07 具有旋转柔性轴承的谐振器机构的抗震保护

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21212441.6A EP4191346B1 (fr) 2021-12-06 2021-12-06 Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif

Publications (2)

Publication Number Publication Date
EP4191346A1 EP4191346A1 (fr) 2023-06-07
EP4191346B1 true EP4191346B1 (fr) 2024-06-26

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EP21212441.6A Active EP4191346B1 (fr) 2021-12-06 2021-12-06 Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif

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US (1) US20230176522A1 (ja)
EP (1) EP4191346B1 (ja)
JP (1) JP7407250B2 (ja)
CN (1) CN116224741A (ja)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH15446A (de) 1897-10-08 1898-06-15 Paul Suess Actiengesellschaft Buchförmiger Behälter mit Einrichtung zum Sammeln und Ordnen von Postkarten oder dergleichen
EP3035127B1 (fr) * 2014-12-18 2017-08-23 The Swatch Group Research and Development Ltd. Oscillateur d'horlogerie à diapason
CH710692B1 (fr) 2015-02-03 2021-09-15 Eta Sa Mft Horlogere Suisse Mécanisme oscillateur d'horlogerie.
EP3438762A3 (fr) * 2017-07-28 2019-03-13 The Swatch Group Research and Development Ltd Oscillateur d'horlogerie a guidages flexibles a grande course angulaire
EP3557333B1 (fr) * 2018-04-16 2020-11-04 Patek Philippe SA Genève Procédé de fabrication d'un ressort moteur d'horlogerie
CH714922A2 (fr) * 2018-04-23 2019-10-31 Eta Sa Mft Horlogere Suisse Protection antichoc d'un mécanisme résonateur d'horlogerie à guidage flexible rotatif.
EP3561607B1 (fr) 2018-04-23 2022-03-16 ETA SA Manufacture Horlogère Suisse Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif
CH715526A2 (fr) 2018-11-08 2020-05-15 Eta Sa Mft Horlogere Suisse Protection antichoc d'un mécanisme résonateur à guidage flexible rotatif.

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JP7407250B2 (ja) 2023-12-28
JP2023084084A (ja) 2023-06-16
US20230176522A1 (en) 2023-06-08
EP4191346A1 (fr) 2023-06-07
CN116224741A (zh) 2023-06-06

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