EP3293584A1 - Oszillatormechanismus für uhr - Google Patents

Oszillatormechanismus für uhr Download PDF

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Publication number
EP3293584A1
EP3293584A1 EP17192071.3A EP17192071A EP3293584A1 EP 3293584 A1 EP3293584 A1 EP 3293584A1 EP 17192071 A EP17192071 A EP 17192071A EP 3293584 A1 EP3293584 A1 EP 3293584A1
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EP
European Patent Office
Prior art keywords
resonators
clock oscillator
mobile
oscillator
control means
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.)
Granted
Application number
EP17192071.3A
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English (en)
French (fr)
Other versions
EP3293584B1 (de
Inventor
Pascal Winkler
Jean-Luc Helfer
Gianni Di Domenico
Thierry Conus
Jean-Jacques Born
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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Publication of EP3293584A1 publication Critical patent/EP3293584A1/de
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Classifications

    • 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
    • G04B29/00—Frameworks
    • 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
    • G04B17/08—Oscillators with coil springs stretched and unstretched axially
    • 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
    • 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
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • 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
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • 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
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • 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 clock oscillator comprising a structure and / or a frame, and a plurality of distinct resonators, temporally and geometrically out of phase, and each comprising at least one inertial mass biased towards said structure or towards said frame by an elastic return means
  • said clock oscillator comprising coupling means arranged to allow the interaction of said resonators, said coupling means comprising a mobile subject to a torque or a motor force and which comprises driving and guiding means arranged to drive and guide a single control means articulated around a first control axis with a plurality of transmission means each articulated around a second axis of articulation, away from said control means, with a said inertial mass of a said resonator, said resonators and said mobile being arranged in such a way that said second hinge pins any two of said resonators and said first control axis of said control means are never coplanar.
  • the invention also relates to a watch movement comprising at least one such watch oscillator.
  • the invention relates to a watch comprising at least one such movement.
  • the invention relates to the field of watch oscillators for watches, in particular for mechanical movements.
  • the exhaust must be robust, shock-resistant, and constructed to prevent entrapment (overturning).
  • the Swiss lever escapement has a low fuel efficiency of around 30%. This low yield is due to the fact that the movements of the exhaust are jerky, and that several parts are transmitted their movement via inclined planes that rub against each other.
  • the documents WO2015104692 and WO2015104693 in the name of EPFL each describe a mechanical isotropic harmonic oscillator which comprises at least one link with two degrees of freedom supporting a mass in orbit relative to a fixed base having springs having linear and isotropic restoring force properties, the mass having a tilting motion.
  • the oscillator may be used in a time measuring device, for example a watch.
  • the document CH451021A on behalf of EBAUCHES SA describes a symmetrical oscillator for bending for a timepiece, in particular for an electric timepiece, comprising a U-shaped part, the two flexible branches of which constitute two vibrating blades, as in a tuning fork. It has two rigid arms, serving as a counterweight, each connected to one of the flexible branches, in the vicinity of the end thereof, the arrangement being such that for each of the two symmetrical parts of this oscillator, the center The instantaneous rotation of the oscillator coincides with the center of gravity, so that the frequency of the oscillator hardly changes with its changes of position in the gravitational field.
  • the present invention aims to provide a high efficiency exhaust system.
  • the invention consists in the development of an architecture for continuous interactions, without saccades, between resonator and escape wheel. To do this, we must concede the use of at least a second resonator out of phase with respect to a first resonator.
  • the invention relates to a clock oscillator according to claim 1.
  • the invention also relates to a watch movement comprising at least one such watch oscillator.
  • the invention relates to a watch comprising at least one such movement.
  • the invention relates to a mechanical watch 200 provided with balanced resonators, out of phase and maintained continuously.
  • the invention relates to a watch oscillator 1 comprising a structure 2 or / and a frame 4, and a plurality of primary resonators 10 and distinct.
  • These primary resonators 10 are phase-shifted temporally and geometrically. They each comprise at least one inertial mass 5, which is recalled to the structure 2, or the frame 4, by an elastic return means 6. It is meant by “distinct resonators” the fact that each primary resonator 10 has its own inertial mass 5 and its own elastic return means 6, especially a spring.
  • this clock oscillator 1 comprises coupling means 11, which are arranged to allow the interaction of the primary resonators 10.
  • the mobile 13 is subjected to a force or / and a motor torque.
  • These coupling means 11 comprise motor means 12, arranged to drive such a mobile 13. More particularly, motor means 12 are arranged to drive this mobile 13.
  • This mobile 13 comprises driving and guiding means 14, which are arranged to drive and guide, preferably captively, a mechanical control means.
  • This control means 15 is articulated around a first control axis with a plurality of transmission means 16, each hinged about a second axis of articulation, away from the control means 15, with an inertial mass 5 of a primary resonator 10.
  • the primary resonators 10 oscillate about axes parallel to each other.
  • the invention sets out to compensate the forces to the recesses, both in translation and in rotation, unlike the known prior art, which performs only compensation in translation.
  • Rotational compensation is an important feature of the invention, it allows the oscillator to vibrate longer, and to have a better quality factor. In addition, the impact sensitivity is lower.
  • the primary resonators 10 and the mobile 13 are arranged in such a way that the second axes of articulation of any two of the primary resonators 10, and the first control axis of the control means 15, are never coplanar. In other words, the projections of these axes in a common perpendicular plane are never aligned. It is understood that the axes of articulation may, in some embodiments, be virtual pivot axes.
  • the mobile 13 is subjected to a rotational movement; more particularly, the motor means 12 are arranged to drive the mobile 13 in a rotational movement about an axis of rotation A.
  • the driving and guiding means 14 are constituted by a groove 140 in which a finger 150 slides which comprises the control means 15.
  • this groove 140 is substantially radial with respect to the axis of rotation A of the mobile 13.
  • the mobile 13 replaces a conventional escape wheel, and is preferably downstream of a finishing train powered by a barrel or the like.
  • the transmission means 16 may in particular be made in the form of connecting rods 160, each having a first articulation 161 with the control means 15, and a second articulation 162 with the inertial mass 5 considered.
  • the first hinge 161 and the second hinge 162 together define a rod direction.
  • all the connecting rod directions are in pairs, at any time, an angle other than zero or ⁇ . Otherwise formulated, the vector product of the two directions of rods is different from zero.
  • the transmission means 16 are non-collinear connecting rods 160.
  • the mobile 13, subjected to a driving torque, and the coupling means 11 have an interaction geometry, which allows to essentially transmit tangential forces to these rods 160.
  • Elementary resonators are termed resonators that together constitute a primary resonator: they are mounted in a tuning fork so that the reactions and errors cancel each other out.
  • a number n of elementary resonators together constitute a primary resonator they are out of phase with each other by 2 ⁇ / n.
  • the figure 1 illustrates a general case of two elementary resonators 10A and 10B mass-spring type oscillating linearly and in different directions, and whose masses 5A and 5B are articulated to connecting rods 16A and 16B, which cooperate together in an articulated manner with a finger 150 , which constitutes the control means 15, which runs through a groove 140 of a wheel constituting the mobile 13, the motor means being represented in FIG. figure 4 which shows a detail at the articulation of the connecting rods on the control means 15.
  • the primary resonators 10 are rotary resonators.
  • at least one mobile of the primary resonator has a large amplitude of oscillation, preferably greater than 180 ° and advantageously greater than 270 °.
  • Such a rotary resonator is distinguished from an angular resonator with recessed cantilever blades known from the prior art.
  • FR 630831 where the oscillation of a blade is limited to a small angle, of the order of 30 °.
  • the figure 2 illustrates such an example, where the primary resonators 10A, 10B, are balance-spiral assemblies, where the spirals 6A, 6B are attached at their outer turn to the structure 2, and at their inner turn to the pendulums 5A, 5B, which are articulated with ends 162A, 162B, connecting rods 16A, 16B, arranged in a manner similar to those of FIG. figure 1 .
  • the oscillator 1 is arranged so that the forces and the reaction torques of all the primary resonators 10 on the support 2 (or on the frame 4 if they are all fixed on such a frame) cancel each other out.
  • the forces cancel out because the center of mass does not move, or very little, when the axis of rotation passes through the center of mass.
  • the center of mass is substantially coincident with the center of rotation, that is to say with a positional deviation of only a few micrometers or tens of micrometers.
  • the pairs cancel each other because each component in rotation is compensated by another component in inverse rotation.
  • the coupling between the resonators can be done via a flexible recess as in a tuning fork or via the connecting rods 160, or, more generally, the transmission means 16.
  • the coupling of the primary resonators 10 with respect to each other is then performed by a flexible embedding of each of the primary resonators 10 with respect to the common structure 2 or to the frame 4.
  • the resultant of the forces and reaction torques of the primary resonators 10 with respect to the common structure 2 or to the frame 4, to which they are attached, is zero, thanks to the phase-shifted arrangement of the n primary resonators. 10, in particular rotary ones.
  • the primary rotary resonators 10 are arranged so that their centers of mass remain in a fixed position, at least during the normal oscillations of these primary resonators 10.
  • the clock oscillator 1 preferably comprises stop means to limit their stroke in case of shock or the like.
  • these primary resonators 10 have at least one substantially identical resonance mode, they are arranged to vibrate in a phase shift between them of the value 2 ⁇ / n, where n is their number, and they are arranged according to a symmetry in the space such that the resultant forces and torques applied by the primary resonators 10 on the structure 2, or on a frame 4 which supports them, is zero.
  • substantially identical resonance mode is meant that these primary resonators 10 have substantially the same amplitude, substantially the same inertia, and substantially the same natural frequency. The most important is this phase shift of 2 ⁇ / n.
  • the primary resonators 10 are even in number, and they constitute pairs of pairs in which the inertial masses 5 are in phase-shifting of ⁇ relative to one another. .
  • At least one of the primary resonators 10 consists of a plurality of n elementary resonators 810.
  • These elementary resonators 810 each comprise at least one elementary mass carried by a flexible elementary elastic blade, constituting an elastic return means, and which is arranged to work in bending, and which is embedded in an elementary cross.
  • These elementary resonators 810 have at least one substantially identical resonance mode, and are arranged to vibrate in a phase shift between them of the value 2 ⁇ / n, where n is the number of elementary resonators 810. They are arranged in a symmetry in the space, such that the resultant forces and torques applied by the elementary resonators 810 on the elementary cross is zero.
  • This elementary crosspiece is fixed to the fixed support 2 by an elementary main elastic connection, whose rigidity is greater than the rigidity of each elastic flexible elemental blade, and whose damping is greater than the damping of each elementary flexible blade.
  • the resonators elementary elements 810 are arranged in space so that the resultant of their operating errors due to gravitation is zero.
  • At least one of the primary resonators 10 consists of a pair of such elementary resonators 810.
  • the elementary inertial masses are in motion phase shifted by ⁇ relative to each other.
  • this pair consists of identical elementary resonators 810, which are geometrically opposed and phase to each other.
  • each primary resonator 10 consists of such a pair of elementary resonators 810.
  • each primary resonator 10A, 10B thus forms, by the combination of two elementary resonators 8101, 8102, respectively 8103, 8104, an isochronous oscillator mechanism of tuning fork type called horned goat horns.
  • a cross 40A, respectively 40B is fixed to the fixed support 2 by a main elastic connection 3A, respectively 3B, whose rigidity is greater than the rigidity of each resilient flexible blade 61 A, 62A, respectively 61B, 62B. And the damping of this main elastic connection is greater than that of each flexible blade.
  • each primary resonator 10 is balanced for itself, in translation and in rotation.
  • the fixed support 2 forms a monolithic assembly with these two primary monolithic structures.
  • planar structure is meant that this monolithic structure is a right prism, realized by raising a two-dimensional contour, along a direction of elongation, and delimited by two end planes parallel to each other and perpendicular. to this direction of elongation of the prism.
  • the monolithic structure has a constant thickness defined by the spacing of these two end planes, and therefore has a single level, in certain variants certain zones, in particular flexible blades of the monolithic structure, may only occupy part of this thickness.
  • the monolithic structure is produced by a growth method, of the "MEMS", "LIGA” or similar type.
  • the monolithic structure is produced by cutting a plate, for example by electro-erosion wire and / or sinking.
  • the cross member 40A carries a pair of masses 5, marked 51A and 52A, respectively 51B and 52B, mounted symmetrically on either side of the fixed support 2 and the main elastic connection 3A, respectively 3B .
  • Each of these masses is mounted oscillatingly and biased by an elastic flexible blade 61 A, 62A, respectively 61B, 62B, which is a spiral, or a spiral assembly.
  • These spirals are each linked directly or indirectly to a mass at their inner turn, and attached to the cross 40A, respectively 40B, by its outer turn.
  • Each mass pivots around a virtual pivot axis of position determined relative to the cross 40A, respectively 40B.
  • Each virtual pivot axis is, in the rest position of the isochronous oscillator mechanism 1, coinciding with the center of mass, of the respective mass.
  • the masses extend substantially parallel to each other in the rest position, in a transverse direction.
  • each spiral has a section or variable curvature along its development.
  • the variant of the figure 5 is a structure similar to that of the figure 3 , where each primary resonator 10A, 10B forms, by the combination of two elementary resonators 8101, 8102, respectively 8103, 8104, an isochronous oscillator mechanism of so-called tuning fork type in H.
  • the resilient flexible blades 6: 61A, 62A, respectively 61 B, 62B, are no longer constituted by spirals, but by straight and short blades.
  • the term “short blade” refers to a blade whose length is less than the smallest value between four times its height or thirty times its thickness, this short blade characteristic making it possible to limit the movements of the center of mass concerned.
  • These short blades are here arranged on either side of a cross 40A, respectively 40B, with which it forms the horizontal bar of an H whose masses form the vertical bars. Due to the symmetry and the alignment, the longitudinal arrangement of the elastic flexible blades makes it possible to compensate the direction of greater displacement of the centers of mass, which move symmetrically with respect to the plane of symmetry.
  • Each primary resonator 10A, 10B thus rendered isochronous by one of these particular combinations of elementary resonators, advantageously comprises rotational abutments, and / or translational limit stops in the longitudinal and transverse directions, and / or abutments. limitation in translation in a direction perpendicular to the two preceding.
  • These stroke limiting means can be integrated, be part of a one-piece construction, and / or be reported.
  • the masses comprise, advantageously, stop means arranged to cooperate with complementary abutment means that the sleepers 40A, 40B comprise, to limit the displacement of the resilient flexible blades relative to these sleepers, in case of shocks or similar accelerations .
  • the figure 5 also illustrates an advantageous variant where the transmission means 16A, 16B, are resilient flexible blades. It is then possible to make a monolithic assembly comprising the structure 2, the primary resonators 10 as described above, in particular complete, and these resilient flexible blades, and the finger 150.
  • the Figures 6 and 7 illustrate variants where the connecting rods are beams having collars at both ends in place of the hubs.
  • the figure 6 illustrates a case of coupling of two primary resonators, the figure 7 of three such resonators.
  • the transmission means 16 thus comprise at least one monolithic connecting rod arranged to cooperate both with the control means 15 and with at least two inertial masses 5 of as many primary resonators 10, and comprise at least one flexible neck at the level of each articulation zone.
  • FIGS. 1, 2 , 3 and 5 illustrate a clock oscillator 1 comprising two primary resonators 10.
  • the watch oscillator 1 comprises at least three primary resonators 10.
  • the figure 8 illustrates a clock oscillator 1 comprising three primary resonators 10. This figure shows the application of the coupling of the figure 7 to the inertial masses 5A, 5B, 5C, of the three primary resonators 10A, 10B, 10C.
  • the figure 9 illustrates a clock oscillator 1 having four resonators. These four resonators may be four primary resonators 10. They may also be four elementary resonators, constituting two by two primary resonators: one composed of the elementary resonators 10A and 10C, phase shifted by ⁇ , the other of the elementary resonators 10B and 10D , also out of phase with ⁇ .
  • each resonator taken alone has a reaction to the embedding, and it is the juxtaposition and the judicious combination of the "n" resonators that compensates for all the reactions.
  • the figures 10 , 12, and 13 illustrate a variant where at least one elastic return means 6 also constitutes a rotary guide, which avoids the friction inherent in the use of pivots.
  • the figure 10 shows a transmission means 16 constituted by a flexible blade, in the configuration of the figure 9 .
  • This figure also shows angular stops: 71, 72, 710, 720, 76 on the mass 5, the respective complementary abutment surfaces 73, 74, 730, 740, 77 at the frame 4 on which is attached a short flexible blade 6, and an anti-shock abutment surface 75 on the mass 5, arranged to cooperate with a complementary surface 750 at the frame 4.
  • These integrated shock are particularly advantageous, and require no adjustment.
  • the mobile 13 is subjected to a rotational movement; more particularly, the motor means 12 are arranged to drive the mobile 13 in a rotational movement, and the mobile 13 and the drive and guide means 14 are arranged to apply by means of command a substantially tangential force relative to the rotation of the mobile 13.
  • the figure 11 illustrates a variant where the mobile 13 comprises a resilient structure 130 deformable, forming a rigid radially rigid guide tangentially, this deformable structure 130 comprises a housing 140 for cooperating with the finger 150 of the control means 15 at the main joint.
  • the elastic return means 6 of the primary resonators 10 comprise flexible blades
  • the primary resonators 10 and / or the common structure 2, and / or the frame 4 comprise radial stops and / or or angular and / or axial arranged to limit the deformations of the flexible blades and to avoid breaks in case of shocks or too high engine torque.
  • the watch oscillator 1 comprises a monolithic structure which groups together a common structure 4 towards which the inertial masses 5 are recalled by their elastic return means 6, the control means 15 and its articulations with the transmission means 16, and the means transmission 16 with their joints to the inertial masses 5.
  • the desired phase shifts are perfectly assured, the cancellation of reactions also.
  • Such monolithic structures allow the removal of traditional pivots, by implementing flexible blades that have a dual function: the pivoting guide constituting a virtual pivot, and the elastic return.
  • this monolithic structure further comprises the stops.
  • the orientation of the elastic return means 6 of the primary resonators 10 is optimized so that the operating errors due to the gravity vanish between the primary resonators 10.
  • the elastic return means 6 of the primary resonators 10 are virtual cross-blade pivots.
  • the primary resonators 10 are isochronous.
  • At least the elastic means that comprises the watch oscillator 1 according to the invention are thermally compensated.
  • An embodiment of micro-machinable material makes it possible to provide such compensation.
  • the invention also relates to a watch movement 100 comprising at least one watch oscillator 1.
  • the invention also relates to a watch 200 comprising at least one such movement 100.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Electric Clocks (AREA)
EP17192071.3A 2015-02-03 2016-01-21 Oszillatormechanismus für uhr Active EP3293584B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP15153657.0A EP3054357A1 (de) 2015-02-03 2015-02-03 Oszillatormechanismus für Uhr
EP16152268.5A EP3054358B1 (de) 2015-02-03 2016-01-21 Oszillatormechanismus für uhr

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP16152268.5A Division EP3054358B1 (de) 2015-02-03 2016-01-21 Oszillatormechanismus für uhr
EP16152268.5A Division-Into EP3054358B1 (de) 2015-02-03 2016-01-21 Oszillatormechanismus für uhr

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EP3293584A1 true EP3293584A1 (de) 2018-03-14
EP3293584B1 EP3293584B1 (de) 2022-03-30

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EP15153657.0A Withdrawn EP3054357A1 (de) 2015-02-03 2015-02-03 Oszillatormechanismus für Uhr
EP17192071.3A Active EP3293584B1 (de) 2015-02-03 2016-01-21 Oszillatormechanismus für uhr
EP16152268.5A Active EP3054358B1 (de) 2015-02-03 2016-01-21 Oszillatormechanismus für uhr

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US (1) US9465363B2 (de)
EP (3) EP3054357A1 (de)
JP (1) JP6114845B2 (de)
CN (2) CN105843026B (de)
CH (1) CH710692B1 (de)
RU (1) RU2692817C2 (de)

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EP3095010B1 (de) 2014-01-13 2024-09-25 Ecole Polytechnique Fédérale de Lausanne (EPFL) Isotroper harmonischer oszillator und zugehörige zeitbasis ohne hemmung oder mit vereinfachter hemmung
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EP3035126B1 (de) * 2014-12-18 2017-12-13 The Swatch Group Research and Development Ltd. Resonator einer Uhr mit sich kreuzenden Blättern
EP3054357A1 (de) * 2015-02-03 2016-08-10 ETA SA Manufacture Horlogère Suisse Oszillatormechanismus für Uhr
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US12265359B2 (en) * 2016-07-06 2025-04-01 Ecole Polytechnique Federale De Lausanne (Epfl) General 2 degree of freedom isotropic harmonic oscillator and associated time base without escapement or with simplified escapement
CH713056A2 (fr) * 2016-10-18 2018-04-30 Eta Sa Mft Horlogere Suisse Mouvement mécanique d'horlogerie avec résonateur à deux degrés de liberté avec mécanisme d'entretien par galet roulant sur une piste.
EP3312682B1 (de) * 2016-10-18 2019-02-20 ETA SA Manufacture Horlogère Suisse Qualitativ hochwertiger resonator für mechanische armbanduhr
CH713069A2 (fr) * 2016-10-25 2018-04-30 Eta Sa Mft Horlogere Suisse Montre mécanique avec résonateur rotatif isochrone, insensible aux positions.
EP3324246B1 (de) * 2016-11-16 2019-11-06 The Swatch Group Research and Development Ltd Schutz eines plattenresonator-mechanismus gegen axiale stosseinwirkungen
FR3059792B1 (fr) * 2016-12-01 2019-05-24 Lvmh Swiss Manufactures Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif
EP3336613B1 (de) * 2016-12-16 2020-03-11 Association Suisse pour la Recherche Horlogère Resonator für uhr, der zwei pendellager umfasst, die so angeordnet sind, dass sie auf derselben ebene schwingen können
CH713288A1 (fr) * 2016-12-23 2018-06-29 Sa De La Manufacture Dhorlogerie Audemars Piguet & Cie Composant monolithique flexible pour pièce d'horlogerie.
WO2018215284A1 (fr) 2017-05-24 2018-11-29 Sa De La Manufacture D'horlogerie Audemars Piguet & Cie Dispositif de régulation pour pièce d'horlogerie avec oscillateur harmonique isotrope ayant des masses rotatives et une force de rappel commune
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EP3561604B1 (de) * 2018-04-25 2020-10-28 The Swatch Group Research and Development Ltd Uhrreglermechanismus mit über gelenke verbundenen resonatoren
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EP3719584A1 (de) * 2019-04-02 2020-10-07 Ecole Polytechnique Fédérale de Lausanne (EPFL) Oszillatorsystem mit zwei freiheitsgraden
EP3739394A1 (de) 2019-05-16 2020-11-18 Ecole Polytechnique Fédérale de Lausanne (EPFL) Kurbelanordnung zum antreiben eines mechanischen oszillators
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EP3919988A1 (de) * 2020-06-04 2021-12-08 Montres Breguet S.A. Gelenkmechanismus eines uhrwerks mit flexibler führung
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CH710692A2 (fr) 2016-08-15
JP2016142736A (ja) 2016-08-08
EP3293584B1 (de) 2022-03-30
EP3054357A1 (de) 2016-08-10
RU2692817C2 (ru) 2019-06-28
US20160223989A1 (en) 2016-08-04
RU2016103417A (ru) 2017-08-07
US9465363B2 (en) 2016-10-11
CN205539955U (zh) 2016-08-31
JP6114845B2 (ja) 2017-04-12
CH710692B1 (fr) 2021-09-15
CN105843026A (zh) 2016-08-10
RU2016103417A3 (de) 2019-05-22
EP3054358A1 (de) 2016-08-10
EP3054358B1 (de) 2019-08-28

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