EP3561609B1 - Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung - Google Patents

Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung Download PDF

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Publication number
EP3561609B1
EP3561609B1 EP18168765.8A EP18168765A EP3561609B1 EP 3561609 B1 EP3561609 B1 EP 3561609B1 EP 18168765 A EP18168765 A EP 18168765A EP 3561609 B1 EP3561609 B1 EP 3561609B1
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EP
European Patent Office
Prior art keywords
freedom
degree
flexible
suspension
rotational
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EP18168765.8A
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English (en)
French (fr)
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EP3561609A1 (de
Inventor
Pascal Winkler
Jean-Luc Helfer
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ETA SA Manufacture Horlogere Suisse
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ETA SA Manufacture Horlogere Suisse
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Application filed by ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP18168765.8A priority Critical patent/EP3561609B1/de
Priority to CH5182018A priority patent/CH714922A2/fr
Priority to EP18205260.5A priority patent/EP3561607B1/de
Priority to JP2019056018A priority patent/JP6763991B2/ja
Priority to US16/392,057 priority patent/US11175630B2/en
Priority to CN201910328567.4A priority patent/CN110389519B/zh
Priority to JP2019195910A priority patent/JP6828117B2/ja
Publication of EP3561609A1 publication Critical patent/EP3561609A1/de
Priority to CN201911081303.XA priority patent/CN111158230B/zh
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Publication of EP3561609B1 publication Critical patent/EP3561609B1/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
    • 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
    • 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • 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
    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C3/00—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means
    • G04C3/04—Electromechanical clocks or watches independent of other time-pieces and in which the movement is maintained by electric means wherein movement is regulated by a balance

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 about 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 first elastic blades each fixed, at a first end to said anchoring block, and at a second end to said inertial element, each said elastic blade being deformable essentially in an XY plane perpendicular to said first direction Z, said resonator mechanism comprising axial stop means comprising at least one first axial stop and/or a second axial stop to limit the travel in translation of said inertial element at least in said first direction Z, said axial abutment means being arranged to cooperate in support of bu ted with said inertial element for the protection of said first blades at least against axial shocks in said first direction Z.
  • the invention also relates to a clock oscillator comprising at least one such resonator mechanism.
  • the invention also relates to a timepiece 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 clockwork resonators, and more particularly those which comprise elastic blades acting as return means for the operation of the oscillator.
  • Shock resistance is a delicate point for most clock oscillators, and in particular for resonators with crossed blades. In fact, during out-of-plane shocks, the stress undergone by the blades quickly reaches very high values, which correspondingly reduces the travel that the part can travel before yielding.
  • Shock absorbers for timepieces come in many variants. However, their main purpose is to protect the fragile pivots of the axle, and not the elastic elements, such as conventionally the spiral spring.
  • the document EP3054357A1 on behalf of ETA Manufacture Horlogère Suisse SA describes a horological oscillator comprising a structure and separate primary resonators, temporally and geometrically out of phase, each comprising a mass returned to the structure by an elastic return means.
  • This oscillator comprises coupling means for the interaction of the primary resonators, comprising motor means for driving a mobile in motion 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 articulations of any two of the primary resonators and the axis of articulation of the control means are never coplanar.
  • the document EP3035127A1 on behalf of SWATCH GROUP RESEARCH & DEVELOPMENT Ltd describes a clockwork oscillator comprising a resonator consisting of 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 mobile part oscillates, the center of mass of which coincides in the rest position with the respective virtual pivot axis.
  • the flexible elements consist of elastic blades crossed at a distance from each other in two parallel planes, the projections of the directions of which on one of the parallel planes intersect at the level of the pivot axis. virtual of the mobile part.
  • New architectures of mechanisms make it possible to maximize the quality factor of a resonator, by the use of a flexible guide with the use of a lever escapement with a very small angle of lift, according to the application CH713150 in the name of ETA Manufacture Horlogère Suisse and its derivatives, the teachings of which can be directly used in the present invention, and whose resonator can be further improved as regards its sensitivity to shocks, in certain particular directions. It is therefore a question of protecting the blades rupture in the event of impact.
  • the invention proposes to limit the out-of-plane displacement travel of the reeds of a reed 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 idea here is to suspend a flexible pivot 200 of a clockwork resonator 100 from a flexible suspension system according to 5 degrees of freedom but stiff according to the single degree of freedom in which said pivot works and which is that of the oscillation of at least one inertial element 2, which this resonator 100 comprises. stops, against which the inertial element of the resonator comes to rest in the event of an impact.
  • the present description illustrates more particularly the case of a mechanical watch movement, provided with a resonator 100 with rotating flexible guide, which constitutes a flexible pivot 200 defining a virtual pivot axis D in a first direction Z.
  • This flexible pivot 200 is made in this particular case on the basis of flexible strips 3, which are, according to the invention, protected from breaking in the event of an impact by an anti-shock system comprising a flexible suspension, which connects the anchoring of the flexible pivot 200 to a structure 1, in particular the movement plate, in combination with a set of stops which are arranged to limit the travel of the inertial element of the resonator via support surfaces.
  • this anti-shock system is flexible according to 5 degrees of freedom, and stiff according to the degree of freedom corresponding to the oscillation of the resonator, here the first direction Z.
  • the stops allow the inertial element 2 to move freely according to the degree of freedom of oscillation of the resonator, but limit its travel for the first direction Z, and advantageously also for the other 4 degrees of freedom.
  • the invention thus relates to a clockwork resonator mechanism 100, comprising a structure 1 and an anchoring block 30, from which is suspended at least one inertial element 2.
  • Each inertial element 2 is arranged to oscillate according to a first degree of freedom in rotation RZ around a pivot axis D extending along a first direction Z.
  • the center of inertia resulting from the set of inertial elements 2 is aligned on the pivot axis D.
  • the inertial element 2 is subjected to restoring forces exerted by a flexible pivot 200 comprising a plurality of first elastic blades 3, each fixed, at a first end to the anchor block 30, and at a second end to the element inertial 2.
  • Each elastic blade 3 is essentially deformable in an XY plane perpendicular to the first direction Z.
  • the resonator mechanism 100 comprises axial stop means, which comprise at least a first axial stop 7 and/or a second axial stop 8 to limit the travel in translation of the inertial element 2, at least according to the first direction Z.
  • axial stop means comprise at least a first axial stop 7 and/or a second axial stop 8 to limit the travel in translation of the inertial element 2, at least according to the first direction Z.
  • These axial abutment means are arranged to cooperate in abutment support with the inertial element 2 for the protection of the first blades 3, at least against axial shocks in the first direction Z.
  • the anchor block 30 is suspended from the structure 1 by a flexible suspension 300, which is arranged to allow the mobility of the anchor block 30 according to five flexible degrees of freedom of the suspension.
  • the anchor block 30 is suspended from the structure 1 by the flexible suspension 300, in a way that allows it a certain mobility according to all the degrees of freedom other than the first degree of freedom in rotation RZ according to which only the inertial element 2 must be mobile, to avoid any disturbance of its oscillation, which is essential for the invention.
  • the anchor block 30 carries the flexible pivot 200 from which the inertial element 2 is suspended, and the stiffness of the suspension 300 according to the first degree of freedom in rotation RZ must be very much greater than the stiffness of the flexible pivot 200 according to this same first degree of freedom in rotation RZ.
  • the matrix below expresses the relative conditions between the stiffness of the suspension and that of the pivot, for each degree of freedom: Degree of freedom i Suspension Condition Pivot
  • the essential degree of freedom of the pivot RZ C RZ susp > N.C RZ pivot
  • the five flexible degrees of freedom of the suspension X K x suspension ⁇ 1/M
  • K X pivot Y K Y susp ⁇ 1/M.
  • K Y swivel Z K Z suspension ⁇ 1/M.
  • K Z swivel X-ray C RX suspended ⁇ 1/M.
  • the value N is preferably chosen greater than or equal to 10, and in particular greater than or equal to 100 or even 1000.
  • the value M is preferably chosen greater than or equal to 10, and in particular greater than or equal to 50.
  • the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least 10 times stiffer than is the flexible pivot 200 according to the first degree of freedom in rotation RZ.
  • the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least 10 times less stiff than the flexible pivot 200 is according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX, said third degree of rotational freedom RY.
  • the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least 100 times less stiff than it is according to the first degree of freedom in rotation RZ.
  • the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least 100 times stiffer than is the flexible pivot 200 according to the first degree of freedom in rotation RZ.
  • the stiffness according to the stiffest degree of freedom of the suspension is at least 100 times greater than the stiffness of the flexible pivot of the resonator.
  • the flexible suspension 300 is, according to the first degree of freedom in rotation RZ, at least 1000 times stiffer than is the flexible pivot 200 according to the first degree of freedom in rotation RZ.
  • the flexible suspension 300 is, according to the first degree of freedom in translation, the second degree of freedom in translation, the third degree of freedom in translation, the second degree of freedom in rotation RX, the third degree of freedom in rotation RY, at least 50 times less stiff than is the flexible pivot 200 according to said first degree of freedom in translation, said second degree of freedom in translation, said third degree of freedom in translation, said second degree of freedom in rotation RX , said third degree of rotational freedom RY.
  • the flexible suspension 300 comprises a first elastic connection, which is arranged to allow its mobility according to the first degree of freedom in translation along the first direction Z, and/or a second elastic connection arranged to allow its mobility according to the second degree of freedom in translation in the second direction X, and/or a third elastic connection arranged to allow its mobility in the third degree of freedom in translation in the third direction Y, and/or a fourth elastic connection arranged to allow its mobility in rotation according to the second degree of freedom in rotation RX, and/or a fifth elastic connection arranged to allow its mobility in rotation according to the third degree of freedom in rotation RY.
  • the axial abutment means are further arranged to cooperate in abutment support with the inertial element 2 for the protection of the first blades 3 in the second direction X, in the third direction Y, in the second degree of freedom in rotation RX, and according to the third degree of freedom in rotation RY.
  • These axial abutment means comprise first bearing surfaces 79, 89, radial, which are arranged to cooperate with first complementary bearing surfaces 279, 289, which the inertial element 2 comprises, and second bearing surfaces 78, 88, which are arranged to cooperate with second complementary bearing surfaces 278, 288, which the inertial element 2 comprises. More particularly, these abutment means are carried by the structure 1. name of Swatch Group Research & Development Ltd can be used in the case of the present invention.
  • the abutment means comprise a first axial abutment 7 and a second axial abutment 8 which are bearing cylinders, arranged on either side of the inertial element 2 along the axis of oscillation of the resonator parallel to the first direction Z.
  • the first complementary bearing surfaces 279, 289, here are bores of the inertial element 2, which extend along the first direction Z, on either side of the element inertial 2.
  • the second bearing surfaces 78, 88 are substantially planar, and arranged to cooperate with an edge of one of the cylinders within reach during a movement according to the degree of freedom RX or RY.
  • the figure 6 illustrates in broken lines two angular stop configurations in RX and in RY, respectively by contacts at points 7RX and 7RY between the first stop 7 and the inertial mass 2.
  • the flexibility of the elastic means, which the flexible suspension comprises, is, according to the five flexible degrees of freedom of the suspension, such that the frequencies of the natural modes of vibration of the flexible suspension are, according to these five degrees of freedom , at least 10 times higher than the main oscillation frequency of the resonator during the oscillation of the inertial mass 2. More particularly they are at least 50 times higher than the main oscillation frequency of the resonator during the oscillation of the inertial mass 2.
  • this main oscillation frequency of the resonator is high, greater than 10 Hz, in particular close to 20 Hz.
  • a plate which comprises at least two parallel and coplanar flexible blades, ensures the first elastic connection of mobility according to the first degree of freedom in translation according to the first direction Z, the fourth elastic connection of mobility in rotation according to the second degree of freedom in rotation RX, and the fifth elastic connection of mobility in rotation according to the third degree of freedom in rotation RY: it controls the flexibility according to the degrees of freedom Z, RX and RY.
  • the figure 4 , 7, and 9 illustrate such a plate 301 with its two flexible blades 302.
  • the mobility according to the second degree of freedom in translation along the second direction X is ensured by a set of flexible blades comprising at least two parallel and non-coplanar flexible blades
  • the mobility according to the third degree of freedom in translation in the third direction Y is ensured by a set of flexible blades comprising at least two parallel and non-coplanar flexible blades.
  • the mobility according to the second degree of freedom in translation according to the second direction X, and according to the second degree of freedom in rotation RX is ensured by a single flexible blade deformable essentially in an XY plane perpendicular to the first direction Z and arranged to tolerate a twist of +/-10° with respect to its longitudinal direction.
  • the mobility according to the third degree of freedom in translation according to the third direction Y, and according to the third degree of freedom in rotation RY is ensured by a single flexible blade deformable essentially in an XY plane perpendicular to the first direction Z and arranged to tolerate a twist of +/-10° with respect to its longitudinal direction.
  • FIG 4 , 7, and 8 illustrate a particular non-limiting embodiment, where a plate 301, comprising two coplanar parallel blades 302, is fixed to the structure 1, and allows mobility along Z of a first intermediate mass 303.
  • the latter carries two non-coplanar parallel flexible blades 304 , providing mobility in X to a second intermediate mass 305, which carries, through two non-coplanar parallel flexible strips 306, the anchoring block 30, allowing it mobility in Y.
  • Mobility along RX and RY are limited, and are authorized only by the slight possible twisting of the blades 302, 304 and 306.
  • the elastic blades 3 of the elastic pivot 200 are straight, and the directions in which the elastic blades 3 extend are, in projection on a plane perpendicular to this pivot axis D, crossed at the level of the pivot axis D. More particularly, these elastic blades are arranged according to the teachings of applications CH712068 in the name of ETA Manufacture Horlogère Suisse and CH710524 in the name of Swatch Group Research & Development Ltd.
  • the pivot is of the large angular travel type, according to application CH714024 in the name of Swatch Group Research & Development Ltd.
  • the mechanical interaction between the axial stop means and surfaces of the inertial element 2 is supplemented by a magnetic interaction between these axial stop means and these surfaces.
  • the inertial element 2 comprises at least one flyweight 29, adjustable in position and/or orientation for adjusting the adjustment of the positioning of its center of mass and its inertia.
  • the mass MA of the anchor block 30, like the mass of any intermediate block, such as the first intermediate mass 303 or the second intermediate mass 305, which is interposed in the flexible suspension between the anchor block 30 and the structure 1, is less than one tenth of the mass M0 of inertial element 2.
  • 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 each other.
  • the inertial element 2 here comprises a pin 28 for this purpose.
  • the invention also relates to a clock movement 1000 comprising at least one such oscillating mechanism 500, and/or at least one such mechanism resonator 100.
  • This movement 1000 carries, on structure 1, an energy source 1100 such as a barrel, powering a gear train 1200 producing the display and coupled with the escapement mechanism 400.
  • this movement is fitted with a Swiss lever escapement.
  • this movement is equipped with a rubbing rest escapement.
  • this movement is fitted with a magnetic rest escapement.
  • the figure 9 illustrates a variant in which the guiding in translation in X, as in Y, has more than two parallel blades, in order to increase its stiffness without increasing the maximum stress that one would have by thickening the two blades of the figure 4 , 7, and 8 .
  • the flexible pivot is made of silicon thermally compensated by a layer of silicon dioxide.
  • the flexible suspension 300 and the anchor block 30 constitute a one-piece assembly.
  • the flexible suspension 300 and the flexible pivot 200 constitute a one-piece assembly.
  • the escapement mechanism 400 comprises at least one of its components in silicon, or similar, to minimize its inertia, and in particular an openwork component, such as the escape wheel of the figure 1 .
  • the inertial element is a latticework structure at least locally openworked in order to minimize its mass/inertia ratio.
  • the invention also relates to a watch 2000 comprising at least one such movement 1000, and/or at least one such oscillator mechanism 500, and/or at least one such resonator mechanism 100.
  • the invention makes it possible to decouple the useful degree of freedom of the flexible pivot from the degrees of freedom of the suspension.
  • the suspension protects the pivot from breaking during shocks for five degrees of freedom, without interfering in the stiffness of the useful pivot according to the degree of freedom that it defines.
  • the suspension would allow the embedding of the blades to move, and this would result in a significant reduction in the quality factor of the resonator. If the suspension were infinitely stiff, the result would be breakage of the pivot blades when accidental shocks.
  • the invention makes it possible to protect the flexible pivot from breaking without altering the qualities of the resonator.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)
  • Vibration Prevention Devices (AREA)

Claims (22)

  1. Resonatormechanismus (100) für die Uhrmacherei, umfassend eine Struktur (1) und einen Ankerblock (30), an dem wenigstens ein Trägheitselement (2) aufgehängt ist, das angeordnet ist, um gemäß einem ersten Drehfreiheitsgrad RZ um eine Drehachse (D) zu schwingen, die sich gemäß einer ersten Richtung Z erstreckt, wobei das Trägheitselement (2) Rückzugsbeanspruchungen ausgesetzt ist, die von einem biegsamen Drehzapfen (200) ausgeübt werden, umfassend eine Vielzahl von ersten elastischen Lamellen (3), die jeweils an einem ersten Ende am Ankerblock (30) und an einem zweiten Ende am Trägheitselement (2) befestigt sind, wobei jede elastische Lamelle (3) im Wesentlichen in einer Ebene XY senkrecht zu der ersten Richtung Z verformbar ist, wobei der Resonatormechanismus (100) axiale Anschlagmittel umfasst, umfassend wenigstens einen ersten axialen Anschlag (7) und/oder einen zweiten axialen Anschlag (8), um den Translationsweg des Trägheitselements (2) wenigstens gemäß der ersten Richtung Z zu begrenzen, wobei die axialen Anschlagmittel angeordnet sind, um durch anschlagendes Anliegen mit dem Trägheitselement (2) für den Schutz der ersten Lamellen (3) wenigstens gegen Axialstöße gemäß der ersten Richtung Z zusammenzuwirken, wobei der Ankerblock (30) an der Struktur (1) durch eine biegsame Aufhängung (300) aufgehängt ist, die angeordnet ist, um die Beweglichkeit des Ankerblocks (30) gemäß fünf biegsamen Freiheitsgraden der Aufhängung zu erlauben, die ein erster Translationsfreiheitsgrad gemäß der ersten Richtung Z, ein zweiter Translationsfreiheitsgrad gemäß einer zweiten Richtung X, orthogonal zu der ersten Richtung Z, ein dritter Translationsfreiheitsgrad gemäß einer dritten Richtung Y, orthogonal zu der zweiten Richtung X und zu der ersten Richtung Z, ein zweiter Drehfreiheitsgrad RX um eine Achse, die sich gemäß der zweiten Richtung X erstreckt, und ein dritter Drehfreiheitsgrad RY um eine Achse, die sich gemäß der dritten Richtung Y erstreckt, sind, wobei die biegsame Aufhängung (300), gemäß dem ersten Drehfreiheitsgrad RZ, wenigstens 10 Mal steifer ist als es der biegsame Drehzapfen (200) gemäß dem ersten Drehfreiheitsgrad RZ ist, und wobei weiter die biegsame Aufhängung (300) gemäß dem ersten Drehfreiheitsgrad, dem zweiten Translationsfreiheitsgrad, dem dritten Translationsfreiheitsgrad, dem zweiten Drehfreiheitsgrad RX, dem dritten Drehfreiheitsgrad RY wenigstens 10 Mal weniger steif ist als es der biegsame Drehzapfen (200) jeweils gemäß dem ersten Translationsfreiheitsgrad, dem zweiten Translationsfreiheitsgrad, dem dritten Translationsfreiheitsgrad, dem zweiten Drehfreiheitsgrad RX und dem dritten Drehfreiheitsgrad RY ist.
  2. Resonatormechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass die biegsame Aufhängung (300) gemäß dem ersten Drehfreiheitsgrad RZ wenigstens 100 Mal steifer ist als es der biegsame Drehzapfen (200) gemäß dem ersten Drehfreiheitsgrad RZ ist.
  3. Resonatormechanismus (100) nach Anspruch 2, dadurch gekennzeichnet, dass die biegsame Aufhängung (300) gemäß dem ersten Drehfreiheitsgrad RZ wenigstens 1000 Mal steifer ist als es der biegsame Drehzapfen (200) gemäß dem ersten Drehfreiheitsgrad RZ ist.
  4. Resonatormechanismus (100) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die biegsame Aufhängung (300) gemäß dem ersten Translationsfreiheitsgrad, dem zweiten Translationsfreiheitsgrad, dem dritten Translationsfreiheitsgrad, dem zweiten Drehfreiheitsgrad RX, dem dritten Drehfreiheitsgrad RY wenigstens 50 Mal weniger steif ist als es der biegsame Drehzapfen (200) jeweils gemäß dem ersten Translationsfreiheitsgrad, dem zweiten Translationsfreiheitsgrad, dem dritten Translationsfreiheitsgrad, dem zweiten Drehfreiheitsgrad RX und dem dritten Drehfreiheitsgrad RY ist.
  5. Resonatormechanismus (100) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die biegsame Aufhängung (300) eine erste elastische Verbindung umfasst, die angeordnet ist, um ihre Beweglichkeit gemäß dem ersten Translationsfreiheitsgrad gemäß der ersten Richtung Z zu erlauben, und/oder eine zweite elastische Verbindung, die angeordnet ist, um ihre Beweglichkeit gemäß dem zweiten Translationsfreiheitsgrad gemäß der zweiten Richtung X zu erlauben, und/oder eine dritte elastische Verbindung, die angeordnet ist, um ihre Beweglichkeit gemäß dem dritten Translationsfreiheitsgrad gemäß der dritten Richtung Y zu erlauben, und/oder eine vierte elastische Verbindung, die angeordnet ist, um ihre Drehbeweglichkeit gemäß dem zweiten Drehfreiheitsgrad RX zu erlauben, und/oder eine fünfte elastische Verbindung, die angeordnet ist, um ihre Drehbeweglichkeit gemäß dem dritten Drehfreiheitsgrad RY zu erlauben.
  6. Resonatormechanismus (100) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die axialen Anschlagmittel weiter angeordnet sind, um durch anschlagendes Anliegen mit dem Trägheitselement (2) für den Schutz der ersten Lamellen (3) gemäß der zweiten Richtung X, gemäß der dritten Richtung Y, gemäß dem zweiten Drehfreiheitsgrad RX und gemäß dem dritten Drehfreiheitsgrad RY zusammenzuwirken, und erste radiale Auflageflächen (79; 89) umfassen, die angeordnet sind, um mit komplementären ersten Auflageflächen (279; 289) zusammenzuwirken, welche das Trägheitselement (2) umfasst, und zweite Auflageflächen (78; 88), die angeordnet sind, um mit komplementären zweiten Auflageflächen (278; 288) zusammenzuwirken, welche das Trägheitselement (2) umfasst.
  7. Resonatormechanismus (100) nach Anspruch 6, dadurch gekennzeichnet, dass die Anschlagmittel einen ersten axialen Anschlag (7) und einen zweiten axialen Anschlag (8) umfassen, die Zylinder mit Lauffläche sind, die beidseits des Trägheitselements (2) gemäß der Schwingungsachse des Resonators parallel zur ersten Richtung Z angeordnet sind, und dadurch, dass die komplementären ersten Auflageflächen (279; 289) Ausreibungen des Trägheitselements (2) sind, die sich gemäß der ersten Richtung Z erstrecken, und dadurch, dass die zweiten Auflageflächen (78; 88) im Wesentlichen eben und angeordnet sind, um mit einer Kante eines der Zylinder mit Lauffläche zusammenzuwirken.
  8. Resonatormechanismus (100) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Anschlagmittel von der Struktur (1) getragen werden.
  9. Resonatormechanismus (100) nach Anspruch 8, dadurch gekennzeichnet, dass die Anschlagmittel einen ersten axialen Anschlag (7) und einen zweiten axialen Anschlag (8) umfassen, die Zylinder mit Lauffläche sind, die beidseits des Trägheitselements (2) gemäß der Schwingungsachse des Resonators parallel zur ersten Richtung Z angeordnet sind, und dadurch, dass die komplementären ersten Auflageflächen (279; 289) Ausreibungen des Trägheitselements (2) sind, die sich gemäß der ersten Richtung Z erstrecken, und dadurch, dass die zweiten Auflageflächen (78; 88) im Wesentlichen eben und angeordnet sind, um mit einer Kante eines der Zylinder mit Lauffläche zusammenzuwirken.
  10. Resonatormechanismus (100) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Biegsamkeit von elastischen Mitteln, welche die biegsame Aufhängung umfasst, gemäß den fünf biegsamen Freiheitsgraden der Aufhängung, so ist, dass die Frequenzen der eigenen Schwingungsmodi der biegsamen Aufhängung, gemäß diesen fünf Freiheitsgraden, wenigstens 10 Mal höher sind als die Hauptschwingungsfrequenz des Resonators bei der Schwingung der Trägheitsmasse (2).
  11. Resonatormechanismus (100) nach Anspruch 5 oder einem der Ansprüche 6 bis 10, wenn sie von Anspruch 5 abhängig sind, dadurch gekennzeichnet, dass eine Platte, die wenigstens zwei biegsame Lamellen umfasst, die parallel und komplanar sind, die erste elastische Verbindung zur Beweglichkeit gemäß dem ersten Translationsfreiheitsgrad gemäß der ersten Richtung Z, die vierte elastische Verbindung zur Drehbeweglichkeit gemäß dem zweiten Drehfreiheitsgrad RX und die fünfte elastische Verbindung zur Drehbeweglichkeit gemäß dem dritten Drehfreiheitsgrad RY sicherstellt.
  12. Resonatormechanismus (100) nach Anspruch 5 oder einem der Ansprüche 6 bis 10, wenn sie von Anspruch 5 abhängig sind, dadurch gekennzeichnet, dass die Beweglichkeit gemäß dem zweiten Translationsfreiheitsgrad gemäß der zweiten Richtung X sichergestellt wird durch einen Satz biegsamer Lamellen, der wenigstens zwei biegsame Lamellen umfasst, die parallel und nicht komplanar sind, und/oder dadurch, dass die Beweglichkeit gemäß dem dritten Translationsfreiheitsgrad gemäß der dritten Richtung Y sichergestellt wird durch einen Satz biegsamer Lamellen, der wenigstens zwei biegsame Lamellen umfasst, die parallel und nicht komplanar sind.
  13. Resonatormechanismus (100) nach Anspruch 5 oder einem der Ansprüche 6 bis 10, wenn sie von Anspruch 5 abhängig sind, dadurch gekennzeichnet, dass die Beweglichkeit gemäß dem zweiten Translationsfreiheitsgrad gemäß der zweiten Richtung X und gemäß dem zweiten Drehfreiheitsgrad RX sichergestellt wird durch eine einzige biegsame Lamelle, die im Wesentlichen in einer Ebene XY senkrecht zu der ersten Richtung Z verformbar und angeordnet ist, um eine Verdrehung von +/- 10° in Bezug auf ihre Längsrichtung zu tolerieren.
  14. Resonatormechanismus (100) nach Anspruch 5 oder einem der Ansprüche 6 bis 10, wenn sie von Anspruch 5 abhängig sind, dadurch gekennzeichnet, dass die Beweglichkeit gemäß dem dritten Translationsfreiheitsgrad gemäß der dritten Richtung Y und gemäß dem dritten Drehfreiheitsgrad RY sichergestellt wird durch eine einzige biegsame Lamelle, die im Wesentlichen in einer Ebene XY senkrecht zu der ersten Richtung Z verformbar und angeordnet ist, um eine Verdrehung von +/- 10° in Bezug auf ihre Längsrichtung zu tolerieren.
  15. Resonatormechanismus (100) für die Uhrmacherei nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass die elastischen Lamellen (3) gerade sind, und dadurch, dass die Richtungen, gemäß welchen sich die elastischen Lamellen (3) erstrecken, in Projektion auf eine Ebene senkrecht zur Drehachse (D), auf Höhe der Drehachse (D) gekreuzt sind.
  16. Resonatormechanismus (100) für die Uhrmacherei nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, dass die mechanische Interaktion zwischen den axialen Anschlagmitteln und den Oberflächen des wenigstens einen Trägheitselements (2) ergänzt wird durch eine magnetische Interaktion zwischen den axialen Anschlagmitteln und den Oberflächen des wenigstens einen Trägheitselements (2).
  17. Resonatormechanismus (100) für die Uhrmacherei nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, dass das Trägheitselement (2) wenigstens ein Gewichtchen umfasst, das in Position und/oder Ausrichtung für die Passung der Positionierung seines Trägheitsmittelpunkts verstellbar ist.
  18. Resonatormechanismus (100) für die Uhrmacherei nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, dass die Masse MA des Ankerblocks (30), wie die Masse jedes Zwischenblocks, der in der biegsamen Aufhängung zwischen dem Ankerblock (30) und der Struktur (1) eingefügt ist, kleiner ist als das Zehntel der Masse M0 des Trägheitselements (2).
  19. Oszillatormechanismus (500) für die Uhrmacherei, umfassend einen Resonatormechanismus (100) für die Uhrmacherei nach einem der Ansprüche 1 bis 18 und einen Hemmungsmechanismus (400), die angeordnet sind, um miteinander zusammenzuwirken.
  20. Werk für die Uhrmacherei (1000), umfassend wenigstens einen Oszillatormechanismus (500) nach Anspruch 19.
  21. Werk für die Uhrmacherei (1000), umfassend wenigstens einen Resonatormechanismus (100) nach einem der Ansprüche 1 bis 18.
  22. Uhr (2000), umfassend wenigstens ein Werk (1000) nach Anspruch 20 oder 21 und/oder wenigstens einen Oszillatormechanismus (500) nach Anspruch 19 und/oder wenigstens einen Resonatormechanismus (100) nach einem der Ansprüche 1 bis 18.
EP18168765.8A 2018-04-23 2018-04-23 Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung Active EP3561609B1 (de)

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EP18168765.8A EP3561609B1 (de) 2018-04-23 2018-04-23 Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung
CH5182018A CH714922A2 (fr) 2018-04-23 2018-04-23 Protection antichoc d'un mécanisme résonateur d'horlogerie à guidage flexible rotatif.
EP18205260.5A EP3561607B1 (de) 2018-04-23 2018-11-08 Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung
JP2019056018A JP6763991B2 (ja) 2018-04-23 2019-03-25 可撓性回転ベアリングを用いた振動子機構のための耐衝撃保護
US16/392,057 US11175630B2 (en) 2018-04-23 2019-04-23 Anti shock protection for a resonator mechanism with rotary flexure bearing
CN201910328567.4A CN110389519B (zh) 2018-04-23 2019-04-23 钟表谐振器机构、钟表振荡器机构、钟表机芯和手表
JP2019195910A JP6828117B2 (ja) 2018-04-23 2019-10-29 回転式の撓み支持体を備えた共振機構のための衝撃に対する保護
CN201911081303.XA CN111158230B (zh) 2018-04-23 2019-11-07 用于具有旋转柔性轴承的谐振器机构的抗震保护

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EP3824353B1 (de) * 2018-07-16 2023-11-29 Patek Philippe SA Genève Schwerkraftunempfindlicher biegeschwenkoszillator
EP3839651B1 (de) 2019-12-19 2024-05-01 Patek Philippe SA Genève Mechanischer oszillator einer uhr mit flexibler führung
EP3971655A1 (de) * 2020-09-18 2022-03-23 ETA SA Manufacture Horlogère Suisse Stossdämpfungsschutz mit anschlag eines resonatormechanismus mit flexibler drehführung
EP4016193A1 (de) * 2020-12-18 2022-06-22 Omega SA Resonatormechanismus eines uhrwerks mit flexibler führung, die mit mitteln zur einstellung der steifigkeit ausgestattet ist
EP4191346B1 (de) * 2021-12-06 2024-06-26 The Swatch Group Research and Development Ltd Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung

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US20190324401A1 (en) 2019-10-24
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CN110389519A (zh) 2019-10-29
EP3561609A1 (de) 2019-10-30
JP6763991B2 (ja) 2020-09-30
JP2019191159A (ja) 2019-10-31
CH714922A2 (fr) 2019-10-31
CN110389519B (zh) 2021-09-03

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