EP3254158B1 - Isochroner resonator für uhr - Google Patents

Isochroner resonator für uhr Download PDF

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Publication number
EP3254158B1
EP3254158B1 EP16701499.2A EP16701499A EP3254158B1 EP 3254158 B1 EP3254158 B1 EP 3254158B1 EP 16701499 A EP16701499 A EP 16701499A EP 3254158 B1 EP3254158 B1 EP 3254158B1
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EP
European Patent Office
Prior art keywords
primary
oscillator mechanism
crosspiece
isochronous
resonators
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.)
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Application number
EP16701499.2A
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English (en)
French (fr)
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EP3254158A1 (de
Inventor
Pascal Winkler
Jean-Luc Helfer
Gianni Di Domenico
Thierry Conus
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ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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Publication date
Priority claimed from EP15153656.2A external-priority patent/EP3054356B1/de
Application filed by ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Publication of EP3254158A1 publication Critical patent/EP3254158A1/de
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Publication of EP3254158B1 publication Critical patent/EP3254158B1/de
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    • 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
    • G04C3/08—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 mechanical oscillator other than a pendulum or balance, e.g. by a tuning fork, e.g. electrostatically
    • 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
    • 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
    • G04B15/00—Escapements
    • G04B15/02—Escapements permanently in contact with the regulating mechanism
    • 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
    • G04B15/06—Free 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
    • G04B17/06—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
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/066—Manufacture of the spiral spring
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/10—Oscillators with torsion strips or springs acting in the same manner as torsion strips, e.g. weight oscillating in a horizontal plane
    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/04—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is limited

Definitions

  • the invention relates to an isochronous clockwork oscillator mechanism, comprising a fixed support which carries a crosspiece carrying a plurality of N primary resonators each comprising at least one mass carried by a flexible rotating guide fixed to said crosspiece.
  • the invention also relates to a timepiece movement comprising at least one such isochronous oscillator mechanism.
  • the invention also relates to a watch comprising at least one such movement.
  • the invention relates to the field of clockwork oscillating and regulating mechanisms, in particular for mechanical movements.
  • the isochronism of the movement must be optimal in all positions in space, which implies the design of movements able to compensate for the effects of gravitation on their constituents.
  • oscillators comprising several primary resonators comprising flexible branches, arranged relative to each other so as to average their errors.
  • a first type of oscillator with coupled primary resonators is known in the form of a U-shaped tuning fork, each branch of which is formed by a primary resonator; however, such a system is very sensitive to variations in position in space.
  • the patent CH 451021 in the name of Ebauches SA thus describes a symmetrical U-shaped oscillator whose two flexible branches vibrate in tuning fork mode, each being connected to a rigid arm forming a counterweight, and each primary resonator thus constituted is arranged so that the instantaneous center of rotation coincides with the center of gravity, so that the frequency of the oscillator hardly varies when the position changes in the center of gravity.
  • the transition to a U-shaped architecture with extended branches proves to be better than the U-shape of the prior art.
  • the instantaneous center of rotation moves permanently during the oscillation of each primary resonator.
  • the patent CH 46203 also in the name of Ebauches SA is a variant of the previous one, comprising a counting device transforming the oscillating movements of one of the two resonators into rotary movements of a counting wheel, this counting device being attached to one of these rigid arms, so that that the counting device is not very sensitive to accelerations and in particular to shocks.
  • the patent GB 1293159 in the name of SEIKO develops a theory based on the influence on the running regularity of the derivative of the displacement of the center of mass with respect to the angle of rotation, and seeks a displacement along a straight line of the center of mass of each primary resonator, to optimize the influence on walking.
  • the center of mass is positioned at two thirds of the blade in flexion used in this system, to theoretically cancel the effect on walking in vertical positions.
  • the center of mass moves a lot, and such a system remains sensitive to shocks.
  • this theory is based on a geometric approximation, because in reality the deformation of the flexible blade is no longer really an arc of a circle, and the presumed rectilinear displacement of the center of mass is not verified.
  • the document FR 1605076 A in the name of Institut Straumann describes a mechanical oscillator with a torsion bar constituting the elastic element.
  • This bar carries at its ends masses of the same moment of inertia with respect to the axis of the bar which has a median symmetry, so that the oscillations of one half of the bar are transmitted to the other half, the ends oscillating in phase opposition.
  • the invention proposes to jointly solve the problem of isochronism and that of obtaining the best possible quality factor. It is a question, in a way, of combining the respective advantages specific to the known mechanisms using as a resonator, or else a balance-spring assembly relatively insensitive to the differences in position in space in its developments and its most advanced assemblies but whose quality factor is strongly limited by the pivotings and the various losses, or else a tuning fork with parallel blades which, freeing itself from the pivotings, has a better quality factor than a balance-spring but is very sensitive to the position in the space.
  • the invention relates to an isochronous clockwork oscillator mechanism according to claim 1.
  • the invention also relates to a timepiece movement comprising at least one such isochronous oscillator mechanism.
  • the invention also relates to a watch comprising at least one such movement.
  • the invention proposes to produce a resonator mechanism with the least possible loss, and which is the least chronometrically sensitive to its orientation in the gravity field.
  • the invention seeks to reduce losses, in particular due to friction of pivots, and to displacements of the recess.
  • the inventive approach consists in eliminating the traditional pivots, while minimizing the displacements of the center of mass and the reactions of the support.
  • a mechanical resonator necessarily comprises at least one elastic element and one inertial element.
  • This elastic element is then advantageously higher, thicker and more rigid than a usual elastic element such as a spiral spring or the like, which leads to favoring the use of flexible blades.
  • the search for a high quality factor encourages the implementation of a tuning fork type structure.
  • the inventive step consists in producing an isochronous resonator of the tuning fork type, with a plurality of primary resonators arranged according to a geometry in symmetry with respect to an axis, and together constituting a tuning fork.
  • the invention endeavors to favor the least possible displacement of the center of mass of each primary resonator, which offers, again, the advantage of very good insensitivity to shocks.
  • the invention proposes the construction of a structure comprising symmetries compensating for all the forces brought to the level of the fixing of the oscillator; to this end, it is advantageous to unfold the U known from the prior art, to form a substantially H-shaped structure.
  • the invention is more particularly described below, in a non-limiting way, in the preferred form of a tuning fork with two primary resonators symmetrical with respect to a plane of symmetry, which constitutes an advantageous particular case in because of its simplicity. But the invention is applicable to any number N of primary resonators: three, four, or more, provided that the symmetry of their relative arrangement and their relative time phase shift make it possible to compensate for the effects of the reaction torques on embedding.
  • the invention relates to a clockwork isochronous oscillator mechanism 1, of the tuning fork type, comprising a fixed support 2 which carries a crosspiece 4 carrying a plurality of N primary resonators 10.
  • Each primary resonator 10 comprises at least one mass 5 carried by a rotating flexible guide 20 fixed to the crosspiece 4.
  • These primary resonators 10 constitute the equivalent of the arms of a conventional forked tuning fork, and the crosspiece 4 the equivalent of the common part of the tuning fork from which these arms protrude.
  • each primary resonator 10 has a center of mass CM which is located, at rest, on the virtual pivot axis APV of the flexible rotary guide 20 that this primary resonator 10 comprises.
  • each primary resonator 10 is arranged to oscillate according to a rotational movement around the virtual pivot axis APV.
  • the N primary resonators 10 are arranged according to a rotational symmetry of order N around a main axis AP which is parallel to all the virtual pivot axes APV which are mutually parallel.
  • each rotary flexible guide 20 is, in projection on a plane perpendicular to the main axis AP, symmetrical with respect to a plane of symmetry PS passing through the virtual pivot axis APV of the rotary flexible guide 20 considered.
  • each plane of symmetry PS passes through the main axis AP.
  • FIG. 24 illustrates an example of an oscillator 1 comprising four identical primary resonators 10 mounted in complete symmetry relative to each other.
  • each rotary flexible guide 20 is arranged to cause a restoring torque proportional to the angle of rotation of the mass 5, or masses 5 if there are several of them, with respect to the virtual pivot axis. APV of the rotating flexible guide 20 considered.
  • rotating flexible guides allows the center of mass CM of each primary resonator 10 to be maintained on the virtual pivot axis APV of the rotating flexible guide 20 considered, or in its immediate vicinity, for example during a strong acceleration or from a shock.
  • the rotating primary resonators 10 surround the crosspiece 4, and have at least one identical resonance mode, and are arranged to vibrate according to a phase shift between them of the value 2 ⁇ /N. Their arrangement of symmetry in space is such that the resultant of the forces and torques applied by the primary resonators 10 on the crosspiece 4 is zero.
  • Each rotating flexible guide 20 constitutes an elastic return means, arranged to work in flexion, and defines a substantially immobile virtual pivot axis APV.
  • all the primary resonators 10 are identical to each other.
  • the crosspiece 4 is fixed to the fixed support 2 by a main elastic connection 3, the rigidity of which is greater than the rigidity of each rotary flexible guide 20.
  • This characteristic ensures coupling between the primary resonators 10.
  • the rigidity of this main elastic connection 3 is greater than the total of the rigidities of all the flexible rotary guides 20 that the isochronous oscillator mechanism 1 comprises.
  • each primary resonator 10 is arranged to oscillate in a plane around a neutral axis AN.
  • the damping of the main elastic link 3 is greater than the damping of each rotary flexible guide 20, and, more particularly, the damping of the main elastic link 3 is greater than the total of the dampings of all the guides rotating hoses 20 that comprise the primary resonators 10.
  • the oscillator 1 comprises three primary resonators 10 mounted in a star, each with a neutral axis inclined with respect to the radial coming from the main axis AP.
  • all the neutral axes AN are angularly offset by the value 2 ⁇ /N.
  • all the neutral axes AN are mutually parallel or coincident.
  • each flexible guide 20 is symmetrical with respect to the neutral axis AN of the primary resonator 10 to which it belongs.
  • the primary resonators 10 are even in number or two in number.
  • the flexible guide 20 comprises at least one elastic flexible blade 6, and its virtual pivot axis APV is in the middle of the elastic flexible blade 6, that is to say halfway between the recesses of this flexible blade 6 in the crosspiece 4 and in the at least one mass 5.
  • the flexible guide 20 comprises at least crossed blades, in the same plane as visible on the figures 23 to 25 , or in projection as visible on the figure 26 .
  • the flexible guide 20 comprises at least one collar with a tapered section, as seen on the picture 3 .
  • the primary resonators 10 are an even number or two in number, and each flexible guide 20 comprises at least one spiral winding around the virtual pivot axis APV which is located on the neutral axis AN of the primary resonator 10 to which it belongs. More particularly so as to ensure operating symmetry, the hairsprings of these primary resonators 10 are arranged in a mirror arrangement two by two.
  • the flexible guide 20 is made of micro-machinable material, or of silicon or/and of silicon oxide, or of quartz, or of DLC, in particular in the form of a one-piece component, while particularly when the flexible guide 20 is substantially planar.
  • This one-piece component can also comprise a support for fixing the mass 5 or the masses 5, which are more particularly made of a material with a density superior.
  • This one-piece component can also be one-piece with the crosspiece 4, or even with its main elastic connection 3, or even with the fixed support 2.
  • each primary resonator 10 comprises thermal compensation means, at least at the level of the flexible guide 20.
  • each mass 5 is designed so that the center of mass CM remains invariant during temperature changes. .
  • thermal compensation means comprise at least one component made of elinvar, or else of silicon and silicon oxide.
  • At least one primary resonator 10 comprises swing-limiting means arranged to cooperate in the event of impact in abutment support with complementary swing-limiting means, which the structure 2 or/and the crosspiece comprises. 4.
  • a mass 5 comprises a circulating finger, during the oscillation of the primary resonator 10, in an oblong groove of the fixed support 2, or vice versa.
  • each primary resonator 10 is coupled to each other, at least intermittently, by an escapement wheel.
  • each primary resonator 10 carries, at the level of a mass 5, an arm whose distal end is arranged to cooperate with the toothing of the escape wheel.
  • the primary resonators 10 are arranged to each oscillate at a frequency between 1 Hz and 100 Hz.
  • THE figures 1 to 17 illustrate examples with two primary resonators
  • the figure 19 illustrates an example with four primary resonators.
  • the primary resonators 10 are arranged therein in space so that the resultant of their path errors due to gravitation is zero.
  • the primary resonators 10 are rotary, which makes the isochronous oscillator mechanism 1 not very sensitive to gravitation.
  • each primary resonator 10 forms a rotary resonator, the center of mass of which is located at the place whose translations are minimal during the rotation, and which it is sought to render zero in normal operation. This is done in order to minimize the displacements of the center of mass in the field of gravity or under the effect of shocks, and, consequently, to improve the chronometry of the system.
  • the main elastic connection 3 between the crosspiece 4 and the fixed support 2 is preferably constituted by an elastic blade, it practically does not move when the isochronous oscillator mechanism 1 oscillates in tuning fork mode. Indeed, the branches of the tuning fork constituted by the primary resonators 10 exchange the energy of the movement through the crosspiece 4, but the movements of the crosspiece 4 are minute.
  • the direction in which the centers of mass CM of the primary resonators 10 are mobile is called the longitudinal direction X.
  • a transverse direction Y is substantially perpendicular to this longitudinal direction X.
  • a direction Z completes the direct trihedron.
  • the crosspiece 4 is straight and extends in the longitudinal direction X.
  • all or part of the isochronous oscillator mechanism 1 is arranged symmetrically with respect to a plane of symmetry PSY which extends parallel to the transverse direction Y.
  • the main elastic connection 3 extends along the main direction Y, as seen in the examples of figures 1 to 17 .
  • the primary direction which connects the point of embedding on the crosspiece 4 of an elastic flexible strip 6 to the center of mass CM of the corresponding primary resonator 10, when the latter is at rest, is parallel to the longitudinal direction X.
  • FIG. 1 illustrates a simplified embodiment of an isochronous oscillator mechanism 1 for watchmaking similar to the invention, of the tuning fork type, comprising a fixed support 2 which carries, via a main elastic connection 3, made in the form of a flexible blade, a crosspiece 4 carrying two plane primary resonators 10A, 10B, symmetrical with respect to a plane of symmetry PSY, and each comprising a mass, respectively 5A, 5B, carried by an elastic flexible strip, respectively 6A, 6B, constituting the flexible guide 20 of the primary resonator 10 concerned, arranged to work in bending and embedded in the crosspiece 4, symmetrically with respect to the plane of symmetry PSY.
  • the primary directions of the various primary resonators 10 which constitute this isochronous oscillator mechanism 1 are parallel to the longitudinal direction X, or coincident.
  • the flexible guides 20, in particular the elastic flexible blades 6, are arranged so that the displacement of each center of mass CM of a given primary resonator 10 is minimal in the transverse direction Y where it is not provided for compensation, and so that the displacements of the different centers of mass CM of the given primary resonators 10 are compensated with respect to each other in the longitudinal direction X: if, as in the case of the figures, the isochronous oscillator mechanism 1 comprises two primary resonators 10A and 10B arranged back to back on either side of the crosspiece 4, their respective centers of mass CMA and CMB move essentially in the longitudinal direction X, but with displacements of the same value but in direction opposites.
  • the advantage of an arrangement according to the invention is to have elastic blades working in quasi-pure bending, which makes it possible to obtain an isochronous resonator.
  • the torque is proportional to the angle ⁇ of which the corresponding mass 5 pivots.
  • the frequency is therefore independent of the amplitude of the oscillation.
  • the distance between the embedding of the elastic flexible blade 6 in the crosspiece 4 and the center of mass CM is equal to the distance between the center of mass CM and the embedding of the elastic flexible blade 6 in the associated mass 5, as visible on the figure 1 .
  • the center of mass CM thus remains on the X axis, or in the immediate vicinity of the X axis, that is to say at a distance of a few micrometers.
  • each primary resonator 10 is arranged to oscillate in one plane.
  • each primary resonator 10 is monolithic.
  • the crosspiece 4 and the flexible guides 20, in particular the elastic flexible strips 6, of the primary resonators 10 form a monolithic assembly.
  • the fixed support 2, the main elastic connection 3, the crosspiece 4, and the flexible guides 20, in particular the flexible elastic strips 6, of the primary resonators 10, form a monolithic assembly.
  • Such an embodiment makes it possible to obtain flexible guides 20, in particular elastic blades 6 called “in high sheet", which have a very great height compared to their thickness, in particular at least five times higher than thick, and more particularly at least ten times higher than thick.
  • Such blades in high sheet make it possible to ensure the guiding function, and to dispense with traditional pivots, which allows a significant increase in the quality factor.
  • the architecture in the form of a tuning fork, according to the invention makes it possible to compensate for all the reactions to embeddings, which again very significantly increases the quality factor.
  • the masses 5, 51, 52 of the primary resonators 10 are essentially subjected to a pivoting movement.
  • the corresponding flexible guide 20, in particular the corresponding elastic flexible blade 6, performs the function of guiding in pivoting.
  • each primary resonator 10 is arranged to oscillate in one plane
  • all the primary resonators 10 are arranged to oscillate in planes parallel to each other, or else in the same plane.
  • all these primary resonators 10 are arranged to oscillate in the same plane, for example on the embodiments illustrated in figures 1 to 12 .
  • these primary resonators 10 each extend in a separate plane.
  • THE figures 1 to 12 illustrate an isochronous oscillator mechanism 1, of which all the primary resonators 10 are identical, in even number, and arranged in symmetry with respect to a plane of symmetry PSY extending parallel to a transverse direction Y which is that of the main elastic connection 3 and perpendicular to a longitudinal direction X along which the centers of mass CM of the primary resonators 10 are mobile.
  • the primary resonators 10 then oscillate in phase opposition, which guarantees the compensation of the movements of the centers of mass CM in the longitudinal direction X.
  • the main elastic link 3 is straight.
  • the elastic flexible blades 6 are straight, in the longitudinal direction X.
  • the centers of mass CM of the primary resonators 10 considered are in their alignment at rest. This arrangement guarantees the insensitivity to the positions of the isochronous oscillator mechanism 1, unlike a tuning fork of the conventional type with parallel branches which is far too sensitive to the positions in space if it is incorporated in a watch, and which can only be suitable to a piece of clock.
  • the residual defect after compensation for displacements of the centers of mass in X is of very low value, of the same order of magnitude as the defect due to displacements of the centers of mass in Y, which is limited to 3 or 4 micrometers, for a blade of 1 millimeter long, the cumulative fault thus remains less than 6 seconds per day.
  • the symmetry thus compensates for any residual rate error.
  • the compensation of the forces and of the torques on embedding allows the primary resonators 10 to oscillate for a very long time without being damped.
  • the elastic flexible strips 6 that comprise the primary resonators 10 are straight and aligned in pairs.
  • the flexible guides 20 consist of elastic flexible blades 6 in spirals, wound around the centers of mass CM of the primary resonators 10 considered.
  • a variant illustrated on the figures 13 and 14 represents a torsion tuning fork which comprises arms 51 and 52, each provided with a mass at its distal end, and oscillating in parallel planes P1 and P2 and symmetrically with respect to an axis A parallel to these two planes P1 and P2.
  • Another tuning fork variant illustrated by the figure 15 comprises two resonators, each comprising a hairspring embedded at a first end on a common crosspiece and comprising a mass at a second distal end, these two resonators extending along two parallel planes and being, in projection on one of these planes, symmetrical with respect to a plane of symmetry PS which is perpendicular to these two planes.
  • the resulting torque is indeed zero when embedded at the level of the crosspiece 4.
  • the mechanisms must be usable in a watch, and incorporate security, in particular anti-shock.
  • the first mode of tuning fork in H is represented on the figures 1 to 7 .
  • This crosspiece 4 carries a pair of masses 5 marked 51 and 52, mounted symmetrically on either side of the fixed support 2 and the first elastic connection 3.
  • each of them comprises an arm connected in its middle to the corresponding flexible blade 6, this arm extending substantially parallel in the transverse direction Y, and being either a solid arm as on the picture 3 , either an arm comprising inertial weights at its opposite ends, or substantially point-like as on the figure 1 , either in the form of annular sectors, as seen on the figure 2 , And 4 to 7 .
  • Each of these masses 51, 52 is mounted in an oscillating manner around a virtual pivot axis of determined position relative to the crosspiece 4, and returned by an elastic flexible strip 6, marked 61, 62 respectively, which constitutes means of elastic return and which is integral with one end 41, 42 of the crosspiece 4, the two ends 41 and 42 being opposite and on either side of the crosspiece 4.
  • These flexible blades 61, 62 preferably extend linearly in the extension and on either side of the crosspiece 4.
  • Each virtual pivot axis is, in the rest position of the isochronous oscillator mechanism 1, coincident with the center of mass CM1, CM2, of the respective mass 51, 52.
  • These elastic flexible blades 61, 62 are arranged to limit the movement of the centers of mass CM1, CM2, to a transverse travel relative to the crosspiece 4, as small as possible in the transverse direction Y, and to a longitudinal travel along the longitudinal direction X greater than this transverse stroke.
  • the isochronous oscillator mechanism 1 advantageously comprises rotation stops, and/or translation limiting stops along the X and Y directions, and/or translation limiting stops in Z.
  • These stroke limiting means can be integrated, form part of a one-piece construction, or/and be attached.
  • the masses 51, 52 advantageously comprise abutment means 7, marked 71, 72, which are arranged to cooperate with complementary abutment means 73, 74, which the crosspiece 4 comprises, and limit the displacement of the flexible elastic blades 61, 62, with respect to the crosspiece 4, in the event of shocks or similar accelerations.
  • a mass 5 is not directly carried by the flexible strip 6, the latter comprises, on the other side relative to the main body of the crosspiece 4, an end plate 45, which is arranged to receive, directly or indirectly, this mass 6.
  • the execution of figure 4 And 5 like the variant of the second mode of the figure 11 And 12 , comprises end pieces 53, 54, arranged to be attached to such an end plate 45 and to receive a mass 51 or 52.
  • the variant of the first mode of the figure 6 And 7 includes a socket 55 arranged to perform the same function.
  • the ends of the crosspiece 4 each have two abutment bearing surfaces 42, which are each arranged to stop an oblique surface 74 that includes the end plate 45, so as to limit the angle of deformation ⁇ (defined in figure 1 ) that can take the flexible blade 6 relative to its embedding in the crosspiece 4, and thus constituting stops in rotation.
  • the corresponding end of the crosspiece 4 further comprises a housing 79, in particular here a bore, arranged to serve as a limiting stop around the periphery 48 of the substantially circular end plate 45, to limit the translations in X and in Y. at these different stops, which limit the translations in X and in Y, the possible influence of shocks is limited, the flexible blade 6 is protected, and this flexible blade 6 is preserved against any excessive deformation. And of course we limit the possible displacement of the centers of mass CM.
  • Z stops are provided primarily when end caps 53, 54, bushings 55, or the like are used; for example the figure 5 illustrates end pieces 53, 54, which either comprise bores aligned with journals 56 carried by a plate, or else comprise bearing surfaces aligned with bores of a plate, the bearings thus formed being without contact in normal operating conditions , and being arranged to take up the forces, in particular in Z, in the event of an impact.
  • the detail of the figure 6 shows, with regard to the variant with the reception of a sleeve 55, a similar arrangement with regard to the stops.
  • the end plate 45 further comprises a lug with stop surfaces 76 arranged to cooperate in abutment support with complementary surfaces 78 of the crosspiece 4, to limit translations.
  • the sleeve 55 has a skirt 57 driven onto the end plate 45 but the periphery 59 of this sleeve 55 remains at a distance from the bore 79 of the crosspiece 4, and then ensure with it safety in translation in X and Y .
  • Shoulders in Z can also be provided on certain surfaces to form limiting abutment surfaces in Z.
  • the complementary surfaces of the stops In the absence of unexpected accelerations such as shocks, the complementary surfaces of the stops must not be in contact with each other, so as to avoid any unnecessary friction detrimental to the quality factor.
  • Certain travel limiting means can be used to perform functions of damping unwanted vibration modes.
  • first and second embodiments thus show the fixed support 2 and the crosspiece 4 which are separated only by a narrow groove 30, called here "honey groove", around the main elastic connection 3, which is designed to authorize coupling in tuning fork mode.
  • the groove 30 makes it possible to limit the angular movement of the crosspiece 4, which is insignificant under normal conditions, but which can occur in the event of an impact.
  • this groove is filled with a viscous or pasty product, which allows the dissipation of energy in the event of excessive movement.
  • the elastic flexible blades 61, 62 which extend substantially along the longitudinal direction X, are short blades, that is to say of a length less than the smallest value between four times their height or thirty times their thickness. It is this short blade characteristic which makes it possible to limit the displacements of the center of mass CM concerned.
  • each primary resonator 10 practically does not move in the transverse direction Y: it performs a reversal movement, on either side of a mean axis parallel to the longitudinal direction X, around from a point located on this mean axis.
  • the elastic flexible strips 61 and 62 are preferably aligned, these strips preferably being straight.
  • the second tuning fork mode in goat horns is represented on the figures 8 to 12 .
  • the fixed support 2, the main elastic connection 3, the crosspiece 4, the flexible elastic blades 6, and the end plates 45 of the primary resonators 10, together form a planar monolithic structure, in silicon, or oxidized silicon, or quartz, or DLC, or similar, which, in the rest position of the isochronous oscillator mechanism 1, is symmetrical with respect to a plane of symmetry PS, and comprises an elongated crosspiece 4 which extends along the longitudinal direction X, perpendicular to the connection main elastic 3, which extends in the transverse direction Y, and which holds the crosspiece 4 on the fixed support 2.
  • this crosspiece 4 carries a pair of masses 5 marked 51 and 52, mounted symmetrically on either side of the fixed support 2 and of the first elastic connection 3.
  • Each of these masses 51, 52 is mounted in an oscillating manner and recalled by an elastic flexible blade 6 marked respectively 61, 62, which is a hairspring 8, respectively 81, 82, or else an assembly of hairsprings.
  • a first hairspring 81 and a second hairspring 82 are each linked at its internal turn to an end plate 45 intended to receive a mass 51, 52, and attached to the respective end 41, 42 of the crosspiece 4 by its outer coil.
  • the masses 51 and 52 each pivot around a virtual pivot axis of determined position with respect to the crosspiece 4.
  • Each virtual pivot axis is, in the rest position of the isochronous oscillator mechanism 1, coincident with the center of mass CM1, CM2, of the respective mass 51, 52.
  • the masses 51, 52 extend substantially in the transverse direction Y.
  • each of them comprises an arm connected in the middle to the corresponding flexible blade 6, this arm being extending substantially parallel in the transverse direction Y, and being either a solid arm as in the picture 3 , either an arm comprising inertial weights at its opposite ends, or substantially point-like as on the figure 8 , either in the form of annular sectors, as seen on the figures 9 to 12 .
  • each hairspring 81, 82 has a section or variable curvature along its development.
  • the version illustrated by the figures is a variant with variable thickness, optimized to limit displacements of the center of mass CM.
  • the pendulum mass 5 is preferably suspended by a coil thicker than the rest of the hairspring.
  • the development of the hairspring is greater than one turn, and in particular greater than 1.5 turns, which proves to be easier to minimize the displacement of the center of mass.
  • a regular decrease in thickness over 270°, followed by an increase in thickness can make it possible to limit the displacement of the center of mass CM to 3 micrometers in Y and 4 micrometers in X.
  • the elementary polar stiffness advantageously passes through an extremum, for example a mini between two maxi, or the reverse.
  • a satisfactory simulation consists, again, in giving the hairspring a greater stiffness in its part 89 which is beyond the center of mass towards the outside, than in its part 88 which is comprised between the two centers of mass CM1 and CM2.
  • variable thickness corresponds to an easier MEMS elaboration.
  • the modes of oscillation in translation and the displacements in the event of shocks are preferably mechanically limited by axes, or by end pieces 53, 54, or bushings 55.
  • the first hairspring 81 and the second hairspring 82 are attached to the ends 41, 42, in alignment with their respective virtual pivot axis, in the rest position of the isochronous oscillator mechanism 1.
  • FIG 16 illustrates another embodiment close to the invention, where this figure diagram of the second mode is extrapolated by suspending each mass, not from a single hairspring, but from pairs of hairsprings 81, 810, respectively 82, 820, attached to the crosspiece 4, on either side of the centers of mass in the Y direction.
  • This very robust construction is closer to a system with crossed flexible blades than to the systems presented in the figures 1-15 And 17-22 .
  • FIG 19 illustrates a variant where the crosspiece 4 constitutes a frame surrounding the primary resonators 10, in an application example with four resonators 10A, 10B, 10C, 10D. It is understood that this inverse architecture of the previous examples can also be used for the implementation of the invention, in all its variants set out above, and which are therefore not further detailed here.
  • FIG 20 illustrates, in this variant of crosspiece 4 formed by a frame, the counterpart of the H-shaped tuning fork.
  • Crosspiece 4 carries a pair 51, 52, of masses 5, mounted symmetrically inside crosspiece 4 which forms a frame suspended by the first elastic connection 3 to the fixed structure 2, the masses 51, 52 extending substantially in the transverse direction Y.
  • Each of the masses 51, 52 is mounted in an oscillating manner around a virtual pivot axis of position determined with respect to the crosspiece 4, and recalled by an elastic flexible blade 6, respectively 61, 62, which is integral with one side of the frame forming the crosspiece 4, the flexible blades 61, 62, extending linearly to the inside the frame.
  • FIG 21 illustrates, in this variant of crosspiece 4 formed by a frame, the counterpart of the goat's horn tuning fork.
  • the crosspiece 4 carries a pair 51, 52, of masses 5, mounted symmetrically inside the crosspiece 4 which forms a frame suspended by the first elastic connection 3 to the fixed structure 2, and substantially in a transverse direction Y perpendicular to the longitudinal direction X in which the centers of mass CM of the primary resonators 10 are mobile. oscillating around a virtual pivot axis of determined position with respect to the crosspiece 4, and returned by a hairspring 8, respectively 81, 82, which is integral with one side of the frame forming the crosspiece 4, these hairsprings 81, 82 , extending inside the frame.
  • the masses 5, 5A, 5B, 51, 52 form pendulums.
  • the masses 51, 52 comprise, for the purposes of balancing adjustment, inertia and oscillation frequency adjustment, weights 91, 92, or/and housings 93 for receive such counterweights, preferably in the zones furthest from the ends 41, 42 of the crosspiece 4.
  • Such counterweights advantageously comprise an eccentric insert, for example made of platinum, to facilitate adjustment by pivoting of the insert.
  • particular zones of these masses 5 can be devoted to laser ablation, or, conversely, to plasma, inkjet or similar resurfacing, to ensure these adjustments.
  • the invention also relates to a clock movement 100, in particular mechanical, comprising such an isochronous oscillator mechanism 1.
  • the invention also relates to a watch 200 comprising such a mechanical movement 100.
  • the oscillator according to the invention constitutes a tuning fork composed of two rotating resonators with bending blades, mounted on a crosspiece connected, preferably visco-elastically, to the plate.
  • each primary resonator 10 The elastic elements of each primary resonator 10 are designed to minimize the displacement of the center of mass CM in the transverse direction Y of the plane of symmetry PSY of the tuning fork.
  • the plane of symmetry PSY of the tuning fork is chosen so that the rate errors due to the positions in the longitudinal direction X perpendicular to the transverse direction Y, are canceled between the two branches of the tuning fork formed by the primary resonators 10, either side of the crosspiece 4.
  • the tuning fork type architecture makes it possible to limit the effect of reactions to embedments.
  • the invention minimizes the displacement of the center of mass CM of each primary resonator 10.
  • the invention makes it possible to obtain a perfectly isochronous oscillator, very compact, requiring no other adjustment than the inertia of the masses, and very easy to assemble.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)

Claims (19)

  1. Isochroner Oszillatormechanismus (1) der Uhrmacherei, der sich im Wesentlichen flach entwickelt und eine feststehende Stütze (2) umfasst, die ein Querelement (4) trägt, das eine Vielzahl von N primären Resonatoren (10) trägt, von denen jeder mindestens eine Masse (5) trägt, die von einer flexiblen Drehführung (20) getragen wird, die an dem Querelement (4) befestigt ist, wobei jeder primäre Resonator (10) einen Massenmittelpunkt (CM) aufweist, der sich im Ruhezustand auf der virtuellen Schwenkachse (APV) seiner jeweiligen flexiblen Drehführung (20) befindet, und jeder primäre Resonator (10) gemäß einer Rotationsbewegung um die virtuelle Schwenkachse (APV) schwingend angeordnet ist, wobei die N primären Resonatoren (10) gemäß einer Rotationssymmetrie der Ordnung N um eine Hauptachse (AP) angeordnet sind, die parallel zu allen virtuellen Schwenkachsen (APV) ist, die parallel zueinander sind, und wobei die Bewegungen der Oszillation von zwei primären Resonatoren (10) des Oszillatormechanismus (1) um den Wert des Winkels in der Mitte phasenverschoben sind, den ihre jeweiligen virtuellen Schwenkachsen (APV) in Bezug auf die Hauptachse (AP) bilden, und die flexible Führung (20) mindestens gekreuzte Klingen umfasst, die entweder in derselben Ebene gekreuzt sind oder deren Projektionen auf einer Ebene senkrecht zur Hauptachse (AP) gekreuzt sind und deren tatsächliche Schnittstelle oder Projektion auf die Ebene, die senkrecht zu der Hauptachse (AP) verläuft, die virtuelle Schwenkachse (APV) der flexiblen Führung (20) definiert, dadurch gekennzeichnet, dass mindestens zwei der primären Resonatoren (10) mindestens intermittierend durch ein Hemmungsrad miteinander gekoppelt sind.
  2. Isochroner Oszillatormechanismus (1) nach Anspruch 1, dadurch gekennzeichnet, dass jede flexible Drehführung (20) in Projektion auf eine Ebene, die senkrecht zu der Hauptachse (AP) verläuft, symmetrisch in Bezug auf eine Symmetrieebene (PS) ist, die durch die virtuelle Schwenkachse (APV) der betrachteten flexiblen Drehführung (20) verläuft.
  3. Isochroner Oszillatormechanismus (1) nach Anspruch 2, dadurch gekennzeichnet, dass jede Symmetrieebene (PS) durch die Hauptachse (AP) verläuft.
  4. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass jede flexible Drehführung (20) so angeordnet ist, dass sie ein Rückstellmoment proportional zu dem Drehwinkel der einen Masse (5) in Bezug auf die virtuelle Schwenkachse (APV) der betrachteten flexiblen Drehführung (20) bewirkt.
  5. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die primären Resonatoren (10) mindestens einen identischen Resonanzmodus aufweisen.
  6. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass alle primären Resonatoren (10) untereinander identisch sind.
  7. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Querelement (4) an der feststehenden Stütze (2) durch eine elastische Hauptverbindung (3) befestigt ist, deren Steifigkeit größer ist als die Steifigkeit jeder flexiblen Drehführung (20).
  8. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass jeder primäre Resonator (10) so angeordnet ist, dass er in einer Ebene um eine neutrale radiale Achse (AN) schwingt, und dadurch, dass alle neutralen radialen Achsen (AN) an einem einzigen Punkt zusammenlaufen oder paarweise an Schnittpunkten zusammenlaufen, die sich alle im gleichen Abstand von der Hauptachse (AP) befinden.
  9. Isochroner Oszillatormechanismus (1) nach Anspruch 8, dadurch gekennzeichnet, dass die primären Resonatoren (10) eine gerade Zahl oder zwei sind, und dadurch, dass alle neutralen Achsen (AN) paarweise parallel zueinander oder zusammenfallend sind.
  10. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die flexible Führung (20) mindestens eine elastische flexible Klinge (6) umfasst, und dadurch, dass die virtuelle Schwenkachse (APV) in der Mitte der elastischen flexiblen Klinge (6) liegt.
  11. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die flexible Führung (20) mindestens einen Hals mit einem sich verjüngenden Abschnitt umfasst.
  12. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die primären Resonatoren (10) eine gerade Zahl oder zwei sind, und dadurch, dass die flexible Führung (20) jedes primären Resonators mindestens eine Spiralfeder umfasst, wobei die Spiralfedern der primären Resonatoren (10) paarweise gespiegelt angeordnet sind.
  13. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass zumindest die flexible Führung (20) aus mikrobearbeitbarem Material oder Silizium oder/und Siliziumoxid oder aus Quarz oder aus DLC besteht.
  14. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass jeder primäre Resonator (10) zumindest auf der Höhe der flexiblen Führung (20) ein thermisches Kompensationsmittel umfasst.
  15. Isochroner Oszillatormechanismus (1) nach Anspruch 14, dadurch gekennzeichnet, dass das thermische Kompensationsmittel mindestens eine Komponente umfasst, die aus Elinvar oder aus Silizium und Siliziumoxid hergestellt ist.
  16. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, dass mindestens einer der primären Resonatoren (10) ein Spieleingrenzungsmittel umfasst, das so angeordnet ist, dass es im Falle eines Stoßes bei Anschlagsauflage mit einem komplementären Spielbegrenzungsmittel, das die feststehende Stütze (2) und/oder das Querelement (4) umfasst, zusammenwirkt.
  17. Isochroner Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, dass die primären Resonatoren (10) so angeordnet sind, dass sie jeweils mit einer Frequenz, die zwischen 1 Hz und 100 Hz liegt, schwingen.
  18. Uhrwerk (100), das zumindest einen isochronen Oszillatormechanismus (1) nach einem der Ansprüche 1 bis 17 umfasst.
  19. Uhr (200), die zumindest ein Uhrwerk (100) nach Anspruch 18 umfasst.
EP16701499.2A 2015-02-03 2016-01-26 Isochroner resonator für uhr Active EP3254158B1 (de)

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EP15153656.2A EP3054356B1 (de) 2015-02-03 2015-02-03 Isochroner Resonator für Uhr
PCT/EP2016/051486 WO2016124436A1 (fr) 2015-02-03 2016-01-26 Resonateur isochrone d'horlogerie

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CN106662839B (zh) 2019-03-29
US9983549B2 (en) 2018-05-29
EP3254158A1 (de) 2017-12-13
US20170123380A1 (en) 2017-05-04
JP6326549B2 (ja) 2018-05-16
WO2016124436A1 (fr) 2016-08-11
JP2017514152A (ja) 2017-06-01

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