EP3054358B1 - Clock oscillator mechanism - Google Patents

Description

Field of the invention

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 the field of watch oscillators for watches, in particular for mechanical movements.

Background of the invention

• l'entretien des va-et-vient du résonateur, constitué par un ensemble balancier-spiral ;
• le comptage de ces va-et-vient.

Most of today's mechanical watches feature a Swiss lever escapement. The two main functions of the exhaust are:

• maintenance of the comings and goings of the resonator, constituted by a pendulum-balance assembly;
• Counting these back and forth.

In addition to these two functions, 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 patent FR 630831 in the name of SCHIEFERSTEIN describes a method and an arrangement for the transmission of power between mechanical systems and for the control of mechanical systems

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.

Summary of the invention

The present invention aims to provide a high efficiency exhaust system. We also propose a oscillator without pivot and without reaction to the support to achieve a very high quality factor.

To achieve this goal, 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.

For this purpose, 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.

Brief description of the drawings

• la figure 1 représente, de façon schématisée et en plan, un oscillateur horloger comportant deux résonateurs élémentaires de type masse-ressort oscillant linéairement et selon des directions différentes, et dont les masses sont articulées à des bielles, lesquelles coopèrent ensemble de façon articulée avec un doigt qui parcourt une rainure d'un mobile soumis à un couple moteur, pour coupler les deux résonateurs élémentaires ;
• la figure 2 représente, de façon schématisée et en vue en plan, une variante de l'invention où les résonateurs primaires sont des résonateurs rotatifs, de type balancier-spiral ;
• la figure 3 représente, de façon schématisée et en vue en plan, une autre variante de l'invention avec deux résonateurs primaires, dont chacun est lui-même constitué d'une paire de résonateurs élémentaires, qui comportent chacun une masse élémentaire portée par une lame flexible élastique élémentaire sous forme de spiral, constituant un moyen de rappel élastique, et qui est agencée pour travailler en flexion, et qui est encastrée dans une traverse ; chaque résonateur primaire forme ainsi, par la combinaison de ces deux résonateurs élémentaires, un mécanisme oscillateur isochrone de type diapason dit en cornes de bouc ;
• la figure 4 représente, de façon schématisée et en perspective, un détail de l'articulation des bielles des figures 1 à 3 ;
• la figure 5 représente, de façon similaire, une structure similaire à celle de la figure 3, où les lames flexibles élastiques ne sont plus constituées par des spiraux, mais par des lames droites et courtes, disposées de part et d'autre d'une traverse avec laquelle elle forment la barre horizontale d'un H dont les masses forment les barres verticales; chaque résonateur primaire forme ainsi, par la combinaison de ces deux résonateurs élémentaires, un mécanisme oscillateur isochrone de type diapason dit en H ; cette figure 5 montre des moyens de transmission constitués par des lames flexibles, en remplacement des bielles des figures précédentes ;
• les figures 6 et 7 représentent, de façon schématisée et en perspective, des variantes où les bielles sont des poutres comportant des cols aux deux extrémités en lieu et place des moyeux, la figure 6 illustre un cas de couplage de deux résonateurs primaires, la figure 7 illustre un cas de couplage de trois tels résonateurs ;
• la figure 8 représente, de façon schématisée et en perspective, un oscillateur horloger comportant trois résonateurs primaires disposés en triangle autour de leur moyen de commande commun ; cette figure montre l'application du couplage de la figure 7 aux masses inertielles des trois résonateurs ;
• la figure 9 représente, de façon similaire à la figure 8, un oscillateur horloger comportant quatre résonateurs;
• la figure 10 représente, de façon schématisée et en perspective, une variante où un moyen de rappel élastique constitue également un guidage rotatif, un moyen de transmission est constitué par une lame flexible, dans la configuration de la figure 9; cette figure montre également des butées angulaires et des butées antichoc, ménagées sur un ensemble monolithique regroupant un cadre, des lames flexibles courtes, les masses inertielles, les moyens de transmission et l'interface avec des moyens de commande ;
• la figure 11 représente, de façon schématisée et en vue en plan, une variante où le mobile comporte une structure élastique déformable, formant un guidage souple radialement et rigide tangentiellement, comportant un logement de réception d'un doigt du moyen de commande, à l'articulation principale, la structure déformable étant représentée en deux positions extrêmes ;
• la figure 12 représente, de façon schématisée et en perspective, l'extrapolation de l'ensemble monolithique de la figure 10 pour un mécanisme comportant quatre masses inertielles ; cet ensemble est élargi, et comporte encore la structure porteuse, et une liaison élastique principale de suspension du cadre à cette structure ;
• la figure 13 représente l'ensemble de la figure 10 dans un champ de gravitation ;
• la figure 14 est un schéma-blocs représentant une montre comportant un mouvement qui intègre un oscillateur horloger selon l'invention.

Other features and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, in which:

• the figure 1 schematically shows in plan a clock oscillator comprising two mass-spring-type elementary resonators oscillating linearly and in different directions, and whose masses are articulated to connecting rods, which cooperate together in an articulated manner with a finger that runs through a groove of a moving body subjected to a driving torque, for coupling the two elementary resonators;
• the figure 2 is schematically shown in plan view, a variant of the invention wherein the primary resonators are rotary resonators, sprung-balance type;
• the figure 3 is schematically and in plan view, another variant of the invention with two primary resonators, each of which is itself constituted by a pair of elementary resonators, each comprising an elementary mass carried by an elastic flexible blade elementary spiral form, constituting an elastic return means, and which is arranged to work in bending, and which is embedded in a cross; each primary resonator thus forms, by the combination of these two elementary resonators, an isochronous oscillator mechanism of tuning fork type known as goat horns;
• the figure 4 represents, schematically and in perspective, a detail of the articulation of the connecting rods of Figures 1 to 3 ;
• the figure 5 represents, similarly, a structure similar to that of the figure 3 , where the elastic flexible blades are no longer constituted by spirals, but by straight and short blades, arranged on either side of a crossbar with which it forms the horizontal bar of an H whose masses form the bars vertical; each primary resonator thus forms, by the combination of these two elementary resonators, an isochronous oscillator mechanism of tuning fork type referred to as H; this figure 5 shows transmission means constituted by flexible blades, replacing the connecting rods of the preceding figures;
• the Figures 6 and 7 represent schematically and in perspective, variants where the rods are beams having collars at both ends instead of hubs, the figure 6 illustrates a case of coupling of two primary resonators, the figure 7 illustrates a case of coupling of three such resonators;
• the figure 8 schematically shows in perspective a clock oscillator comprising three primary resonators arranged in a triangle around their common control means; this figure shows the application of the coupling of the figure 7 the inertial masses of the three resonators;
• the figure 9 represents, similarly to the figure 8 a watch oscillator with four resonators;
• the figure 10 represents schematically and in perspective, a variant where an elastic return means also constitutes a rotary guide, a transmission means is constituted by a flexible blade, in the configuration of the figure 9 ; this figure also shows angular stops and shockproof stops, formed on a monolithic assembly comprising a frame, short flexible blades, the inertial masses, the transmission means and the interface with control means;
• the figure 11 represents schematically and in plan view, a variant where the mobile comprises a deformable elastic structure, forming a rigid radially and tangentially rigid guide, comprising a housing for receiving a finger of the control means, at the main joint the deformable structure being represented in two extreme positions;
• the figure 12 represents, schematically and in perspective, the extrapolation of the monolithic set of the figure 10 for a mechanism with four inertial masses; this assembly is enlarged, and still includes the supporting structure, and a main elastic link suspension frame to this structure;
• the figure 13 represents the whole of the figure 10 in a field of gravitation;
• the figure 14 is a block diagram representing a watch comprising a movement that integrates a watch oscillator according to the invention.

Detailed Description of the Preferred Embodiments

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.

According to the invention, 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.

Preferably, 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.

Of course, the fact of canceling the reactions to the recesses is not essential for the operation of the oscillator, but it represents a very advantageous characteristic because this arrangement very significantly improves sensitivity to small impacts.

In addition, 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.

In the nonlimiting embodiments of embodiments illustrated in FIGS. Figures 1 to 9 , 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.

In a particular variant embodiment, the driving and guiding means 14 are constituted by a groove 140 in which a finger 150 slides which comprises the control means 15. Preferably, this groove 140 is substantially radial with respect to the rotation axis A of the mobile 13.

It is understood that 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. According to the invention, all the connecting rod directions are in pairs, at any time, an angle other than zero or π. Otherwise formulated, the vector product of the two directions of rods is different from zero.

In a particular application, 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. When a number n of elementary resonators together constitute a primary resonator, they are out of phase with each other by 2π / 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.

In a particular preferred application of the invention, but not limited to, and illustrated by the figures, the primary resonators 10 are rotary resonators. By this is meant that 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 °.

These rotary primary resonators are not very sensitive to shocks in translation, and to positioning problems, in contrast to linear and angular resonators.

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 .

To obtain a better quality factor, 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 in an approximate way because the center of mass remains fixed only approximately, or moves 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.

Thus, preferably, the resultant of the forces and reaction torques of the primary resonators 10 with respect to the common structure 2 or the frame 4, to which they are attached, is approximately zero, thanks to the phase-shifted arrangement of the n resonators. primary 10, in particular rotary.

For optimum operation, the primary rotary resonators 10 are arranged so that their centers of mass remain approximately in fixed position, at least during the normal oscillations of these primary resonators 10. The watch oscillator 1 preferably comprises means for stop to limit their stroke in case of shock or the like.

Preferably, 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 2π / 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.

By "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 2π / n. In a particular application, as can be seen in the figures, 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 π relative to one another. .

In a particular arrangement, as visible on the Figures 3 and 5 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 2π / 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. And the elementary resonators 810 are arranged in space so that the resultant of their operating errors due to gravitation is zero.

More particularly, at least one of the primary resonators 10 consists of a pair of such elementary resonators 810. In this pair, the elementary inertial masses are in phase shift of π relative to each other.

More particularly, this pair consists of identical elementary resonators 810, which are geometrically opposed and phase to each other.

In the particular case of Figures 3 and 5 each primary resonator 10 consists of such a pair of elementary resonators 810.

In the variant of the figure 3 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 elastic flexible blade 61A, 62A, respectively 61B, 62B. And the damping of this main elastic connection is greater than that of each flexible blade. These characteristics provide a coupling between the elementary resonators 8101 and 8102, respectively 8103 and 8104.

In this variant, each primary resonator 10 is balanced for itself, in translation and in rotation.

For each primary resonator 10A, 10B, at least the main elastic connection 3A, respectively 3B, the cross member 40A, respectively 40B, the flexible flexible blades 61A, 62A, respectively 61B, 62B, together form a flat primary monolithic structure, made of micro material -usinable, such as silicon, or oxidized silicon, or quartz, or DLC, or the like, which, in the rest position of the isochronous oscillator mechanism 1, is symmetrical with respect to a plane of symmetry. Advantageously, the fixed support 2 forms a monolithic assembly with these two primary monolithic structures. By "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.

If, in a particular embodiment, 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 areas, in particular blades flexible of the monolithic structure, can occupy only part of this thickness.

Such a monolithic embodiment, particularly advantageous, is applicable to the various non-limiting variants of the invention illustrated in the present description. In a first variant, the monolithic structure is produced by a growth method, of the "MEMS", "LIGA" or similar type.

In another variant, the monolithic structure is produced by cutting a plate, for example by electro-erosion wire and / or sinking.

The cross member 40A, respectively 40B, 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 oscillatingly mounted and biased by an elastic flexible blade 61A, 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. To limit the displacement of the centers of mass to a transverse stroke relative to the crossbar 4, as small as possible in this transverse direction Y, and to a longitudinal race in a longitudinal direction (perpendicular to this transverse direction) which is greater than this transversal stroke, 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 the so-called tuning fork type in H. The elastic flexible blades 6: 61A, 62A, respectively 61B , 62B, are no longer constituted by spirals, but by straight and short blades. The term "short blade" is used here to denote 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 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.

The Figures 1, 2 , 3 and 5 illustrate a clock oscillator 1 comprising two primary resonators 10.

In a particular embodiment, 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 π, the other of the elementary resonators 10B and 10D , also out of phase with π.

For the achievements of these Figures 8 and 9 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.

• ou bien chacun équilibré, ou bien équilibrés collectivement du fait de leur agencement particulier,
• équilibrés en translation ou/et en rotation.

In sum, the invention covers all combinations of primary resonators which are:

• or else each one balanced, or else balanced collectively because of their particular arrangement,
• balanced in translation and / or rotation.

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.

In the variants shown, 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 to the control means 15 a substantially tangential force with respect 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.

In the various variants described here, preferably the elastic return means 6 of the primary resonators 10 comprise flexible blades, and 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.

In an advantageous embodiment, as can be seen in particular on the Figures 12 and 13 , 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.

Advantageously, this monolithic structure further comprises the stops.

Preferably, 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.

In a variant that is not illustrated, the elastic return means 6 of the primary resonators 10 are virtual cross-blade pivots.

In a particular variant of the watch oscillator 1 according to the invention, the primary resonators 10 are isochronous.

Preferably, 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.

• une roue à rainure, contrairement à une liaison élastique sur une manivelle, n'ajoute pas de force de rappel parasite aux résonateurs lorsque l'amplitude change. Il s'ensuit un meilleur isochronisme ;
• l'utilisation de résonateurs rotatifs dont le centre de rotation est sensiblement confondu avec le centre de masse évite que le centre de masse se déplace dans le champ de gravité, et, partant, évite que la période soit affectée par un changement d'orientation de la montre. Le même argument explique que notre système est moins affecté par des chocs en translations ;
• de préférence, les résonateurs sont tous identiques et montés en parallèle. Les mouvements de l'un ne risquent donc pas de parasiter l'inertie de l'autre, contrairement aux montages en série ;
• l'utilisation de deux résonateurs, ou davantage, complètement distincts, c'est-à-dire avec une masse inertielle propre à chaque résonateur primaire ou élémentaire, permet d'optimiser l'isochronisme des résonateurs séparément, et de jouer sur leur orientation pour que les erreurs dues aux positions et les réactions à l'encastrement s'annulent. Cela est un grand avantage pour obtenir un oscillateur indépendant des positions de la montre, et ayant un facteur de qualité très élevé.
• la conception permet une fabrication très simple de la version intégrée ;
• l'invention permet des réalisations dans la plus pure tradition horlogère puisqu'on peut simplement utiliser deux ensembles balancier-spiral reliés à la roue d'échappement par des bielles très légères ou des lames flexibles.

The advantages of the invention are numerous:

• a grooved wheel, unlike an elastic link on a crank, does not add a parasitic biasing force to the resonators when the amplitude changes. It follows a better isochronism;
• the use of rotary resonators whose center of rotation is substantially coincidental with the center of mass prevents the center of mass from moving in the gravitational field, and thus avoids that the period is affected by a change of orientation of the watch. The same argument explains that our system is less affected by shocks in translations;
• preferably, the resonators are all identical and connected in parallel. The movements of one are not likely to interfere with the inertia of the other, unlike series editing;
• the use of two or more completely distinct resonators, that is to say with an inertial mass specific to each primary or elementary resonator, makes it possible to optimize the isochronism of the resonators separately, and to play on their orientation for that positional errors and flush responses cancel each other out. This is a great advantage to obtain an oscillator independent of the positions of the watch, and having a very high quality factor.
• the design allows a very simple manufacture of the integrated version;
• the invention allows achievements in the purest watchmaking tradition since one can simply use two sprung balance assemblies connected to the escape wheel by very light rods or flexible blades.

Claims (21)

1. Clock oscillator (1) comprising a structure (2) or/and a frame (4), and a plurality of separate temporally and geometrically offset resonators, and each comprising at least one inertial mass (5) returned to said structure (2) or to said frame (4) by an elastic return means (6), said clock oscillator (1) comprising coupling means (11) arranged to allow the interaction of said resonators, said coupling means (11) comprising a wheel set (13) subjected to a drive torque by motor means (12) arranged such that they drive said wheel set (13) in a rotational movement and which comprise drive and guide means (14) arranged such that they drive and guide a single control means (15), which is articulated about a first control axis with a plurality of transmission means (16), each articulated about a second hinge axis, remote from said control means (15), with one said inertial mass (5) of one said resonator, said resonators and said wheel set (13) being arranged such that said second hinge axes of any two of said resonators and said first control axis of said control means (15) are never coplanar, characterised in that said resonators are rotating or angular resonators, the centres of mass whereof remain, during the normal oscillations of said resonators, in immediate proximity, at a distance of less than several tens of micrometres, to the centres of rotation of said resonators.
2. Clock oscillator (1) according to claim 1, characterised in that said drive and guide means (14) are formed by a groove (140) in which slides a finger (150) comprised in said control means (15).
3. Clock oscillator (1) according to claim 2, characterised in that said groove (140) is substantially radial with respect to the axis of rotation (A) of said wheel set (3).
4. Clock oscillator (1) according to one of claims 1 to 3, characterised in that the resultant of the reaction torques of all of said resonators with respect to said common structure (2) or to said frame (4) is zero.
5. Clock oscillator (1) according to one of claims 1 to 4, characterised in that said resonators have at least one substantially identical resonance mode, and are arranged such that they vibrate with a phase-shift therebetween of value 2π/n, where n is the number of said resonators.
6. Clock oscillator (1) according to one of claims 1 to 5, characterised in that said transmission means (16) are flexible elastic blades.
7. Clock oscillator (1) according to one of claims 1 to 5, characterised in that said transmission means (16) comprise at least one one-piece connecting rod arranged such that it engages both with said control means (15) and with at least two said inertial masses (5) of as many said resonators, and comprise at least one flexible neck in each articulation area.
8. Clock oscillator (1) according to one of claims 1 to 7, characterised in that said transmission means (16) comprise connecting rods (160) each comprising a first articulation (161) with said control means (15) and a second articulation (162) with said inertial mass (5), said first articulation (161) and said second articulation (162) jointly defining a connecting rod direction, and characterised in that all of said connecting rod directions form, in pairs, at any time, an angle different from zero or π.
9. Clock oscillator (1) according to one of claims 1 to 8, characterised in that said wheel set (13) and said drive and guide means (14) are arranged such that they apply to said control means (15) an essentially tangential force with respect to said rotation of said wheel set (3).
10. Clock oscillator (1) according to one of claims 1 to 9, characterised in that said elastic return means (6) of said resonators comprise flexible blades, and in that said resonators and/or said common structure (2) or said frame (4) comprise radial and/or angular and/or axial bankings arranged such that they limit the deformations of said flexible blades and prevent breakage in the event of impacts or excessive drive torque.
11. Clock oscillator (1) according to one of claims 1 to 10, characterised in that said clock oscillator (1) comprises a one-piece structure which combines a common structure (4) to which are returned said inertial masses (5) and said elastic return means (6) thereof, said control means (15) and the articulations thereof with said transmission means (16), and said transmission means (16) with the articulations thereof to said inertial masses (5).
12. Clock oscillator (1) according to claim 10 and claim 11, characterised in that said one-piece structure further comprises said bankings.
13. Clock oscillator (1) according to either claim 11 or claim 12, characterised in that said one-piece structure is a straight prism delimited by two planes that are parallel to one other and perpendicular to the direction of elongation of said prism.
14. Clock oscillator (1) according to one of claims 1 to 13, characterised in that said elastic return means (6) of said resonators comprise short rectilinear blades, the length whereof is less than the smallest value of four times the height or thirty times the thickness of said blades.
15. Clock oscillator (1) according to one of claims 1 to 14, characterised in that said resonators are isochronous.
16. Clock oscillator (1) according to one of claims 1 to 8, characterised in that said resonators jointly form an isochronous, so-called H-shaped, tuning fork-type oscillator mechanism and each comprise flexible elastic blades formed by short straight blades, the length whereof is less than the smallest value of four times the height or thirty times the thickness of said blades, arranged on either side of a crosspiece (40A; 40B) with which they form the horizontal bar of an H, the vertical bars whereof are formed by said masses (5).
17. Clock oscillator (1) according to one of claims 1 to 8, characterised in that said resonators jointly form an isochronous, so-called goat horn-shaped, tuning fork-type oscillator mechanism and each comprise a crosspiece (40A; 40B) bearing said masses (5), each mounted in an oscillating manner and returned by a flexible elastic blade which is a balance spring or an assembly of balance springs, each said balance spring being directly or indirectly connected to one said mass (5) at the inner coil thereof, and attached to said crosspiece (40A; 40B) via the outer coil thereof, each said balance spring having a variable section or curvature along the developed length thereof.
18. Clock oscillator (1) according to one of claims 1 to 8, characterised in that at least one said elastic return means (6) also forms a rotating guide member.
19. Clock oscillator (1) according to one of claims 1 to 8, characterised in that at least said elastic means comprised therein are temperature compensated.
20. Clock movement (100) comprising at least one clock oscillator (1) according to one of claims 1 to 19.
21. Watch (200) comprising at least one movement (100) according to claim 20.

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