EP2908185A1 - Device for maintaining and adjusting a clock piece resonator - Google Patents

Abstract

Clock resonator (1) oscillating at a natural frequency (É0), comprising at least one oscillating member (100), and oscillation maintenance means (200). Said oscillating member (100) carries a regulator (2) oscillating at a control frequency (R) of between 0.9 times and 1.1 times the value of an integer multiple greater than or equal to 2 of the eigenfrequency (E0). Movement (10) comprising a resonator (1) of eigenfrequency (É0). A regulator (2) imposes a periodic modulation of the resonance frequency and / or the quality factor and / or the rest point of said resonator (1) with a control frequency (R) of between 0.9 times and 1.1 times the value. an integer multiple greater than or equal to 2 of the eigenfrequency (É0). Timepiece (30), in particular a watch, comprising at least one watch movement (10).

Description

Field of the invention

The invention relates to a forced oscillation clock resonator mechanism arranged to oscillate at a natural frequency and comprising on the one hand at least one oscillating member, and secondly oscillation maintenance means arranged to exert an impact. and / or a force and / or a torque on said oscillating member.

The invention also relates to a clockwork movement comprising at least one resonator mechanism arranged to oscillate around its natural frequency.

The invention also relates to a timepiece, including a watch, comprising at least one such movement.

The invention relates to the field of time bases in mechanical watchmaking.

Background of the invention

The search for improved performance of watch time bases is a constant concern.

An important limitation to the chronometric performance of mechanical watches is the use of conventional impulse exhausts, and no escape solution has ever been able to avoid this type of disturbance.

Summary of the invention

The invention proposes to manufacture a time base as accurate as possible.

For this purpose, the invention relates to a clockwork resonator mechanism with forced oscillation arranged to oscillate at a natural frequency and comprising on the one hand at least one oscillating member, and secondly oscillation maintenance means arranged for exerting an impact and / or a force and / or a torque on said oscillating member, characterized in that said oscillating member carries at least an oscillating regulating device whose natural frequency is a control frequency which is between 0.9 times and 1.1 times the value of an integer multiple of the eigenfrequency of said resonator mechanism, said integer being greater than or equal to 2.

According to one characteristic of the invention, said regulating device comprises, mounted pivotally on said oscillating member, at least one secondary balance spring with an eccentric unbalance relative to the secondary pivoting axis about which said secondary balance-spring pivots; .

According to one characteristic of the invention, said regulating device comprises at least one spring-feeder assembly comprising a feeder attached by a spring at a point of said oscillating member.

According to a characteristic of the invention, said regulating device comprises at least one blade or blade movable under the effect of aerodynamic variations and attached by a pivot or by an elastic blade or by an arm to said oscillating member.

The invention also relates to a watch movement comprising at least one resonator mechanism arranged to oscillate around its natural frequency, characterized in that said movement comprises at least one regulating device comprising means arranged to act on said resonator mechanism by imposing a periodic modulation of the resonance frequency and / or the quality factor and / or the rest point of said resonator mechanism with a control frequency which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency of said resonator mechanism, said integer being greater than or equal to 2.

According to a feature of the invention, said movement comprises at least one such resonator mechanism, said oscillating member carries at least one said regulating device.

According to a characteristic of the invention, said movement comprises at least one said regulating device distinct from one said at least one resonator mechanism, and which acts either by contact with or at a distance from at least one component of said resonator mechanism resonator by modulating an aerodynamic flow or a magnetic field or an electrostatic field or an electromagnetic field.

The invention also relates to a timepiece, including a watch, comprising at least one such movement.

Brief description of the drawings

• la figure 1 représente, de façon schématisée, partielle et en plan, un mécanisme résonateur paramétrique régulé selon l'invention, comportant un balancier-spiral d'horlogerie, constituant un résonateur, et dont l'inertie et/ou le facteur de qualité est modulé par des masses disposées radialement ou tangentiellement par l'intermédiaire de ressorts et excitées à une fréquence double de la fréquence du résonateur à balancier-spiral incorporant ce balancier, dont le spiral n'est pas représenté ; ce balancier porte sur sa serge des éléments vibrant radialement ou tangentiellement lors du mouvement de pivotement du balancier ;
• la figure 2 représente, de façon schématisée, partielle et en plan, un balancier comportant quatre ressorts radiaux liés à la serge et porteur de masses, et soumis à une excitation de régulation à une fréquence double de la fréquence du résonateur à balancier-spiral incorporant ce balancier, dont le spiral n'est pas représenté;
• la figure 3 représente, de façon schématisée, partielle et en plan, un balancier porteur de balanciers-spiraux embarqués présentant chacun un fort balourd, montés libres ;
• la figure 4 représente, de façon schématisée, partielle et en plan, un balancier suspendu par deux ressorts radiaux diamétralement opposés, la trajectoire du centre de gravité du balancier correspondant à la direction commune de ces deux ressorts ;
• les figures 5A, 5B, 5C représentent, de façon schématisée, partielle et en plan, un balancier portant sur sa serge des éléments qui pivotent lors du mouvement de pivotement du balancier ;
• la figure 6 représente, de façon schématisée, partielle et en plan, un balancier au voisinage duquel un patin faisant frein aérodynamique est mobile à une fréquence double de celle du résonateur à balancier-spiral incorporant ce balancier, dont le spiral n'est pas représenté ;
• la figure 7 représente un balancier similaire à celui de la figure 3, avec deux balanciers-spiraux à fort balourds, montés libres sur un même diamètre et dans une position d'alignement des balourds, différents (au point de repos) de ceux de la figure 3, et soit en phase, soit en alternance anti-phase;
• la figure 8 représente, de façon schématisée, partielle et en plan, un diapason dont un bras est en contact avec un patin frottant excité à une fréquence double de la fréquence du résonateur à diapason ;
• la figure 9 illustre un mécanisme résonateur comportant un balancier comportant une virole maintenant un fil de torsion, dont un dispositif régulateur commande une variation périodique de la tension avec une fréquence double de celle du résonateur à balancier et fil de torsion ;
• la figure 10 représente, de façon schématisée, un mécanisme résonateur paramétrique régulé selon l'invention, comportant un balancier-spiral d'horlogerie, dont la spire externe du spiral est fixée à un piton auquel un dispositif régulateur impose un mouvement périodique, ce piton étant mobile en translation, pivotement, et en inclinaison dans l'espace pour vriller le spiral si nécessaire;
• la figure 11 représente, de façon schématisée, un spiral équipé d'un mécanisme de raquetterie à goupilles, avec un système bielle-manivelle pour actionner un déplacement continu de la raquette, pour une variation continue de la longueur active du spiral;
• la figure 12 représente, de façon schématisée, un spiral sur lequel appuie une came, pour une variation continue de la longueur active du spiral et/ou de la position du point d'attache et/ou de la géométrie du spiral. Cette figure est une représentation simplifiée où une came unique appuie sur le spiral d'un côté seulement ; il est évidemment possible de combiner deux cames agencées pour pincer le spiral de part et d'autre;
• la figure 13 représente, de façon schématisée, et partielle, le spiral d'un ensemble balancier-spiral, avec une spire additionnelle fixée à ce spiral et venant en doublure localement avec la courbe terminale du spiral, et un dispositif régulateur actionnant une extrémité de cette spire additionnelle ;
• la figure 14 illustre un spiral avec, au voisinage de sa courbe terminale, une autre spire qui est maintenue à une première extrémité par un appui manoeuvré par un dispositif régulateur, et qui est libre à une deuxième extrémité agencée pour venir périodiquement en contact avec la courbe terminale sous l'action du dispositif régulateur sur cet appui ;
• la figure 15 illustre une régulation obtenue avec un résonateur du type de la figure 2 ;
• les figures 16A et 16B illustrent une modification du centre de gravité du résonateur, avec un résonateur à balancier-spiral comportant un balancier porteur de ressorts sensiblement radiaux fixés à la serge et porteurs de masselottes oscillantes, certains vers l'intérieur et d'autres vers l'extérieur de la serge ;
• les figures 17A et 17B illustrent, de façon analogue à la figure 5, un autre système à balancier à ailettes à pivot flexible permettant de modifier les pertes aérodynamiques et l'inertie ;
• les figures 18A à 18 D illustrent une modulation du centre de gravité, sur la base d'un résonateur tel celui de la figure 3 ou de la figure 7, comportant des balanciers-spiraux embarqués ;
• la figure 19 illustre un exemple de réalisation d'oscillateur paramétrique avec une virole de balancier porteuse d'un ressort en silicium porteur d'une masselotte périphérique alourdie par une couche d'or, l'ensemble ressort-masselotte oscillant à une fréquence de régulation ωR ;
• la figure 20 représente un balancier comportant des ensembles ressort-masselotte similaires à celui de la figure 19 ;
• la figure 21 représente un diapason dont une branche est porteuse d'un ensemble balancier-spiral secondaire monté fou en pivotement ;
• la figure 22 représente un diapason dont une branche est porteuse d'un ensemble ressort-masselotte monté libre en vibration ;
• la figure 23 représente, sous forme d'un schéma-blocs, une montre comportant un mouvement mécanique avec un mécanisme résonateur régulé selon l'invention par un dispositif régulateur à fréquence double.

Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, schematizing in a partial manner parametric oscillators corresponding to different modes and variants of implementation of the invention, and or :

• the figure 1 represents, schematically, partially and in plan, a regulated parametric resonator mechanism according to the invention, comprising a balance-spiral watchmaker, constituting a resonator, and whose inertia and / or the quality factor is modulated by masses arranged radially or tangentially by means of springs and excited at a frequency double the frequency of the spring-balance resonator incorporating this balance, the spiral of which is not shown; this balance carries on its serge elements vibrating radially or tangentially during the pivoting movement of the balance;
• the figure 2 represents schematically, partially and in plan, a rocker having four radial springs connected to the serge and carrying masses, and subjected to a regulation excitation at a frequency double the frequency of the spring balance resonator incorporating this beam, whose spiral is not represented;
• the figure 3 represents, schematically, partially and in plan, a pendulum carrying pendulum-spiral embedded each with a strong unbalance, mounted free;
• the figure 4 represents, schematically, partially and in plan, a rocker suspended by two radial springs diametrically opposed, the trajectory of the center of gravity of the balance corresponding to the common direction of these two springs;
• the FIGS. 5A, 5B, 5C represent, schematically, partially and in plan, a pendulum bearing on its serge elements that pivot during the pivoting movement of the balance;
• the figure 6 represents, schematically, partially and in plan, a balance wheel in the vicinity of which an aerodynamic brake pad is movable to a frequency twice that of the spring-balance resonator incorporating this balance, the spiral of which is not shown;
• the figure 7 represents a pendulum similar to that of the figure 3 , with two balances-spirals with great unbalance, mounted free on the same diameter and in a position of alignment unbalance, different (at the point of rest) from those of the figure 3 and either in phase or alternating anti-phase;
• the figure 8 represents, schematically, partially and in plan, a tuning fork whose arm is in contact with a friction pad excited at a frequency twice the frequency of the tuning fork resonator;
• the figure 9 illustrates a resonator mechanism comprising a balance having a ferrule holding a torsion wire, a regulating device of which controls a periodic variation of the voltage with a frequency twice that of the balance resonator and torsion wire;
• the figure 10 represents, schematically, a parametric resonator mechanism regulated according to the invention, comprising a balance-spiral watchmaker, the outer coil of the spiral is attached to a peak to which a regulating device imposes a periodic movement, this pin being movable in translation, pivoting, and tilting in space to twist the spiral if necessary;
• the figure 11 schematically represents a hairspring equipped with a pin-type reel mechanism, with a crank-handle system for actuating a continuous movement of the racket, for a continuous variation of the active length of the hairspring;
• the figure 12 schematically represents a hairspring supported by a cam, for a continuous variation of the active length of the hairspring and / or the position of the attachment point and / or the spiral geometry. This figure is a simplified representation where a single cam presses on the hairspring on one side only; it is obviously possible to combine two cams arranged to clamp the spiral on both sides;
• the figure 13 represents, in a schematic and partial manner, the hairspring of a balance-hairspring assembly, with an additional turn fixed to this hairspring and lining locally with the end curve of the hairspring, and a control device actuating an end of this additional turn ;
• the figure 14 illustrates a spiral with, in the vicinity of its terminal curve, another turn which is held at a first end by a support operated by a regulating device, and which is free at a second end arranged to periodically come into contact with the terminal curve under the action of the regulating device on this support;
• the figure 15 illustrates a regulation obtained with a resonator of the type of the figure 2 ;
• the Figures 16A and 16B illustrate a modification of the center of gravity of the resonator, with a sprung balance resonator comprising a rocker carrying substantially radial springs attached to the serge and carrying oscillating weights, some inwards and others to the outside of the serge;
• the Figures 17A and 17B illustrate, in a similar way to figure 5 , another balancing system with fins with flexible pivot for modifying aerodynamic losses and inertia;
• the Figures 18A to 18D illustrate a modulation of the center of gravity, on the basis of a resonator such as that of the figure 3 or from figure 7 , incorporating on-board spiral balances;
• the figure 19 illustrates an exemplary embodiment of a parametric oscillator with a bearing ferrule carrying a silicon spring carrying a peripheral weight weighted by a gold layer, the spring-motor assembly oscillating at a control frequency ωR;
• the figure 20 represents a pendulum comprising spring-weight assemblies similar to that of the figure 19 ;
• the figure 21 represents a tuning fork whose branch is carrying a secondary balance-spiral assembly mounted pivotally mad;
• the figure 22 represents a tuning fork whose branch is carrying a spring-flyweight assembly freely mounted in vibration;
• the figure 23 represents, in the form of a block diagram, a watch comprising a mechanical movement with a resonator mechanism regulated according to the invention by a dual frequency regulating device.

Detailed Description of the Preferred Embodiments

The object of the invention is to manufacture a time base for rendering a timepiece, in particular a mechanical timepiece, in particular a mechanical watch, as accurately as possible.

One way of doing this is to associate different resonators, either directly or via the exhaust.

To overcome the instability factor associated with an escape mechanism, a parametric resonator system makes it possible in particular to reduce the influence of this escapement mechanism, and thus make the watch more accurate.

A parametric oscillator uses, for the maintenance of oscillations, a parametric actuation which consists in varying at least one of the parameters of the oscillator with a regulation frequency ωR.

By convention and in order to distinguish them well, here is called "regulator" 2 the oscillator which serves for the maintenance and regulation of the other system maintained, which remains referred to as "the resonator" 1.

où T est l'énergie cinétique et V l'énergie potentielle et l'inertie I(t), la rigidité k(t) et la position de repos x ₀(t) dudit résonateur sont une fonction périodique du temps. x est la coordonnée généralisée du résonateur.
L'équation du résonateur paramétrique forcé et amorti est obtenue par l'équation de Lagrange pour la lagrangienne L en ajoutant un forçant f(t) et une force de Langevin prenant en compte les mécanismes dissipatifs : $$\frac{{\partial }^{2}x}{{\partial }^{2}t}+\gamma \left(t\right)\frac{\partial x}{\partial t}+{\omega }^2\left(t\right)\left[x-x_0\left(t\right)\right]=f\left(t\right)$$

où le coefficient de la dérivée du premier ordre en x est : $$\gamma \left(t\right)=\left[\beta \left(t\right)+\dot{I}\left(t\right)\right]/I\left(t\right),$$

β(t) > 0 étant le terme décrivant les pertes,
et où le coefficient du terme d'ordre nul dépend de la fréquence du résonateur $$\omega \left(t\right)=\sqrt{k\left(t\right)/I\left(t\right)}\mathrm{.}$$

La fonction f(t) prend la valeur 0 dans le cas d'un oscillateur non-forcé.
Cette fonction f(t) peut, encore, être une fonction périodique, ou encore être représentative d'une impulsion de type Dirac.The Lagrangian L of a parametric resonator of dimension 1 is: $$\mathrm{The}=T-V=\frac{1}{2}I\left(t\right){\dot{x}}^2-\frac{1}{2}k\left(t\right){\left[x-x_0\left(\mathrm{<figure-callout\; id="2"\; label="t"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">t</figure-callout>}\right)\right]}^2$$

where T is the kinetic energy and V the potential energy and the inertia I ( t ), the stiffness k (t) and the rest position x ₀ ( t ) of said resonator are a periodic function of time. x is the generalized coordinate of the resonator.
The equation of the forced and damped parametric resonator is obtained by the Lagrange equation for the Lagrangian L by adding a forcing f (t) and a Langevin force taking into account the dissipative mechanisms: $$\frac{{\partial }^{2}x}{{\partial }^{2}t}+\gamma \left(t\right)\frac{\partial x}{\partial t}+{\omega }^2\left(t\right)\left[x-x_0\left(t\right)\right]=f\left(t\right)$$

where the coefficient of the first-order derivative in x is: $$\gamma \left(t\right)=\left[\beta \left(t\right)+\dot{I}\left(t\right)\right]/I\left(t\right),$$

β (t) > 0 being the term describing the losses,
and where the coefficient of the zero-order term depends on the frequency of the resonator $$\omega \left(t\right)=\sqrt{k\left(t\right)/I\left(t\right)}\mathrm{.}$$

The function f (t) takes the value 0 in the case of a non-forced oscillator.
This function f (t) can, again, be a periodic function, or be representative of a Dirac type pulse.

The invention consists in varying, by the action of a maintenance oscillator called regulator, one and / or the other, or all, the terms β (t), k (t), l (t) ), x ₀ (t), with a control frequency ωR which is between 0.9 times and 1.1 times the value of a integer multiple, in particular double, of the natural frequency ω 0 of the oscillator system to be regulated.

où le terme du premier ordre en x est le terme de pertes, et où le terme d'ordre nul est le terme de fréquence du résonateur, et où x_o (t) correspond à la position de repos du résonateur.
La fonction f(t) prend la valeur 0 dans le cas d'un oscillateur non-forcé.
Cette fonction f(t) peut, encore, être une fonction périodique, ou encore être représentative d'une impulsion de type Dirac.To understand this phenomenon, we can approach the example of a pendulum whose length is varied. The equation of a damped oscillator is: $$\frac{{\partial }^{2}x}{{\partial }^{2}t}+\beta \left(t\right)\frac{\partial x}{\partial t}+{\omega }^2\left(t\right)\left[x-x_0\left(t\right)\right]=f\left(t\right)$$

where the term of the first order in x is the term of losses, and where the term of zero order is the frequency term of the resonator, and where x _o (t) corresponds to the rest position of the resonator.
The function f (t) takes the value 0 in the case of a non-forced oscillator.
This function f (t) can, again, be a periodic function, or be representative of a Dirac type pulse.

The invention consists in varying, by the action of a maintenance oscillator or regulator 2, one and / or the other, or all, the terms β (t), k (t), l ( t), x ₀ (t), with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple, this integer being greater than or equal to 2, in particular equal to 2, of the natural frequency ω0 of the oscillator system to be regulated, in this case the resonator 1. In a particular application, the regulation frequency ωR is between 1.8 times and 2.2 times the natural frequency ω0, and more particularly, the regulation frequency ωR is the double of the natural frequency ω0.

Preferably, one or more terms, or all the terms β (t), k (t), l (t), x ₀ (t), vary with a regulation frequency ωR thus defined, and which is preferably multiple integer , in particular double, of the natural frequency ω0 of the resonator system 1 to be regulated.

Generally, the maintenance oscillator or regulator, in addition to the modulation of the parametric terms, also introduces a non-parametric maintenance term f (t), the amplitude of which is negligible once the parametric regime is reached [WB Case, The pumping of a swing from the standing position, Am. J. Phys. 64, 215 (1996)].

Alternatively, the forcing term f (t) may be introduced by a second maintenance mechanism.

The maintenance oscillator or regulator 2 allows, again, to vary, if it is not zero, the term f (t).

In the example of the non-forced damped oscillator, and in the case where x ₀ is a constant, the parameters of the equation are summarized at the frequency term ω and at the end of losses β, in particular of losses by mechanical friction, or aerodynamic, or internal, or other.

The quality factor of the oscillator is defined by Q = ω / β.

avec L la longueur du pendule, et g l'attraction de la pesanteur.To better understand the phenomenon, we can approach the example of a pendulum whose length is varied. In that case, $${\mathrm{<figure-callout\; id="2"\; label="\omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\omega </figure-callout>}}^2=\frac{\mathrm{boy\; Wut}}{\mathrm{The}}$$

with L the length of the pendulum, and g the attraction of gravity.

In this particular example, if the length L is modulated in time periodically with a frequency 2ω and a modulation amplitude δL sufficient (δL / L> 2β / ω), the system oscillates at the frequency ω without amortizing.

In the particular example given of the pendulum, if the length L is modulated in time periodically with a frequency 2ω and a modulation amplitude δL sufficient (δL / L> 2β / ω), the system oscillates at the frequency ω without s' cushion.
[D. Rugar and P. Grutter, Mechanical parametric amplification and thermomechanical noise squeezing, PRL 67, 699 (1991), AH Nayfeh and DT Mook, Nonlinear Oscillations, Wiley-Interscience, (1977)].

The term of zero order can still take the form ω ² (A, t), where A is the amplitude of oscillation.

Thus, the invention relates to a method and a system for maintaining and regulating a clock resonator mechanism 1 around its natural frequency ω0. According to the invention is implemented at least one regulating device 2 acting on the resonator mechanism 1 with a periodic movement.

Thus, the invention relates to a method and a system for regulating a clock resonator mechanism 1 around its natural frequency ω0.

According to the invention, at least one regulating device 2 is printed which imparts periodic movement to at least one internal component of the resonator mechanism 1, or to an external component exerting an influence on such an internal component such as aerodynamic influence or braking. , or still modulating a magnetic or electrostatic or electromagnetic or similar field exerting a so-called recall force (to be taken here in a broad sense: of attraction or repulsion) on such an internal component of the resonator 1.

According to the invention, this periodic movement imposes a periodic modulation of the resonant frequency and / or the quality factor and / or the rest point of the resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a first particular embodiment of the invention, this periodic movement imposes a periodic modulation at least of the resonance frequency of the resonator mechanism 1, with such a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a second particular embodiment of the invention, this periodic movement imposes a periodic modulation at least of the quality factor of the resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a third particular embodiment of the invention, this periodic movement imposes a periodic modulation at least of the resting point of the resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

Of course, other particular embodiments of the invention allow the mixing of these first, second and third modes.

Thus, in a fourth particular mode of implementation of the invention combining the first and second modes, this periodic movement imposes a periodic modulation at least of the resonance frequency and the quality factor of the resonator mechanism 1, with a frequency of regulation ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a fifth particular mode of implementation of the invention combining the second and third modes, this periodic movement imposes a periodic modulation of at least the quality factor and the rest point of the invention. resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a sixth particular mode of implementation of the invention combining the first and third modes, this periodic movement imposes a periodic modulation at least of the resonance frequency and the rest point of the resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a seventh particular mode of implementation of the invention combining the first, second and third modes, this periodic movement imposes a periodic modulation of the resonance frequency and the quality factor and the rest point of the resonator mechanism 1, with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0, this integer being greater than or equal to 2.

In a particular implementation of these different modes of implementation of the method, all the modulations are made, either with the same frequency ωR, or with frequencies ωR multiples of each other.

Let us detail below the first three main modes of implementation of the invention.

In a particular embodiment of the first embodiment of the invention, this periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1, acting on the rigidity and / or the inertia of the resonator mechanism 1. More particularly this periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1, by imposing both a modulation of the rigidity of the resonator mechanism 1 and an inertia modulation of the resonator mechanism 1.

• Dans une première variante du premier mode, ce mouvement périodique impose une modulation périodique de la fréquence de résonance du mécanisme résonateur 1, en imposant une modulation de l'inertie du mécanisme résonateur 1 par modulation de la masse du mécanisme résonateur 1, et/ou par modulation de la forme du mécanisme résonateur 1 (tel que visible aux figures 1, 2, ou 3), et/ou par modulation de la position du centre de gravité du mécanisme résonateur 1 tel que visible par exemple sur le croquis de la figure 4.

Various advantageous variants allow different embodiments of the invention in this first mode:

• In a first variant of the first mode, this periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1, by imposing a modulation of the inertia of the resonator mechanism 1 by modulating the mass of the resonator mechanism 1, and / or by modulating the shape of the resonator mechanism 1 (as Figures 1, 2, or 3 ), and or by modulating the position of the center of gravity of the resonator mechanism 1 as visible for example on the sketch of the figure 4 .

Still in this first variant of the first mode, the Figures 16A and 16B also illustrate a modification of the center of gravity of the resonator, and also of its inertia.

Still in this first variant of the first mode, the Figures 18A to 18D illustrate a modulation of the center of gravity, on the basis of a resonator such as that of the figure 3 or from figure 7 . Such a system comprises embedded secondary balance-balance balances 260. These secondary spiral balances 260 are advantageously replaced by systems without axes, that is to say, flexible guidance, this all the more easily as the amplitude of their oscillation is not necessarily high. In this case, only the inertia of the main balance spring is modified. Depending on the angular position of the unbalance of the small balance-springs, it is thus possible to create a system whose center of gravity is modulated.

Such a modulation of the position of the center of gravity is preferably a dynamic modulation, acting on one or more of the components of the resonator 1. The modulation of inertia is achievable by modification of shape, by mass change, or by change of the center gravity of the resonator relative to its center of rotation, for example with the use of a flexible balance. It is still possible to use embedded resonators, with an asymmetry with an adequate phase ratio, as visible on the figure 7 , where the imbalances are either in phase or alternating anti-phase.

In a second variant of the first mode, this periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1, by imposing a modulation of the rigidity of an elastic return means that comprises the resonator mechanism 1 or a modulation of a return exerted by a magnetic or electrostatic or electromagnetic field within the resonator mechanism 1. More particularly, in this second variant, the periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1, by imposing a modulation of the length spring loaded by the oscillator mechanism 1 (as visible in FIGS. Figures 11 and 12 ), or a modulation of the section of a spring that the oscillator mechanism 1 (as visible Figures 13 and 14 ), or a modulation of the modulus of elasticity of a return means that the resonator mechanism 1, or a modulation of the shape of a return means that comprises the resonator mechanism 1. The modulation of the modulus of elasticity of a component of the resonator 1 can be obtained by the implementation of a piezoelectric system , of an electric field (electrodes), by a localized periodic heating, by the action of a magnetic field subjecting particular alloys to expansion, by opto-mechanical resonance systems, by torsion or by twisting, in particularly for shape memory materials.

In a third variant of the first mode resulting from a combination with the third embodiment of the invention, the periodic movement imposes a periodic modulation of the resonance frequency of the resonator mechanism 1 by imposing both a modulation of the rigidity of the resonator mechanism 1, and a modulation of the rest point of the resonator mechanism 1.

To act on the rigidity, it is advantageous to use magnetostriction phenomena, by modifying the rigidity periodically, by submitting a component, made in a suitable material, of the resonator 1 to a magnetic field (internal magnetization and / or field external), or shocks.

To act on the modulus of elasticity, it is also possible to use the magnetostriction phenomenon, but also to resort to a periodic rise in temperature, shape memory components, to the piezoelectric effect, or to the nonlinear regimes by the use of particular constraints.

• dans une première variante de ce deuxième mode, le mouvement périodique impose une modulation périodique du facteur de qualité du mécanisme résonateur 1, en agissant sur les pertes aérodynamiques du mécanisme résonateur 1, par modulation de la forme du mécanisme résonateur 1 (tel que visible en figure 5 sur un balancier muni d'ailettes pivotantes, ou en figure 17) et/ou par modification de l'environnement autour du mécanisme résonateur 1 (tel que visible en figure 6 où un patin animé d'un mouvement périodique modifie la circulation d'air autour du balancier) ;
• dans une deuxième variante de ce deuxième mode, le mouvement périodique impose une modulation périodique du facteur de qualité du mécanisme résonateur 1, en modulant l'amortissement interne des moyens de rappel élastique que comporte le mécanisme résonateur 1, par exemple avec une circulation de liquide dans un corps creux (par exemple le spiral ou le balancier d'un ensemble balancier-spiral), ou encore sous l'effet d'une torsion appliquée de façon périodique à un ressort-spiral ou similaire, entraînant à la fois des modifications induites de la rigidité et de l'amortissement du résonateur comportant ce ressort. Dans un cas particulier on peut modifier les pertes internes, sans modifier la rigidité : on substitue deux ressorts à un ressort unique de rigidité globale équivalente, les pertes internes sont alors supérieures ; on peut notamment mettre en série, ou en parallèle selon le cas, deux ressorts, dont l'un peut être précontraint. Un autre moyen de modifier les pertes tout en conservant la même rigidité est d'utiliser, sur un ressort, une compensation thermique (par dopage du silicium, ou par oxydation). On peut encore utiliser un effet thermo-élastique avec un transfert de chaleur entre deux parties différentes de la spire d'un ressort, cet effet thermo-élastique peut d'ailleurs être influencé par le niveau de dopage.
• dans une troisième variante de ce deuxième mode, le mouvement périodique impose une modulation périodique du facteur de qualité du mécanisme résonateur 1, en modulant les frottements mécaniques au sein du mécanisme résonateur 1, avec un effet analogue à une augmentation virtuelle de gravité. Un exemple est visible à la figure 8, où une lame frottante coopère, de façon modulée, avec un bras d'un diapason.

In a particular embodiment of the second embodiment of the invention, this periodic movement imposes a periodic modulation of the quality factor of the resonator mechanism 1, acting on the losses and / or the damping and / or the friction of the resonator mechanism 1 In particular we can act in different ways:

• in a first variant of this second mode, the periodic movement imposes a periodic modulation of the quality factor of the resonator mechanism 1, acting on the aerodynamic losses of the resonator mechanism 1, by modulating the shape of the resonator mechanism 1 (as visible in FIG. figure 5 on a rocker equipped with pivoting fins, or figure 17 ) and / or by modifying the environment around the resonator mechanism 1 (such as visible in figure 6 where a slider with a periodic movement modifies the air circulation around the balance);
• in a second variant of this second mode, the periodic movement imposes a periodic modulation of the quality factor of the resonator mechanism 1, modulating the internal damping of the elastic return means that comprises the resonator mechanism 1, for example with a circulation of liquid in a hollow body (for example the hairspring or the balance of a balance-hairspring assembly), or else under the effect of a twist applied periodically to a hairspring or the like, resulting in both induced changes the rigidity and damping of the resonator comprising this spring. In a particular case, the internal losses can be modified without modifying the rigidity: two springs are substituted for a single spring of equivalent overall stiffness, the internal losses are then greater; it is possible in particular to put in series, or in parallel as the case may be, two springs, one of which may be prestressed. Another way to modify the losses while maintaining the same rigidity is to use, on a spring, a thermal compensation (by silicon doping, or by oxidation). It is also possible to use a thermoelastic effect with a transfer of heat between two different parts of the coil of a spring, this thermoelastic effect can also be influenced by the doping level.
• in a third variant of this second mode, the periodic movement imposes a periodic modulation of the quality factor of the resonator mechanism 1, by modulating the mechanical friction within the resonator mechanism 1, with an effect similar to a virtual increase in gravity. An example is visible at the figure 8 , where a friction blade cooperates modulated with an arm of a tuning fork.

• plus particulièrement, dans une première variante de ce troisième mode, le mouvement périodique impose une modulation périodique du point de repos du mécanisme résonateur 1, par modulation de l'équilibre entre les forces de rappel agissant sur le mécanisme résonateur 1 générées par des moyens mécaniques de rappel élastique et/ou des moyens de rappel magnétiques et/ou des moyens de rappel électrostatiques. Pour moduler cet équilibre, le plus simple est de soumettre le résonateur à plusieurs forces de rappel d'origines différentes, dont il suffit de moduler au moins l'une dans le temps, en intensité et/ou en direction. Ces forces ne sont pas nécessairement toutes de même nature, certaines peuvent être mécaniques (ressorts) et d'autres liées à l'application d'un champ. Un exemple particulier est l'application à un balancier-spiral 3 équipé de deux spiraux, la modulation de position d'un seul des pitons suffit à moduler l'équilibre. Un vrillage d'un ressort-spiral, selon l'angle ψ de la figure 10, est un bon moyen de modifier le bilan des forces appliquées sur le résonateur 1, et donc de moduler leur équilibre. On note à ce propos qu'on peut appliquer les six degrés de liberté au piton, la figure représentant une application particulière simplifiée, et notamment la rotation autour de l'axe Z peut être avantageuse ;
• dans une deuxième variante de ce troisième mode, on combine la modulation du point de repos avec une modulation de la rigidité selon le premier mode : en effet, souvent, si on modifie l'équilibre des forces, on modifie aussi la rigidité globale. L'action de modulation sur le point de repos se combine alors avec une action de modulation de la rigidité.

In a particular embodiment of the third embodiment of the invention, this periodic movement imposes a periodic modulation of the rest point of the resonator mechanism 1, by modulation of the fixing position of the resonator mechanism 1 and / or by modulation of the equilibrium between the restoring forces acting on the resonator mechanism 1. The modulation of the fixing position of the resonator mechanism 1 can be exerted on at least one fixing point of this resonator 1. For example, on a resonator 1 with balance spring 3, it is possible to act on the pin and / or on the ferrule 7 for fixing the spring 4, on at least one point of pivoting by action on the anti-shock of the pivots. We can use for this purpose certain functions of the movement, for example in a conventional escapement mechanism, the percussion of the anchor on springs or the like.

• more particularly, in a first variant of this third mode, the periodic movement imposes a periodic modulation of the rest point of the resonator mechanism 1, by modulating the equilibrium between the restoring forces acting on the resonator mechanism 1 generated by mechanical means resilient return means and / or magnetic return means and / or electrostatic return means. To modulate this equilibrium, the simplest is to subject the resonator to several recall forces of different origins, of which it is sufficient to modulate at least one in time, intensity and / or direction. These forces are not necessarily all of the same nature, some may be mechanical (springs) and others related to the application of a field. A particular example is the application to a balance spring 3 equipped with two spirals, the modulation of position of only one of the pitons is enough to modulate the balance. Twisting of a spiral spring, according to the angle ψ of the figure 10 , is a good way to modify the balance of the forces applied on the resonator 1, and thus to modulate their equilibrium. It should be noted in this connection that the six degrees of freedom can be applied to the piton, the figure representing a particular simplified application, and in particular the rotation around the Z axis can be advantageous;
• in a second variant of this third mode, the modulation of the rest point is combined with a modulation of the rigidity according to the first mode: indeed, often, if the balance of forces is modified, the overall rigidity is also modified. The modulation action on the rest point then combines with a modulation action of the stiffness.

Preferably, when the component on which the rigidity can be modulated consists of several elements, the modulation is carried out on at least one of these elements.

In another embodiment of the invention, the periodic movement imposes a periodic modulation of the quality factor of the resonator mechanism 1, and according to the invention, the periodic movement is printed at the same regulation frequency ωR at the same time. one component of the resonator mechanism 1 and a mechanism generating losses on at least one component of the resonator mechanism 1.

In yet another embodiment of the invention, compatible with each of the various modes presented above, the regulator mechanism 2 imposes a periodic modification of the frequency of the resonator mechanism 1 having a greater relative amplitude than the inverse of the quality factor of the resonator mechanism 1.

In one embodiment of the invention easy to implement, such a regulator device 2 acts on at least one attachment of the resonator mechanism 1.

With regard to the frequency ωR, it is conceivable that the periodic modulation of the different characteristics: resonance frequency, quality factor, rest point, is done for each according to multiples different from the frequency ω0, (for example, a modulation rigidity with twice the base frequency and modulation of the quality factor at quadruple of the base frequency), this does not bring any particular advantage, because the maximum of the effect and stability of parametric amplification is obtained when the frequency is twice the base frequency. In addition, it is not easy to imagine a system for which each characteristic is modulated differently, unless there are a plurality of regulators 2, which would make the system complex. Also preferably, the modulation of all the parameters is done according to the same frequency ωR.

Different applications of the invention are possible.

In a conventional application, the invention is applied to a resonator mechanism 1 comprising at least one elastic return means 40, and at least one such regulator device 2 is actuated by controlling a periodic variation in the frequency of the resonator mechanism 1 and / or or the quality factor of this resonator mechanism 1.

In a usual application in watchmaking, the invention is applied to a resonator mechanism 1 comprising at least one balance-spring assembly 3 comprising a rocker arm 26 with at least one spiral 4 as an elastic return means 40. More particularly, such as visible on the figure 3 the inertia and the quality factor of the resonator mechanism 1 are modified by oscillating, by the regulating device 2, secondary balances 260 with residual high unbalance 261 mounted eccentrically on the balance 26, and oscillating as a function of the speed of the resonator 1.

In another variant of the application to a sprung balance assembly 3 comprising a rocker arm 26 with at least one spiral 4 as an elastic return means 40, the quality factor of the resonator mechanism 1 is modified by a modification of the friction in FIG. the air of the balance 26, generated by a local modification of the geometry of the balance 26 under the action of the regulating device 2, the device is here on the balance wheel 26. For example, as visible in FIG. figure 5 the rocker 26 may carry wing wings articulated at its periphery, in particular by flexible guides or the like, these fins being preferably reversible and can then rock entirely in the direction of movement. Preferably these fins are held by flexible blades. When the speed is intermediate the fins are close to the serge, according to the Figure 5A . When the speed is maximum according to the Figure 5B , an aerodynamic effect makes them get up (wing effect of plane), during the reversal the fins pass on the other side as visible on the Figure 5C . In this example, the inertia is modified with a frequency which is 4 times the natural frequency of the balance-spring resonator. An air-brake type air friction is thus obtained, with a flap on the periphery of the balance, having an influence on the quality factor and / or on the inertia. This flap can be pivotally mounted free, or pivoted and recalled by a spiral type spring or flexible guide or the like. One variant may consist of a variable geometry balance serge Thus, in such a variant, the quality factor of the resonator mechanism 1 is modified by a modification of the friction in the air of the balance 26 generated by a local modification of this geometry. pendulum 26 under the action of the regulator device 2. It will be noted that the regulator 2 can move independently of the speed of the regulator 1. A particular variant consists in combining this variant with the preceding variant of oscillating eccentric balance-spring balances 260.

In another variant where one plays on its environment rather than on the balance itself, one modifies the quality factor of the resonator mechanism 1 by a modification of the friction in the air of the balance 26 generated by a local modification of the geometry of the surrounding the balance 26 under the action of the regulating device 2, as visible in FIG. figure 6 where a slider with a periodic movement changes the air flow around the balance.

The invention is also applicable to resonator mechanisms 1 without mechanical return means. Thus, in particular applications, not illustrated, the periodic movement of the regulating mechanism 2 imposes the modulation of the frequency and / or the quality factor and / or the rest point of the resonator mechanism 1 by means of an electric force or magnetic or electromagnetic remote.

Another variant of application of the invention, visible in figure 9 relates to a resonator mechanism 1 comprising at least one rocker 26 comprising a ferrule 7 holding a torsion wire 46 which constitutes an elastic return means 40, wherein at least one regulating device 2 is actuated by controlling a periodic variation of the voltage of the Twisting wire 46. In a similar variant, the twist wire is replaced by a flexible guide.

Another variant of application of the invention, visible in figure 8 relates to a resonator mechanism 1 comprising at least one tuning fork, wherein at least one regulating device 2 is actuated by controlling a periodic variation of the frequency of the resonator mechanism 1 and / or the rigidity of at least one arm of the tuning fork defining the quality factor of the resonator mechanism 1. More particularly the regulating device 2 can act on the tuning fork, or / and on a mobile bearing a support on at least one arm of the tuning fork. It should be noted that such a tuning fork is not necessarily in the conventional form of a fork, and may take, among other possible forms, a heart shape or a shape of H.

Alternatively, the invention is still applicable to a resonator with a single arm, or a resonator working in torsion, or in elongation.

Advantageously, the invention makes it possible to use the regulating device 2 for starting and / or maintaining the resonator mechanism 1. Preferably, this regulating device 2 is in cooperation with a start-up and / or maintenance mechanism of the resonator mechanism 1 to increase the oscillation amplitude of the resonator 1.

The invention advantageously allows co-maintenance: low consumption standard maintenance, combined with the parametric process to support the oscillation. The regulator device 2 is used for the continuous maintenance of the resonator mechanism 1, alone or in cooperation with a start-up mechanism and / or impulse maintenance.

For example, such maintenance can be obtained with a balance spring system, comprising a balance comprising on its serge springs bearing oscillating weights, according to the configuration of the figure 2 . An anchor escapement, or the like, then makes it possible to excite oscillations of the balance and the small flyweights. The springs and the weights oscillate at a frequency, here double, of the natural frequency of the spiral balance. The weights oscillate by inertial coupling. The parametric effect takes place because the inertia of the pendulum then varies at a frequency twice that of the balance-spring. The figure 15 illustrates a regulation obtained with such a resonator. It should be noted that in this case, the aerodynamic losses are also modified.

Another example is to use a detent escapement, also counting, in cooperation with a regulating mechanism 2 acting on the rigidity of the hairspring 4 (with pins that move).

The invention also relates to a clockwork movement 10 comprising at least one resonator mechanism 1. According to the invention, this movement 10 comprises at least one such regulator device 2, arranged to act on the resonator mechanism 1, by imposing a periodic modulation of one or more physical characteristics of the resonator mechanism 1: resonant frequency and / or quality factor and / or quiescent point, with a control frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0 of the resonator mechanism 1, this integer being greater than or equal to 2.

In a variant, this regulator device 2 is arranged to act on the resonator mechanism 1 by directly impressing it with a periodic movement with such a regulation frequency ωR.

In a variant, this regulator device 2 acts on at least one attachment of the resonator mechanism 1, and / or on the frequency, in particular on the rigidity and / or the inertia, of the resonator mechanism 1, and / or on the quality factor of the resonator mechanism 1, and / or on the losses or friction of the resonator mechanism 1.

In a variant, this regulator device 2 acts on the resonator mechanism 1 by printing the periodic movement to a component of the resonator mechanism 1 and / or to a mechanism generating losses on at least one component of the resonator mechanism 1.

The invention also relates to a timepiece 30 comprising at least one such watch movement 10.

The few examples of parametric oscillators, illustrated here are not limiting. Some, like those of Figures 15 to 18 , can be introduced directly into existing movements, substituting standard components such as rockers, which is an advantage, because there is no questioning the design or manufacture of mechanical components of the movement concerned.

One of the advantages of these systems is to be able to operate a high frequency hairspring, despite the inherent decrease in exhaust performance.

The easiest principle to implement is to swing a part of the pendulum. These oscillations (at a frequency n ≥ 2 of the natural frequency of the sprung balance) modify either the inertia or the center of gravity, or the aerodynamic losses.

The figures illustrate simple, non-limiting examples of embodiments of the invention. Some can be implemented very simply, for example by substituting a particular pendulum for a standard pendulum.

These examples show that the constituents of the regulator 2 can be embedded on certain components of the resonator 1. In many cases, the invention does not require a secondary excitation circuit, it is the sizing of the regulator components that allows it to oscillate at a frequency ωR defined in its particular relation with respect to the natural frequency ω0 of the resonator 1.

The figure 1 represents a regulated parametric resonator mechanism 1 according to the invention, comprising a balance spring 3 with a balance 26 and a not shown spiral constituting a resonator. The inertia and / or the quality factor is modulated by flyweights 71 arranged radially or tangentially by means of springs 72, the latter fixed at points of connection 73 to the structure of the rocker 26, in particular its serge . These flyweights-spring assemblies are excited at a frequency twice the frequency ω0 of the resonator 1 with spring balance 3. The resonator 1 carries here the elements of the regulator 2 constituted by the flyweight-spring assemblies, which vibrate radially and / or tangentially during of the pivoting movement of the balance wheel 26. Some may in particular be guided in a track 74 that includes the balance 26. The radial vibration of the weights influences the inertia and the friction term, the tangential vibration affects the dynamic inertia. The rocker 26 again carries arms 85 carrying vibrating blades 84, which oscillate essentially radially. For a good efficiency of such a regulator 2, the springs 72 are preferably of large volume in comparison with the balance, their radial grip is for example of the order of the beam radius of the beam itself, or even more with example a radial grip of the spring 72 and the weight 71 equivalent to four times the radius of a ferrule 7.

Preferably, and this applies to all the examples, all the vibratory sets that the regulator has oscillate oscillate at the same frequency ωR defined by the invention. One can, again, admit that some of them oscillate at an integer multiple frequency of this frequency ωR defined by the invention in relation to the natural frequency ω0.

The figure 2 also represents a resonator 1 with a spring balance 3, whose balance 26 carries the elements of the regulator 2: four radial springs 72 connected to the serge at points 73 and bearing weights 71, and subjected to a control excitation at a double frequency of the frequency ω0 of the resonator 1. The figure 15 illustrates a regulation obtained with such a resonator.

• ou bien les balanciers-spiraux secondaires 260 sont entièrement libres en rotation, sans limitation d'amplitude, par exemple avec un pivotement mécanique classique ;
• ou bien les balanciers-spiraux secondaires 260 sont limités en amplitude, et sont par exemple réalisés monobloc avec le balancier 26 dans une exécution en silicium ou similaire, avec un pivot flexible, et donc une amplitude limitée.

The figure 3 represents a very easy solution of substitution of an existing balance, with a resonator 1 similar to those of Figures 1 and 2 , comprising a rocker 26 carrying onboard secondary balance balances 260 each having a large unbalance 261, mounted free in rotation. We can distinguish two embodiments:

• or else the secondary balance-springs 260 are completely free in rotation, without amplitude limitation, for example with a conventional mechanical pivoting;
• or the secondary spiral balances 260 are limited in amplitude, and are for example made integral with the balance 26 in a silicon implementation or the like, with a flexible pivot, and therefore a limited amplitude.

The figure 4 represents with a resonator 1 similar to those of the preceding figures, with a rocker 26 suspended from one or more structures 50 by two diametrically opposed substantially radial springs 51, the trajectory of the center of gravity of the balance 26 corresponding to the common direction of these two springs 51. In a variant, the axis of the balance is held by springs. In another variant, the rocker 26 is not pivoted with a conventional shaft, but only with flexible guides; the virtual axis of the balance is then defined by the direction of the springs. The figure is deliberately simplified with only two springs, it is naturally conceivable to suspend the balance 26 between three springs 51 or more. One-piece execution of all this set is possible, within the limit of the desired pivot amplitude for the balance 26. It is understood that a multi-level execution is possible, to distribute the functional components on different planes.

The FIGS. 5A, 5B, 5C represent, again a similar resonator 1 incorporating a beam 26 bearing on its serge fins 60, aerodynamic profile articulated at flexible pivots 81 on the beam of the balance 26, and which pivot during the pivoting movement of the balance 26, such as explained above. This configuration can operate in a vacuum, with a frequency of regulation of the double fins of the natural frequency ω0, or in the air, with a quadruple frequency of ω0.

The figure 6 represents a resonator 1 with a rocker 26. Here the regulator 2 is completely separated from the resonator 1: a shoe 82 in the vicinity of the sill of the rocker 26 is aerodynamic brake, is suspended by a spring 83 to a structure 50, and is movable to a frequency twice that of the resonator 1 with sprung balance incorporating this balance. This mobility can come from an external source of excitation, it can, again, come from a profile, for example toothed, of the balance rod, which creates a variation of air flow in the vicinity of the shoe 82.

The figure 7 represents a pendulum similar to that of the figure 3 , with two secondary balance-spring balances 260 with a large unbalance 261, mounted free on the same diameter and in an unbalance alignment position, different (at the point of rest) from those of the figure 3 , and either in phase or alternating anti-phase. Preferably, this embodiment is made of silicon or other similar micro-machinable material (in particular silicon oxide, quartz, "LIGA" ®, amorphous metal, or the like): the secondary balance-springs and their imbalances 261 are integral with the balance 26 relative to which they pivot by flexible links, and the unbalance alignment is the rest state of this structure. Such balance also represents a very easy alternative to an existing balance, to improve chronometric performance.

The figure 8 represents a tuning fork resonator 55 attached to a structure 50 and having an arm 56 in contact with a friction pad 57 excited at a frequency twice the frequency of the tuning fork resonator.

The figure 9 illustrates a resonator mechanism comprising a rocker 26 comprising a ferrule 7 holding a torsion wire 46, a regulator device 2 controls a periodic variation of the voltage with a frequency twice that of the resonator 1 with pendulum and torsion wire.

The figure 10 represents a parametric resonator mechanism 1 comprising a balance spring 3, whose outer coil 6 of the spiral 4 is fixed to a peak 5, to which a regulating device 2 imposes a periodic movement, this pin 5 being movable in translation, pivoting, and tilt in the space to twist the spiral 4 if necessary.

The figure 11 represents another resonator 1 with spring balance 3, with a hairspring 4 equipped with a racking mechanism with a racket 12 with pins 11, with a regulating system 2 with connecting rod-crank to actuate a continuous movement of the racket 12, for a continuous variation of the active length of the hairspring 4.

The figure 12 is similarly a spiral 4 on which a cam 14 driven in rotation by a regulator 2, for a continuous variation of the active length of the spiral 4 and / or the position of the point of attachment and / or the geometry of the spiral. This figure is a simplified representation where a single cam presses on the hairspring on one side only; it is obviously possible to combine two cams arranged to clamp the spiral 4 on both sides.

The figure 13 is similarly a hairspring 4, with an additional turn 18 fixed to this hairspring and lining locally with the end curve 17 of the hairspring, and a regulating device 2 actuating an end 18A of this additional turn 18.

The figure 14 further illustrates a hairspring 4, with, in the vicinity of its end curve 17, another turn 23 which is held at a first end 24 by a support 59 operated by a regulating device 2, and which is free at a second end 25 arranged to come periodically in contact with the terminal curve 17 under the action of the regulating device 2 on this support.

The Figures 16A and 16B illustrate a modification of the center of gravity of the resonator 1, with a spring balance resonator 3 comprising a rocker 26 carrying substantially radial springs 72 fixed to the serge and bearing oscillating weights 71, similar to the figure 2 but some inward and others outward of the serge. The associated centripetal or centrifugal effects allow the modulation of the position of the center of gravity of the resonator 1.

The Figures 17A and 17B illustrate, in a similar way to figure 5 , another variant of a balance system 26 to fins 80 with flexible pivot 81 for changing the aerodynamic losses and inertia.

The Figures 18A to 18D illustrate a modulation of the center of gravity, on the basis of a resonator such as that of the figure 3 or from figure 7 , comprising secondary balance-balances 260 unbalanced 261 embedded.

The figure 19 illustrates an exemplary embodiment of a parametric oscillator with a ferrule 7 carrying a balance spring 72 of silicon carrying a peripheral weight 71 weighed by a layer 75 of gold or other heavy metal obtained for example by galvanic deposition or other, the oscillating spring-motor assembly at a control frequency ωR. For example, ω0 = 10 Hz and ωR = 20 Hz. figure 20 shows a rocker 26 where such spring-weight assemblies extend from the ferrule 7 to the largest diameter of the serge.

The figure 21 represents a tuning fork 55 embedded in a support 50, and a branch 56 of which carries a secondary balance spring-balance 260, with an eccentric unbalance 261, pivotally mounted on this branch 56.

The figure 22 represents a tuning fork 55, a branch 56 of which carries a spring assembly 72 / counterweight 71 mounted freely in vibration.

The invention further relates, in an advantageous embodiment, to a forced oscillation clocking resonator mechanism 1 arranged to oscillate at a natural frequency ω0, and comprising at least one oscillating member 100, which preferably comprises a balance 26 or tuning fork 55 or a vibrating blade, or the like "and secondly oscillation maintenance means 200 arranged to exert an impact and / or a force and / or a torque on this oscillating member 100.

According to the invention, this oscillating member 100 carries at least one oscillating regulating device 2 whose natural frequency is a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the eigenfrequency ω0 of said resonator mechanism 1, this integer being greater than or equal to 2. The particular values of ωR with respect to the natural frequency ω0 preferably obey the particular rules stated above.

In a first variant, this regulating device 2 comprises at least one secondary balance-spring 260 pivoting about a secondary axis of pivoting, with an unbalance 261 eccentric with respect to this secondary pivoting axis of this secondary balance-spring 260, which is pivotally mounted on pivoting member 100.

In particular, the oscillating member pivots about a main pivot axis, and this at least one secondary balance spring 260 is of secondary axis eccentric with respect to the main pivot axis.

In a particular embodiment, the regulating device 2 comprises at least a first secondary balance spring 260 and a second secondary balance-spring 260 whose imbalances 261, in a state of rest in the absence of stress, are aligned with the axes of secondary pivoting secondary balances 260. And, more particularly, the oscillating member 10 pivots about a main pivot axis, and at least one said secondary balance-spring 260 is of secondary axis eccentric to the main pivot axis.

In an advantageous embodiment authorized by micromaterial technology, at least one such secondary balance-spring 260 pivots about a virtual secondary axis that define means of elastic retention that includes the oscillating member 10 for maintaining the balance -spiral secondary 260, and is limited in amplitude of movement relative to the oscillating member 10.

Advantageously, at least one such balance-secondary balance 260 is integral with the oscillating member 100.

More particularly, at least one said secondary balance spring 260 is integral with a rocker 26 that includes the oscillating member 100, or which constitutes this oscillating member 100.

In a second variant, the regulator device 2 comprises at least one spring-feeder assembly comprising a weight 71 attached by a spring 72 at a point 73 of the oscillating member 100.

In particular, the oscillating member 10 pivots about a main pivot axis, and at least one such spring 72 extends radially relative to this main pivot axis.

In a particular embodiment, the oscillating member 10 carries a plurality of such spring-feeder assemblies, whose springs 72 extend radially relative to the main axis of pivoting, and of which at least a first carries its weight 71 further away from the main pivot axis that its spring 72, and at least one other carries its weight 71 closer to the main pivot axis that its spring 72.

In particular, the oscillating member 10 pivots about a main pivot axis, and at least one such spring 72 extends in a direction tangential to the point 73, relative to the main pivot axis.

In particular, at least one such spring-feeder assembly is, outside its attachment point 73, free of movement with respect to the oscillating member 100.

In a particular embodiment, the spring-weight unit is movable in a limited manner by guide means that comprises said oscillating member 100, or flows in a track 74 that includes said oscillating member 100.

In a third variant, the regulating device 2 comprises at least one fin 80 or a blade 84 movable under the effect of aerodynamic variations and attached by a pivot 81 or by an elastic blade or by an arm 85 to the oscillating member 100.

In particular, in a particular embodiment, at least one fin 80 or blade 84 is pivotable relative to the pivot 81 or to the elastic blade or the arm 85 which supports it.

In an advantageous embodiment which allows an easy adaptation of the invention to existing movements, making it possible to significantly improve their chronometric performance at the lowest costs, the oscillating member 100 is a pendulum 26 subjected to the action of means oscillation maintenance 200 which are return means comprising at least one spiral 4 and / or at least one torsion wire 46.

In another particular embodiment, the oscillating member 100 is a tuning fork 55 of which at least one branch 56 is subjected to the action of the oscillation maintenance means 200.

It is understood that these different variants, non-limiting, can be combined with each other, and / or with other variants respecting the principles of the invention.

The invention also relates to a watch movement 10 comprising at least one resonator mechanism 1 arranged to oscillate around its own frequency ω0. According to the invention this movement comprises at least one regulator device comprising means arranged to act on this resonator mechanism 1 by imposing a periodic modulation of the resonant frequency and / or the quality factor and / or the rest point of the resonator mechanism. resonator mechanism 1 with a regulation frequency ωR which is between 0.9 times and 1.1 times the value of an integer multiple of the natural frequency ω0 of said resonator mechanism 1, this integer being greater than or equal to 2.

In a first variant, this movement 10 comprises at least one such resonator mechanism 1, whose oscillating member 100 carries at least one said regulating device 2.

In a second variant, this movement 10 comprises at least one such regulator device 2 distinct from such at least one resonator mechanism 1, and which acts, either by contact with at least one component of this resonator mechanism 1, or distance from this resonator mechanism 1 by modulating an aerodynamic flow or a magnetic field or an electrostatic field or an electromagnetic field.

Advantageously, this resonator mechanism 1 comprises at least one deformable component of variable rigidity and / or inertia, and this at least one regulating device 2 comprises means arranged to deform this deformable component to vary its rigidity and / or its inertia.

In a particular embodiment, this at least one regulator device 2 comprises means arranged to deform the resonator mechanism 1 and modulate the position of the center of gravity of this resonator mechanism 1.

In a particular embodiment, this at least one regulator device 2 comprises means generating losses on at least one component of this resonator mechanism 1.

In an advantageous embodiment because very easy to implement, the regulator device 2 comprises means for modulating an aerodynamic flow in the vicinity of the oscillating member 100, these modulation means comprising at least one shoe 83 suspended on a structure 50 by elastic return means 83.

The invention also relates to a timepiece 30, in particular a watch, comprising at least one such watch movement 10.

Naturally, the invention is perfectly applicable to another timepiece such as a clock. It is applicable to any type of oscillator comprising a mechanical oscillating member 100, and in particular to a pendulum.

The excitation at the frequency ωR as defined above, and more particularly at twice the frequency ω0, can be performed with a square or pulse signal, it is not essential to have a sinusoidal excitation.

The maintenance regulator does not need to be very precise: its possible lack of precision only results in a loss of amplitude, but without variation of the frequency except of course if this frequency is very variable, which is to avoid. In fact, these two oscillators, maintenance regulator and resonator maintained, are not coupled, but one of the two maintains the other, ideally (but not necessarily) one-way.

In a preferred embodiment, there is no coupling spring between this maintenance regulator 2 and the maintained resonator 1.

The invention differs from the coupled oscillators known moreover by the fact that the frequency of the regulator is double or multiple of the natural frequency of the resonator (or at least very close to such a multiple), as well as by the transfer mode of 'energy.

Claims (27)

Clockwise oscillating clock resonator mechanism (1) arranged to oscillate at a natural frequency (ω0) and comprising on the one hand at least one oscillating member (100), and on the other hand oscillating maintenance means ( 200) arranged to exert an impact and / or a force and / or a torque on said oscillating member (100), characterized in that said oscillating member (100) carries at least one oscillating regulating device (2) whose natural frequency is a control frequency (ωR) which is between 0.9 times and 1.1 times the value of an integer multiple of the eigenfrequency (ω0) of said resonator mechanism (1), said integer being greater than or equal to 2. Resonator mechanism (1) according to claim 1, characterized in that said regulating device (2) comprises, pivotally mounted on said oscillating member (100), at least one secondary balance-spring (260) with an unbalance (261). eccentric with respect to the secondary pivot axis about which pivots said secondary balance-spring (260). Resonator mechanism (1) according to claim 2, characterized in that said oscillating member (10) pivots around a main pivot axis, and in that said at least one secondary balance-spring (260) pivots about a secondary pivot axis eccentric with respect to said main pivot axis. Resonator mechanism (1) according to claim 2 or 3, characterized in that said regulating device (2) comprises at least a first secondary balance spring (260) and a second secondary balance-spring (260) which said unbalance (261) , in a state of rest in the absence of stress, are aligned with the secondary pivoting axes around which these secondary spiral rockers (260) pivot. Resonator mechanism (1) according to claim 4, characterized in that said oscillating member (10) pivots about a main pivot axis, and in that said at least one secondary balance-spring (260) pivots about a secondary pivot axis eccentric with respect to said main pivot axis. Resonator mechanism (1) according to one of claims 2 to 5, characterized in that at least one said secondary balance-spring (260) pivots about a virtual secondary axis that defines elastic holding means that includes said oscillating member (10) for maintaining said sprung balance secondary (260), and is limited in amplitude of movement with respect to said oscillating member (10). Resonator mechanism (1) according to one of claims 2 to 6, characterized in that at least one said secondary balance spring (260) is integral with said oscillating member (100). Resonator mechanism (1) according to one of claims 2 to 6, characterized in that at least one said secondary balance-spring (260) is integral with a rocker (26) that comprises said oscillating member (100). Resonator mechanism (1) according to claim 1, characterized in that said regulating device (2) comprises at least one spring-feeder assembly comprising a weight (71) attached by a spring (72) at a point (73) of said oscillating member (100). Resonator mechanism (1) according to claim 9, characterized in that said oscillating member (10) pivots about a pivot axis, and in that at least one said spring (72) extends radially with respect to said axis of rotation. pivoting. Resonator mechanism (1) according to claim 10, characterized in that said oscillating member (10) carries a plurality of said spring-feeder assemblies whose said springs (72) extend radially with respect to said pivot axis, and of which at least one door its said flyweight (71) farther from said pivot axis than said said spring (72), and at least one gate said said flyweight (71) closer to said pivot axis than said said spring (72). Resonator mechanism (1) according to claim 9, characterized in that said oscillating member (10) pivots about a pivot axis, and in that at least one said spring (72) extends in a direction tangential to said point (73) with respect to said pivot axis. Resonator mechanism (1) according to one of claims 9 to 12, characterized in that at least one said spring-feeder assembly is, outside its said attachment point (73), free movement relative to said body oscillating (100). Resonator mechanism (1) according to one of claims 9 to 12, characterized in that at least one said spring-motor assembly is movable in a limited manner by guide means that comprises said oscillating member (100), or circulates in a track (74) that comprises said oscillating member (100). Resonator mechanism (1) according to claim 1, characterized in that said regulating device (2) comprises at least one fin (80) or a blade (84) movable under the effect of aerodynamic variations and attached by a pivot (81) or by an elastic blade or by an arm (85) to said oscillating member (100). Resonator mechanism (1) according to claim 15, characterized in that said at least one fin (80) or blade (84) is pivotable relative to said pivot (81) or to said elastic blade or said arm (85) which supports it . Resonator mechanism (1) according to one of the preceding claims, characterized in that said oscillating member (100) comprises a rocker (26) or a tuning fork (55) or a vibrating blade. Resonator mechanism (1) according to one of the preceding claims, characterized in that said oscillating member (100) is a rocker (26) subjected to the action of oscillation maintenance means (200) which are means of reminder comprising at least one hairspring (4) and / or at least one torsion wire (46). Resonator mechanism (1) according to one of claims 1 to 17, characterized in that said oscillating member (100) is a tuning fork (55) of which at least one branch (56) is subjected to the action of said maintenance means oscillation (200). Clockwork movement (10) comprising at least one resonator mechanism (1) arranged to oscillate around its natural frequency (ω0), characterized in that said movement (10) comprises at least one regulating device (2) comprising arranged means to act on said resonator mechanism (1) by imposing a periodic modulation of the resonance frequency and / or the quality factor and / or the rest point of said resonator mechanism (1) with a control frequency (ωR) which is included between 0.9 times and 1.1 times the value of an integer multiple of the eigenfrequency (ω0) of said resonator mechanism (1), said integer being greater than or equal to 2. Clock movement (10) according to claim 20, characterized in that it comprises at least one said resonator mechanism (1) according to one of claims 1 to 20, said oscillating member (100) carries at least one said regulating device (2). Timepiece movement (10) according to claim 20 or 21, characterized in that it comprises at least one said regulating device (2) distinct from one said at least one resonator mechanism (1), and which acts either by contact with at least one component of said resonator mechanism (1), or remote from said resonator mechanism (1) by modulating an aerodynamic flow or a magnetic field or an electrostatic field or an electromagnetic field. Clockwork movement (10) according to one of claims 20 to 22, characterized in that said resonator mechanism (1) comprises at least one deformable component of variable rigidity and / or inertia, and in that said at least one a regulating device (2) comprises means arranged to deform said component to vary its rigidity and / or its inertia. Clockwork movement (10) according to one of claims 20 to 23, characterized in that said at least one regulating device (2) comprises means arranged to deform said resonator mechanism (1) and modulate the position of the center of gravity said resonator mechanism (1). Clockwork movement (10) according to one of claims 20 to 24, characterized in that said at least one regulating device (2) comprises means generating losses on at least one component of said resonator mechanism (1). Clockwork movement (10) according to one of claims 20 to 25, characterized in that said regulating device (2) comprises means for modulating an aerodynamic flow in the vicinity of said oscillating member (100) comprising at least one pad (83) suspended from a structure (50) by elastic return means (83). Timepiece (30), in particular a watch, comprising at least one watch movement (10) according to one of the preceding claims.

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