EP3316047A1 - Mechanical watch with isochronous rotary resonator, which is not position-sensitive - Google Patents

Abstract

Clock resonator mechanism (100), comprising a central mobile (30), fixed in rotation about an axis (D) of an input moving wheel (1) subjected to a driving torque, arranged to rotate continuously, and comprising, a plurality of N inertial elements (2), each movable in a degree of freedom with respect to the central mobile (30) and biased towards the axis (D) by elastic return means (4), said mechanism ( 100) having a rotation symmetry of order N, wherein said mechanism (100) comprises kinematic connection means between all the inertial elements (2), arranged to maintain, at all times, all the centers of mass of the inertial elements ( 2) at the same distance, R, from the axis (D), and where the elastic return means (4) cause an elastic potential such that: Vtot = E o 2. j (M j, R 2), - Vtot being the elastic potential, - £ j being the sum on the j of the quantity in parentheses, - É o being the speed of rotation that we see t impose, - R j = R being the position of the center of mass G j of the inertial element j of mass M j.

Description

Field of the invention

The invention relates to a resonator mechanism for a clockwork movement, comprising an input movable pivotally mounted about an axis of rotation and subjected to a driving torque, and comprising a central mobile, integral in rotation with said input mobile around said axis of rotation and arranged to rotate continuously, said resonator mechanism comprising a plurality of N inertial elements, each movable in at least one degree of freedom with respect to said central mobile, and biased towards said axis of rotation by biasing means elastic, which are arranged to cause a return force on the center of mass of said inertial element, said resonator mechanism having a symmetry of rotation of order N.

The invention also relates to a watch movement comprising at least one such resonator mechanism.

The invention also relates to a timepiece, including a watch, including such a watch movement.

The invention relates to the field of clock resonator mechanisms constituting time bases.

Background of the invention

Most of the current mechanical watches are equipped with a sprung balance and a Swiss lever escapement mechanism. The sprung balance is the time base of the watch. It is also called resonator.

• entretenir les va-et-vient du résonateur ;
• compter ces va-et-vient.

The escapement, meanwhile, performs two main functions:

• maintain the comings and goings of the resonator;
• count these back and forth.

In addition to these two main functions, the exhaust must be robust, withstand shocks, and avoid trapping the movement (overturning).

The Swiss lever escapement mechanism has a low fuel efficiency (about 30%). This low efficiency comes from the fact that the movements of the exhaust are jerky, that there are falls or path lost to accommodate the machining errors, and also because several components are transmitted their movement via inclined planes that rub against each other.

To constitute a mechanical resonator, an inertial element, a guide and an elastic return element are required. Traditionally, a spiral spring acts as an elastic return element for the inertial element that constitutes a pendulum. This rocker is guided in rotation by pivots which turn in smooth bearings in rubies. This gives rise to friction, and therefore to energy losses and disturbances, which depend on the positions, and which one seeks to suppress. The losses are characterized by the quality factor Q. We seek to maximize this Q factor.

Requirement EP2847547 BREGUET Watches describes a mechanism for regulating the pivoting speed, around a first pivot axis, of a moving part, in particular a ringing device, comprising a pivoting flyweight around a second pivot axis parallel to the first axis. The regulator comprises means for returning the weight to the first axis. When the mobile rotates at a speed below a set speed, the flyweight remains confined in a first volume of revolution about the first axis. When this mobile rotates at a speed greater than the set speed, the weight engages in a second volume of revolution around the first axis, contiguous and external to the first volume of revolution, and a peripheral portion of the counterweight cooperates in this second revolution volume with control means arranged to cause the braking of the mobile and reduce its slew rate to the set speed, and to dissipate excess energy. In particular the mobile is subjected to a braking torque by eddy currents.

Requirement EP14184155 in the name of ETA Manufacture Horlogère Suisse describes a watchmaking mechanism comprising, mounted mobile, at least pivotally relative to a plate, an escape wheel arranged to receive a motor torque via a train, and a first oscillator comprising a first rigid structure connected to the plate by first elastic return means. This regulator mechanism comprises a second oscillator comprising a second rigid structure connected to the first rigid structure by second elastic return means, and which comprises guide means arranged to cooperate with complementary guide means that comprises the escape wheel, synchronizing the first oscillator and the second oscillator with the wheel.

Requirement EP15153657 in the name of ETA Manufacture Horlogère Suisse describes a clock oscillator comprising a structure and primary resonators, temporally and geometrically out of phase, each comprising a mass biased towards the structure by an elastic return means. This clock oscillator comprises coupling means for the interaction of the primary resonators, comprising motor means for driving a mobile in motion which comprises driving and guiding means arranged to drive and guide an articulated control means with means for transmission each articulated, remote control means, with a mass of a primary resonator, and the primary resonators and the mobile are arranged such that the axes of the joints of any two of the primary resonators and the axis of articulation of the control means are never coplanar.

International demand PCT / EP2015 / 065434 The Swatch Group Research & Development Ltd describes a watch ensemble with a combined resonator with improved isochronism, at least two degrees of freedom, which comprises a first linear or rotary oscillator with reduced amplitude in a first direction, with respect to which oscillates a second linear oscillator or reduced amplitude oscillator in a second direction substantially orthogonal to the first direction, the second oscillator having a second mass carrying a slider. This watch assembly comprises a mobile arranged for the application of a torque to the resonator, this mobile having a groove in which the slider slides with minimal clearance. This slide is arranged for at least, or follow the curvature of the groove when it has one, or friction rub in the groove, or push the inner side surfaces that the groove comprises by magnetized or electrified surfaces that includes the slide.

The document FR630831A in the name of Schieferstein describes a method and a device for the transmission of power between mechanical systems or for the control of mechanical systems, where two oscillating motions of flexible mechanisms, forming a suitable angle between them, act on each other in such a way that oscillation takes place following a closed curve, and which, for the purpose of force transmission or control, is loosely coupled in accordance with a rotary motion. The associated return means are attached to the plate. The connecting elements between the masses are elastic, and therefore do not constitute kinematic linkage means.

The document EP3095011A2 and the document WO2015 / 104962 on behalf of EPFL on behalf of EPFL describe a mechanical isotropic harmonic oscillator, comprising at least one bond with two degrees of freedom, supporting a mass in orbit relative to a fixed base with springs having isotropic return properties and linear. More particularly, a plane spring stage forms a link with two degrees of freedom causing a purely translational movement of the mass in orbit, so that the mass moves along its orbit while maintaining a fixed orientation. In a variant, each spring stage comprises at least two parallel springs. Again, the springs or other associated return means are attached to the plate.

When a mass, guided in rotation about a fixed axis, and connected to this axis by a linear radial return spring, is driven in its rotation by a grooved wheel, if we fix on the mass a pin working in this groove if this mass is punctual, its trajectories are ellipses or circles, and are all isochronous. If the mass has rotational inertia, then only the circular trajectories are isochronous. Special conditions, quite difficult to develop, can stabilize the trajectories on circles, the resonator then remaining isochronous depending on the driving torque of the wheel.

Summary of the invention

• supprimer les perturbations dues aux frottements des pivots du résonateur pour augmenter son facteur de qualité ;
• supprimer les saccades de l'échappement afin d'augmenter le rendement du mécanisme, et notamment le rendement de la fonction d'entretien et de comptage, habituellement dévolue à un mécanisme d'échappement.

The present invention proposes to achieve two objectives, namely:

• remove disturbances due to friction of the pivots of the resonator to increase its quality factor;
• remove the saccade of the exhaust to increase the efficiency of the mechanism, including the performance of the maintenance and counting function, usually assigned to an exhaust mechanism.

To achieve these objectives, the invention proposes a rotary resonator mechanism according to claim 1.

Historically, watchmakers have not considered rotary resonators as the time base for watches because they are not usually isochronous, and they are sensitive to gravity.

Also a rotary resonator mechanism according to the invention is particularly designed to include guides, in which friction of guiding does not dissipate energy in steady state, thus improving the quality factor.

And, in this particular rotary resonator mechanism, the maintenance of the rotation is performed by a torque applied directly to a resonator shaft, thus avoiding the dynamic losses of a conventional anchor escapement.

• condition d'isochronisme : le mécanisme résonateur rotatif comporte une pluralité d'éléments inertiels mobiles, chacun rappelé vers un axe de rotation principal par des moyens de rappel élastique, dont l'effort élastique de rappel provoque sur le centre de masse de cet élément inertiel une force centrale d'intensité proportionnelle à la distance entre l'axe de rotation et ce centre de masse ;
• condition d'insensibilité aux positions : l'utilisation d'une pluralité d'éléments inertiels mobiles, chacun guidé de façon à pouvoir s'éloigner de l'axe de rotation, en combinaison avec :
  • ∘ ou bien une fréquence élevée, c'est-à-dire supérieure à 20 Hz, dans le cas d'une application à une montre ;
  • ∘ ou bien un mécanisme de liaison agencé pour forcer le centre de masse global (de l'ensemble de ces éléments inertiels) à rester sur l'axe de rotation quelle que soit l'amplitude, c'est-à-dire un lien cinématique qui force les centres de masse des différents éléments inertiels à être sur un même rayon, par rapport à l'axe de rotation, à chaque instant ;
• condition d'insensibilité aux chocs et perturbations : frottement radial permettant de ramener les centres de masse des éléments inertiels sur une trajectoire circulaire suite à une perturbation de trajectoire. Ce frottement radial peut être réalisé par frottement de l'air, frottement d'un pivot, d'une glissière, ou similaire.

To obtain a rotary resonator mechanism that can be used as a time base for a time instrument, the invention sets out to respect the main conditions:

• isochronism condition: the rotary resonator mechanism comprises a plurality of mobile inertial elements, each recalled towards a main axis of rotation by elastic return means, whose elastic return force causes on the center of mass of this inertial element a central force of intensity proportional to the distance between the axis of rotation and this center of mass;
• condition of insensitivity to the positions: the use of a plurality of moving inertial elements, each guided so as to be able to move away from the axis of rotation, in combination with:
  • ∘ or a high frequency, that is to say greater than 20 Hz, in the case of an application to a watch;
  • ∘ or a linking mechanism arranged to force the overall center of mass (of all these inertial elements) to remain on the axis of rotation regardless of the amplitude, that is to say a kinematic link which forces the centers of mass of the different inertial elements to be on the same radius, with respect to the axis of rotation, at each instant;
• condition of insensitivity to shocks and disturbances: radial friction making it possible to reduce the centers of mass of the inertial elements on a circular trajectory following a perturbation of trajectory. This radial friction can be achieved by friction of the air, friction of a pivot, a slide, or the like.

The invention also relates to a watch movement comprising at least one such resonator mechanism.

The invention also relates to a timepiece, including a watch, including such a watch movement.

Brief description of the drawings

• la figure 1 représente, de façon schématisée et en vue en plan, un mouvement mécanique d'horlogerie, comportant un barillet entraînant un rouage de finissage, qui entraîne un mobile d'entrée d'un mécanisme régulateur rotatif continu selon l'invention, dans une variante articulée comportant deux éléments inertiels portés par des bras montés pivotants par rapport à une structure commune tournant autour de l'axe de rotation du mobile d'entrée, chaque bras étant rappelé vers cet axe par des moyens de rappel élastique particuliers;
• la figure 2 représente, de façon similaire à la figure 1, un mécanisme dérivé de celui de la figure 1, comportant des moyens pour maintenir à tout instant les centres de masse des éléments inertiels à la même distance de l'axe de rotation de façon à rendre le mécanisme régulateur rotatif continu insensible aux effets du champ de gravité, ces moyens comportant ici un pantographe articulé ;
• la figure 3 est une variante du mécanisme de la figure 2, où les éléments inertiels sont combinés avec des bras adjacents du pantographe ;
• la figure 4 est une variante du mécanisme de la figure 3, où les bras sont tous remplacés par des éléments inertiels articulés sur un mobile central entraîné par le rouage, et un mobile central secondaire constituant ensemble une croix au coeur du pantographe ;
• la figure 5 est un schéma d'un losange formant demi-pantographe à côtés de dimensions quelconques, et la figure 6 est un schéma du même demi-pantographe montrant les coordonnées polaires du centre de masse d'un segment j ;
• la figure 7, similaire à la figure 6, concerne le cas particulier d'un demi-pantographe en losange isocèle régulier, où tous les bras entre articulations sont de longueur égale ;
• la figure 8 représente, de façon schématisée et en perspective, une autre variante, avec une structure voisine de celles des figures 3 et 4, dépourvue d'articulation à pivot, sauf au niveau de l'axe de rotation, et dont les bras constituant les segments du pantographe forment les éléments inertiels, et où les liaisons entre ces bras comportent des guidages flexibles à lames croisées en projection ;
• la figure 8A représente, de façon similaire à la figure 8, une variante avantageuse de réalisation comportant, en superposition, une structure supérieure monobloc, qui comporte toutes les lames supérieures, et une structure inférieure monobloc, qui comporte toutes les lames inférieures ; les figures 8B et 8C sont des vues de côté du mobile central et du mobile central secondaire de ce pantographe ;
• les figures 9 et 10 représentent, de façon schématisée, respectivement en plan et en perspective, une variante de liaison cinématique rigide entre deux éléments inertiels, comportant une roue dentée axiale folle, qui coopère en permanence avec deux secteurs dentés solidaires des éléments inertiels, lesquels sont articulés sur la structure commune par des guidages flexibles à lames croisées en projection ;
• la figure 11 représente, de façon schématisée et en vue en plan, une variante de pantographe, dont le mobile central est fixé au mobile d'entrée par une liaison élastique, et le mobile central secondaire est fixé au mobile d'entrée par une autre liaison élastique ;
• la figure 12 représente, de façon schématisée et en vue en plan, une autre variante de liaison cinématique en guidage linéaire radial, avec une barre de guidage radiale coulissant dans des alésages des éléments inertiels, les moyens de rappel élastique des éléments inertiels étant constitués par des ressorts en vé ;
• la figure 13 représente, de façon schématisée et en vue en plan, une autre variante encore, dans laquelle la liaison cinématique comporte des moyens de guidage curviligne, combinant une rainure courbe du mobile central, et un pion porté par l'élément inertiel concerné, et où les moyens de rappel élastique comportent deux lames élastiques parallèles l'une à l'autre, pour limiter le mouvement de chaque élément inertiel selon un seul degré de liberté ;
• la figure 14 représente, de façon schématisée et en vue en plan, une structure voisine de celle de la figure 9, comportant une roue dentée axial folle coopérant avec deux roues intermédiaires qui elles-mêmes engrènent avec des roues solidaires des éléments inertiels et des bras, lesquels sont articulés sur la structure commune par des ressorts de traction classiques ;
• la figure 15 représente, de façon schématisée et en vue en plan, une variante où la liaison cinématique est flexible, la structure commune étant une lame flexible qui porte les éléments inertiels, qui portent chacun un bras porteur d'un élément de crémaillère coopérant avec une roue folle axiale ;
• la figure 16 représente, de façon schématisée et en vue en plan, une variante de la figure 15, comportant des moyens de rappel élastique comportant, pour chaque élément inertiel, deux lames élastiques parallèles, pour limiter le mouvement de chaque élément inertiel selon un seul degré de liberté ;
• la figure 17 est un schéma-blocs représentant une montre comportant un mouvement qui comporte lui-même un mécanisme régulateur rotatif continu 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 represents schematically and in plan view, a mechanical clockwork movement, comprising a barrel driving a finishing train, which drives an input mobile of a continuous rotary regulating mechanism according to the invention, in an articulated variant having two inertial elements carried by arms pivotally mounted relative to a common structure rotating about the axis of rotation of the input mobile, each arm being biased towards this axis by particular elastic return means;
• the figure 2 represents, similarly to the figure 1 , a mechanism derived from that of the figure 1 , comprising means for maintaining at any moment the centers of mass of the inertial elements at the same distance from the axis of rotation so as to make the continuous rotary regulating mechanism insensitive to the effects of the gravity field, these means comprising here an articulated pantograph ;
• the figure 3 is a variant of the mechanism of the figure 2 , where the inertial elements are combined with adjacent arms of the pantograph;
• the figure 4 is a variant of the mechanism of the figure 3 , where the arms are all replaced by inertial elements articulated on a central mobile driven by the gear, and a secondary central mobile together constituting a cross in the heart of the pantograph;
• the figure 5 is a diagram of a rhombus forming half-pantograph with sides of any size, and the figure 6 is a diagram of the same half-pantograph showing the polar coordinates of the center of mass of a segment j;
• the figure 7 , similar to figure 6 relates to the particular case of a regular isosceles rhombus pantograph, where all the arms between joints are of equal length;
• l figure 8 represents, schematically and in perspective, another variant, with a structure similar to those of Figures 3 and 4 without pivot articulation, except at the level of the axis of rotation, and whose arms constituting the segments of the pantograph form the inertial elements, and where the connections between these arms comprise flexible guides with crossed blades in projection;
• the figure 8A represents, similarly to the figure 8 , an advantageous embodiment having, in superposition, a monobloc upper structure, which comprises all the upper blades, and a lower monobloc structure, which comprises all the lower blades; the Figures 8B and 8C are side views of the central mobile and the secondary central mobile of this pantograph;
• the Figures 9 and 10 schematically represent, respectively in plan and in perspective, a rigid kinematic link variant between two inertial elements, comprising a crazy axial gear, which cooperates permanently with two integral toothed sectors of the inertial elements, which are articulated on the structure common by flexible guides with crossed blades in projection;
• the figure 11 shows schematically and in plan view, a pantograph variant, whose central mobile is fixed to the input mobile by an elastic connection, and the secondary central mobile is fixed to the input mobile by another elastic connection;
• the figure 12 is schematically and in plan view, another kinematic connection variant in radial linear guide, with a radial guide bar sliding in bores of the inertial elements, the elastic return means of the inertial elements being constituted by springs in vé;
• the figure 13 represents, schematically and in plan view, yet another variant, in which the kinematic connection comprises curvilinear guide means, combining a curved groove of the central mobile, and a pin carried by the inertial element concerned, and where the resilient return means comprise two elastic blades parallel to each other, to limit the movement of each inertial element in a single degree of freedom;
• the figure 14 represents, schematically and in plan view, a structure similar to that of the figure 9 , comprising a crazy axial gear cooperating with two intermediate wheels which themselves mesh with integral wheels of the inertial elements and arms, which are articulated on the common structure by conventional tensile springs;
• the figure 15 represents, schematically and in plan view, a variant where the kinematic connection is flexible, the common structure being a flexible blade which carries the inertial elements, each carrying a carrying arm of a rack member cooperating with a idler wheel axial;
• the figure 16 represents, schematically and in plan view, a variant of the figure 15 , comprising elastic return means comprising, for each inertial element, two parallel elastic blades, for limiting the movement of each inertial element in a single degree of freedom;
• the figure 17 is a block diagram showing a watch having a movement which itself comprises a continuous rotary regulating mechanism according to the invention.

Detailed Description of the Preferred Embodiments

The invention relates to a resonator mechanism 100, provided for a watch movement 200 intended primarily to be integrated in a watch 300. Indeed, the resonator mechanism 100 according to the invention is designed to be isochronous, insensitive to positions in the field gravity, and, otherwise insensitive to shocks and disturbances, at least arranged to resume very quickly its normal operation.

This resonator mechanism 100 is a rotary resonator. It has the particularity to be devoid of usual exhaust mechanism, and to operate continuously. The absence of saccades can significantly improve the energy efficiency, compared with a conventional resonator-type sprung balance coupled with an escapement anchor.

This resonator mechanism 100 comprises an input mobile 1, pivotally mounted about an axis of rotation D. This input mobile 1 is subjected to a motor torque. The figure 1 illustrates a conventional configuration of a watch movement 200 which comprises energy storage and storage means 210, here including in a non-limiting manner a cylinder 211, arranged to drive conventionally a gear train 220, in particular a gear train, finishing, the most downstream element drives the input mobile 1, thus subjected to the torque of the finishing train.

According to the invention, the resonator mechanism 100 comprises a common structure, which is deformable or articulated, and which is integral in rotation with the input mobile 1 about the axis of rotation D. This common structure carries, or comprises, a plurality of inertial elements 2. And this common structure rotates continuously. There is no movement back and forth: once subjected to a motor torque, the common structure rotates in a single direction of rotation. This does not prevent the structure can be reversible, and able to turn in the other direction if it is subjected to a pair of opposite direction.

Each inertial element 2 is guided, according to at least one degree of freedom with respect to the common structure.

Each inertial element 2 is biased towards the axis of rotation D by elastic return means 4, which are arranged to cause a return force on the center of mass of this inertial element 2.

According to the invention, these elastic return means 4 are embedded in the rotary resonator mechanism 100.

This return force is directed towards the axis of rotation D, and has an intensity proportional to the distance R _G between the axis of rotation D and the center of mass of the inertial element 2 considered.

In a particular variant, the same elastic return means 4 are common to several inertial elements 2, and may in particular consist of a tension spring joining pins disposed on the inertial masses, or the like.

In another variant, illustrated in particular by the Figures 1, 2 , 12, 13 , 14 , where the resonator mechanism 100 is articulated, such elastic return means 4 are arranged between, on the one hand, the common structure, and on the other hand an inertial mass 2, or an arm 31, 32, carrying a inertial mass 2.

In yet another variant, as visible in the figure 15 , the common structure is elastically deformable, and constitutes such elastic return means 4.

The resonator mechanism 100 has a rotation symmetry of order N, N being the number of the inertial masses 2. This is not the case of the prior art mentioned above.

In a variant in which the resonator mechanism 100 is articulated, each inertial element 2 is guided, directly or indirectly, by means of arms or secondary articulated systems, with respect to the common structure by at least one guiding means 5.

The figure 1 illustrates an example where the common structure comprises a central mobile 30, which carries at its two ends, pivot pins 51, 52, about axes D31 and D32, and which respectively bear arms 31, 32, which are themselves carriers of inertial elements 2: 21 and 22, which, according to the alternative embodiment, can be, or else mounted idle on these arms 31, 32, at axes D1, D2, passing through their center mass, or mounted fixed relative to these arms.

In this variant of the figure 1 , the elastic return means 4 are in rotation, and separated: 41 and 42, arranged between, on the one hand, the central mobile 30 of the common structure 3 at the level of an inner fastener 410, 420, and on the other hand the arm 31, 32, at an outer attachment 411, 421.

It will be understood that each inertial element 2 may comprise a degree of freedom in rotation, as in most of the present figures, or else a degree of freedom in translation as in the figure 12 .

où :

• Vtot est le potentiel élastique, qui représente une énergie élastique,
• ∑j est la somme sur les j de la quantité entre parenthèses,
• ω₀est la vitesse de rotation qu'on veut imposer,
• Rj(βi) est la position du centre de masse de l'élément inertiel j, en fonction de la valeur du degré de liberté βi,
• Mj est la masse de l'élément inertiel j.

In the variant in which each inertial element 2 comprises a degree of freedom in rotation, more particularly, the elastic return means 4 cause an elastic potential, comparable to a total elastic potential energy, characterized by the following relation: $$\mathrm{Vtot}=\mathrm{½}\mathrm{.}{{\mathrm{\omega }}_{\mathrm{0}}}^{\mathrm{2}}\mathrm{.}\Sigma \mathrm{j}\left(\mathrm{mj}\mathrm{.}{\mathrm{R}}^{\mathrm{2}}\mathrm{j}\left(\mathrm{\beta i}\right)\right),$$

or :

• Vtot is the elastic potential, which represents an elastic energy,
• Σj is the sum on j of the quantity in parentheses,
• ω ₀ is the speed of rotation that we want to impose,
• Rj (βi) is the position of the center of mass of the inertial element j, as a function of the degree of freedom βi,
• Mj is the mass of the inertial element j.

We understand that in the articulated example of figure 1 , comprising two inertial elements 21 and 22, the resonator mechanism 100 according to the invention must control, at all times, three angles: that which the common structure 3 with a turntable of the watch movement, or the like, and those, β1 and β2, what do the centers of mass of the inertial elements 21 and 22 with respect to the common structure 3, with reference to the axes D31 and D32 of the respective guides 51 and 52. Of course, in the case of N inertial elements, it is a matter of piloting N1 + angles.

The system is self-regulated: under the effect of the torque imparted by the driving means of the movement, each inertial element tends to deviate from the axis of rotation D, to a radial position where the friction of the air print a resistive torque which balances, in a tangential direction, the effect of the torque applied to the input mobile 1, relative to the center of mass of the inertial element. In the radial direction, it is the centrifugal force which balances the radial component of the return force printed by the elastic return means 4. This double balance, tangential and radial, determines the radial position of the center of mass at all times. , according to the instantaneous value of the torque emitted by the motor means. The angular rotation speed is equal to the square root of the quotient of the stiffness of the elastic return means by the mass of the inertial element, whereas the instantaneous radius of the center of mass with respect to the axis of rotation D is equal at the square root of the quotient between the engine torque and the product of the angular velocity and the coefficient of friction between the ambient medium and the inertial element.

The centers of mass of the inertial elements tend to reach the axis of rotation D, when the drive means are at a standstill, this position corresponding to the exercise of a zero tensile force on the part of the elastic return means 4 It may be easier to make a resonator mechanism 100 where the inertial masses 2 approach the axis of rotation, especially if these inertial masses 2 are in the same plane, and come for example in contact with each other. other in a rest position, the elastic return means 4 being then assembled with a prestressing.

The disturbance due to the field of gravity tends, in certain positions of the watch 300, to differentiate the behavior of the inertial elements. For example, the figure 1 has a reference Z, in the plane of the sheet and directed towards the bottom of the sheet, which indicates the vertical of the place and the field of gravity, the inertial element 22 tends to deviate from the common structure 3, while the inertial element 21 tends to approach it. If the inertial elements 2 are completely free radially, they may be located on different radii with respect to the axis of rotation D.

It is therefore advantageous, to overcome this effect of the gravity field, to perform a transfer of motion reducing the number of degrees of freedom of each inertial element 2, and to establish a mechanical coupling which forces the radial position, relative to the axis of rotation D, of each inertial element 2 relative to the others. Thus, the overall center of mass of the entire resonator mechanism can remain on the axis of rotation D. Preferably, a symmetry is established with respect to the axis of rotation D.

For this purpose, the rotary resonator mechanism 100 advantageously comprises a kinematic connection, and more particularly a rigid kinematic connection, between at least two inertial elements 2, and preferably between all the inertial elements 2. This connection forces the inertial elements 2 to find at the same distance of the axis of rotation D, permanently. That is to say, the inertial elements 2 have only one degree of freedom with respect to the common structure 3.

This kinematic connection is useful for small frequencies, 2 to 5 Hz in particular. On the other hand, if the rotational speed of the common structure 3 is high, in particular corresponding to a period greater than or equal to 20 Hz, for example of the order of 50 Hz, the effect of the gravitational field is negligible compared to the effects of inertia, and such a kinematic connection is not essential. Such a very simple embodiment may be suitable for single-use applications, such as fireworks or the like. The kinematic connection becomes necessary, however, as soon as one seeks to achieve good chronometric performance, especially for use in a watch.

Various examples of such kinematic links are illustrated on the figures 2 , 3 , 4 , 8 , 9, 10 , 12, 13 , 14, 15 and 16 , and will be exposed later. Most of them are articulated rigid kinematic links, some of them illustrating flexible kinematic links.

The figure 2 illustrates, in an extended position, an advantageous embodiment of the invention, wherein the kinematic connection is made by means of a pantograph structure: the resonator mechanism 100 comprises a symmetrical pantograph articulated structure around the axis of rotation D, comprising at least all the inertial elements 2, articulated directly, or articulated indirectly via arms which are designated, according to the variants, by the marks 31, 32, 131, 132, 121, 122, 123, 124, around the central mobile 30 and a secondary central mobile 130 which is arranged to pivot about the axis of rotation (D and which constitutes a cross structure with the central mobile unit 30. "Arm" here means a component comprising two articulations.

Here is called "pantograph" a double articulated structure, about a central axis, the double diamond shape is more particularly illustrated in the figures; the half-pantograph is the part of the structure on one side of the central axis. The pantograph has two half pantographs, comprising common elements, forming a cross structure.

More particularly, this crossed structure formed by the central mobile 30 and the secondary central mobile 130 has its center of mass on the axis of rotation D.

So, on the figure 2 , the kinematic connection and the guides are made by combining, on the basis of the example of the figure 1 , a central mobile 30, a secondary central mobile 130 pivoting about the axis of rotation D at an axial pivot, the two arms 31 and 32 pivoted on the central mobile 30, two other secondary arms 131 and 132 rotated crazy , both on the secondary central mobile 130 about axes D131 and D132, at the level of non-detailed pivots, and on the inertial elements 21 and 22 at the axes D1 and D2, and the seven joints necessary for its operation, to form a pantograph having a rotation symmetry of order 2.

In a particular variant, the secondary central mobile 130 rotates crazy around the axis of rotation D.

The elastic return means 41 and 42 are the same as on the figure 1 , since the linkage formed by the two arms 131 and 132 around the secondary central mobile 130 is passive, its only function being to maintain the centers of mass of the inertial elements 21 and 22 in symmetry with respect to the axis of rotation D.

Naturally, as visible on the variants illustrated in Figures 3 and 4 some of the arms may be inertial elements. The variant of the figure 3 , very close to that of the figure 2 , illustrated in a folded position, combines the inertial element 21 and the secondary arm 131 to form an inertial element 121, and combines the inertial element 22 and the secondary arm 132 to form an inertial element 123, the arm 31 constituting an element inertial 122, and the arm 32 constituting an inertial element 124.

More particularly, all the inertial elements 2 are articulated directly on the central mobile 30 and the secondary central mobile 130. Thus, the variant of the figure 4 , very compact, comprises four inertial elements which also constitute arms 31, 32, 131, 132, articulated in pantograph around the central mobile 30 and the secondary central mobile 130.

The Figures 5 and 6 are diagrams of the semi-pantograph, with in figure 6 the polar coordinates of the center of mass of a segment j. The term "segment" is here referred to as the geometric definition of one side of the semi-pantograph diamond, and "arm" is used to designate the physical component incorporated in the mechanism.

avec les centres de masse G3 et G4 des segments 73 et 74 qui sont situés sur la droite qui lie les rotules de part et d'autre du segment concerné, respectivement A13 à A34, et A24 à A34.The figure 7 illustrates the particular case of an isosceles and regular diamond half pantograph, where: $${\mathrm{<figure-callout\; id="1"\; label="\beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{1}}={\mathrm{<figure-callout\; id="2"\; label="\beta "\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{2}}={\mathrm{<figure-callout\; id="3"\; label="\beta "\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{3}}={\mathrm{<figure-callout\; id="4"\; label="\beta "\; filenames="imgf0001.png,imgf0005.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{4}},$$

with the centers of mass G3 and G4 of the segments 73 and 74 which are situated on the line which links the ball joints on either side of the segment concerned, respectively A13 to A34, and A24 to A34.

(cette condition permet de garantir l'isochronisme d'un pantographe quelconque), où :

• V(β₁) est le potentiel en fonction de l'angle β₁,
• β₁ est l'angle d'ouverture du pantographe, c'est-à-dire l'angle entre d'une part la droite qui joint la pointe du pantographe opposée à l'axe de pivotement à l'axe de pivotement, et d'autre part le segment considéré, $${\mathrm{\omega }}_{\mathrm{0}}={\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{dt\; est\; la\; vitesse\; de\; rotation\; du\; mécanisme\; résonateur\; rotatif}\mathrm{100},$$
  
  est la vitesse de rotation du mécanisme résonateur rotatif 100,
• ∑j est la somme sur les j de la quantité entre parenthèses,
  Mj est la masse de l'élément inertiel 2 de rang j
  Rj(β₁) est la distance de l'axe de rotation au centre de masse Gj de l'élément inertiel 2 de rang j,
• R'j(β₁) est la dérivée de la distance entre l'axe de pivotement et le centre de masse de l'élément inertiel 2 de rang j par rapport à β₁.

In the case of any half-pantograph, as visible on the Figures 5 and 6 each member, in quadrilateral form, of the pantograph comprises four segments 71, 72, 73, 74, hinged together and with respect to a pivot axis consisting of a main ball 70 or the axis of rotation D. The central mobile 30 consists of two first segments 71 in the extension of one another relative to the main ball 70, and the secondary central mobile 130 consists of two second segments 72 in the extension of one another by relative to the main ball 70. And the elastic return means 4 generate a potential energy V which is a function of the angle of deformation β ₁ of the pantograph member, satisfying the relationship: $$\partial \mathrm{<figure-callout\; id="1"\; label="V\; \beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">V\; </figure-callout>}\left({\mathrm{\beta }}_{}\right)\left({\mathrm{}}_{\mathrm{1}}\right)/\partial {\mathrm{<figure-callout\; id="1"\; label="\beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{1}}=\mathrm{½}\mathrm{.}{\left({\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{<figure-callout\; id="2"\; label="dt"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">dt</figure-callout>}\right)}^{\mathrm{2}}\mathrm{.}\Sigma \mathrm{j}\left(\mathrm{mj}\mathrm{.}\mathrm{<figure-callout\; id="1"\; label="Rj\; \beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">Rj\; </figure-callout>}\left({\mathrm{\beta }}_{}\right)\left({\mathrm{}}_{\mathrm{1}}\right)\mathrm{.}\mathrm{R}\text{'}\mathrm{<figure-callout\; id="1"\; label="j\; \beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">j\; </figure-callout>}\left({\mathrm{\beta }}_{}\right)\left({\mathrm{}}_{\mathrm{1}}\right)\right),$$

(This condition guarantees the isochronism of any pantograph), where:

• V (β ₁ ) is the potential as a function of the angle β ₁ ,
• β ₁ is the opening angle of the pantograph, that is to say the angle between, on the one hand, the straight line joining the point of the pantograph opposite to the axis of pivoting to the pivot axis, and on the other hand the segment considered, $${\mathrm{\omega }}_{\mathrm{0}}={\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{dt\; is\; the\; speed\; of\; rotation\; of\; the\; <figure-callout\; id="100"\; label="rotating\; resonator\; mechanism"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">rotating\; resonator\; mechanism</figure-callout>}\mathrm{100},$$
  
  is the speed of rotation of the rotary resonator mechanism 100,
• Σj is the sum on j of the quantity in parentheses,
  Mj is the mass of the inertial element 2 of rank j
  Rj (β ₁ ) is the distance from the axis of rotation to the center of mass Gj of the inertial element 2 of rank j,
• R'j (β ₁ ) is the derivative of the distance between the pivot axis and the center of mass of the inertial element 2 of rank j with respect to β ₁ .

More particularly, the center of mass of each arm (31; 32; 131; 132; 121; 122; 123; 124) which is between two joints is located on a line joining the two joints on either side of the considered arm.

More particularly, and particularly in the variant of figures 4 and 7 each member of the semi-pantograph has four segments of equal length L, together constituting a regular diamond. And the center of mass of the central mobile 30 and that of the secondary central mobile 130 are on the axis of rotation D of the resonator mechanism 100, and the centers of mass of each of the inertial arms are on a line defined by the two joints of the corresponding arm.

où :

• β₁ est l'angle d'ouverture du pantographe,
• L est la longueur de chaque segment entre les articulations,
• M₃ est la masse d'un troisième segment 73 formant un des deux éléments inertiels opposés à l'axe de pivotement constitué par une rotule principale 70 ou par l'axe de rotation D, et compris entre une première rotule latérale A13 et une rotule de sommet A34 opposée à une rotule d'axe A12 constituant la rotule principale 70,
• M₄ est la masse d'un quatrième segment 74 formant l'autre des deux éléments inertiels opposés audit axe de pivotement, et compris entre une deuxième rotule latérale A24 et la rotule de sommet A34,
• R₃ est la distance de la première rotule latérale A13 au centre de masse G3 du troisième segment 73,
• R₄ est la distance de deuxième rotule latérale A24 au centre de masse G4 du quatrième segment 74,
• dα₀/dt est la vitesse de rotation du résonateur rotatif.

In particular, with reference to the ratings of the figure 7 , the potential energy V _tot elastic return means is connected to their angle of deformation by the relation: $${\mathrm{V}}_{\mathrm{<figure-callout\; id="1"\; label="early\; \beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">early\; </figure-callout>}}\left(\mathrm{\beta }\right)\left(\mathrm{}\mathrm{1}\right)=\mathrm{The}\left({\mathrm{<figure-callout\; id="3"\; label="M"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">M</figure-callout>}}_{\mathrm{3}}\mathrm{.}{\mathrm{<figure-callout\; id="3"\; label="R"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">R</figure-callout>}}_{\mathrm{3}}+{\mathrm{<figure-callout\; id="4"\; label="M"\; filenames="imgf0001.png,imgf0005.png"\; state="\{\{state\}\}">M</figure-callout>}}_{\mathrm{4}}\mathrm{.}{\mathrm{<figure-callout\; id="4"\; label="R"\; filenames="imgf0001.png,imgf0005.png"\; state="\{\{state\}\}">R</figure-callout>}}_{\mathrm{4}}\right)\mathrm{.}{\left({\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{<figure-callout\; id="2"\; label="dt"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">dt</figure-callout>}\right)}^{\mathrm{2}}\mathrm{.}\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">cos</figure-callout>}\mathrm{2}{\mathrm{<figure-callout\; id="1"\; label="\beta "\; filenames="imgf0004.png"\; state="\{\{state\}\}">\beta </figure-callout>}}_{\mathrm{1}}$$

or :

• β ₁ is the opening angle of the pantograph,
• L is the length of each segment between the joints,
• M ₃ is the mass of a third segment 73 forming one of the two inertial elements opposite to the pivot axis formed by a main ball 70 or the axis of rotation D, and between a first lateral ball joint A13 and a ball joint A34 vertex opposite to a ball joint A12 constituting the main ball 70,
• M ₄ is the mass of a fourth segment 74 forming the other of the two inertial elements opposite to said pivot axis, and between a second lateral ball joint A24 and the crown ball A34,
• R ₃ is the distance from the first lateral ball joint A13 to the center of mass G3 of the third segment 73,
• R ₄ is the distance of the second lateral ball joint A24 to the center of mass G4 of the fourth segment 74,
• dα ₀ / dt is the speed of rotation of the rotary resonator.

Such a pantograph type structure, combined with adequate elastic return means, thus constitutes a mechanism which, theoretically, makes it possible to guarantee the constancy of the rotation period of the input mobile 1, and to ensure the insensitivity to changes of position in the gravity field.

The practical implementation nevertheless requires performance precautions, because of the large number of articulation guides, synonymous with friction and loss of efficiency.

Other types of kinematic link will be presented later.

To overcome the cost of an articulated system, related to the machining precision and the parallelism of the axes, and the alteration of the yield by the friction pivots, a particular embodiment of the invention relates to a mechanism whose at least one of the guide elements and at least one of the elastic return means 4 are made jointly by a flexible guide. That is, the separate guiding and elasticity functions are provided by a single flexible guide. More particularly, with the exception of the guides at the level of the axis of rotation, all of the rotating guides and elastic return means is made by flexible guides.

More particularly, at least one such flexible guide comprises at least two blades included in planes, and which define one with the other the virtual axis of rotation of a flexible rotary guide.

More particularly, in a pantograph type structure as described above, at least four of its joints are made by rotating flexible guides.

The figure 8 illustrates a structure similar to those of Figures 3 and 4 , devoid of pivot articulation, except at the axis of rotation D, and whose arms 31, 131, 32, 132 constituting the segments of the pantograph form the inertial elements. In this nonlimiting variant, the flexible guides each comprise two blades, arranged in parallel and distinct levels, and which, in projection on a parallel plane, intersect at the axes of articulation D31, D1, D131, D132, D2 , and D32.

A simple realization is illustrated in Figures 8A, 8B and 8C , and consists of the superposition of a monobloc upper structure 101, which includes all the upper blades 103, and a monobloc lower structure 102, which includes all the lower blades 102. These upper structure 101 and lower structure 102 may be very easily assembled to one another, by gluing, riveting, or other, and the radial positions of the different joints, and the symmetry of the inertial elements, relative to the axis of rotation D, are fully guaranteed.

More particularly, these flexible guides rotating between two components are of the type crossed blades in projection, as explained above, whose opening angle θ, read on the plane of projection between the axis of crossing C and the points of embedding of the blades on one of the components, has a value of 40 ° +/- 4 °, and the blades crossing at a proportion of length of 0.15 +/- 0.015. This crossing can be performed both near the most mobile component, that is to say the race is the most important, the least mobile component, and it is in determined by the dimensioning of the components to ensure the required distance between the points of embedding of the blades.

More particularly, the flexible guides are made of oxidized silicon to compensate for the thermal effects.

The Figures 9 to 16 illustrate several variants to guarantee the radial symmetry of movement of the centers of mass of the inertial elements, as the case on the basis of articulated rigid kinematic links, or of flexible kinematic links.

The achievement of Figures 9 and 10 comprises, to establish the rigid kinematic connection between the inertial elements 2 (21 and 22) is carried out by means of a toothed wheel 60 mounted concentrically crazy to the axis of rotation D, and which cooperates permanently with two toothed sectors 61 and 62 are integral with the inertial elements 21 and 22. These are represented here hinged on the common structure 3 by such flexible guide blades crossed projection 41 and 42.

In a particular variant of the pantograph type structure, comprising a central mobile 30 and a secondary central mobile 130, the central mobile 30 is fixed to the mobile entrance 1 by an elastic connection 80, and the secondary central mobile 130 pivots around the axis of rotation D, but this pivoting is limited by an elastic connection 80 connecting it to the mobile input 1. In this particular variant illustrated by the figure 11 , the central mobile 30 and the secondary central mobile 130 are each subjected to a driving torque equivalent to half the equivalent exhaust torque in a conventional exhaust mechanism.

More particularly, this elastic connection 80 is a flexible rotary guide, in particular comprising two resilient blades.

The figure 12 illustrates another variant, in which the kinematic connection comprises radial linear guide means 90, with a radial guide bar 91 sliding in bores 911 and 912 of the inertial elements 21 and 22. The elastic return means 4 are constituted here by each time by a mainspring 41, 42.

The figure 13 illustrates another variant, in which the kinematic connection comprises curvilinear guide means 95, combining a curved groove 35 of the central mobile 30, and a pin 25 carried by the inertial element 21, 22, concerned. In this variant, the elastic return means 4 comprise, for the suspension and the return of each inertial element 21, 22, two elastic blades 45 and 46 substantially parallel to each other, so as to limit the movement of each inertial element 21, 22, in a single degree of freedom.

The figure 14 represents a structure similar to that of the figure 9 , comprising a gear 60 mounted concentrically concentrically to the axis of rotation D, and which cooperates continuously with two intermediate wheels 610 and 620, which themselves meshing with wheels or toothed sectors 61 and 62 integral with the inertial elements 21 and 22 and arms 31 and 32. These are shown here articulated on the common structure 3 by conventional tensile springs.

The figure 15 illustrates a variant where the kinematic connection is not rigid, but flexible, the common structure 30 being a flexible blade which carries the inertial elements 21 and 22, each carrying a carrier arm of a rack member 161, 162, which It cooperates with an axial impeller 60. In this very simple mechanism, the inertial elements 21 and 22 can, however, move in two degrees of freedom.

The realization of the figure 16 solves this problem, through employment, as in the realization of the figure 13 , resilient return means 4 which comprise, for the suspension and the return of each inertial element 21, 22, two elastic blades 45 and 46 substantially parallel to each other, so as to limit the movement of each inertial element 21, 22, according to a single degree of freedom.

In a particular embodiment, the complete resonator mechanism 100 (guiding, inertial element, elastic return means, arm, mobile) is in one piece. It is possible to realize the multi-level DRIE machined silicon rotary resonator, for example. When this execution is inconvenient, especially when using crossed blades in different levels, it is advantageous, as in the case of figure 8A superimposing a monoblock top structure 101 and a monobloc lower structure 102, each simple to manufacture, and which can be easily assembled to one another by gluing, riveting, screwing or otherwise. More particularly, the monobloc upper structure 101 and the one-piece lower structure 102 are irreversibly joined to one another to create an integral, unbreakable component.

In a particular variant, the rotation frequency of the rotary resonator mechanism 100 is greater than 20 Hz, and especially greater than 50 Hz. This relatively high frequency makes it possible to limit the sensitivity to positions in the gravitational field, in the case where there is no kinematic connection.

It is understood that the invention, designed for the counting of time, is also usable for other mechanisms, such as a ring regulator, or other. The elastic return means of the invention are embedded in the rotary resonator, which simplifies its construction.

In addition, the kinematic linkage means of the invention reduce the number of degrees of freedom of the system by completely linking the displacement of the masses, whereas in the prior art, the link is flexible and can not reduce the number of degrees of freedom.

The invention also relates to a watch movement 200 comprising a platen carrying energy storage and storage means 210, in particular at least one barrel 211, arranged to conventionally drive a gear train 220, in particular a work train , whose most downstream element is arranged to drive the mobile input 1 of such a rotary resonator mechanism 100, that includes this movement 200.

The invention also relates to a timepiece, in particular a watch 300, comprising at least one watch movement 200, and / or such a rotary resonator mechanism 100.

• suppression du mécanisme d'échappement traditionnel, permettant une simplification du mécanisme;
• suppression du travail du frottement des pivots d'un balancier-spiral, permettant d'augmenter le facteur de qualité du mécanisme résonateur ;
• suppression des saccades de l'échappement, permettant d'augmenter le rendement ;
• augmentation de la réserve de marche et/ou de la précision des montres mécaniques actuelles.

This invention has various advantages, including:

• removal of the traditional escape mechanism, allowing simplification of the mechanism;
• eliminating the work of the friction of the pivots of a sprung balance, making it possible to increase the quality factor of the resonator mechanism;
• suppression of saccades of the exhaust, allowing to increase the yield;
• increase of the power reserve and / or accuracy of current mechanical watches.

For a given movement size, it is possible to quintuple the autonomy of the watch, and to double the regulating power of the watch. That is to say that the invention allows a gain of a factor 10 on the performance of the movement.

Claims (24)

Resonator mechanism (100) for a watch movement, comprising an input mobile (1), pivotally mounted about an axis of rotation (D) and subjected to a driving torque, and comprising a central mobile (30), integral in rotation with said input mobile (1) around said axis of rotation (D) and arranged to rotate continuously, said resonator mechanism (100) comprising a plurality of N inertial elements (2), each movable relative to said central mobile (30), and biased towards said axis of rotation (D) by elastic return means (4) that comprises said resonator mechanism (100), which are arranged to cause a return force on the center of mass of said inertial element ( 2), said resonator mechanism (100) having a rotation symmetry of order N, characterized in that said resonator mechanism (100) comprises kinematic connection means between all said inertial elements (2) and which are arranged to maintain, at any moment , all the centers of mass of said inertial elements (2) at the same distance from said axis of rotation (D), and further characterized in that said elastic return means (4), which are rotated and embedded by said resonator mechanism ( 100), provoke an elastic potential characterized by the following relation: $$\mathrm{V}=\mathrm{1}/\mathrm{2.}{\left({\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{dt}\right)}^{\mathrm{2}}\mathrm{.}\Sigma (\mathrm{mj}{\mathrm{R}}^{\mathrm{2}}$$

or : - This is the elastic potential, - Σj is the sum of the quantity in parentheses, - (dα ₀ / dt) is the speed of rotation that we want to impose, - Rjest the distance from the axis of rotation to the center of mass G of said inertial element (2) - M is the mass of said inertial element. Resonator mechanism (100) according to claim 1, characterized in that said resonator mechanism (100) comprises a pantograph articulated structure about said axis of rotation (D), comprising at least all said directly articulated inertial elements (2), or articulated indirectly via arms (31; 32; 131; 132; 121; 122; 123; 124), around said central mobile (30) and a secondary central mobile (130) arranged to pivot about said axis of rotation; rotation (D) and which constitutes with said central mobile (30) a cross structure. Resonator mechanism (100) according to claim 2, characterized in that said crossed structure constituted by said central mobile (30) and said secondary central mobile (130) has its center of mass on said axis of rotation (D). Resonator mechanism (100) according to claim 2 or 3, characterized in that each member of said pantograph comprises four segments (71, 72, 73, 74) hinged together and with respect to a pivot axis consisting of a main ball joint ( 70) or said axis of rotation (D), said central mobile (30) consisting of two first segments (71) in the extension of one another relative to said main ball (70), and said central mobile secondary (130) being constituted by two second segments (72) in the extension of one another with respect to said main ball (70), and in that said elastic return means 4 generate a potential energy V which is function of the angle of deformation β _{1 of} said pantograph member, satisfying the relation: $$\partial \mathrm{V}\left({\mathrm{\beta }}_{\mathrm{1}}\right)/\partial {\mathrm{\beta }}_{\mathrm{1}}=\mathrm{½}\mathrm{.}{\left({\mathrm{d\alpha }}_{\mathrm{0}}/\mathrm{dt}\right)}^{\mathrm{2}}\mathrm{.}\Sigma \mathrm{j}\left(\mathrm{mj}\mathrm{.}\mathrm{Rj}\left({\mathrm{\beta }}_{\mathrm{1}}\right)\mathrm{.}\mathrm{R}\text{'}\mathrm{j}\left({\mathrm{\beta }}_{\mathrm{1}}\right)\right),$$

or : V (β ₁ ) is the potential as a function of the angle β ₁ , - β ₁ is the angle of opening of the pantograph, that is to say the angle between on the one hand the line joining the tip of the pantograph opposite to the axis of pivoting to the axis of pivoting, and on the other hand the segment considered, dα ₀ / dt is the rotational speed of said rotary resonator mechanism (100), - Σj is the sum on j of the quantity in parentheses, Mj is the mass of the inertial element 2 of rank j, Rj (β ₁ ) is the distance from the axis of rotation to the center of mass Gj of the inertial element 2, R'j (β ₁ ) is the derivative of the distance between the pivot axis and the center of mass of the inertial element 2 with respect to β ₁ . Resonator mechanism (100) according to one of claims 2 to 4, characterized in that said articulated structure constitutes a pantograph symmetric about said axis of rotation (D), or symmetry of rotation of order 2 about said axis of rotation (D). Resonator mechanism (100) according to one of claims 2 to 5, characterized in that all said inertial elements (2) are articulated directly on said central mobile (30) and said secondary central mobile (130). Resonator mechanism (100) according to one of claims 2 to 6, characterized in that the center of mass of each said arm (31; 32; 131; 132; 121; 122; 123; 124) which is between two joints , is located on a straight line joining the two joints on either side of said arm considered. Resonator mechanism (100) according to one of claims 2 to 7, characterized in that each member of said pantograph comprises four segments of equal length constituting together a regular diamond. Resonator mechanism (100) according to claims 7 and 8, characterized in that the potential energy V _{tot of} said elastic return means (4) is connected to their angle of deformation by the relation: V _tot (β1) = L (M ₃ R ₃ + M ₄ R ₄ ). (dα ₀ / dt) ² . cos 2β ₁ , where: - β ₁ is the opening angle of the pantograph, which is the angle between on the one hand the straight line joining the pantograph tip opposite the pivot axis to the pivot axis, and on the other hand the segment considered, - L is the length of each segment between the joints, M ₃ is the mass of a third segment (73) forming one of the two inertial elements opposite to the axis of pivoting formed by a main ball joint (70) or by said axis of rotation (D), and between a first lateral ball joint (A13) and a crown ball (A34) opposite to an axis ball joint (A12) constituting said main ball joint (70), - M ₄ is the mass of a fourth segment (74) forming the other of the two inertial elements opposite to said pivot axis, and between a second lateral ball (A24) and said crown ball (A34), R ₃ is the distance from the first lateral ball (A13) to the center of mass G3 of said third segment (73), R ₄ is the distance of the second lateral ball (A24) to the center of mass G4 of said fourth segment (74), dα ₀ / dt is the speed of rotation of the rotary resonator. Resonator mechanism (100) according to one of claims 2 to 9, characterized in that said central mobile (30) and said secondary central mobile (130) are each fixed to said input mobile (1) by an elastic connection (80 ). Resonator mechanism (100) according to claim 10, characterized in that said elastic connection (80) is a flexible rotary guide comprising two resilient blades. Resonator mechanism (100) according to claim 2 or one of the dependent claims, characterized in that each said inertial element (2) is guided, directly or indirectly through arms or secondary articulated systems, relative to to the common structure by at least a guide means (5), and in that at least one of the guide elements (5) and at least one of said elastic return means (4) are jointly made by a flexible guide. Resonator mechanism (100) according to claim 12, characterized in that , with the exception of the guides at said axis of rotation (D), all of the rotating guides and resilient return means (4) that includes said mechanism resonator (100) is provided by flexible guides. Resonator mechanism (100) according to claim 12 or 13, characterized in that at least one said flexible guide comprises at least two resilient blades included in planes, and which define with each other the virtual rotation axis d a flexible rotary guide. Resonator mechanism (100) according to one of claims 2 to 11, characterized in that , in said pantograph type structure, at least four of its joints are formed by rotary flexible guides according to claim 14. Resonator mechanism (100) according to claim 14 or 15, characterized in that at least one said flexible guide rotatable between two components is a crossblade guide projection on a projection plane, the opening angle θ, read on the plane of projection between the axis of intersection C projections of said blades on said plane and the mounting points of the blades on one of the components, has a value of 40 ° +/- 4 °, and the blades intersect at a proportion of length of 0.15 +/- 0.015. Resonator mechanism (100) according to one of claims 12 to 15, characterized in that said flexible guides are made of oxidized silicon to compensate for thermal effects. Resonator mechanism (100) according to one of claims 1 to 17, characterized in that said kinematic connecting means between all of said inertial elements (2) comprise at least one idler wheel (60) mounted concentrically crazy to said axis of rotation (D ), and which cooperates continuously with a toothed sector or a rack (61, 62) that each said inertial element comprises. Resonator mechanism (100) according to one of claims 1 to 17, characterized in that said kinematic connection means comprise radial linear guide means (90), with a radial guide bar (91) sliding in bores (911 , 912) that comprise said inertial elements (2). Resonator mechanism (100) according to one of claims 1 to 19, characterized in that said complete resonator mechanism (100) is in one piece. Resonator mechanism (100) according to one of claims 1 to 19, characterized in that said resonator mechanism (100) comprises flexible guides with crossed blades in different levels, and comprises, superimposed, and assembled one to the another, an integral monobloc structure (101) having all the upper blades (103), and a monobloc lower structure (102) having all the lower blades (102). Resonator mechanism (100) according to one of claims 1 to 21, characterized in that the rotation frequency of said rotary resonator mechanism (100) is greater than 20 Hz. Timepiece movement (200) comprising a rotary resonator mechanism (100) according to one of claims 1 to 22, and comprising a platen carrying energy accumulation and storage means (210) or at least one barrel ( 211), arranged to drive a gear train (220) arranged to drive the input mobile (1) of said rotary resonator mechanism (100). Watch (300) comprising at least one watch movement (200) according to claim 23.

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