CH710160A2 - Device controller of walking a mechanical watch movement. - Google Patents

Abstract

The regulating device (2) for the operation of a mechanical clockwork movement comprises: a frame (4); a resonator fixed to the frame and comprising a first annular magnetic structure (8) having a first number N1 of magnets arranged regularly in a circle and an elastic structure (20, 21, 22); a second annular magnetic structure (14) having a second number N2 of magnets and defining a central axis (16) around which it rotates, N2 being different from N1. The resonator is arranged such that a resonance mode in which the first magnetic structure undergoes a curvilinear, preferably substantially circular, translation around the central axis, is excited by the rotation of the second magnetic structure. The two magnetic structures define a cycloidal magnetic gear so that the regulating device incorporates a frequency reducer between the resonant frequency and the rotation frequency of the second magnetic structure integral with an escape wheel.

Description

Technical area

The present invention relates to the field of devices regulating the relative angular velocity between a magnetic structure and a resonator magnetically coupled to define together such a regulator device.

In particular, the invention relates to a mechanical watch movement equipped with a regulating device of its operation which is formed by a resonator and a magnetic exhaust associated with this resonator. By escapement, it is generally understood in the field of watchmaking a system formed by a maintenance mechanism of the periodic movement of a resonator resonance mode and by a period counting mechanism of this periodic movement to clock the drive of a device, in particular a display of at least one temporal information. It should be noted that the maintenance mechanism and the counting mechanism are generally formed by one and the same energy distribution mechanism, provided by a motor device, which performs both functions; as is the case in the context of the present invention.

In particular, the invention relates to magnetic regulating devices for mechanical watch movements in which there is provided a direct magnetic coupling between a resonator and an annular magnetic structure.

Finally, the invention relates to a watchmaking device in which the escape wheel has a continuous rotation, that is to say not jerky as is the case in conventional regulators formed of a pendulum -spiral and a Swiss lever escapement forming a stop and a toothed escape wheel.

Technological background

In the field of the mechanical watch, it is generally used regulating devices formed of a swinging balance spring and an escapement, in particular Swiss anchor, comprising a retainer, including an anchor, and a wheel of toothed exhaust, the stopper being an intermediate member between the balance and the escape wheel and oscillating synchronously with the balance. The stop has a back and forth movement with periods of rest, which generates a jerky advance of the escape wheel. These regulating devices, although having been perfected in a remarkable manner in the development of traditional watchmaking, have a rather poor performance due in particular to the oscillating movement of the anchor with its two extreme rest positions where it blocks the wheel. exhaust. We also know the cylinder escapement, which is without anchor. In the latter case, the stopper device is integrated in an open tube forming the balance shaft. The escape wheel also has a jerky advance and the efficiency is greatly reduced by the fact that the teeth of this escape wheel press successively and alternately against the inner wall and the outer wall of the open tube.

It has also been known for many years devices for regulating the speed of a wheel, also called rotor, by a magnetic coupling, also called magnetic coupling, which solve the disadvantages of the aforementioned traditional devices. The watch application is also known, but industrial achievements are rare or nonexistent. Numerous patent applications relating to this field have been filed by Horstmann Clifford Magnetics for C. F. Clifford's inventions. In particular, documents FR 1.113.932 and US 2,946,183 are mentioned. It is also known from the Japanese utility model JPS 5 263 453 U (application No. JP19 750 149 018 U) a magnetic escapement of the same type with a direct magnetic coupling between a resonator and an escape wheel formed by a disc supporting two annular magnetic coaxial tracks. These two magnetic tracks are substantially contiguous and each comprise magnetic high permeability platelets forming magnetic zones which are regularly arranged with a given angular period, the platelets of the first track being shifted or out of phase by half a period relative to the platelets. the second track. Between the platelets are provided non-magnetic zones, that is to say areas with low magnetic permeability. Areas of high magnetic permeability are thus alternately distributed on one side and the other of a circle corresponding to the rest position of at least one magnet carried by the end of a branch of a resonator of the tuning fork type. The magnet of the resonator is magnetically coupled to these two out-of-phase tracks so that it is alternately attracted by the magnetic zones of the first track and the second track. The escape wheel thus rotates with a speed of rotation such that it advances an angular period of the two tracks at each oscillation of the resonator. What is remarkable in such a system is the absence of mechanical friction in the magnetic escapement and the fact that the escape wheel has a substantially continuous rotation in a single direction of rotation.

It will be noted that the above-mentioned magnetic type regulating devices are provided for resonators having a single degree of freedom for each part undergoing a resonance movement. In general, the resonator is arranged so that the magnet, carried by a member undergoing a resonance movement, oscillates in a substantially radial direction, that is to say substantially orthogonal to the two annular magnetic tracks. In this case, the embodiments mentioned in the prior art have the advantage of having a frequency reduction between the frequency of the oscillation of the resonator and the rotation frequency (in revolutions / s) of the escapement wheel carrying the magnetic structure. No rotated mobile turns or oscillates at a frequency of the order of magnitude of the resonant frequency. The reduction factor is given by the number of angular periods of the annular magnetic tracks.

However, the advantage resulting from a reduction in frequency between the oscillation of the resonator and the rotation of the escape wheel has a corollary which poses a problem for the strength of the magnetic coupling given the dimensions of a classic watch movement. Indeed, to increase the frequency reduction it is necessary to increase the number of periods of the magnetic tracks. For a given diameter of the escape wheel, an increase in the number of periods results in a decrease in the area of the magnetic zones of the annular tracks. Since the magnet of the resonator generally extends over an angular distance less than half a period of the annular tracks, the dimensions of this magnet must also decrease as the frequency reduction increases. It is therefore understood that the magnetic interaction force between the resonator and the escape wheel decreases; which limits the engine torque that can be applied to the escape wheel and therefore increases the risk of loss of synchronization between the resonator and the escape wheel, also called stall of the regulating system. Synchronization here comprises a proportional relationship determined between the resonance frequency and the rotation frequency of the escape wheel.

Summary of the invention

The present invention aims to provide a new type of device for regulating the movement of a watch movement in which the resonator has a resonance mode that can have a frequency greater than the rotation frequency or oscillation of the mobiles. of this clock movement and in which all the moving parts have a continuous movement in the same direction.

For this purpose, the present invention relates to a device for regulating the running of a mechanical watch movement, this regulating device comprising: a chassis; a resonator fixed to the frame and comprising a first annular and periodic magnetic structure having a first integer number N1 of angular periods and defining a first central axis, this first magnetic structure forming the inertial portion of the resonator; a second annular and periodic magnetic structure having a second integer number N2 of angular periods and defining a second central axis, the second number N2 being different from the first number N1, this second magnetic structure being arranged so as to be rotatable relative to the frame around the second central axis which has a determined position relative to this frame.

At least one magnetic structure among the first and second magnetic structures has in each of its angular periods a magnetic material. The resonator is arranged so that it has a resonance mode in which the first magnetic structure follows a curvilinear trajectory, notably substantially circular, relative to the frame around the second central axis with a resonance frequency F1 without this first magnetic structure rotating. on itself relative to this frame (in other words, the first magnetic structure undergoes a curvilinear translation about the second central axis). The first and second magnetic structures are arranged to have a magnetic interaction between them such that the aforementioned relative rotation of the second magnetic structure, by applying a motor torque in a useful range of the driving torque, excites said resonance and in such a way that the frequency F2 of this relative rotation of the second magnetic structure and the resonance frequency F1 have between them a RFrdetermined ratio, ie RFr = F1 / F2, which is equal to the second integer number N2 divided by the difference ΔN between this second number N2 and the first number N1, ie ΔN = N2-N1 and RFr = N2 / ΔN. In a particular variant, the magnetic material of said at least one magnetic structure has an axial magnetization.

In a main embodiment, the resonator comprises an elastic structure connecting the first structure to the frame, this elastic structure being arranged so that the first magnetic structure has a rest position in which the first and second central axes are substantially confused, and so as to exert a return force (centripetal force) substantially in the direction of the second central axis regardless of the angular position of the first magnetic structure relative to the second central axis. In a preferred variant, the restoring force of the elastic structure is provided substantially isotropically and substantially proportional to the distance between the first and second central axes. A substantially isochronous system is thus obtained.

In an improved embodiment, the regulating device of the invention further comprises a mechanical anti-stall system of the synchronization between the first and second magnetic structures which is formed by a planetary gear with a satellite wheel provided. a first gear and rotating inside a ring provided internally with a second toothing. The satellite wheel is associated with the structure having the lower number of angular periods among the first and second magnetic structures and the ring is associated with the other structure having the greater number of angular periods. Then, the structure associated with the second magnetic structure is integral in rotation with this second structure. It is expected that, at least in an upper zone of the useful range of the engine torque, the upper value of which defines the maximum value of this useful range, the first and second teeth penetrate at least partially into one another. These first and second sets of teeth are configured and arranged relative to each other so that, within said useful range, they do not touch one another, the coupling between the first and second magnetic structures being purely magnetic in this useful range.

In a main variant, the ratio RZ between the number Z1 of teeth of the toothing of the ring gear and the number Z2 of teeth of the toothing of the satellite wheel is equal to the ratio RM * between the greater number of angular periods and the lower number of angular periods.

According to a particular variant of the above-mentioned improved embodiment, said useful range of the engine torque is a first useful range of purely magnetic coupling of the first and second magnetic structures, the maximum value of this first useful range being less than a value of stall of this purely magnetic coupling. The regulating device also operates in a second useful range of the engine torque, greater than the first useful range and contiguous thereto, corresponding to a useful magneto-mechanical coupling range in which the first and second sets of teeth mesh with the first one. other so that one exerts a mechanical drive torque on the other. The first and second teeth are configured and arranged relative to each other so that, at least in a lower zone of the second useful range whose lower value defines the minimum value of this second useful range, these first and second teeth have a radial clearance allowing an increase in the amplitude of the curvilinear translation generated in said excited resonance mode during an increase in the engine torque. Finally, the elastic structure is arranged so that it has a substantially elastic deformation, preferably purely elastic, in the first and second useful ranges of the engine torque applied to the regulating device.

According to an improved variant, the first toothing of the satellite wheel is arranged relative to the second toothing of the ring so that, in an area of the useful range of the engine torque in which these first and second sets of teeth present a penetration without contact, teeth of the first toothing located in corresponding spaces of the second toothing, in the area where the first and second teeth are radially closest, are substantially centered within a given total tangential clearance for a shift relative angular medium, between the angular periods of the first magnetic structure and the angular periods of the second magnetic structure, within a relative angular offset range defined by a variation of the motor torque in said useful range.

The invention also relates to a mechanical watchmaking movement comprising a regulating device according to the invention, a counter wheel clocked by this regulating device and a motor device driving the counter wheel and maintaining a resonance mode of the regulating device.

Other particular features of the invention will be described below in the detailed description of the invention.

Brief description of the drawings

The invention will be described below with the aid of the accompanying drawings, given by way of non-limiting examples, in which: <tb> Fig. 1 <SEP> shows in perspective a first embodiment of a regulating device according to the invention; <tb> fig. 2 <SEP> shows in plan the resonator of the regulating device of FIG. 1; <tb> figs. 3A to 3D <SEP> are four schematic representations respectively of four successive positions of the regulator device in a variant of the first embodiment; <tb> fig. 4 <SEP> shows in perspective a second embodiment of a regulating device according to the invention; <tb> fig. <SEP> is a top view of the regulating device of FIG. 4; <tb> fig. 6 <SEP> is a section along the line VI-VI of FIG. 5; <tb> fig. 7 <SEP> is a schematic plan view of a first variant of a third embodiment; <tb> fig. <SEP> is a schematic plan view of a second variant of the third embodiment; <tb> fig. 9 <SEP> is a schematic plan view of a third variant of the third embodiment; <tb> fig. <SEP> is a schematic plan view of a fourth variant of the third embodiment; <tb> fig. SEP shows in perspective a fourth embodiment of a regulating device according to the invention; <tb> fig. 12 <SEP> is a section of FIG. 11 according to a section plane comprising the central axis of rotation; <tb> figs. 13A and 13B <SEP> show the regulating device of the fourth embodiment in two successive positions.

Detailed description of the invention

With the help of FIGS. 1, 2 and 3A to 3D, a first embodiment of the invention will be described. The regulator device 2 comprises: a chassis 4; a resonator 6 fixed to the frame and comprising a first annular and periodic magnetic structure 8 having a first integer number N1 of angular periods P1 and defining a first central axis 10, this first magnetic structure forming the inertial portion of the resonator; a second annular and periodic magnetic structure 14 having a second integer number N2 of angular periods P2 and defining a second central axis 16, the second number N2 being different from the first number N1.

In general, N1⋅P1 = N2⋅P2 = 360 ° and therefore N1 / N2 = P2 / P1. In the variant shown in FIGS. 1 and 2, N1 = 15 and N2 = 14. The second magnetic structure 14 is rotatably arranged relative to the frame 4 about the second central axis 16 which has a fixed and determined position relative to this frame. The first magnetic structure 8 comprises an annular non-magnetic support having a central opening 9 and a first number N1 of magnets 12 regularly distributed in a circular manner on or in this support. The second magnetic structure 14 is supported by a non-magnetic disk connected to a shaft 17 and comprises a second number N2 of magnets 18 are evenly distributed circularly on or in this disk.

In this first embodiment, the first and second magnetic structures are arranged in two different general planes that are parallel. Then, the plurality of magnets 12 and the plurality of magnets 18 have axial magnetization and are repulsively arranged relative to each other.

The resonator 6 comprises an elastic structure, formed in the variant represented by three resilient blades 20, 21 & 22, which connects the first magnetic structure 8 to the frame 4. It can be said that the structure 8 is suspended from the frame by the intermediate of the elastic structure. Each elastic blade has a first folded end 20A which is anchored in a slot of the frame 4 and a second folded end 20B which is anchored in a slot of the annular support of the resonant magnetic structure 8. This elastic structure is arranged so that the first magnetic structure has a rest position in which the first and second central axes 10 and 16 are merged or virtually merged, and so as to exert a restoring force substantially in the direction of the second central axis 16 regardless of the angular position of the first magnetic structure relative to this second central axis. Preferably, the restoring force of the elastic structure is substantially proportional to the distance between the first and second central axes, that is to say the amplitude A of the circular resonance movement around the central axis 16 ( see Fig. 3D).

As shown schematically in FIGS. 3A to 3D which show four corresponding angular positions of the first and second magnetic structures during the expected resonance movement, the resonator 6 is arranged so that it has a resonance mode in which the first magnetic structure undergoes, relative to the frame, a substantially circular translation about the second central axis 16 with a given resonance frequency F1. The first and second magnetic structures are arranged so that their two pluralities of respective magnets have between them a magnetic interaction such as a relative rotation of the second magnetic structure around the second central axis 16, by the application of a pair motor in a useful range of the engine torque for normal operation of the watch movement incorporating such a regulating device, excites the aforementioned resonance mode and so that the frequency F2 of the relative rotation of the second magnetic structure and the resonance frequency F1 present between them, in the useful range of the aforementioned motor torque, a determined RFrd ratio, RFr = F1 / F2. This ratio RFrest equal to the second integer number N2 divided by the difference ΔN between the second integer number N2 and the first integer number N1, ie ΔN = N2-N1 and RFr = N2 / AN.

In both variants shown in Figs. 1, 2 and 3A to 3D, the difference in absolute value | ΔN | between the second number N2 and the first number N1 is equal to one, ie | ΔN | = 1. Then, preferably, as is the case in these two variants, the ratio RFrest greater than five, RFr> 5.

It will be noted that the driving torque is preferably provided to the second magnetic structure 14 via the shaft 17.

However, in an alternative embodiment of a watch movement incorporating such a regulating device, the magnetic structure 14 is fixed and it is the frame 4 which is rotated by a motor torque around the central axis 16 It should be noted that, in another variant, the two structures can rotate about the axis 16, the difference of the torques respectively applied to the frame and to the second magnetic structure defining the useful torque supplied to the regulating device. Whatever the variant considered, one can however speak of a rotation of the magnetic structure 14 relative to the frame 4 and thus of a relative rotation of this magnetic structure 14, and so appoint the latter 'a rotating magnetic structure'.

The regulating device according to the invention is particularly notable in that it incorporates a cycloidal multiplier, respectively a cycloidal reducer. More precisely, as shown schematically in FIGS. 3A to 3D, the first magnetic structure 8 of the resonator and the second magnetic structure 14 are configured and arranged relative to each other so that its resonant magnetic structure defines a first mobile of a cycloidal magnetic gear while the structure Magnetic resonating motion activation device (or magnetic resonant mode excitation structure, also hereinafter also called rotating magnetic structure) defines a second mobile of this cycloidal magnetic gear. The magnets of the resonant magnetic structure follow cycloidal paths when the magnets of the rotating magnetic structure rotate relative to the frame of the resonant magnetic structure about the central axis of this rotating magnetic structure. To do this, the invention selects a particular cycloidal gear in which the first mobile associated with the resonator undergoes a resonance movement with two degrees of freedom, generally following a curvilinear trajectory, preferably substantially circular, around the central axis 16 of the second mobile without rotating on itself relative to the frame and wherein the second mobile serves to excite and maintain the corresponding resonance mode, that is to say to generate the resonance movement by actuating the first mobile relative to the frame to which it is connected by an elastic structure. In other words, this first mobile undergoes, when the resonance movement is activated and stabilized, a curvilinear translation about the axis 16, whose position is fixed and determined relative to the frame, and preferably a substantially circular translation and centered on this axis 16. In FIGS. 3A to 3D, we chose an optimal case with a circular translation. It is therefore possible to speak of a regulating device with cycloidal resonance movement or, more briefly, of a cycloidal regulating device.

By analogy with the mechanical case, the two magnetic structures have, when said resonance mode is activated and the magnetic interaction between these two structures is sufficient to ensure a synchronous magnetic coupling between the aforementioned relative rotation of the second structure. magnetic and the substantially circular translation of the first magnetic structure, a magnetic meshing so that a pitch circle 26 of the first magnetic structure 8 rolls virtually without sliding on a corresponding pitch circle 28 of the second magnetic structure 14. By synchronization, one here generally comprises a fixed and substantially fixed ratio between the rotational frequencies in the presence, or between the resonant frequency and the rotation frequency of the second magnetic structure. The primitive circles are geometric circles-defining a virtual raceway. The ratio R of the respective radii R1 and R2 of the pitch circles 26 and 28 is set by the ratio RM of the respective numbers of magnets N1 and N2 of the two magnetic structures, ie R = R1 / R2 = RM = N1 / N2 = P2 / P1 . On the other hand, in the specific case of the cycloidal gearing provided for the invention, the frequency F1 of the circular translation around the axis 16, corresponding to the resonance frequency of the resonator, is a function of the frequency of the F2 rotation of the second magnetic structure about this axis 16 relative to the chassis, this function being given by the mathematical relationship F2⋅N2 = F1⋅ (N2-N1). We can deduce from this mathematical relation the ratio RFr of the frequencies F1 and F2 given by RFr = F1 / F2 = N2 / ΔN where ΔN = N2-N1. We thus obtain the following mathematical relation between the ratios RFret R, respectively RM: RFr = 1 / (1-R) = 1 / (1-RM). It is therefore found that the rotation frequency of the second magnetic structure is determined by the resonance frequency of the resonator; which makes it possible to clock the running of a clockwork movement equipped with a counter wheel coupled to the part of the regulating device which defines an escape wheel.

It will be noted that the frequency ratio can be positive or negative depending on whether the ratio RM of the number of angular periods N1 and N2 is less than or greater than one. A negative RFr ratio indicates that the direction of the circular translation of the resonant magnetic structure is inverted with respect to the direction of the relative rotation of the magnetic excitation structure of the intended resonance mode (rotating magnetic structure); which is the case in the example shown in FIGS. 3A to 3D where the resonant magnetic structure 8 has a greater number of magnets than the rotating magnetic structure 14. It will be noted that the magnets can, in various variants, be arranged with different radial positions without the ratio R of respective radii R1 and R2 of the primitive circles 26 and 28 do not vary. Those skilled in the art will optimize these radial positions to optimize the magnetic coupling between the two magnetic structures in the useful range of the motor torque applied to the regulating device of the invention. Magnetic structure firstly comprises the magnetic parts or elements (magnets or materials with high magnetic permeability involved in the magnetic interaction in question) which form the magnetic structure, the support of these magnetic parts or elements being physically necessary but secondary for the magnetic coupling. By 'annular magnetic structure', it is therefore understood an arrangement of the magnetic parts or elements in an annular manner, in particular circular. In figs. 3A to 3D were represented only the magnets of the two magnetic structures.

In FIG. 3A, one starts from a relative position in which two respective magnets 12A and 18A of the two magnetic structures 8 and 14 are aligned on the vertical axis 30 and the two respective central axes 10 and 16. In the variant shown in FIGS. 3A-3D, the structure 8 comprises eight magnets 12 while the structure 14 comprises seven magnets 18. As shown in FIG. 1, the two magnetic structures are arranged in general planes parallel and distant from each other, the pluralities of magnets 12 and 18 having an axial magnetization and being arranged in repulsion. It will be understood that the two vertically aligned magnets repel each other and that the magnets in the diametrically opposite zone penetrate one between two others and repel less strongly, or even attract each other according to the intended arrangement. It can thus be seen that there is a radial magnetic force with a difference of magnets | ΔN | = 1 which generates an initial off-centering of the axis 10 relative to the axis 16 in a state of rest of the regulating device and thus at the start of the relative rotation of the magnetic structure 14. Such decentering can allow a sufficient magnetic coupling between the two magnetic structures to excite the resonance mode at startup. It will be noted that the elasticity coefficient of the elastic structure and the inertial mass of the resonator essentially determine the resonance frequency. When there is resonance, the restoring force of the elastic structure corresponds to the centripetal force, necessary to generate the circular translation of the structure 8, in the absence of other parasitic forces; so that a radial magnetic force is not necessary. The amplitude of the resonance movement depends on the applied motor torque as well as the value of the restoring force generating the centripetal force, but these two forces remain equal when there is resonance in the absence of other parasitic forces. It is thus possible to provide a specific arrangement of the two magnetic structures for which the radial magnetic force vanishes by at least one resonance movement for a value of the engine torque in the expected effective range. Preferably, this specific arrangement is such that the radial magnetic force has a relatively low value, in particular substantially zero, for all this useful range of the engine torque, so as to obtain the operation of the most isochronous regulating device possible throughout this range. useful. It will also be noted that an increase in the amplitude A (distance between the central axes 10 and 16) results in greater penetration of the magnets of the two magnetic structures.

In figs. 3B and 3C, there are shown two relative positions of the two magnetic structures during the excitation of the expected resonance mode which generates a circular translation of the resonant magnetic structure 8 around the central axis 16 of the magnetic structure 14. When this structure 14 rotates counterclockwise to an angle α relative to the frame of the structure 8, the latter undergoes a circular translation clockwise over an angular distance B. Thus, the central axis 10 rotates about the central axis 16 following a circular path. The angle β is greater than the angle α and proportional thereto. These angles α and β are proportional to the two frequencies F1 and F2 because β / α = RFr = F1 / F2 = N2 / ΔN = 7. It can be seen that the magnet 12A considered and the central axis 10 remain aligned on a vertical line . In fig. 3D, we see that when the structure 14 has rotated a half-period P2 (α = P2 / 2), the angle β is equal to 180 ° (3 = 180 °). For a rotation of the structure 14 corresponding to its angular period P2, the central axis 10 of resonant structure performs a complete revolution (case ΔN = 1).

In figs. 4 to 6 is shown a second embodiment. The controller 32 incorporates the elements of the first embodiment which will not be described again here. This regulator device 32 operates in a manner similar to the device 2 described above. It differs from the latter in that it comprises a third magnetic structure 34 having a configuration similar to the second magnetic structure 14 and integral therewith. The two similar magnetic structures 14 and 34 are aligned in the direction defined by the second central axis 16 and arranged on either side of the magnetic structure 8 at a substantially same distance from the latter. The resonant magnetic structure 8 and the elastic structure connecting it to the plate 4 of the chassis are identical to those described above. The positioning of the resonant magnetic structure relative to the magnetic structure 14, respectively 34 is also identical to that of the first embodiment. In fig. 5, the resonator 8 is activated and the structure 8 is in a position of the circular path that it follows in the excited resonance mode. The frame comprises a lower plate 36 and an upper plate 37 in which the shaft 17A is rotatably mounted about the central axis 16 by means of two ball bearings. This shaft 17A can alternatively be pivoted in conventional bearings or magnetic bearings. The plates 4, 36 and 37 are fixed by screws 38 and fixedly held in parallel general planes by spacers 39 and 40 traversed by the screws. The representation of the plates and their assembly is schematic in the figures, each of these plates being able to form a plate or a bridge of a watch movement in which the regulating device 32 is arranged.

The magnetic structures 14 and 34 are fixed to the shaft 17A and driven simultaneously in rotation by a motor torque. These two similar structures have their magnets 18 and 19 aligned axially and having an axial magnetization of the same direction while the magnets 12 of the resonant magnetic structure 8 have an axial magnetization of inverted direction. Thus, each of the magnetic structures 14 and 34 has its magnets arranged in repulsion relative to the magnets of the intermediate structure 8. This constitutes a major advantage of this second embodiment because the axial magnetic forces undergone by the resonant magnetic structure 8 cancel each other out. globally. In a variant, the two similar structures are mounted on two coaxial shafts and at least one of these shafts receives a driving torque. In a first particular variant, a first shaft receives a driving torque while the second shaft is rotated by the resonant magnetic structure at the same frequency as the rotation frequency of the first shaft. In a second particular variant, the two shafts each receive a motor torque to excite the resonance mode and ensure its maintenance. The resonator synchronizes the rotation frequencies of the two shafts.

In another embodiment not shown, it is the resonant magnetic structure 8 which is doubled, that is to say that the resonator comprises two resonant magnetic structures similar and integral in motion. The two resonant magnetic structures are aligned in the axial direction and arranged on either side of a magnetic structure of excitation of the expected resonance mode (similar to structure 14 described above) at a substantially same distance from the latter. The two resonant magnetic structures can be connected to the frame by the same median elastic structure or by two elastic structures respectively extending in the two general planes of these two resonant magnetic structures. In a variant of the latter case, the two resonant magnetic structures are independent and arranged to have a substantially identical resonant frequency.

With the aid of FIGS. 7 to 10, will be described below four variants of a third embodiment of a regulating device according to the invention. It will be noted from the outset that the first variant corresponds in its operating principle to the first and second embodiments described above in the variant where the frame is fixed relative to the watch movement. Thus, the general explanations given for the operation of the regulating device and the various mathematical relations also apply to this third embodiment.

The third embodiment differs essentially from the first embodiment in that the first and second magnetic structures of the regulating device are arranged in the same general plane, one of these first and second magnetic structures being located at the same location. inside the other; and in that the magnetic material forming at least one of the two magnetic structures has a radial magnetization. In the variants described below, the two magnetic structures each comprise a plurality of magnets having a radial magnetization. In the first and second variants, the magnets of one structure are arranged in repulsion magnets of the other structure. In the third and fourth variants, the magnets of a magnetic structure are arranged in attraction of the magnets of the other magnetic structure. In the first case, the circular movement of the resonant magnetic structure is such that the magnets thereof follow cycloidal trajectories so that the magnet or the two magnets of this resonant magnetic structure which are radially closest to the magnets of the magnet. the rotating magnetic structure (undergoing rotation relative to the frame) is / are substantially out of phase (s). In the second case, the magnet or two magnets of the resonant magnetic structure which is radially closest to the magnets of the rotating magnetic structure are substantially aligned therewith.

It will also be noted that in the variants described below, the inner magnetic structure has eighteen magnets while the outer magnetic structure has twenty magnets. We therefore have a difference of magnets ΔN = +/- 2. As a result, the resonance frequency F1 = +/- F2⋅N2 / 2, where F2 and N2 are respectively the rotation frequency and the number of magnets of the rotating magnetic structure, according to the explanations that have been given previously. Thus, when the rotating magnetic structure has made a rotation corresponding to its angular magnetic period P2, the resonant magnetic structure has made a circular translation of an angle of +/- 180 ° because P2⋅N2 = 360 °. Since, with a difference in magnets in absolute value greater than one, let | ΔN | > 1, there is generally no radial magnetic force when the central axes of the two magnetic structures are merged, it is intended to arrange a mechanical means for initially off-center the resonant magnetic structure relative to the rotating magnetic structure, so to generate an initial magnetic coupling between the two magnetic structures which is sufficient to allow the starting of the regulating device by the relative rotation of the rotating magnetic structure and thus to excite the expected resonance mode, the latter being then maintained by this relative rotation of this rotating magnetic structure in the useful range of the engine torque. In other variants of the third embodiment, corresponding to the above-mentioned four variants, a difference of magnets in absolute value equal to one, ie | ΔN | = 1, the magnets being arranged either in repulsion or in attraction. Finally, it will be noted that the various variants of the third mode described hereinafter can also be applied to the other embodiments of the invention, in particular to the other embodiments given in the present description of the invention, that is, that is to say embodiments where the resonant magnetic structure and the rotating magnetic structure are arranged in different general planes, in particular with the magnets of these magnetic structures having axial magnetization.

The regulator device 42 of FIG. 7 includes: a frame 44 forming a frame integral with the watch movement in which the regulating device is incorporated; a resonant magnetic structure 8A of annular shape and comprising at its inner periphery a plurality of magnets 12A arranged circularly and defining a central axis 10; a rotating wheel comprising at its outer periphery a plurality of magnets 18A arranged circularly and defining a rotating magnetic structure 14A, this mobile being arranged inside the structure 8A and comprising a central non-magnetic disk 50 mounted on a shaft 17A whose axis of rotation coincides with the central axis 16 of the rotating magnetic structure; an elastic structure formed of four identical springs 46,47,48 & 49 which are arranged in pairs on two orthogonal geometric axes (precisely when the central axes 10 and 16A coincide), the anchors of each pair of springs on the frame and on the resonant magnetic structure being diametrically opposed.

The magnetic structure 14A is rotated by a motor torque with an angular velocity u> dependent on the resonant frequency when the resonance mode is excited and stabilized. It thus forms an escape wheel of the regulating device 42 to which the engine torque supplied is applied. To have an isotropic restoring force generated by the elastic structure, the distance between the two anchors of a spring is identical for the four springs when the central axes 10 and 16 are merged. These springs are each formed by an elastic blade having in plan a sinuous profile. Various variants may be provided by those skilled in the art.

The regulating device 52 of FIG. 8 includes: a magnetic structure 14B of annular shape and comprising at its inner periphery a plurality of magnets 18B arranged circularly and defining a central axis 16A, this magnetic structure being integral with the watch movement in which the regulating device is incorporated (shown schematically by a material connection to a mass 56); a frame formed by a central shaft 54 whose axis of rotation coincides with the central axis 16A and arranged inside the structure 14B; a resonant magnetic structure 8B of annular shape and comprising at its outer periphery a plurality of magnets 12B arranged circularly and defining a central axis 10, this resonant magnetic structure being arranged inside the structure 14B and the central shaft 54 being located inside structure 8B; an elastic structure formed of four identical springs 46,47,48 & 49 which are arranged in pairs on two orthogonal geometric axes (precisely when the central axes 10 and 16A coincide), the anchors of each pair of springs on the frame and on the resonant magnetic structure being diametrically opposed.

The central shaft 54 is rotated by a motor torque with an angular velocity ω dependent on the resonance frequency when the resonance mode is excited and stabilized. The chassis thus forms an escape wheel to which the engine torque supplied to the regulating device 52 is applied. To have an isotropic restoring force generated by the elastic structure, the distance between the two anchorages of a spring is identical for the four springs. when the central axes 10 and 16A are merged. These springs are each formed by an elastic blade having in plan a sinuous profile. Various variants may be provided by those skilled in the art. Note that, although fixed relative to the watch movement, the magnetic structure 14B has relative to the frame 54 relative rotation about its central axis 16A, which has a fixed position determined relative to the frame. Thus, in the terminology used, the structure 14B defines a rotating magnetic structure in the frame-linked frame.

The regulating device 62 of FIG. 9 includes: a frame secured to the watch movement in which the regulating device is incorporated (shown schematically by a material link to a mass 56), this frame being formed by a central block 64 and an outer support 66 having a circular opening; a rotating magnetic structure 14C of annular shape and comprising at its inner periphery a plurality of magnets 18C arranged circularly and defining a central axis 16, this structure 14G having a circular outer surface and rotating about its central axis 16 inside the outer support 66 which guides it in rotation by a ball bearing 68; a resonant magnetic structure 8B of annular shape and comprising at its outer periphery a plurality of magnets 12B arranged circularly and defining a central axis 10, this structure 8B being arranged inside the structure 14C and the central block 64 being located inside this structure 8B; an elastic structure formed of four identical springs 46,47,48 & 49 which are arranged in pairs on two orthogonal geometric axes (precisely when the central axes 10 and 16A coincide), the anchors of each pair of springs on the frame and on the resonant magnetic structure being diametrically opposed.

The magnetic structure 14C is rotated by a motor torque with an angular velocity ω dependent on the resonance frequency when the resonance mode is excited and stabilized. It thus forms an escape wheel of the regulating device 62. The springs 46, 47, 48 and 49 are similar to those of the preceding variant (FIG 8) and arranged in a similar manner.

The regulator device 72 of FIG. 10 includes: a central magnetic structure 14D comprising at its outer periphery a plurality of magnets 18A arranged circularly and defining a central axis 16A, this central magnetic structure being integral with the watch movement in which the regulating device is incorporated (schematized by a material link to a mass 56); an outer support 66 having a circular opening and also integral with the watch movement in which the regulating device is incorporated; a frame formed by a rotating annular support 74 whose axis of rotation coincides with the central axis 16A and arranged inside the outer support 66, this annular support 74 having a circular outer surface and rotating inside the outer support 66 which guides it in rotation by a ball bearing 68; a resonant magnetic structure 8B of annular shape and comprising at its inner periphery a plurality of magnets 12B arranged circularly and defining a central axis 10, this structure 8B being arranged inside the rotating annular support 74 and the central magnetic structure 14D being located within this structure 8B; an elastic structure formed of four spiral elastic blades 77, 78, 79 & 80 which are identical and arranged between the resonant magnetic structure 8B and the rotating annular support 74 to which these four elastic blades are respectively fixed at their two ends.

The rotating annular support 74 is rotated by a motor torque with an angular velocity α) dependent on the resonant frequency when the resonance mode is excited and stabilized. It thus forms an escape wheel of the regulating device 72. The four spiral elastic blades are angularly offset by 90 ° and they are nested without touching each other. In the variant shown, each elastic blade substantially defines a turn (it extends substantially over an angular distance of 360 °). Thus, the two anchors of each elastic blade respectively to the resonant magnetic structure and to the rotating annular support are substantially aligned in a radial direction of this rotating annular support. Note that the spiral spring blades can have various lengths, including a turn and a half (540 °) so the two anchors of each elastic blade are substantially diametrically opposed relative to the central axes 10 and 16A. This last variant is advantageous.

With the aid of FIGS. 11, 12, 13A and 13B, a fourth embodiment of the invention will be described below. The regulator device according to this fourth embodiment is an improved device which associates with any one of the previously described embodiments a mechanical anti-stall system of the coupling between the resonant magnetic structure and the rotating magnetic structure to ensure operation. the watch movement which incorporates the regulating device into a wider range of engine torque and also to prevent the aforementioned coupling from stalling in the event of angular shocks or accelerated movements generating torques greater than the intended effective range. The various elements already described and the operation of the magnetic system of the resonator device will not be described again here. In general, the term "mechanical anti-stall system" is understood to mean a system which ensures the synchronization between the resonant magnetic structure and the rotating magnetic structure in a range of the engine torque where the purely magnetic coupling could no longer suffice or fail to fulfill its function in a sufficiently precise or safe manner and also in the case of higher torques momentarily generated by shocks or movements with high acceleration. This system can thus preferably intervene before the magnetic interaction between these two structures is no longer sufficient to ensure this synchronization, that is to say before a stall torque purely magnetic coupling. In one variant, it is therefore possible to provide such a system as a complementary mechanical system to the magnetic system of the regulating device of the invention, this complementary mechanical system intervening only in an upper part of the total range of the engine torque provided for the operation of this system. However, the upper value of this total range is less than the stall torque of the purely magnetic coupling. In the latter case, the complementary mechanical system nevertheless has a safety function by allowing a momentarily greater torque than the normal operating range does not cause a loss of synchronization. In another variant, it can be provided that the mechanical anti-stall system intervenes substantially only when the stall torque is reached and then exceeded.

The variant of the fourth embodiment which is shown in the figures is based on the second embodiment of the invention. The frame, the elastic structure and the two rotating magnetic structures mounted on the shaft 17A (magnetic structures 14 and 34 carrying respectively a number N2 of magnets 18 and the same number N2 of magnets 19) are identical to the corresponding parts of the variant of the second embodiment shown in FIGS. 4-6. The resonant magnetic structure comprises a number N1 of magnets, N1 being different from N2 as already stated. In general, the mechanical anti-stall system is formed by a planetary gear with a satellite wheel 86 provided with a first toothing 88 and rotating inside a ring 84 provided internally with a second toothing 90. Then, the satellite wheel is associated with the structure 14 having the lower number of angular periods among the first and second magnetic structures 8 and 14 (the lower number of magnets among the two numbers N1 and N2), and the crown is associated with the other structure 8 having the greater number of angular periods (the higher number of magnets among the two numbers N1 and N2). To ensure the anti-stall function, the part of the planetary gear associated with the second magnetic structure 14 must be integral in rotation with this second structure.

It is provided that the first and second teeth penetrate at least partially into each other at least in an upper zone of the useful range of the engine torque provided for a purely magnetic coupling, the upper value of this upper zone. defining the maximum value of this useful range. Finally, the first and second sets of teeth 88 and 90 are configured and arranged relatively to each other so that, in the useful range of purely magnetic coupling, these first and second sets of teeth do not touch each other.

In a main variant, the ratio RZ between the number Z1 of teeth 90 of the ring gear and the number Z2 of teeth 88 of the satellite wheel is equal to the ratio RM * between the upper number and the lower number of angular periods. Thus, RZ = Z1 / Z2 = RM * = Sup (N1, N2) / Inf (N1, N2) where Inf (N1, N2) is the lower value of the numbers N1 and N2 while Sup (Nt, N2) is the higher value of these numbers N1 and N2.

In the particular variant shown in the figures, the number Z2 of teeth 88 of the satellite wheel 86 is identical to the number N2 of magnets of the magnetic structure 14, respectively 34. Similarly, the number Z1 of teeth 90 of the crown 84 is identical to the number N1 of magnets of the magnetic structure 8.

In the variant shown in the figures, the ring 84 forms the non-magnetic support of the resonant magnetic structure 8. These two elements are thus integral and together form the same body. In this variant, the number Z1 of teeth 90 of the ring is preferably identical to the number N1 of magnets 12 of the resonant magnetic structure, the magnets being substantially aligned with the teeth, as shown in the figures. It will be seen later, in an improved variant, that the angular positions of the teeth can be shifted relative to the angular positions of the magnets to increase the useful range of purely magnetic coupling. To do this, it will be noted that the teeth and the magnets can be provided at two different levels of the body that they form together, in particular to allow a design of the teeth independent of that of the magnets and their arrangement in this body. In other variants, the ring and the satellite wheel are in a general plane different from that of the resonant magnetic structure, the ring and this structure being formed in particular by two distinct elements. In a first variant, the ring and the resonant magnetic structure are integral and fixed together to the frame by the same elastic structure. In a second variant, the ring and the resonant magnetic structure are also integral and form two distinct elements, but there are two elastic structures respectively fixed to these two distinct elements. In a third variant, the ring and the resonant magnetic structure form two distinct elements and are not directly integral with each other (in the direction fixed to one another), but each of them is fixed to the frame by its own elastic structure. In this third variant, however, the ring and the resonant magnetic structure are associated with each other in that the ring with its first elastic structure is arranged to present substantially a resonance frequency identical to that of the resonant magnetic structure. with its second elastic structure.

In the variant shown in the figures, the satellite wheel is a separate element of the magnetic structures 14 and 34. However, in other variants, the satellite wheel can form the same member with one of these two magnetic structures (c '). that is to say with a rotating magnetic structure). Thus, the plurality of magnets of the rotating magnetic structure are incorporated in or on the satellite wheel. Preferably, the number Z2 of teeth 88 of the satellite wheel is identical to the number N2 of magnets 18 of the rotating magnetic structure 14, the magnets being substantially aligned with the teeth. This situation is also presented in a variant where the two pluralities of magnets are arranged in attraction. It will be seen later, in an improved variant, that the angular positions of the teeth can be shifted relative to the angular positions of the magnets to increase the useful range of purely magnetic coupling. In the other variants mentioned above, one can essentially distinguish two main variants. In the first main variant, the crown and the satellite wheel are in a general plane different from that of the resonant magnetic structure and the rotating magnetic structure is also arranged in this different general plane. In the case where there are two rotating magnetic structures, as in the figures, it is possible in a particular variant to double the planetary gear and to arrange these two similar planetary gears in the two general planes of these two rotating magnetic structures. The second main variant is based on the third embodiment described above. In this case, the ring and the magnetic structure having the largest diameter together form a first member and the sun wheel and the magnetic structure having the smallest diameter together form a second member, the first and second members being substantially located in the same general plan. Note however that the teeth and magnets can be provided at two different levels including to allow a design of the teeth independent of that of the magnets and their arrangement in the corresponding member.

Figs. 13A and 13B show the regulating device 82 at the plate 4 respectively in two successive positions when a force torque is applied on the shaft 17A, generating a rotation of the magnetic structures 14 and 34 and the satellite wheel 86. L planetary gear defines a cycloidal mechanical gear that operates similarly to the cycloidal magnetic gear. In the example shown in FIGS. 13A and 13B, the applied motor torque is in the useful range provided for purely magnetic coupling. In this case, the ring 84 rolls virtually without sliding and without contact around the satellite wheel 86 by the effect of the magnetic interaction. In other words, in the aforementioned useful range, the pitch circles of the crown and the satellite wheel have the same ratio as those of the magnetic structures 8 and 14, but the scale of the primitive circles of the planetary gear is selected. and the design of the teeth 88 and 90 is designed so that the teeth do not touch. In the first relative position of the satellite wheel 86 and the ring 84 shown in FIG. 13A, the tooth 91A of the crown is centered in the space between the teeth 89A and 89B of the satellite wheel. Note that there is a tangential clearance on each side of the tooth 91 A, and the same for the adjacent teeth (for example the tooth 91B) which normally have tangential clearances at least as large. In addition, there is provided a radial clearance to increase the amplitude of the resonance movement. The situation shown corresponds in particular to a motor torque lower than the maximum value of the useful range provided for a purely magnetic coupling. Continuing the rotation of the satellite wheel, we observe the virtual rolling without sliding and without contact of the two teeth and we arrive at the second relative position of FIG. 13B where the ring (having the central axis 10) has been circularly translated about the axis 16 of the satellite wheel. In this second relative position, it is in the same situation as that of the first relative position, but with an angular offset corresponding to the angular offset between two magnets or two adjacent teeth of the ring 84. Thus, the tooth 91B is centered in the space between the teeth 89B and 89C of the satellite wheel and the tangential clearances as well as the radial clearance are similar to those of the first relative position.

In a first variant, the first and second teeth penetrate into each other at least in most of said useful range of said engine torque. In a second variant, the first and second teeth penetrate one into the other over the entire useful range and finally, in a third variant corresponding to the example shown in the figures, the first and second teeth penetrate the one in the other also when no driving torque is applied to this regulator device. This last variant can be advantageous because the toothing of a first part of the planetary gear associated with the rotating magnetic structure then generates an initial off-centering of the resonant magnetic structure since the teeth of the second part of the planet gear associated with this last are substantially aligned with a few teeth of the first part of the planetary gear. This therefore makes it possible to activate the regulating device in the case where the difference in absolute value | ΔN | = | N1-N2 | is greater than one, ie | ΔN | > 1, as already explained above.

In a particular variant, the regulating device is intended to operate with a purely magnetic coupling in a first useful range of the engine torque and then with a magneto-mechanical coupling in a second useful range of this engine torque greater than the first range. useful and contiguous to it. The maximum value of the first useful range is predicted to be less than a stall value of purely magnetic coupling. In the second useful range, the two respective toothings of the crown and the planet wheel meshing with each other so that one exerts a mechanical drive torque on the other which is added to the torque of magnetic drive. The two teeth are configured and arranged relative to each other so that, at least in a lower zone of the second useful range whose lower value defines the minimum value of this second useful range, these two teeth present a set radial allowing an increase in the amplitude of the substantially circular translation of the resonance movement during an increase in the engine torque. Finally, the elastic structure is arranged so that it has a substantially elastic, preferably purely elastic, deformation in the first and second useful ranges of the engine torque applied to the regulating device.

In the context of this fourth improved embodiment, the observation of the purely magnetic coupling as a function of the engine torque is important to optimize the regulator device. For a first relatively low motor torque, the magnetic interaction is such that there is in the magnetic meshing zone (zone where the magnets of the resonant magnetic structure are radially closest to the magnets of the rotating magnetic structure). first phase shift (also called angular offset) between the magnets of the two magnetic structures (for example relative to the axis of rotation of the rotating magnetic structure). By increasing the engine torque, this phase difference is varied and a second phase difference is obtained which is different from the first for a second engine torque greater than the first engine torque. More precisely, the angular offset between the magnets of the two magnetic structures in the direction of the applied motor torque decreases when this engine torque increases and this angular offset, which is in particular close to a half-magnetic period for a low engine torque, can become relatively small for close motor torque but lower than the magnetic coupling stall motor torque. If, as shown in FIG. 11, the magnets of the two magnetic structures are radially aligned on the teeth of the two parts of the planetary gear respectively integral with these two magnetic structures, there is the following problem: The two teeth will come into contact, that is to say say that the side flanks of their respective teeth will touch and a mechanical drive will intervene for a motor torque still far from the stalling motor torque of the magnetic coupling; this has the effect of limiting the useful range of purely magnetic coupling. Now purely magnetic coupling is contactless and therefore without friction and without mechanical interaction forces at the teeth. These mechanical interaction forces can cause not only a problem of energy efficiency, but also a problem of operation of the resonator resonance mode and the accuracy of the regulating device. Indeed, the elastic structure of the resonator and the operating conditions of the watch movement incorporating the regulating device in question can generate a natural resonance movement which does not follow a well circular trajectory, likewise for the resonance movement resulting from the magnetic coupling provided . It is therefore advantageous to have a useful range of purely magnetic coupling which is as great as possible for a smooth operation of the watch movement over an extended useful range, and therefore to be able to get as close as possible to the stall torque of the magnetic coupling without the teeth do not come into contact and a mechanical torque is transmitted via the resulting mechanical coupling.

Following the observations given above, it is proposed an improved variant of the fourth embodiment in which the first toothing of the satellite wheel is arranged relative to the second toothing of the ring so that in the area of the useful range of the engine torque in which these first and second sets of teeth have a non-contact penetration, teeth of the first toothing located in corresponding spaces of the second toothing, in the area where the first and second set of teeth are radially closest, are substantially centered within a given total tangential clearance for a relative phase shift (angular offset), between the angular periods of the first magnetic structure and the angular periods of the second magnetic structure, within a range phase shift (relative angular offset) defined by a variation of the motor torque in said useful range.

In a variant where the planetary mechanical gear is located in a general plane different from the general plane or the general planes of the cycloidal magnetic gear, it is possible to configure the two gears independently of one another. and realize the improved variant described above optimally. In the case where a magnetic structure is provided in the same general plane as the mechanical gear, but the other magnetic structure is in a general plane where there is no part of this mechanical gear, it is easy to shift angularly at an optimum angular distance the magnets of this other magnetic structure relative to the teeth of the part of the mechanical gear integral with this other magnetic structure. In the case of the third embodiment, it will be advantageous to arrange the mechanical gear in a different level from that of the magnets, each magnetic structure and the corresponding part of the planetary mechanical gear together forming a compact member having both levels. meshing. However, if it is intended to provide a single level with the magnets arranged in repulsion, the tooth heads or half teeth of the teeth can be formed of magnetized material. In a variant with the magnets arranged in attraction, it is possible to provide a plurality of magnets inside the circle defined by the bottoms of the spaces of the corresponding toothing; which makes it possible to have this plurality of magnets substantially aligned radially with the spaces of this toothing.

Claims (21)

1. Device regulating the gait of a mechanical clockwork movement, this regulating device comprising: - a chassis; A resonator fixed to the frame and comprising a first annular and periodic magnetic structure having a first integer number N1 of angular periods and defining a first central axis, this first magnetic structure forming the inertial portion of the resonator; A second annular and periodic magnetic structure having a second integer number N2 of angular periods and defining a second central axis, the second number N2 being different from the first number N1, this second magnetic structure being arranged so as to be able to turn relative to said frame around said second central axis which has a determined position relative to this frame; wherein at least one magnetic structure of the first and second magnetic structures has in each of its angular periods a magnetic material; said resonator being arranged so that it has a resonance mode in which said first magnetic structure undergoes, relative to said frame, a curvilinear translation about said second central axis with a resonant frequency F1; said first and second magnetic structures being arranged to present to each other a magnetic interaction such as a relative rotation of the second magnetic structure relative to said frame and around said second central axis, by the application of a motor torque in a range of the motor torque, excites said resonance mode and in such a way that the frequency F2 of said relative rotation of the second magnetic structure and said resonant frequency F1 have between them, within said useful range of the motor torque, a determined RF ratio, ie RFr = F1 / F2, which is equal to said second integer number N2 divided by the difference ΔN between the second integer number N2 and the first integer number N1, ie ΔN = N2-N1 and RFr = N2 / ΔN. 2. Watchdog device according to claim 1, characterized in that said resonator comprises an elastic structure connecting said first magnetic structure to said frame, this elastic structure being arranged so that said first magnetic structure has a rest position in which the first and second central axes are substantially merged, and so as to exert a return force substantially in the direction of said second central axis regardless of the angular position of the first magnetic structure relative to the second central axis. 3. clock watch device according to claim 1 or 2, characterized in that said restoring force of the elastic structure is substantially isotropic and substantially proportional to the distance between the first and second central axes. 4. Regulator device according to any one of the preceding claims, characterized in that said RFrest ratio greater than five, RFr> 5. 5. Regulator device according to any one of the preceding claims, characterized in that said first magnetic structure comprises a first plurality of magnets regularly distributed in a circular manner and whose number is equal to said number N1, and said second magnetic structure comprises a second plurality of magnets regularly distributed in a circular manner and whose number is equal to said number N2. 6. Regulator device according to claim 5, characterized in that said second plurality of magnets is arranged in repulsion relative to said first plurality of magnets. 7. Regulator device according to any one of the preceding claims, characterized in that said first and second magnetic structures are arranged in two parallel general planes distant from each other. 8. Regulator device according to claim 7, characterized in that said magnetic material of said at least one magnetic structure has an axial magnetization. 9. Control device according to claim 7 or 8, characterized in that it comprises a third magnetic structure having a configuration similar to the first or second magnetic structure, the two similar magnetic structures being aligned in the direction defined by the first central axis , respectively the second central axis and arranged on either side of the different magnetic structure at a substantially same distance from the latter. 10. Regulator device according to any one of claims 1 to 6, characterized in that said first and second magnetic structures are arranged in the same general plane, one of these first and second magnetic structures being located inside of the other; and in that said magnetic material of said at least one magnetic structure has a radial magnetization. 11. Regulator device according to any one of the preceding claims, characterized in that said second magnetic structure forms an escape wheel to which said engine torque is applied. 12. Regulator device according to any one of claims 1 to 10, characterized in that said frame forms an escape wheel to which said engine torque is applied. 13. Control device according to any one of the preceding claims, characterized in that it further comprises a mechanical anti-stall system of synchronization between said first and second magnetic structures which is formed by a planetary gear with a wheel satellite provided with a first toothing and rotating inside a ring provided internally with a second toothing, the satellite wheel being associated with the structure having the lower number of angular periods among said first and second magnetic structures and the crown being associated with the other structure having the higher number of angular periods; in that the structure associated with said second magnetic structure is integral in rotation with this second structure; in that, at least in an upper zone of said useful range of the engine torque, the upper value of which defines the maximum value of this useful range, the first and second sets of teeth penetrate at least partially into one another; and in that the first and second sets of teeth are configured and arranged relative to one another so that, in said useful range, these first and second sets of teeth do not touch each other, the coupling between the first and second magnetic structures being purely magnetic in this useful range. 14. Regulator device according to claim 13, characterized in that the ratio RZ between the number Z1 of teeth of the toothing of the ring gear and the number Z2 of teeth of the toothing of the satellite wheel is equal to the ratio RM * between said upper number of angular periods and said lower number of angular periods. 15. Control device according to claim 13 or 14, characterized in that said first and second sets of teeth penetrate at least partially into each other without touching all of said useful range of the engine torque. The regulator device according to any one of claims 13 to 15 dependent on claim 2, wherein said useful range of said motor torque is a first useful range of purely magnetic coupling of the first and second magnetic structures, the maximum value of this first useful range being less than a stall value of this purely magnetic coupling, characterized in that it comprises a second useful range of the motor torque, greater than the first useful range and contiguous to this first useful range, corresponding to a useful range of magneto-mechanical coupling in which said first and second toothing meshes with each other so that one exerts a mechanical driving torque on the other; in that the first and second teeth are configured and arranged relative to one another so that, at least in a lower zone of the second useful range whose lower value defines the minimum value of this second useful range, these first and second teeth have a radial clearance allowing an increase in the amplitude of said curvilinear translation of said first magnetic structure during an increase in the engine torque; and in that said elastic structure is arranged such that it has a substantially elastic deformation in the first and second useful ranges of the engine torque applied to the regulating device. 17. Control device according to any one of claims 13 to 15, characterized in that said first toothing of the satellite wheel is arranged relative to said second toothing of the ring so that, in an area of said useful range of the driving torque wherein said first and second sets of teeth have a non-contacting penetration, teeth of the first toothing located in corresponding spaces of the second toothing, in an area where the first and second sets of teeth are radially closest, are substantially centered at the within a given total tangential clearance for a relative angular offset, between the angular periods of the first magnetic structure and the angular periods of the second magnetic structure, within a relative angular offset range defined by a variation the engine torque in said useful range. 18. Regulator device according to any one of claims 1 to 17, characterized in that the difference in absolute value | ΔN | between the second integer number N2 and the first integer number N1 is equal to one, ie | ΔN | = 1. 19. Control device according to any one of claims 1 to 17, characterized in that said difference in absolute value | ΔN | between the second integer number N2 and the first integer number N1 is greater than one, ie | ΔN | > 1. 20. Regulator device according to claim 19, characterized in that it comprises a mechanical means for initially off-centering said first magnetic structure relative to said second magnetic structure, so as to generate a sufficient initial magnetic coupling between the first and second structures to enable starting said regulator device by said relative rotation of the second magnetic structure. 21. Mechanical watch movement comprising a regulating device, a counter wheel clocked by this regulating device and a motor device driving the counter wheel and maintaining a resonance mode of the regulating device, characterized in that said regulating device is a regulating device according to the invention. any of the preceding claims.