CH713837B1 - Regulation device based on an isotropic harmonic oscillator for a timepiece. - Google Patents

Abstract

The present invention relates to a device for regulating a watch mechanism based on an isotropic harmonic oscillator, intended to be integrated into a timepiece, in particular into a wristwatch, said regulating device comprising a rigid frame, at the at least two masses (1.3) mounted so that they are movable relative to the rigid frame, a variable radius drive means (1.4) coupled by an elastic coupling means to at least one of said masses (1.3), said drive means (1.4) being capable of being driven by an energy source of said timepiece as well as transmitting the energy received to said masses (1.3) so as to set them in motion, and means of inversion (1.5) coupled to said masses (1.3) and arranged to reduce the displacement of the center of mass of the regulating device. The device is distinguished by the fact that it comprises a bearing structure (1.2) mounted on said rigid frame in a pivoting manner via at least one pivot and able to form a guide for the movement of the masses (1.3.1, 1.3.2), said masses (1.3) being mounted on said supporting structure (1.2), and in that the reversing means (1.5) are located on or form part of said supporting structure (1.2) and are arranged so as to cause a correlated and symmetrical movement of said masses (1.3.1, 1.3.2). The present invention also relates to a timepiece movement, respectively a timepiece, comprising such a regulation device.

Description

Fields of invention

The present invention relates to a device for regulating a watch mechanism based on an isotropic harmonic oscillator, intended to be integrated into a timepiece, in particular into a wristwatch, said regulating device comprising a rigid frame, at least two masses mounted so that they are movable relative to the rigid frame, a variable radius drive means coupled by an elastic coupling means to at least one of said masses, said drive means being adapted to be driven by a source of energy from said timepiece as well as to transmit the energy received to said masses so as to set them in motion, and inversion means coupled to said masses and arranged so as to reduce the displacement of the center of mass of the regulating device.

[0002] In general, the invention relates to efforts to produce a regulating member for timepieces having a mechanical movement, in particular mechanical wristwatches, by overcoming the usual need to integrate a horological escapement, this using an isotropic harmonic oscillator.

State of the prior art

[0003] Efforts aimed at producing a regulating member that does not need to be coupled to an escapement have already been undertaken several times since the existence of mechanical watch movements with escapements. A recent example of this kind of effort is the document WO2015/104692 which includes, in addition, a structured review of many different and theoretically possible approaches to realize an isotropic harmonic oscillator as well as some theoretical bases of the physics of such oscillator. This document also includes sketches of many forms of execution of such an isotropic harmonic oscillator, without the technical feasibility, or even the effective performance of these proposals having apparently been evaluated in all detail, so that it It is unclear which of these many proposals are actually viable.

Another recent example of this kind of effort is document EP 3 054 358 which discloses a horological oscillator comprising a rigid frame, a plurality of distinct primary resonators, temporally and geometrically out of phase, and each comprising at least one inertial mass returned to said frame by an elastic return means, coupling means arranged to allow the interaction of said primary resonators, and drive and guide means arranged to drive and guide said inertial masses with the aid of a means control. This device therefore realizes, in principle, a specific embodiment of an isotropic harmonic oscillator in which, in particular, said primary resonators are rotary resonators and are arranged in such a way that the axes of the joints of any two of said primary resonators and the axis of articulation of said control means are never coplanar. If this proposal is more detailed, the specific construction proposed imposes a certain number of limitations, in particular in terms of the axes of the articulations of the primary resonators and of the control means. Moreover, although this device is supposed to carry out a compensation of the forces both in translation and in rotation, the proposed constellation does not seem to be optimal in this respect.

[0005] The disclosure of document FR 630 8310009 is an older example of the efforts made in the past to produce an isotropic harmonic oscillator that can be used, among other things, as part of a regulating member for the watchmaking field. This document also includes a large number of embodiments for making such an oscillator which are however either not suitable for integration into wristwatches or not endowed with sufficient rate precision for this task, reason for which these proposals are not reviewed in detail below.

[0006] It should therefore be noted that, despite the fact that several prior art solutions exist for producing a regulating member based on an isotropic harmonic oscillator, these solutions are not completely satisfactory, in particular as regards the complexity of construction and the technical feasibility of such a mechanism, the arrangement of its drive, the compensation for the influence of gravity and the forces both in translation and in rotation, shock absorption, as well as the rate precision of a timepiece fitted with such a regulating organ.

Objectives of the invention

The object of the present invention is to remedy, at least partially, the drawbacks of known devices and to produce a device for regulating a timepiece mechanism based on an isotropic harmonic oscillator for timepieces which allows to construct watch movements without an escapement, which has a simple and robust structure, moreover in order to guarantee a reasonable production cost, as well as reliable operation, and which makes it possible to obtain an improved rate precision of a corresponding timepiece. Furthermore, such a regulation device should have sufficient flexibility, both in terms of its structure and its concrete embodiment, to allow integration into a wide variety of timepieces.

Solution according to the invention

[0008] To this end, the present invention proposes a device for regulating a watch mechanism based on an isotropic harmonic oscillator of the aforementioned type which is distinguished by the characteristics set out in claim 1. In particular, the device for regulation of a timepiece mechanism according to the present invention comprises a bearing structure mounted on said rigid frame in a pivoting manner via at least one pivot and able to form a guide for the movement of the masses, said masses being mounted on said structure supporting structure, the reversing means being located on or forming part of said supporting structure and being arranged so as to cause a correlated and symmetrical movement of said masses.

[0009] By means of these measures, the device for regulating a watch mechanism comprises masses which are not mounted directly on the rigid frame of the device, but which are mounted on the rigid frame by means of said support structure. Moreover, given that the supporting structure is pivotally mounted on said rigid frame, this structure simultaneously serves as a support for the masses as well as a means for balancing the movements of said masses.

In a preferred embodiment of the regulating device according to the present invention, the drive means is coupled directly and decentralized to one of said masses via a return spring simultaneously serving as a means of transmission of the drive force and elastic return means. Such a direct and decentralized drive of one of the masses is possible thanks to the presence of said bearing structure mounted in a pivoting manner, respectively of its function of balancing the movements of said masses, and makes it possible to simplify the construction of the regulation device, d to adapt its design to the needs, as well as to improve its functioning.

[0011] Preferably, the regulating device according to the present invention comprises an even number of masses mounted on said bearing structure. Preferably, said supporting structure comprises at least one crossbar pivotally mounted on said rigid frame. Furthermore, the reversing means are preferably located on or form part of said bearing structure and are arranged so as to cause a symmetrical movement of said masses. By means of these measures, the device for regulating a timepiece mechanism can be arranged in a particularly simple and effective manner.

Furthermore, the invention also relates to a mechanical timepiece movement and a timepiece comprising at least one regulating device according to the present invention.

[0013] Other characteristics, as well as the corresponding advantages, will emerge from the dependent claims, as well as from the description setting out the invention in more detail below.

Brief description of the drawings

The accompanying drawings show schematically and by way of example several embodiments of the invention. FIG. 1a shows a schematic perspective view from above of a first embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated in order to simplify the understanding; Figure 1b shows a top plan view of the regulator device of Figure 1a; Figure 1c shows a cross-section of the regulating device along the line A-A indicated in Figure 1b. FIG. 2a shows a schematic perspective view from above of a first embodiment of a drive means for a device for regulating a timepiece mechanism according to the present invention; Figure 2b shows a top plan view of the drive means of Figure 2a; Figure 2c shows a top plan view of the drive means of Figure 2a, including a mass coupled to the drive means; Figure 2d shows a cross-section of the drive means along line B-B indicated in Figure 2c; FIG. 2e shows a schematic perspective view from above of a second embodiment of a drive means for a device for regulating a timepiece mechanism according to the present invention; Figure 2f shows a top plan view of the drive means of Figure 2e. FIG. 3a shows a schematic perspective view from above of a second embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated in order to simplify the understanding; Figure 3b shows a schematic perspective view from below of the regulating device of Figure 3a; Figure 3c shows a top plan view of the regulator device of Figure 3a; Figure 3d shows a cross-section of the regulator along line C-C shown in Figure 3c. FIG. 4a shows a schematic perspective view from below of a third embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated in order to simplify the understanding; Figure 4b shows a bottom plan view of the regulator device of Figure 4a; Figure 4c shows a bottom plan view of the controller of Figure 4a in which part of the rigid frame is illustrated; Figure 4d shows a cross-section of the regulator along line D-D shown in Figure 4c. FIG. 5a shows a schematic perspective view from below of a fourth embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated in order to simplify the understanding; FIG. 5b shows a plan view from below of the regulating device of FIG. 5a when the latter is in the neutral position; Fig. 5c shows a cross-section of the regulating device along the line E-E indicated in Fig. 5b; Figure 5d shows a bottom plan view of the regulator device of Figure 5a when the device is in a different position from Figure 5b; Figure 5e shows a bottom plan view of the regulator in the position shown in Figure 5d, including a line F-F for a cross section; Figure 5f shows a cross-section of the regulator along line F-F shown in Figure 5e. FIGS. 6a to 6h show alternative embodiments of the first embodiment of a device for regulating a timepiece mechanism according to the present invention using knife guides, flexible blades, and a monolithic design; FIG. 6a shows a schematic perspective view from above of an alternative embodiment of the first embodiment of a device for regulating a timepiece mechanism according to the present invention using a knife guide, the drive means of the device not being indicated to simplify understanding; Figure 6b shows a top plan view of the regulator device of Figure 6a; FIG. 6c shows a schematic perspective view from below of an alternative embodiment of the first embodiment of a device for regulating a timepiece mechanism according to the present invention using a guide with a flexible blade, the drive means of the device not being indicated to simplify understanding; Figure 6d shows a bottom plan view of the regulator device of Figure 6c; Figure 6e shows a cross-section of the regulator along line G-G indicated in Figure 6d; Figure 6f shows a horizontal section of the regulator device of Figure 6d; FIG. 6g shows a schematic perspective view from above of an alternative embodiment of the first embodiment of a device for regulating a timepiece mechanism according to the present invention using a monolithic design, the drive means of the device not being indicated to simplify understanding; Figure 6h shows a top plan view of the regulator device of Figure 6g. Figures 7a to 7j show alternative embodiments of the second embodiment of a device for regulating a timepiece mechanism according to the present invention using a different geometric arrangement, a flexible guide, and a flexible guide combined with oblong holes ; FIG. 7a shows a schematic perspective view from below of an alternative embodiment of the second embodiment of a device for regulating a timepiece mechanism according to the present invention using a different geometric arrangement, the drive means of the device not being indicated to simplify understanding; Figure 7b shows a schematic perspective view from above of the regulating device of Figure 7a; Figure 7c shows a top plan view of the regulator device of Figure 7a; Figure 7d shows a cross-section of the regulator along the H-H line indicated in Figure 7c; FIG. 7e shows a schematic perspective view from above of an alternative embodiment of the second embodiment of a device for regulating a timepiece mechanism according to the present invention using a flexible guide, the drive means of the device not being indicated to simplify understanding; Figure 7f shows a top plan view of the regulator device of Figure 7e; FIG. 7g shows a schematic perspective view from above of another alternative embodiment of the second embodiment of a device for regulating a timepiece mechanism according to the present invention using a flexible guide, the drive means of the device not being indicated to simplify understanding; Figure 7h shows a top plan view of the regulator device of Figure 7g; FIG. 7i shows a schematic perspective view from above of yet another alternative embodiment of the second embodiment of a device for regulating a timepiece mechanism according to the present invention using a flexible guide combined with oblong holes, the drive means of the device not being indicated to simplify the understanding; Figure 7j shows a top plan view of the regulator device of Figure 7i. FIG. 8a shows a schematic perspective view from above of an embodiment of a device for regulating a timepiece mechanism according to the present invention which is produced using two juxtaposed devices according to the first embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated to simplify understanding; Figure 8b shows a top plan view of the regulator device of Figure 8a; Figure 8c shows a bottom plan view of the regulator device of Figure 8a; Figure 8d shows a cross-section of the regulating device along the line I-I indicated in Figure 8c. FIG. 9a shows a schematic perspective view from below of an alternative embodiment of the third embodiment of a device for regulating a timepiece mechanism according to the present invention, produced using two partially superposed devices according to the first embodiment execution of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated to simplify understanding; Figure 9b shows a bottom plan view of the regulator device of Figure 9a; Figure 9c shows a cross-section of the regulator along line J-J indicated in Figure 9b. FIGS. 10a to 10f show an alternative embodiment of the fourth embodiment of a device for regulating a timepiece mechanism according to the present invention using weights in the form of dumbbells; FIG. 10a shows a schematic perspective view from below of this alternative embodiment of the fourth embodiment of a device for regulating a timepiece mechanism according to the present invention, the drive means of the device not being indicated to simplify understanding; FIG. 10b shows a plan view from below of the regulating device of FIG. 10a when the latter is in the neutral position; Figure 10c shows a cross-section of the control device along line K-K indicated in Figure 10b; Figure 10d shows a schematic perspective view from below of the regulator device of Figure 10a when the device is in a different position from Figure 10b; Figure 10e shows a bottom plan view of the regulator in the position shown in Figure 10d; Figure 10f shows a cross section of the regulator along the line L-L indicated in Figure 10e.

Detailed description of the invention

The invention will now be described in detail with reference to the accompanying drawings illustrating by way of example several embodiments of the invention.

The present invention relates to a device for regulating a watch mechanism based on an isotropic harmonic oscillator, the device being intended to be integrated into a timepiece, preferably into a wristwatch having a mechanical movement. For reasons of simplification of the language used, we will speak hereafter indiscriminately of "timepiece" and "watch", without however wishing to limit the scope of the corresponding explanations which extend in all cases to any type of timepieces, having a source of energy either mechanical or electrical. Moreover, such a device for regulating a timepiece mechanism can be integrated into modules of such a timepiece, such as a timepiece movement or other mechanisms which are likely to be equipped with a device regulating a watch mechanism according to the present invention. Because a watch movement and its essential components, or even other similar mechanisms which are adapted to be combined with the device for regulating a watch mechanism according to the invention, are known per se to those skilled in the art, the following description will be limited mainly and as far as possible to the structure and operation of said device for regulating a timepiece mechanism.

In order to first comment on the structure of a device for regulating a timepiece mechanism according to the present invention, reference is made to Figures 1a to 1c which schematically illustrate and by way of example a first embodiment of such a device capable of forming the regulating member of a watch movement. This regulation device 1 comprises a rigid frame 1.1, indicated in FIG. 1c symbolically by a plate and a bridge parallel to the plate, or even parallel bridges, which can, depending on the concrete arrangement of the device, take any necessary shape. , and at least two masses 1.3.1, 1.3.2 mounted so that they are mobile relative to the rigid frame 1.1. The regulating device 1 further comprises a variable radius drive means 1.4 which is coupled by an elastic coupling means to at least one of said masses 1.3.1, 1.3.2. Said drive means 1.4, which is not illustrated in FIGS. 1a to 1c in order to simplify understanding and which will be described in more detail below, is able to be driven by a source of energy from said piece of watchmaking, for example by a mainspring, as well as transmitting the energy received from the source of energy to said masses 1.3.1, 1.3.2 so as to set them in motion in a plane. Furthermore, the regulation device 1 further comprises inversion means 1.5 coupled to said masses 1.3.1, 1.3.2 and arranged so as to reduce the displacement of the center of mass of the regulation device during its operation, that is ie during the movement of the masses 1.3.1, 1.3.2. In addition, the regulating device 1 further comprises a support structure 1.2 pivotally mounted on said rigid frame 1.1, said masses 1.3.1, 1.3.2 being mounted on this support structure 1.1. In general, the bearing structure 1.2, the masses 1.3.1, 1.3.2, the variable radius drive means 1.4, and the inversion means 1.5 are mounted between the plates of the rigid frame 1.1, formed for example by the plate and a bridge, so that, during impacts perpendicular to the plane of the system, said plates limit the travel of the moving parts and the risk of damage. The distance between the plates and the moving parts of the device is chosen so as to avoid losses by shearing of layers of air, furthermore by providing, if necessary, absorbent protrusions attached to the moving parts or to the plates.

In order to describe in more detail the main components listed above of a device for regulating a timepiece mechanism according to the present invention, it can be seen in Figures 1a and 1b that the first embodiment of such a regulating device comprises two masses 1.3.1, 1.3.2 which are mounted on said supporting structure 1.2 and which constitute a pair of masses having a correlated movement. The supporting structure 1.2 comprises for this purpose two suspension rods 1.2.1, 1.2.2, each carrying one of said masses 1.3.1, 1.3.2 which can either be fixed on the suspension rods 1.2.1, 1.2.2 by any means known to those skilled in the art, for example by screwing, by tightening, or the like, or being made in one piece with said suspension rods 1.2.1, 1.2.2, as well as a spreader bar 1.2.3. This lifter 1.2.3 has at its center a pivot axis 1.2.3.1 which is oriented perpendicular to the longitudinal axis of the lifter as well as to said bridges forming the rigid frame 1.1 and which is pivotally mounted on this rigid frame 1.1 not -illustrated in Figures 1a and 1b, preferably with the aid of shockproof bearings 1.2.3.2 placed at the ends of the pivot axis 1.2.3.1 and each fixed in one of said bridges. Thus, said supporting structure 1.2, including the suspension rods 1.2.1, 1.2.2 and the masses 1.3.1, 1.3.2, can perform a pivoting movement in a pivoting plane which is parallel to the bridges forming the frame rigid 1.1, as shown in Figure 1c. Each of the two suspension rods 1.2.1, 1.2.2 is hinged at one of its ends, preferably via ruby bearings, at one end of the crossbar 1.2.3, the two suspension rods 1.2.1 , 1.2.2, respectively the corresponding masses 1.3.1, 1.3.2, being placed on either side of the spreader bar 1.2.3 which is in the middle. In addition, the masses 1.3.1, 1.3.2 have a shape and are oriented so that the centers of mass M1, M2, symbolically indicated by a cross in Figure 1b, of each mass 1.3.1, 1.3. 2 of said pair of masses 1.3 are aligned with the pivot axis 1.2.3.1 of the lifter 1.2.3, as shown in Figure 1b. The density of the material of masses 1.3.1, 1.3.2 is as high as possible in order to maximize the mass and minimize the inertia of each of the masses 1.3.1, 1.3.2 around an axis perpendicular to said plane of pivoting and passing through their respective center of gravity. One of the masses 1.3.1, 1.3.2, in the example illustrated in Figures 1a to 1c the mass 1.3.1, carries in its center of mass M1 a pin 1.3.1.1 oriented perpendicularly to said pivot plane and capable of being driven by said drive means 1.4 in order to transmit energy to said masses 1.3 and thus set them in motion.

To produce said correlated movement of the pair of masses 1.3, the reversing means 1.5 consist in the first embodiment of a regulating device according to the present invention in a first reversing lever 1.5.1 and a second reversing lever 1.5.2 coupled to said masses 1.3.1, 1.3.2 of the pair of masses 1.3. The first inversion lever 1.5.1 is in this embodiment oriented in extension of the longitudinal axis of the suspension rod 1.2.1 carrying the first mass 1.3.1, for example by having come from a piece with said suspension link 1.2.1 or by being fixed to this link 1.2.1, and is in particular located at the end of the suspension link 1.2.1 which is articulated to the crossbar 1.2.3, so that the first reversal lever 1.5.1 faces the suspension rod 1.2.2 carrying the second mass 1.3.2. The second inversion lever 1.5.2 is hinged at one of its ends to the other end of the suspension rod 1.2.2 carrying the second mass 1.3.2 and is hinged at its other end to the free end of the first reversing lever 1.5.1, the joints of the second reversing lever 1.5.2 being preferably also made by means of ruby bearings. The first inversion lever 1.5.1 has a length chosen so that the second inversion lever 1.5.2 is parallel to the rudder bar 1.2.3, that is to say the length of the first inversion lever 1.5.1 corresponds substantially to the length of the suspension link 1.2.2 carrying the second mass 1.3.2, and the second reversing lever 1.5.2 has a length chosen so that the assembly formed by the link of suspension 1.2.1 carrying the first mass 1.3.1 and the first inversion lever 1.5.1 is parallel to the suspension rod 1.2.2 carrying the second mass 1.3.2, that is to say the length of the second inversion lever 1.5.2 corresponds substantially to the length of the crossbar 1.2.3, so that the inversion means 1.5 and part of the supporting structure 1.2 form a parallelogram which is deformable during the movement of the masses 1.3 .1, 1.3.2 in the pivot plane, the opposite sides of said parallelogram being at all times alleles during said movement. In other words, this is thanks to the fact that, of the four joints located at the corners of said parallelogram, the two joints located at the ends of the crossbar 1.2.3 are separated by the same distance as the two joints located at the ends of the second lever inversion 1.5.2 as well as the joints located at the ends of the suspension link 1.2.2 carrying the second mass 1.3.2 are separated by the same distance as the joints located at the ends of the first inversion lever 1.5.1, which emerges very clearly from FIG. 1b. In addition, this constellation ensures that the straight line passing through the centers of mass M1, M2 of each mass 1.3.1, 1.3.2 of said pair of masses 1.3 and through the pivot axis 1.2.3.1 of the rudder bar 1.2.3 is parallel to the assembly formed by the suspension link 1.2.1 carrying the first mass 1.3.1 and the first reversing lever 1.5.1 as well as to the suspension link 1.2.2 carrying the second mass 1.3.2.

Thus, thanks to the pivot axis 1.2.3.1 of the lifter 1.2.3 of the pivoting support structure 1.2 which forms a central pivot P1as well as the four joints which are located in said parallelogram and which each constitute an additional pivot P2, P3, P4, P5, the first embodiment of a regulating device according to the present invention comprises five pivots. These pivots allow, via the inversion means 1.5 coupled to said masses 1.3.1, 1.3.2, a correlated and symmetrical movement of the masses 1.3.1, 1.3.2 in the pivot plane while reducing the displacement of the center of mass of the pair of masses 1.3 formed by these masses 1.3.1, 1.3.2, respectively of the center of mass of the entire regulating device. This is also due to the fact that the centers of mass M1, M2 of each mass 1.3.1, 1.3.2 of said pair of masses 1.3 remain aligned, during the deformation of said parallelogram during the movement of the masses 1.3.1, 1.3.2 in the pivot plane, with the pivot axis of the rudder 1.2.3.

[0021] It remains to be noted in this context that the suspension rods 1.2.1, 1.2.2, the crossbar 1.2.3, as well as the reversing levers 1.5.1, 1.5.2 are manufactured so as to be the as light as possible, for example aluminum, titanium, magnesium, carbon or another suitable material which is very light and rigid, in order to reduce as much as possible the variation of the center of mass of the whole regulating device resulting from the displacement of these components and not from the displacement of masses 1.3.1, 1.3.2. Furthermore, those skilled in the art easily understand that, for reasons of simplification and understanding, the suspension rods 1.2.1, 1.2.2, the crossbar 1.2.3, as well as the reversing levers 1.5.1, 1.5.2 have been represented, in FIGS. 1a to 1c as well as in the other figures illustrating the other embodiments of a regulation device according to the present invention, only schematically and, in particular, often almost identically, while in reality the dimensions, that is to say in particular the section, of these components are normally different. For example, in order to influence the variation of the center of mass of the entire regulating device as little as possible, the reversing levers 1.5.1, 1.5.2 illustrated in FIGS. 1a to 1c preferably have a much larger section. small than the suspension rods 1.2.1, 1.2.2, the latter being able in turn to have a section smaller than the spreader bar 1.2.3. In this way, these components have the minimum dimensions and mass required to fulfill their respective function, namely to carry the masses and allow their movement by producing a pivoting supporting structure for the suspension rods 1.2.1, 1.2.2 and the crossbar 1.2.3 as well as inverting the movement of the masses for the reversing levers 1.5.1, 1.5.2 (and also the rudder bar 1.2.3 which participates in this function). Likewise, in terms of concrete realization, it should be clarified that the shockproof bearings 1.2.3.2 mentioned above in the context of the pivot axis 1.2.3.1 and the ruby bearings mentioned above in the context of the joints of the parallelogram formed by the inversion means 1.5 and part of the supporting structure 1.2 can be replaced by any suitable means known to those skilled in the watchmaking art. In this context, it should also be noted that, apart from the variable radius drive means 1.4 which will be described below, the pivot axis 1.2.3.1, respectively its shockproof bearings 1.2.3.2, is in the first embodiment of a control device according to the present invention the only link between the supporting structure 1.2 and the rigid frame 1.1, so that the pivot axis 1.2.3.1 performs one of the main functions of the supporting structure 1.2 , namely to allow, in cooperation with the additional pivots P2, P3, P4, P5, a guided movement of the masses 1.3.1, 1.3.2 in the pivot plane. The shockproof function of this component is only secondary while being necessary in order to protect the device against shocks.

A first embodiment of a variable radius drive means 1.4 for a device for regulating a timepiece mechanism according to the present invention is illustrated in Figures 2a to 2d. This variable radius drive means 1.4 realizes, in general terms, a rotary drive system whose length of the lever transmitting the torque is variable and comprises a rotary plate 1.4.2 which is driven in rotation by a power source of the corresponding timepiece, preferably by a source of mechanical energy such as a spiral spring housed in a barrel which is kinematically linked to a clockwork train. The barrel and the gear train are not illustrated in the figures, since they are well known to those skilled in the art, and the gear train can simply comprise a drive pinion 1.4.1 on which said rotary plate 1.4.2 is fixed coaxially. which rotates with the drive pinion 1.4.1 driven by the mainspring. In principle, it can also be a source of electrical energy, for example if the drive pinion 1.4.1, respectively said rotary plate 1.4.2, is driven by an electric motor, so that A device for regulating a timepiece mechanism according to the present invention can be integrated into a timepiece having a source of energy that is either mechanical or electrical. The turntable 1.4.2 carries a support lever 1.4.3 articulated at one of its ends which is located substantially on the periphery of the turntable 1.4.2. The free end of the support lever 1.4.3 is oriented towards the center of the rotary plate 1.4.2 and has on its front face oriented towards the center of the rotary plate 1.4.2 a substantially V-shaped notch which is able to receive either directly said pin 1.3.1.1 fixed on one of the masses 1.3.1, 1.3.2 of the pair of masses 1.3, or a roller 1.3.1.2 mounted on said pin 1.3.1.1 in order to reduce the friction forces between the lever support 1.4.3 and said pin 1.3.1.1. A return spring 1.4.4 substantially in the shape of a U mounted on the rotary plate 1.4.2 presses on the rear face of the free end of the support lever 1.4.3, so that its front face constrains , via the substantially V-shaped notch, the roller 1.3.1.2, respectively said pin 1.3.1.1 fixed to one of the masses 1.3.1, 1.3.2 of the pair of masses 1.3, against an eccentric 1.4 .5 mounted on the turntable 1.4.2. By adjusting the position of the eccentric 1.4.5 which is mounted close to the center of the rotary plate 1.4.2, it is possible to ensure that said pin 1.3.1.1 is never, during normal operation of the regulating device, merged with the center of the rotary plate 1.4.2, that is to say that the pin 1.3.1.1 normally always has a slight eccentricity with respect to the rotary plate 1.4.2. Thus, a rotation of the rotary plate 1.4.2, driven by the energy source of the corresponding timepiece via the gear train, causes a movement of the pin 1.3.1.1, so that the masses 1.3 .1, 1.3.2 of the pair of masses 1.3 are driven, with their pivoting supporting structure 1.2 and the reversing means 1.5, moving in said pivoting plane. The support lever 1.4.3, respectively the substantially V-shaped notch on its front face, realizes in cooperation with the return spring 1.4.4 a substantially radial guiding of the roller 1.3.1.2, respectively of the pin 1.3. 1.1, relative to the center of the turntable 1.4.2. The eccentricity of the pin 1.3.1.1 with respect to the center of the rotary plate 1.4.2 also guarantees self-starting of the regulating device following a stop, for example following winding of the barrel spring serving as a source of energy.

Simultaneously, the variable radius drive means 1.4 has anti-shock means in order to avoid any breakage of the kinematic connection, namely the pin 1.3.1.1, between the variable radius drive means 1.4 and the masses 1.3 in the event of external shocks. Indeed, in the event of a transverse shock overload, that is to say a shock oriented transversely to the substantially radial guiding of the pin 1.3.1.1 produced by the substantially V-shaped indentation of the front face of the lever support 1.4.3 in cooperation with the return spring 1.4.4, the support lever 1.4.3 moves back while pivoting slightly and the roller 1.3.1.2 slides or rolls on the inclined plane of the notch substantially in the shape of V of the front face of the support lever 1.4.3. In the event of a radial shock overload, that is to say a shock oriented parallel to the substantially radial guide, the support lever 1.4.3 also moves back in the direction of the shock. For the latter case, the eccentric 1.4.5 can preferably be mounted on the rotary plate 1.4.2 using an eccentric lever which carries the eccentric 1.4.5 and which is prestressed by a preload spring towards the rest position of the eccentric 1.4.5. This configuration is not illustrated in Figures 2a to 2d, but also allows protection against radial shocks in the direction of the eccentric 1.4.5, because in this case it is the eccentric lever including the eccentric 1.4.5 which moves back instead of the support lever 1.4.3. In all cases, after a certain stroke following a shock, the masses 1.3.1, 1.3.2 hit stops which can for example be provided on the rigid frame 1.1 and are not illustrated in the figures.

A second embodiment of a variable radius drive means 1.4 for a device for regulating a timepiece mechanism according to the present invention is illustrated in FIGS. 2e and 2f. This variable radius drive means 1.4 also comprises a rotary plate 1.4.2 which is driven in rotation by a power source of the corresponding timepiece in the same way as explained above. Similarly, the rotary plate 1.4.2 also carries in this embodiment a support lever 1.4.7, an eccentric 1.4.5, and a return spring 1.4.4. These parts do not all have exactly the same role as in the first embodiment of the drive means. Indeed, in the second embodiment of the drive means, it is the U-shaped return spring 1.4.4 which has on its free end a substantially V-shaped notch and formed directly by the blade of the return spring 1.4.4 in order to accommodate the roller 1.3.1.2, respectively said pin 1.3.1.1 fixed to one of the masses 1.3.1, 1.3.2 of the pair of masses 1.3, the free end of the return spring 1.4 .4 preferably also having an additional loop which constrains the roller 1.3.1.2, respectively said pin 1.3.1.1, in said substantially V-shaped notch. Thus, it is in this embodiment only the return spring 1.4 .4 which ensures, by deformation of its U-shaped blade, the substantially radial guiding of the roller 1.3.1.2, respectively of the pin 1.3.1.1, with respect to the center of the rotary plate 1.4.2. Indeed, as in the first embodiment of the drive means, the roller 1.3.1.2, respectively said pin 1.3.1.1, performs during the movement of the masses 1.3.1, 1.3.2 in the pivot plane a movement substantially rectilinear and radial with respect to the center of the rotary plate 1.4.2. The support lever 1.4.7, also articulated at one of its ends on the rotary plate 1.4.2, presses with a protrusion on its front face either directly on the roller 1.3.1.2, respectively said pin 1.3.1.1, or preferably on said additional loop on the free end of the return spring 1.4.4, so as to guarantee, during normal operation of the regulating device, a minimum eccentricity of the pin 1.3.1.1 with respect to the center of the rotary plate 1.4. 2. To ensure this eccentricity, respectively the normal position of the support lever 1.4.7 which defines said minimum eccentricity, an eccentricity preload spring 1.4.6 is fixed on the rotary plate 1.4.2 and constrains the support lever 1.4 .7 against an eccentric 1.4.5 mounted on the rotary plate 1.4.2, an adjustment of the position of said eccentric 1.4.5 allowing adjustment of the normal position of the support lever 1.4.7. The eccentricity of the pin 1.3.1.1 with respect to the center of the rotary plate 1.4.2 obviously also guarantees in this case a self-starting of the regulating device following a stop. Simultaneously, this configuration automatically has shock protection, since in the event of a transverse or radial shock overload the U-shaped return spring 1.4.4 will deform, until the masses 1.3. 1, 1.3.2 type, after a certain stroke following a shock, on stops provided on the rigid frame 1.1. Furthermore, it is possible to provide, in the two embodiments of a variable radius drive means 1.4, a limitation of the space available for the movement of the pin 1.3.1.1 or of a cylinder coaxial with said pin, for example by a bore in part of the frame 1.1. This option is not illustrated in the figures, but makes it possible to limit the amplitude of the movement of the pin 1.3.1.1, respectively of the masses 1.3.1, 1.3.2, and to slow down the speed of rotation in the event of exceeding the speed by the viscous friction of the air which will be sheared in the small space available between the pin 1.3.1.1 and said bore or by dry friction in extreme cases. The bore in part of the frame 1.1 can be arranged so that, during impacts, the pin 1.3.1.1 abuts against the inside of the bore before the mechanism is damaged.

In both embodiments of the variable radius drive means 1.4 described above, the return spring 1.4.4 is chosen and calibrated so as to form, on the one hand, an elastic coupling means which is capable of coupling said drive means 1.4 to at least one of masses 1.3.1, 1.3.2 so as to transmit the energy received from the energy source of the corresponding timepiece to said masses 1.3 and to put the masses 1.3.1, 1.3.2 in motion when said drive means 1.4 is driven by said energy source. On the other hand, the return spring 1.4.4 is chosen and calibrated so as to form an elastic return means of the masses 1.3.1, 1.3.2 ensuring the natural frequency of the movement of these masses 1.3.1, 1.3.2 . In particular, it has an elastic constant K adapted to the targeted stabilized rotation frequency and able to ensure a linear restoring force. Consequently, the return spring 1.4.4 serves simultaneously as a means of transmitting the driving force as well as an elastic return means for the masses 1.3.1, 1.3.2 of the regulating device. Preferably and as is the case in the first embodiment of the regulating device illustrated in FIGS. 1a to 1c, the drive means 1.4 is coupled directly and decentralized to one of said masses 1.3.1, 1.3.2 through said return spring 1.4.4.

The previous explanations concerning the structure of the first embodiment of a device for regulating a timepiece mechanism according to the present invention, in particular at the level of the supporting structure 1.2 and the reversing means 1.5 as well as at the variable radius drive means 1.4, make it easy to understand its operation. Indeed, it emerges from the description appearing above of the regulating device illustrated in FIGS. 1a to 1c that, upon activation, or even winding, of the energy source of the corresponding timepiece, the drive of the cog by said energy source causes, independently of the use of the first - or of the second embodiment of the variable radius drive means 1.4 and via the drive pinion 1.4.1 which is integrated into the gear train, a rotation of the rotary plate 1.4.2. The latter in turn causes, via the return spring 1.4.4 transmitting the driving force, a movement of the pin 1.3.1.1 fixed to the center of mass M1, M2 of one of the masses 1.3.1, 1.3 .2, so that the masses 1.3.1, 1.3.2 of the pair of masses 1.3 are driven, with their pivoting supporting structure 1.2 and the reversing means 1.5, in motion in the pivoting plane of the structure pivoting bearing 1.2. The bearing structure 1.2 and the reversing means 1.5, in particular the pivot. central P1 of the supporting structure 1.2, formed by its pivot axis 1.2.3.1, as well as the four joints P2, P3, P4, P5 of the parallelogram formed by the inversion means 1.5 and part of the supporting structure 1.2, guarantee a movement correlated and symmetrical masses 1.3.1, 1.3.2 in said pivot plane, during which the centers of mass M1, M2 of each mass 1.3.1, 1.3.2 of said pair of masses 1.3 remain aligned with the pivot axis of the lifter 1.2.3 of the pivoting support structure 1.2. In general, the cooperation between the bearing structure 1.2 and the inversion means 1.5 defines a guiding of the masses 1.3.1, 1.3.2 which guarantees a correlated and symmetrical movement of these masses 1.3.1, 1.3.2 in the plane of pivoting, thus making it possible to reduce the displacement of the center of mass of the whole of the regulating device. During this guided movement of the masses 1.3.1, 1.3.2, the return spring 1.4.4 carries out, by its action as a return spring 1.4.4 exerting on the driven mass 1.3.1, 1.3.2 a force linear return oriented substantially radially towards the center of the rotary plate 1.4.2 and where appropriate in cooperation with the support lever 1.4.3, 1.4.7, a substantially radial guiding of the pin 1.3.1.1, respectively of the roller 1.3 .1.2, and therefore from the center of mass M1, M2 of the driven mass 1.3.1, 1.3.2, on the rotary plate 1.4.2. Thus, under the effect of the rotation of the rotary plate 1.4.2, of the substantially radial guidance on said rotary plate 1.4.2 and of the masses 1.3.1, 1.3.2 as well as due to the linear and isotropic central restoring force exerted on a mass in orbit, the pin 1.3.1.1, respectively the center of mass M1, M2 of the driven mass 1.3.1, 1.3.2 describes a circular or elliptical trajectory whose amplitude stabilizes the speed of rotation of the rotary plate 1.4 .2, respectively of the cog. This results in a period of the rotational motion which should be, at least theoretically, constant.

Consequently, a regulating device according to the present invention produces an isotropic harmonic oscillator and then makes it possible to intrinsically regulate the speed of rotation of the gear train to which it is kinematically linked via the variable radius drive means 1.4, in particular the drive pinion 1.4.1. It can therefore serve as a time base in chronometry, without the need to connect a conventional horological escapement to this gear train. The five-pivot regulating device according to the first embodiment described above makes it possible to reduce the inevitable deviations in any physical realization of an isotropic harmonic oscillator of its theoretically constant and desired rotational movement period, given that it is balanced with respect to gravity, that is to say changes of position in space of a watch housing this device, as well as with respect to disturbances due to linear accelerations , that is to say shocks in translation. On the other hand, the first embodiment of this regulation device is not balanced with respect to rotational accelerations, that is to say rotational shocks. The eccentricity of the pin 1.3.1.1, respectively of the roller 1.3.1.2, and therefore of the center of mass M1, M2 of the driven mass 1.3.1, 1.3.2 with respect to the center of the rotary plate 1.4.2 guarantees a self- starting of the regulation device following a stoppage or deactivation of the energy source of the corresponding timepiece, for example following winding of the mainspring in the case of a mechanical energy source.

In the following description, other embodiments of a control device according to the present invention will be described. These embodiments differ from the first embodiment of the regulation device mainly by the arrangement and the resulting characteristics of the pivoting supporting structure as well as the inversion means used, then, sometimes, by the number of masses mounted on the supporting structure. On the other hand, these embodiments may further comprise one or other of the embodiments of the variable radius drive means 1.4 described above or any other equivalent variable radius drive means , which also applies to the first embodiment of the regulating device. Moreover, the general operation of the corresponding regulation devices is always analogous to the operation of the first embodiment of a regulation device according to the present invention. For these reasons, the following description will not repeat the details already appearing above neither at the level of the variable radius drive means nor at the level of the operation of these devices, but will concentrate on explaining the arrangement and the characteristics of the supporting structures as well as the corresponding inversion means and any particularities in the operation of the corresponding regulation devices which result therefrom.

A second embodiment of a control device according to the present invention is illustrated in Figures 3a to 3d. This regulation device also comprises two masses 1.3.1, 1.3.2, that is to say a pair of masses 1.3, which are carried by a corresponding supporting structure 1.2. In this embodiment, the supporting structure 1.2 comprises a first lifter 1.2.3 and a second lifter 1.2.4 each of which comprises a pivot axis 1.2.3.1, 1.2.4.1 linked via shockproof bearings 1.2.3.2 , 1.2.4.2 corresponding to the rigid frame 1.1. In addition, the supporting structure 1.2 comprises, on either side of the first crossbar 1.2.3 which is located in the middle, two suspension rods 1.2.1, 1.2.2 each carrying one of said masses 1.3.1, 1.3.2 . The two suspension rods 1.2.1, 1.2.2 are oriented substantially perpendicular to the longitudinal axis of the first crossbar 1.2.3 as well as articulated both at the corresponding end of the masses 1.3.1, 1.3.2 and at the corresponding end of the first lifter 1.2.3, for example using ruby bearings. The inversion means 1.5 of the second embodiment of a regulating device according to the present invention can then simply consist of a first inversion lever 1.5.1 hinged to one end of the second crossbar 1.2.4 and fixed the other side to the first mass 1.3.1 as well as a second inversion lever 1.5.2 hinged to the other end of the second crossbar 1.2.4 and fixed on the other side to the second mass 1.3.2 of the pair of masses 1.3, the second lifter 1.2.4 being in fact oriented substantially perpendicular to the first lifter 1.2.3. Again, the suspension rods 1.2.1, 1.2.2 and the reversing levers 1.5.1, 1.5.2 are manufactured as lightly as possible, the reversing levers 1.5.1, 1.5.2 being able to , preferably, be even lighter than the suspension rods 1.2.1, 1.2.2 and can for example be constituted by double triangular arms as illustrated in Figures 3a to 3c. The second embodiment of a regulating device according to the present invention then comprises eight pivots P1, P2, P3, P4, P5, P6, P7, P8 in the form of the two pivot axes 1.2.3.1, 1.2.4.1 of the first lifter 1.2.3 and the second lifter 1.2.4 as well as the six joints on the suspension rods 1.2.1, 1.2.2 and the reversing levers 1.5.1, 1.5.2, as emerges for example from the Figure 3c.

[0030] As regards the functions attributed to these parts, it should be noted, insofar as there are particularities with respect to what has been described above with respect to the first embodiment of the device regulation, that the first crossbar 1.2.3 ensures, in cooperation with the suspension rods 1.2.1, 1.2.2, the symmetry of the correlated movement of the masses 1.3.1, 1.3.2 and the balance with respect to the direction perpendicular to the line passing through the pivot axes 1.2.3.1, 1.2.4.1 of the spreaders 1.2.3, 1.2.4. In this context, it may be noted that the first crossbar 1.2.3 may be slightly asymmetrical with respect to its pivot axis 1.2.3.1 in order to take into account the difference in position of the attachment points of the suspension rods 1.2.1, 1.2.2 on masses 1.3.1, 1.3.2. The second lifter 1.2.4 ensures, in cooperation with the inversion levers 1.5.1, 1.5.2, the symmetry of the movement and the balance with respect to the other direction in the pivoting plane of the bearing structure 1.2, that is to say the direction parallel to the line passing through the pivot axes 1.2.3.1, 1.2.4.1 of the pedals 1.2.3, 1.2.4. It should be noted in this context that, as in the first embodiment of the regulation device, it is not possible to completely separate the functions of the supporting structure 1.2 and of the inversion means 1.5, since at least one of these two parts of the device has, and in the second embodiment of the regulating device each of them, two functions, namely carrying the masses as well as guiding the movement in order to cause a correlated and symmetrical movement of the masses 1.3 .1, 1.3.2. Therefore, depending on the specific constellation, the reversing means 1.5 either are simply located on the supporting structure 1.2 or simultaneously form part of said supporting structure 1.2. The shape and composition of the masses 1.3.1, 1.3.2 are chosen so as to ensure that, in the position of the device illustrated in FIG. 3c, the center of gravity of each mass 1.3.1, 1.3.2 is on a straight line passing through the pivot axis of the first rudder bar 1.2.3 and perpendicular to the line passing through the pivot axes 1.2.3.1, 1.2.4.1 of the rudder bar 1.2.3, 1.2.4. In addition, this choice is made so that the positions of the centers of gravity of each mass 1.3.1, 1.3.2 are symmetrical with respect to the straight line passing through the pivot axes 1.2.3.1, 1.2.4.1 of the spreaders 1.2.3, 1.2.4 as well as the center of gravity of each mass 1.3.1, 1.3.2 is on a straight line parallel to the straight line passing through the pivot axes 1.2.3.1, 1.2.4.1 of the rudder bars 1.2.3, 1.2.4 and passing through the corresponding lateral articulation of the second crossbar 1.2.4. Using such a configuration, the masses 1.3.1, 1.3.2 move, once driven by the corresponding variable radius drive means 1.4 via a pin fixed to the center of gravity of one of the masses 1.3.1, 1.3.2, in pseudotranslation and, for low displacement amplitudes, the angular parasitic movements are minimal, respectively negligible. Furthermore, the other explanations appearing above with respect to the first embodiment of the regulation device apply by analogy to the second embodiment. In particular, this regulation device with eight pivots is likewise balanced with respect to gravity and translational accelerations. The pivots of the spreaders 1.2.3, 1.2.4 are again, preferably, anti-shock systems constructed according to the same principle as the pivot of a balance wheel - conventional watchmaker's hairspring and all the other pivots are also of the watchmaker's type, with a pin of very small diameter in the bore of a ruby.

A third embodiment of a control device according to the present invention is illustrated in Figures 4a to 4d. This regulation device also comprises two masses 1.3.1, 1.3.2, that is to say a pair of masses 1.3, which are carried by a corresponding supporting structure 1.2. In this embodiment, the two masses 1.3.1, 1.3.2 are arranged one on top of the other in two parallel planes, in particular so that the centers of mass M1, M2 of the masses 1.3.1, 1.3 .2 are superimposed in the neutral position of the device, as shown schematically in Figure 4a. The supporting structure 1.2 comprises in this case a first lifter 1.2.3 and a second lifter 1.2.4 which both have substantially an L-shape as well as a third lifter 1.2.5 of straight shape each of which comprises a pivot axis 1.2.3.1, 1.2.4.1, 1.2.5.1 which connect the supporting structure 1.2, preferably by means of corresponding anti-shock bearings 1.2.3.2, 1.2.4.2, 1.2.5.2, to the rigid frame 1.1, the pivot axes 1.2 .3.1, 1.2.4.1, 1.2.5.1 forming corresponding pivots P1, P2, P3. The first lifter 1.2.3 and the second lifter 1.2.4 substantially L-shaped each comprise a first arm oriented towards the masses 1.3.1, 1.3.2 and a second arm oriented towards the corresponding second arm of the other lifter substantially a shape of L. The first arm of the first lifter 1.2.3 is articulated at its free end, by a pivot P4, at one end of a first suspension rod 1.2.1 which carries in its middle the first mass 1.3.1 and which is articulated at the other end, by a pivot P5, at one end of a first inversion lever 1.5.1 of the inversion means 1.5. The other end of this first inversion lever 1.5.1 is hinged, by a pivot P6, to one end of the third crossbar 1.2.5. Similarly, the first arm of the second crossbar 1.2.4 is articulated at its free end, by a pivot P7, at one end of a second suspension rod 1.2.2 which is located in a plane parallel to the plane in which finds the first suspension link 1.2.1 and which carries in its middle the second mass 1.3.2. The other end of the second suspension link 1.2.2 is hinged, by a pivot P8, to one end of a second reversing lever 1.5.2 of the reversing means 1.5, this second reversing lever 1.5. 2 being articulated at the other end, by a pivot P9, at the other end of the third spreader bar 1.2.5. In addition, the second arm of the first lifter 1.2.3 and of the second lifter 1.2.4 are linked, via pivots P10, P11, to one, respectively to the other end of a third lever of inversion 1.5.3 inversion means 1.5. In order to have the necessary space for the third inversion lever 1.5.3, the second arm of the first rudder 1.2.3 forms an angle slightly less than a right angle with respect to its first arm and the second arm of the second rudder 1.2.4 forms an angle slightly greater than a right angle to his first arm, or vice versa. Again, the suspension rods 1.2.1, 1.2.2 and the reversing levers 1.5.1, 1.5.2, 1.5.3 are manufactured as lightly as possible. Thus, as in the other embodiments of a regulation device described above or below comprising several lifters, the three lifters 1.2.3, 1.2.4, 1.2.5 are connected by a kinematic chain formed by the suspension rods 1.2.1, 1.2.2 and the reversing levers 1.5.1, 1.5.2, 1.5.3 which are located on or form part of the bearing structure 1.2.

The third embodiment of a regulating device according to the present invention then comprises eleven pivots P1, P2, P3, P4, P5, P6, P7, P8, P9, P10, P11 in the form of three pivot axes 1.2.3.1, 1.2.4.1, 1.2.5.1 of the three spreaders 1.2.3, 1.2.4, 1.2.5 as well as eight joints on the suspension rods 1.2.1, 1.2.2 and the reversing levers 1.5. 1, 1.5.2, 1.5.3, as shown for example in Figure 4a. In this context, it should also be specified that, on one side, the pivots P4, P8, and, on the other side, the pivots P5, P7 are superimposed in the neutral position of the device without however being in contact. Moreover, in order to guarantee the desired guidance of the movement of the masses 1.3.1, 1.3.2, the distance between the pivots P4 and P5 is equal to the distance between the pivots P7 and P8 as well as the distance between the pivots P6 and P9. Preferably, this distance also corresponds to the distance between the pivots P1 and P2, which can all the same be chosen differently by modifying the angles between the first arm and the second arm of the first and of the second crossbar 1.2.3, 1.2.4. Similarly, the distance between the pivots P1 and P4 is equal to the distance between the pivots P2 and P7, the distance between the pivots P8 and P9, as well as the distance between the pivots P5 and P6.

[0033] As regards the functions assigned to these parts, it should be noted, insofar as there are particularities with respect to what has been described above with respect to the first and second forms of execution of the regulating device, which the first and second crossbars 1.2.3, 1.2.4 ensure, in cooperation with the suspension rods 1.2.1, 1.2.2 and the third reversing lever 1.5.3, the symmetry of the correlated movement of the masses 1.3.1, 1.3.2 and the balance with respect to a first direction in the pivot plane, while the third rudder 1.2.5 ensures, in cooperation with the first and second inversion levers 1.5. 1, 1.5.2, the symmetry of the correlated motion of the masses 1.3.1, 1.3.2 and the balance with respect to the direction perpendicular to said first direction in the pivot plane. Furthermore, due to the fact mentioned above that the masses 1.3.1, 1.3.2 are located one on top of the other, this device comprises a double pivoting plane of the pivoting structure 1.2. Finally, it remains to be noted with respect to this embodiment that this regulating device with eleven pivots is balanced with respect to gravity and accelerations in translation as well as, contrary to the first and second embodiments of the regulation device and due to the arrangement of the masses 1.3.1, 1.3.2 so that the centers of gravity M1, M2 of the masses 1.3.1, 1.3.2 coincide in the neutral position of the device, also vis- with respect to rotational accelerations.

A fourth embodiment of a control device according to the present invention is illustrated in Figures 5a to 5f. This regulation device also comprises two masses 1.3.1, 1.3.2, that is to say a pair of masses 1.3, which are carried by a corresponding supporting structure 1.2, the two masses 1.3.1, 1.3.2 being again arranged one on top of the other in two parallel planes, in particular so that the centers of mass M1, M2 of the masses 1.3.1, 1.3.2 are superimposed in the neutral position of the device, as illustrated diagrammatically in figures 5a to 5c. In this embodiment, the supporting structure 1.2 comprises a first lifter 1.2.3, a second lifter 1.2.4, a third lifter 1.2.5 and a fourth lifter 1.2.6 each of which comprises a pivot axis 1.2.3.1, 1.2.4.1, 1.2.5.1, 1.2.6.1 linked via shockproof bearings 1.2.3.2, 1.2.4.2, 1.2.5.2, 1.2.6.2 corresponding to the rigid frame 1.1 and each of which has two arms of identical and perpendicular length to one another. The first spreader 1.2.3 and the second spreader 1.2.4 carry, with the aid of first and second suspension rods 1.2.1, 1.2.2, the first mass 1.3.1. To this end, the first suspension rod 1.2.1 is articulated at one of its ends to an arm of the first spreader bar 1.2.3 and at its other end to said first mass 1.3.1, while the second suspension rod 1.2. 2 is hinged at one of its ends to an arm of the second lifter 1.2.4 and is fixed at its other end to said first mass 1.3.1. Similarly, the third lifter 1.2.5 and the fourth lifter 1.2.6 carry, with the aid of the third and fourth suspension rods 1.2.7, 1.2.8, the second mass 1.3.2. To this end, the third suspension link 1.2.7 is articulated at one of its ends to an arm of the third crossbar 1.2.5 and is fixed at its other end to said second mass 1.3.2, while the fourth suspension link 1.2.8 is articulated at one of its ends to an arm of the fourth crossbar 1.2.6 and its other end to said second mass 1.3.2. In addition, the supporting structure 1.2 comprises in this embodiment of the regulating device a first inversion lever 1.5.1 of the inversion means 1.5 which is articulated at one of its ends to the other arm of the first lifter 1.2 .3 and at its other end to the other arm of the third lifter 1.2.5 as well as a second reversal lever 1.5.2 which is articulated at one of its ends to the other arm of the second lifter 1.2.4 and at its other end at the other arm of the fourth rudder 1.2.6. Consequently, similarly to the other embodiments of a regulation device described above or below comprising several lifters, the four lifters 1.2.3, 1.2.4, 1.2.5, 1.2.6 are connected by a kinematic chain formed by the suspension rods 1.2.1, 1.2.2, 1.2.7, 1.2.8 and the reversing levers 1.5.1, 1.5.2 which are located on or form part of the structure bearing 1.2.

As is apparent for example from Figure 5d, the fourth embodiment of a regulating device according to the present invention comprises fourteen pivots P1, P2, P3, P4, P5, P6, P7, P8, P9 , P10, P11, P12, P13, P14 in the form of four pivot axes 1.2.3.1, 1.2.4.1, 1.2.5.1, 1.2.6.1 of the four crossbars 1.2.3, 1.2.4, 1.2.5, 1.2.6, six joints on the suspension rods 1.2.1, 1.2.2, 1.2.7, 1.2.8, as well as four joints on the reversing levers 1.5.1, 1.5.2. The arrangement of the parts is such that, in the neutral position of the device, the pivots P3et P8, on the one hand, and the pivots P5et P10, on the other hand, are superimposed, without however being in contact, such as the connecting rods corresponding suspensions 1.2.1 and 1.2.7, on the one hand, and 1.2.2 and 1.2.8, on the other hand. Due to the arrangement of the masses 1.3.1, 1.3.2 so that the centers of gravity M1, M2 of the masses 1.3.1, 1.3.2 coincide in the neutral position of the device, this embodiment of a fourteen-pivot regulating device is also balanced with respect to gravity and translational accelerations as well as rotational accelerations. The general operation of this device also corresponds to the explanations given above, in particular in terms of drive via the variable radius drive means 1.4, except that a pin 1.3.2.1 has in this case been placed, by way of example, on the second mass 1.3.2.

In the following description, several other embodiments of a regulating device according to the present invention will be described, these embodiments corresponding to variants and alternative embodiments, for example using equivalent means, of the embodiments of the control device described above, this mainly at the level of the realization of the pivoting supporting structure as well as the reversing means, more particularly at the level of the means used for the realization of the pivots. Therefore, it is obvious that these embodiments may further comprise one or other of the embodiments of the variable radius drive means 1.4 described above or any other means of equivalent variable radius drive, without it being necessary to describe these drive means here. Moreover, the general operation of these alternative regulation devices is analogous to the operation of the corresponding embodiment of the regulation device shown above. For these reasons, the following description will not repeat the details already appearing above neither at the level of the variable radius drive means nor at the level of the operation of these devices, but will concentrate on explaining the alternative embodiment of the load-bearing structures as well as corresponding reversing means and possible peculiarities in the operation of the corresponding regulation devices which result therefrom.

To this end, Figures 6a to 6h schematically show alternative embodiments of the first embodiment of a device for regulating a timepiece mechanism according to the present invention described above with the aid of Figures 1a at 1c. In particular, FIGS. 6a and 6b illustrate an alternative embodiment of the first embodiment of the device for regulating a timepiece mechanism using knife guides. In this case, in order to minimize friction and play in the transmission, the four pivots P2, P3, P4, P5 located at the corners of the parallelogram mentioned above in the context of the description of the first embodiment and formed by the rudder 1.2.3, the first and second reversing levers 1.5.1, 1.5.2 and the second suspension rod 1.2.2 are constructed using knife guides instead of ruby bearings. To this end, the first inversion lever 1.5.1 and the second suspension rod 1.2.2 have, at the locations of the pivots P2, P3, P4, P5, V-shaped notches each of which is able to accommodate a knife edge provided on the ends of the rudder bar 1.2.3 and of the second reversing lever 1.5.2. This makes it possible to avoid the play of a ruby bearing and to integrate an anti-shock system. In addition, two springs are arranged on either side of the second mass 1.3.2, in each case outside the rudder bar 1.2.3, respectively the second reversing lever 1.5.2, as illustrated in by way of example in Figures 6a and 6b, in order to produce a preload in the parallelogram, which generates a little friction at the level of each knife bearing. To ensure better symmetry of the system, the two springs can alternately be arranged on either side of the second mass 1.3.2 with respect to the 3rd dimension not visible in FIG. 6b, that is to say in below and/or above the crossbar 1.2.3, respectively the second reversing lever 1.5.2. The length of the springs is substantially identical to that of the crossbar 1.2.3 and of the second reversing lever 1.5.2, in order to avoid restoring forces in the rest position. In addition, the lifter 1.2.3 and the second reversing lever 1.5.2 have projections, not visible in the figures, on either side of the first reversing lever 1.5.1 and the second suspension rod 1.2. 2 in order to limit the relative displacement and to ensure the return of the blades to the bottom of the V-shaped notches following an impact, then in order to avoid any untimely dismantling during impacts. On each knife bearing, a lateral stop very close to the cutting edge of the knife is provided in order to prevent movement along said 3rd dimension not visible in FIG. 6b. Furthermore, the operation of this alternative embodiment of the first embodiment of the regulation device corresponds to the detailed explanations appearing above.

[0038] Figures 6c to 6f illustrate a preferred alternative embodiment of the first embodiment of the regulating device according to the present invention using a guide with a flexible blade. Indeed, such a regulating device can be produced using flexible blades, which makes it possible to further minimize the play and the friction generated at the level of the pivots. Such an embodiment requires ensuring that the rigidity of the flexible blades used does not disturb the operation of the regulation device, in particular that their use does not produce an excessively high natural frequency at the level of the rotary plate 1.4.2 of the means of drive 1.4 while guaranteeing a constant centripetal return force by the return spring 1.4.4 regardless of the angular position of the rotary plate 1.4.2 of the drive means 1.4. In the alternative embodiment of the first embodiment of the regulating device illustrated in FIGS. 6c to 6f, the spreader bar 1.2.3 is still linked to the rigid frame by means of a shockproof bearing forming the central pivot P1, but has openings in its side arms making it possible to accommodate freely in translation, on one side, the part formed by the first suspension rod 1.2.1 and the first reversing lever 1.5.1 and, on the other side, the second suspension link 1.2.2. The first suspension rod 1.2.1 and the second suspension rod 1.2.2 each comprise, arranged parallel to their respective longitudinal axis, a flexible blade which is fixed at one end to a lateral protrusion at the outer end of the rods suspension 1.2.1, 1.2.2 and at the other end at the corresponding end of the spreader bar 1.2.3. The second reversing lever 1.5.2 is made entirely as a flexible blade and is attached at its ends to the first reversing lever 1.5.1 and to the second suspension rod 1.2.2. The flexible blades can be fixed to the corresponding parts of the supporting structure 1.2, respectively inversion means 1.5, by any means known to those skilled in the art or can also be manufactured in one piece with these parts, and also with the masses 1.3 .1, 1.3.2, for example by wire EDM cutting or made in Si by conventional processes, with very thin bending thickness zones and, where appropriate, with inserts of high density material for securing the masses 1.3.1, 1.3.2. In an alternative embodiment not shown in the figures, the central pivot P1 can be ensured by an elastic guide with crossed blades or concurrent blades, an anti-overload system being integrated in these two cases either between the crossed blade assembly and the rigid frame 1.1, or between the cross blade assembly and the other parts of the pivoting support structure 1.2. Furthermore, the operation of this alternative embodiment of the regulating device is identical to that of the first embodiment of the regulating device.

[0039] Figures 6g and 6h illustrate yet another preferred alternative embodiment of the first embodiment of the control device using a monolithic design. In this case, all the parts of the supporting structure 1.2 and the reversing means 1.5 and, if desired, also the masses 1.3.1, 1.3.2 and their fastening elements, are in the form of a single monolithic piece. which can for example be cut by wire spark erosion or manufactured by any other conventional method known to those skilled in the art. In the case where the masses form separate parts, each of them can for example be made in two parts and tightened on the monolithic part at the appropriate places. The bearing structure 1.2, respectively the central beam 1.2.3, comprises in this alternative embodiment a U-shaped part 1.2.3.3 which forms the central pivot P1 and is fixed by clamping to the rigid frame 1.1. This device can be protected against out-of-plane shocks by being arranged with clearance between two plates, for example the plate and a bridge of the rigid frame 1.1, so that the masses 1.3.1, 1.3.2 abut against these front plates d reach their elastic limit. Furthermore, the operation of this alternative embodiment of the regulating device is identical to that of the first embodiment of the regulating device.

[0040] In general, although the alternatives at the level of the concrete embodiment, in particular parts of the supporting structure and the inversion means 1.5 as well as the pivots, have been described above in the context of the first form of execution of a regulating device according to the present invention, it is obvious that these embodiments using knife blades, flexible blades, or a monolithic design can be transposed to the other embodiments of the regulating device described above or below.

[0041] Figures 7a to 7j schematically show alternative embodiments of the second embodiment of a device for regulating a timepiece mechanism according to the present invention described above with the aid of Figures 3a to 3d. In particular, FIGS. 7a to 7d illustrate an alternative embodiment of the second embodiment of the device for regulating a timepiece mechanism in which all the pedals are positioned outside with respect to the masses. Indeed, depending on the configuration of the timepiece in which the device should be integrated, respectively its movement, it may be advantageous to move the first spreader bar 1.2.3 outside the zone where the two masses are located. 1.3.1, 1.3.2. Furthermore, the remarks appearing above concerning the relative positions of the pivots P1, P2, P3, P4, P5, P6, P7, P8 and the centers of gravity of the masses of the second embodiment of a regulating device are still valid and the operation of this alternative embodiment of the regulating device is also identical to that of the second embodiment of the regulating device.

[0042] Figures 7e and 7f illustrate an alternative embodiment of the second embodiment of the device for regulating a timepiece mechanism in which the technical instruction of the alternative embodiment described above comprising pedals positioned outside relative to the masses is combined with the technical instruction of the alternative embodiment illustrated in the context of Figures 6c to 6f, i.e. to use a flexible blade guide. Indeed, the device shown schematically in Figures 7e and 7f comprises, instead of shockproof or ruby bearings producing pivots as in the embodiment shown in Figures 7a to 7d, guides with flexible blades or other variable section segment ensuring the functionality of a pivot. The pivoting of the lifters 1.2.3, 1.2.4 are each ensured by two blades fixed to the rigid frame 1.1 and fixed to the respective lifter, so that the point of intersection of the two blades is, for small movements, comparable to the center of pivoting of the corresponding rudder. The arrangement presented proposes the longest possible blades in order to minimize the restoring forces and moments, but it is possible to shorten these parts according to the needs. Moreover, in this embodiment, the four flexible blades forming the reversing levers 1.5.1, 1.5.2 are all connected to the second crossbar 1.2.4. Two of these blades connect the ends of the lifter 1.2.4 to the masses 1.3.1, 1.3.2, while the other two blades are respectively connected to projections of the masses 1.3.1, 1.3.2 in the direction of the second lifter 1.2. 4 and a boss close to the center of pivoting of this lifter 1.2.4. These last two blades can be made in a single continuous piece fixed at its center to the second crossbar 1.2.4. It is also possible to lengthen these two blades by fixing each of these blades on the opposite side of the crossbar 1.2.4 and by choosing blade shapes allowing the blades to cross without interference.

Figures 7g and 7h illustrate an alternative embodiment of the second embodiment of the regulating device of a timepiece mechanism corresponding substantially to the embodiment according to Figures 7e and 7f, except that in the embodiment according to Figures 7g and 7h the four flexible blades forming the reversing levers 1.5.1, 1.5.2 are not all connected to the second spreader bar 1.2.4. In this embodiment, if two of these blades still connect the ends of the crossbar 1.2.4 to the masses 1.3.1, 1.3.2, the other two blades are in fact each connected to an outgrowth of the respective mass 1.3.1, 1.3. 2 in the direction of the second rudder 1.2.4 and to the rigid frame 1.1, so that in this embodiment the pivots P5, P6 are made using a connection to the rigid frame 1.1 instead of a connection to the second rudder 1.2.4. In the alternative embodiments according to FIGS. 7e and 7f as well as according to FIGS. 7g and 7h, the blades which connect the ends of the spreader bar 1.2.4 to the masses 1.3.1, 1.3.2 are arranged so that their extension passes through the centers of gravity of each of the masses 1.3.1, 1.3.2 in order to limit parasitic moments on the masses. Obviously, in the two alternative embodiments, it is also possible to produce the entire part comprising the supporting structure 1.2, the inversion means 1.5, and the masses 1.3.1, 1.3.2 by a monolithic part as described above in the context of Figures 6g and 6h. In all these cases, the operation of these alternative embodiments of the corresponding regulation device is analogous to that of the second embodiment of the regulation device illustrated in FIGS. 3a to 3d.

[0044] Figures 7i and 7j illustrate yet another alternative embodiment of the second embodiment of the device for regulating a timepiece mechanism using a guide with flexible blades, the direction of which corresponds to the direction of the main force and the like to the guide with flexible blades of the embodiments according to FIGS. 7e and 7f as well as according to FIGS. 7g and 7h. On the other hand, this embodiment comprises, at the level of each crossbar 1.2.3, 1.2.4, a central pivot P1, P2 realized by means of a pin 1.2.3.1, 1.2.4.1 combined with an oblong hole whose axis longitudinal is oriented in the direction of the corresponding flexible blade. Similarly, the suspension rods 1.2.1, 1.2.2 carrying the masses 1.3.1, 1.3.2, mounted in this embodiment on the second lifter 1.2.4, each comprise at the end articulated to the second lifter 1.2.4 a pin cooperating with an oblong hole corresponding to the ends of said second spreader bar 1.2.4. A guide by this oblong hole - pin system ensures that the mobility perpendicular to the direction of the corresponding blade is blocked, up to the clearance between the oblong hole and the pin, while allowing the aid of the oblong hole to avoid overguiding . The relative movement at the level of the pin and the oblong hole is very low, which drastically limits the energy dissipated. In the figures, for the pivoting of the spreaders 1.2.3, 1.2.4, the oblong hole is made on the moving part and the pin is mounted on the fixed frame, but the reverse is possible. The position of the oblong hole and of the pin can also be reversed at the joints located between the second crossbar 1.2.4 and the suspension rods 1.2.1, 1.2.2. Furthermore, due to the fixing of the suspension rods 1.2.1, 1.2.2 carrying the masses 1.3.1, 1.3.2 on the second crossbar 1.2.4, this embodiment of the device comprises reversing levers additional 1.5.3, 1.5.4, 1.5.5, 1.5.6 two of which, namely those formed by the flexible blades 1.5.5, 1.5.6 illustrated in Figures 7i and 7j, are each fixed at one end to the center of the corresponding beam 1.2.3, 1.2.4 and at the other end to the rigid frame 1.1. As for the alternative embodiments of the regulating device described previously, the ratio between the lengths of the arms of the first spreader bar 1.2.3 can be adapted according to the position of attachment of the flexible blades to the masses 1.3.1, 1.3.2 and their extensions. Again, the extension of the flexible blades 1.5.1, 1.5.2 passes through the center of gravity of the corresponding mass 1.3.1, 1.3.2 and the general operation of this alternative embodiment of the regulating device is analogous to the explanations given below. -above.

[0045] In general, although these alternatives at the level of the concrete embodiment, in particular in terms of the geometric arrangement of certain parts of the device, have been described above in the context of the second embodiment of a device regulator according to the present invention, it is obvious that similar modifications can be applied to the other embodiments of the regulator device described above or below.

[0046] Figures 8a to 8d show schematically and by way of example an embodiment of a device for regulating a timepiece mechanism constructed on the basis of the first embodiment of the device described above, but modified so that the device is balanced not only with respect to gravity and translational accelerations, but also with respect to rotational accelerations. Indeed, another measure making it possible to avoid disturbing moments due to angular accelerations, alongside an arrangement of the masses so that the centers of gravity of the masses coincide in the neutral position of the regulation device, consists in providing devices identical to those mentioned above, for example a device according to the first embodiment of the device illustrated in FIGS. 1a to 1c, to which is added an identical device, but connected to the first device with lifting beams and control levers inversion to reverse the effect of rotational accelerations on the masses. The embodiment of the regulating device according to FIGS. 8a to 8d is an example of this type of device and corresponds to the combination of two devices according to the first embodiment of the device according to FIGS. 1a to 1c. The first sub-entity of the device according to FIGS. 8a to 8d therefore comprises a first crossbar 1.2.3 pivoting around a first pivot axis 1.2.3.1, first and second suspension rods 1.2.1, 1.2.2, first and second inversion levers 1.5.1, 1.5.2, and first and second masses 1.3.1, 1.3.2, these parts being assembled as described in the context of the first embodiment of the device illustrated in figures 1a to 1c. The second sub-entity of the device according to FIGS. 8a to 8d similarly comprises a second crossbar 1.2.4 pivoting around a second pivot axis 1.2.4.1, third and fourth suspension rods 1.2.5, 1.2.6 , third and fourth reversing levers 1.5.3, 1.5.4, and third and fourth masses 1.3.3, 1.3.4, these parts being assembled in the same way. In addition, this device further comprises a fifth reversing lever 1.5.5 as well as a third crossbar 1.2.7 pivoting about the third pivot axis 1.2.7.1 and sixth and seventh reversing levers 1.5.6, 1.5. 7. The two sub-entities are linked kinematically, on the one hand, using the fifth inversion lever 1.5.5 which is linked to respective extensions of the first and second pedals 1.2.3, 1.2.4 and which transmits the movement of the first lifter 1.2.3 pivoting around the first pivot axis 1.2.3.1 to the second lifter 1.2.4 pivoting around the second pivot axis 1.2.4.1. The geometric arrangement, as also apparent from Figure 8b, ensures that the angular movements of the first spreader 1.2.3 and the second spreader 1.2.4 are reversed. On the other hand, the sixth and seventh reversing levers 1.5.6, 1.5.7 are each hinged at one of their ends to one end of said third crossbar 1.2.7 and at the other of their ends to a respective extension of the second suspension link 1.2.2 of the first sub-entity, respectively to a respective extension of the fourth suspension link 1.2.6 of the second sub-entity. Thus, via the third crossbar 1.2.7 pivoting about the third pivot axis 1.2.7.1, said sixth and seventh reversing levers 1.5.6, 1.5.7 transmit the movement of the second suspension rod 1.2.2 from the first sub-entity to the fourth suspension link 1.2.6 of the second sub-entity, the third crossbar 1.2.7 and the said extensions on the second and fourth suspension link 1.2.2, 1.2.6 making it possible to ensure a reversal of motion between the first sub-entity and the second sub-entity. To produce the same effect, it is also possible to articulate the seventh inversion lever 1.5.7 on an extension of the third inversion lever 1.5.3 instead of articulating it on an extension of the fourth suspension rod 1.2 .6 of the second sub-entity. This same regulating device can of course be produced using a guide with flexible blades, a guide with knives, or a monolithic part as described above. As also apparent from FIG. 8b, this device has seventeen pivots and is balanced with respect to gravity as well as with respect to accelerations in translation and accelerations in rotation.

Analogously to the embodiment of the control device illustrated in Figures 8a to 8d, Figures 9a to 9c show schematically and by way of example an alternative embodiment of the third embodiment of a device regulation of a timepiece mechanism described above in the context of FIGS. 4a to 4d, the embodiment of the device according to FIGS. 9a to 9c being produced by using two partially superposed devices according to the first embodiment of the device regulator according to FIGS. 1a to 1c. The device is therefore constructed in the same way on the basis of a first sub-entity and a second sub-entity which each comprise the same components as listed above, namely a first spreader bar 1.2.3 pivoting around a first pivot axis 1.2.3.1, first and second suspension rods 1.2.1, 1.2.2, first and second reversing levers 1.5.1, 1.5.2, and first and second masses 1.3.1, 1.3.2 for the first sub-entity as well as a second crossbar 1.2.4 pivoting about a second pivot axis 1.2.4.1, third and fourth suspension rods 1.2.5, 1.2.6, third and fourth inversion levers 1.5.3, 1.5.4, and third and fourth masses 1.3.3, 1.3.4 for the second sub-entity, these sub-entities each being assembled in the same manner as described above. These two sub-entities are in the embodiment of the device according to FIGS. 9a to 9c positioned relative to each other so that the centers of gravity M1, M3 of the mass 1.3.1 of the first sub-entity and mass 1.3.3 of the second sub-entity are confused. Moreover, these two sub-entities are simply linked kinematically to each other by passing the pin 1.3.1.1 mounted for example at the center of gravity M1 of the mass 1.3.1 through a bore, preferably equipped with a ruby to minimize friction, provided at the center of gravity M3 of mass 1.3.3. Obviously, the reverse constellation is possible. In this context it can also be noted that the pin 1.3.1.1, respectively the roller 1.3.1.2 mentioned above, can in all embodiments be fixed on the return spring 1.4.4 of the rotary plate 1.4.2 of the variable radius drive means 1.4 instead of being fixed to a mass which in this case includes a means of interaction with the pin, for example a corresponding housing. This device has, as is further apparent from Figure 9b, eleven pivots, including the pivot P11 made by the pin 1.3.1.1 as well as located at the centers of gravity M1, M3 of the masses 1.3.1, 1.3.3, and is balanced with respect to gravity as well as with respect to accelerations in translation and accelerations in rotation. The general operation of this alternative embodiment of a regulating device is again analogous to the explanations given above.

Figures 10a to 10f show schematically and by way of example an alternative embodiment of the fourth embodiment of a device for regulating a timepiece mechanism described above in the context of Figures 5a to 5f, the embodiment of the device according to FIGS. 10a to 10f being produced using weights in the form of dumbbells. For this purpose and as visible in Figures 10a and 10d, each of the first and second suspension rods 1.2.1, 1.2.2 carrying the first mass 1.3.1 as well as third and fourth suspension rods 1.2.7, 1.2. 8 carrying the second mass 1.3.2 are in this alternative embodiment, in comparison with the fourth embodiment illustrated in Figures 5a to 5f, extended symmetrically with respect to the joints connecting them to the first and second spreaders 1.2.3, 1.2.4, respectively to the third and fourth rudder bars 1.2.5, 1.2.6. In addition, each arm of the first and second suspension rods 1.2.1, 1.2.2 as well as of the third and fourth suspension rods 1.2.7, 1.2.8 carries at its opposite ends an identical mass 1.3.1a, 1.3.1b , 1.3.1c, 1.3.1d, 1.3.2a, 1.3.2b, 1.3.2c, 1.3.2d. The identical masses 1.3.1a, 1.3.1b, 1.3.1c, 1.3.1d together form the first mass 1.3.1 and the identical masses 1.3.2a, 1.3.2b, 1.3.2c, 1.3.2d together form the second mass 1.3.2, the first and second suspension rods 1.2.1, 1.2.2, respectively the third and fourth suspension rods 1.2.7, 1.2.8 being articulated to one another at the level of the center of gravity of the identical superimposed masses 1.3.1a and 1.3.1c, respectively identical superimposed masses 1.3.2a and 1.3.2c. This specific configuration of the masses makes it possible to balance the device even better. Furthermore, the structure as well as the operation of this device for regulating a timepiece mechanism are analogous to the explanations appearing above in the context of the fourth embodiment illustrated in FIGS. 5a to 5f.

The present invention also relates to a timepiece movement, intended to be integrated into a timepiece, in particular into a mechanical wristwatch, comprising a power source, a gear train, and a regulating member. In particular, the regulating member of a watch movement according to the present invention consists of a regulating device as described above, so that it is not necessary for this movement to include an escapement. Indeed, the frequency of rotation of the drive means 1.4 being managed directly by the oscillation of said at least two masses 1.3.1, 1.3.2 forming the isotropic harmonic oscillator of the regulation device, the cog of the watch movement can be in direct kinematic connection with the drive means 1.4, without the need for an additional component such as the escapement of traditional mechanical watch movements.

Finally, the present invention also relates to a timepiece, in particular a mechanical wristwatch, which comprises at least one device for regulating a timepiece mechanism or a timepiece movement as described above. In particular, it may be not only a timepiece equipped with a source of mechanical energy, that is to say a barrel spring housed in a corresponding barrel, but also a another type of timepiece, for example a wristwatch equipped with a source of electrical energy. In the latter case, the timepiece may nevertheless comprise a device for regulating a timepiece mechanism according to the present invention, the gear train of said timepiece being directly linked to the regulation device.

Given the arrangement and operation of the different embodiments of a device for regulating a watch mechanism described above, it is understood that it makes it possible to achieve the main objective of the present invention, namely to produce a device for regulating a watch mechanism on the basis of an isotropic harmonic oscillator making it possible to construct watch movements without an escapement. Furthermore, such a regulating device has many other advantages, including, in the majority of the embodiments, a simple and robust structure so as to guarantee a reasonable production cost as well as reliable and precise operation, in addition in terms of the rate accuracy of a corresponding timepiece. In addition, the large number of different embodiments described above shows that it has a very great flexibility, both in terms of its structure and its concrete realization, to allow integration into a wide variety of parts. of watchmaking. In general, the device can be integrated into all kinds of timepieces, preferably into wristwatches having a mechanical energy source, but it is also possible to use it in watches having an electrical energy source . More particularly, in terms of the drive means, the regulation device proposed makes it possible to achieve, by means of an adequately calibrated return spring, a substantially radial guiding almost without friction as well as a proportional return force to the radial displacement of the masses. In particular, there is no difference in stiffness of the return spring according to its angular position. In addition, the system only has play at the level of the roller, respectively of the pin fixed to one of the masses, this play being able to be reduced by conventional means of production known to those skilled in the art, and it is Equipped with shockproof function in all directions of the swing plane. In addition, the system does not require any lubrication, and therefore no maintenance, and can be integrated into existing watch movements without further ado. Similarly, the minimum eccentricity present in the drive means ensures self-starting following any stoppage of the device. In addition, in terms of the supporting structure and the inversion means, the regulation device proposed makes it possible to achieve a large number of variants, whether at the geometric and constructive level or at the level of the concrete realization, for example at the using traditional horological means such as bearings used as pivots or using other means such as flexible blades or monolithic structures. In all cases, a correlated and symmetrical movement of the masses of at least one pair of masses is ensured by the inversion means located on and in cooperation with the bearing structure which carries the masses. This reduces the displacement of the center of mass of the entire regulating device. The correlated and symmetrical movement of the masses of at least one pair of masses ensured by the inversion means located on and in cooperation with the supporting structure has in all the embodiments, due to the pivots provided in the devices according to the present invention, a rotating component, which allows a great simplification of the design and construction of these systems. Depending on the choice in terms of construction and implementation among the options described above, it is possible to reduce the influence of gravity depending on the position in space of the watch on the behavior of the regulation device proposed as well as to avoid, respectively to reduce to a large extent, disturbances during shocks in translation and, in certain proposed constellations, during shocks in rotation, so that the device is, in short, balanced with respect to gravity as well as linear accelerations and, in some cases, rotary accelerations.

Claims (20)

1. Regulating device (1) for a watch mechanism based on an isotropic harmonic oscillator, intended to be integrated into a timepiece, in particular into a wristwatch, said regulating device comprising a rigid frame (1.1 ), at least two masses (1.3.1, 1.3.2) mounted so that they are movable relative to the rigid frame (1.1), a variable radius drive means (1.4) coupled by a coupling means elastic to at least one of said masses (1.3.1, 1.3.2), said drive means (1.4) being adapted to be driven by a source of energy from said timepiece as well as to transmit energy received from said energy source to said masses (1.3.1, 1.3.2) so as to set them in motion, and reversing means (1.5) coupled to said masses (1.3.1, 1.3.2) and arranged so as to reduce the displacement of the center of mass of the regulating device,characterised in thatthe regulating device comprises a s supporting structure (1.2) mounted on said rigid frame (1.1) in a pivoting manner via at least one pivot (P1, P2, P3, P4) and able to form a guide for the movement of the masses (1.3.1, 1.3.2), said masses (1.3.1, 1.3.2) being mounted on said supporting structure (1.2), and in that the reversing means (1.5) are located on or form part of said supporting structure (1.2 ) and are arranged so as to cause a correlated and symmetrical movement of said masses (1.3.1, 1.3.2). 2. Control device according to the preceding claim, characterized in that the drive means (1.4) is coupled directly and decentralized to one of said masses (1.3) by means of a return spring (1.4.4) serving simultaneously as a means of transmission of the driving force and as an elastic return means of the masses (1.3.1, 1.3.2). 3. Control device according to one of the preceding claims, characterized in that the supporting structure (1.2) comprises at least one lifter (1.2.3) mounted on said rigid frame (1.1) in a pivoting manner via said au least one pivot (P1, P2, P3, P4). 4. Control device according to one of the preceding claims, characterized in that the control device comprises an even number of masses (1.3.1, 1.3.2) mounted on said supporting structure (1.2). 5. Control device according to one of claims 3 to 4, characterized by the fact that the supporting structure (1.2) is connected to the rigid frame (1.1) via a central pivot (P1) formed by a pivot axis (1.2.3.1) located in the center of said lifter (1.2.3) of the supporting structure (1.2). 6. Regulating device according to the preceding claim, characterized in that the reversing means (1.5) and part of the supporting structure (1.2) form a parallelogram which is deformable during the movement of the masses (1.3.1, 1.3.2 ) in the pivot plane by means of four joints located at the corners of said parallelogram, so that the device comprises five pivots (P1, P2, P3, P4, P5) constituted by the pivot axis (1.2.3.1) of the lifter (1.2.3) of the bearing structure (1.2) and by said joints of said parallelogram. 7. Regulating device according to claim 5 or 6, characterized in that the centers of mass of each mass (1.3.1, 1.3.2) of a pair of masses (1.3) are aligned with the pivot axis of the rudder (1.2.3) matching. 8. Control device according to one of claims 1 to 4, characterized by the fact that the supporting structure (1.2) is connected to the rigid frame (1.1) by means of two pivots (P1, P2) formed by pivot axes (1.2.3.1, 1.2.4.1) of a first spreader (1.2.3) and a second spreader (1.2.4) of the supporting structure (1.2), the second spreader (1.2.4) being oriented substantially perpendicular to the first rudder bar (1.2.3). 9. Control device according to the preceding claim, characterized in that the supporting structure (1.2) comprises, on either side of the first spreader bar (1.2.3) which is located in the middle, two suspension rods (1.2.1, 1.2.2) each carrying one of the masses (1.3.1, 1.3.2) of a pair of masses (1.3), oriented substantially perpendicularly to the longitudinal axis of the first crossbar (1.2.3), and articulated both at the corresponding end of the masses (1.3.1, 1.3.2) than at the corresponding end of the first crossbar (1.2.3), and speaks of the fact that the reversing means (1.5) comprise a first reversing lever ( 1.5.1) articulated at one end of the second rudder bar (1.2.4) and fixed on the other side to the first mass (1.3.1) and a second reversing lever (1.5.2) articulated at the other end of the second crossbar (1.2.4) and fixed on the other side to the second mass (1.3.2) of the pair of masses (1.3), so that the device comprises eight pivots (P1, P2, P3, P4, P5, P6, P7, P8) consisting of the pivot axes (1.2.3.1, 1.2.4.1) of the spreaders (1.2.3, 1.2.4) of the supporting structure (1.2) as well as by said joints of the connecting rods suspension (1.2.1, 1.2.2) of the supporting structure (1.2) and reversing levers (1.5.1, 1.5.2) of the reversing means (1.5). 10. Control device according to one of claims 1 to 4, characterized by the fact that the bearing structure (1.2) is connected to the rigid frame (1.1) by means of three pivots (P1, P2, P3) formed by axes of pivoting (1.2.3.1, 1.2.4.1, 1.2.5.1) of a first rudder bar (1.2.3), of a second rudder bar (1.2.4), and of a third rudder bar (1.2.5) of the bearing structure (1.2), the device comprising eleven pivots (P1, P2, P3, P4, P5, P6, P7, P8, P9, P10, P11) constituted by the pivot axes (1.2.3.1, 1.2.4.1, 1.2 .5.1) of the spreaders (1.2.3, 1.2.4, 1.2.5) of the supporting structure (1.2) as well as by the joints of the suspension rods (1.2.1, 1.2.2) of the supporting structure (1.2) and reversing levers (1.5.1, 1.5.2) of the reversing means (1.5). 11. Control device according to one of claims 1 to 4, characterized by the fact that the bearing structure (1.2) is connected to the rigid frame (1.1) by means of four pivots (P1, P2, P3, P4) formed by pivot axes (1.2.3.1, 1.2.4.1, 1.2.5.1, 1.2.6.1) of four spreaders (1.2.3, 1.2.4, 1.2.5, 1.2.6) of the supporting structure (1.2), the device comprising fourteen pivots (P1, P2, P3, P4, P5, P6, P7, P8, P9, P10, P11, P12, P13, P14) constituted by the pivot axes (1.2.3.1, 1.2.4.1, 1.2. 5.1, 1.2.6.1) of the spreaders (1.2.3, 1.2.4, 1.2.5, 1.2.6) of the supporting structure (1.2) as well as by the joints of the suspension rods (1.2.1, 1.2.2) of the bearing structure (1.2) and of the inversion levers (1.5.1, 1.5.2) of the inversion means (1.5). 12. Regulating device according to one of claims 10 or 11, characterized by the fact that the masses (1.3.1, 1.3.2) are mounted one on the other in parallel planes on said supporting structure (1.1) of so that, in the neutral position of the regulation device, the centers of mass (M1, M2) of the corresponding masses (1.3.1, 1.3.2) either of each pair of masses (1.3) between them, or of all the pairs of masses (1.3) together, either of a mass of at least two pairs of masses (1.3) different, are superimposed. 13. Control device according to the preceding claim 11, characterized by the fact that the masses (1.3.1, 1.3.2) are in the form of dumbbells, each comprising at least two identical masses (1.3.1a, 1.3.1b, 1.3. 1c, 1.3.1d, 1.3.2a, 1.3.2b, 1.3.2c, 1.3.2d) arranged symmetrically with respect to a joint. 14. Regulating device according to one of the preceding claims, characterized in that the device comprises horological pivots, preferably anti-shock bearings and ruby bearings, in order to produce the pivots of the support structure (1.2) and means inversion (1.5). 15. Control device according to one of the preceding claims, characterized in that the device comprises knife guides in order to produce the pivots of the support structure (1.2) and reversing means (1.5). 16. Control device according to one of the preceding claims, characterized in that the device comprises flexible blades in order to produce the pivots of the supporting structure (1.2) and reversing means (1.5). 17. Control device according to one of the preceding claims, characterized in that the device is produced at least partially in the form of a monolithic structure making it possible to produce the pivots of the supporting structure (1.2) and reversing means ( 1.5). 18. Regulating device according to one of the preceding claims, characterized in that the variable radius drive means (1.4) comprises a rotary plate (1.4.2) being adapted to be driven in rotation by the energy source of the corresponding timepiece and carrying a support lever (1.4.3, 1.4.7), a return spring (1.4.4) forming said elastic coupling means, and an eccentric (1.4.5), the return spring (1.4.4) and/or the support lever (1.4.3) providing substantially radial guidance of the center of mass (M1, M2) of the driven mass (1.3.1, 1.3.2) relative to said rotary plate (1.4.2) and the eccentric ensuring, directly or indirectly using the support lever (1.4.7), a minimum eccentricity of said center of mass (M1, M2) of the driven mass (1.3 .1, 1.3.2) relative to the center of the turntable (1.4.2). 19. Watch movement comprising a power source, a cog, and a regulating member, in particular for a mechanical wristwatch, characterized in that the regulating member is constituted by a regulating device according to one of the preceding claims, so as to that the movement does not have an escapement. 20. Timepiece, in particular mechanical wristwatch, characterized in that it comprises a regulating device according to one of the preceding claims 1 to 18 or a watch movement according to the preceding claim.