EP3252545B1 - Timepiece mechanism with balance wheel inertia adjustment - Google Patents

Description

Field of the invention

The invention relates to a timepiece with inertia adjustment, comprising a shaft bearing on the one hand a serge via at least one arm, and on the other hand an inner flange fixed on said shaft and bearing directly or indirectly an outer ring with, between said inner flange and said outer ring, a plurality of first guide elastic links balanced in inertia with respect to the axis of said shaft and in a plane perpendicular to said axis, said outer ring being distinct from said serge and arranged to pivot relative to said inner flange under the action of an external torque exerted against a resisting torque exerted by said first elastic guide links, said balance having a plurality of weights each carried by said outer ring by means of at least one outer flexible blade.

The invention also relates to a mechanical clockwork movement comprising at least one clock oscillator mechanism comprising such a balance.

The invention also relates to a watch comprising such a movement, and a control member consisting of a pusher or a ring arranged to control through a sliding pinion the movement of a timer.

The invention also relates to a watch assembly comprising such a watch, and a setting tool arranged to allow the inertia adjustment of said balance.

The invention relates to the field of mechanical clockwork movements with pendulum oscillator, and the gait adjustment of such an oscillator.

Background of the invention

To adjust the running of a mechanical watch, it is generally necessary to open the box and extract the movement, to then access the components allowing the adjustment of the step: rotation of the racket to change the rigidity of the spiral, rotation of the screws of the pendulum to change the inertia, or other. This operation therefore requires additional operations that are time consuming. In addition, the leak test must be redone. Sometimes, too, there is also a shift of the step during the casing operation.

In the existing mechanisms, the movement must be disassembled to access the adjustment members, the structure does not cooperate with an internal setting. In addition, the risk of introducing unbalance during adjustment is not minimized.

The document CH 709 052 A2 In the name of Seiko Instruments there is a pendulum composed of two parts, one being rigid and provided with two cams at 180 °, and the other composed of two elastic arms pressing on these cams, ended by weights. The relative rotation between these two members causes a change of inertia by radial stroke of the weights. A variant is provided with a set of teeth allowing the insertion of a special tool terminated by two pins, the rotation of this tool causes a precise tangential displacement of the weights. Although taking advantage of the lack of play, this adjustment requires disassembly of the movement to access the tool with the pendulum. This adjustment mode does not prevent the occurrence of unintentional unbalance during adjustment: the angular displacement imposed by the tool at one end may produce a smaller amplitude shift at the other end diametrically opposite, due to friction.

The document CH 708 675 A1 in the name of Sercalo Microtechnology Ltd has a monolithic structure in "LIGA" -metal (Lithografie, Galvanoformung und Abformung) or "DRIE" -Si (Deep Reactive Ion Etchning), with several elastic blades between an inner fixing rhomb and a ring slightly outer elliptical, which can be fixed by elastic forces inside a serge. The march is performed by rotating the outer elastic ellipse with tweezers, which moves the blades away from the center, and changes the inertia. However, there is no built-in adjustment tool. Even using silicon technology to achieve a very high manufacturing accuracy of this part, the positioning of the elliptical ring being performed at two points, unbalance may appear.

The document CH 320 818 A in the name of H. Siegwart, also describes elastic blades and an elastic support resting inside the serge.

Summary of the invention

The invention proposes to develop a solution to adjust the running of a mechanical movement, without having to open the watch case, and without introducing unbalance.

The proposed solution preferably uses the high precision of silicon micro-fabrication, or similar, to minimize any imbalances introduced during the adjustment, and especially to propose a solution to adjust without having to disassemble the watch, with means integrated adjustment to the movement.

For this purpose, the invention relates to a timepiece with inertia adjustment according to claim 1.

The invention also relates to a mechanical clockwork movement comprising at least one clock oscillator mechanism comprising such a balance.

The invention also relates to a watch comprising such a movement, and a control member, in particular pre-existing, consisting of a pusher or a ring arranged to control through a sliding pinion the movement of a timer.

The invention also relates to a watch assembly comprising such a watch, and a setting tool arranged to allow the inertia adjustment of said balance.

Brief description of the drawings

• la figure 1 représente, de façon schématisée, et en coupe, un balancier d'horlogerie à réglage d'inertie selon l'invention, qui comporte, dans un premier plan supérieur un anneau extérieur, porteur d'une denture périphérique, monté de façon élastique par rapport à un flasque intérieur solidaire de l'arbre de ce balancier, et agencé pour commander le mouvement de masselottes du balancier, et, dans un deuxième plan inférieur et parallèle au premier, une surface d'appui et de maintien, consistant en une surface extérieure de la serge du balancier, ou en une denture d'une planche inférieure. Ce balancier est représenté face à un organe de manoeuvre selon l'invention, qui comporte, au niveau du plan supérieur une denture de commande agencée pour coopérer avec la denture périphérique, et au niveau du plan inférieur une surface complémentaire d'appui et de maintien;
• la figure 2 est un schéma de principe d'une planche supérieure comportant, entre le flasque intérieur et l'anneau extérieur, d'une part trois premières liaisons élastiques à 120° les unes des autres et remplissant la fonction de guidage en rotation, et, intercalées entre les précédentes, et également disposées à 120° les unes des autres, trois masselottes chacune suspendue de part et d'autre par une deuxième liaison élastique non représentée;

• la figure 3 est similaire à la figure 2, mais avec deux premières liaisons élastiques à un angle de 180° au lieu de 120°, et deux masselottes seulement ;
• la figure 4 représente, de façon schématisée, partielle et en vue de dessus, une partie du mécanisme de réglage d'inertie, dans une première variante où la masselotte comporte un secteur denté qui est suspendu par une liaison à trois cols qui définissent ensemble un triangle isocèle symétrique par rapport à une perpendiculaire à une radiale issue de l'axe du balancier, entre deux tronçons de bras radiaux, l'un issu du flaque intérieur du balancier, et l'autre issu de l'anneau extérieur, le flasque intérieur portant encore un sautoir saillant radialement et coopérant en arrêt de maintien avec des dents du secteur denté, lequel comporte une graduation de repérage de la position angulaire de la masselotte ;
• la figure 5 est une illustration simplifiée des liaisons du mécanisme de la figure 4 ;
• la figure 6 représente, de façon schématisée, partielle et en vue de dessus, une partie du mécanisme de réglage d'inertie, dans une deuxième variante, dite à cames, où la masselotte est un disque comportant deux dents opposées, attaché par une lame flexible perpendiculaire à un bras radial issu du flasque intérieur du balancier, et où l'anneau extérieur porte, sur des pistes non concentriques avec l'axe du balancier, deux secteurs dentés avec lesquels coopèrent les deux dents de la masselotte ;
• la figure 7 représente, de façon schématisée, partielle et en vue de dessus, une partie d'un mécanisme de guidage à lames flexibles, dans une variante où le flasque intérieur porte des bras radiaux qui portent, par l'intermédiaire de lames élastiques radiales à deux cols chacune, un secteur concentrique intermédiaire qui est suspendu par l'intermédiaire de deux autres lames élastiques radiales à deux cols chacune, à l'anneau extérieur ;
• la figure 8 est une illustration simplifiée des liaisons du mécanisme de la figure 7 ;
• la figure 9 représente, de façon schématisée, partielle et en vue de dessus, un mécanisme où le réglage d'inertie et le guidage sont alternés par secteurs de 60°, sensiblement selon les variantes respectivement des figures 6 et 7 ;
• la figure 10 représente, de façon schématisée, partielle et en vue de dessus, un détail avec des ressorts, montés radialement, pour la réduction du couple élastique de rappel, et la figure 11 illustre la variation du couple élastique en fonction de l'angle de déformation, en trait plein sans ces ressorts, et en trait interrompu avec ces ressorts ;
• la figure 12 représente, de façon schématisée et en vue de dessus, une troisième variante avec structure flexible planétaire, où le flasque intérieur porte directement des secteurs dentés qui, au besoin, peuvent être non concentriques avec l'axe du balancier, indexé en position par un sautoir solidaire de l'anneau extérieur, et où des masselottes-planètes sont chacune reliées à la fois au flasque intérieur et à l'anneau extérieur, par des lames élastiques sensiblement concentriques ;
• la figure 13 est un schéma montrant que les couples provoqués par les balourds des masselotte-planètes de la figure 12 lors d'un choc linéaire s'annulent et ne provoquent pas de rotation involontaire de l'anneau extérieur ;
• la figure 14 représente, de façon schématisée, partielle et en vue de dessus, un détail d'un mouvement d'horlogerie comportant un tel balancier, au niveau de l'interface, dans le plan supérieur, entre l'anneau extérieur et l'organe de manoeuvre qui en commande la rotation, comportant un levier muni de roues, le corps de levier étant visible dans un plan inférieur distinct du plan supérieur dans lequel se fait un engrènement entre une roue menante que comporte l'organe de manoeuvre et une denture extérieure que comporte l'anneau extérieur;
• la figure 15 est un détail grossi de cet engrènement ;
• la figure 16 représente, de façon schématisée, partielle et en vue de dessus, un détail d'une montre comportant un tel mouvement d'horlogerie, en particulier : un mécanisme de commande comportant une bague d'embrayage commandant le levier de la figure 14, au niveau de l'interfaçage, dans le plan inférieur, une denture d'une planche inférieure du balancier et un peigne que comporte ce levier, et, au niveau de l'interfaçage supérieur, l'anneau extérieur et l'organe de manoeuvre, ici une roue, qui en commande la rotation ;
• la figure 17 est un détail de variante de réalisation de planche supérieure ou inférieur du balancier avec une pluralité de lames élastiques pinçant l'arbre de balancier ;
• la figure 18 représente, de façon schématisée, et en perspective, une réalisation particulière de balancier, selon une deuxième famille de variantes, qui est une structure de réglage d'inertie à spirale centrale, dans laquelle le pivotage est réalisé par frottement sur trois appuis de centrage ;
• la figure 19 représente, de façon schématisée, et en coupe, un balancier-spiral comportant une planche supérieure monobloc, et dans lequel le blocage de la serge se fait dans ce cas par friction sur le diamètre extérieur de celle-ci ;
• la figure 20 représente, de façon schématisée, et en vue de dessus, une montre comportant un mouvement d'horlogerie, avec un balancier-spiral comportant un balancier selon l'invention, avec son mécanisme de commande de réglage d'inertie commandé par la couronne, et, en perspective, un outillage externe, associé à ce type de montre, agencé pour commander sans contact, au travers de la boîte de la montre, la bague d'embrayage de la figure 16.

Other features and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings illustrating two families of variants of the invention, where:

• the figure 1 schematically shows, in section, an inertia-controlled timepiece according to the invention, which comprises, in a first upper plane, an outer ring bearing a peripheral toothing, mounted elastically relative to to an inner flange integral with the shaft of this balance, and arranged to control the movement of flyweights balance, and, in a second lower plane and parallel to the first, a bearing surface and maintenance, consisting of an outer surface of the serge of the balance, or in a toothing of a lower plate. This balance is shown facing an operating member according to the invention, which comprises, at the upper plane a control gear arranged to cooperate with the peripheral toothing, and at the lower plane a complementary surface support and maintenance ;
• the figure 2 is a schematic diagram of an upper board comprising, between the inner flange and the outer ring, first three first links resilient at 120 ° to each other and performing the function of guiding in rotation, and, interposed between the preceding, and also arranged at 120 ° from each other, three weights each suspended on either side by a second elastic connection not shown;

• the figure 3 is similar to the figure 2 but with two first elastic links at an angle of 180 ° instead of 120 °, and only two flyweights;
• the figure 4 represents, in a diagrammatic, partial and top view, part of the inertia adjustment mechanism, in a first variant where the weight comprises a toothed sector which is suspended by a three-neck connection which together define a symmetrical isosceles triangle relative to a perpendicular to a radial stem from the axis of the balance, between two radial arm sections, one from the inner puddle of the balance, and the other from the outer ring, the inner flange still carrying a jumper radially projecting and cooperating in holding stop with teeth of the toothed sector, which comprises a graduation marking of the angular position of the weight;
• the figure 5 is a simplified illustration of the links of the mechanism of the figure 4 ;
• the figure 6 represents, schematically, partially and in plan view, a portion of the inertia adjustment mechanism, in a second variant, called cams, where the weight is a disc having two opposite teeth, attached by a flexible blade perpendicular to a radial arm from the inner flange of the balance, and wherein the outer ring carries, on non-concentric tracks with the axis of the balance, two toothed sectors with which cooperate the two teeth of the weight;
• the figure 7 represents, in a schematic, partial and top view, a portion of a flexible blade guide mechanism, in a variant where the inner flange carries radial arms which carry, via radial two-necked elastic blades each, an intermediate concentric sector which is suspended by means of two other radial elastic blades with two necks each, to the outer ring;
• the figure 8 is a simplified illustration of the links of the mechanism of the figure 7 ;
• the figure 9 represents, schematically, partially and in plan view, a mechanism where the inertia adjustment and the guidance are alternated by sectors of 60 °, substantially according to the variants respectively of the Figures 6 and 7 ;
• the figure 10 schematically, partially and in plan view, a detail with radially mounted springs for the reduction of the elastic return torque, and the figure 11 illustrates the variation of the elastic torque as a function of the angle of deformation, in solid lines without these springs, and in broken lines with these springs;
• the figure 12 represents, schematically and in plan view, a third variant with planetary flexible structure, wherein the inner flange directly carries toothed sectors which, if necessary, may be non-concentric with the axis of the balance, indexed in position by a jumper integral with the outer ring, and where flyweights planets are each connected to both the inner flange and the outer ring, by substantially concentric resilient blades;
• the figure 13 is a diagram showing that the couples caused by the imbalances of the flyweight-planets of the figure 12 during a linear shock cancel out and do not cause involuntary rotation of the outer ring;
• the figure 14 represents, schematically, partially and in plan view, a detail of a clockwork movement comprising such a balance, at the interface, in the upper plane, between the outer ring and the operating member which controls rotation thereof, comprising a lever provided with wheels, the lever body being visible in a lower plane distinct from the upper plane in which is meshing between a driving wheel that comprises the actuating member and an external toothing that includes the outer ring;
• the figure 15 is a gross detail of this meshing;
• the figure 16 represents, schematically, partially and in plan view, a detail of a watch comprising such a clockwork movement, in particular: a control mechanism comprising a clutch ring controlling the lever of the watch; figure 14 at the level of the interfacing, in the lower plane, a toothing of a lower plate of the balance and a comb that comprises this lever, and, at the level of the upper interface, the outer ring and the operating member here a wheel, which controls its rotation;
• the figure 17 is a detail of an embodiment variant of upper or lower plate of the balance with a plurality of elastic blades pinching the balance shaft;
• the figure 18 schematically represents, in perspective, a particular embodiment of a balance, according to a second family of variants, which is a central spiral inertia adjusting structure, wherein the pivoting is achieved by friction on three centering supports;
• the figure 19 represents, schematically, and in section, a sprung balance having a monoblock top board, and wherein the locking of the serge is in this case by friction on the outer diameter thereof;
• the figure 20 represents, schematically, and in top view, a watch comprising a clockwork movement, with a balance spring comprising a rocker according to the invention, with its inertia control mechanism controlled by the crown, and , in perspective, an external tool, associated with this type of watch, arranged to control without contact, through the watch case, the clutch ring of the figure 16 .

Detailed Description of the Preferred Embodiments

The invention proposes a solution for adjusting the running of a mechanical movement, without opening the watch case, with an inertia adjusting device concerning both a specially equipped oscillator, and accessible control means. to a user from outside the watch case, for example by the winding and setting rod, a push, or other.

As can be seen in particular on the figure 20 the invention is described for a watch 1000, comprising a mechanical movement 300, itself comprising at least one oscillator 100 comprising at least one balance 10, in particular a balance-balance oscillator, comprising a balance 10 and at least one spiral 18.

More particularly, the inertia adjustment device according to the invention comprises a flexible structure of balance inertia adjustment.

As visible in the figures, especially on the Figures 1 to 3 the invention relates to a balance wheel 10 with inertia adjustment, comprising a shaft 11 which carries at least one serge 12 through at least one arm 13. This balance 10 comprises at least one inner flange 1 fixed on the shaft 11, and at least one outer ring 2, which is distinct from the serge 12.

• sur les variantes des figures 4 à 9 et 12 à 16, l'anneau extérieur 2 est relié directement à un flasque intérieur 1, avec lequel il forme de préférence un ensemble monobloc, par une pluralité de premières liaisons élastiques de guidage 3 ;
• sur la variante préférée de la figure 18, le flasque intérieur 1 porte directement ou indirectement l'anneau extérieur 2 avec, entre le flasque intérieur 1 et l'anneau extérieur 2, une pluralité de premières liaisons élastiques de guidage 3. Dans la variante illustrée, le flasque intérieur 1 et l'anneau extérieur 2 sont agencés pour pivoter l'un par rapport à l'autre, sont coplanaires et distincts. Selon l'amplitude de liberté en rotation, une exécution monobloc est possible, et requiert alors un niveau supplémentaire.

According to the variants of the invention, this outer ring 2 can be fixed in different ways:

• on variants of Figures 4 to 9 and 12 to 16 , the outer ring 2 is connected directly to an inner flange 1, with which it preferably forms a one-piece assembly, by a plurality of first elastic guide links 3;
• on the preferred variant of the figure 18 , the inner flange 1 directly or indirectly carries the outer ring 2 with, between the inner flange 1 and the outer ring 2, a plurality of first elastic guide links 3. In the variant shown, the inner flange 1 and the outer ring 2 are arranged to pivot relative to each other, are coplanar and distinct. Depending on the amplitude of freedom in rotation, a one-piece execution is possible, and then requires an additional level.

In either case, these first elastic guide links 3 are balanced in a plane perpendicular to the axis B of the shaft 11, so that the shaft 11 is positioned exactly in the center of inertia the structure to avoid unbalance, especially in the case where the inner flange 1 and the outer ring 2 are part of the same monobloc structure. This outer ring 2 is arranged to pivot relative to the inner flange 1, under the action of an external torque exerted against a resistant torque exerted by these first elastic guide links 3.

• sur la première famille de variantes des figures 4 à 9 et 12 à 16, ces masselottes sont fixées chacune par au moins une deuxième liaison élastique 5 à un flasque intérieur 1, et qui, selon les variantes, peuvent encore être fixées par une troisième liaison élastique 50 à un anneau extérieur 2, tel que visible notamment sur les figures 1, 4 et 12. Chaque masselotte 4 comporte des moyens d'indexage en position 6, lesquels sont agencés pour coopérer dans une position stable avec des moyens complémentaires d'indexage en position 7 que comporte un flasque intérieur 1 et/ou un anneau extérieur 2 ;
• sur la deuxième famille de variantes de la figure 18, chaque masselotte 4 est portée par l'anneau extérieur 2 par le moyen d'au moins une lame flexible extérieure 94, et est indexable dans une position angulaire stable définie par la coopération entre une première denture d'indexage 91 portée par le flasque intérieur 1 et une deuxième denture d'indexage 92 qui est portée par la masselotte 4.

According to the invention, the balance 10 comprises a plurality of weights 4. According to the variants:

• on the first family of variants of Figures 4 to 9 and 12 to 16 these flyweights are each fastened by at least one second elastic connection 5 to an inner flange 1, and which, according to the variants, can still be fixed by a third elastic connection 50 to an outer ring 2, as can be seen in particular on the figures 1 , 4 and 12 . Each weight 4 comprises indexing means in position 6, which are arranged to cooperate in a stable position with complementary indexing means in position 7 that includes an inner flange 1 and / or an outer ring 2;
• on the second family of variants of the figure 18 each weight 4 is carried by the outer ring 2 by means of at least one outer flexible blade 94, and is indexable in a stable angular position defined by the cooperation between a first indexing teeth 91 carried by the inner flange 1 and a second indexing teeth 92 which is carried by the weight 4.

The invention is described more particularly in the simple case where the balance has a single inner flange 1, a single outer ring 2, and is easy to extrapolate for a multi-stage construction.

According to the invention, any rotation of the outer ring 2 relative to the inner flange 1 changes the angular position of these weights 4.

More particularly, but not exclusively, the indexing means in position 6, and the complementary indexing means in position 7 comprise teeth. It is still conceivable to perform indexing magnetic type, or other.

In this variant with teeth, and in particular as visible on the Figures 4 and 6 , the balance 10 comprises a plurality of weights 4. In the first family of variants, each of the weights 4 is carried at least by the inner flange 1 by at least one second elastic connection 5 and each indexable in a stable angular position defined by the cooperation between a first indexing toothing 91 carried by the inner flange 1 or the flyweight 4, and a second indexing toothing 92. This second indexing gear 92 is carried by the flyweight 4 or by the outer ring 2 when the first indexing toothing 91 is carried by the inner flange 1, or is carried by the outer ring 2 when the first indexing tooth 91 is carried by the flyweight 4. In the second family of variants, each counterweight 4 is carried by the outer ring 2.

Any rotation of this outer ring 2 relative to the inner flange 1 under the action of an external torque changes the angular position of the weights 4 of the balance 10, each carried by the inner flange 1 by elastic connection 5 and each indexable among different positions stable angular corresponding to different inertias of the balance 10. The rotation of the outer ring 2, modifying the position of the flyweights 4, therefore modifies the inertia adjustment of the balance 10.

The figure 1 is a watch 10 according to the invention, which comprises, in a first upper plane PS an outer ring 2, carrying a peripheral toothing 8, and resiliently mounted relative to an inner flange 1 integral with the 11 of the balance wheel 10. The balance 10 comprises, in a second lower plane PI and parallel to the first upper plane PS, a surface support and angular support of the balance, which consists of either an outer surface 120 of the seam 12 of the balance 10, or a toothing 15 of a lower board 14, or the like; the lower plate 14 is shown with a lower elastic connection 16 with a hub 17 fixed on the shaft 11. This rocker 10 is shown facing an operating member 20 according to the invention, which comprises, at the level of the upper plane PS a control means 80, in particular carrying a control gear, in particular in the form of a driving wheel 81, arranged to cooperate with the peripheral toothing 8 of the outer ring 2, and at the lower plane PI complementary means 150 of support and holding, arranged to cooperate with the outer surface 120 of the serge 12 in particular by frictional elastic support, or the toothing 15 of the lower board 14 by locking meshing. If the cooperations by teeth in the upper planes PS and lower PI are convenient, they are not limiting, and may also consist of friction, or other.

More particularly, the function of variation of inertia is carried out in a built-in and redesigned balance, instead of being thus reported. A lower board 14 is fixed to the shaft 11 of the balance beam, while a monobloc top board 30 is fixed at its center to the shaft 11 of the balance, but can rotate in its outside. Centering springs relative to the shaft 11 of the balance, advantageously made in the form of elastic strips 19, visible on the figure 17 , make it possible to cancel any unintentional unbalance introduced by one or other of the lower boards 14 or greater 30 added. Care should be taken to judiciously adapt the number of elastic blades to the type of material. For example, since the rigidity of the monocrystalline silicon is anisotropic, and which, for example, in the case of a perpendicular to the crystal plane <100> has an azimuthal period of 90 °, this number should be even and equal to or greater than 4. In the case of an isotropic material, this number may be odd and equal to or greater than 3. After insertion on the shaft 11, the centers of these boards are preferably fixed permanently by means such as, but not limited to, a bonding or brazing.

In an alternative, the resilient blades pinching the shaft 11 of the balance must exert a friction greater than the maximum torque exerted on the outer ring 2 during the adjustment of inertia. To this end, the operating member 20 used to control the inertia adjustment advantageously comprises a setting device for limiting this printed torque to the outer ring 2.

In an advantageous embodiment, the rocker 10 comprises a monoblock top board 30 which comprises the inner flange 1, the first elastic guide links 3, the outer ring 2, the weights 4, the second elastic links 5, the first teeth of indexing 91, and the second indexing teeth 92, and the third elastic links 50 when the balance 10 comprises.

In a particular embodiment, the inner flange 1 comprises a plurality of resilient blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque.

In another particular embodiment, the inner flange 1 is irreversibly fixed to the shaft 11, by welding, brazing, bonding, or other similar process.

In yet another embodiment, the inner flange 1 comprises a plurality of resilient blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque, and these resilient blades 19 are fixed irreversibly on the shaft 11, by welding, brazing, gluing, or other similar process.

In an advantageous variant, to make a stop in angular position better than a simple pressing on the serge, the rocker 10 comprises a lower plate 14 fixed directly or indirectly to the shaft 11 and having peripheral stop means 15, such as than a toothing or the like.

In an advantageous variant, for precise control of inertia adjustment, the outer ring 2 comprises a peripheral and continuous toothing 8 oriented on the axis B of the shaft 11, and the rotation of the toothing 8 modifies the position of the weights 4 between two stable indexing positions.

In a particular embodiment, the inner flange 1 is integral with the shaft 11.

In a particular embodiment, the rocker 10 embeds a flexible monolayer and micro-machined structure, taking advantage of the high contour accuracy of "MEMS" technologies, typically 1 to 2 micrometers of positioning accuracy, for a thickness of 150 microns, constituting an upper monobloc board 30 as defined above.

Preferably, in order to give the system maximum precision, the boards are micro-machined (techniques resulting from the manufacture on silicon) and if each possible in a single layer (mask process), as shown.

It is thus possible to add such a monobloc top board 30 on an existing balance to bring it the inertia adjustment function offered by the invention, without significant volume occupation in the oscillator.

When the rocker 10 has a lower plate 14, it can also be performed in a "MEMS" technology or the like.

Of course, any other technology as precise, adapted and known to those skilled in the art is conceivable, such as laser cutting, water jet, or other.

The Figures 2 to 11 illustrate variants of flexible inertia adjustment mechanisms, according to the invention, in an advantageous but non-limiting embodiment comprising a monobloc top board 30.

Generally speaking, as visible on figure 2 and 3 , the outer ring 2, in particular provided with a toothing 8 in the preferred embodiment illustrated, can pivot elastically relative to its center, which is fixed to the balance shaft 11 as explained above. Angular portions of 180 °, 120 °, 90 °, 72 °, ..., and the number of respectively 2, 3, 4, 5, ..., are arranged between the center and the outer ring 2. They are responsible for carrying out the two main functions, ie the guiding for example with elastic blades, and the inertia adjustment for example with movable weights. One can imagine that these functions are alternated by angular sector, or integrated if it is possible. The rule of adaptation of the number of sectors to the material, mentioned above for the number of centering blades, also applies here.

The Figures 2 and 3 illustrate two variants, at 120 ° and at 180 °, of an upper board 30 comprising, between the inner flange and the outer ring, an alternation of first elastic bonds filling the rotational guiding function, and interposed between the previous ones , weights each elastically suspended.

In a first variant visible on the figure 4 , the first indexing toothing 91 is carried by the inner flange 1 and is constituted by an inner jumper 42 protruding radially, and the second indexing toothing 92 is carried by the flyweight 4 and is a first gear sector 43. This flyweight is suspended by a connection with three first necks 45, 21, 41, which together define an isosceles triangle ACC 'symmetrical about a perpendicular to a radial from the axis B of the beam 10, between two radial arm sections, one from the inner flange 11, and the other from the outer ring 2. The flyweight 4 in the form of circle sector can rotate elastically at C, during the angular displacement of the outer ring 2, moved by the triangle of elastic pivots C'-AC. The inner jumper 42 cooperates in holding stop with teeth of the toothed sector 43, and allows the precise positioning of the weight 4. A registration graduation 93 on the weight 4 allows the reading of its angular position. Correct sizing of the mechanism causes the synchronized displacement in the same notches of all weights, at the risk of causing an imbalance. An alternative consists of a mechanism comprising a single jumper and a single indexing rack for the complete structure, with a compensation weight to reduce the center of gravity to the center of rotation of the balance.

In a second variant visible on the figure 6 , the first indexing toothing 91 is carried by the weight 4 and comprises at least one tooth 46, and the second indexing teeth 92 is carried by the outer ring 2 and comprises at least a second toothed sector 72 of distinct center of the shaft B of the shaft 11. In this second variant, called cam, the weight 4 is a disc having two opposite teeth 46, attached by a flexible blade 47 perpendicular to a radial arm 49 from the inner flange 1. The outer ring 2 carries, on tracks, RA and RB rays, non-concentric with the axis B of the balance 10, which makes it possible to modify the inertia, two toothed sectors 72, with which the two teeth 46 of the flyweight 4. The change in inertia comes from the change in the radial position of the flyweight 4, which itself results from the change of relative angular position between the flyweight and the outer ring 2, via the slope corresponding to the radius RB or RA. This second variant comprises, like the first, a bidirectional range of adjustment. It should be noted that in neutral position, in both solutions there is no clamping / stress between jumper and rack, the space will be as thin as one can micro-machine slots in a single-layer process (a only photolithographic mask). This space (type 5 micrometers for 0.10 mm thick) can of course be reduced to 0 or less (constrained state) for the other angular positions.

The figure 7 illustrates a guide mechanism with flexible blades, in a variant where the inner flange 1 carries radial arms which themselves carry, for example, by means of radial elastic blades 31 with two second necks 34 each, an intermediate concentric sector 33 which is suspended by means of two other radial elastic blades 32 with two second necks 34 each, to the outer ring 2. The outer ring 2 is suspended on two concurrent blades in the center, fixed on the intermediate bend 33, which is itself connected to the inner flange 1. This is the series connection of two rotary guides RCC (remote center compliance = elasticity with remote center of rotation). The principle is explained in figure 8 , which illustrates the articulated connection at the second necks, for a half-structure with the four second necks 34 replaced by pivots K'L'M'N '. It is clear that the instantaneous center of rotation for small amplitudes is at the axis B of the shaft 11 of the balance 10.

The figure 9 illustrates a mechanism in which the inertia adjustment and the guidance are alternated by sectors of 60 °, substantially according to the variants respectively of the Figures 6 and 7 . The modification of inertia comes from the change in the radial position of the flyweight 4, which itself results from the change of relative angular position between the weight and the outer ring 2, via the slope corresponding to the radius RB or RA. Between the radial arms coming from the inner flange 1 and the outer ring 2 are seen pairs consisting, on the one hand of radial elastic blades 31 seen above, and also springs 36, mounted radially, for the reduction of the elastic torque of recall. These springs reduce the natural rotation rigidity of the blades, if one wants to avoid a too strong torque to exert on the outer ring 2 and use a low constant force indexing rack-jumper system. Since it is impossible to lithograph armed springs, it is possible to use hooks to arm springs made in a relaxed position: advantageously, when the rocker 10 comprises a monoblock top board 30, made by a "LIGA" or "MEMS" method or similar, each spring 36 consists of half-springs 361 provided with hooks 362 presented head to tail, remote from each other during the preparation of the one-piece board 30, as visible in the left part of the figure, and then just hang to form a hitch 363 to obtain the required return force. The figure 11 illustrates the variation of the elastic torque CE as a function of the deformation angle θ, in solid lines without these springs, and in broken line with these springs.

In a third variant illustrated in figure 12 the first indexing gear 91 is carried by the inner flange 1 and has a third sector toothed 44 whose center is distinct from the axis B of the shaft 11, and the second indexing teeth 92 is carried by the outer ring 2, and is constituted by an outer jumper 29. More particularly the balance 10 comprises here an upper monobloc board 30 which is a planetary flexible structure whose planets are unbalanced weights allowing the adjustment of inertia, which are connected to the inner flange 1 and / or to the outer ring 2 by means of elastic blades.

More particularly, the inner flange 1 directly carries non-concentric toothed sectors 44 with the axis B of the balance 10, each indexed in position by an outer jumper 29 secured to the outer ring 2, and the weights 4 are each connected to both the inner flange 1 and the outer ring 2, by resilient blades 48 substantially concentric with each other and with the axis B of the shaft 11.

This third variant functions as a planetary movement, in which the two flyweights 4 (planets) roll between the inner flange 1 and the outer ring 2, which are held together by these elastic blades 48 which wind around the flyweights 4. As the angle of rotation increases, the elastic return torque due to the resilient blades 48 may vary, in particular but not necessarily increase. Thus, to prevent skidding of the indexing system, it is possible to incline the toothed third sector rack 44 so as to obtain a retaining force which compensates for the torque of the blades 48 by the action of the external jumper 29. a particular embodiment, this retaining force is progressive. Note that this system is insensitive to shocks. Indeed, the couples caused by the imbalances of the flyweight-planets during a linear shock cancel each other out and do not cause involuntary rotation of the outer ring 2, as visible on the figure 13 . This is also valid for N flyweights solicited in any direction in the plane of motion. The external jumpers 29 must overcome the return torques exerted by the resilient blades 48, and, what is very important, center the outer ring 2 to not introduce unbalance.

Another embodiment, of the second family of variants, is illustrated in FIG. figure 18 : It is a central spiral inertia adjustment structure, in which the pivoting is not elastic, but made by friction on supports, here three centering supports.

In this embodiment, the balance wheel 10 with inertia adjustment comprises a shaft 11 carrying on the one hand a serge 12 via at least one arm 13, and on the other hand an inner flange 1 fixed on this shaft 11 and carrying, directly or indirectly, an outer ring 2, with, between the inner flange 1 and outer ring 2, a plurality of first elastic guide links 3, which are balanced in a plane perpendicular to the B-axis of the shaft 11.

According to the invention, in this embodiment, the outer ring 2 is distinct from the serge 12, and is arranged to pivot relative to the inner flange 1 under the action of an external torque exerted against a resistant torque exerted by the first elastic guide links 3.

This balance 10 comprises a plurality of weights 4, each carried by the outer ring 2 by means of at least one outer flexible blade 94, and each indexable in a stable angular position defined by the cooperation between a first indexing teeth 91 carried by the inner flange 1 and a second indexing teeth 92 which is carried by the flyweight 4. Any rotation of the outer ring 2 relative to the inner flange 1 changes the angular position of the flyweights 4. And the outer ring 2 comprises bearings 52 bearing guide lands 52 that includes the inner flange 1. Each bearing 5 is deployed on an angular sector corresponding to the adjustment range of the balance 10. The supports 52 that includes the inner flange 1 are advantageously located at the end of arm 51 substantially radial with respect to the axis B of the shaft 11. In a particular embodiment, these arms 51 are flexible, but are less s flexible as the outer flexible blades 94.

More particularly, the inner flange 1 comprises, as a first indexing toothing 91, a notched spiral 44 fixed to the shaft 11 of the balance 10, formed here of three notched sections of progressive radial dimension, while the outer ring 2 carries weights 4, of which there are three in this nonlimiting example, each secured by means of at least one outer flexible blade 94. In this same nonlimiting example, the outer ring 2 here comprises three bearing surfaces 53 on which sliding three supports 52, on an angular sector of 30 °, corresponding to the adjustment range, that comprise arms 51 of the toothed spiral 44. The relative rotation between the outer ring 2 and the toothed spiral 44, with which cooperate teeth 55, at the level of the second indexing teeth 92 of each weight 4, causes the centro-symmetric deployment of the weights 4.

In a particular and nonlimiting application, for a beam 10 with a serge 12 with a diameter of 10.6 mm, a monobloc top board 30 made of silicon with a diameter of 7.9 mm and a thickness of 150 micrometers, a total inertia of 1.83 . 10 ^-9 kg.m ² , the run setting corresponding to the 30 ° amplitude setting reaches 37.4 seconds per day.

The notches of the toothed spiral 44 can of course be adapted and reduced, in particular to achieve a requested resolution of, for example, 0.5 seconds per day. Advantageously, this mechanism also comprises vertical guiding elements to ensure the Z-resistance of the outer ring 2, not shown in the figure. The supports 52 for centering the outer ring 2 and the bearing surfaces 53 are advantageously far from a non-zero clearance of a value of a few micrometers, and adapted to guarantee the simultaneous fall of the jumpers of the balance wheel 10 during a tangential adjustment. Thus it is the flyweights 4 which perfectly center the outer ring 2 to the notched spiral 44, itself centered on the shaft 11 by flexible blades 19. During the rotational loading of the outer ring 2, the function arm 51 is to ensure that the teeth 55 of the three weights 4 fall synchronously into their toothed spiral notches 44, so that there is no offset. As a result, the torque exerted by the blades via these notches is higher than the friction torque at the end of the fall of the weights in the notches.

In an advantageous embodiment, this rocker 10 comprises a one-piece board which comprises the outer ring 2, the weights 4, the outer flexible blades 94 and the second indexing teeth 92. In an advantageous embodiment, the inner flange 1 comprises a plurality elastic blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque. In another embodiment, this inner flange 1 is irreversibly fixed on the shaft 11.

Naturally, this embodiment can be realized with a number of different elements.

The invention also relates to a 300 mechanical clockwork movement, such as visible in particular on the figure 20 , comprising at least one clock oscillator mechanism 100 comprising such a pendulum 10, and an oscillating member maneuver 20 arranged to control the inertia adjustment of the balance 10 by changing the position of at least some of the weights 4 that includes the balance 10. This actuator 20 is movable between an engaged position and at least one disengaged position. According to the invention, the operating member 20 comprises a stop means 160 arranged to immobilize directly or indirectly the serge 12 in the engaged position, and at least one control means 80, in particular toothed, arranged for, in the position engaged, rotate the outer ring 2, including a toothing 8 that includes the outer ring 2, to change the position of the weights 4 with which cooperates the outer ring 2.

The invention also concerns, as can be seen in particular on the figure 20 , a watch 1000 comprising such a movement 300, a control member constituted by a pusher or a ring gear 110 arranged to control through a sliding pinion 111 the movement of a timer 112. This timer 112 comprises a wheel 115, which is arranged to drive at least one such control means 80 toothed in the engaged position of the actuating member 20. And the watch 1000 according to the invention comprises a clutch ring 102 rotatable to control the clutch or disengagement of the actuator 20, and this clutch ring 102 is preferably hidden from the user.

Such an arrangement allows the transformation of an existing watch, having, pre-existing, a control member such as crown, push, bezel, bolt or the like, a sliding pinion, and a timer.

The invention is described here in the particular, non-limiting case of a rocker 10 having a monobloc top plate 30, the outer ring 2 of which has a toothing 8.

As can be seen in particular on the figure 16 by rotation of this upper monobloc board 30 relative to the seam 12 of the balance 10, or, as here to the lower board 14 when the balance 10 has one, and which is synchronous with the seam 12, this serge 12 being in advance locked in rotation, and for any angular position of the serge 12, the inertia of the upper monobloc board 30, and therefore of the balance 10, changes. The rotation of the outer ring 2, in particular of this one-piece upper board 30 is carried out by the control means 80 of the operating member 20, in particular in the form of a driving wheel 81 adjacent the balance 10, carried by a 150 bistable lever that comprises the stop means 160, in the non-limiting embodiment illustrated by the figures. The lever 150 is engaged / disengaged laterally by the mechanical action of a rotary ring 102 peripheral to the watch movement 300 which includes the oscillator 100, which allows access to the oscillator 100 wherever it is located on the periphery.

The figure 16 shows an example of a part of this clutch mechanism. The clutch ring 102 acts on two slopes 154 and 155 of the lever 150 by a finger 103 that it comprises, to control the tilting of the lever 150, according to its direction of rotation. The position drawn in solid lines shows the lever 150 in the locking position of the toothing 15 of the lower board 14, by a comb 151 that includes the lever 150, in an "ON" position: the balance 10 is engaged with the timer and the crown 110 of the watch 1000. A jumper lever 156 introduces a bistability on the lever 150. To move to the "OFF" position of unblocking, in broken lines in the figure, the ring 102 rotates downwards and causes the tilting and disengagement of the lever 150, releasing the pendulum 10.

If here the lever 150 comprises a comb 151 to cooperate with the lower toothing 15 of the lower plate 14, it is understood that it can also, when the rocker 10 is devoid of lower plate 14, have a friction surface arranged to cooperate and in particular come into contact with the outer surface 120 of the serge 12.

When the lever 150 is released, the flexible structure is held by an integrated jumper, such as the inner jumper 42 of the figure 4 , or the outer jumper 29 of the figure 12 . This integrated jumper retains the flyweight 4, and exerts a sufficient return torque to also retain the outer ring 2.

Preferably, in order to give the system maximum precision, the lower 14 and upper 30 boards are micromachined (techniques from silicon fabrication) and if possible in a single layer (mask process), as shown. The lever 150, engaged by the action of the ring 102, approaches laterally of the balance 10 (ON position) and angularly maintains it by means of its comb 151 in engagement with the lower board 14 attached to the balance 10 The driving wheel 81 then meshes simultaneously with the upper board 30.

The watch 1000 according to the invention comprises a control member constituted by a pusher, a bolt, or the like, or, as shown in the figures, in particular on the figure 20 , a crown 110, which has the advantage a reversible setting in both directions. The rotation by the crown 110, conventionally mobile between at least two positions T1 and T3, drives through the sliding pinion 111 the movement of the timer 112, the input wheel 115, the driving wheel 81, and therefore the outer ring 2 of the upper board 30, which can rotate and change the inertia of the balance 10.

To guarantee an effortless insertion of the teeth, these are pointed, as visible on the figure 15 . Once inserted, their profile being straight, to a slightly negative degree, the shearing of the contact forces exerted by the driving wheel 81 and the comb 151 of the lever 150 on the two boards, upper 30, and lower 14, do not cause of radial resultant capable of moving the shockproof pivots of the balance 10.

The timer 112 may cause a wheel at the center 113 carrying a needle 114 to display the adjustment made.

The invention also relates to a watch assembly comprising such a watch 1000, as visible on the Figures 20 and 21 , and an adjustment tool 200 which is arranged to control the rotation of the clutch ring 102. Advantageously and according to the invention, the clutch ring 102 and the adjustment tool 200, in particular constituted by a magnetic key, as illustrated, comprise complementary magnetic zones 101, respectively 201, for the rotational drive of the clutch ring 102 under the action of the adjusting tool 200 when the complementary magnetic zones 101 and 201 are cooperatively through the case of the watch 1000. The ring 102 is advantageously, in a particular variant, provided with ferromagnetic targets 101: P, Q, R, S, judiciously placed and hidden, so that only a key 200 outer having magnetic studs 201, including neodymium magnets or the like, placed in certain places P ', Q', R ', S', and put in relation, can take off if necessary and turn. The advantage of a ring 102 only ferromagnetic, and of substantially circular shape, generally of revolution, is its insensitivity to external magnetic fields capable of rotating it, and external ferromagnetic objects in the undesirable case of presence of magnets.

The figure 20 illustrates an overview of the gait adjustment device by changing the inertia of the balance 10, without opening the watch 1000 and without adding a pusher. The clutch ring 102 comprising the ferromagnetic targets 101 is rotated by a magnetic key 200, an external tool the watch, comprising the magnetic pads 201, when it is positioned coaxially with the watch (with their axes combined). The ring 102 may first be attracted axially against the magnets, then a rotation of the key 200 causes a rotation of the ring 102 by reluctant torque on the ferromagnetic targets 101. The angular position of these targets being hidden from the user, only the right key can cause the ring to rotate. The goal is to make the adjustment by the SAV, so as not to tarnish the reputation of the brand in case of attempted unsuccessful adjustment on the part of the wearer. The magnetic key 200 thus cooperates with the clutch ring 102, the number and position of the ferromagnetic targets 101 are hidden from the user, to prevent an unsuccessful attempt by the user to adjust. Preferably, the magnetic pads 201 are also hidden at the key 200.

The process of setting the procedure is as follows. Firstly, the pivoting of the ring 102 by means of the magnetic key 200 causes the lever 150 to tilt towards the balance 10, in order to engage the driving wheel 81 of the lever 150 with the adjusting device of the lever. rotary inertia embedded on the balance 10. It thus passes from the OFF position to the ON position. The driving wheel 81 is integral with the idler wheel 115 of the timer 112. Then, by pulling the crown 110 at position T3 (setting the time), the crown 110 is at the same time engaged with the minute hand 114 and the inertia adjustment of the balance 10, via the sliding pinion 111 and the return. The rotation of the ring 110 then allows the adjustment of inertia, with in addition a reading of this possible correction by the minute hand 114, which is very convenient. Once the adjustment has been made, the lever 150 is disengaged with the aid of the key 200 by returning from the ON position to the OFF position, then a time-setting is performed and the crown 110 is finally put back into position T1.

• de modifier l'inertie du balancier, notamment sur une plage de typiquement 10 à 100 secondes par jour, voire davantage;
• par modification de position de masselottes entre différentes positions stables, puisqu'elles sont toujours accrochées dans des crans ;
• à l'aide d'au moins un élément flexible à inertie réglable micro-usiné, embarqué sur ce balancier ;
• de disposer d'un mécanisme d'embrayage de la rotation de couronne vers le changement d'inertie via une clé magnétique agissant sur une bague d'embrayage au travers de l'emboîtage.

In short, the invention allows:

• to modify the inertia of the balance, in particular over a range of typically 10 to 100 seconds per day or more;
• by modifying the position of weights between different stable positions, since they are always hooked in notches;
• using at least one flexible element with adjustable micromachined inertia, embedded on this beam;
• to have a clutch mechanism of the rotation of the crown to the change of inertia via a magnetic key acting on a clutch ring through the casing.

Claims (15)

1. Timepiece balance wheel with adjustable inertia (10), comprising a staff (11) carrying, on the one hand, a rim (12) via at least one arm (13), and on the other hand, an inner flange (1) fixed to said staff (11) and directly or indirectly carrying an outer ring (2) with, between said inner flange (1) and said outer ring (2), a plurality of first elastic guide connections (3), which are inertia balanced with respect to the axis (B) of said staff (11) and in a plane perpendicular to said axis (B), said outer ring (2) being distinct from said rim (12) and arranged to pivot with respect to said inner flange (1) under the action of an external torque exerted against a resistant torque exerted by said first elastic guide connections (3), said balance (10) comprising a plurality of inertia blocks (4) each carried by said outer ring (2) by means of at least one external flexible strip (94), characterized in that each said external flexible strip (94) can be indexed in a stable angular position defined by the cooperation between a first indexing toothing (91) carried by said inner flange (1) and a second indexing toothing (92) which is carried by said inertia block (4), and in that any rotation of said outer ring (2) with respect to said inner flange (1) modifies the angular position of said inertia blocks (4), said outer ring (2) comprising guide shoulders (53) sliding on supports (52) comprised in said inner flange (1).
2. Balance (10) according to claim 1, characterized in that each said shoulder (53) extends over an angular sector corresponding to the range of adjustment of said balance (10).
3. Balance (10) according to claim 1 or 2, characterized in that said supports (52) comprised in said inner flange (1) are located at the end of substantially radial arms (51) with respect to said axis (B) of said staff (11).
4. Balance (10) according to any of claims 1 to 3, characterized in that said balance (10) forms an inertia adjustment structure with a central spiral, wherein pivoting is achieved by friction of said supports (52) on said shoulders (53), and in that said inner flange (1) includes, as said first indexing toothing (91), a notched spiral (44) fixed to said staff (11), and in that any relative rotation between said outer ring (2) and said notched spiral (44), which cooperates with teeth (55) comprised in said second indexing toothing (92) of each said inertia block (4), causes the centrosymmetric deployment of said inertia blocks (4).
5. Balance (10) according to any of claims 1 to 4, characterized in that said balance (10) further includes vertical guide elements for ensuring the axial retention, parallel to said axis (B) of said staff (11), of said outer ring (2).
6. Balance (10) according to any of claims 1 to 5, characterized in that said centring supports (52) of said outer ring (2) and said shoulders (53) are advantageously separated by a non-zero play, with a value of a few micrometers, and adapted to ensure the simultaneous drop of jumper springs (42, 49) comprised in said balance (10) during a tangential adjustment.
7. Balance (10) according to any of claims 1 to 6, characterized in that said balance (10) comprises a one-piece upper plate which includes said outer ring (2), said inertia blocks (4), said external flexible strips (94) and said second indexing toothings (92).
8. Balance (10) according to any of claims 1 to 7, characterized in that said inner flange (1) comprises a plurality of elastic strips (19) concentrically clamping said staff (11) with a friction torque greater than the maximum value of said external torque.
9. Balance (10) according to any of claims 1 to 7, characterized in that said inner flange (1) is irreversibly attached to with said staff (11).
10. Balance (10) according to any of claims 1 to 9, characterized in that said outer ring (2) comprises a peripheral and continuous toothing (8) centred on said axis (B) of said staff (11), and in that the rotation of said toothing (8) modifies the position of said inertia blocks (4) between two stable indexing positions.
11. Mechanical timepiece movement (300) comprising at least one timepiece oscillator mechanism (100) including a said balance (10) according to any of claims 1 to 10, characterized in that said mechanical movement (300) includes an operating member (20) arranged to control the inertia adjustment of said balance (10) by modifying the position of at least some of said inertia blocks (4) comprised in said balance (10), said operating member (20) being movable between a coupled position and at least one uncoupled position, characterized in that said operating member (20) comprises a stop means (160) arranged to directly or indirectly immobilise said rim (12) in said coupled position, and at least one control means (80) arranged, in said coupled position, to drive in rotation said outer ring (2) to modify the position of said inertia blocks (4) which cooperate with said outer ring (2).
12. Mechanical movement (300) according to claim 11, characterized in that the rotation of said outer ring (2) is accomplished by said control means (80) which includes a drive wheel (81) adjacent to said balance (10), carried by a bistable lever (150) comprised in said stop means (160), said lever (150) being coupled/uncoupled sideways by the mechanical action of a rotary ring (102) peripheral to said timepiece movement (300).
13. Watch (1000) comprising a said movement (300) according to claim 12, and a control member consisting of a push piece or a crown (110) arranged to control, via a sliding pinion (111), the movement of a motion-work (112), characterized in that said motion-work (112) includes an input wheel (115) arranged to drive at least a said control means (80) in said coupled position of said operating member (20), and further characterized in that said watch (1000) includes a coupling ring (102) that can be moved in rotation to control the coupling or uncoupling of said operating member (20).
14. Timepiece assembly comprising a said watch (1000) according to claim 13, and an adjustment tool (200) arranged to allow the inertia adjustment of said balance (10), characterized in that said adjustment tool (200) is arranged to control the rotation of said coupling ring (102), and in that said coupling ring (102) and said adjustment tool (200) include complementary magnetic areas (101; 201) for driving in rotation said coupling ring (102) under the action of said adjustment tool (200) when said complementary magnetic areas (101; 201) are cooperating.
15. Timepiece assembly according to claim 14, characterized in that said adjustment tool (200) is a magnetic key comprising magnetic studs (201) and arranged to cooperate with said coupling ring (102), whose magnetic areas (101) are ferromagnetic targets (101), the number and position of which are concealed from the user, to prevent an unsuccessful attempt at adjustment by the user.

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