EP3435173B1 - Mechanical movement with isochronous rotary resonator, which is not position-sensitive - Google Patents

Description

Field of the invention

The invention relates to a mechanical clockwork movement comprising at least one energy storage means arranged to drive a gear train, an output mobile of which is arranged to pivot around a motor axis, and comprising a rotary resonator which comprises at least a central mobile, arranged to pivot about a central axis, and comprising an input mobile arranged to cooperate with the output mobile.

The invention also relates to a watch comprising such a movement.

The invention relates to the field of time bases for mechanical watch movements.

Invention background

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

Most modern mechanical watches are equipped with a balance-spring and a Swiss lever escapement. The balance-spring constitutes the time base of the watch. It is also called resonator. As for the exhaust, it fulfills two main functions:

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

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

The most commonly used Swiss lever escapement has a low energy efficiency, around 30%. This low efficiency comes from the fact that the movements of the exhaust are jerky, that there are falls or lost paths that are necessary to accommodate the machining dispersions, and also from the fact that several components transmit their movement. via inclined planes which rub against each other. Such mechanisms are disclosed in the documents CH293180 A and FR630831A .

Summary of the invention

The present invention aims to eliminate the jerks of the exhaust, in order to increase the yield. To achieve this objective, a rotary resonator is proposed, characterized in particular by the possibility of maintaining rotation by a torque applied directly to the axis of the resonator, thus avoiding the dynamic losses of a conventional anchor escapement.

Historically, watchmakers have not considered rotary resonators as a time base for watches because rotary resonators are generally not isochronous, and they are moreover sensitive to gravity, therefore to the position of the watch in the field of gravity.

A mechanism like the Watt regulator can form a basis for a rotary resonator, but at the cost of modifications to make it isochronous and insensitive to gravity. Indeed, the Watt regulator is sensitive to its orientation in the gravity field, because the global center of mass of the two weights moves when the amplitude changes: the weights rise along the axis when the amplitude increases. Consequently, the contribution of gravity to the restoring force fluctuates with orientation. In addition, the watt regulator is anisochronous because the return force of the weights, by spring and / or by gravity does not meet certain conditions.

• condition d'isochronisme : existence de forces de rappel élastiques (ou potentiel élastique) provoquant sur le centre de masse de chaque demi-bras une force centrale d'intensité proportionnelle à la distance entre l'axe de rotation et le centre de masse du demi-bras ;
• - condition d'insensibilité aux positions : utilisation d'au moins deux demi-bras guidés, de façon à pouvoir éloigner leur centre de masse de l'axe de rotation, tout en maintenant le centre de masse global du résonateur en position fixe ;
• - condition de forces de réactions nulles dans le support: utilisation de bras répartis en symétrie autour de l'axe, pour annuler les réactions dans les pivots à toutes les amplitudes.

The invention therefore endeavors to fulfill the conditions which make it possible to have a rotary resonator which can be used as a time base for a time instrument:

• isochronism condition: existence of elastic restoring forces (or elastic potential) causing on the center of mass of each half-arm a central force of intensity proportional to the distance between the axis of rotation and the center of mass of the half -arms ;
• - condition of insensitivity to positions: use of at least two guided half-arms, so as to be able to move their center of mass away from the axis of rotation, while maintaining the overall center of mass of the resonator in a fixed position;
• - condition of zero reaction forces in the support: use of arms distributed symmetrically around the axis, to cancel the reactions in the pivots at all amplitudes.

To this end, the invention relates to a mechanical clockwork movement according to claim 1.

The invention also relates to a watch comprising such a movement.

Brief description of the drawings

• la figure 1 représente, de façon schématisée et en perspective, une première variante de mécanisme résonateur selon l'invention, réalisée sur la base base du mécanisme résonateur à pantographe selon la demande EP16195399 du du même déposant, mais où le pivotement des éléments inertiels se fait orthogonalement au pivotement de l'entraînement ;
• la figure 2 représente, de façon similaire à la figure 1, une autre variante de mécanisme résonateur selon l'invention, simplifiée par suppression des liaisons cinématiques articulées ;
• la figure 3 représente le détail d'un mécanisme résonateur rotatif, similaire à celui de la figure 2, comportant un mobile central agencé pour pivoter autour d'un axe central, et par rapport auquel sont mobiles, selon un axe orthogonal, deux éléments inertiels méplats, rappelés vers le mobile central par des moyens de rappel élastique ici constitués par des vés élastiques à lames fines ;
• la figure 4 est une variante dans laquelle les moyens de rappel élastique sont constitués par des guidages flexibles à lames croisées, chaque guidage flexible comportant deux niveaux et une lame par niveau, ces deux lames se croisant en projection sur un pan parallèle à ceux des niveaux ;
• la figure 5 est une vue en projection plane d'un premier agencement comportant deux telles lames croisées asymétriques, dans un agencement particulier agencé pour créer un couple de rappel proportionnel au sinus du double de l'angle de pivotement ;
• la figure 6 est une vue en projection plane d'un deuxième agencement comportant deux lames formant un pivot RCC à centre de rotation déporté, dans un agencement particulier agencé pour créer également un couple de rappel proportionnel au sinus du double de l'angle de pivotement ;
• la figure 7 représente, de façon schématisée et en perspective, un mouvement comportant un tel résonateur rotatif, d'axe central parallèle à l'axe principal d'affichage du mouvement ;
• la figure 8 représente, de façon schématisée et en perspective, un mouvement comportant un tel résonateur rotatif, d'axe central perpendiculaire à l'axe principal d'affichage du mouvement.

Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, where:

• the figure 1 shows, schematically and in perspective, a first variant of a resonator mechanism according to the invention, produced on the basis of the pantograph resonator mechanism according to demand EP16195399 from the same applicant, but where the pivoting of the inertial elements is orthogonal to the pivoting of the drive;
• the figure 2 represents, similarly to the figure 1 , another variant of a resonator mechanism according to the invention, simplified by eliminating the articulated kinematic links;
• the figure 3 represents the detail of a rotary resonator mechanism, similar to that of the figure 2 , comprising a central mobile arranged to pivot about a central axis, and with respect to which are movable, along an orthogonal axis, two flat inertial elements, returned to the central mobile by elastic return means here constituted by elastic ves with thin blades;
• the figure 4 is a variant in which the elastic return means are constituted by flexible guides with crossed blades, each flexible guide comprising two levels and one blade per level, these two blades intersecting in projection on a pan parallel to those of the levels;
• the figure 5 is a plan projection view of a first arrangement comprising two such asymmetrical crossed blades, in a particular arrangement arranged to create a return torque proportional to the sine of twice the pivot angle;
• the figure 6 is a plan view of a second arrangement comprising two blades forming an RCC pivot with offset center of rotation, in a particular arrangement arranged also to create a return torque proportional to the sine of twice the pivot angle;
• the figure 7 shows, schematically and in perspective, a movement comprising such a rotary resonator, with a central axis parallel to the main axis of display of the movement;
• the figure 8 shows, schematically and in perspective, a movement comprising such a rotary resonator, of central axis perpendicular to the main axis of display of the movement.

Detailed description of preferred embodiments

Requirement EP16195399 by the same applicant relates to a resonator mechanism for a clockwork movement, comprising an input mobile mounted pivoting about an axis of rotation and subjected to a motor torque, and comprising a central mobile, integral in rotation with this input mobile about the axis of rotation and arranged to rotate continuously. This resonator mechanism comprises a plurality of N inertial elements, each mobile according to at least one degree of freedom relative to the central mobile, and returned towards the axis of rotation by elastic return means, which are arranged to cause a return force. on the center of mass of the inertial element. This resonator mechanism has a symmetry of rotation of order N. This resonator mechanism comprises means of kinematic connection between all the inertial elements, and which are arranged to maintain, at all times, all the centers of mass of the inertial elements at the same distance from the axis of rotation, and the elastic return means cause an elastic potential characterized by a particular relationship. More particularly, this resonator mechanism has a pantograph type structure.

The aim here is to improve such a mechanism. Indeed, the drive torque and the aerodynamic resistance torque generate a radial force which adds to the elastic potential, and disturbs the isochronism.

The present invention proposes to orient the pivoting of the inertial elements differently, so as not to disturb the isochronism by the drive or tangential aerodynamic forces. The figure 1 illustrates a variant of a resonator mechanism according to the invention, in which the pivoting of the inertial elements takes place orthogonally to the pivoting of the drive.

The figure 2 shows that the complex articulated link of the mechanism of the figure 1 , arising directly from the request EP16195399 , may disappear in favor of a very simple structure: the present invention has the advantage of combining the driving mobile and the resonator in a single entity which is very simple to produce.

This mechanism avoids the shocks and friction inherent in badly tuned groove or connecting rod-crank mechanisms.

The invention avoids the unnecessary multiplication of elastic elements, between the plate and the inertial element on the one hand, and between the driving mobile and the inertial element on the other hand.

Thus, the invention relates to a mechanical clockwork movement 100 comprising at least one energy storage means 200, such as a barrel or the like, arranged to drive a gear train 300 of which an output mobile is arranged to pivot around d 'a motor axis.

This movement 100 comprises a rotary resonator 10, which comprises at least one central mobile 1, arranged to pivot around a central axis A.

More particularly, this central axis A is parallel or perpendicular to the motor axis.

The central mobile 1 comprises an input mobile 2, which is arranged to cooperate with the output mobile.

According to the invention, the rotary resonator 10 comprises at least one inertial element 3 arranged to pivot relative to the central mobile 1 around a secondary axis B perpendicular to the central axis A and intersecting with it, and returned to a position of rest, relative to the central mobile 1, by at least one elastic return element 4, and this secondary axis B passes through the center of mass of the inertial element 3 which is associated with it.

More particularly, the rotary resonator 10 comprises a plurality of inertial elements 3, each arranged to pivot relative to the central mobile 1 around a secondary axis B perpendicular to the central axis A and intersecting with it, and each recalled towards a rest position, relative to the central mobile 1, by at least one elastic return element 4.

And each secondary axis B passes through the center of mass of the inertial element 3 which is associated with it.

• où θ₁ est l'angle d'inclinaison de l'élément inertiel 3 par rapport à sa position de repos qui est sa position d'équilibre à l'arrêt,
• où ω₃ est la vitesse de rotation du mobile central 1, qui est donc la pulsation du résonateur,
• où I₂ est l'inertie de l'élément inertiel 3 par rapport un axe transverse E perpendiculaire à la fois à l'axe central A et à l'axe secondaire B,
• et où I₃ est l'inertie de l'élément inertiel 3 par rapport à l'axe central A.

More particularly, this at least one elastic return element 4 is arranged to apply to the respective inertial element 3 a torque with an elastic return moment, according to the relationship: $$\mathrm{M}(({\mathrm{\theta }}_{1)}=\mathrm{½}.{{\mathrm{<figure-callout\; id="3"\; label="\omega "\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_3}^2.\left({\mathrm{I}}_2-{\mathrm{<figure-callout\; id="3"\; label="I"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">I</figure-callout>}}_3\right).{\mathrm{<figure-callout\; id="1"\; label="sin2\theta "\; filenames="imgf0003.png"\; state="\{\{state\}\}">sin2\theta </figure-callout>}}_1,$$

• where θ ₁ is the angle of inclination of the inertial element 3 relative to its rest position which is its position of equilibrium when stopped,
• where ω ₃ is the speed of rotation of the central mobile 1, which is therefore the pulsation of the resonator,
• where I ₂ is the inertia of the inertial element 3 with respect to a transverse axis E perpendicular to both the central axis A and the secondary axis B,
• and where I ₃ is the inertia of the inertial element 3 with respect to the central axis A.

More particularly, this rotary resonator 10 has, in a rest position, a rotational symmetry about the central axis A, of order N, where N is an integer, greater than or equal to 2.

More particularly, the inertial elements 3 that the rotary resonator 10 comprises are, in a rest position, in rotational symmetry about the central axis A, of order N, where N is an integer, greater than or equal to 2.

More particularly still, each inertial element 3 has a symmetry of rotation of order 2 around its secondary axis B.

In a variant, at least one elastic return element 4 is fixed at a first end to the central mobile 1, and at a second end to the inertial element 3.

In another variant, which can naturally be combined with the previous one, at least one elastic return element 4 is fixed at a first end to an inertial element 3, and at a second end to another inertial element 3.

In yet another variant, visible in particular on figures 3 and 4 , each elastic return element 4 is fixed at a first end to the central mobile 1, and at a second end to an inertial element 3.

More particularly, and as can be seen in the embodiments illustrated, which are not limitative, all the inertial elements 3 of the same rotary resonator 10 are arranged to pivot around a common secondary axis B.

In particular variants visible in particular to figures 3 and 4 , at least one said inertial element 3 is at least 5 times longer than wide, and at least 5 times wider than thick.

In an advantageous embodiment, the rotary resonator 10 comprises at least one flexible guide, to ensure the pivoting and the elastic return of at least one inertial element 3 relative to the central mobile 1.

This flexible guidance can be achieved in different ways: flexible blades or necked blades, arranged in a crossed plane, or in parallel and crossed planes projected onto one of these parallel planes, or else arranged in an RCC (Remote Center) configuration. Compliance), that is to say with a remote center of rotation, the blades making a vee between them, or others.

The use of such flexible guides to perform the function of rotary guide and elastic return makes it possible to eliminate the friction inherent in a traditional pivot of the shaft-bearing type, or the like.

Depending on the embodiment, these flexible guides can either be attached to the central mobile 1 and / or on an inertial element 3, or be in one piece with at least one, or both. The monobloc executions can be in micro-machinable material, implemented by “Liga” or “Mems” process or similar, in at least partially amorphous material, in silicon and silicon oxide, in “DLC” (diamond like carbon), Or other.

More particularly, this flexible guide is a pivot with blades which are, or crossed coplanar, or crossed in projection on a projection plane perpendicular to the central axis A as in the embodiment of the figure 4 . This configuration has the advantage of guaranteeing excellent walking performance.

It is advantageous that the overall center of mass remains fixed, and that the cumulation of any parasitic displacements of the individual centers of mass of the inertial elements, during their pivoting, vanishes. In other words, the overall center of mass of the entire rotary resonator 10 remains fixed regardless of the amplitude. This can be obtained in particular by the combination of geometric symmetry in rotation, and by the choice of identical flexible guidance for the entire rotary resonator 10: each inertial element 3 which composes it is recalled by the same flexible guidance.

The use of crossed blades, in particular geometries, also makes it possible to ensure that the restoring torque caused by the flexible guidance on each of the inertial elements is proportional to the sine of twice the pivot angle of this inertial element 3.

Two particular arrangements, in no way limitative, are described below to explain the means of achieving this.

The figure 5 shows a pivot with asymmetrical crossed blades: this flexible guide is arranged to impart to the inertial element 3 a return torque proportional to the sine of twice the pivot angle of said inertial element 3. This flexible guide comprises two flexible blades 31, 32, asymmetrical each joining a first recess 41, 42, of the central mobile 1 to a second recess 51, 52 of the inertial element 3. These first recesses 41, 42, define with the second recesses 51, 52, respectively two main directions DL1, DL2 blades. The central mobile 1 and the inertial element 3 are each more rigid than each of the flexible blades 31, 32. The two main directions of blades DL1, DL2, define a theoretical pivot axis D, at their crossing when these two flexible blades 31 , 32 are coplanar, or at the crossroads of their projections on the projection plane when the two flexible blades 31, 32 develop on two levels parallel to the projection plane but are not coplanar as in the case of the figure 4 , and at an angle at the top α equal to 112.5 °. The second 32 of these blades has, between its opposite recesses, a second total length L2 three times the first total length L1 of the first 31 of the blades. And the distances between the first recesses 41, 42, and the theoretical pivot axis D are, for the second blade 32 a second axial distance D2 equal to 0.875 times the second total length L2, and, for the first blade 31, a first axial distance D1 equal to 0.175 times the first total length L1.

The figure 6 shows a configuration RCC, with offset center of rotation, which is not produced in a single piece, but where the blades are angularly constrained by a small angle, in the vicinity of at least one of their ends, for example by introduction of 'A laterally offset slot relative to the theoretical blade direction. The flexible guidance produced by this particular RCC pivot also makes it possible to create a torque proportional to the sine of twice the angle, said flexible guidance is produced by a pivot pivot with offset center of rotation constituting a virtual pivot, the embedding of which blades 31, 32, in housings 51, 52, which comprises the central mobile 1 and / or the inertial element 3 results from an angular preload of 0.15 radian, with a torsion at the embedding, the angle at the top which form the directions of the recesses of the blades 31, 32, at the level of the virtual pivot is 52.642 °, and the distance between the virtual pivot and the nearest recess is equal to 0.268864 times the length of each of the blades 31, 32, which are identical here, between their recesses in the free state before the prestressing of their end.

More particularly, this flexible guide is thermally compensated.

More particularly still, this flexible guide comprises blades of oxidized silicon, on which a differential growth of silicon dioxide during a heat treatment makes it possible to put under strong prestressing elements of smaller section, such as blades within a one-piece assembly.

In the variant of the figure 1 , the rotary resonator 10 comprises, articulated with certain inertial elements 3, additional kinetic connecting elements 5, which constitute with these inertial elements 3 a structure articulated pantograph type, and which are arranged to increase the radial deployment of the rotary resonator 10 by limiting its height along the central axis A.

In the variant of the figure 7 , the movement 100 comprises at least one main axis P of display by needles or discs, and the central axis A is parallel to this main axis P.

In the variant of the figure 8 , the central axis A is this time perpendicular to the main axis P.

For example, the gearbox output mobile 300 is an endless screw, arranged to cooperate with a pinion which constitutes the input mobile 2.

In particular, the rotary resonator 10 comprises only two or three inertial elements 3. In fact, a compromise is to be found between performance and size, and a resonator with two inertial elements in rotation symmetry ensures the required performance.

In an advantageous variant, the pivoting of the central mobile 1 is carried out on at least one magnetic pivot, so as to obtain the best efficiency.

The invention also relates to a mechanical watch 1000 comprising at least one such movement.

• la suppression du travail du frottement des pivots d'un balancier-spiral usuel, pour augmenter le facteur de qualité du résonateur ;
• la suppression des saccades de l'échappement afin d'augmenter le rendement d'échappement ;
• l'augmentation de la réserve de marche des montres mécaniques actuelles ;
• l'augmentation de la précision des montres mécaniques actuelles.

The present invention has important advantages:

• the elimination of the work of the friction of the pivots of a usual balance-spring, to increase the quality factor of the resonator;
• the elimination of exhaust jerks in order to increase the exhaust efficiency;
• increasing the power reserve of current mechanical watches;
• increasing the precision of current mechanical watches.

For a given movement size, we expect to increase the watch’s autonomy fivefold, and to double the regulating power of the watch. This amounts to saying that the invention allows a gain of a factor of 10 on the performance of the movement.

Claims (25)

1. Mechanical horological movement (100) comprising at least one energy storage means (200) designed to drive a gear train (300) of which an output mobile component is designed to pivot about a drive axis and comprising a rotary resonator (10) which comprises at least one central mobile component (1) designed to pivot about a central axis (A) and comprising an input mobile component (2) designed to collaborate with the said output mobile component, the said rotary resonator (10) comprising at least one inertial element (3) designed to pivot with respect to the central mobile component (1) about a secondary axis (B) perpendicular to the said central axis (A) and secant therewith, and characterized in that the said inertial element (3) is returned towards a rest position, relative with respect to the said central mobile component (1), by at least one elastic return element (4), and further characterized in that the said secondary axis (B) passes through the centre of mass of the said inertial element (3) associated with it.
2. Movement (100) according to Claim 1, characterized in that the said rotary resonator (10) comprises a plurality of inertial elements (3) each one designed to pivot with respect to the central mobile component (1) about a secondary axis (B) perpendicular to the said central axis (A) and secant therewith, and each one returned towards a rest position, relative with respect to the said central mobile component (1), by at least one elastic return element (4), and further characterized in that each said secondary axis (B) passes through the centre of mass of the said inertial element (3) associated with it.
3. Movement (100) according to Claim 1 or 2, characterized in that the said at least one elastic return element (4) is designed to apply to the said inertial element (3) a torque with an elastic return moment, according to the relationship: $$\mathrm{M}\left({\mathrm{\theta }}_1\right)=\mathrm{½}.{{\mathrm{\omega }}_3}^2.\left({\mathrm{I}}_2-{\mathrm{I}}_3\right).\sin \left({\mathrm{2\theta }}_1\right),$$

   

   where θ₁ is the angle of inclination of the said inertial element (3) with respect to its said rest position which is its position of equilibrium when stationary, where ω₃ is the angular velocity of the said central mobile component (1), where I₂ is the inertia of the said inertial element (3) with respect to a transverse axis (E) perpendicular both to the said central axis (A) and to the said secondary axis (B) and where I₃ is the inertia of the said inertial element (3) with respect to the said central axis (A).
4. Movement (100) according to one of Claims 1 to 3, characterized in that the said rotary resonator (10) exhibits, in a rest position, rotational symmetry about the said central axis (A) of order N, where N is greater than or equal to 2.
5. Movement (100) according to Claim 2, characterized in that the said inertial elements (3) that the said rotary resonator (10) comprises have, in a rest position, rotational symmetry about the said central axis (A) of order N, where N is greater than or equal to 2.
6. Movement (100) according to one of Claims 1 to 5, characterized in that at least one said inertial element (3) exhibits rotational symmetry of order 2 about its said secondary axis (B).
7. Movement (100) according to Claim 6, characterized in that each said inertial element (3) exhibits rotational symmetry of order 2 about its said secondary axis (B).
8. Movement (100) according to one of Claims 1 to 7, characterized in that at least one said elastic return element (4) is fixed at a first end to the said central mobile component (1) and at a second end to the said inertial element (3).
9. Movement (100) according to one of Claims 1 to 8, characterized in that at least one said elastic return element (4) is fixed at a first end to one said inertial element (3) and at a second end to another said inertial element (3).
10. Movement (100) according to Claim 8, characterized in that each said elastic return element (4) is fixed at a first end to the said central mobile component (1) and at a second end to the said inertial element (3).
11. Movement (100) according to one of Claims 1 to 10, characterized in that all the said inertial elements (3) are designed to pivot about a common secondary axis (B).
12. Movement (100) according to one of Claims 1 to 11, characterized in that at least one said inertial element (3) is at least 5 times as long as it is wide, and at least 5 times as wide as it is thick.
13. Movement (100) according to one of Claims 1 to 12, characterized in that the said rotary resonator (10) comprises at least one flexible guide to provide the pivoting and elastic return of at least one said inertial element (3) with respect to the said central mobile component (1).
14. Movement (100) according to Claim 13, characterized in that the said flexible guide is a pivot with blades which are either intersecting coplanar, or intersecting in projection onto a plane of projection perpendicular to the said central axis (A) or with an offset centre of rotation.
15. Movement (100) according to Claim 13 or 14, characterized in that the said flexible guide is designed to impart to the said inertial element (3) a return torque that is proportional to the sine of twice the angle of pivoting of the said inertial element (3).
16. Movement (100) according to Claims 14 and 15, characterized in that the said flexible guide is designed to impart to the said inertial element (3) a return torque that is proportional to the sine of twice the angle of pivoting of the said inertial element (3), and characterized in that the said flexible guide comprises two asymmetric flexible blades (31; 32) each joining a first in-built restraint (41; 42) of the said central mobile component (1) to a second in-built restraint (51; 52) of the said inertial element (3), the said first in-built restraints (41; 42) defining with the said second respective in-built restraints (51; 52), two main blade directions (DL1; DL2), the said central mobile component (1) and the said inertial element (3) each being more rigid than each of the said flexible blades (31; 32), and the said two main blade directions (DL1; DL2) defining a theoretical axis of pivoting (D) where they intersect when the said two flexible blades (31; 32) are coplanar, or where their projections onto the said plane of projection intersect when the said two flexible blades (31; 32) extend on two levels parallel to the said plane of projection but are not coplanar, and with a vertex angle (α) equal to 112.5°, in that the second (32) of the said blades has, between its opposite in-built restraints, a second total length (L2) that is triple the first total length (L1) of the first (31) of the said blades, and in that the distances between the said first in-built restraints (41; 42) and the said theoretical axis of pivoting (D) are, for the said second (32) of the said blades a second axial distance (D2) equal to 0.875 times the said second total length (L2) and, for the said first (31) of the said blades a first axial distance (D1) equal to 0.175 times the said first total length (L1).
17. Movement (100) according to Claim 13 or 14, characterized in that the said flexible guide is produced by a remote centre compliance bladed pivot constituting a virtual pivot, in which the insetting of the blades (31; 32) into housings (51; 52) that the said central mobile component (1) or the said inertial element (3) comprises results from an angular preload of 0.15 radian, in that the vertex angle formed by the directions of insetting of the said blades (31; 32) at the said virtual pivot is 52.642°, and in that the distance between the said virtual pivot and the closest in-built restraint is equal to 0.268864 times the length of each of the said blades (31; 32) between their in-built restraints in the unloaded state prior to the preloading of their end.
18. Movement (100) according to one of Claims 13 to 17, characterized in that the said flexible guide is thermally compensated and comprises blades made of oxidized silicon.
19. Movement (100) according to one of Claims 1 to 18, characterized in that the said rotary resonator (10) comprises, articulated to some of the said inertial elements (3), additional dynamic linkage elements (5) which, with the said inertial elements (3), constitute a structure of the pantograph type and which are designed to increase the radial deployment of the said rotary resonator (10) by limiting its height along the said central axis (A).
20. Movement (100) according to one of Claims 1 to 19, characterized in that the said movement (100) comprises at least one main display axis (P) for displaying using hands or discs, and in that the said central axis (A) is parallel to the said main axis (P).
21. Movement (100) according to one of Claims 1 to 20, characterized in that the said movement (100) comprises at least one main display axis (P) for displaying using hands or discs, and in that the said central axis (A) is perpendicular to the said main axis (P).
22. Movement (100) according to one of Claims 1 to 21, characterized in that the said output mobile component of the said gear train (300) is a worm.
23. Movement (100) according to one of Claims 1 to 22, characterized in that the said rotary resonator (10) comprises just two or three said inertial elements (3).
24. Movement (100) according to one of Claims 1 to 23, characterized in that the pivoting of the said central mobile component (1) takes place on at least one magnetic pivot.
25. Mechanical watch (1000) comprising at least one movement (100) according to one of Claims 1 to 24.

Images