EP3327515B1 - Flexibly guided rotary resonator maintained by a free escapement with pallet - Google Patents

Description

Field of the invention

The invention relates to a clockwork regulating mechanism, comprising, arranged on a plate, a resonator mechanism of a quality factor Q, and an escapement mechanism which is subjected to a couple of driving means which comprises a movement, said resonator mechanism comprising an inertial element arranged to oscillate relative to said plate, said inertial element being subjected to the action of elastic return means fixed directly or indirectly to said plate, and said inertial element being arranged to cooperate with a mobile of exhaust that includes said exhaust mechanism.

The invention also relates to a timepiece movement comprising motor means, and such a regulating mechanism, the escapement mechanism of which is subjected to the torque of these motor means.

The invention also relates to a watch, more particularly a mechanical watch, comprising such a movement, and / or such a regulating mechanism.

The invention relates to the field of clockwork regulation mechanisms, in particular for watches.

Invention background

Most mechanical watches have a balance-spring type oscillator, cooperating with a Swiss lever escapement. The balance-spring constitutes the time base of the watch. It is called here resonator. As for the exhaust, it fulfills two main functions, namely to maintain the comings and goings of the resonator, and to count these comings and goings. This escapement must be robust, not disturb the pendulum far from its point of equilibrium, resist shock, avoid jamming the movement (for example during a reversal), and therefore constitutes a nerve component of the watch movement.

Typically, a balance spring oscillates with an amplitude of 300 °, and the lifting angle is 50 °. The lifting angle is the angle of the pendulum on which the fork of the anchor interacts with the pin, also called ellipse, of the pendulum. In most current Swiss anchor escapements, the lift angle is distributed on either side of the balance point of the pendulum (+/- 25 °), and the anchor tips +/- 7 °.

The Swiss anchor escapement belongs to the category of free escapements because, beyond the half-lift angle, the resonator no longer touches the anchor. This characteristic is essential for obtaining good chronometric properties.

A mechanical resonator comprises an inertial element, a guide and an elastic return element. Traditionally, the balance constitutes the inertial element, and the hairspring constitutes the elastic return element. The pendulum is guided in rotation by pivots, which rotate in smooth ruby bearings. The associated friction is at the origin of energy losses and walking disturbances. We seek to eliminate these disturbances, which, moreover, depend on the orientation of the watch in the gravity field. The losses are characterized by the quality factor Q of the resonator. We generally seek to maximize this quality factor Q, in particular in order to obtain the best possible power reserve. It is understood that the guidance constitutes an essential factor of losses.

The use of a flexible rotary guide, instead of pivots and the traditional hairspring, is a solution which makes it possible to maximize the quality factor Q. Flexible blade resonators, provided that they are well designed, have promising chronometric properties, independently of the orientation in gravity, and have high quality factors, in particular thanks to the absence of pivoting friction. In addition, the use of flexible guides eliminates the problems of wear of the pivots.

However, the flexible blades generally used in such flexible rotary guides are more rigid than spirals. This leads to working at a higher frequency, for example of the order of 20 Hz, and at a lower amplitude, for example from 10 ° to 20 °. At first glance, this hardly seems compatible with a Swiss anchor type escapement.

A range of operation compatible with a resonator with flexible rotary guide, in particular with blades, is typically from 6 ° to 15 °. This results in a certain lift angle value, which must be twice the minimum operating amplitude.

The document EP3032352A1 in the name of LVMH describes a clock regulator comprising two inertial regulating members, each mounted on a support by an elastic suspension in order to be able to oscillate in translation. The two members are linked by a lever so as to form a rotary resonator with virtual pivot. The regulator has a dowel pin and an anchor.

The document EP2990885A1 in the name of ETA SA describes a mechanical watch movement comprising a resonator, an escapement associated with this resonator and a time information display, this display being driven by a mechanical motor device via a gear train whose operation is clocked by the exhaust , at least the resonator being housed in an enclosure in which a reduced pressure prevails relative to atmospheric pressure. The exhaust is a magnetic exhaust comprising an escape wheel coupled directly or indirectly to the resonator via a non-contact magnetic coupling system, this magnetic coupling system being formed so that a non-magnetic wall of the enclosure passes through the magnetic exhaust so that a first part of this exhaust is located inside the enclosure, while a second part of this exhaust is located outside this enclosure.

The document EP2894520A2 in the name of NIVAROX SA describes an oscillating mechanism for a clock movement, comprising a first rigid element (200) and a second rigid element, each designed to be fixed to an element different from said movement, one of which is capable of move relative to each other and pivots around an axis. The oscillating mechanism is a flexible monobloc mechanism with variable geometry, and comprises a first elastic return means ensuring an elastic connection between the first rigid element and an intermediate rigid element, and comprises at least a second elastic return means providing an elastic connection between this intermediate rigid element and this second rigid element. The first rigid element, the first elastic return means, the intermediate rigid element, the second elastic return means and the second rigid element are coplanar on a plane and designed to deform on this plane.

In the absence of special precautions, an exhaust with a low angle of lift can have a poor performance, and cause too great a delay. However, the combination of a high frequency and a low amplitude allows speeds of passage of the balance which are acceptable, without being too high, and therefore the efficiency of the exhaust is not automatically poor.

The resonator must have an acceptable size, compatible with its housing in a watch movement, it is not possible to date to realize a flexible rotary guide of very large diameter, or several pairs of blade levels, which would theoretically allow, by the series of successive flexible guides, to obtain an oscillation amplitude of the inertial element of several tens of degrees: it is therefore advisable to use a flexible guide with one or two levels of blades at most, for example as known from the document EP3035126 on behalf of THE SWATCH GROUP RESEARCH & DEVELOPMENT Ltd.

In short, the effect of choosing a flexible rotary guide is that the amplitude of the balance is reduced, and that it is no longer possible to use a traditional Swiss lever escapement, which requires an amplitude of the balance clearly greater than half lifting angle, that is to say greater than 25 °. A regulator comprising a resonator with flexible guidance therefore requires a specific exhaust mechanism, with a dimensioning different from what a conventional Swiss anchor escapement would be designed to operate with the same inertial element of the resonator.

Summary of the invention

The present invention has the overall objective of increasing the power reserve and accuracy of current mechanical watches. To achieve this objective, the invention combines a resonator with flexible rotary guide with an anchor escapement optimized to maintain acceptable dynamic losses and limit the chronometric effect of the release.

In the absence of teaching in the prior art for the dimensioning, both of the resonator and of the escape mechanism, calculations of an analytical model and a campaign of simulations made it possible to highlight parameters of the resonator and of the escape , which are compatible with acceptable yield and delay.

These calculations and simulations demonstrate that the relationship between the inertia of the inertial element, in particular a pendulum, and the inertia of the anchor is decisive.

To this end, the invention relates to a regulating mechanism according to claim 1.

Such resonators with flexible rotary guidance have very high quality factors, for example of the order of 3000, to be compared with a quality factor of 200 for a conventional watch. However, the dynamic losses (kinetic energy of the escapement mobile and of the anchor at the end of the pulse) are independent of the quality. These losses can therefore become too large, with a high quality factor, in relative level with respect to the energy transmitted to the balance.

For correct operation of the mechanism, a plate pin secured to the inertial element must penetrate a certain value, called penetration, into the opening of the anchor fork. Similarly, to ensure safety during release, this platform pin must then be able, after releasing the pin, to be kept at a certain distance, called safety, from the horn of the fork opposite to that on which it was in contact immediately before release.

Also, the invention also sets out to impose a particular relationship, according to claim 4, between the dimensions of the anchor fork, the penetration and safety values, and the values of the angles of lifting of the anchor and of the inertial element, to ensure that the dowel retracts correctly from the fork, once the lifting half-angle has been traversed.

The invention also relates to a timepiece movement comprising motor means, and such a regulating mechanism, the escapement mechanism of which is subjected to the torque of these motor means.

The invention also relates to a watch, more particularly a mechanical watch, comprising such a movement, and / or such a regulating mechanism.

Brief description of the drawings

• la figure 1 comporte un double graphique comportant sur la même abscisse le rapport entre l'inertie de l'élément inertiel du résonateur et l'inertie de l'ancre, et qui, en ordonnée montre, pour un exemple particulier de mécanisme, d'une part au niveau du graphique supérieur en partie positive l'allure du rendement du régulateur en %, et au niveau du graphique inférieur en partie négative l'allure du retard en secondes par jour; ces graphiques supérieur et inférieur sont établis pour une même géométrie d'échappement donnée, avec des valeurs particulières de facteur de qualité, d'angle de levée d'ancre, et d'amplitude de fonctionnement;
• la figure 2 représente, de façon schématisée, partielle, et en perspective, un mouvement d'horlogerie, avec une platine porteuse d'un mécanisme régulateur selon l'invention, comportant un résonateur à guidage flexible avec deux lames flexibles disposées sur deux niveaux parallèles et croisées en projection, fixées à la platine par l'intermédiaire d'un élément élastique, ce résonateur comportant un élément inertiel de grande étendue, en forme de lettre omega, et dont la partie centrale, portée par les deux lames flexibles, porte une cheville agencée pour coopérer avec une ancre symétrique, dont le pivotage par un arbre métallique sur la platine n'est pas représenté, qui coopère elle-même avec une roue d'échappement classique;

• la figure 3 représente, en vue en plan, le seul mécanisme régulateur de la figure 2, agencé sur la platine du mouvement;
• la figure 4 représente, en vue en plan, le détail du mécanisme régulateur de la figure 2 ;
• la figure 5 représente, en perspective partiellement éclatée, le mécanisme régulateur de la figure 2 ;
• la figure 6 représente, en vue en plan, un détail de la zone de coopération entre la cheville de plateau de l'élément inertiel du résonateur, et la fourchette de l'ancre, représentée dans une position de butée sur une goupille de limitation;
• la figure 7 représente, en vue en plan, l'ancre du mécanisme de la figure 2, en forme de cornes de bovin watusi ;
• la figure 8 représente, en vue en plan, le guidage flexible du mécanisme de la figure 2 ;
• la figure 9 représente, en vue en plan, une exécution particulière d'un niveau du guidage flexible du mécanisme de la figure 2 ;
• la figure 10 représente, en vue de côté, le mécanisme régulateur de la figure 2;
• la figure 11 représente, en perspective, un détail du mécanisme régulateur de la figure 2, concernant des butées anti-choc au niveau de sa platine;
• les figures 12 à 14 sont des graphiques comportant en abscisse le couple appliqué au mobile d'échappement, et en ordonnée, respectivement l'amplitude mesurée en degrés sur la figure 12, le retard en secondes par jour sur la figure 13, et le rendement du régulateur en % sur la figure 14 ;
• la figure 15 est un schéma-blocs qui représente une montre comportant un mouvement avec des moyens moteurs et un mécanisme régulateur selon l'invention.

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 comprises a double graph comprising on the same abscissa the relationship between the inertia of the inertial element of the resonator and the inertia of the anchor, and which, on the ordinate shows, for a particular example of mechanism, on the one hand at level of the upper graph in part positive the shape of the regulator output in%, and in the level of the lower graph partly negative the shape of the delay in seconds per day; these upper and lower graphics are established for the same given escape geometry, with particular values of quality factor, angle of lifting of anchor, and amplitude of operation;
• the figure 2 shows schematically, partially, and in perspective, a clockwork movement, with a plate carrying a regulating mechanism according to the invention, comprising a resonator with flexible guidance with two flexible blades arranged on two parallel and crossed levels in projection, attached to the plate by means of an elastic element, this resonator comprising an inertial element of large extent, in the shape of an omega letter, and the central part of which, carried by the two flexible blades, carries a pin arranged to cooperate with a symmetrical anchor , whose pivoting by a metal shaft on the plate is not shown, which itself cooperates with a conventional escape wheel;

• the figure 3 represents, in plan view, the only mechanism regulating the figure 2 , arranged on the movement plate;
• the figure 4 represents, in plan view, the detail of the regulating mechanism of the figure 2 ;
• the figure 5 represents, in partially exploded perspective, the regulating mechanism of the figure 2 ;
• the figure 6 represents, in plan view, a detail of the cooperation zone between the plate pin of the inertial element of the resonator, and the fork of the anchor, represented in a position of abutment on a limiting pin;
• the figure 7 represents, in plan view, the anchor of the mechanism of the figure 2 , in the shape of watusi bovine horns;
• the figure 8 represents, in plan view, the flexible guidance of the mechanism of the figure 2 ;
• the figure 9 represents, in plan view, a particular execution of a level of the flexible guide of the mechanism of the figure 2 ;
• the figure 10 represents, in side view, the regulating mechanism of the figure 2 ;
• the figure 11 represents, in perspective, a detail of the regulatory mechanism of the figure 2 , concerning anti-shock stops at its plate;
• the figures 12 to 14 are graphs comprising on the abscissa the torque applied to the exhaust mobile, and on the ordinate, respectively the amplitude measured in degrees on the figure 12 , the delay in seconds per day on the figure 13 , and the efficiency of the regulator in% over the figure 14 ;
• the figure 15 is a block diagram which represents a watch comprising a movement with motor means and a regulating mechanism according to the invention.

Detailed description of preferred embodiments

The invention combines a resonator with flexible rotary guide, in order to increase the power reserve and the precision, with an anchor escapement optimized to maintain acceptable dynamic losses and limit the chronometric effect of the release.

The invention thus relates to a clockwork regulating mechanism 300, comprising, arranged on a plate 1, a resonator mechanism 100 of quality factor Q, and an exhaust mechanism 200, which is subjected to a couple of motor means 400 that has a movement 500.

This resonator mechanism 100 includes an inertial element 2 which is arranged to oscillate relative to the plate 1. This inertial element 2 is subjected to the action of elastic return means 3 fixed directly or indirectly to the plate 1. The inertial element 2 is arranged to cooperate indirectly with an exhaust mobile 4, in particular an escape wheel, which includes the exhaust mechanism 200, and which pivots around an exhaust axis DE.

According to the invention, the resonator mechanism 100 is a rotary resonator with virtual pivot, around a main axis DP, with flexible guide comprising at least two flexible blades 5, and comprises a plate pin 6 secured to the inertial element 2 The exhaust mechanism 200 comprises an anchor 7, which pivots around a secondary axis DS and comprises an anchor fork 8 arranged to cooperate with the plate pin 6, and is thus a free exhaust mechanism: in its operating cycle, the resonator mechanism 100 has at least one freedom phase where the plateau pin 6 is at a distance from the anchor fork 8. The resonator lifting angle β, during which the plateau pin 6 is in contact with the anchor fork 8, is less than 10 °.

Given a particular exhaust geometry, and a particular operating amplitude, in particular 8 °, dynamic multi-body simulations (that is to say relating to a set of several components each of which is assigned a mass and a particular inertia distribution) make it possible to evaluate the efficiency and the delay of this escape mechanism as a function of the inertia ratio between the inertia of the inertial element and the inertia of the anchor, what usual kinematic simulations do not allow establishing. As seen on the figure 1 , we note that, under the conditions of simulations, there is a threshold of good performance, higher than 35%, and of weak delay, lower than 8 seconds per day, for inertia of the inertial element, in particular of a pendulum, which is 10,000 times greater than the inertia of the anchor.

The analytical model of the system has thus shown that, if we want to limit the dynamic losses, a particular condition links the inertia of the anchor, the inertia of the inertial element, the quality factor of the resonator, and the angles of lifting of the anchor and the inertial element: for a coefficient ε of dynamic losses, the inertia I _B of the inertial element 2 with respect to the main axis DP on the one hand, and the inertia I _A of the anchor 7 relative to the secondary axis DS on the other hand, are such that the ratio I _B / I _A is greater than 2Q.α ² /(ε.π.β ² ), where α is the angle of lifting of the anchor which corresponds to the maximum angular stroke of the anchor fork 8.

According to the invention, to limit the dynamic losses to a factor ε = 10%, the inertia I _B of the inertial element 2 with respect to the main axis DP on the one hand, and the inertia I _A of l anchor 7 relative to the secondary axis DS on the other hand, are such that the ratio I _B / I _A is greater than 2Q.α ² /(0.1.π.β ² ), where α is the angle of lifting of the anchor which corresponds to the maximum angular travel of the anchor fork 8.

More particularly, the resonator lift angle β, which is an overall angle, taken on either side of the rest position, is less than twice the amplitude angle from which deviates the maximum inertial element 2 with respect to a rest position, in one direction of its movement.

More particularly, the amplitude angle, from which the inertial element 2 deviates as far as possible relative to a rest position, is between 5 ° and 40 °.

More particularly, during each alternation, in a contact phase the plate pin 6 penetrates into the anchor fork 8 with a penetration stroke P greater than 100 micrometers, and in a release phase the plate pin 6 remains at distance from the anchor fork 8 with a safety distance S greater than 25 micrometers.

And the plate pin 6 and the anchor fork 8 are dimensioned so that the width L of the anchor fork 8 is greater than (P + S) / sin (α / 2 + β / 2), the stroke of penetration P and the safety distance S being measured radially with respect to the main axis DP.

The useful width L1 of the plate pin 6, visible on the figure 6 , is slightly less than the width L of the anchor fork 8, and more particularly less than or equal to 98% of L. This plate pin 6 is advantageously in clearance behind its surface of useful width L1, the pin may in particular have a prismatic shape of triangular section as suggested in the figure, or the like.

Thus, the invention defines, by construction, a new dowel-fork layout, which has a very particular characteristic, according to which the horns of the fork are more apart, and the dowel is wider, than for a Swiss anchor mechanism of known type with a usual lifting angle of 50 °.

Thus, by significantly widening the range of the anchor compared to the usual proportions, it is also possible to size a Swiss anchor escapement with a very small lifting angle, for example of the order of 10 °.

More particularly, the anchor 7 is made of a single level of silicon, attached to a metallic axis pivoted relative to the plate 1.

More particularly, the exhaust mobile 4 is a silicon escape wheel.

More particularly, the exhaust mobile 4 is an escape wheel which is perforated to minimize its inertia with respect to its pivot axis DE.

More particularly, the anchor 7 is perforated to minimize its inertia I _A with respect to the secondary axis DS.

Preferably, the anchor 7 is symmetrical with respect to the secondary axis DS, so as to avoid any imbalance, and to avoid parasitic torques during linear shocks. The figure 7 shows the two horns 81 and 82 arranged to cooperate with the plate pin 6, the pallets 72 and 73 arranged to cooperate with teeth of the exhaust mobile 4, and false horns 80 and false pallets 70 whose only role is perfect balancing,

More particularly, the largest dimension of the inertial element 2 is greater than half of the largest dimension of the plate 1.

More particularly, the main axis DP, the secondary axis DS and the pivot axis of the exhaust mobile 4, are arranged according to a pointing at a right angle whose apex is the secondary axis DS.

More particularly, the flexible guide comprises two flexible blades 5 crossed in projection on a plane perpendicular to the main axis DP, at the virtual pivot defining the main axis DP, and located in two parallel and distinct levels. More particularly still, the two flexible blades 5, projected onto a plane perpendicular to the main axis DP, form an angle between them between 59.5 ° and 69.5 °, and intersect between 10.75% and 14.75% of their length, so as to give the resonator mechanism 100 a deliberate isochronism defect opposed to the defect in delay in the exhaust of the exhaust mechanism 200 .

The resonator thus presents an anisochronism curve which compensates for the delay caused by the exhaust. In other words, the free resonator is designed with an isochronism defect opposite to the defect caused by the anchor escapement. We therefore compensate for the delay in exhaust by the design of the resonator.

More particularly, the two flexible blades 5 are identical and are positioned in symmetry. More particularly still, each flexible blade 5 belongs to a monobloc assembly 50, in one piece with its first alignment means 52A, 52B, and of attachment 54 on the plate 1, or, advantageously and as visible on the figure 10 , fixing on an intermediate elastic suspension blade 9 fixed to the plate 1 and which is arranged to allow movement of the flexible guide and the inertial element 2 in the direction of the main axis DP.

In the nonlimiting variant illustrated by the figures, the first alignment means are a first vee 52A and a first flat 52B, and the first fixing means comprise at least a first bore 54. A first veneer blade 53 ensures the support on the first fixing means. Similarly, the monobloc assembly 50 comprises, for its attachment to the inertial element 2, second alignment means which are a second vee 56A and a second plate 56B, and the second attachment means comprise at least a second bore 58. A second plating blade 57 provides support for the second fixing means.

The flexible guide 3 with crossed blades 5 advantageously consists of two monobloc assemblies 50 identical silicon parts, assembled in symmetry to form the crossing of the blades, and precisely aligned with respect to each other thanks to the integrated alignment means. and auxiliary means such as pins and screws, not shown in the figures.

Thus, more particularly, at least the resonator mechanism 100 is fixed to an elastic intermediate suspension blade 9 fixed to the plate 1 and arranged to allow movement of the resonator mechanism 100 in the direction of the axis. main DP, and the plate 1 comprises at least one shockproof stop 11, 12, at least in the direction of the main axis DP, and preferably at least two such shockproof stops 11,12, which are arranged to cooperate with elements rigid of the inertial element 2, for example flanges 21 and 22 added during assembly of the inertial element with the flexible guide 3 comprising the blades 5.

The elastic suspension blade 9, or a similar device, allows displacements of the entire resonator 100 substantially in the direction defined by the virtual axis of rotation DP of the guide. The purpose of this device is to prevent the blades 5 from breaking in the event of a transverse impact in the direction DP.

FIG. 21 illustrates the presence of shock-absorbing stops limiting the travel of the inertial element 2 in three directions in the event of an impact, but located at a sufficient distance so that the inertial element does not touch the stops under the effect of the gravity. For example, the flange 21 or 22 comprises a bore 211 and a face 212, capable of cooperating respectively in support of an impact-resistant stop with a pin 121 and a complementary surface 122 at the level of the stop 21 or 22.

More particularly, the inertial element 2 comprises weights 20 for adjusting the gait and the unbalance.

More particularly, the plate pin 6 is in one piece with a flexible blade 5, or more particularly, such a one-piece assembly 50 as illustrated in the figures.

More particularly, the anchor 7 comprises bearing surfaces arranged to cooperate in support with teeth which comprises the exhaust mobile 4 and to limit the angular travel of the anchor 7. These supports make it possible to limit the angular travel of anchor, as would the starlets. The angular travel of the anchor 78 can moreover be conventionally limited by limitation pins 700.

More particularly, the flexible guide 3 is made of oxidized silicon to compensate for the effects of temperature on the operation of the regulating mechanism 300.

The invention also relates to a timepiece movement 500 comprising motor means 400, and such a regulating mechanism 300, the escapement mechanism 200 of which is subjected to the torque of these motor means 400.

The graphics of figures 12 to 14 present a series of simulation results in which Q = 2000, I _B = 26550 mg.mm ² , frequency of 20Hz, mobile exhaust with 20 teeth, more particularly the lifting angle α of the anchor is 14 °, and the resonator lifting angle β is 10 °.

The invention also relates to a watch 1000, more particularly a mechanical watch, comprising such a movement 500, and / or such a regulating mechanism 300.

In summary, the present invention makes it possible to increase the power reserve and / or the precision of current mechanical watches. For a given movement size, you can quadruple the autonomy of the watch and double the regulating power of the watch. This amounts to saying that the invention allows a gain of a factor of 8 on the performance of the movement.

Claims (22)

1. Horological regulator mechanism (300), comprising, arranged on a plate (1), a resonator mechanism (100) with a quality factor Q, and an escapement mechanism (200) which is subject to a torque (400) of a driving means comprised by a movement (500), said resonator mechanism (100) comprising an inertial element (2) arranged to oscillate with respect to said plate (1), said inertial element (2) being subject to the action of resilient return means (3) directly or indirectly attached to said plate (1), and said inertial element (2) being arranged to cooperate indirectly with an escapement wheel (4) comprised by said escapement mechanism (200), wherein said resonator mechanism (100) is a rotary resonator with virtual pivot, about a main axis (DP), with flexible guide comprising at least two flexible blades (5), and comprising an impulse pin (6) integral with said inertial element (2), wherein said escapement mechanism (200) comprises a pallet (7) pivoting about a secondary axis (DS) and comprising a pallet fork (8) arranged to cooperate with said impulse pin (6), characterised in that said escapement mechanism is a free escapement mechanism in the operating cycle of which said resonator mechanism (100) has at least one phase of freedom where said impulse pin (6) is at a distance from said pallet fork (8), and in that the overall resonator lift angle (β), during which said impulse pin (6) is in contact with said pallet fork (8), is less than 10°, and where the inertia I_B of said inertial element (2) with respect to said main axis (DP) on the one hand, and the inertia I_A of said pallet (7) with respect to said secondary axis (DS) on the other hand, are such that the ratio I_B/I_A is greater than 2Q · α²/(π · β²/10), where α is the overall lift angle of the pallet which corresponds to the maximum angular travel of said pallet fork (8).
2. Regulator mechanism (300) according to claim 1, characterised in that said overall resonator lift angle (β) is less than twice the maximum amplitude angle by which said inertial element (2) deviates from a rest position, in only one direction of its movement.
3. Regulatory mechanism (300) according to claim 1 or 2, characterised in that the maximum amplitude angle, by which said inertial element (2) deviates from a rest position, is comprised between 5° and 40°.
4. Regulator mechanism (300) according to one of claims 1 to 3, characterised in that, during each alternation, in a contact phase said impulse pin (6) penetrates into said pallet fork (8) with a penetration travel (P) greater than 100 micrometres, and in a disengagement phase said impulse pin (6) remains at a distance from said pallet fork (8) with a safety distance (S) greater than 25 micrometres, and in that said impulse pin (6) and said pallet fork (8) are dimensioned so that the width (L) of said pallet fork (8) is greater than (P + S)/sin(α/2 + β/2), said penetration travel (P) and said safety distance (S) being measured radially with respect to said main axis (DP).
5. Regulator mechanism (300) according to one of claims 1 to 4, characterised in that said pallet (7) consists of a single layer of silicon, connected to a metal axis pivoted with respect to said plate (1).
6. Regulator mechanism (300) according to one of claims 1 to 5, characterised in that said escapement wheel (4) is a silicon escapement wheel.
7. Regulator mechanism (300) according to one of claims 1 to 6, characterised in that said escapement wheel (4) is an escapement wheel which is perforated in order to minimise its inertia with respect to the pivot axis thereof.
8. Regulator mechanism (300) according to one of claims 1 to 7, characterised in that said pallet (7) is perforated in order to minimise said inertia (I_A) thereof with respect to said secondary axis (DS).
9. Regulator mechanism (300) according to one of claims 1 to 8, characterised in that said pallet (7) is symmetric with respect to said secondary axis (DS).
10. Regulator mechanism (300) according to one of claims 1 to 9, characterised in that the largest dimension of said inertial element (2) is greater than half the largest dimension of said plate (1).
11. Regulator mechanism (300) according to one of claims 1 to 10, characterised in that said main axis (DP), said secondary axis (DS) and the pivot axis (DE) of said escapement wheel (4), are arranged according to a centring at right angles, the apex of which is said secondary axis (DS).
12. Regulator mechanism (300) according to one of claims 1 to 11, characterised in that said flexible guide comprises two flexible blades (5) intersecting in projection onto a plane perpendicular to said main axis (DP), at said virtual pivot defining said main axis (DP), and located in two parallel and separate levels.
13. Regulator mechanism (300) according to claim 12, characterised in that said two flexible blades (5), in projection onto a plane perpendicular to said main axis (DP), form between them an angle comprised between 59.5° and 69.5°, and intersect at between 10.75% and 14.75% of their length, so as to provide said resonator mechanism (100) with a voluntary isochronism defect that opposes the escapement loss defect of said escapement mechanism (200).
14. Regulator mechanism (300) according to claim 12 or 13, characterised in that said two flexible blades (5) are identical and are positioned symmetrically.
15. Regulator mechanism (300) according to one of claims 12 to 14, characterised in that each said flexible blade (5) belongs to an integral one-piece assembly (50) with means for alignment and attachment on said plate (1) or on an intermediate resilient suspension blade (9) attached to said plate (1) and arranged to allow a movement of said flexible guide and said inertial element (2) along the direction of said main axis (DP).
16. Regulator mechanism (300) according to one of claims 1 to 15, characterised in that at least said resonator mechanism (100) is attached to an intermediate resilient suspension blade (9) attached to said plate (1) and arranged to allow a resonator mechanism movement (100) along the direction of said main axis (DP), and in that said plate (1) comprises at least one shock-resistant abutment (11, 12) at least along the direction of said main axis (DP), arranged to cooperate with the rigid elements of said inertial element (2).
17. Regulator mechanism (300) according to one of claims 1 to 16, characterised in that said inertial element (2) comprises inertia-blocks for regulating the rate and unbalance.
18. Regulator mechanism (300) according to one of claims 1 to 17, characterised in that said impulse pin (6) is integral with said flexible blade (5).
19. Regulator mechanism (300) according to one of claims 1 to 16, characterised in that said pallet (7) comprises support surfaces arranged to cooperate in contact with teeth comprised by set escapement wheel (4) and for limiting the angular travel of said pallet (7).
20. Regulator mechanism (300) according to one of claims 1 to 19, characterised in that said flexible guide is made of oxidised silicon in order to compensate the effects of temperature on the operation of said regulator mechanism (300).
21. Horological movement (500) comprising drive means (400) and a regulator mechanism (300) according to one of claims 1 to 20, the escapement mechanism (200) of which is subject to the torque of said driving means (400).
22. Timepiece (1000) comprising a movement (500) according to claim 21, and/or a regulator mechanism (300) according to one of claims 1 to 20.

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