CH714361A2 - Flexible guided rotary resonator serviced by a free anchor escapement. - Google Patents

Abstract

The invention relates to a watchmaking regulator (300) comprising a free anchor escapement mechanism (7) and a Q quality factor resonator (100) comprising at least one inertial element (2) comprising an integral pin (2). (6) cooperating with a fork of the anchor (7), this inertial element (2) being subjected to the action of elastic return means (3) fixed directly or indirectly to the plate (1) and being arranged to cooperate indirectly with an escape wheel (4) that the escape mechanism comprises, this resonator mechanism is a virtual pivot rotary resonator around a main axis (DP), with flexible guiding subject to the recall of at least two flexible blades (5) fixed to the plate (1), together defining a virtual pivot of main axis (DP), the anchor (7) pivoting about a secondary axis (DS), and the range is widened relative to to that of a classic Swiss anchor.

Description

Description

FIELD OF THE INVENTION [0001] The invention relates to a timepiece control mechanism, comprising, arranged on a plate, a resonator mechanism of a quality factor Q, and an escapement mechanism which is subjected to a pair of motor means that 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 an escape wheel that includes said exhaust mechanism.

The invention also relates to a watch movement comprising motor means, and such a regulating mechanism, the exhaust mechanism is subject to the torque of these motor means.

The invention further 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 clock regulation mechanisms, particularly for watches.

BACKGROUND OF THE INVENTION [0005] Most mechanical watches comprise a sprung-balance oscillator cooperating with a Swiss lever escapement. The sprung balance is the time base of the watch. It is called here resonator. The exhaust, meanwhile, performs two main functions, namely to maintain the comings and goings of the resonator, and count these back and forth. This exhaust must be robust, do not disturb the balance far from its equilibrium point, withstand shocks, avoid trapping the movement (for example during a reversal), and is therefore a key component of the watch movement.

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

The Swiss lever escapement is part of the category of free exhausts, because, beyond the half-angle of lift, the resonator does not touch the anchor. This characteristic is essential to obtain good chronometric properties.

[0008] A mechanical resonator comprises an inertial element, a guide and an elastic return element. Traditionally, the pendulum constitutes the inertial element, and the spiral constitutes the elastic return element. The balance is guided in rotation by pivots, which turn in smooth ruby bearings. The associated friction is at the origin of energy losses and disturbances. We try to eliminate these disturbances, which, moreover, depend on the orientation of the watch in the field of gravity. The losses are characterized by the quality factor Q of the resonator. It is generally sought to maximize this quality factor Q, so as to obtain the best possible power reserve. It is understood that guidance is an essential factor of losses.

The use of a flexible rotary guide, instead of the pivots and the traditional spiral, is a solution that maximizes the quality factor Q. The flexible blade resonators, as far as they are good designed, have promising chronometric properties, regardless of the orientation in gravity, and have high quality factors, especially thanks to the absence of pivoting friction. In addition, the use of flexible guides makes it possible to eliminate the problems of wear of the pivots.

However, the flexible blades generally used in such flexible rotating guides are stiffer 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 seems unlikely to be compatible with a Swiss anchor type escapement.

An operating amplitude compatible with a rotary flexible guide resonator, including blades, is typically 6 ° to 15 °. This results in a certain lift angle value, which must be twice the minimum operating amplitude.

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

The resonator must have an acceptable size, compatible with its housing in a watch movement, it is not possible today to achieve a flexible rotary guide of very large diameter, or multiple pairs of levels of blades , which would allow in theory, by the series setting of successive flexible guides, to obtain an amplitude of oscillation of the inertial element of several tens of degrees: it is therefore advisable to use a flexible guidance at one or two levels of blades at most, for example as known from EP 3 035 126 in the name of THE SWATCH GROUP RESEARCH & DEVELOPMENT Ltd.

In sum, the effect of the choice of a flexible rotary guide is that the amplitude of the balance is reduced, and that we can no longer use a traditional Swiss lever escapement, which requires a pendulum amplitude clearly greater than the half-angle of lift, that is to say greater than 25 °. A regulator comprising a flexible guide resonator therefore requires a particular exhaust mechanism, with a different dimensioning than would be a usual Swiss lever escapement designed to operate with the same inertial element of the resonator. SUMMARY OF THE INVENTION [0015] The overall object of the present invention is to increase the power reserve and the accuracy of current mechanical watches. To achieve this objective, the invention combines a rotatable flexible guide resonator with an optimized anchor escapement to maintain acceptable dynamic losses and limit the time effect of the release. Without teaching in the prior art for the design of both the resonator and the exhaust mechanism, calculations of an analytical model and a simulation campaign have made it possible to highlight parameters of the resonator and exhaust, which are compatible with acceptable performance and retardation.

These calculations and these simulations demonstrate that the ratio between the inertia of the inertial element, including a pendulum, and the inertia of the anchor is decisive.

For this purpose, the invention relates to a regulating mechanism according to claim 1.

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

For proper operation of the mechanism, a plate pin integral with the inertial element, must penetrate a certain value, called penetration, into the opening of the anchor fork. Similarly, to ensure the safety clearance, this plateau pin must then be able, after release of the ankle, to be kept at a certain distance, called safety, the horn of the fork opposite to that on which it was in contact immediately before its release.

Also, the invention is still attached to imposing a particular relationship between the dimensions of the anchor fork, the values of penetration and safety, and the values of the angles of lift of the anchor and the Inertial element, to ensure that the ankle retracts correctly from the fork, once the half-angle of lift traveled.

The invention also relates to a watch movement comprising motor means, and such a regulating mechanism, the exhaust mechanism is subject to the torque of these motor means.

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

BRIEF DESCRIPTION OF THE DRAWINGS [0024] Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, in which: FIG. 1 comprises a double graph comprising on the same abscissa the ratio 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 a mechanism, on the one hand at the level of the upper graph at the positive part the rate of the efficiency of the regulator in%, and at the level of the lower graph at the negative part the pace of the delay in seconds per day; these upper and lower graphs are established for the same given escape geometry, with particular values of quality factor, anchor lift angle, and operating amplitude; fig. 2 represents, schematically, partially, and in perspective, a clockwork movement, with a platinum bearing a regulating mechanism according to the invention, comprising a flexible guide resonator with two flexible blades arranged on two parallel and crossed levels in projection, fixed to the plate by means of an elastic element, this resonator comprising a large inertial element, in the form of an omega letter, and whose central part, carried by the two flexible blades, carries an arranged pin to cooperate with a symmetrical anchor, whose pivo-tage by a metal shaft on the plate is not shown, which cooperates itself with a conventional escapement wheel; fig. 3 shows, in plan view, the only regulating mechanism of FIG. 2, arranged on the platen of the movement; fig. 4 shows, in plan view, the detail of the regulating mechanism of FIG. 2; fig. 5 shows, in partially exploded perspective, the regulating mechanism of FIG. 2; fig. 6 shows, in plan view, a detail of the zone of cooperation between the plate pin of the inertial element of the resonator, and the fork of the anchor, shown in an abutment position on a limiting pin; fig. 7 shows, in plan view, the anchor of the mechanism of FIG. 2, shaped horns of watusi cattle; fig. 8 shows, in plan view, the flexible guide of the mechanism of FIG. 2; fig. 9 is a plan view of a particular embodiment of a level of the flexible guidance of the mechanism of FIG. 2; fig. 10 shows, in side view, the regulating mechanism of FIG. 2; fig. 11 shows, in perspective, a detail of the regulating mechanism of FIG. 2, concerning anti-shock abutments at its platen; figs. 12 to 14 are graphs comprising on the abscissa the torque applied to the escape wheel, and in ordinate, respectively the amplitude measured in degrees in FIG. 12, the delay in seconds per day in FIG. 13, and the regulator efficiency in% in FIG. 14; fig. 15 is a block diagram showing a watch comprising a movement with motor means and a regulating mechanism according to the invention; figs. 16 to 19 show, in plan view, steps of the kinematics, already symbolized by FIG. 6, at the balance peg, the fork of the anchor of FIG. 7, and the escape wheel here constituted by a traditional escape wheel: FIG. 16: rest of the escape wheel on the entry pallet, free arc of the resonator; Fig. 17: release; Fig. 18: beginning of the impulse; Fig. 19: rest of the escape wheel on the output pallet, free arc of the resonator, and safety; figs. 20 to 24 show, in plan view, kinematic steps in a low angle of lift escape mechanism, comprising an escape wheel constituted by a coaxial wheel escape wheel having, on different levels, direct impulse teeth with the balance, rest teeth arranged to cooperate with rest pallets of an anchor, and indirect impulse teeth arranged to cooperate with a pulse pallet of the same anchor, which comprises still two anchor horns defining an enlarged fork according to the invention arranged to cooperate with the rocker pin dimensioned according to the invention, which rocker comprises a radial arm carrying a pulse pallet arranged to cooperate with the teeth of direct impulse of the escapement mobile: fig. 20: exit release clearance: rest of a resting tooth of the escape wheel on the anchor exit pallet, free arc of the resonator counter-clockwise until it comes to a stop. ankle on a first anchor horn, rotation of the anchor clockwise; Fig. 21: indirect impulse: rotation of the escapement wheel released counter-clockwise, abutment of an indirect impulse tooth of the escape wheel on the impulse pallet of the anchor which rotates clockwise until the cooperation of the second anchor horn with the ankle, thereby transmitting indirectly the impulse of the escapement mobile to the balance, through the anchor; Fig. 22: lift raised entry: arrival at abutment of a rest tooth of the escape wheel on the anchor entry pallet, then end of the free arc of the beam in the counterclockwise direction; Fig. 23: release lifting input: reversal of the direction of rotation of the beam that starts in ho day, the ankle bears on the second horn of the anchor and drives it counterclockwise, until the clearance between the pallet of rest of the anchor inlet and the rest tooth of the escape wheel, thus allowing the rotation of the escape wheel; Fig. 24: Indirect impulse: stop of a direct impulse tooth of the escape wheel on the impulse diaphragm of the balance, allowing direct drive of the balance by the mobile escape.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [0025] The invention combines a rotatable flexible guide resonator, in order to increase power reserve and accuracy, with an optimized anchor escapement to maintain acceptable dynamic losses and limit the effect. time of release.

The invention thus relates to a 300 clock control mechanism, comprising, arranged on a plate 1, a resonator mechanism 100 Q quality factor, rotatable about a main axis DP, and an exhaust mechanism 200 which is subjected to a pair of motor means 400 that includes a movement 500.

This resonator mechanism 100 comprising at least one inertia element! 2 which is arranged to oscillate relative to the plate 1, about a main axis DP. This inertial element 2 is subjected to the action of resilient return means 3 fixed directly or indirectly to the plate 1. The inertial element 2 is arranged to cooperate indirectly with an escape wheel 4, in particular an escape wheel, that includes the exhaust mechanism 200, and which pivots about an exhaust axis DE.

According to the invention, these elastic return means 3 comprise at least two flexible blades 5 which is suspended from this at least one inertial element 2, including a rocker or the like, and which define a flexible guide with virtual pivot of this minus an inertial element 2. This at least one inertial element 2 integrally carries an anchor 6. And the escapement mechanism 200 comprises an anchor 7 arranged to pivot about a secondary axis DS, and comprising an anchor fork 8 which is arranged to cooperate with the pin 6. This escapement mechanism 200 is a free escape mechanism, in the operating cycle of which the resonator mechanism 100 has at least one phase of freedom where the pin 6 is at a distance from the fork anchor 8.

According to the invention, during each alternation, in a contact phase the pin 6 enters the anchor fork 8 with a penetration distance P greater than or equal to 40 micrometers and less than or equal to 200 micrometers, and in a disengagement phase the peg 6 remains at a distance from the anchor fork 8 with a safety distance S greater than or equal to 10 micrometers and less than or equal to 60 micrometers. The anchor 6 and the anchor fork 8 are dimensioned so that the width L of the anchor fork 8 is greater than (P + S) / sin (a / 2 + β / 2), the penetration stroke P and the safety distance S being measured radially with respect to the main axis DP, where a is the angle of lift of the anchor corresponding to the maximum angular travel of the anchor fork 8, and where ß is the resonator lift angle, during which the pin 6 is in contact with the anchor fork 8.

More particularly, the penetration stroke P is greater than or equal to 80 micrometers and less than or equal to 120 micrometers.

More particularly, the penetration stroke P is greater than or equal to 100 micrometers.

More particularly, the safety distance S is greater than or equal to 20 micrometers and less than or equal to 30 micrometers.

More particularly, the safety distance S is greater than or equal to 25 micrometers.

More particularly, the angle of lift of the anchor a is greater than or equal to 5 ° and less than or equal to 30 °.

More particularly, the angle of lift of the anchor a is less than or equal to 20 °.

More particularly, the angle of lift of the anchor a is greater than or equal to 12 ° and less than or equal to 16 °.

More particularly, the β resonator lift angle is greater than or equal to 3 ° and less than or equal to 30 °.

More particularly, the β resonator lift angle is greater than or equal to 8 ° and less than or equal to 12 °.

More particularly, the β resonator lift angle is less than or equal to 10 °.

More particularly, the anchor 7 is a bistable stop.

Given a particular escape geometry, and a particular operating amplitude, in particular 8 °, dynamic multibody 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 ratio of inertia between the inertia of the inertial element and the inertia of the anchor, what usual kinematic simulations do not make it possible to establish. As shown in fig. 1, it can be seen that, under the simulation conditions, there is a threshold of good efficiency, greater than 35%, and of small delay, less than 8 seconds per day, for an inertia of the inertial element, in particular of a pendulum, which is 10,000 times larger than the inertia of the anchor. The analytical model of the system has shown that, if we want to limit the dynamic losses, a particular condition relates the inertia of the anchor, the inertia of the inertial element, the quality factor of the resonator, and the angles of lift of the anchor and of the inertial element: for a coefficient ε of dynamic losses, the inertia Ib of the set of inertial elements 2 with respect to the main axis DP on the one hand, and the inertia lA of the anchor 7 with respect to the secondary axis DS on the other hand, are such that the ratio lB / lA is greater than 2Ο.α2 / (0.1.π.β2), where a is the angle of lift of the anchor corresponding to the maximum angular travel of the anchor fork 8.

More particularly, if we want to limit the dynamic losses to a factor = 10%, the inertia IB of this at least one inertial element 2 relative to the main axis DP on the one hand, and the inertia lA of the anchor 7 with respect to the secondary axis DS on the other hand, are such that the ratio Ιβ / ΙΑ is greater than 2Q.a2 / (0.1 π.β2), where a is the lifting angle of the anchor corresponding 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 of which deviates from the maximum the inertial element 2 relative to a rest position, in one direction of its movement.

More particularly, the amplitude angle, which deviates the maximum inertial element 2 from a rest position, is between 5 ° and 40 °.

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

The fork 8 of the anchor 7 is thus enlarged compared to what would be a conventional range of Swiss anchor, which is much narrower and allows less freedom to the ankle 6, which would not manage to return and get out of the fork of a classic Swiss anchor with such a small angular amplitude. This concept of extended fork makes it possible to operate an anchor escapement even though the amplitude of the resonator is much smaller than in a conventional balance spring, which is particularly advantageous for flexible guide resonators, which have a low amplitude, as in this case. Indeed, it is important that during the operating cycle the balance is completely free at certain times.

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

The useful width L1 of the ankle 6, visible in FIG. 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 peg 6 is advantageously undercut behind its effective width L1 surface, the ankle can in particular have a prismatic shape of triangular section as suggested in the figure, or the like.

The observation of the figures shows a complementary action on the positioning of the ankle 6, located much further from the axis of rotation of the balance 2 than in a conventional exhaust mechanism: the upper radius combined with an angle of lower pivoting makes it possible to maintain an equivalent curvilinear stroke of the ankle 6, which is necessary to enable it to perform its distribution-counting function. The use of a large diameter rocker is therefore particularly interesting.

More particularly, the eccentricity E2 of the peg 6 with respect to the axis of the balance, and the eccentricity E7 of the fork horn 8 with respect to the axis of the anchor 7, are between 40.degree. % and 60% of the center distance E between the axis of the anchor 7 and the axis of the balance. More particularly, the eccentricity E2 is between 55% and 60% of the center distance E, and the eccentricity E7 is between 40% and 45% of the center distance E. More particularly, the interference zone between the ankle 6 and the fork 8 extends over 5% to 10% of the center distance E.

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

Thus, by substantially widening the range of the anchor compared to the usual proportions, we can still size a Swiss lever escapement with a very small angle of lift, for example of the order of 10 °.

FIG. 6 shows that, even with very small angles of rotation, one manages to enter the pin 6 in the fork 8 with a good penetration P, and to leave it with sufficient security S.

Figs. 16 to 19 illustrate the kinematics and show that there are adequate penetrations P and S safety, with this combined design of the ankle 6 very far from the axis of the balance, and anchor 7 of particular shape and in particular to extended range.

Similarly, FIGS. 20 to 24 illustrate the kinematics in another escapement mechanism 200 with a low lift angle, which comprises an escapement wheel 4 constituted by a coaxial wheel escapement wheel (which can constitute a one-piece assembly in a particular embodiment) comprising, on different levels: - direct impulse teeth 41 for a direct impulse with the balance, - rest teeth 42 arranged to cooperate with pallets of rest 71 and 72 of an anchor 7, - and teeth of indirect impulse 43 arranged to cooperate with a pulse pallet 73 of the same anchor 7.

Unlike a Swiss anchor whose pallets each have a dual function, namely stop the escape wheel on a rest at a rest plane, and give an impulse at a level of impulse plane, the anchor 7 of the coaxial type of FIGS. 20 to 24 separates the functions: - rest pallets 71 and 72: rest function only; - Pulse pad 73: Pulse function only.

Similarly, each tooth of an escape wheel for Swiss anchor fulfills both the function of taking rest and pulse, which is certainly advantageous in terms of size. But the Swiss anchor is poorly adapted to low amplitude oscillations which are a common feature of flexible guide resonators, including flexible blades. This is to ensure a perfect operation of the exhaust mechanism for small amplitudes of the resonator, and with the best possible performance. For this reason the escape wheel 4 is more complex here, since it comprises at least two levels, because: the rest teeth 42, which cooperate with the rest pallets 71 and 72 for the rest function, must, in the present particular and nonlimiting design, go under the beam, in particular under its impulse pallet 610, - while the direct impulse teeth 41, which cooperate for a direct impulse with the impulse pallet 610 must be coplanar to the latter; the indirect impulse teeth 43, which cooperate for an indirect impulse with the impulse pallet 73 of the anchor, are, in the nonlimiting embodiment illustrated by the figures, on a third level, but it is conceivable that they be housing on one of the two aforementioned levels, provided to design a mechanism without parasitic interference, in particular with regard to the arm of the balance which is carrying the pulse pallet 610.

The anchor 7 further comprises two anchor horns, first horn 81 and second horn 82, which together define such an enlarged fork according to the invention, arranged to cooperate with the rocker pin 6 sized according to the invention.

The rocker 2 comprises a radial arm carrying a pulse pallet 610, which is arranged to cooperate with the direct impulse teeth 41 of the escapement wheel 4.

The direct impulse teeth 41, and the indirect impulse teeth 43 of the illustrated variant are of very small radial extension in comparison with that of the rest teeth 42, in particular between 20% and 35%; in the illustrated example, the radial extension of the indirect pulse teeth 43 is 25% of that of the rest teeth 42, and the radial extension of the direct pulse teeth 41 is 31% of that of the rest teeth 42, which is of the order of 49% of the center distance E between the axis DP of the balance 2 and that DS of the anchor 7.

The bulk of the balance is, however, increased compared to a sprung balance balance for Swiss anchor, since it is advantageous to move the pin 6 of the pivot axis of the inertial mass. The outer surface 60 of the peg 6 is ci over a radius of 120% with respect to the radial extension of the rest teeth 42, or, to relate to the spacing E between the axis of the balance and that of the anchor, 59% of E.

As regards the anchor, with reference to the same radial extension of the rest teeth 42, the radial dimension of the end of the rest pallets 71 and 72 is here 60% or 30% of E, that the pulse pallet 73 of 95%, 47% of E, as well as horns 81 and 82.

The distance between the axis D4 of the escape wheel 4 and the DS of the anchor 7 is here 58% of E, and the distance between the axis DP of the balance 2 and that D4 of the escape wheel 4 is 89% of E.

FIG. 20 shows the exit release clearance: rest of a rest tooth 42 of the escape wheel 4 at rest on the exit rest pallet 72 of the anchor 7, free arc rotation of the beam 2 in the anti direction A-hour A until abutment of the ankle 6 on a first anchor horn 81 by a first edge 61, the balance 2 pushes the anchor 7, the rotation of the anchor 7 clockwise C clears the escape wheel of exit pallet 72.

FIG. 21 shows the indirect pulse: the rotation of the escapement wheel 4 released counter-clockwise E, abutment of an indirect pulse tooth 43 of the escape wheel 4 on the pulse pallet 73 of the anchor 7. Pushed by the escape wheel 4, the anchor 7 is leading, turns clockwise C until catch the balance 2, by the cooperation of the second anchor horn 82 with the ankle 6 on a second edge 62, thus indirectly transmitting the pulse of the escapement wheel 4 to the balance 2, through the anchor 7.

FIG. 22 shows the rest raised entry: arrival at the stop of a rest tooth 42 of the escape wheel 4 on the pallet of entry 71 rest of the anchor 7. The balance 2 continues then finishes his free arc in the counterclockwise B; he may miss the first anchor horn 81 without interfering with it during this race.

FIG. 23 shows the raised lifting input, after the end of the free arc of the balance, there is reversal of the direction of rotation of the balance 2 which starts in a clockwise direction B, the pin 6 bears on the second horn 82 of the anchor 7 and the anti-clockwise drive D, to the clearance between the entry pallet 71 input of the anchor 7 and the rest tooth 42 of the escape wheel 4, thus allowing the rotation of the exhaust wheel 4.

FIG. 24 shows the indirect pulse: stopping a direct impulse tooth 41 of the escape wheel 4 on the impulse pallet 610 of the rocker 2, allowing the direct drive of the rocker 2 by the mobile escape 4 The anchor 7 remains driven by its second horn 82 pushed by the ankle 6.

This kinematics is possible only because of the significant widening of the anchor fork between the first horn 81 and the second horn 82, and the adjustment of the penetration stroke P and the distance of safety S, which together ensure the possibility for the ankle 6 to get out of the anchor fork.

It is noted that this construction eliminates the presence of a dart on the anchor 7, which allows the manufacture thereof on a single level, for example micro-machinable material, silicon or similar, by "LIGA" or "MEMS" method or the like. Indeed, here the first horn 81 presses the ankle 6 when the balance 2 runs its free arc, which prevents the anchor from pivoting in case of shock, which makes the presence of a sting unnecessary, and a fortiori a small plateau on the balance 2, which can also be realized on one level.

And we understand the interest, to maximize the efficiency of the resonator, the particular relationship, described above and which binds the inertia of the inertial element and the inertia of the anchor, in a higher ratio to 10,000.

It is therefore particularly advantageous to have an anchor both very small and very light, and a large scale and high mass balance.

More particularly, the anchor 7 is silicon, which allows a miniaturized execution and very accurate, with a density less than one third of that of steel. The fact of having a silicon anchor makes it possible to reduce its inertia with respect to a metal anchor. A low inertia of the anchor relative to the balance is crucial to have a good performance at low amplitude and high frequency, in this case resonators with flexible guides.

The pendulum is, meanwhile, when the range of the watch allows it, advantageously made of a heavy metal or alloy, comprising gold, platinum, tungsten, or the like, and may include flyweights of similar constitution. Otherwise the balance is conventionally made CuBe2 copperbéryllium alloy, or the like, and weight balancing weights and / or control weights in nickel silver or other alloy.

More particularly this anchor 7 is on a single level of silicon, reported on a shaft, metal or the like, such as ceramic, or other, rotated relative to the plate 1.

More particularly, the escape wheel 4 is an escape wheel made of micro-machinable material, in particular silicon or the like.

More particularly, the escape wheel 4 is an escape wheel which is perforated to minimize its inertia relative to its pivot axis DE.

More particularly, the anchor 7 is perforated to minimize its inertia U relative to the secondary axis DS.

Preferably, the anchor 7 is symmetrical with respect to the secondary axis DS, so as to avoid unbalance, and avoid parasitic couples during linear shocks, especially in translation. An additional advantage is the great ease of assembly of this very small component, which the operator performing the assembly can handle from any side.

FIG. 7 shows the two horns 81 and 82 arranged to cooperate with the pin 6, the pallets 72 and 73 arranged to cooperate with the teeth of the escapement wheel 4, and false horns 80 and false pallets 70 whose only role is a perfect balancing.

More particularly, the largest dimension of this at least one 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 escapement wheel 4, are arranged according to a right-angle pointing whose apex is on the secondary axis DS. It is understood that, in reference to a classic Swiss anchor in the shape of a tee with a rod and two arms, it removes the rod, which becomes one of the two arms 76, visible in FIG. 7, which carries the horns 81 and 82 and the output pallet 72 almost coincides with the horn 82, the other arm 75 carrying the entry pallet 73.

The comparison with the Swiss anchor is to be continued with regard to the means of preventing overturning, usually constituted by a dart located on a remote plane of the anchor. This function is important to avoid jamming the pendulum. In particular, the pendulum is devoid of a small plateau and therefore tray notch provided to cooperate with such a sting. Here, because of the low angles of rotation, the ankle is never far from the fork. The anti-rollover function is then advantageously fulfilled by the combination of the perimeter 60 in an arc of the ankle 6, and by the corresponding surface 810, 820, of the anchor horn 81, 82 concerned: this horn plays the usual role. a dart, and the circumference of the ankle plays the role of the small plateau. The additional advantage that results is that, as regards its cooperation with the anchor of a single level, the balance can be also, locally, at a single level, which simplifies its manufacture and reduces its cost.

The design of a single-level anchor, which greatly simplifies the manufacture of the anchor, is possible only because the reversal is thus prevented by the small amplitude of the resonator, combined with the large width of the ankle (width approximately equal to the widened range).

More particularly, the flexible guide comprises two flexible blades crossed 5 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, the two flexible blades 5, projecting on a plane perpendicular to the main axis DP, form between them an angle between 59.5 ° and 69.5 °, and intersect between 10.75% and 14.75% of their length, from in order to provide the resonator mechanism 100 with a voluntary isochronism defect opposite to the escape delay fault of the escape mechanism 200.

The resonator thus has an anisochronism curve that compensates for the delay caused by the escape. That is, the free resonator is designed with an isochronism defect opposite the defect caused by the anchor escapement. We thus compensate the exhaust delay by the design of the resonator.

More particularly, the two flexible blades 5 are identical and are positioned in symmetry. More particularly, each flexible blade 5 belongs to a one-piece assembly 50, in one piece with two solid portions 51, 55, and with its first alignment means 52A, 52B, and attachment 54 on the plate 1, or , advantageously and as visible in FIG. 10, of fixing on an intermediate resilient spring plate 9 fixed to the plate 1 and which is arranged to allow a displacement of the flexible guide and this at least one inertial element 2 in the direction of the main axis DP, so as to provide a good protection against shocks Z direction perpendicular to the plane of such a one-piece assembly 10, and thus to avoid the breaking of the blades of the flexible guide. This intermediate elastic suspension plate 9 is advantageously made of alloy "Durimphy" or the like.

In the nonlimiting variant illustrated by the figures, the first alignment means are a first vee 52A and a first plate 52B, and the first fixing means comprise at least a first bore 54. A first veneer blade 53 provides support on the first fastening means. Similarly, the one-piece 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 fixing means comprise at least one second 58. A second veneer blade 57 bears on the second attachment means.

The flexible guide 3 with crossed blades 5 is advantageously constituted by 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 by means of integrated alignment and auxiliary means such as pins and screws, not shown in the figures.

Thus, more particularly, at least the resonator mechanism 100 is fixed on an intermediate resilient spring plate 9 fixed to the plate 1 and arranged to allow a movement resonator mechanism 100 in the direction of the main axis DP, and the platinum 1 comprises at least one anti-shock abutment 11, 12, at least in the direction of the main axis DP, and preferably at least two such abutments 11, 12, which are arranged to cooperate with at least one rigid element of this at least one inertial element 2, for example a flange 21 or 22 attached during the assembly of the inertial element with the flexible guide 3 comprising the blades 5.

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

FIG. 11 illustrates the presence of shock-proof abutments limiting the stroke of this at least one inertial element 2 along the three directions in the event of an impact, but located at a sufficient distance so that the inertial element does not touch the abutments under the effect of the gravity. For example, the flange 21 or 22 comprises a bore 211 and a face 212, able to cooperate respectively abutment abutment bearing with a pin 121 and a complementary surface 122 at the stop 21 or 22.

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

More particularly, the peg 6 is integral with a flexible blade 5, or more particularly, such a one-piece assembly 50 as shown in the figures.

More particularly, the anchor 7 has support surfaces arranged to cooperate in support with the teeth that includes the movable exhaust 4 and to limit the angular travel of the anchor 7. These supports can limit the angular course of the anchor, as would the stars. The angular travel of the anchor 78 may also be classically limited by limiting 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 regulator mechanism 300.

The invention also relates to a watch movement 500 comprising motor means 400, and such a regulator mechanism 300, whose escape mechanism 200 is subjected to the torque of these motor means 400.

The graphics of FIGS. 12 to 14 show a series of simulation results in which Q = 2000, lB = 26,550 mg.mm2, frequency of 20 Hz, mobile exhaust with 20 teeth, more particularly the angle of lift of the anchor is 14 °, and the resonator lift 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 regulator mechanism 300.

In short, the present invention makes it possible to increase the power reserve and / or the precision of the current mechanical watches. For a given size of movement, one can quadruple the autonomy of the watch and to double the regulating power of the watch. That is to say that the invention allows a gain of a factor 8 on the performance of the movement.

[0102] The skilled person will relate profitably to the thesis No. 3806 (2007) of Μ. Thierry CONUS, at EPFL in Lausanne (Switzerland) "Design and multi-criteria optimization of free escapements for mechanical wristwatches", presented on 01 June 2007, and in particular Chapter 8 Free Exhausts, pages 107 to 141, including §8.5. 1 Bistable stop and tangential pulse, pages 129 to 132.

The invention also relates to various exhaust mechanisms very varied, including, but not limited to, all escapements free bistable stopper including: - Swiss lever escapement - coaxial escapement - Fasoldt escapement (page 130 thesis T. Conus ) - escapement with articulated stop (page 133 thesis T. Conus) - escape of Bourquin de la Heute (page 119 thesis T. Conus) - escape Daniels (page 123 thesis T. Conus) - natural escape of Breguet (page 133 thesis T Conus) - Robin escapement - escapement with pins of Roskopf type (page 121 thesis T. Conus) - Melly escapement (page 130 thesis T. Conus) - two-wheeled escapement independent of Daniels (page 132 thesis T. Conus).

Claims (36)

claims 1. Time control mechanism (300), comprising, arranged on a plate (1), a resonator mechanism (100) of a quality factor Q, rotatable about a main axis (DP), and a mechanism exhaust (200) which is subjected to a pair of motor means (400) that comprises a movement (500), said resonator mechanism (100) having at least one inertia element! (2) arranged to oscillate with respect to said plate (1), said at least one inertial element (2) being subjected to the action of elastic return means (3) fixed directly or indirectly to said plate (1), and said at least one inertial element (2) being arranged to cooperate indirectly with an escapement wheel (4) provided by said escapement mechanism (200), characterized in that said elastic return means (3) comprise at least two blades hoses (5) to which said at least one inertial element (2) is suspended and which define a flexible guide with virtual pivoting of said at least one inertial element (2), said at least one inertial element (2) integrally carrying an anchor (6). ), and in that said escapement mechanism (200) comprises an anchor (7) arranged to pivot about a secondary axis (DS) and comprising an anchor fork (8) arranged to cooperate with said pin (6). ), and is a mechanism for free exhaust in the operating cycle of which said resonator mechanism (100) has at least one phase of freedom where said pin (6) is at a distance from said anchor fork (8) characterized in that, at each alternation, in a contact phase said pin (6) penetrates into said anchor fork (8) with a penetration stroke (P) greater than or equal to 40 micrometers and less than or equal to 200 micrometers, and in a disengagement phase said pin (6) remains at a distance from said anchor fork (8) with a safety distance (S) greater than or equal to 10 micrometers and less than or equal to 60 micrometers, and in that said peg (6) and said fork d anchor (8) are dimensioned so that the width (L) of said anchor fork (8) is greater than (P + S) / sin (a / 2 + β / 2), said penetration stroke ( P) and said safety distance (S) being measured radially by r relative to said main axis (DP), where a is the angle of lift of the anchor corresponding to the maximum angular travel of said anchor fork (8), and where β is the resonator lift angle, during which said peg (6) is in contact with said anchor fork (8). 2. Regulating mechanism (300) according to claim 1, characterized in that said penetration stroke (P) is greater than or equal to 80 micrometers and less than or equal to 120 micrometers. 3. Regulator mechanism (300) according to claim 1 or 2, characterized in that said penetration stroke (P) is greater than or equal to 100 micrometers. 4. Regulating mechanism (300) according to one of claims 1 to 3, characterized in that said safety distance (S) is greater than or equal to 20 micrometers and less than or equal to 30 micrometers. 5. Regulator mechanism (300) according to one of claims 1 to 4, characterized in that said safety distance (S) is greater than or equal to 25 micrometers. 6. Regulating mechanism (300) according to one of claims 1 to 5, characterized in that said lifting angle of the anchor (a) is greater than or equal to 5 ° and less than or equal to 30 °. 7. Regulator mechanism (300) according to claim 6, characterized in that said lifting angle of the anchor (a) is less than or equal to 20 °. 8. Regulator mechanism (300) according to claim 7, characterized in that said angle of lift of the anchor (a) is greater than or equal to 12 ° and less than or equal to 16 °. 9. Regulator mechanism (300) according to one of claims 1 to 9, characterized in that said resonator lift angle (β) is greater than or equal to 3 ° and less than or equal to 30 °. 10. Regulator mechanism (300) according to claim 9, characterized in that said resonator lifting angle (β) is greater than or equal to 8 ° and less than or equal to 12 °. 11. Regulator mechanism (300) according to claim 9 or 10, characterized in that said resonator lift angle (β) is less than or equal to 10 °. 12. Regulator mechanism (300) according to one of claims 1 to 11, characterized in that said anchor (7) constitutes a bistable stop. 13. Regulating mechanism (300) according to one of claims 1 to 12, characterized in that the inertia IB of all of said inertial elements (2) relative to said main axis (DP) on the one hand, and the Inertia 1A of said anchor (7) relative to said secondary axis (DS) on the other hand, are such that the ratio lB / lA is greater than 2Ο.α2 / (0.1.π.β2), where a is the angle of lift of the anchor which corresponds to the maximum angular travel of said anchor fork (8). 14. Regulating mechanism (300) according to one of claims 1 to 13, characterized in that said overall angle of resonator lift (β) is less than twice the amplitude angle of which deviates to the maximum, in a single direction of its movement said at least one inertial element (2) relative to a rest position. 15. Regulating mechanism (300) according to one of claims 1 to 14, characterized in that the amplitude angle, which deviates at most said at least one inertial element (2) relative to a rest position is between 5 ° and 40 °. 16. Regulator mechanism (300) according to one of claims 1 to 15, characterized in that said anchor (7) is in a single level of silicon, reported on a shaft rotated relative to said plate (1). 17. Regulator mechanism (300) according to one of claims 1 to 16, characterized in that said mobile exhaust (4) is a silicon escapement wheel. 18. Regulating mechanism (300) according to one of claims 1 to 17, characterized in that said mobile escape (4) is an escape wheel which is perforated to minimize its inertia relative to its pivot axis. 19. Regulating mechanism (300) according to one of claims 1 to 18, characterized in that said anchor (7) is perforated to minimize its said inertia (lA) relative to said secondary axis (DS). 20. Regulating mechanism (300) according to one of claims 1 to 19, characterized in that said anchor (7) is symmetrical with respect to said secondary axis (DS). 21. Regulating mechanism (300) according to one of claims 1 to 20, characterized in that the largest dimension of said at least one inertial element (2) is greater than half of the largest dimension of said platen (1 ). 22. Regulating mechanism (300) according to one of claims 1 to 21, characterized in that said main axis (DP), said secondary axis (DS) and the pivot axis (DE) of said mobile escape (4 ), are arranged in a right angle pointing whose apex is on said secondary axis (DS). 23. Regulating mechanism (300) according to one of claims 1 to 22, characterized in that said flexible guide comprises two flexible blades (5) crossed in projection on a plane perpendicular to said main axis (DP) at said virtual pivot defining said main axis (DP), and located in two parallel and distinct levels. 24. Regulating mechanism (300) according to claim 23, characterized in that said two flexible blades (5), in projection on a plane perpendicular to said main axis (DP), form between them an angle between 59.5 ° and 69.5 °, and intersect between 10.75% and 14.75% of their length, so as to provide said resonator mechanism (100) with a voluntary isochronism defect opposite the exhaust delay fault of said exhaust mechanism (200). 25. Regulator mechanism (300) according to claim 23 or 24, characterized in that said two flexible blades (5) are identical and are positioned symmetrically. 26. Regulating mechanism (300) according to one of claims 23 to 25, characterized in that each said flexible blade (5) belongs to a one-piece assembly (50) in one piece with its alignment and fixing means on said plate (1) or on an intermediate elastic suspension plate (9) fixed to said plate (1) and arranged to allow a displacement of said flexible guide and of said at least one inertial element (2) in the direction of said main axis ( DP). 27. Regulator mechanism (300) according to one of claims 1 to 26, characterized in that at least said resonator mechanism (100) is fixed on an intermediate elastic suspension plate (9) fixed to said plate (1) and arranged to allow a movement resonator mechanism (100) in the direction of said main axis (DP), and in that said plate (1) comprises at least one shock-proof abutment (11, 12) at least in the direction of said main axis (DP) , arranged to cooperate with at least one rigid element of said at least one inertial element (2). 28. Regulating mechanism (300) according to one of claims 1 to 27, characterized in that said at least one inertial element (2) comprises weights for adjusting the step and unbalance. 29. Regulating mechanism (300) according to one of claims 1 to 28, characterized in that said pin (6) is integral with a said flexible blade (5). 30. Regulating mechanism (300) according to one of claims 1 to 29, characterized in that said anchor (7) comprises bearing surfaces arranged to cooperate in abutment with teeth that includes said mobile escape (4) and to limit the angular travel of said anchor (7). 31. Regulator mechanism (300) according to one of claims 1 to 30, characterized in that said flexible guide is made of oxidized silicon to compensate for the effects of temperature on the operation of said regulator mechanism (300). 32. Regulator mechanism (300) according to one of claims 1 to 31, characterized in that said exhaust mechanism (200) is a coaxial exhaust mechanism. 33. Regulating mechanism (300) according to one of claims 1 to 31, characterized in that said exhaust mechanism (200) is a Fasoldt exhaust mechanism. 34. Regulating mechanism (300) according to one of claims 1 to 31, characterized in that said exhaust mechanism (200) is an exhaust mechanism with articulated retainer. 35. A watch movement (500) comprising motor means (400) and a regulating mechanism (300) according to one of claims 1 to 34, wherein said exhaust mechanism (200) is subjected to the torque of said motor means ( 400). 36. Watch (1000) comprising a movement (500) according to claim 35, and / or a regulating mechanism (300) according to one of claims 1 to 34.