Classifications

• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/06—Free escapements
  • G04B15/08—Lever escapements
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B17/00—Mechanisms for stabilising frequency
  • G04B17/20—Compensation of mechanisms for stabilising frequency
  • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B18/00—Mechanisms for setting frequency
  • G04B18/02—Regulator or adjustment devices; Indexing devices, e.g. raquettes
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B17/00—Mechanisms for stabilising frequency
  • G04B17/04—Oscillators acting by spring tension
  • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B17/00—Mechanisms for stabilising frequency
  • G04B17/20—Compensation of mechanisms for stabilising frequency
  • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses

Definitions

• the invention relates to a timepiece control mechanism, comprising, arranged on a plate, a resonator mechanism of a Q quality factor, and an exhaust mechanism which is subjected to a pair of motor means that comprises a movement, said resonator mechanism comprising an inertial element arranged to oscillate with respect 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 device; exhaust 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 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 clock regulation mechanisms, in particular for watches.
• a balance-spring oscillates with an amplitude of 300 °, and the angle of emergence 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.
• 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 free escapement category because, beyond the half-angle of lift, the resonator no longer touches the anchor. This characteristic is essential to obtain good chronometric properties.
• a mechanical resonator comprises an inertial element, a guide and an elastic return element.
• the pendulum constitutes the inertial element
• 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 rotating flexible guide, in place of the pivots and the traditional hairspring, is a solution that maximizes the quality factor Q.
• the flexible blade resonators as long as they are well designed, have promising chronometric properties, irrespective of the orientation in gravity, and have high quality factors, notably thanks to the absence of pivoting friction.
• the use of flexible guides makes it possible to eliminate the problems of wear of the pivots.
• 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, in particular blades, is typically 6 ° to 15 °. This results in a certain lift angle value, which must be twice the minimum operating amplitude.
• the resonator must have an acceptable size, compatible with its housing in a clockwork 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 putting series of successive flexible guides in series, to obtain an amplitude of oscillation 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 EP3035126 in the name of THE SWATCH GROUP RESEARCH & DEVELOPMENT Ltd.
• 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 magnitude significantly greater than half lifting angle, 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.
• 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 rotatable flexible guide resonator with an optimized anchor escapement to maintain acceptable dynamic losses and limit the time effect of the release.
• 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.
• the dynamic losses 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.
• a plate anchor integral with the inertial element must penetrate a certain value, called penetration, into the opening of the anchor fork.
• 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.
• the invention is further concerned with imposing a particular relationship between the dimensions of the anchor fork, the penetration and safety values, and the values of the lifting angles of the anchor and the inertial element, to ensure that the ankle is properly retracted 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 also relates to a watch, more particularly a mechanical watch, comprising such a movement, and / or such a regulating mechanism.
• FIG. 2 is a diagrammatic, partial and perspective view of a watch movement with a platinum carrying a regulating mechanism according to the invention, comprising a flexible guide resonator with two flexible blades arranged on two parallel levels. and crossed 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 a peg arranged to cooperate with a symmetrical anchor, whose pivoting by a metal shaft on the plate is not shown, which cooperates itself with a conventional escape wheel;
• Figure 3 shows, in plan view, the only regulating mechanism of Figure 2, arranged on the stage of the movement;
• Figure 4 shows, in plan view, the detail of the regulating mechanism of Figure 2;
• FIG. 5 shows, in perspective partially exploded, the regulating mechanism of Figure 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, represented in an abutment position on a limiting pin;
• Figure 7 shows, in plan view, the anchor of the mechanism of Figure 2, in the form of bovine horns watusi;
• Figure 8 shows, in plan view, the flexible guide of the mechanism of Figure 2;
• Figure 9 shows, in plan view, a particular embodiment of a level of the flexible guidance of the mechanism of Figure 2;
• FIG. 10 represents, in side view, the regulating mechanism of FIG.
• FIG. 11 represents, 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 escapement 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 Figure 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 a plan view, the steps of the kinematics, already symbolized in FIG. 6, at the level of the rocker pin, the fork of the anchor of FIG. 7, and the rotor of FIG. exhaust here constituted by a traditional escape wheel:
• figure 16 rest of the escape wheel on the entry pallet, free arc of the resonator
• Figure 19 rest of the escape wheel on the output pallet, free arc of the resonator, and setting safe;
• FIGS. 20 to 24 show, in a plan view, kinematic steps in a low angle of lift escape mechanism, comprising an escape wheel constituted by a coaxial wheel escape wheel comprising, on levels separate, direct impulse teeth with the balance wheel, 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 further comprises two anchor horns defining an enlarged fork according to the invention arranged to cooperate with the rocker pin dimensioned according to the invention, which balance comprises a radial arm carrying a pulse pallet arranged to cooperate with the teeth direct impulse of the mobile escape:
• exit release clearance rest of a rest tooth of the escape wheel on the anchor outlet pallet rest, free arc of the resonator in the counterclockwise direction until it stops the ankle on a first anchor horn, rotating the anchor clockwise;
• figure 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 in direction time 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;
• figure 22 rest lift raised: arrival at abutment of a rest tooth of the escape wheel on the pallet of rest of entrance of the anchor, then end of the free arc of the pendulum in the anti-clockwise direction ;
• figure 23 release lifting input: reversal of the direction of rotation of the balance which starts in clockwise direction, the peg bears on the second horn of the anchor and drives it counter-clockwise, 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: stopping of a direct impulse tooth of the escape wheel on the pendulum impulse pallet, allowing the pendulum to be driven directly by the escapement mobile.
• the invention combines a rotatable flexible guide resonator to increase power reserve and accuracy, with an optimized anchor escapement to maintain acceptable dynamic losses and limit the timing effect of the release.
• the invention thus relates to a clocking mechanism 300 comprising, arranged on a plate 1, a resonator mechanism 100 of quality factor Q, rotatable about a main axis DP, and an escape 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 inertial element 2 which is arranged to oscillate with respect to the plate 1, about a main axis DP.
• 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 escape wheel 4, in particular an escape wheel, which the escape mechanism 200 comprises, and which pivots about an exhaust axis DE.
• these resilient return means 3 comprise at least two flexible blades 5 to which this at least one inertial element 2 is suspended, in particular a rocker or the like, and which define a flexible guide with virtual pivoting of this at least one element. inertial 2.
• This at least one inertial element 2 integrally carries a pin 6.
• the escapement mechanism 200 comprises an anchor 7 arranged to pivot about a secondary axis DS, and having a 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 away from the anchor fork 8.
• 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 one phase the ankle 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 + 3/2), 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 ⁇ is the resonator lift angle, during which the pin 6 is in contact with the anchor fork 8.
• the penetration stroke P is greater than or equal to 80 micrometers and less than or equal to 120 micrometers.
• the penetration stroke P is greater than or equal to 100 micrometers.
• the safety distance S is greater than or equal to 20 micrometers and less than or equal to 30 micrometers.
• the safety distance S is greater than or equal to 25 microns.
• the angle of lift of the anchor a is greater than or equal to 5 ° and less than or equal to 30 °.
• the angle of lift of the anchor a is less than or equal to 20 °.
• the angle of lift of the anchor a is greater than or equal to 12 ° and less than or equal to 16 °.
• the ⁇ resonator lift angle is greater than or equal to 3 ° and less than or equal to 30 °.
• the resonator raising angle ⁇ is greater than or equal to 8 ° and less than or equal to 12 °. More particularly, the ⁇ resonator lift angle is less than or equal to 10 °.
• the anchor 7 constitutes a bistable stop.
• the analytical model of the system has 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 lift of the anchor and of the inertial element: for a coefficient ⁇ of dynamic losses, the inertia IB of all the inertial elements 2 with respect to the main axis DP on the one hand, and the inertia of the anchor 7 relative to the secondary axis DS on the other hand, are such that the ratio IB / IA is greater than 20. ⁇ 2 /( ⁇ . ⁇ . ⁇ 2 ), where a is the lifting angle of the anchor corresponding to the maximum angular travel of the anchor fork 8.
• the inertia IB of this at least one inertial element 2 with respect to the main axis DP on the one hand, and the inertia of the anchor 7 relative to the secondary axis DS on the other hand are such that the ratio IB / IA is greater than 2Q.a 2 /(0.1 . ⁇ . ⁇ 2 ), where a is the lifting angle of the anchor corresponding to the maximum angular travel of the anchor fork 8.
• the resonator lifting angle ⁇ which is an overall angle, taken on either side of the rest position, is less than twice the amplitude angle of which deviates as much as possible. inertial element 2 with respect to a rest position, in one direction of its movement.
• the angle of amplitude from which the inertial element 2 deviates as much as possible 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 distance P greater than 100 micrometers, and in a release phase the pin 6 remains at a distance from the fork anchor 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 Swiss anchor fork, which is much narrower and allows less freedom to the ankle 6, which would not manage to get in and 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.
• 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 + 3/2), the penetration stroke P and the safety distance S being measured radially with respect to the main axis DP.
• the effective width L1 of the peg 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 in behind the L1 effective width surface, the peg may in particular have a prismatic shape of triangular section as suggested in the figure, or the like.
• 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% and 60 % of the center distance E between the axis of the anchor 7 and the axis of the pendulum. 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.
• 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 further apart, and the ankle is wider, than for a Swiss anchor mechanism. known type with a usual lifting angle of 50 °.
• FIG. 6 shows that, even with very small pivoting angles, it is possible to retract the pin 6 into 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 adequate penetrations P and safety S are available, with this combined design of the ankle 6 very far from the axis of the balance, and anchor 7 of particular shape and especially with an extended fork.
• 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 an assembly).
• monobloc in a particular embodiment comprising, on different levels:
• the coaxial type anchor 7 of FIGS. 20 to 24 separates the functions:
• each tooth of a Swiss anchor escapement wheel performs both the idle and pulse function, which is certainly advantageous in terms of size.
• 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.
• 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, pass under the beam, in particular under its pulse pallet 610,
• 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 extended fork according to the invention, arranged to cooperate with the rocker pin 6 dimensioned 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 have a 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.
• the radial dimension of the end of the rest pallets 71 and 72 is here 60% or 30% of E, that of the pallet pulse 73 of 95%, ie 47% of E, just like those of the 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 wheel d Exhaust 4 is 89% of E.
• FIG. 20 shows the emergent 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 balance 2 in the anti-clockwise A until abutment of the ankle 6 on a first anchor horn 81 by a first edge 61, the rocker 2 pushes the anchor 7, the rotation of the anchor 7 in the clockwise direction C releases the escape wheel from the exit pallet 72.
• FIG. 21 shows the indirect pulse: the rotation of the escapement wheel 4 released in counterclockwise direction E, abutment of an indirect impulse tooth 43 of the escape wheel 4 on the impulse pallet 73 of the anchor 7.
• the anchor 7 is driving, turns clockwise C to 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 lift released entry: arrival at the stop of a rest tooth 42 of the escape wheel 4 on the entry pallet 71 of the anchor 7.
• the rocker 2 continues and then finishes its free arc counter-clockwise 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 again in a clockwise direction B, the pin 6 bears on the second horn 82 of the anchor 7 and trains him in counter-clockwise direction D, until the clearance between the inlet rest pallet 71 of the anchor 7 and the rest tooth 42 of the escape wheel 4, thus allowing the rotation of the escape 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 pendulum 2, allowing the pendulum 2 to be driven directly by the mobile of FIG. 4.
• the anchor 7 remains driven by its second horn 82 pushed by the ankle 6.
• this construction makes it possible to dispense with the presence of a stinger on the anchor 7, which authorizes the manufacture thereof on a single level, for example of micro-machinable material, silicon or the like, by "LIGA” or “MEMS” method or the like.
• 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.
• the anchor 7 is made of silicon, which allows a miniaturized and very precise execution, 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, for its part, when the range of the watch authorizes it, advantageously made of a metal or heavy alloy, comprising gold, platinum, tungsten, or the like, and may comprise weights of similar constitution . Otherwise the pendulum is conventionally made of CuBe2 alloy copper- beryllium, or the like, and weighted with balancing weights and / or adjusting weights in nickel silver or other alloy.
• 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.
• the escape wheel 4 is an escape wheel made of micro-machinable material, in particular silicon or the like.
• the escape wheel 4 is an escape wheel which is perforated to minimize its inertia with respect to its pivot axis DE.
• the anchor 7 is perforated to minimize its inertia relative to the secondary axis DS.
• the anchor 7 is symmetrical with respect to the secondary axis DS, so as to avoid any 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 peg 6, the vanes 72 and 73 arranged to cooperate with the teeth of the escape wheel 4, and false horns 80 and false pallets 70 whose only role is a perfect balancing,
• the largest dimension of this at least one inertial element 2 is greater than half of the largest dimension of the plate 1.
• the main axis DP, the secondary axis DS and the pivot axis of the escapement wheel 4 are arranged in a right-angle pointing whose apex is on the secondary axis DS.
• the comparison with the Swiss anchor is to be continued with regard to the means of preventing the overturning, usually consisting of a dart located on a plan deported from the anchor.
• This function is important to avoid jamming the pendulum.
• the pendulum is devoid of small tray and therefore plateau notch provided to cooperate with such a dart.
• the ankle is never far from the fork.
• the anti-rollover function is then advantageously fulfilled by the combination of the periphery 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 flexible guide comprises two flexible blades 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, 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.
• 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 can be seen in FIG. 10, of attachment to an intermediate elastic suspension plate 9 fixed to the plate 1 and which is arranged to allow displacement of the flexible guide and of this at least one inertial element 2 in the direction of the main axis DP, so as to provide good protection against shocks Z direction perpendicular to the plane of such a one-piece assembly 10, and thus to prevent the rupture of the blades of the flexible guide.
• This intermediate elastic suspension plate 9 is advantageously made of alloy "Durimphy" or the like.
• the first alignment means are a first vee 52A and a first plate 52B, and the first attachment means comprise at least a first bore 54.
• a first veneer blade 53 provides the support on the first fastening means.
• 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 cross-blade guide 3 advantageously consists of two identical 50-piece monobloc assemblies of silicon, assembled in symmetry to form the crossing of the blades, and precisely aligned with respect to one another by virtue of the integrated alignment means. and auxiliary means such as pins and screws, not shown in the figures.
• the resonator mechanism 100 is fixed on an intermediate elastic suspension 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 plate 1 comprises at least one shockproof abutment 1 1, 12, at least in the direction of the main axis DP, and preferably at least two such abutments 1 1, 12, which are arranged to cooperate with at least one rigid element of this to less an inertial element 2, for example a flange 21 or 22 reported during assembly of the inertial element with the flexible guide 3 comprising the blades 5.
• the elastic suspension plate 9, or a similar device allows displacements 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 shockproof abutments limiting the travel of this at least one inertial element 2 according to the three directions in the event of impact, but located at a distance sufficient that the inertial element does not touch the stops under the effect of gravity.
• the flange 21 or 22 has a bore 21 1 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.
• the inertial element 2 comprises weights 20 for adjusting the step and unbalance.
• the peg 6 is integral with a flexible blade 5, or more particularly, such a one-piece assembly 50 as illustrated in the figures.
• the anchor 7 comprises bearing surfaces arranged to cooperate in abutment with the teeth of the escapement wheel 4 and to limit the angular travel of the anchor 7. These supports make it possible to limit the angular travel of the anchor, as would the stars.
• the angular travel of the anchor 78 may also be classically limited by limiting pins 700.
• 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 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 invention also relates to a watch 1000, more particularly a mechanical watch, comprising such a movement 500, and / or such a regulating mechanism 300.
• 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.
• the invention also relates to various very varied escape mechanisms, including, but not limited to, all free exhausts with bistable arrestors, including:

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• Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)

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• 2016
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• 2017
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• 2019
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