EP3545368B1 - Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird - Google Patents

Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird Download PDF

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Publication number
EP3545368B1
EP3545368B1 EP17752312.3A EP17752312A EP3545368B1 EP 3545368 B1 EP3545368 B1 EP 3545368B1 EP 17752312 A EP17752312 A EP 17752312A EP 3545368 B1 EP3545368 B1 EP 3545368B1
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EP
European Patent Office
Prior art keywords
regulating mechanism
resonator
inertia
plate
main axis
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EP17752312.3A
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English (en)
French (fr)
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EP3545368A1 (de
Inventor
Pascal Winkler
Jean-Luc Helfer
Gianni Di Domenico
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ETA SA Manufacture Horlogere Suisse
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ETA SA Manufacture Horlogere Suisse
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    • 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
    • G04B17/04—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
    • G04B17/28—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
    • G04B17/20—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 clockwork regulating mechanism, comprising, arranged on a plate, a resonator mechanism with a quality factor Q, and an escape mechanism which is subjected to a torque of motor means which a movement comprises, said movement.
  • 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 said exhaust mechanism comprises.
  • the invention also relates to a clockwork movement comprising motor means, and such a regulating mechanism, the escape 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.
  • the escapement for its part, 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 balance far from its point of equilibrium, resist shocks, avoid jamming the movement (for example during a reversal), and therefore constitutes a key component of the watch movement.
  • a sprung balance oscillates with an amplitude of 300 °, and the lift angle is 50 °.
  • the angle of lift is the angle of the balance on which the fork of the anchor interacts with the pin, also called the ellipse, of the balance.
  • the lift angle is distributed on either side of the balance point of the balance (+/- 25 °), and the anchor tilts +/- 7 °.
  • the Swiss lever escapement belongs to the category of free escapements, because, beyond the half-angle of lift, 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.
  • the balance constitutes the inertial element
  • the hairspring constitutes the elastic return element.
  • the balance is guided in rotation by pivots, which rotate in plain ruby bearings.
  • the associated friction is the source of energy losses and operating disturbances.
  • the losses are characterized by the quality factor Q of the resonator.
  • the flexible blades generally used in such rotating flexible guides are more rigid than balance springs. 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 does not seem compatible with a Swiss lever type escapement.
  • An operating amplitude compatible with a resonator with rotary flexible guide, in particular with blades, is typically 6 ° to 15 °. This results in a certain value of the angle of lift, 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 to date to achieve a flexible rotary guide of very large diameter, nor with several pairs of levels of blades, which would allow in theory, by placing 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 the document EP2894520 in the name of NIVAROX SA, or the document EP3035126 on behalf of THE SWATCH GROUP RESEARCH & DEVELOPMENT Ltd.
  • the effect of choosing 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 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 particular escapement mechanism, with a dimensioning different from what would be a conventional 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 the precision of current mechanical watches. To achieve this objective, the invention combines a resonator with rotating flexible guidance with an lever escapement optimized to maintain acceptable dynamic losses and limit the chronometric effect of the release.
  • the invention relates to a regulating mechanism according to claim 1.
  • Such resonators with rotating flexible guide have very high quality factors, for example of the order of 3000, compared with a quality factor of 200 for a conventional watch.
  • the dynamic losses kinetic energy of the escape mobile and of the anchor at the end of the pulse
  • These losses can therefore become too great, with a high quality factor, in a relative level with respect to the energy transmitted to the balance.
  • a plate pin secured to the inertial element must penetrate by a certain amount, called penetration, into the opening of the anchor fork.
  • this platform pin must then be able, after release of the pin, to be kept at a certain distance, called security, from the horn of the fork opposite to that on which it was in contact. immediately before its release.
  • the invention also seeks 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 lift of the anchor and of the inertial element, to ensure that the pin retracts correctly from the fork, once the half-angle of lift has been completed.
  • the invention also relates to a clockwork movement comprising motor means, and such a regulating mechanism, the escape 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 combines a resonator with rotating flexible guidance, in order to increase the power reserve and precision, with an lever escapement optimized to maintain acceptable dynamic losses and limit the chronometric effect of the release.
  • the invention thus relates to a clockwork regulator mechanism 300, comprising, arranged on a plate 1, a resonator mechanism 100 of quality factor Q, and an escape mechanism 200, which is subjected to a torque of motor means 400 that features a 500 movement.
  • This resonator mechanism 100 comprising 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 escapement mobile 4, in particular an escape wheel, which the escape mechanism 200 comprises, and which pivots about an escape axis DE.
  • the resonator mechanism 100 is a rotary resonator with virtual pivot, around a main axis DP, with flexible guidance comprising at least two flexible blades 5, and comprises a plate pin 6 integral with the inertial element 2
  • the escape mechanism 200 comprises an anchor 7, which pivots about a secondary axis DS and comprises an anchor fork 8 arranged to cooperate with the plate pin 6, and is thus a free escape mechanism: in its operating cycle, the resonator mechanism 100 has at least one phase of freedom where the plate pin 6 is at a distance from the anchor fork 8.
  • the resonator lift angle ⁇ , during which the plate pin 6 is in contact with the anchor fork 8, is less than 10 °.
  • dynamic multibody simulations make it possible to evaluate the efficiency and the delay of this escapement mechanism as a function of the inertia ratio between the inertia of the inertial element and the inertia of the anchor, which usual kinematic simulations do not allow to establish.
  • 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 dynamic loss coefficient ⁇ , 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 with respect to the secondary axis DS on the other hand, are such that the ratio I B / I A is greater than 2Q. ⁇ 2 /( ⁇ . ⁇ . ⁇ 2 ), where a is the Anchor lift angle that corresponds to the maximum angular travel of the anchor fork 8.
  • 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 with respect to the secondary axis DS on the other hand are such that the ratio IB / IA is greater than 2.Q. ⁇ 2 /( ⁇ . ⁇ /10), where a is the lifting angle of the anchor which corresponds to the maximum angular travel of the anchor fork 8.
  • the resonator lift angle ⁇ which is an overall angle, taken on either side of the rest position, is less than twice the amplitude angle from which the maximum deviates. inertial element 2 with respect to a rest position, in a single direction of its movement.
  • the amplitude angle, from which the inertial element 2 deviates as far as possible from a rest position is between 5 ° and 40 °.
  • the plate pin 6 in a contact phase the plate pin 6 enters 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.
  • the plate peg 6 and the anchor fork 8 are dimensioned so that the width L of the anchor fork 8 is greater than (P + S) / sin ( ⁇ / 2 + ⁇ / 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 platform peg 6 is advantageously undercut behind its surface of useful width L1, the peg can in particular have a prismatic shape of triangular section as suggested in the figure, or the like.
  • the invention defines, by construction, a new ankle-fork outline, which has a very particular characteristic, according to which the horns of the fork are more apart, and the ankle is wider, than for a Swiss lever mechanism of known type with a usual lifting angle of 50 °.
  • the anchor 7 is made of a single level of silicon, attached to a metal axis pivoted relative to the plate 1.
  • the escape mobile 4 is a silicon escape wheel.
  • the escape wheel set 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 I A with respect to the secondary axis DS.
  • the anchor 7 is symmetrical with respect to the secondary axis DS, so as to avoid any unbalance, 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 paddles 72 and 73 arranged to cooperate with the teeth of the exhaust mobile 4, and false horns 80 and false paddles 70 whose only role is perfect balance,
  • the largest dimension of the 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 escape wheel set 4 are arranged in a right angle pointing, the apex of which is the secondary axis DS.
  • the flexible guide comprises two flexible blades 5 crossed in projection on a plane perpendicular to the main axis DP, at the level of the virtual pivot defining the main axis DP, and located in two parallel and distinct levels. More particularly still, the two flexible blades 5, in projection on a plane perpendicular to the main axis DP, form between them an angle of between 59.5 ° and 69.5 °, and cross between 10.75% and 14.75% of their length, of so as to provide the resonator mechanism 100 with a voluntary defect of isochronism opposed to the defect of delay on the escapement of the escapement mechanism 200.
  • the resonator thus exhibits an anisochronism curve which compensates for the delay caused by the escapement. That is, the free resonator is designed with a defect of isochronism opposed to the defect caused by the lever escapement. The exhaust delay is therefore compensated by the design of the resonator.
  • each flexible blade 5 is identical and are positioned in symmetry. More particularly still, each flexible blade 5 belongs to a one-piece assembly 50, in one piece with its first alignment means 52A, 52B, and fixing 54 on the plate 1, or, advantageously and as visible on the figure 10 , for 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 of the inertial element 2 in the direction of the main axis DP.
  • 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.
  • 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 attachment means comprise at least a second bore 58.
  • a second veneer blade 57 provides support on the second fixing means.
  • the flexible guide 3 with crossed blades 5 is advantageously made up of two one-piece assemblies of 50 identical silicon pieces, 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 to auxiliary means such as pins and screws, not shown in the figures.
  • the resonator mechanism 100 is fixed to an intermediate elastic suspension strip 9 fixed to the plate 1 and arranged to allow a displacement of the resonator mechanism 100 in the direction of the main axis DP, and the plate 1 comprises at least one anti-shock stop 11, 12, at least in the direction of the main axis DP, and preferably at least two such anti-shock stops 11, 12, which are arranged to cooperate with rigid elements of the inertial element 2, for example flanges 21 and 22 added 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 movement 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 anti-shock stops limiting the travel of the inertial element 2 in the 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 shock. gravity.
  • the flange 21 or 22 comprises a bore 211 and a face 212, able to cooperate respectively in support of the shock-proof stop with a journal 121 and a complementary surface 122 at the level of the stop 21 or 22.
  • the inertial element 2 comprises weights 20 for adjusting the rate and the unbalance.
  • the platform peg 6 is in one piece 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 bearing with the teeth that the escape wheel set 4 comprises and to limit the angular travel of the anchor 7. These bearings make it possible to limit the angular travel of anchor, as stars would.
  • the angular travel of the anchor 78 can moreover be conventionally 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 timepiece movement 500 comprising motor means 400, and such a regulator mechanism 300, of which the 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 current mechanical watches. For a given movement size, we 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.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Electromechanical Clocks (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)

Claims (23)

  1. Regelmechanismus (300) für eine Uhr, der eine Platine (1) beinhaltet, und auf der Platine (1) angeordnet,
    einen Resonator-Mechanismus (100) mit einem Qualitätsfaktor Q, und einen Hemmungsmechanismus (200), der angeordnet ist, um einem Moment von Antriebsmitteln (400) ausgesetzt zu werden, die ein Werk (500) beinhaltet, wobei der Resonator-Mechanismus (100) ein Trägheitselement (2) beinhaltet, das angeordnet ist, um in Bezug auf die Platine (1) zu schwingen, wobei das Trägheitselement (2) der Aktion von elastischen Rückzugsmitteln (3) ausgesetzt ist, die direkt oder indirekt an der Platine (1) befestigt sind, und das Trägheitselement (2) angeordnet ist, um indirekt mit einem Hemmungsdrehteil (4) zusammenzuwirken, das der Hemmungsmechanismus (200) beinhaltet, wobei der Resonator-Mechanismus (100) ein drehender Resonator mit virtueller Drehführung um eine Hauptachse (DP) herum, mit flexibler Führung ist, der mindestens zwei flexible Klingen (5) beinhaltet, und einen Hebelstein (6) beinhaltet, der fest mit dem Trägheitselement (2) verbunden ist, wobei der Hemmungsmechanismus (200) einen Anker (7) beinhaltet, der sich um eine Sekundärachse (DS) dreht und eine Ankergabel (8) beinhaltet, die angeordnet ist, um mit dem Hebelstein (6) zusammenzuwirken, und ein freier Hemmungsmechanismus ist, in dessem Betriebszyklus der Resonator-Mechanismus (100) mindestens eine Freiheitsphase besitzt, in der der Hebelstein (6) auf Abstand von der Ankergabel (8) ist, dadurch gekennzeichnet, dass der Resonator-Hebungswinkel (β), bei dem der Hebelstein (6) in Kontakt mit der Ankergabel (8) ist, kleiner als 10° ist.
  2. Regelmechanismus (300) nach Anspruch 1, dadurch gekennzeichnet, dass die Trägheit IB des Trägheitselements (2) in Bezug auf die Hauptachse (DP) einerseits, und die Trägheit IA des Ankers (7) in Bezug auf die Sekundärachse (DS) andererseits, derart sind, dass das Verhältnis IB/IA größer ist als: 2Q.α2/(π.β2/10), wobei α der Hebungswinkel des Ankers ist, der dem maximalen Winkelweg der Ankergabel (8) entspricht.
  3. Regelmechanismus (300) nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der globale Resonator-Hebungswinkel (β) kleiner als das Doppelte des Amplitudenwinkels ist, um den sich das Trägheitselement (2) in Bezug auf eine Ruheposition höchstens in einer einzigen Richtung seiner Bewegung entfernt.
  4. Regelmechanismus (300) nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Amplitudenwinkel, um den sich das Trägheitselement (2) in Bezug auf eine Ruheposition höchstens entfernt, zwischen 5° und 40° enthalten ist.
  5. Regelmechanismus (300) nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass der Hebelstein (6) bei jeder Halbschwingung in einer Berührungsphase mit einem Eindringweg (P) größer als 100 Mikrometer in die Ankergabel (8) eindringt, und der Hebelstein (6) in einer Auslösungsphase mit einem Sicherheitsabstand (S) von mehr als 25 Mikrometern auf Abstand zur Ankergabel (8) bleibt, und dadurch, dass der Hebelstein (6) und die Ankergabel (8) bemessen sind, damit die Breite (L) der Ankergabel (8) größer als (P+S)/sin(a/2+β/2) ist, wobei der Eindringweg (P) und der Sicherheitsabstand (S) in Bezug auf die Hauptachse (DP) radial gemessen werden.
  6. Regelmechanismus (300) nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Anker (7) aus einer einzigen Silicium-Stufe ist, die auf eine Metallachse zurückgebracht wird, die in Bezug auf die Platine (1) gedreht wird.
  7. Regelmechanismus (300) nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Hemmungsdrehteil (4) ein Hemmungsrad aus Silicium ist.
  8. Regelmechanismus (300) nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass das Hemmungsdrehteil (4) ein Hemmungsrad ist, das durchbrochen ist, um dessen Trägheit in Bezug auf seine Drehachse zu minimieren.
  9. Regelmechanismus (300) nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass der Anker (7) durchbrochen ist, um dessen Trägheit (IA) in Bezug auf die Sekundärachse (DS) zu minimieren.
  10. Regelmechanismus (300) nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Anker (7) in Bezug auf die Sekundärachse (DS) symmetrisch ist.
  11. Regelmechanismus (300) nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die größte Abmessung des Trägheitselements (2) größer als die Hälfte der größten Abmessung der Platine (1) ist.
  12. Regelmechanismus (300) nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die Hauptachse (DP), die Sekundärachse (DS) und die Drehachse (DE) des Hemmungsdrehteils (4) entlang einer Ankörnung im rechten Winkel angeordnet sind, deren Scheitelpunkt die Sekundärachse (DS) ist.
  13. Regelmechanismus (300) nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass der flexible Mitnehmer zwei flexible Klingen (5) beinhaltet, die sich in Projektion auf eine Ebene senkrecht zur Hauptachse (DP) im Bereich der virtuellen Drehführungs, der die Hauptachse (DP) bildet kreuzen, und auf zwei parallelen und unterschiedlichen Niveaus befinden.
  14. Regelmechanismus (300) nach Anspruch 13, dadurch gekennzeichnet, dass die beiden flexiblen Klingen (5) zwischen sich in Projektion auf eine Ebene senkrecht zur Hauptachse (DP) einen Winkel bilden, der zwischen 59,5° und 69,5° enthalten ist, und einander zwischen 10,75 % und 14,75 % ihrer Länge kreuzen, um dem Resonator-Mechanismus (100) einen absichtlichen Isochronismus-Fehler entgegengesetzt zum Nachgehfehler bei der Hemmung des Hemmungsmechanismus (200) zu verleihen.
  15. Regelmechanismus (300) nach Anspruch 13 oder 14, dadurch gekennzeichnet, dass die beiden flexiblen Klingen (5) identisch sind und symmetrisch positioniert sind.
  16. Regelmechanismus (300) nach einem der Ansprüche 13 bis 15, dadurch gekennzeichnet, dass jede flexible Klinge (5) einer einteiligen Einheit (50) eines einzigen Teils mit seinen Ausricht- und Befestigungsmitteln an der Platine (1) oder an einer elastischen Zwischenaufhängungsklinge (9), die an der Platine (1) befestigt ist, angehört und angeordnet ist, um eine Verschiebung der flexiblen Führung und des Trägheitselements (2) in der Richtung der Hauptachse (DP) zu erlauben.
  17. Regelmechanismus (300) nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, dass mindestens der Resonator-Mechanismus (100) auf einer elastischen Zwischenaufhängungsklinge (9), die an der Platine (1) befestigt ist, und angeordnet ist, um eine Verschiebung des Resonator-Mechanismus (100) in der Richtung der Hauptachse (DP) zu erlauben, befestigt ist, und dadurch, dass die Platine (1) mindestens einen stoßsicheren Anschlag (11, 12) mindestens in der Richtung der Hauptachse (DP) beinhaltet, die angeordnet sind, um mit starren Elementen des Trägheitselements (2) zusammenzuwirken.
  18. Regelmechanismus (300) nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, dass das Trägheitselement (2) Gewichtchen zum Einstellen des Ganges und des Ungleichgewichts beinhaltet.
  19. Regelmechanismus (300) nach einem der Ansprüche 1 bis 18, dadurch gekennzeichnet, dass der Hebelstein (6) einteilig mit einer flexiblen Klinge (5) ist.
  20. Regelmechanismus (300) nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, dass der Anker (7) Auflageoberflächen beinhaltet, die angeordnet sind, um aufliegend mit Zähnen, die das Hemmungsdrehteil (4) beinhaltet, zusammenzuwirken, und um den Winkelweg des Ankers (7) zu begrenzen.
  21. Regelmechanismus (300) nach einem der Ansprüche 1 bis 20, dadurch gekennzeichnet, dass die flexible Führung aus oxidiertem Silicium ist, um die Wirkungen der Temperatur auf den Gang des Regelmechanismus (300) zu kompensieren.
  22. Uhrwerk (500), das Antriebsmittel (400) und einen Regelmechanismus (300) nach einem der Ansprüche1 bis 21 beinhaltet.
  23. Uhr (1000), die ein Uhrwerk (500) nach Anspruch 22, und/oder einen Regelmechanismus (300) nach einem der Ansprüche 1 bis 21 beinhaltet.
EP17752312.3A 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird Active EP3545368B1 (de)

Applications Claiming Priority (2)

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EP16200152.3A EP3327515B1 (de) 2016-11-23 2016-11-23 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
PCT/EP2017/069037 WO2018095592A1 (fr) 2016-11-23 2017-07-27 Résonateur rotatif à guidage flexible entretenu par un échappement libre à ancre

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EP3545368A1 EP3545368A1 (de) 2019-10-02
EP3545368B1 true EP3545368B1 (de) 2020-11-18

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EP16200152.3A Active EP3327515B1 (de) 2016-11-23 2016-11-23 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17745180.4A Active EP3545365B1 (de) 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17749674.2A Pending EP3545367A2 (de) 2016-11-23 2017-07-27 Durch eine freie hemmung mit palette aufrechterhaltener flexibel geführter rotierender resonator
EP17746073.0A Pending EP3545366A2 (de) 2016-11-23 2017-07-27 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
EP17745178.8A Pending EP3545363A2 (de) 2016-11-23 2017-07-27 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
EP17745179.6A Active EP3545364B1 (de) 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17752312.3A Active EP3545368B1 (de) 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17794727.2A Active EP3545369B1 (de) 2016-11-23 2017-11-07 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17803933.5A Pending EP3545370A2 (de) 2016-11-23 2017-11-22 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung

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EP16200152.3A Active EP3327515B1 (de) 2016-11-23 2016-11-23 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17745180.4A Active EP3545365B1 (de) 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17749674.2A Pending EP3545367A2 (de) 2016-11-23 2017-07-27 Durch eine freie hemmung mit palette aufrechterhaltener flexibel geführter rotierender resonator
EP17746073.0A Pending EP3545366A2 (de) 2016-11-23 2017-07-27 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
EP17745178.8A Pending EP3545363A2 (de) 2016-11-23 2017-07-27 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
EP17745179.6A Active EP3545364B1 (de) 2016-11-23 2017-07-27 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird

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EP17794727.2A Active EP3545369B1 (de) 2016-11-23 2017-11-07 Sich drehender resonator mit einer flexiblen führung, der von einer freien ankerhemmung gehalten wird
EP17803933.5A Pending EP3545370A2 (de) 2016-11-23 2017-11-22 Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung

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US (6) US11520289B2 (de)
EP (9) EP3327515B1 (de)
JP (6) JP6931392B2 (de)
CN (6) CN110023845B (de)
CH (1) CH713150A2 (de)
WO (8) WO2018095596A2 (de)

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US11675312B2 (en) 2023-06-13
US20190302695A1 (en) 2019-10-03
EP3545369B1 (de) 2020-11-04
JP2020501167A (ja) 2020-01-16
WO2018095596A2 (fr) 2018-05-31
CN110023846A (zh) 2019-07-16
CH713150A2 (fr) 2018-05-31
WO2018095997A3 (fr) 2018-08-30
WO2018099616A3 (fr) 2019-02-21
JP6828180B2 (ja) 2021-02-10
WO2018095596A3 (fr) 2018-09-13
JP2019536067A (ja) 2019-12-12
WO2018103978A2 (fr) 2018-06-14
JP2019536021A (ja) 2019-12-12
EP3545369A2 (de) 2019-10-02
JP2019537015A (ja) 2019-12-19
JP2019536038A (ja) 2019-12-12
US20190271945A1 (en) 2019-09-05
JP6931392B2 (ja) 2021-09-01
WO2018095593A2 (fr) 2018-05-31
EP3545365A1 (de) 2019-10-02
US20200064775A1 (en) 2020-02-27
JP6828179B2 (ja) 2021-02-10
CN109983410B (zh) 2020-09-29
CN110235064A (zh) 2019-09-13
EP3545363A2 (de) 2019-10-02
JP6931394B2 (ja) 2021-09-01
WO2018095594A1 (fr) 2018-05-31
WO2018103978A4 (fr) 2019-01-17
CN110023847A (zh) 2019-07-16
EP3327515A1 (de) 2018-05-30
US20190243308A1 (en) 2019-08-08
EP3545370A2 (de) 2019-10-02
EP3545365B1 (de) 2020-12-16
EP3545368A1 (de) 2019-10-02
WO2018095592A1 (fr) 2018-05-31
EP3545364B1 (de) 2020-10-28
US20190278227A1 (en) 2019-09-12
WO2018103978A3 (fr) 2018-11-29
EP3545366A2 (de) 2019-10-02
WO2018095997A4 (fr) 2018-11-01
US11619909B2 (en) 2023-04-04
WO2018095596A4 (fr) 2018-11-01
CN109983409B (zh) 2020-09-15
JP6810800B2 (ja) 2021-01-06
CN110023845B (zh) 2020-10-23
JP2019536034A (ja) 2019-12-12
US11493882B2 (en) 2022-11-08
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US11487245B2 (en) 2022-11-01
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US11520289B2 (en) 2022-12-06
US11467537B2 (en) 2022-10-11
WO2018095593A3 (fr) 2019-02-21
US20190369559A1 (en) 2019-12-05
WO2018095997A2 (fr) 2018-05-31
JP6931395B2 (ja) 2021-09-01
WO2018095595A1 (fr) 2018-05-31
EP3545367A2 (de) 2019-10-02
WO2018099616A2 (fr) 2018-06-07
CN109983409A (zh) 2019-07-05
CN110023846B (zh) 2020-11-03
EP3327515B1 (de) 2020-05-06
WO2018095997A9 (fr) 2019-08-15
EP3545364A1 (de) 2019-10-02
CN110023847B (zh) 2020-12-22
CN110235064B (zh) 2021-03-12

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