EP2090941B1 - Mechanischer Oszillator - Google Patents

Mechanischer Oszillator Download PDF

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Publication number
EP2090941B1
EP2090941B1 EP08101699A EP08101699A EP2090941B1 EP 2090941 B1 EP2090941 B1 EP 2090941B1 EP 08101699 A EP08101699 A EP 08101699A EP 08101699 A EP08101699 A EP 08101699A EP 2090941 B1 EP2090941 B1 EP 2090941B1
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EP
European Patent Office
Prior art keywords
balance
oscillator
zero
oscillator according
designed
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EP08101699A
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English (en)
French (fr)
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EP2090941A1 (de
Inventor
Pierre-Marcel Genequand
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Centre Suisse dElectronique et Microtechnique SA CSEM
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Centre Suisse dElectronique et Microtechnique SA CSEM
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Priority to EP08101699A priority Critical patent/EP2090941B1/de
Priority to US12/372,091 priority patent/US7963693B2/en
Publication of EP2090941A1 publication Critical patent/EP2090941A1/de
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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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/22—Compensation of changes in the motive power of the mainspring
    • 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

Definitions

  • the present invention relates to mechanical oscillators, especially those which equip the timepieces. It relates, more particularly, such an oscillator with a device for adjusting and correcting its frequency.
  • a first object of the invention is to provide an oscillator for a mechanical watch equipped with means for correcting the isochronism defect induced by the variations of the engine torque of the mainspring, according to a principle of correction as a function of the amplitude.
  • the object of the invention is to be able to maintain a constant frequency of the oscillator, in its useful range of operation, based on the amplitude variations to correct an effect comparable to a non-linearity of the spring of recall.
  • the present invention relates to a mechanical oscillator of the type comprising an oscillating system mounted on a frame and formed of a rocker and its return spring.
  • This oscillator further comprises a frequency correction device formed of at least a first and a second element respectively fixed to said frame and to the oscillating system, the first of these elements comprising a resilient flexible blade fixed by one of its ends and the second being a connecting member weighing, during part of the oscillation, against the free end of said blade.
  • the oscillator according to the invention may comprise only one flexible blade but, advantageously, it comprises two acting in opposition on the connecting member and offset, with respect to each other, a half-cycle of the oscillation, in order to symmetrize the characteristic of the return correction as a function of the deflection.
  • the single blade - or both blades - is fixed - or are fixed - to the frame via an interface allowing a position adjustment in translation and rotation.
  • the single blade - or both blades - is - or are - in contact, at a non-zero pressure, with the connecting member when the balance is in the neutral position, that is to say say when its angle relative to its rest position is equal to zero, so as to obtain an increase in the frequency when the amplitude decreases (negative correction).
  • the single blade - or the two blades - is - or is not - in contact, at a non-zero pressure, with the connecting member when the balance is in a neutral position, so that to obtain an increase of the frequency when the amplitude increases (positive correction).
  • the connecting member may be fixed to the balance either directly or by an intermediate piece of the return spring oscillating at a reduced deflection angle relative to that of the balance.
  • the oscillator may advantageously comprise a fixed stop located opposite the connecting member for a deflection angle of the balance relative to its rest position equal to zero, and intended to exert a prestress on said blade when said connecting member n is not in contact.
  • the oscillator for mechanical watch according to the invention is particularly applicable to the exhaust system described in the document EP 1 736 838 , already cited, in particular in Figure 2a.
  • a rocker 1 (partially shown) oscillating about its axis 2 and its return spring, or spiral spring, 3 fixed between the arm 1a of the beam and the frame 4 of the watch.
  • an escape wheel 5 is driven by two elastic blades 6 and 7, connected to the arm 1a of the balance 1 by one end and whose other end, or pallet, engages in the teeth (not shown) of the wheel exhaust 5.
  • the oscillating system By oscillating, under the impulse of a driving torque delivered by a mainspring, the oscillating system (balance 1 and spiral 3) rotates the escapement wheel 5 at a rate which must be as regular as possible, because he determines the accuracy of the watch he controls.
  • mechanical watches and, more particularly, those equipped with an exhaust system as just described suffer from a defect of isochronism that can result in a difference of about ten seconds a day for a variation of the engine torque of ten percent, corresponding to an amplitude variation of five percent.
  • the principle of the invention is to provide the oscillator with a correction device 20 having a frequency characteristic inverse to its own in the operating range.
  • the correction device 20 comprises two resilient blades 9 and 10 which bear, in opposition, on a connecting member or stop 8, T-shaped, connected to the arm 1 a of the balance 1, to the nearest of its center of rotation.
  • These elastic blades 9 and 10 are, via lugs 12 and 13, linked at their other end to a fixing and adjusting interface 11 by means of locking screws 15 and 16, respectively.
  • the interface 11, secured to the frame 4 by a screw 17, can be positioned relative to the axis 2 of the beam by moving it along a slide 14 of the frame against which it is applied under the action of a spring 18.
  • the interface 11 makes it possible to adjust the position of the fulcrum of the elastic blades 9 and 10 on the connecting member 8 and, therefore, their effective length and their stiffness.
  • the lugs 12 and 13 make it possible to adjust the orientation of these elastic blades with respect to the stop and, thereby, to adjust the angle of deflection of the rocker relative to its rest position for which they come in contact or leave. this same stop.
  • the position adjustment thus makes it possible to adjust the amplitude of the frequency variation, while the adjustment of the contact angle makes it possible to adjust the useful deflection range as well as the sign of the non-linearity.
  • the two elastic blades 9 and 10 are in contact with the stop 8 and they constitute an additional spring which acts on the balance in addition to the spiral spring 3. If the amplitude of the oscillations increases, it happens a moment when one of the blades ceases to be in contact with the stop, thus modifying the elastic constant of the overall return spring. This creates a negative non-linearity (i.e., a decrease in slope) in the response of this global return spring, as will be discussed later with respect to the figure 2 , and it is this non-linearity that makes it possible to compensate for the positive isochronism defect mentioned above (that is to say, a frequency which increases when the amplitude increases).
  • the frequency of the oscillator decreases as the maintenance torque and the oscillation amplitude decrease. It is therefore necessary to apply a negative compensation, that is to say produce a lower average return stiffness at high amplitudes.
  • the figure 2 shows the curve of the additional return moment generated by the blades as a function of the deflection angle of the balance relative to its rest position, that is to say the variation of the torque ⁇ M as a function of the deflection D.
  • the dotted upper curve is relative to the blade 10
  • the dotted lower curve is relative to the blade 9
  • the solid line curve is relative to the combined effect of the two blades.
  • the global curve versus deflection has a slope of 2. ⁇ K (K is the elastic constant of the global return spring) due to the action of two elastic strips 9 and 10 added to that of the spiral spring 3.
  • K is the elastic constant of the global return spring
  • the slope of the response curve is only ⁇ K, which corresponds to the fact that there is only one elastic blade (9 or 10) bearing on the abutment 8.
  • the slope 2. ⁇ K is constant.
  • the torque correction ⁇ M as a function of deflection is no longer linear and the average slope lies between 2. ⁇ K at small amplitudes and ⁇ K at large amplitudes.
  • the useful area of correction is in the vicinity, but outside, of the interval A-B.
  • ⁇ K E . b . h 3 / 4.
  • E the Young's modulus
  • b the width of the strip
  • L the effective length
  • R the pivoting radius of the stop.
  • E 200,000 N / mm 2 (for steel)
  • b is of the order of 0.5 mm
  • L 8 mm
  • R goal is 1 mm. It can therefore be deduced, using the preceding formulas, that the thickness h of the blade is of the order of 10 -5 m.
  • Such a blade can be cut into a sheet 10 microns thick and folded to allow attachment.
  • the figure 3 illustrates a variant of adjustment of the orientation of the elastic blades, in which they are positioned in such a way that they are not in contact with the stop when the balance is in the neutral position (deflection angle equal to zero) but contact for a deflection angle A or B. That is to say that ⁇ M is zero in the range between A and B and slope ⁇ M outside this range. Consequently, the frequency variation ⁇ f is the opposite of that described above and allows therefore to correct a negative dependence as a function of the driving torque.
  • the correction device can operate with a single elastic blade.
  • the overall curve (solid line) of the torque ⁇ M merges with one of the two dotted curves of the Figures 2 and 3 .
  • the answer is asymmetrical, the correction operating only on a single alternation of the oscillation of the balance.
  • the connecting member 8 is fixed, not on the rocker 1, but on an intermediate piece 19, T-shaped and serving as an anchor, whose horizontal bar 19a (on the figure) is the base of the elastic blades 6 and 7 and whose vertical bar 19b (in the figure) is mounted, free to oscillate, on the axis 2 of the balance 1.
  • the spiral spring 3 is then fixed between the arm 1 a pendulum and the vertical bar 19b, which is subject, moreover, to the action of two return springs 21, acting in opposition.
  • the provision of the figure 4 has the effect of reducing the angle of oscillation of the anchor 19 relative to that of the balance 1, which allows, on the one hand, to use more rigid blades and, on the other hand, to avoid excessive deformation and friction.
  • the figure 5 shows yet another variant with a fixed stop 22 linked to the frame 4 facing the abutment 8 for a deflection angle of the balance 1 relative to its rest position equal to zero.
  • This stop serves to connect and disconnect under prestressing the elastic blades 9 and 10 of the movable connecting member 8.
  • an oscillator advantageously usable in a mechanical timepiece, which is provided with means for correcting the defect of isochronism induced by the variations of the engine torque.
  • the correction performed is all the more effective as the amplitude-defect isochronism equilibrium is stable, which is the case of an elastic suspension balance such as, for example, that of the figure 5 of the document EP 1 736 838 , already quoted.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Springs (AREA)
  • Inductance-Capacitance Distribution Constants And Capacitance-Resistance Oscillators (AREA)

Claims (10)

  1. Mechanischer Oszillator, der ein auf einem Gestell (4) montiertes oszillierendes System umfasst, das von einer Wippe (1) und ihrer Rückholfeder (3) gebildet wird und weiterhin eine Frequenzkorrekturvorrichtung (20) aufweist, dadurch gekennzeichnet, dass die Frequenzkorrekturvorrichtung (20) von mindestens einem ersten und einem zweiten starren Element gebildet wird, die jeweils am Gestell (4) und am oszillierenden System befestigt sind, wobei das erste dieser Elemente mindestens ein flexibles elastisches Plättchen (9, 10) umfasst, das mit einem seiner Enden befestigt ist, wobei das zweite ein Verbindungsorgan (8) ist, das ausgebildet ist, um während eines Oszillationsabschnitts gegen das freie Ende des Plättchens zu drücken.
  2. Oszillator nach Anspruch 1, dadurch gekennzeichnet, dass das Plättchen (9, 10) ausgebildet ist, um bei einem Druck, der nicht null ist, bei einem Deflexionswinkel der Wippe (1) im Verhältnis zu ihrer Ruhestellung von gleich null mit dem Verbindungsorgan (8) in Berührung zu sein.
  3. Oszillator nach Anspruch 1, dadurch gekennzeichnet, dass das Plättchen (9, 10) ausgebildet ist, um bei einem Deflexionswinkel der Wippe (1) im Verhältnis zu ihrer Ruhestellung von gleich null mit dem Verbindungsorgan (8) nicht in Berührung zu sein.
  4. Oszillator nach Anspruch 1, dadurch gekennzeichnet, dass das erste der Elemente zwei elastische Plättchen (9, 10) umfasst, die ausgebildet sind, um in entgegengesetzter Abstützung und um eine halbe Oszillationsschwingung zueinander versetzt auf das Verbindungsorgan (8) einzuwirken.
  5. Oszillator nach Anspruch 4, dadurch gekennzeichnet, dass die Plättchen (9, 10) ausgebildet sind, um bei einem Druck, der nicht null ist, bei einem Deflexionswinkel der Wippe (1) im Verhältnis zu ihrer Ruhestellung von gleich null mit dem Verbindungsorgan (8) in Berührung zu sein.
  6. Oszillator nach Anspruch 4, dadurch gekennzeichnet, dass die Plättchen (9, 10) ausgebildet sind, um bei einem Deflexionswinkel der Wippe (1) im Verhältnis zu ihrer Ruhestellung von gleich null mit dem Verbindungsorgan (8) nicht in Berührung zu sein.
  7. Oszillator nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass der Verbindungsorgan (8) direkt an der Wippe (1) befestigt ist.
  8. Oszillator nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Verbindungsorgan (8) am oszillierenden System durch ein Verbindungsteil (19) der Rückholfeder (3) befestigt ist, das mit einem im Verhältnis zur Wippe (1) reduzierten Deflexionswinkel oszilliert.
  9. Oszillator nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass er einen starren Anschlag (22) aufweist, der sich bei einem Deflexionswinkel der Wippe (1) im Verhältnis zu ihrer Ruhestellung von gleich null gegenüber dem Verbindungsorgan (8) befindet und dazu bestimmt ist, eine Vorspannung auf das Plättchen auszuüben, wenn das Verbindungsorgan nicht in Berührung ist.
  10. Oszillator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass das elastische Plättchen (9, 10) mit einer Schnittstelle (11) am Gestell (4) befestigt ist, die die Einstellung ihrer Stellung durch Verschieben und Drehen erlaubt.
EP08101699A 2008-02-18 2008-02-18 Mechanischer Oszillator Active EP2090941B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08101699A EP2090941B1 (de) 2008-02-18 2008-02-18 Mechanischer Oszillator
US12/372,091 US7963693B2 (en) 2008-02-18 2009-02-17 Mechanical oscillator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08101699A EP2090941B1 (de) 2008-02-18 2008-02-18 Mechanischer Oszillator

Publications (2)

Publication Number Publication Date
EP2090941A1 EP2090941A1 (de) 2009-08-19
EP2090941B1 true EP2090941B1 (de) 2011-10-19

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US (1) US7963693B2 (de)
EP (1) EP2090941B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2553533B2 (de) † 2010-04-01 2019-06-19 Rolex S.A. Blockiervorrichtung für Zahnrad

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2105806B1 (de) * 2008-03-27 2013-11-13 Sowind S.A. Hemmungsmechanismus
EP2290476B1 (de) * 2009-08-18 2014-04-23 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Isochronismuskorrektor für Uhrhemmungsmechanismus und mit einem solchen Korrektor ausgestatteter Hemmungsmechanismus
WO2013144238A1 (fr) * 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à balancier sans plateau
US9075394B2 (en) * 2012-03-29 2015-07-07 Nivarox-Far S.A. Flexible escapement mechanism with movable frame
JP6661543B2 (ja) 2014-01-13 2020-03-11 エコール・ポリテクニーク・フェデラル・ドゥ・ローザンヌ （ウ・ペ・エフ・エル）Ｅｃｏｌｅ Ｐｏｌｙｔｅｃｈｎｉｑｕｅ Ｆｅｄｅｒａｌｅ Ｄｅ Ｌａｕｓａｎｎｅ （Ｅｐｆｌ） 脱進機のない、または簡易脱進機を有する一般２自由度等方性調和振動子および関連するタイムベース
RU2686446C2 (ru) * 2014-01-13 2019-04-25 Эколь Политекник Федераль Де Лозанн (Епфл) Изотропный гармонический осциллятор с по меньшей мере двумя степенями свободы и соответствующий регулятор с отсутствующим спусковым механизмом или с упрощенным спусковым механизмом
EP2911012B1 (de) * 2014-02-20 2020-07-22 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Oszillator einer Uhr
EP3076245B1 (de) 2015-04-02 2021-03-17 CSEM Centre Suisse D'electronique Et De Microtechnique SA Dämpfungsvorrichtung, insbesondere für mikromechanische uhrkomponente
FR3048792B1 (fr) * 2016-03-14 2019-07-19 Lvmh Swiss Manufactures Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif
US11029649B2 (en) 2016-03-14 2021-06-08 LVHM Swiss Manufactures SA Device for timepiece, clockwork movement and timepiece comprising such a device
FR3048791B1 (fr) 2016-03-14 2018-05-18 Lvmh Swiss Manufactures Sa Mecanisme pour piece d'horlogerie et piece d'horlogerie comprenant un tel mecanisme
EP3299905B1 (de) 2016-09-27 2020-01-08 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanischer oszillator für ein uhrwerk
JP7000585B2 (ja) * 2017-10-02 2022-01-19 マニュファクチュール・ドルロジュリ・オーデマ・ピゲ・ソシエテ・アノニム 回転錘と共通の反動力を持つ調和振動子を備えた時計設定装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2789414A (en) * 1947-08-28 1957-04-23 George S Andrews Automatic regulator for timepieces
DE10160287A1 (de) * 2001-12-07 2003-06-26 Lange Uhren Gmbh Tourbillon
FR2842313B1 (fr) * 2002-07-12 2004-10-22 Gideon Levingston Oscilliateur mecanique (systeme balancier et ressort spiral) en materiaux permettant d'atteindre un niveau superieur de precision, applique a un mouvement d'horlogerie ou autre instrument de precision
ATE389902T1 (de) 2005-06-23 2008-04-15 Suisse Electronique Microtech Uhr

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2553533B2 (de) † 2010-04-01 2019-06-19 Rolex S.A. Blockiervorrichtung für Zahnrad

Also Published As

Publication number Publication date
US20090207700A1 (en) 2009-08-20
US7963693B2 (en) 2011-06-21
EP2090941A1 (de) 2009-08-19

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