EP3433680B1 - Unruh-spiralfeder-oszillator für eine uhr - Google Patents

Unruh-spiralfeder-oszillator für eine uhr Download PDF

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Publication number
EP3433680B1
EP3433680B1 EP17712250.4A EP17712250A EP3433680B1 EP 3433680 B1 EP3433680 B1 EP 3433680B1 EP 17712250 A EP17712250 A EP 17712250A EP 3433680 B1 EP3433680 B1 EP 3433680B1
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EP
European Patent Office
Prior art keywords
balance
oscillator
hairspring
curves
curve
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EP17712250.4A
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English (en)
French (fr)
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EP3433680A1 (de
Inventor
Jean-Luc Bucaille
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Publication of EP3433680A1 publication Critical patent/EP3433680A1/de
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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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G—PHYSICS
    • G04—HOROLOGY
    • G04D—APPARATUS OR TOOLS SPECIALLY DESIGNED FOR MAKING OR MAINTAINING CLOCKS OR WATCHES
    • G04D7/00—Measuring, counting, calibrating, testing or regulating apparatus
    • G04D7/10—Measuring, counting, calibrating, testing or regulating apparatus for hairsprings of balances
    • 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
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/063—Balance construction
    • 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
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/066—Manufacture of the spiral spring
    • 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
    • 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
    • G04D—APPARATUS OR TOOLS SPECIALLY DESIGNED FOR MAKING OR MAINTAINING CLOCKS OR WATCHES
    • G04D7/00—Measuring, counting, calibrating, testing or regulating apparatus
    • G04D7/08—Measuring, counting, calibrating, testing or regulating apparatus for balance wheels

Definitions

  • the present invention relates to an oscillator of the balance-spring type for a timepiece, more particularly such an oscillator whose isochronism is improved.
  • isochronism is meant the variations of the gearing as a function of the amplitude of oscillation of the balance and as a function of the position of the timepiece. The smaller these variations, the more isochronous the oscillator.
  • the walking of a balance-spring oscillator is equal to the sum of the walking due to the balance imbalance and the walking due to the balance spring.
  • the lack of balance or unbalance of the balance disturbs the regularity of the oscillations.
  • Gait variations due to the hairspring are mainly caused by the eccentric development and the weight of the hairspring.
  • the eccentric development of the balance spring generates a disturbing torque, the same in all positions, created by the restoring forces between the pivots of the oscillator shaft and the bearings in which they rotate.
  • the weight of the balance spring generates another disturbing torque, a function of the inclination of the timepiece relative to the horizontal position.
  • the patent application WO 2014/001341 describes a method for determining and modifying an unbalance characteristic of an oscillator or spiral balance assembly.
  • the present invention aims to propose another approach to improve the isochronism of a balance-spring oscillator and in particular to reduce the gait differences between its different vertical positions.
  • the present invention proposes to design the balance and the balance spring in such a way that the step due to the lack of balance of the balance and the step due to the weight of the balance spring compensate at least partially and preferably substantially entirely in all or almost all the normal operating range of the balance wheel. Contrary to the state of the art, there is therefore no attempt in the present invention to cancel the imbalance of the pendulum, the latter may even be high. Likewise, no attempt is made to minimize walking due to weight of hairspring. This new approach makes it possible to obtain very small step deviations between the different vertical positions of the oscillator and therefore improves the precision of the timepiece.
  • the amplitude of oscillation at which the curves representing the march of the oscillator due to the weight of the hairspring pass through zero may be slightly different from one curve to another.
  • said curves pass through zero at the same amplitude of oscillation and therefore intersect at the same point.
  • the balance imbalance and balance spring geometry are such that the average slope of each curve among said curves representing the walking of the oscillator due to the balance imbalance has substantially the same absolute value as the average slope of the corresponding curve among said curves representing the walking of the oscillator due to the weight of the hairspring, in the range of oscillation amplitudes from 150 ° to 280 °.
  • the balance imbalance of the balance and the geometry of the balance spring can be such that the maximum deviation of the walking of the oscillator due to the balance imbalance and the weight of the balance spring between said vertical positions in the amplitude range oscillation from 150 ° to 280 ° is less than 4 seconds / day, or even 2 seconds / day, or even 1 second / day, or even 0.7 seconds / day.
  • the distance between the inner end of the hairspring and the center of rotation of the hairspring can be greater than 500 ⁇ m, or even 600 ⁇ m, or even 700 ⁇ m.
  • the balance imbalance can be greater than 0.5 ⁇ g.cm or even 1 ⁇ g.cm.
  • the inner coil of the hairspring has a stiffened portion and / or is shaped according to a Grossmann curve.
  • the outer turn of the balance spring may also have a stiffened portion.
  • the hairspring has a rigidity and / or a pitch which vary continuously over at least several turns.
  • a balance-spring oscillator for a watch movement intended for equip a timepiece such as a wristwatch or a pocket watch, comprises a pendulum 1 mounted on a pendulum axis 2 and a hairspring 3 whose inner end 3a is fixed to the pendulum axis 2 by via a ferrule 4 and the outer end 3b of which is fixed to the frame of the movement by means of one or more members.
  • the outer end 3b of the hairspring 3 is extended by a rigid fixing part 5 which is held by a clamp 6 mounted on the frame of the movement, as described in the patent EP 1780611 of the plaintiff.
  • the outer end 3b could however be fixed to the frame in another way, for example by means of a traditional peg.
  • the assembly comprising the hairspring 3, the ferrule 4 and the rigid fixing part 5 can be monolithic and produced for example from silicon or diamond.
  • the pendulum axis 2 also carries a plate or double plate 7 itself carrying a plate pin 8 and forming part of an exhaust serving to maintain and count the oscillations of the oscillator.
  • Spiral 3 does not have the traditional form of an Archimedes spiral with a constant blade section.
  • the geometry of the hairspring is indeed irregular in the sense that it has a section and / or a pitch which vary along its blade.
  • a portion 3c of the outer coil hereinafter “exterior rigidified portion” and a 3d portion of the interior coil (hereinafter “interior rigidified portion”) have a larger section, therefore a greater great rigidity, that the rest of the blade forming the hairspring 3. Outside these portions 3c and 3d the section of the blade is constant.
  • the pitch of hairspring 3 is constant from a point 3e 'located on its inner turn to a point 3e located on its outer turn.
  • the end part 3f of the hairspring 3 extending between the points 3e and 3b comprises at least a part of, typically all, the external stiffened portion 3c.
  • the inner coil could be shaped according to a Grossmann curve.
  • the inner coil instead of changing the section of the hairspring blade only locally at the level of the inner and outer turns, one could continuously change the section all along the blade or on several turns, it that is to say on a number (not necessarily an integer) of turns greater than 1, for example equal to 2 or more.
  • the step of a balance-spring oscillator is equal to the sum of the step due to the balance and the step due to the balance spring.
  • the pendulum influences walking in vertical positions only.
  • the walking of the oscillator due to the pendulum is caused by the balance imbalance of the pendulum, that is to say by the fact that, due to manufacturing tolerances, the center of gravity of the pendulum is not on the axis of rotation of the latter.
  • the unbalance A of the pendulum and the angular position ⁇ b of its center of gravity G are gait adjustment parameters due to a lack of balance in the balance.
  • the hairspring influences the walking in the horizontal position and in the vertical positions.
  • the eccentric development of the balance spring causes in the bearings of the balance axis reactions which vary, this in all the positions of the oscillator.
  • the displacement of the center of gravity of the balance spring caused by the eccentric development of the latter creates an isochronism defect due to the weight of the balance spring applied to said center of gravity. This disturbance is different from the elastic gravitational collapse effect of the hairspring, which is neglected in the present invention.
  • the curve representing the walking of the oscillator due to the balance imbalance as a function of the amplitude of oscillation of the balance, in any vertical position of the latter passes through the value zero (c (i.e. crosses the abscissa axis) at an oscillation amplitude of 220 °.
  • the curve representing the march of the oscillator due to the weight of the hairspring as a function of the amplitude of oscillation of the pendulum, in any vertical position of the latter passes through the value zero (that is to say crosses the x-axis) at oscillation amplitudes of 163.5 ° and 330.5 °.
  • the present invention is based on the observation that it is possible to choose parameters A, ⁇ b of pendulums and spiral geometries so that the gait due to the balance imbalance and the gait due to the weight of the hairspring compensate each other, thus making it possible to reduce, or even to make substantially zero, the walking differences between the different vertical positions.
  • hairspring 3 has 14 turns.
  • the thickness eo of the blade forming the hairspring measured along a radius starting from the center of rotation O of the hairspring, is 28.1 ⁇ m, except along the stiffened outer portion 3c and the stiffened inner portion 3d where it is bigger.
  • the hairspring pitch between points 3e 'and 3e is 86.8 ⁇ m.
  • the radius R of the ferrule 4, or distance between the inner end 3a of the hairspring and the center O, defined as the radius of the circle of center O passing through the middle (at half the thickness eo) of the end interior 3a, is 545 ⁇ m.
  • the maximum thickness e d of the interior rigidified portion 3d measured along a radius starting from the center of curvature Cd from the start of the interior turn (between points 3a and 3e '), is 73 ⁇ m.
  • the maximum thickness e c of the external rigidified portion 3c measured along a radius starting from the center of curvature Cc of the terminal part 3f of the hairspring 3, is 88 ⁇ m.
  • the angular extent ⁇ c and the angular position ⁇ c (position of its center relative to the outer end 3b of the hairspring 3) of the outer stiffened portion 3c, measured from the center of curvature Cc, are 94 ° and 110 °.
  • the curves S1 to S4 intersect at a point P1 located on the abscissa axis at an oscillation amplitude of approximately 218 °, amplitude which is therefore close to the oscillation amplitude of 220 ° at which the corresponding curves of a pendulum intersect.
  • the part of hairspring 3 which has the most influence on the position of the crossing point P1 is the stiffened inner portion 3d.
  • the external stiffened portion 3c makes it possible to refine the adjustment of the crossing point P1, and / or to produce a walking advance which compensates for a walking delay caused by the exhaust as described in the patent applications. WO 2013/034962 and WO 2014/072781 of this plaintiff.
  • the crossing at point P1 or in the vicinity of point P1 occurs in all the vertical positions of the oscillator.
  • the figure 5 represents the operation of the oscillator 1, 2, 3 due to the balance imbalance of the balance 1 as a function of the amplitude of oscillation of the balance 1 in each of the aforementioned four vertical positions of the oscillator, namely the vertical position high VH (curve B1), the right vertical position VD (curve B2), the left vertical position VG (curve B3) and the low vertical position VB (curve B4).
  • ⁇ is the step
  • ⁇ 0 is the amplitude of the balance with respect to its equilibrium position
  • M b is the mass of the balance
  • g is the constant of gravity
  • d is the radial position of the center of gravity of the pendulum
  • J b is the moment of inertia of the pendulum
  • est 0 is the proper pulsation of the oscillator
  • J 1 is the Bessel function of order 1 (which s canceled for a value of ⁇ 0 of approximately 220 °)
  • the diagram of the figure 5 is that of a pendulum with an unbalance A of 0.6 ⁇ g.cm and whose angular position ⁇ b of the center of gravity is 60 °.
  • the slope, in particular the average slope, of each curve B1 to B4 is of opposite sign to that of the slope, in particular the average slope, of each curve S1 to S4 respectively.
  • the curves S1 and S2 decrease while the curves B1 and B2 increase
  • the curves S3 and S4 increase while the curves B3 and B4 decrease. This is particularly true in the current operating range of a pendulum in a vertical position, namely the range of oscillation amplitudes from 150 ° to 280 °.
  • the average slope of each curve S1 to S4 has substantially the same absolute value as the average slope of the corresponding curve B1 to B4 in the range of oscillation amplitudes from 150 ° to 280 °.
  • the slopes B1 to B4 are adjusted during the design of the oscillator by varying the unbalance A of the balance and the angular position bal b of its center of gravity.
  • varying the angular position ⁇ b of the balance center of gravity changes the relative position of the curves B1 to B4. It is therefore advisable to choose a value ⁇ b so that the order of the curves B1 to B4 (according to their slope) is the reverse of that of the curves S1 to S4.
  • varying the unbalance A increases or decreases the slope of each curve B1 to B4, which optimizes the degree of compensation between the balance and the balance spring.
  • the figure 6 shows the walking of the oscillator due to the balance imbalance and the weight of the balance spring (sum of the walking due to the balance imbalance and the walking due to the weight of the balance spring) in each of the four vertical positions mentioned above , namely the high vertical position VH (curve J1), the right vertical position VD (curve J2), the left vertical position VG (curve J3) and the low vertical position VB (curve J4).
  • VH curve J1
  • VD curve J2
  • V3 the left vertical position VG
  • VB low vertical position VB
  • the unbalance A and the angular position ⁇ b of the center of gravity can be adjusted by milling and / or by means of adjustment screws which equip the balance and / or by means of weights which equip the balance .
  • the increase in unbalance A results in an increase in the slope of the curves B1 to B4.
  • the figure 9 shows the operation of the oscillator 1, 2, 3 'due to the balance imbalance of the balance 1 as a function of the amplitude of oscillation of the balance 1 in each of the four vertical positions mentioned above, namely the high vertical position VH ( curve B1 '), the right vertical position VD (curve B2'), the left vertical position VG (curve B3 ') and the low vertical position VB (curve B4').
  • the diagram of the figure 9 was obtained with a balance having an unbalance A of 1.25 ⁇ g.cm and whose angular position ⁇ b of the center of gravity is 55 °. It can be seen that the slopes of the curves S1 'to S4' and the slopes of the curves B1 'to B4' allow a gait compensation between the balance 1 and the hairspring 3 '.
  • the figure 10 shows the walking of the oscillator 1, 2, 3 'due to the balance balance 1 and the weight of the balance spring 3' (sum of the walking due to the balance 1 balance and the walking due to the weight spiral 3 ') in each of the four vertical positions mentioned above, namely the high vertical position VH (curve J1'), the right vertical position VD (curve J2 '), the left vertical position VG (curve J3') and the position vertical low VB (curve J4 '). It can be noted that the path deviations between these vertical positions are very small, the maximum path deviation in the range of oscillation amplitudes from 150 ° to 280 ° being less than 0.7 s / d.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Springs (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Electric Clocks (AREA)
  • Cosmetics (AREA)
  • Micromachines (AREA)
  • Testing Of Balance (AREA)

Claims (10)

  1. Oszillator für Uhren, der eine Unruh (1) und eine Spiralfeder (3; 3') umfasst, wobei die Unruh eine Unwucht aufweist, wobei die Unwucht der Unruh und die Geometrie der Spiralfeder derart sind, dass:
    a) die Kurven (S1 bis S4; S1' bis S4'), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder in Abhängigkeit von der Schwingungsweite der Unruh in mindestens vier vertikalen Positionen des Oszillators darstellen, die um 90° beabstandet sind, den Wert Null jeweils bei einer Schwingungsweite der Unruh durchqueren, die zwischen 200° und 240° beträgt;
    b) zwischen der Schwingungsweite von 150° und der Schwingungsweite von 280° die Kurven (B1 bis B4; B1' bis B4'), die den Gang des Oszillators aufgrund der Unwucht der Unruh in Abhängigkeit von der Schwingungsweite der Unruh in den vertikalen Positionen des Oszillators darstellen, jeweils eine mittlere Steigung aufweisen, deren Vorzeichen der mittleren Steigung der entsprechenden Kurve unter den Kurven (S1 bis S4; S1' bis S4') entgegengesetzt ist, die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen.
  2. Oszillator nach Anspruch 1, dadurch gekennzeichnet, dass die Geometrie der Spiralfeder derart ist, dass die Kurven (S1 bis S4; S1' bis S4'), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen, den Wert Null jeweils bei einer Schwingungsweite der Unruh durchqueren, der zwischen 210° und 230° beträgt.
  3. Oszillator nach Anspruch 2, dadurch gekennzeichnet, dass die Geometrie der Spiralfeder derart ist, dass die Kurven (S1 bis S4; S1' bis S4'), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen, den Wert Null jeweils bei einer Schwingungsweite der Unruh durchqueren, die zwischen 215° und 225° beträgt.
  4. Oszillator nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Unwucht der Unruh und die Geometrie der Spiralfeder derart sind, dass die mittlere Steigung von jeder Kurve unter den Kurven (B1 bis B4; B1' bis B4'), die den Gang des Oszillators aufgrund der Unwucht der Unruh darstellen, im Wesentlichen den gleichen Absolutwert wie die durchschnittliche Steigung der entsprechenden Kurve unter den Kurven (S1 bis S4; S1' bis S4'), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen, im Schwingungsweitenbereich von 150° bis 280° aufweist.
  5. Oszillator nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Unwucht der Unruh und die Geometrie der Spiralfeder derart sind, dass die maximale Abweichung des Gangs des Oszillators aufgrund der Unwucht der Unruh und des Gewichts der Spiralfeder zwischen den vertikalen Positionen in dem Schwingungsweitenbereich von 150° bis 280° kleiner als 4 Sekunden/Tag, vorzugsweise 2 Sekunden/Tag, noch mehr zu bevorzugen 1 Sekunde/Tag, noch mehr zu bevorzugen 0,7 Sekunde/Tag ist.
  6. Oszillator nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Abstand (R) zwischen dem inneren Ende (3a) der Spiralfeder (3') und dem Drehpunkt (O) der Spiralfeder (3') größer als 500 µm, vorzugsweise größer als 600 µm, noch mehr zu bevorzugen größer als 700 µm ist.
  7. Oszillator nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Ungleichgewicht der Unruh größer als 0,5 µg.cm, vorzugsweis größer als 1 µg.cm ist.
  8. Oszillator nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die innere Windung der Spiralfeder (3; 3') einen versteiften Abschnitt (3d) aufweist und/oder gemäß einer Grossmann-Kurve angepasst ist.
  9. Oszillator nach Anspruch 8, dadurch gekennzeichnet, dass die äußere Windung der Spiralfeder (3; 3') einen versteiften Abschnitt (3c) aufweist.
  10. Oszillator nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Spiralfeder eine Steifigkeit und/oder eine Steigung aufweist, die sich über mindestens mehrere Windungen kontinuierlich ändert bzw. ändern.
EP17712250.4A 2016-03-23 2017-03-15 Unruh-spiralfeder-oszillator für eine uhr Active EP3433680B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16161964 2016-03-23
PCT/IB2017/051480 WO2017163148A1 (fr) 2016-03-23 2017-03-15 Oscillateur balancier-spiral pour piece d'horlogerie

Publications (2)

Publication Number Publication Date
EP3433680A1 EP3433680A1 (de) 2019-01-30
EP3433680B1 true EP3433680B1 (de) 2020-04-29

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EP17712250.4A Active EP3433680B1 (de) 2016-03-23 2017-03-15 Unruh-spiralfeder-oszillator für eine uhr

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US (1) US11249440B2 (de)
EP (1) EP3433680B1 (de)
JP (1) JP6991154B2 (de)
KR (1) KR102305812B1 (de)
CN (1) CN108885426B (de)
SG (1) SG11201806735QA (de)
WO (1) WO2017163148A1 (de)

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EP3913441B1 (de) 2020-05-22 2024-05-01 Patek Philippe SA Genève Oszillator für eine uhr
EP3968097A1 (de) * 2020-09-09 2022-03-16 Nivarox-FAR S.A. Uhrenreihe und ihr herstellungsverfahren
EP4293428A1 (de) 2022-06-14 2023-12-20 Patek Philippe SA Genève Spirale für resonator einer uhr
EP4372479A1 (de) * 2022-11-18 2024-05-22 Richemont International S.A. Verfahren zur herstellung von uhrenspiralfedern

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Publication number Publication date
JP6991154B2 (ja) 2022-01-12
KR102305812B1 (ko) 2021-09-29
US20190049900A1 (en) 2019-02-14
US11249440B2 (en) 2022-02-15
WO2017163148A1 (fr) 2017-09-28
JP2019509492A (ja) 2019-04-04
CN108885426A (zh) 2018-11-23
SG11201806735QA (en) 2018-09-27
KR20180127367A (ko) 2018-11-28
EP3433680A1 (de) 2019-01-30
CN108885426B (zh) 2020-10-27

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