Nothing Special   »   [go: up one dir, main page]

EP3913441B1 - Oszillator für eine uhr - Google Patents

Oszillator für eine uhr Download PDF

Info

Publication number
EP3913441B1
EP3913441B1 EP20175995.8A EP20175995A EP3913441B1 EP 3913441 B1 EP3913441 B1 EP 3913441B1 EP 20175995 A EP20175995 A EP 20175995A EP 3913441 B1 EP3913441 B1 EP 3913441B1
Authority
EP
European Patent Office
Prior art keywords
oscillator
balance
hairspring
shaft
assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20175995.8A
Other languages
English (en)
French (fr)
Other versions
EP3913441A1 (de
Inventor
Séverine DOMANGE
Jean-Luc Bucaille
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Patek Philippe SA Geneve
Original Assignee
Patek Philippe SA Geneve
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Patek Philippe SA Geneve filed Critical Patek Philippe SA Geneve
Priority to EP20175995.8A priority Critical patent/EP3913441B1/de
Publication of EP3913441A1 publication Critical patent/EP3913441A1/de
Application granted granted Critical
Publication of EP3913441B1 publication Critical patent/EP3913441B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • G04B17/32—Component parts or constructional details, e.g. collet, stud, virole or piton
    • G04B17/34—Component parts or constructional details, e.g. collet, stud, virole or piton for fastening the hairspring onto the balance
    • G04B17/345—Details of the spiral roll
    • 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
    • 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

Definitions

  • the present invention relates to an oscillator for a timepiece comprising, on an axis, a balance, an escapement plate and a hairspring, the hairspring being mounted on the axis via a ferrule.
  • the present invention relates more particularly to such an oscillator whose isochronism is improved.
  • isochronism we mean variations in rate as a function of the amplitude of oscillation of the balance wheel and as a function of the position of the timepiece. The weaker these variations are, the more isochronous the oscillator.
  • the rate of such an oscillator with balance and hairspring is equal to the sum of the rate due to the lack of balance of the balance and the rate due to the hairspring.
  • the oscillator axis and the escapement plate, with its pin, contribute to the imbalance of the balance wheel.
  • the contribution of the ferrule to this lack of balance is, however, neglected because it is accepted that a ferrule must be as balanced as possible or as small as possible (see for example the work “Theory of Watchmaking” published by the Fédération des ijks Techniques, 1998, page 142 and the patent application EP 1584994 , paragraphs 2 and 6).
  • the lack of balance or unbalance of the balance disrupts the regularity of the oscillations.
  • the variations in rate due to the hairspring are mainly caused by the eccentric development and the weight of the hairspring.
  • the eccentric development of the hairspring generates a disruptive torque, the same in all positions, created by the restoring forces between the pivots of the oscillator axis and the bearings in which they rotate.
  • the weight of the hairspring generates another disruptive torque, depending on the inclination of the timepiece in relation to the horizontal position.
  • the unbalance of the balance of this oscillator is still relatively small (0.6 ⁇ g.cm in the first embodiment described).
  • a balance whose target unbalance is low is less easy to manufacture and adjust than a balance whose target unbalance is high.
  • the unbalance of the balance can be increased by compensating for it by increasing the radius of the ferrule, like the second embodiment set out in the patent application. WO 2017/163148 .
  • one increased ferrule radius at constant bulk and stiffness of the hairspring requires reducing the number of turns of the hairspring, and therefore the thickness of the turns, which increases the manufacturing dispersion, in particular the dispersion of the elastic torque, between different batches of hairsprings and even between hairsprings from the same batch.
  • the present invention aims to allow an increase in the unbalance of the balance wheel while at least partially compensating the movement due to the lack of balance of the balance by the movement due to the weight of the hairspring, this without requiring modification of the geometric and dimensional characteristics of the hairspring.
  • the unbalance of the ferrule is not neglected in the present invention.
  • the present invention even goes against the principle accepted in the state of the art according to which the ferrule must unbalance the balance as little as possible.
  • the ferrule according to the invention is deliberately unbalanced by a value (unbalance) which can be large and in a direction such that its unbalance partially compensates, or overcompensates, the unbalance of the axle-balance-plate assembly.
  • the lack of balance of the axis-balance-plate-ferrule assembly can compensate for the movement due to the weight of the balance spring, by analogy with the teaching of the patent application WO 2017/163148 , and the unbalance of the axle-balance-plate assembly can be high, thus facilitating the manufacture and adjustment of the balance. Furthermore, as all the organs carried by the oscillator axis are taken into account to determine the unbalance, the performance of the oscillator in terms of isochronism is improved.
  • the amplitude of oscillation at which the curves representing the movement 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 oscillation amplitude and therefore intersect at the same point.
  • the lack of balance of the axis-balance-plate-ferrule assembly and the geometry of the hairspring are such that the average slope of each curve among said curves representing the movement of the oscillator due to said defect equilibrium has substantially the same absolute value as the average slope of the corresponding curve among said curves representing the movement of the oscillator due to the weight of the hairspring, in the oscillation amplitude range of 150° to 280°.
  • the lack of balance of the axis-balance-plate-ferrule assembly and the geometry of the hairspring can be such that the maximum deviation in the course of the oscillator due to said lack of balance and the weight of the hairspring between said positions verticals in the oscillation amplitude range of 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 (ferrule radius) between the inner end of the hairspring and the center of rotation of the hairspring is preferably at most 800 ⁇ m, or even at most 700 ⁇ m, or even at most 600 ⁇ m.
  • the unbalance of the axle-balance-plate assembly is preferably at least 0.8 ⁇ g.cm, or even at least 1 ⁇ g.cm, or even at least 1.2 ⁇ g.cm, or even at least 1.4 ⁇ g.cm.
  • the unbalance of the ferrule is preferably at least 0.3 ⁇ g.cm, or even at least 0.4 ⁇ g.cm, or even at least 0.5 ⁇ g.cm, or even at least 0, 6 ⁇ g.cm, or even at least 0.7 ⁇ g.cm, or even at least 0.8 ⁇ g.cm, or even at least 0.9 ⁇ g.cm.
  • any range of values of the shell radius can be combined with any range of values of the unbalance of the axle-balance-plate assembly and/or with any range of values of the unbalance of the ferrule.
  • the inner turn of the hairspring has a stiffened portion and/or is shaped according to a Grossmann curve.
  • the outer turn of the hairspring can also have a stiffened portion.
  • the hairspring has a rigidity and/or a pitch which vary continuously over at least several turns.
  • the ferrule and/or the hairspring are made of a silicon-based material.
  • the present invention further proposes a watch movement comprising the oscillator defined above.
  • the present invention finally proposes a timepiece, such as a wristwatch or a pocket watch, comprising this watch movement or the oscillator defined above.
  • an oscillator for a watch movement intended to equip a timepiece such as a wristwatch or a pocket watch, comprises a balance wheel 1 mounted on a balance shaft 2 and a hairspring 3 whose inner end 3a is fixed to the balance axis 2 via a ferrule 4 and whose outer end 3b is fixed to the movement frame via one or more organs.
  • the outer end 3b of the balance spring 3 is extended by a rigid fixing part 5 which is held by a clamp 6 mounted on the movement frame, 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 eyebolt.
  • the assembly comprising the spring 3, the ferrule 4 and the rigid fixing part 5 can be monolithic and made for example of silicon or diamond, preferably of silicon covered with a layer of silicon oxide.
  • the oscillator also includes, mounted on the balance axis 2, an escapement plate 7 which can be single (without a small plate) or double (with a small notched plate 7a intended to cooperate with a stinger, as shown) , this escapement plate 7 comprising a washer 7b (“large plate”) and a plate pin 8 carried by the washer 7b and intended to cooperate in a conventional manner with the fork of an escape anchor.
  • the plate pin 8 can project out of the plane of the washer 7b, in the traditional manner, or extend radially from the periphery of the washer, as is also known.
  • the balance spring 3 does not have the traditional shape of an Archimedes spiral with a constant blade section.
  • the geometry of the hairspring is in fact irregular in the sense that it has a section and/or a pitch which vary along its blade.
  • a portion 3c of the outer turn hereinafter “external stiffened portion” and a portion 3d of the inner turn (hereinafter “inner stiffened portion”) have a larger section, therefore a greater great rigidity, than the rest of the blade forming the hairspring 3.
  • the section of the blade is constant.
  • the pitch of the hairspring 3 is constant from a point 3e' located on its inner turn to a point 3e located on its outer turn.
  • the terminal part 3f of the balance spring 3 extending between points 3e and 3b comprises at least a part of, typically all of, the external stiffened portion 3c.
  • the interior turn could be shaped according to a Grossmann curve.
  • the section instead of changing the section of the hairspring blade only locally at the level of the inner turn and the outer turn, the section could be continuously changed all along the blade or on several turns, this that is to say on a number (not necessarily integer) of turns greater than 1, for example equal to 2 or more.
  • the rigidity of the balance spring could be varied along its blade in a way other than by changing its section, for example by doping or heat treatment.
  • the rate of such an oscillator is equal to the sum of the disturbance due to the axis 2 - balance 1 - plate 7 - ferrule 4 assembly and the disturbance due to the balance spring 3.
  • the rigid assembly axis-balance-plate- ferrule which will be called “oscillating assembly” in the following, influences walking in vertical positions only.
  • the movement of the oscillator in vertical positions due to this oscillating assembly is caused by the lack of balance of the latter, that is to say by the fact that, due to manufacturing tolerances, the center of gravity of the oscillating assembly is not on the imaginary axis of rotation.
  • the unbalance A and the angular position ⁇ bv of the center of gravity G bv are parameters for adjusting the step due to the lack of balance of the oscillating assembly.
  • the hairspring influences walking in the horizontal position and in the vertical positions.
  • the eccentric development of the hairspring causes reactions in the bearings of the balance axis 2 which vary, this in all positions of the oscillator.
  • the displacement of the center of gravity of the hairspring caused by the eccentric development of the latter creates an isochronism defect due to the weight of the hairspring applied to said center of gravity. This disturbance is different from the elastic gravitational sagging effect of the hairspring, which is neglected in the present invention.
  • the curve representing the progress of the oscillator due to the lack of balance of the balance, more precisely of the oscillating assembly, as a function of the amplitude of oscillation of the balance, in any vertical position of this last passes through the zero value (i.e. crosses the abscissa axis) at an oscillation amplitude of 220°.
  • the curve representing the rate of the oscillator due to the weight of the hairspring as a function of the amplitude of oscillation of the balance wheel, in any vertical position of the latter passes through the zero value (i.e. crosses the abscissa 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, ⁇ bv of oscillating assemblies and geometries of hairsprings so that the movement due to the lack of balance of the oscillating assembly and the movement due to the weight of the hairspring compensate for each other, thus making it possible to reduce, or even make substantially zero, the differences in rate between the different vertical positions.
  • the hairspring 3 has 14 turns.
  • the thickness e 0 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 outer stiffened portion 3c and the inner stiffened portion 3d where it is bigger.
  • the step of the spiral between the 3rd' and 3rd points 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 with center O passing through the middle (at half the thickness e 0 ) of the inner end 3a, is 545 ⁇ m.
  • the maximum thickness e d of the interior stiffened portion 3d measured along a radius starting from the center of curvature Cd of the start of the interior turn (between points 3a and 3e'), is 73 ⁇ m.
  • the maximum thickness e c of the external stiffened 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 respectively 94° and of 110°.
  • ⁇ is the rate
  • m s is the mass of the hairspring
  • L is the length of the hairspring
  • E is the Young's modulus of the hairspring
  • I is the quadratic moment of the hairspring
  • g is the gravity constant
  • ⁇ is the elongation of the balance wheel relative to its equilibrium position
  • ⁇ 0 is the amplitude of the balance wheel relative to its equilibrium position
  • y g is the ordinate of the center of gravity of the hairspring in the frame (O, x, y) of the Figure 3 where the y-axis is opposite gravity
  • ⁇ denotes the derivative.
  • the displacement of the center of gravity of the hairspring was calculated by finite elements. The derivative and integral were then calculated numerically.
  • the curves S1 to S4 intersect at a point P1 located on the abscissa axis at an oscillation amplitude of approximately 218°, an amplitude which is therefore close to the oscillation amplitude of 220 ° at which the corresponding curves of a balance or an axis-balance-plate-ferrule assembly intersect.
  • the part of the hairspring 3 which has the most influence on the position of the crossing point P1 is the interior stiffened portion 3d.
  • the external stiffened portion 3c makes it possible to refine the adjustment of the crossing point P1, and/or to produce a running advance which compensates for a running delay caused by the exhaust as described in the patent applications WO 2013/034962 And WO 2014/072781 of the present plaintiff.
  • the crossing at or near point P1 occurs in all vertical positions of the oscillator.
  • FIG. 5 represents the operation of the oscillator 1, 2, 3, 4, 7 due to the lack of balance of the oscillating assembly 1, 2, 4, 7 as a function of the amplitude of oscillation of the balance 1 in each of the four aforementioned vertical positions of the oscillator, 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).
  • ⁇ is the rate
  • ⁇ 0 is the amplitude of the balance wheel relative to its equilibrium position
  • m bv is the mass of the oscillating assembly
  • g is the constant of gravity
  • d is the radial position of the center of gravity of the oscillating assembly
  • J bv is the moment of inertia of the oscillating assembly
  • ⁇ 0 is the natural pulsation of the oscillator
  • J 1 is the function of Bessel of order 1 (which vanishes for a value of ⁇ 0 of approximately 220°)
  • the diagram of the Figure 5 is that of an oscillating assembly having an unbalance A of 0.6 ⁇ g.cm and whose angular position ⁇ bv 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.
  • curves S1 and S2 decrease while curves B1 and B2 increase
  • curves S3 and S4 increase while curves B3 and B4 decrease. This is particularly true in the current operating range of a balance in the vertical position, namely the range of oscillation amplitudes of 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 amplitude range oscillation from 150° to 280°.
  • the adjustment of the slopes of curves B1 to B4 during the design of the oscillator is carried out by varying the unbalance A of the oscillating assembly and the angular position ⁇ bv of its center of gravity G bv .
  • varying the angular position ⁇ bv of the center of gravity of the oscillating assembly changes the relative position of curves B1 to B4. It is therefore appropriate to choose a value ⁇ bv so that the order of curves B1 to B4 (according to their slope) is the opposite of that of curves S1 to S4.
  • varying the unbalance A increases or decreases the slope of each curve B1 to B4, which makes it possible to optimize the degree of compensation between the oscillating assembly and the hairspring.
  • FIG. 6 shows the rate of the oscillator due to the lack of balance of the oscillating assembly and the weight of the balance spring (sum of the rate due to the lack of balance of the oscillating assembly and the rate due to the weight of the balance spring) in each of the four aforementioned vertical positions, 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 shroud 4 of the oscillator is unbalanced - its center of gravity is not on the imaginary axis of rotation - and the shroud 4 comprises for this purpose one or more unbalancing parts 4a.
  • the position of the center of gravity of the shroud 4 is such that partial compensation takes place between the unbalance of the axle-balance-plate assembly 1, 2, 7 and the unbalance of the shroud 4.
  • This partial compensation allows the oscillating assembly 1, 2, 4, 7 (axis-balance-plate-shell) to have for example the unbalance value A of 0.6 ⁇ g.cm mentioned above (and the angle ⁇ bv of 60° ) to compensate for the movement due to the weight of the balance spring 3, and to the axis-balance-plate assembly 1, 2, 7 to have a greater unbalance, such as an unbalance of at least 0.8 ⁇ g.cm , or even at least 1 ⁇ g.cm, or even at least 1.2 ⁇ g.cm, or even at least 1.4 ⁇ g.cm.
  • the unbalance of the axle-balance-plate assembly and the angular position of its center of gravity can be adjusted by milling the balance or by turning adjustment screws and/or weights which equip the balance.
  • the ferrule can be manufactured very precisely, with a controlled balance fault, for example by deep reactive ion etching known as DRIE.
  • the unbalance of the ferrule is preferably at least 0.3 ⁇ g.cm, preferably at least 0.4 ⁇ g.cm, preferably at least 0.5 ⁇ g.cm, preferably at least least 0.6 ⁇ g.cm, preferably at least 0.7 ⁇ g.cm, preferably at least 0.8 ⁇ g.cm, preferably at least 0.9 ⁇ g.cm. It is typically between 0.8 and 1 ⁇ g.cm.
  • the first term of this inequality represents the unbalance of the oscillating assembly (i.e. the quantity A mentioned previously) while the second term represents the unbalance of the axis-balance-plate assembly.
  • the vector m bv . OG bv represents the lack of balance of the oscillating assembly and the vector m b . OG b represents the lack of balance of the axis-balance-platter assembly.
  • FIG. 7 illustrates different cases conforming to the invention.
  • the vectors m v . OG v and m b . OG b are collinear and in opposite directions and the unbalance m v ⁇ OG v ⁇ of the ferrule is smaller than the unbalance m b ⁇ OG b ⁇ of the axle-balance-platter assembly.
  • the unbalance of the axle-balance-plate assembly is partially compensated by that of the shell and can be very high.
  • the vectors m v . OG v and m b are collinear and in opposite directions and the unbalance m v ⁇ OG v ⁇ of the ferrule. This is the preferred case.
  • the unbalance of the axle-balance-plate assembly is partially compensated by that of the shell and can be very high.
  • the vectors m v . OG v and m b are collinear and in opposite directions and the unbalance m v
  • OG b are not collinear but the vector m v . OG v presents a component oriented in the opposite direction to the vector m b . OG b .
  • the unbalance of the axle-balance-plate assembly is partially compensated by that of the shell and can be high.
  • the vectors m v . OG v and m b . OG b are collinear and in opposite directions and the unbalance m v ⁇ OG v ⁇ of the ferrule is greater than the unbalance m b ⁇ OG b ⁇ of the axle-balance-platter assembly.
  • the unbalance of the axle-balance-plate assembly is overcompensated by that of the shell and can be raised, provided that the unbalance of the shell is itself high.
  • ferrule radius R will preferably remain at most 800 ⁇ m, or even at most 700 ⁇ m, or even at most 600 ⁇ m in the present invention.
  • unbalancing parts 4a To bring the desired lack of balance to the ferrule 4, it is possible to play on its geometry by forming unbalancing parts 4a during its manufacture. It is also possible, as a variant or in addition to the unbalancing parts 4a, to add material to the ferrule, for example by PVD (physical vapor deposition), CVD (chemical vapor deposition) or brazing.
  • PVD physical vapor deposition
  • CVD chemical vapor deposition
  • the unbalancing parts 4a can advantageously consist of peripheral protrusions separated from a central elastic clamping part 4b of the ferrule 3 by interstices 4c in the form of slots so as not to substantially modify the elasticity of the central part 4b and therefore the holding of the ferrule 4 on the balance axis 2.
  • These peripheral protrusions can also advantageously be separated from one another or from each other by one or more interstices in the form of slots 4d.
  • the present invention makes it possible to obtain a watch oscillator whose operating differences between the different vertical positions are minimal and which lends itself well to industrial production thanks to the increase in the unbalance of the axis-balance-plate assembly which 'she makes it possible.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Micromachines (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (16)

  1. Oszillator für Uhr, der auf einer Achse (2) eine Unruh (1), ein Hemmungsschale (7) und eine Spiralfeder (3) umfasst, wobei die Spiralfeder (3) mittels einer Spiralrolle (4) auf der Achse (2) montiert ist, wobei die Achse-Unruh-Schale-Spiralrolle-Anordnung einen Gleichgewichtsfehler aufweist, wobei der Gleichgewichtsfehler und die Geometrie der Spiralfeder derart sind, dass
    a) die Kurven (S1 bis S4), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder in Abhängigkeit von der Schwingungsamplitude der Uhruh in mindestens vier vertikalen Positionen des Oszillators darstellen, die um 90° beabstandet sind, jeweils bei einer Schwingungsamplitude der Uhruh von zwischen 200° und 240° durch den Wert null verlaufen:
    b) zwischen der Schwingungsamplitude von 150° und der Schwingungsamplitude von 280° die Kurven (B1 bis B4), die den Gang des Oszillators aufgrund des Gleichgewichtsfehlers der Achse-Uhruh-Schale-Spiralrolle-Anordnung in Abhängigkeit von der Schwingungsamplitude der Uhruh in den vertikalen Positionen des Oszillators darstellen, jeweils eine mittlere Steigung mit Vorzeichen aufweisen, das der mittleren Steigung der entsprechenden Kurve unter den Kurven (S1 bis S4) entgegengesetzt ist, die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen,
    wobei in dem Oszillator die folgende Ungleichung erfüllt ist: m bv ‖ OG bv → ‖ < m b ‖ OG b → ‖
    Figure imgb0007
     wo mbv die Masse der Achse-Uhruh-Schale-Spiralrolle-Anordnung ist, O der Drehmittelpunkt dieser Anordnung in der Orthogonalprojektion in einer Ebene senkrecht zur Achse (2) ist, Gbv der Schwerpunkt der Achse-Uhruh-Schale-Spiralrolle-Anordnung in der Orthogonalprojektion in der Ebene ist, mb die Masse der Achse-Unruh-Schale-Anordnung ist und Gb der Schwerpunkt der Achse-Uhruh-Schale-Anordnung in der Orthogonalprojektion in der Ebene ist.
  2. Oszillator nach Anspruch 1, dadurch gekennzeichnet, dass die Geometrie der Spiralfeder derart ist, dass die Kurven (S1 bis S4), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen, jeweils bei einer Schwingungsamplitude der Uhruh von zwischen 210 und 230° durch den Wert null verlaufen.
  3. Oszillator nach Anspruch 2, dadurch gekennzeichnet, dass die Geometrie der Spiralfeder derart ist, dass die Kurven (S1 bis S4), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder darstellen, jeweils bei einer Schwingungsamplitude der Uhruh von zwischen 215° und 225° durch den Wert null verlaufen.
  4. Oszillator nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Gleichgewichtsfehler der Achse-Uhruh-Schale-Spiralrolle-Anordnung und die Geometrie der Spiralfeder derart sind, dass die mittlere Steigung von jeder Kurve unter den Kurven (B1 bis B4), die den Gang des Oszillators aufgrund des Gleichgewichtsfehlers darstellen, im Wesentlichen den gleichen Absolutwert aufweist wie die mittlere Steigung der entsprechenden Kurve unter den Kurven (S1 bis S4), die den Gang des Oszillators aufgrund des Gewichts der Spiralfeder im Bereich von Schwingungsamplituden von 150° bis 280° darstellen.
  5. Oszillator nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Gleichgewichtsfehler der Achse-Unruh-Schale-Spiralrolle-Anordnung und die Geometrie der Spiralfeder derart sind, dass die Höchstabweichung des Gangs des Oszillators aufgrund des Gleichgewichtsfehlers und des Gewichts der Spiralfeder zwischen den vertikalen Positionen im Schwingungsamplitudenbereich von 150° bis 280° kleiner als 4 Sekunden/Tag, vorzugsweise 2 Sekunden/Tag, ferner vorzugsweise 1 Sekunde/Tag, ferner vorzugsweise 0,7 Sekunde/Tag, ist.
  6. Oszillator nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Abstand (R) zwischen dem unteren Ende (3a) der Spiralfeder (3') und dem Drehmittelpunkt (O) der Spiralfeder (3') höchstens 800 µm, vorzugsweise höchstens 700 pm, vorzugsweise höchstens 600 µm, beträgt.
  7. Oszillator nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Unwucht mb ∥ OGb ∥ der Achse-Unruh-Schale-Anordnung mindestens 0,8 pg.cm, vorzugsweise mindestens 1 pg.cm, vorzugsweise mindestens 1,2 µg.cm, vorzugsweise mindestens 1,4 µg.cm, beträgt.
  8. Oszillator nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Unwucht mv ∥ OGv ∥ der Spiralrolle (4), wo mv die Masse der Spiralrolle (4) und Gv der Schwerpunkt der Spiralrolle (4) in der Orthogonalprojektion in der Ebene ist, mindestens 0,3 µg.cm, vorzugsweise mindestens 0,4 µg.cm, vorzugsweise mindestens 0,5 µg.cm, vorzugsweise mindestens 0,6 µg.cm, vorzugsweise mindestens 0,7 µg.cm, vorzugsweise mindestens 0,8 µg.cm, vorzugsweise mindestens 0,9 µg.cm, beträgt.
  9. Oszillator nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Spiralrolle (4) mindestens eine Ausstülpung (4a) zum Aus-dem-Gleichgewicht-Bringen umfasst, die von einem elastischen Teil (4b) der Spiralrolle (4), der die Welle (2) elastisch einklemmt, durch mindestens einen vorzugsweise schlitzförmigen Spalt (4c) getrennt ist.
  10. Oszillator nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die innere Windung der Spiralfeder (3; 3') einen versteiften Abschnitt (3d) aufweist und/oder entlang einer Grossmann-Kurve angepasst ist.
  11. Oszillator nach Anspruch 10, dadurch gekennzeichnet, dass die äußere Windung der Spiralfeder (3; 3') einen versteiften Abschnitt (3c) aufweist.
  12. Oszillator nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Spiralfeder eine Steifigkeit und/oder einen Schritt aufweist, die sich über mindestens mehrere Windungen ununterbrochen ändern.
  13. Oszillator nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Spiralrolle (4) aus einem Material auf Siliziumbasis besteht.
  14. Oszillator nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass die Spiralfeder (3) aus einem Material auf Siliziumbasis besteht.
  15. Uhrwerk, das einen Oszillator nach einem der Ansprüche 1 bis 14 umfasst.
  16. Uhr, wie beispielsweise Armbanduhr oder Taschenuhr, die einen Oszillator nach einem der Ansprüche 1 bis 14 oder ein Uhrwerk nach Anspruch 15 umfasst.
EP20175995.8A 2020-05-22 2020-05-22 Oszillator für eine uhr Active EP3913441B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20175995.8A EP3913441B1 (de) 2020-05-22 2020-05-22 Oszillator für eine uhr

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20175995.8A EP3913441B1 (de) 2020-05-22 2020-05-22 Oszillator für eine uhr

Publications (2)

Publication Number Publication Date
EP3913441A1 EP3913441A1 (de) 2021-11-24
EP3913441B1 true EP3913441B1 (de) 2024-05-01

Family

ID=70804488

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20175995.8A Active EP3913441B1 (de) 2020-05-22 2020-05-22 Oszillator für eine uhr

Country Status (1)

Country Link
EP (1) EP3913441B1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4293428A1 (de) 2022-06-14 2023-12-20 Patek Philippe SA Genève Spirale für resonator einer uhr

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8047705B2 (en) * 2006-02-09 2011-11-01 The Swatch Group Research And Development Ltd Anti-shock collet

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1445670A1 (de) 2003-02-06 2004-08-11 ETA SA Manufacture Horlogère Suisse Spiralfeder der Resonatorunruh und Fabrikationsmethode
EP1473604B1 (de) 2003-04-29 2010-06-23 Patek Philippe SA Genève Unruh- und fläche Spiralfederregulator für Uhrwerk
DE602004019183D1 (de) 2004-04-06 2009-03-12 Nivarox Sa Spiralrolle ohne Deformation des Fixierungsradius der Spiralfeder und Herstellungsverfahren derartige Spiralrolle
CH700805B1 (fr) 2005-10-25 2010-10-29 Patek Philippe Sa Geneve Dispositif régulateur pour pièce d'horlogerie et mouvement d'horlogerie comprenant un tel dispositif.
CH702708B1 (fr) * 2007-04-27 2011-08-31 Sigatec S A Ensemble oscillateur balancier-spiral avec éléments détachables et procédé d'ajustement de sa fréquence d'oscillation.
CH701846B8 (fr) 2009-09-21 2015-06-15 Rolex Sa Spiral plat pour balancier d'horlogerie et ensemble balancier-spiral.
CH705471B1 (fr) 2011-09-07 2016-03-31 Patek Philippe Sa Geneve Mouvement d'horlogerie à balancier-spiral.
US10120341B2 (en) * 2012-06-26 2018-11-06 Rolex Sa Method for determining an imbalance characteristic of an oscillator
CH707165B1 (fr) 2012-11-07 2016-12-30 Patek Philippe Sa Geneve Mouvement d'horlogerie à balancier-spiral.
JP6991154B2 (ja) 2016-03-23 2022-01-12 パテック フィリップ ソシエテ アノニム ジュネーブ 時計用のテンプ－ヒゲゼンマイ振動子

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8047705B2 (en) * 2006-02-09 2011-11-01 The Swatch Group Research And Development Ltd Anti-shock collet

Also Published As

Publication number Publication date
EP3913441A1 (de) 2021-11-24

Similar Documents

Publication Publication Date Title
EP3433680B1 (de) Unruh-spiralfeder-oszillator für eine uhr
EP2102717B1 (de) Mechanischer oszillator für uhr
EP2215531B1 (de) Mechanischer oszillator mit einem optimierten thermoelastischen koeffizienten
EP2455825B1 (de) Verfahren zur Paarung und Angleichung einer Untereinheit einer Uhr
WO2015189278A2 (fr) Oscillateur pour un ensemble de balancier-spiral d&#39;une pièce d&#39;horlogerie
EP3181940B1 (de) Herstellungsverfahren einer spiralfeder mit einer vorbestimmten steifigkeit durch lokalisierte wegnahme von material
CH709291A2 (fr) Oscillateur de pièce d&#39;horlogerie.
WO2011026725A1 (fr) Ressort spiral
EP2690506B1 (de) Antischwingungsspirale für Uhr
EP3913441B1 (de) Oszillator für eine uhr
EP3792700B1 (de) Oszillator einer uhr mit flexiblem zapfen
EP1654597B1 (de) Unruh mit thermokompensation
EP2753985B1 (de) Uhrwerk mit unruh und spiralfeder
CH713409B1 (fr) Balancier pour balancier-spiral du type thermocompensé, balancier-spiral du type thermocompensé, mouvement et pièce d&#39;horlogerie.
EP3037893B1 (de) Mikromechanische Komponente oder Uhr mit flexiblem Führungsdraht
EP3485334B1 (de) Verfahren zur gangeinstellung einer uhr
CH716331B1 (fr) Arbre horloger à pivot dont le coefficient de frottement est réduit.
EP4179391A1 (de) Oszillator einer uhr mit flexiblem zapfen
CH701155B1 (fr) Oscillateur pour pièce d&#39;horlogerie.
EP3391154B1 (de) Schwingsystem für eine uhr
WO2023242746A1 (fr) Spiral pour résonateur horloger
EP3534222A1 (de) Herstellungsverfahren eines thermokompensierten oszillators
WO2020144587A1 (fr) Organe régulateur pour mouvement horloger
CH710581B1 (fr) Ressort spiral et son procédé de fabrication.
CH706760A2 (fr) Mécanisme et spiral d&#39;horlogerie anti-galop.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

B565 Issuance of search results under rule 164(2) epc

Effective date: 20201103

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20220516

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230521

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20231204

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602020029935

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240802

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240902

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1683196

Country of ref document: AT

Kind code of ref document: T

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20240903

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240902

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240801

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240901

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240802

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240501

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20240801