EP3252545A1 - Uhrenmechanismus zum einstellen der unruhträgheit - Google Patents

Uhrenmechanismus zum einstellen der unruhträgheit Download PDF

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Publication number
EP3252545A1
EP3252545A1 EP16172841.5A EP16172841A EP3252545A1 EP 3252545 A1 EP3252545 A1 EP 3252545A1 EP 16172841 A EP16172841 A EP 16172841A EP 3252545 A1 EP3252545 A1 EP 3252545A1
Authority
EP
European Patent Office
Prior art keywords
outer ring
balance
inner flange
ring
shaft
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.)
Granted
Application number
EP16172841.5A
Other languages
English (en)
French (fr)
Other versions
EP3252545B1 (de
Inventor
Lionel Paratte
Donald William Corson
Dominique Léchot
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.)
Swatch Group Research and Development SA
Original Assignee
Swatch Group Research and Development SA
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 Swatch Group Research and Development SA filed Critical Swatch Group Research and Development SA
Priority to EP16172841.5A priority Critical patent/EP3252545B1/de
Priority to JP2017082591A priority patent/JP6313882B2/ja
Priority to CN201710408233.9A priority patent/CN107463082B/zh
Priority to US15/613,791 priority patent/US10222748B2/en
Publication of EP3252545A1 publication Critical patent/EP3252545A1/de
Priority to HK18107285.9A priority patent/HK1247998A1/zh
Application granted granted Critical
Publication of EP3252545B1 publication Critical patent/EP3252545B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • G04B18/00—Mechanisms for setting frequency
    • G04B18/006—Mechanisms for setting frequency by adjusting the devices fixed on the balance
    • 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
    • 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
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • 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
    • 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
    • G04D7/082—Measuring, counting, calibrating, testing or regulating apparatus for balance wheels for balancing
    • G04D7/084—Measuring, counting, calibrating, testing or regulating apparatus for balance wheels for balancing by setting adjustable elements, e.g. balance wheel screws

Definitions

  • the invention relates to a timepiece with inertia adjustment, comprising a shaft bearing on the one hand a serge via at least one arm, and on the other hand an inner flange fixed on said shaft and bearing directly or indirectly an outer ring with, between said inner flange and said outer ring, a plurality of first elastic guide links balanced in a plane perpendicular to the axis of said shaft.
  • the invention also relates to a mechanical clockwork movement comprising at least one clock oscillator mechanism comprising such a balance.
  • the invention also relates to a watch comprising such a movement, and a control member consisting of a pusher or a ring arranged to control through a sliding pinion the movement of a timer.
  • the invention also relates to a watch assembly comprising such a watch, and a setting tool arranged to allow the inertia adjustment of said balance.
  • the invention relates to the field of mechanical clockwork movements with pendulum oscillator, and the gait adjustment of such an oscillator.
  • the document CH 708 675 A1 in the name of Sercalo Microtechnology Ltd has a monolithic structure in "LIGA” -metal (Lith react, Galvanoformung und Abformung) or "DRIE” -Si (Deep Reactive Ion Etchning), with several elastic blades between an inner fixing rhomb and a ring slightly outer elliptical, which can be fixed by elastic forces inside a serge.
  • the march is performed by rotating the outer elastic ellipse with tweezers, which moves the blades away from the center, and changes the inertia.
  • there is no built-in adjustment tool Even using silicon technology to achieve a very high manufacturing accuracy of this part, the positioning of the elliptical ring being performed at two points, unbalance may appear.
  • the invention proposes to develop a solution to adjust the running of a mechanical movement, without having to open the watch case, and without introducing unbalance.
  • the solution proposed preferably uses the high precision of silicon micro-fabrication, or the like, to minimize any imbalances introduced during the adjustment, and especially to propose a solution allowing to make the adjustment without having to disassemble the watch, with adjustment means integrated into the movement.
  • the invention relates to a timepiece with inertia adjustment, comprising a shaft carrying on the one hand a serge via at least one arm, and on the other hand an inner flange fixed on said shaft and bearing directly or indirectly an outer ring with, between said inner flange and said outer ring, a plurality of first guide elastic bonds balanced in a plane perpendicular to the axis of said shaft, according to claim 1.
  • the invention also relates to a mechanical clockwork movement comprising at least one clock oscillator mechanism comprising such a balance.
  • the invention also relates to a watch comprising such a movement, and a control member, in particular pre-existing, consisting of a pusher or a ring arranged to control through a sliding pinion the movement of a timer.
  • the invention also relates to a watch assembly comprising such a watch, and a setting tool arranged to allow the inertia adjustment of said balance.
  • the invention proposes a solution for adjusting the running of a mechanical movement, without opening the watch case, with an inertia adjusting device concerning both a specially equipped oscillator, and accessible control means. to a user from outside the watch case, for example by the winding and setting rod, a push, or other.
  • a watch 1000 comprising a mechanical movement 300, itself comprising at least one oscillator 100 comprising at least one balance 10, in particular a balance-balance oscillator, comprising a balance 10 and at least one spiral 18.
  • the inertia adjustment device comprises a flexible structure of balance inertia adjustment.
  • the invention relates to a balance wheel 10 with inertia adjustment, comprising a shaft 11 which carries at least one serge 12 via at least one arm 13.
  • This balance 10 comprises at least one inner flange 1 fixed on the shaft 11, and at least one outer ring 2, which is distinct from the serge 12.
  • these first elastic guide links 3 are balanced in a plane perpendicular to the axis B of the shaft 11, so that the shaft 11 is positioned exactly in the center of inertia the structure to avoid unbalance, especially in the case where the inner flange 1 and the outer ring 2 are part of the same monobloc structure.
  • This outer ring 2 is arranged to pivot relative to the inner flange 1, under the action of an external torque exerted against a resistant torque exerted by these first elastic guide links 3.
  • the balance 10 comprises a plurality of weights 4.
  • the invention is described more particularly in the simple case where the balance has a single inner flange 1, a single outer ring 2, and is easy to extrapolate for a multi-stage construction.
  • any rotation of the outer ring 2 relative to the inner flange 1 changes the angular position of these weights 4.
  • the indexing means in position 6, and the complementary indexing means in position 7 comprise teeth. It is still conceivable to perform indexing magnetic type, or other.
  • the balance 10 comprises a plurality of weights 4.
  • each of the weights 4 is carried at least by the inner flange 1 by at least one second elastic connection 5 and each indexable in a stable angular position defined by the cooperation between a first indexing toothing 91 carried by the inner flange 1 or the flyweight 4, and a second indexing toothing 92.
  • This second indexing gear 92 is carried by the flyweight 4 or by the outer ring 2 when the first indexing toothing 91 is carried by the inner flange 1, or is carried by the outer ring 2 when the first indexing tooth 91 is carried by the flyweight 4.
  • each counterweight 4 is carried by the outer ring 2.
  • the figure 1 is a watch 10 according to the invention, which comprises, in a first upper plane PS an outer ring 2, carrying a peripheral toothing 8, and resiliently mounted relative to an inner flange 1 integral with the 11 of the balance wheel 10.
  • the balance 10 comprises, in a second lower plane PI and parallel to the first upper plane PS, a support surface and angular support of the balance, which consists, or an outer surface 120 of the serge 12 of the balance 10, or in a toothing 15 of a lower board 14, or the like; the lower plate 14 is shown with a lower elastic connection 16 with a hub 17 fixed on the shaft 11.
  • This rocker 10 is shown facing an operating member 20 according to the invention, which comprises, at the level of the upper plane PS a control means 80, in particular carrying a control gear, in particular in the form of a driving wheel 81, arranged to cooperate with the peripheral toothing 8 of the outer ring 2, and at the lower plane PI complementary means 150 of support and holding, arranged to cooperate with the outer surface 120 of the serge 12 in particular by frictional elastic support, or the toothing 15 of the lower board 14 by locking meshing.
  • a control means 80 in particular carrying a control gear, in particular in the form of a driving wheel 81, arranged to cooperate with the peripheral toothing 8 of the outer ring 2, and at the lower plane PI complementary means 150 of support and holding, arranged to cooperate with the outer surface 120 of the serge 12 in particular by frictional elastic support, or the toothing 15 of the lower board 14 by locking meshing.
  • a lower board 14 is fixed to the shaft 11 of the balance beam, while a monobloc top board 30 is fixed at its center to the shaft 11 of the balance, but can rotate in its outside.
  • Centering springs relative to the shaft 11 of the balance advantageously made in the form of elastic strips 19, visible on the figure 17 , make it possible to cancel any unintentional unbalance introduced by one or other of the lower boards 14 or greater 30 added. Care should be taken to judiciously adapt the number of elastic blades to the type of material.
  • the rigidity of the monocrystalline silicon is anisotropic, and which, for example, in the case of a perpendicular to the crystal plane ⁇ 100> has an azimuthal period of 90 °, this number should be even and equal to or greater than 4. In the case of an isotropic material, this number may be odd and equal to or greater than 3.
  • the centers of these boards are preferably fixed permanently by means such as, but not limited to, a bonding or brazing.
  • the resilient blades pinching the shaft 11 of the balance must exert a friction greater than the maximum torque exerted on the outer ring 2 during the adjustment of inertia.
  • the operating member 20 used to control the inertia adjustment advantageously comprises a setting device for limiting this printed torque to the outer ring 2.
  • the rocker 10 comprises a monoblock top board 30 which comprises the inner flange 1, the first elastic guide links 3, the outer ring 2, the weights 4, the second elastic links 5, the first teeth of indexing 91, and the second indexing teeth 92, and the third elastic links 50 when the balance 10 comprises.
  • the inner flange 1 comprises a plurality of resilient blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque.
  • the inner flange 1 is irreversibly fixed to the shaft 11, by welding, brazing, bonding, or other similar process.
  • the inner flange 1 comprises a plurality of resilient blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque, and these resilient blades 19 are fixed irreversibly on the shaft 11, by welding, brazing, gluing, or other similar process.
  • the rocker 10 comprises a lower plate 14 fixed directly or indirectly to the shaft 11 and having peripheral stop means 15, such as than a toothing or the like.
  • the outer ring 2 comprises a peripheral and continuous toothing 8 oriented on the axis B of the shaft 11, and the rotation of the toothing 8 modifies the position of the weights 4 between two stable indexing positions.
  • the inner flange 1 is integral with the shaft 11.
  • the rocker 10 embeds a flexible monolayer and micro-machined structure, taking advantage of the high precision of contour "MEMS" technologies, typically 1 to 2 micrometers of positioning accuracy, for a thickness of 150 microns, constituting a monoblock top board 30 as defined above.
  • the boards are micro-machined (techniques from manufacturing on silicon) and if possible each in a single layer (mask process), as shown.
  • the rocker 10 When the rocker 10 has a lower plate 14, it can also be performed in a "MEMS" technology or the like.
  • FIGS. 2 to 11 illustrate variants of flexible inertia adjustment mechanisms, according to the invention, in an advantageous but non-limiting embodiment comprising a monobloc top board 30.
  • the outer ring 2 in particular provided with a toothing 8 in the preferred embodiment illustrated, can pivot elastically relative to its center, which is fixed to the balance shaft 11 as explained above.
  • Angular portions of 180 °, 120 °, 90 °, 72 °, ..., and the number of respectively 2, 3, 4, 5, ..., are arranged between the center and the outer ring 2. They are responsible for carrying out the two main functions, ie the guiding for example with elastic blades, and the inertia adjustment for example with movable weights.
  • these functions are alternated by angular sector, or integrated if it is possible.
  • the rule of adaptation of the number of sectors to the material, mentioned above for the number of centering blades also applies here.
  • FIGS. 2 and 3 illustrate two variants, at 120 ° and at 180 °, of an upper board 30 comprising, between the inner flange and the outer ring, an alternation of first elastic bonds filling the rotational guiding function, and interposed between the previous ones , weights each elastically suspended.
  • the first indexing toothing 91 is carried by the inner flange 1 and is constituted by an inner jumper 42 protruding radially
  • the second indexing toothing 92 is carried by the flyweight 4 and is a first gear sector 43.
  • This flyweight is suspended by a connection with three first necks 45, 21, 41, which together define an isosceles triangle ACC 'symmetrical with respect to a perpendicular to a radial end of the axis B of the beam 10, between two radial arm sections, l one resulting from the inner flange 11, and the other coming from the outer ring 2.
  • the flyweight 4 in the form of a circle sector can rotate elastically at C, during the angular displacement of the outer ring 2, moved by the triangle of C'-AC elastic pivots.
  • the inner jumper 42 cooperates in holding stop with teeth of the toothed sector 43, and allows the precise positioning of the weight 4.
  • a registration graduation 93 on the weight 4 allows the reading of its angular position. Correct sizing of the mechanism causes the synchronized displacement in the same notches of all weights, at the risk of causing an imbalance.
  • An alternative consists of a mechanism comprising a single jumper and a single indexing rack for the complete structure, with a compensation weight to reduce the center of gravity to the center of rotation of the balance.
  • the first indexing toothing 91 is carried by the weight 4 and comprises at least one tooth 46
  • the second indexing teeth 92 is carried by the outer ring 2 and comprises at least a second toothed sector 72 of distinct center of the shaft B of the shaft 11.
  • the weight 4 is a disc having two opposite teeth 46, attached by a flexible blade 47 perpendicular to a radial arm 49 from the inner flange 1.
  • the outer ring 2 carries, on tracks, RA and RB rays, non-concentric with the axis B of the balance 10, which makes it possible to modify the inertia, two toothed sectors 72, with which the two teeth 46 of the flyweight 4.
  • the change in inertia comes from the change in the radial position of the flyweight 4, which itself results from the change of relative angular position between the flyweight and the outer ring 2, via the slope corresponding to the radius RB or RA.
  • This second variant comprises, like the first, a bidirectional range of adjustment. It should be noted that in neutral position, in both solutions there is no tightening / constraint between jumper and rack, the space will be as thin as one can micro-machine slots in a monolayer process (a single photolithographic mask). This space (type 5 micrometers for 0.10 mm thick) can of course be reduced to 0 or less (constrained state) for the other angular positions.
  • the figure 7 illustrates a guiding mechanism with flexible blades, in a variant where the inner flange 1 carries radial arms which themselves, by means of radial elastic blades 31 with two second necks 34 each, an intermediate concentric sector 33 which is suspended by means of two other radial resilient blades 32 with two second necks 34 each, to the outer ring 2.
  • the outer ring 2 is suspended on two intersecting blades in the center, fixed on the intermediate bend 33, which is - even connected to the inner flange 1.
  • figure 8 illustrates the articulated connection at the second necks, for a half-structure with the four second necks 34 replaced by pivots K'L'M'N '. It is clear that the instantaneous center of rotation for small amplitudes is at the axis B of the shaft 11 of the balance 10.
  • the figure 9 illustrates a mechanism in which the inertia adjustment and the guidance are alternated by sectors of 60 °, substantially according to the variants respectively of the Figures 6 and 7 .
  • the modification of inertia comes from the change in the radial position of the flyweight 4, which itself results from the change of relative angular position between the weight and the outer ring 2, via the slope corresponding to the radius RB or RA.
  • pairs consisting, on the one hand of radial elastic blades 31 seen above, and also springs 36, mounted radially, for the reduction of the elastic torque of recall.
  • each spring 36 consists of half-springs 361, provided with hooks 362 presented head to tail, remote from each other during the development of the one-piece board 30, as visible in the left part of the figure, and it then suffices to hang to form a hitch 363 to obtain the required return force.
  • the figure 11 illustrates the variation of the elastic torque CE as a function of the deformation angle ⁇ , in solid lines without these springs, and in broken line with these springs.
  • the first indexing gear 91 is carried by the inner flange 1 and has a third gear sector 44 whose center is distinct from the axis B of the shaft 11, and the second indexing gear 92 is carried by the outer ring 2, and is constituted by an outer jumper 29.
  • the rocker 10 here comprises a monobloc upper board 30 which is a flexible planetary structure whose planets are unbalanced weights allowing the adjustment of inertia, which are linked to the inner flange 1 and / or to the outer ring 2 by means of elastic blades.
  • the inner flange 1 directly carries non-concentric toothed sectors 44 with the axis B of the balance 10, each indexed in position by an outer jumper 29 secured to the outer ring 2, and the weights 4 are each connected to both the inner flange 1 and the outer ring 2, by resilient blades 48 substantially concentric with each other and with the axis B of the shaft 11.
  • This third variant functions as a planetary movement, in which the two flyweights 4 (planets) roll between the inner flange 1 and the outer ring 2, which are held together by these elastic blades 48 which wind around the flyweights 4.
  • the elastic return torque due to the resilient blades 48 may vary, in particular but not necessarily increase.
  • FIG. figure 18 Another embodiment, of the second family of variants, is illustrated in FIG. figure 18 : It is a central spiral inertia adjustment structure, in which the pivoting is not elastic, but made by friction on supports, here three centering supports.
  • the balance wheel 10 with inertia adjustment comprises a shaft 11 carrying on the one hand a serge 12 via at least one arm 13, and on the other hand an inner flange 1 fixed on this shaft 11 and carrying, directly or indirectly, an outer ring 2, with, between the inner flange 1 and outer ring 2, a plurality of first elastic guide links 3, which are balanced in a plane perpendicular to the B-axis of the shaft 11.
  • the outer ring 2 is distinct from the serge 12, and is arranged to pivot relative to the inner flange 1 under the action of an external torque exerted against a resistant torque exerted by the first elastic guide links 3.
  • This balance 10 comprises a plurality of weights 4, each carried by the outer ring 2 by means of at least one outer flexible blade 94, and each indexable in a stable angular position defined by the cooperation between a first indexing teeth 91 carried by the inner flange 1 and a second indexing teeth 92 which is carried by the flyweight 4. Any rotation of the outer ring 2 relative to the inner flange 1 changes the angular position of the flyweights 4.
  • the outer ring 2 comprises bearings 52 bearing guide lands 52 that includes the inner flange 1. Each bearing 5 is deployed on an angular sector corresponding to the adjustment range of the balance 10.
  • the supports 52 that includes the inner flange 1 are advantageously located at the end of arm 51 substantially radial with respect to the axis B of the shaft 11. In a particular embodiment, these arms 51 are flexible, but are less s flexible as the outer flexible blades 94.
  • the inner flange 1 comprises, as the first indexing toothing 91, a toothed spiral 44 fixed to the shaft 11 of the balance 10, formed here of three notched sections of evolutive radial dimension, while the outer ring 2 carries weights 4, three in number in this non-limiting example, each secured by means of at least one outer flexible blade 94.
  • the outer ring 2 here comprises three bearing surfaces 53 on which slide three supports 52, on an angular sector of 30 °, corresponding to the adjustment range, which comprise arms 51 of the toothed spiral 44.
  • the rotation relative between the outer ring 2 and the toothed spiral 44, with which cooperate teeth 55, at the second indexing teeth 92 of each weight 4 causes the centro-symmetric deployment of the weights 4.
  • a monobloc top board 30 made of silicon with a diameter of 7.9 mm and a thickness of 150 micrometers, a total inertia of 1.83 . 10 -9 kg.m 2 , the run setting corresponding to the 30 ° amplitude setting reaches 37.4 seconds per day.
  • the notches of the toothed spiral 44 can of course be adapted and reduced, in particular to achieve a requested resolution of, for example, 0.5 seconds per day.
  • this mechanism also comprises vertical guide elements to ensure the Z-resistance of the outer ring 2, not shown in the figure.
  • the supports 52 for centering the outer ring 2 and the bearing surfaces 53 are advantageously far from a non-zero clearance of a value of a few micrometers, and adapted to guarantee the simultaneous fall of the jumpers of the balance wheel 10 during a tangential adjustment.
  • the flyweights 4 which perfectly center the outer ring 2 to the notched spiral 44, itself centered on the shaft 11 by flexible blades 19.
  • the function arm 51 is to ensure that the teeth 55 of the three weights 4 fall synchronously into their toothed spiral notches 44, so that there is no offset. As a result, the torque exerted by the blades via these notches is higher than the friction torque at the end of the fall of the weights in the notches.
  • this rocker 10 comprises a one-piece board which comprises the outer ring 2, the weights 4, the outer flexible blades 94 and the second indexing teeth 92.
  • the inner flange 1 comprises a plurality elastic blades 19 concentrically tightening the shaft 11 with a friction torque greater than the maximum value of the external torque. In another embodiment, this inner flange 1 is irreversibly fixed on the shaft 11.
  • this embodiment can be realized with a number of different elements.
  • the invention also relates to a 300 mechanical clockwork movement, such as visible in particular on the figure 20 , comprising at least one clock oscillator mechanism 100 comprising such a rocker 10, and an actuator 20 arranged to control the inertia adjustment of the balance 10 by changing the position of at least some of the weights 4 that includes the This operating member 20 is movable between an engaged position and at least one disengaged position.
  • the operating member 20 comprises a stop means 160 arranged to immobilize directly or indirectly the serge 12 in the engaged position, and at least one control means 80, in particular toothed, arranged for, in the position engaged, rotate the outer ring 2, including a toothing 8 that includes the outer ring 2, to change the position of the weights 4 with which cooperates the outer ring 2.
  • the invention also concerns, as can be seen in particular on the figure 20 , a watch 1000 comprising such a movement 300, a control member constituted by a pusher or a ring gear 110 arranged to control through a sliding pinion 111 the movement of a timer 112.
  • This timer 112 comprises a wheel 115, which is arranged to drive at least one such control means 80 toothed in the engaged position of the actuating member 20.
  • the watch 1000 according to the invention comprises a clutch ring 102 rotatable to control the clutch or disengagement of the actuator 20, and this clutch ring 102 is preferably hidden from the user.
  • Such an arrangement allows the transformation of an existing watch, having, pre-existing, a control member such as crown, push, bezel, bolt or the like, a sliding pinion, and a timer.
  • the invention is described here in the particular, non-limiting case of a rocker 10 having a monobloc top plate 30, the outer ring 2 of which has a toothing 8.
  • this upper monobloc board 30 As can be seen in particular on the figure 16 by rotation of this upper monobloc board 30 relative to the seam 12 of the balance 10, or, as here to the lower board 14 when the balance 10 has one, and which is synchronous with the seam 12, this serge 12 being in advance locked in rotation, and for any angular position of the serge 12, the inertia of the upper monobloc board 30, and therefore of the balance 10, changes.
  • the rotation of the outer ring 2, in particular of this one-piece upper board 30 is carried out by the control means 80 of the operating member 20, in particular in the form of a driving wheel 81 adjacent the balance 10, carried by a 150 bistable lever that comprises the stop means 160, in the non-limiting embodiment illustrated by the figures.
  • the lever 150 is engaged / disengaged laterally by the mechanical action of a rotary ring 102 peripheral to the watch movement 300 which includes the oscillator 100, which allows access to the oscillator 100 wherever it is located on the periphery.
  • the figure 16 shows an example of a part of this clutch mechanism.
  • the clutch ring 102 acts on two slopes 154 and 155 of the lever 150 by a finger 103 that it comprises, to control the tilting of the lever 150, according to its direction of rotation.
  • the position drawn in solid lines shows the lever 150 in the locking position of the toothing 15 of the lower board 14, by a comb 151 that includes the lever 150, in an "ON" position: the balance 10 is engaged with the timer and the crown 110 of the watch 1000.
  • a jumper lever 156 introduces a bistability on the lever 150.
  • lever 150 comprises a comb 151 to cooperate with the lower toothing 15 of the lower plate 14, it is understood that it can also, when the rocker 10 is devoid of lower plate 14, have a friction surface arranged to cooperate and in particular come into contact with the outer surface 120 of the serge 12.
  • the flexible structure is held by an integrated jumper, such as the inner jumper 42 of the figure 4 , or the outer jumper 29 of the figure 12 .
  • This integrated jumper retains the flyweight 4, and exerts a sufficient return torque to also retain the outer ring 2.
  • the lower 14 and upper 30 boards are micromachined (techniques from silicon fabrication) and if possible in a single layer (mask process), as shown.
  • the lever 150 engaged by the action of the ring 102, approaches laterally of the balance 10 (ON position) and angularly maintains it by means of its comb 151 in engagement with the lower board 14 attached to the balance 10
  • the driving wheel 81 then meshes simultaneously with the upper board 30.
  • the watch 1000 comprises a control member constituted by a pusher, a bolt, or the like, or, as shown in the figures, in particular on the figure 20 a crown 110, which has the advantage of reversible adjustment in both directions.
  • the rotation by the crown 110 conventionally mobile between at least two positions T1 and T3, drives through the sliding pinion 111 the movement of the timer 112, the input wheel 115, the driving wheel 81, and therefore the outer ring 2 of the upper board 30, which can rotate and change the inertia of the balance 10.
  • the timer 112 may cause a wheel at the center 113 carrying a needle 114 to display the adjustment made.
  • the invention also relates to a watch assembly comprising such a watch 1000, as visible on the Figures 20 and 21 , and an adjustment tool 200 which is arranged to control the rotation of the clutch ring 102.
  • the clutch ring 102 and the adjustment tool 200 in particular constituted by a magnetic key, as illustrated, comprise complementary magnetic zones 101, respectively 201, for the rotational drive of the clutch ring 102 under the action of the adjusting tool 200 when the complementary magnetic zones 101 and 201 are cooperatively through the box of the watch 1000.
  • the ring 102 is advantageously, in a particular variant, provided with targets ferromagnetic 101: P, Q, R, S, judiciously placed and hidden, so that only an outer key 200 having magnetic pads 201, including neodymium magnets or the like, placed in certain places P ', Q', R ', S ', and facing, can take off if necessary and turn.
  • targets ferromagnetic 101 P, Q, R, S, judiciously placed and hidden, so that only an outer key 200 having magnetic pads 201, including neodymium magnets or the like, placed in certain places P ', Q', R ', S ', and facing, can take off if necessary and turn.
  • the advantage of a ring 102 only ferromagnetic, and of substantially circular shape, generally of revolution, is its insensitivity to external magnetic fields capable of rotating it, and external ferromagnetic objects in the undesirable case of presence of magnets.
  • the figure 20 illustrates an overview of the gait adjustment device by changing the inertia of the balance 10, without opening the watch 1000 and without adding a pusher.
  • the clutch ring 102 comprising the ferromagnetic targets 101 is rotated by a magnetic key 200, external tool to the watch, comprising the magnetic pads 201, when it is positioned coaxially with the watch (with their axes coincident).
  • the ring 102 may first be attracted axially against the magnets, then a rotation of the key 200 causes a rotation of the ring 102 by reluctant torque on the ferromagnetic targets 101.
  • the angular position of these targets being hidden from the user, only the right key can cause the ring to rotate.
  • the goal is to make the adjustment by the SAV, so as not to tarnish the reputation of the brand in case of attempted unsuccessful adjustment on the part of the wearer.
  • the magnetic key 200 thus cooperates with the clutch ring 102, the number and position of the ferromagnetic targets 101 are hidden from the user, to prevent an unsuccessful attempt by the user to adjust.
  • the magnetic pads 201 are also hidden at the key 200.
  • the process of setting the procedure is as follows. Firstly, the pivoting of the ring 102 by means of the magnetic key 200 causes the lever 150 to tilt towards the balance 10, in order to engage the driving wheel 81 of the lever 150 with the adjusting device of the lever. rotary inertia embedded on the balance 10. It thus passes from the OFF position to the ON position.
  • the driving wheel 81 is integral with the idler wheel 115 of the timer 112.
  • the crown 110 is at the same time engaged with the minute hand 114 and the inertia adjustment of the balance 10, via the sliding pinion 111 and the return.
  • the rotation of the crown 110 then allows the adjustment of inertia, with in addition a reading of this possible correction by the minute hand 114, which is very convenient.
  • the lever 150 is disengaged with the aid of the key 200 by returning from the ON position to the OFF position, then a time-setting is performed and the crown 110 is finally put back into position T1.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Adornments (AREA)
EP16172841.5A 2016-06-03 2016-06-03 Uhrenmechanismus zum einstellen der unruhträgheit Active EP3252545B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP16172841.5A EP3252545B1 (de) 2016-06-03 2016-06-03 Uhrenmechanismus zum einstellen der unruhträgheit
JP2017082591A JP6313882B2 (ja) 2016-06-03 2017-04-19 慣性を調整可能なバランス車を備えた計時器用機構
CN201710408233.9A CN107463082B (zh) 2016-06-03 2017-06-02 具有可调节惯性摆轮的钟表机构
US15/613,791 US10222748B2 (en) 2016-06-03 2017-06-05 Timepiece mechanism with adjustable inertia balance wheel
HK18107285.9A HK1247998A1 (zh) 2016-06-03 2018-06-04 具有可調節慣性擺輪的鐘錶結構

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EP3502786A1 (de) * 2017-12-22 2019-06-26 The Swatch Group Research and Development Ltd Unruh für uhr, und herstellungsverfahren einer solchen unruh
EP3795855A1 (de) * 2019-09-20 2021-03-24 Patek Philippe SA Genève Herstellungsverfahren einer uhrfeder aus monokristallinem material, und nach diesem verfahren erzeugte uhrfeder
CN113031423A (zh) * 2019-12-09 2021-06-25 斯沃奇集团研究和开发有限公司 具有带惯性和/或不平衡调节的惯性质量件的钟表谐振器机构
EP4174584A1 (de) 2021-10-26 2023-05-03 The Swatch Group Research and Development Ltd Magnetischer mechanismus zur steuerung und/oder zum antrieb durch ein armbanduhrengehäuse
EP4174586A1 (de) * 2021-10-29 2023-05-03 The Swatch Group Research and Development Ltd Uhreneinheit, die eine armbanduhr und ein uhrzeitkorrektursystem umfasst

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EP3252546B1 (de) * 2016-06-03 2019-08-28 The Swatch Group Research and Development Ltd Uhrenmechanismus zum einstellen der unruhträgheit
EP3499317A1 (de) * 2017-12-13 2019-06-19 Rolex Sa Triebfeder eines kalender-uhrwerksmechanismus
EP3502787B1 (de) 2017-12-22 2020-11-18 The Swatch Group Research and Development Ltd Herstellungsverfahren einer unruh für uhren
EP3525046A1 (de) * 2018-02-12 2019-08-14 The Swatch Group Research and Development Ltd Uhrwerkoszillator, der für winkelbeschleunigungen des tragens unempfindlich ist
EP3534222A1 (de) * 2018-03-01 2019-09-04 Rolex Sa Herstellungsverfahren eines thermokompensierten oszillators
EP3540528B1 (de) * 2018-03-16 2020-08-05 The Swatch Group Research and Development Ltd Uhr, die ein mechanisches uhrwerk umfasst, dessen ganggenauigkeit durch eine elektronische vorrichtung reguliert wird
CH715091A2 (fr) * 2018-06-07 2019-12-30 Swatch Group Res & Dev Ltd Pièce d'horlogerie comprenant un mouvement mécanique dont la marche est régulée par un dispositif électromécanique.
US11454932B2 (en) * 2018-07-24 2022-09-27 The Swatch Group Research And Development Ltd Method for making a flexure bearing mechanism for a mechanical timepiece oscillator
EP3605243A1 (de) * 2018-07-31 2020-02-05 Montres Breguet S.A. Uhr-anzeigemechanismus mit variabler geometrie und elastischem zeiger
EP3667431A1 (de) * 2018-12-13 2020-06-17 Montres Breguet S.A. Mobile anzeigeeinheit einer uhr mit reibungsregulierungsmechanismus
EP3772673B1 (de) * 2019-08-08 2022-04-06 ETA SA Manufacture Horlogère Suisse Indexierungselement für uhren
EP3839656B1 (de) * 2019-12-18 2023-12-13 Nivarox-FAR S.A. Unruh für uhrwerk
CN112666818B (zh) * 2020-12-28 2022-03-11 深圳穿金戴银科技股份有限公司 手表调时结构

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CH320818A (fr) 1953-12-11 1957-04-15 Siegwart Hans Balancier pour pièce d'horlogerie
CH333583A (fr) * 1958-01-23 1958-10-31 Ciana Jean Charles Balancier à moment d'inertie variable
CH342898A (fr) * 1958-08-08 1959-11-30 Rolex Montres Balancier pour pièce d'horlogerie
CH708675A2 (it) 2013-10-14 2015-04-15 Giuseppe Fabozzi Processo di recupero di fibre polimeriche filamentose.
CH709052A2 (fr) 2013-12-27 2015-06-30 Seiko Instr Inc Balancier-spiral, mouvement et pièce d'horlogerie.

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EP3502786A1 (de) * 2017-12-22 2019-06-26 The Swatch Group Research and Development Ltd Unruh für uhr, und herstellungsverfahren einer solchen unruh
EP3795855A1 (de) * 2019-09-20 2021-03-24 Patek Philippe SA Genève Herstellungsverfahren einer uhrfeder aus monokristallinem material, und nach diesem verfahren erzeugte uhrfeder
WO2021053454A1 (fr) * 2019-09-20 2021-03-25 Patek Philippe Sa Geneve Procédé de réalisation d'un ressort horloger en matériau monocristallin et ressort horloger obtenu par ce procédé
CN113031423A (zh) * 2019-12-09 2021-06-25 斯沃奇集团研究和开发有限公司 具有带惯性和/或不平衡调节的惯性质量件的钟表谐振器机构
CN113031423B (zh) * 2019-12-09 2022-08-16 斯沃奇集团研究和开发有限公司 具有带惯性和/或不平衡调节的惯性质量件的钟表谐振器机构
US11714386B2 (en) 2019-12-09 2023-08-01 The Swatch Group Research And Development Ltd Horological resonator mechanism with inertial mass with adjustment of inertia and/or unbalance
EP4174584A1 (de) 2021-10-26 2023-05-03 The Swatch Group Research and Development Ltd Magnetischer mechanismus zur steuerung und/oder zum antrieb durch ein armbanduhrengehäuse
WO2023072437A1 (fr) 2021-10-26 2023-05-04 The Swatch Group Research And Development Ltd Mecanisme magnetique de commande et/ou d'entrainement a travers une boite de montre
EP4174586A1 (de) * 2021-10-29 2023-05-03 The Swatch Group Research and Development Ltd Uhreneinheit, die eine armbanduhr und ein uhrzeitkorrektursystem umfasst
CN116068872A (zh) * 2021-10-29 2023-05-05 斯沃奇集团研究及开发有限公司 包括表和用于校正时间的系统的时计组件

Also Published As

Publication number Publication date
HK1247998A1 (zh) 2018-10-05
US10222748B2 (en) 2019-03-05
CN107463082A (zh) 2017-12-12
JP2017219538A (ja) 2017-12-14
JP6313882B2 (ja) 2018-04-18
CN107463082B (zh) 2019-07-16
US20170351219A1 (en) 2017-12-07
EP3252545B1 (de) 2019-10-16

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