EP3246764B1 - Stossdämpfende vorrichtung für uhrwerk - Google Patents

Stossdämpfende vorrichtung für uhrwerk Download PDF

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Publication number
EP3246764B1
EP3246764B1 EP17167110.0A EP17167110A EP3246764B1 EP 3246764 B1 EP3246764 B1 EP 3246764B1 EP 17167110 A EP17167110 A EP 17167110A EP 3246764 B1 EP3246764 B1 EP 3246764B1
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EP
European Patent Office
Prior art keywords
pivot
magnet
shock
magnets
force
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EP17167110.0A
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English (en)
French (fr)
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EP3246764A1 (de
Inventor
Deirdré LENOIR
Davide Sarchi
Benoît LÈGERET
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Montres Breguet SA
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Montres Breguet SA
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Publication of EP3246764A1 publication Critical patent/EP3246764A1/de
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings
    • 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
    • G04B29/00—Frameworks
    • G04B29/02—Plates; Bridges; Cocks
    • G04B29/022—Bridges
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings
    • G04B31/04—Shock-damping bearings with jewel hole and cap jewel

Definitions

  • the present invention relates to horological shockproof devices.
  • shockproof devices are generally associated with bearings that guide rotating rotated elements of the watch movement, in particular rockers.
  • shock absorbers, bumpers or shock absorbers we also speak of shock absorbers, bumpers or shock absorbers.
  • the invention relates more particularly to the damping of axial shocks undergone by pivoting elements and the mechanical stresses experienced by the pivots during such axial shocks.
  • a conventional horological shock-absorbing device comprises an elastic member which carries or exerts pressure against at least one counter-pivoting stone of the bearing equipped with this shock-proof device, this counter-pivot stone forming a stop for the pivot inserted in this bearing in the direction of the axis of rotation of the pivoting element considered.
  • This shockproof device is arranged so as to generate, via the counter-pivot stone, a restoring force on the pivot in question when the pivot presses in case of impact against the stone against pivot.
  • pivoting stone is meant any structure, in any suitable material, which defines an axial bearing surface for the pivot.
  • Such anti-shock devices generally comprise mechanical springs which are dimensioned empirically, following practical rules such as that of the best compromise between mechanical stability during operation and elastic resistance to deformation.
  • mechanical Indeed, it is desirable to have a relatively rigid damper which does not generate axial movements of the pivoting element at each small impact, while ensuring the function of shock absorber for violent shocks generating large axial accelerations (positive or negative) for this pivoting element that could damage its pivots.
  • the conventional shock devices of the sprung balance, the parachutes (also called scrapers) and the lyres are sized not to be activated until relatively large shock accelerations (between 200g and 500g, g being the same). acceleration), thanks to a preload of the spring forming these parachutes and lyres which defines a threshold value. Beyond this threshold value, it is expected that the spring deforms and absorbs some of the energy of the shock. However, because of the low mechanical damping of the metal blades used, most of the energy is returned to the pendulum. The local deformation of the pendulum pivot is therefore very likely, already for relatively small shocks.
  • the document JP-2011-185673 describes a bearing for a watch mobile that is associated with a shockproof device.
  • This shockproof device conventionally comprises a kitten in which are arranged a pierced stone and a counter-pivot stone.
  • the kitten is located in a housing of a base which has at the bottom of its side wall magnets arranged to exert axially, continuously, a magnetic attraction force on the kitten which is provided for this purpose in magnetic material .
  • This magnetic system is intended to participate in the shockproof function.
  • rigid or elastic axial stops are arranged in the base above the kitten.
  • the present invention aims to provide a watch movement equipped with at least one effective shockproof device that provides a solution to the problem of deterioration of the pivots of a pivoting element in case of shocks, even in case of strong shocks.
  • the present invention relates to a watch movement as defined in claim 1.
  • the shockproof device has a lower resistance for relatively strong shocks while ensuring good stability for less shock.
  • the rigidity of the anti-shock device according to the invention no longer behaves like a mechanical spring which generates a restoring force substantially proportional to the axial displacement of the stone against pivot. On the contrary, it exerts a relatively large force when the displacement is zero, which then decreases at least on an initial portion of the shock-absorbing path that can cross the stone against pivot.
  • the first and second magnets and the high magnetic permeability element are aligned in a direction substantially parallel to the axis of rotation of the pivoting element, the first and second magnets having opposite polarities according to this direction.
  • the high magnetic permeability element is attached to the first magnet.
  • the anti-shock device 30 comprises an elastic member 32 which exerts a force on a counter-pivoting stone 36, which forms a stop for the pivot 26 in the direction of the axis of rotation of the pivoting element.
  • This shockproof device is arranged in such a way as to be able to generate, by means of the counter-pivot stone, a restoring force on the pivot 26 when this pivot presses, in the event of an impact, against this stone. against pivot.
  • the anti-shock device further comprises a magnetic system 40 formed of two magnets 42, 44 and a high magnetic permeability element 46 arranged between these two magnets and integral with one of them.
  • the magnet 44 integral with the elastic member, is arranged to undergo, in the event of relatively strong axial shocks for the pivoting element, a back and forth movement symbolized by the Figure 2 by a two-way arrow.
  • the elastic member In the absence of shock, the elastic member is in a specific rest position and the magnet that it also carries. Note that in this rest position, the elastic member may have an initial elastic deformation. In the latter case, it is said that the elastic member is prestressed.
  • the two magnets 42 and 44 are arranged to generate between them, in association with the high magnetic permeability element 46, a global magnetic attraction force on a first section of the aforementioned relative distance and a global magnetic force of repulsion on a second section of this relative distance, this second section corresponding to distances (referenced E to the Figure 3 ) between the first and second magnets which are greater than the distances corresponding to the first section.
  • the magnetic system 40 and the elastic member 32 are arranged so that the total force exerted in case of shock by the shockproof device on the pivot 26 remains a restoring force for the integer of the relative distance.
  • both magnets are cylindrical and the wafer is in the form of a disk made of, for example, a ferromagnetic material.
  • the magnetic system 40 and its operation will be described below.
  • the magnetic system 52 comprises a first magnet 4, a high magnetic permeability element 6 which is integral with the first magnet, and a second magnet 8 which is movable along a displacement axis , relative to the assembly formed by the first magnet 4 and the element 6.
  • the element 6 is arranged between the first magnet and the second magnet, in contact or close to the first magnet.
  • the element 6 is glued to the first magnet as shown in FIG. Figure 3 .
  • the first magnet can be driven into the high magnetic permeability element which then has for example the shape of a cylindrical box open at one end to receive the first magnet.
  • the distance between the element 6 and the magnet 4 integral with this element is less than or substantially equal to one-tenth of the length of the magnet along its axis of magnetization.
  • the first magnet 4 and the element 6 form a first part of the magnetic system and the second magnet 8 forms a second part of this system.
  • Element 6 is made up of, for example, carbon steel, tungsten carbide, nickel, FeSi or FeNi, or other alloys with cobalt such as Vacozet® (CoFeNi) or Vacoflux® (CoFe).
  • this element with high magnetic permeability consists of a metal glass based on iron or cobalt.
  • Element 6 is characterized by a saturation field Bs and a permeability ⁇ .
  • the magnets 4 and 8 are for example ferrite, FeCo or PtCo, rare earths such as NdFeB or SmCo. These magnets are characterized by their remanent field Br1 and Br2.
  • the element with high magnetic permeability 6 has a central axis 10 which is substantially coincident with the magnetization axis of the first magnet 4 and also with the magnetization axis of the second magnet 8.
  • the respective magnetization directions of the magnets 4 and 8 are opposed.
  • These first and second magnets therefore have opposite polarities and they are likely to undergo a relative movement between them over a certain relative distance D.
  • the magnet 4 is fixed and the magnet 8 is movable so that the relative movement between them has a direction substantially along the central axis 10 which then defines the axis of displacement.
  • the axis 10 is linear, but this is a non-limiting variant.
  • the axis of displacement is substantially circular arc, the central axis of the element 46 being substantially tangential to this axis of displacement curve.
  • the behavior of the magnetic system 40 is similar to that of the magnetic system 52. This is all the more true that the radius of curvature is large relative to the maximum possible distance between the element 46 and the magnet 44, as is the case in the first embodiment of the invention.
  • the element 6 has dimensions in a plane orthogonal to the central axis 10 which are greater than those of the first magnet 4 and those of the second magnet 8 in projection in this orthogonal plane. It will be noted that, in the case where the second magnet abuts against the element 6 at the end of the magnetic attraction stroke, this second magnet advantageously has a hardened surface or a thin layer of hard material on its surface.
  • the two magnets 4 and 8 are arranged in magnetic repulsion so that, in the absence of the element with high magnetic permeability 6, a repulsive force tends to move these two magnets away from each other. Surprisingly, however, the arrangement between these two magnets of the element 6 reverses the direction of the magnetic force between the first and second parts of the magnetic system when they are at a short distance from each other. so that a global force of magnetic attraction is then generated between these two parts.
  • the Figure 4 is a graph whose curve 54 represents the magnetic interaction force between the first and second parts of the magnetic system 52 as a function of the distance E between the two magnets, respectively of the relative distance D between the moving magnet 8 and the element with high magnetic permeability 6.
  • the magnet 8 undergoes, on a first section D1 of the relative distance, generally a magnetic attraction force which tends to hold the magnet 8 against the element 6 or to the bring back to it in case of removal. Then, the element 6 and the two magnets are arranged so that the second magnet 8 undergoes, on a second section D2 of the aforementioned relative distance, globally a magnetic repulsion force.
  • This second section corresponds to distances between the first and second parts, and therefore at distances D between the element 6 and the magnet 8, which are greater than the distances corresponding to the first section of the relative distance.
  • the second section is limited by a maximum distance D max which is generally defined by a stop limiting the distance of the moving magnet.
  • the overall magnetic force is a continuous function of the distance between the components and it has a zero value at the distance D inv .
  • this magnet is subjected to a global magnetic repulsion force which tends to move it away from the element 6.
  • the magnet 8 is subjected to a global magnetic attraction force which tends to approach the element 6 and, if nothing do not oppose it, put it in contact with that element, and then keep it in that position.
  • the inversion distance D inv is determined by the geometry of the three magnetic parts forming the magnetic system and their magnetic properties.
  • the elastic member 32 is formed by a flat spring having a first end 56 and a second end 58, the first end being fixed to the support 48 by means of a screw 60 and the second end bearing the second magnet 44.
  • the counter-pivoting stone 36 is located, in projection in a general plane of the flat spring, between the first and second ends.
  • the bearing 28 comprises a base 62 fixedly arranged in an opening of the support 48. In a conventional manner, this base has at its center a hole through which the pivot 26 passes.
  • the pivoting element 24, here the shaft of a balance (not shown) has a bearing 70 which classically limits the movement of this element along the axis 50, this bearing abutting against a surface defined by the base to the device of the hole.
  • the bearing 28 further comprises a kitten 64 in which is inserted the counter pivot stone 36. In the variant shown, it is a magnetic bearing. Thus, the kitten still supports a magnet 66 and a closing stone 68. This kitten also participates in the anti-shock device.
  • He is arranged in a housing formed by the base 62 and a closure plate 72 fixed to the support 48, so as to be able to undergo an axial movement at least a distance corresponding to the maximum displacement that can undergo in case of impact the pivot 26 when the range 70 comes into abutment against the base.
  • a short tube 74 is fixed to the flat spring 32 at its end end 58 so as to bear against the kitten or the closure stone.
  • the anti-shock device acts on the integral assembly of the counter-pivot stone via this tube.
  • the invention is not limited to a magnetic bearing.
  • there is a conventional bearing with a kitten incorporating a pierced stone and a counter-pivot stone the latter may have a flat surface opposite the pivot.
  • the magnetic system and the elastic member are arranged so that, in a rest position of the shockproof device, the pivoting stone or a kitten to which it is fixed is held in abutment against the support of the bearing or against a base of this bearing as the force exerted by the pivot considered against the pivot-stone is less than a limit value, the latter being preferably provided greater than the gravitational force acting on the pivoting element, including the sprung balance.
  • the elastic element is prestressed in the rest position of the shock-proof device, so that the counter-pivot stone remains immobile over a larger range of values of the force exerted by the mobile element undergoing axial acceleration. in case of shock.
  • the graph of the total force exerted by the anti-shock device on the assembly carrying the counter-pivot stone, and through it on the pivot 26 bearing against this stone, according to its displacement DP is given by the curve 78 which corresponds to the sum of the elastic force and the overall magnetic force generated by the magnetic system 40. It is observed that this total force (restoring force) is greater than the elastic force on a first section DP1 between a distance DP R , corresponding to the rest position of the anti-shock device, and a distance DP inv corresponding to a position of the counter-pivot stone for which the overall magnetic force exerted on the magnet 44 is zero.
  • the total force is less than the elastic force because the overall magnetic force then opposes the elastic force, which decreases the total force exerted on the pivot of the rotating element.
  • the anti-shock device according to the invention has a remarkable behavior as shown by the curve 78.
  • the force exerted on the pivot bearing against the counter-pivot stone, at least for a displacement distance of this stone less than DP inv is maximum for the idle distance DP R of the anti-shock device.
  • the counter-pivot stone moves away from its rest position and then the total force against the pivot 26 decreases relatively quickly, which directly ensures a relatively large movement of the stone against pivot and a good shock damping to the stop position.
  • the flat spring has a rigidity close to a standard stiffness but its preload is reduced, compared to a standard prestressing, by a factor of about 30% to 40%, while having a usual stability for the anti-shock device in his rest position.
  • the shock device can return to its initial position, because it is expected that the total force remains positive (restoring force) and exceeds the friction forces.
  • the inversion of the magnetic force which takes place when the moving magnet is sufficiently close to the ferromagnetic element, simultaneously ensures the absolute absence of mechanical hysteresis and the re-centering of the bearing after an impact.
  • a watch movement 82 incorporating a second embodiment of an anti-shock device according to the invention.
  • the bearing and the anti-shock device 86 associated with it are arranged in an opening of a plate 84.
  • the elastic member 88 is a lyre spring having two branches 89 and 90 arranged to exert pressure on the counter-pivoting stone 36A .
  • the two branches press on a kitten which is fixed against the pivot stone.
  • the anti-shock device comprises a first magnetic system 40A and a second magnetic system 40B each similar to the magnetic system 40 described in the first embodiment.
  • the two magnetic systems are respectively associated with two structures 92 and 94 which are respectively fixed to the two branches 89 and 90 substantially in their central zone. These two structures respectively carry two magnets 44A and 44B each forming the moving magnet of the respective magnetic system.
  • the two branches are respectively associated with the first and second magnetic systems and carry, through the structures 92 and 94, each a movable magnet 44A, respectively 44B which cooperates with a fixed magnet 42A, respectively 42B.
  • Each magnetic system further comprises a high magnetic permeability element 46A, respectively 46B, which is integral with the fixed magnet of the respective magnetic system.
  • each of the branches 89, 90 of the lyre spring in conventional manner, is held axially at its two ends by angularly projecting portions of an upper ring of the base 62A of the bearing.
  • the lyre spring undergoes in the event of stress a maximum elastic deformation.
  • each branch substantially presses in the middle on the counter-pivot stone.
  • the two structures 92 and 94 are integral with the lyre spring and have a greater rigidity than that of the respective branches, in particular by a greater thickness as shown in the figures.
  • the structures have the same thickness as the branches of the lyre spring to facilitate manufacture, but have larger sections.
  • the rigidity of the supporting structures of the moving magnets is not greater than those of the branches, the mobile magnets performing in case of large shocks longer courses than the counter-pivot stone.
  • the arrangement of two magnetic systems symmetrically associated respectively with the two elastic branches of the lyre spring is advantageous because it results from such an arrangement the same pressure of each branch on the counter-pivot stone, or more generally on the mobile assembly 96 of the bearing, for the same elastic deformation of the two branches. This maintains a uniform behavior of the anti-shock device and in particular the counter-pivot stone 36A in a general plane perpendicular to the axis of rotation of the balance in the event of axial shocks.
  • the Figure 8 shows the curve 76A of the elastic force applied by the spring-lyre to the stone against pivot, and thus on the pivot 26 bearing against it, depending on the axial displacement of the stone against pivot, as well as the curve 100 of the total force exerted by the anti-shock device 86 on the pivot as a function of said axial displacement.
  • the variant shown is particular in that no mechanical prestressing of the anti-shock device is provided in the rest position, only the magnetic attraction force ensuring the immobility of the anti-shock device in its static operating range ( idle position here corresponding to a displacement DP equal to zero) up to a certain maximum static force of this shockproof device.
  • the preponderance of the magnetic force in the rest position makes it possible to reduce the total restoring force well below the maximum force of the static situation as soon as the shockproof device enters its dynamic operating range and is therefore armed. .
  • the balance moves with less resistance until it meets the stop formed by the base of the bearing. Note that this stop, by acting on an annular bearing shaft 24 of the balance, protects the pendulum pivot in case of violent shocks.
  • the stiffness of the lyre spring and the sizing of the two magnetic systems are provided so that the total resulting force applied by the shockproof remains a greater restoring force to the friction forces to ensure, after an impact generating a force greater than the maximum force intervening for the static situation on the mobile assembly 96 of the bearing, the return of the shockproof device in its initial position and a good refocusing of this mobile assembly (crucial property to ensure good chronometry of the watch movement).
  • the two bearings of a balance spring are equipped with a shock-absorbing device of the type described above.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Vibration Prevention Devices (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Claims (11)

  1. Uhrwerk (22; 82), umfassend ein Schwenkelement (24), ein Lager (28), in dem ein Drehzapfen (26) dieses Schwenkelements angeordnet ist, und eine Stoßdämpfungsvorrichtung (30; 86), die diesem Lager zugeordnet ist, wobei die Stoßdämpfungsvorrichtung ein Federorgan (32; 88) umfasst, das dafür angeordnet ist, auf mindestens einen Drehzapfengegenstein (36; 36A), der einen Anschlag für den Drehzapfen in Richtung der Drehachse (50) des Schwenkelements bildet, einen Druck ausüben zu können, wobei diese Stoßdämpfungsvorrichtung so angeordnet ist, dass sie über den Drehzapfengegenstein auf den Drehzapfen eine Rückstellkraft ausüben kann, wenn dieser Drehzapfen bei einem Stoß gegen den Drehzapfengegenstein drückt; wobei die Stoßdämpfungsvorrichtung ferner ein magnetisches System (40; 40A; 40B) umfasst, das zwei Magneten (42, 44) enthält, wobei dieser erste und dieser zweite Magnet an einem Träger (48) der Stoßdämpfungsvorrichtung bzw. an dem Federorgan befestigt sind, derart, dass sie zwischen sich eine Relativbewegung über eine bestimmte relative Strecke aufweisen können, wenn das Federorgan bei einem Stoß eine elastische Verformung unter einem Druck, der durch den Drehzapfen auf den Drehzapfengegenstein ausgeübt wird, erfährt; wobei das magnetische System und das Federorgan so angeordnet sind, dass die Gesamtkraft, die bei einem Stoß durch die Stoßdämpfungsvorrichtung auf den Zapfen ausgeübt wird, über die gesamte relative Strecke eine Rückstellkraft bleibt; wobei dieser erste und dieser zweite Magnet so angeordnet sind, dass sie auf einem erstem Teilstück der relativen Strecke zwischen sich eine magnetische Gesamtanziehungskraft ausüben;
    dadurch gekennzeichnet, dass das magnetische System ferner ein Element (46) mit hoher magnetischer Permeabilität umfasst, das zwischen den beiden Magneten angeordnet und mit einem von ihnen fest verbunden ist; und dass der erste und der zweite Magnet so angeordnet sind, dass sie auf einem zweiten Teilstück der relativen Strecke zwischen sich in Verbindung mit dem Element mit hoher magnetischer Permeabilität eine magnetische Gesamtabstoßungskraft ausüben, wobei dieses zweite Teilstück Entfernungen zwischen dem ersten und dem zweiten Magneten entspricht, die größer als die Entfernungen sind, die dem ersten Teilstück entsprechen.
  2. Uhrwerk nach Anspruch 1, dadurch gekennzeichnet, dass der erste und der zweite Magnet und das Element mit hoher magnetischer Permeabilität auf eine zu der Drehachse (50) des Schwenkelements im Wesentlichen parallele Richtung ausgerichtet sind, wobei der erste und der zweite Magnet in dieser Richtung entgegengesetzte Polaritäten aufweisen.
  3. Uhrwerk nach Anspruch 2, dadurch gekennzeichnet, dass das Element mit hoher magnetischer Permeabilität durch eine Patte gebildet ist, die eine Mittelachse besitzt, die mit der Magnetisierungsachse des ersten Magneten im Wesentlichen zusammenfällt.
  4. Uhrwerk nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Abstand zwischen dem Element mit hoher magnetischer Permeabilität und dem mit diesem Element fest verbundenen Magneten kleiner oder im Wesentlichen gleich einem Zehntel der Länge dieses Magneten längs seiner Magnetisierungsachse ist.
  5. Uhrwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Element mit hoher magnetischer Permeabilität an dem ersten Magneten befestigt ist.
  6. Uhrwerk nach Anspruch 5, dadurch gekennzeichnet, dass das magnetische System und das elastische Organ so beschaffen sind, dass in einer Ruheposition der Stoßdämpfungsvorrichtung das elastische Organ den Drehzapfengegenstein oder ein Futter hält, an dem dieser Drehzapfengegenstein abgestützt an dem Träger oder an einer mit diesem Träger fest verbundenen Basis befestigt ist, solange die durch den Drehzapfen auf den Drehzapfengegenstein ausgeübte Kraft kleiner als ein Grenzwert ist, wobei dieser Grenzwert größer als die Schwerkraft, die auf das Schwenkelement wirkt, vorgesehen ist.
  7. Uhrwerk nach Anspruch 6, dadurch gekennzeichnet, dass das Federelement (32) in der Ruheposition der Stoßdämpfungsvorrichtung vorgespannt ist.
  8. Uhrwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Element mit hoher magnetischer Permeabilität aus einem amorphen Metall auf Eisen- oder Cobaltbasis hergestellt ist.
  9. Uhrwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Federelement eine Blattfeder (32) ist, die ein erstes Ende und ein zweites Ende besitzt, wobei das erste Ende an dem Träger befestigt ist und das zweite Ende (58) den zweiten Magneten trägt, wobei der Drehzapfengegenstein in der Projektion auf eine allgemeine Ebene der Blattfeder zwischen dem ersten und dem zweiten Ende angeordnet ist.
  10. Uhrwerk nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass das Federorgan eine Leierfeder (88) ist, die zwei Schenkel (89, 90) aufweist, die so angeordnet sind, dass sie auf den Drehzapfengegenstein oder auf ein Futter, an dem dieser Drehzapfengegenstein befestigt ist, einen Druck ausüben; dass das magnetische System ein erstes magnetisches System definiert und die Stoßdämpfungsvorrichtung ferner ein zweites magnetisches System umfasst, wie es in einem der Ansprüche 1 bis 8 definiert ist, wobei die beiden Schenkel dem ersten bzw. dem zweiten magnetischen System zugeordnet sind und jeweils einen Magneten tragen, der dem zweiten Magneten entspricht, der mit einem jeweiligen Magneten, der dem ersten Magneten entspricht und an dem Träger der Stoßdämpfungsvorrichtung befestigt ist, zusammenwirkt.
  11. Uhrwerk nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Schwenkelement eine Unruh ist.
EP17167110.0A 2016-05-18 2017-04-19 Stossdämpfende vorrichtung für uhrwerk Active EP3246764B1 (de)

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US (1) US10222754B2 (de)
EP (1) EP3246764B1 (de)
JP (1) JP6340114B2 (de)
CN (1) CN107402511B (de)
CH (1) CH712502A2 (de)
HK (1) HK1245425A1 (de)

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JP7171988B2 (ja) 2019-11-05 2022-11-16 ゲイツ・ユニッタ・アジア株式会社 ケーブル端末加工装置及びケーブル端末加工方法
EP3929667A1 (de) * 2020-06-26 2021-12-29 ETA SA Manufacture Horlogère Suisse Mobiles drehsystem eines uhrwerks
EP4063973A1 (de) * 2021-03-23 2022-09-28 The Swatch Group Research and Development Ltd Uhr mit integriertem stellglied, das eine elektromechanische vorrichtung umfasst

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HK1245425A1 (zh) 2018-08-24
CN107402511B (zh) 2019-08-09
CH712502A2 (fr) 2017-11-30
JP6340114B2 (ja) 2018-06-06
US20170336761A1 (en) 2017-11-23
US10222754B2 (en) 2019-03-05
CN107402511A (zh) 2017-11-28
EP3246764A1 (de) 2017-11-22
JP2017207485A (ja) 2017-11-24

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