EP2533109A1 - Mechanismus zur Vermeidung der schwerkraftbedingten Gangvariationen auf einer Reguliervorrichtung mit Spiralunruh, und mit dieser Perfektionierung ausgestattete Uhr - Google Patents

Mechanismus zur Vermeidung der schwerkraftbedingten Gangvariationen auf einer Reguliervorrichtung mit Spiralunruh, und mit dieser Perfektionierung ausgestattete Uhr Download PDF

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Publication number
EP2533109A1
EP2533109A1 EP11004697A EP11004697A EP2533109A1 EP 2533109 A1 EP2533109 A1 EP 2533109A1 EP 11004697 A EP11004697 A EP 11004697A EP 11004697 A EP11004697 A EP 11004697A EP 2533109 A1 EP2533109 A1 EP 2533109A1
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EP
European Patent Office
Prior art keywords
platform
wheel
axis
kinematic chain
plate
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Granted
Application number
EP11004697A
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English (en)
French (fr)
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EP2533109B1 (de
Inventor
Carole Kasapi
Patrick Pichot
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.)
Cartier International AG
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Cartier Creation Studio SA
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Publication date
Application filed by Cartier Creation Studio SA filed Critical Cartier Creation Studio SA
Priority to EP11004697.6A priority Critical patent/EP2533109B1/de
Priority to US14/123,818 priority patent/US9134702B2/en
Priority to PCT/IB2012/001008 priority patent/WO2012168773A1/fr
Priority to CN201280028354.6A priority patent/CN103797426B/zh
Publication of EP2533109A1 publication Critical patent/EP2533109A1/de
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Publication of EP2533109B1 publication Critical patent/EP2533109B1/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
    • 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
    • G04B17/20—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
    • G04B17/285—Tourbillons or carrousels
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency

Definitions

  • the object of the present invention is to improve these existing mechanisms by adding a device that prevents strong accelerations are transmitted to the sprung balance when the watch is subjected to movements of the user.
  • the subject of the present invention is a mechanism which avoids the differences of steps due to the effect of gravitation on a regulating member of a clockwork movement comprising a balance-spring and an escape wheel mounted on a platform.
  • said platform having an unbalance and being mounted in free rotation about at least a first axis with respect to a platen of movement so that said platform rotates about said first axis under the effect of earth gravitation;
  • said mechanism comprising a train comprising a driving kinematic chain connecting the escape wheel to a cylinder of the watch movement and a corrective kinematic chain which compensates for the movements and the speed of the platform relative to the plate, characterized in that it comprises a regulating device comprising an organ regulator connected to the platform and driven by the relative movements between the platform and the turntable of the watch movement.
  • the Figures 1 to 6 partially and schematically illustrate three examples of mechanisms that avoid gravity-induced changes in travel, avoiding variations or variations in the operation of a spiral balance-type regulating device of a timepiece such as a wristwatch or a watch the Earth's gravitational effect resulting from changes in the spatial orientation of the regulating device.
  • the mechanism comprises means allowing the regulating device to remain in a stable spatial position despite the movements imposed by the wearer to the timepiece while avoiding disrupting the display of time.
  • the stable spatial position of the regulating device is a position for which the balance remains in a horizontal or vertical reference plane whatever the position of the watch.
  • such a mechanism further comprises a regulating device comprising at least one regulating member connected to the platform carrying the regulating device (preferably via an inertial kinematic chain), as described below with reference to to the figures 7 and 8 .
  • a regulating device comprising at least one regulating member connected to the platform carrying the regulating device (preferably via an inertial kinematic chain), as described below with reference to to the figures 7 and 8 .
  • three examples of mechanisms avoiding gravitational shift are described first with reference to Figures 1 to 6 .
  • the principle of such mechanisms avoiding gait deviations consists in mounting the regulating member, generally the sprung balance, the anchor and the escape wheel on a mobile platform rotated along one or two orthogonal axes with respect to the platinum of the watch movement, this platform being subjected to the action of an unbalance which thus makes it possible to maintain said platform in a fixed reference plane (either horizontal, vertical or possibly inclined), by the action Earth's gravity whatever the position of the watch and therefore its movement.
  • a mechanism of this mechanism includes a driving kinematic chain connecting the escape wheel to the barrel system and a corrective kinematic chain that compensates the movements and speeds of the platform relative to the plate so that these movements of the plate -form do not disrupt chronometry of the timepiece.
  • this corrective kinematic chain when the platform rotates under the effect of its unbalance, it is possible to cancel the effect of displacements and the speed of the plate -form on the main driving kinematic chain.
  • a particularity of the mechanisms illustrated in Figures 1 to 6 is that in each case the cog, and in particular the motor and corrective kinematic chains, has the peculiarity of including only epicyclic gear trains whose mobiles meshing in a straight manner.
  • Another important feature of these mechanisms lies in the fact that a mobile main driving kinematic chain is mounted in a satellite carrier rotating around two coaxial motor axes embedded or not on a mobile equipment comprising the platform carrying the pendulum and a cage pivoted on the plate of the movement on which is rotated said platform. In this way, these mechanisms consume little energy which reduces the weight of the unbalance of the platform and does not significantly reduce the power reserve of the watch movement.
  • the corrective kinematic chain connects the escape wheel to the plate and comprises at least one mobile which pivots on the plate, which advantageously reduces the effect of the weight of this corrective chain on the unbalanced platform.
  • the second wheel is on board the platform, which greatly minimizes the influence that the rotation of the platform can have on the torque transmitted to the exhaust by the driveline. main driving force.
  • FIG. figure 1 The first embodiment of the mechanism avoiding the deviations of a clocking device is illustrated in FIG. figure 1 .
  • This is a simplified mechanism in that the platform carrying the regulating device is rotatably mounted on the plate of movement along a single axis of rotation AA perpendicular to the plane of the plate 1 of the clockwork movement.
  • the regulating device comprising a rocker 2, an anchor (not shown) and an escape wheel 3 is carried by a platform 4 pivoted on the plate 1 of the movement concentrically to the axis A-A.
  • the axis of rotation AA of the platform 4 comprises a first motor shaft 20 and a second motor shaft 22, the platform being constructed so that these two motor shafts rotate around the same axis AA .
  • the axis of the balance 2 is parallel to this axis of rotation A-A of the platform 4.
  • the escape wheel 3, rotated coaxially with the axis AA on the platform 4, is secured to a drive wheel or second driving wheel 5 connected to the escape wheel by the second drive shaft 22.
  • This second driving wheel 5 is engaged with the first mobile 6.2 of a satellite 6 rotated crazy in a satellite holder 7 which is itself pivoted on the platform 4 and rotated about the axis AA by a wheel of satellite door 7.1.
  • the satellite gate 7 effectively constitutes a cage rotating concentrically with the platform 4 and in which the satellite mobile 6 is mounted crazy.
  • the rotational speed of this satellite carrier 7 is a function of the speed of rotation of the platform 4 about the axis A-A.
  • the second mobile 6.1 of the satellite 6, integral and coaxial with the first mobile 6.2 of the satellite 6 is engaged with a first driving wheel 8 integral with the first motor shaft 20 pivoted on the plate 1 of the movement.
  • the wheel 8 and the shaft 20 are integral with the second wheel 9 of the clockwork motor of the watch movement.
  • this second wheel 9 is kinematically connected to the barrel system 10 of the clockwork movement via the middle wheel 12 and the center wheel 11 all pivoted on the plate 1 of the following watch movement axes parallel to the AA axis.
  • the escape wheel 3 is thus connected to the barrel 10 by a main driving kinematic chain comprising a straight epicyclic gear train formed of the driving wheel 5, the first 6.1 and second mobile 6.2 of the satellite 6, of the first wheel. 8, of the second wheel 9, the average wheel 12, the center wheel 11 and the cylinder 10.
  • This drive main drive train has no conical return and therefore has a very good performance, for example a yield which is substantially equal to the engine power of a conventional mechanical watch.
  • a mobile of the main driving driveline in this case the mobile 6, is mounted idle in the satellite holder 7, the latter being part of a correction kinematic chain also comprising the satellite gate wheel 7.1, a mobile idler 13, pivoted on the platform 4 along an axis parallel to the axis AA, and a fixed wheel 14 concentric with the axis AA and integral with the plate 1 of the movement.
  • the idler 13 comprises a first wheel 13.1 meshing with the satellite gate wheel 7.1 and a second wheel 13.2 (integral and coaxial with the wheel 13.1) engaged with the fixed wheel 14.
  • Rx being the number of teeth of wheel X.
  • V 9 a speed of the average wheel at the output of the platform V u the useful speed transmitted to the exhaust (these speeds being still relative to a fixed reference)
  • V 9 1 k 2 ⁇ V u + k 1 + k 2 - k 1 ⁇ k 2 .
  • V 4 or k 2 R 8. ⁇ R 6.2 R 6.1 .
  • R 5
  • the unbalance of the platform 4 can be constituted by the regulating device, sprung balance and escapement, itself since it can be mounted on the platform 4 offset from the axis of rotation AA of it. This avoids weighing down the watch movement.
  • a weight or mass could be attached eccentrically to the axis A-A on the platform 4 to increase the unbalance thereof.
  • the figure 1a illustrates a variant of the mechanism described with reference to the figure 1 .
  • the second wheel 9 of the work train is loaded on the platform 4 and meshes with the pinion of the escape wheel 3.
  • the axis of the escape wheel 3 which is confused with the axis AA of rotation of the platform 4, but the axis of the wheel of second 9, the rocker 2 and the escape wheel 3 being pivoted on the platform 4 parallel to the axis AA.
  • the second wheel 9 which is integral and concentric with the drive wheel 5 via the second drive shaft 22.
  • the first drive wheel 8 is secured to it by the first drive shaft 20, a third drive wheel 15 engaged with the average wheel 12.
  • FIGS. 2, 3 and 4 illustrate by way of example a practical execution of the embodiment of the mechanism described with reference to the diagram of the figure 1a , that is to say for a stabilization around a single axis AA of the platform 4 carrying the regulating device 2, 3 and the second wheel 9.
  • the platform 4 is formed of an upper bridge 4.1, an intermediate bridge 4.2 carrying an exhaust bridge 3.1 and a lower bridge 4.3 pivoted on the plate 1 concentrically to the axis A-A.
  • the three bridges 4.1, 4.2 and 4.3 of the platform 4 are integrally connected together by columns 4.4 which ensures that all these elements of the platform rotate together freely in rotation relative to the plate.
  • the third drive wheel 15 is integral with the lower end of the first drive shaft 20 pivoted by a bearing 21 in the plate 1, the shaft 20 being free in rotation relative to the platen as indicated above.
  • This first motor shaft 20 has at its upper end the first drive wheel 8.
  • the fixed wheel 14 of the plate 1 meshes with the second wheel 13.2 of the idler 13 while the first wheel 13.1 of this idler, rotated crazy on the lower deck 4.3 meshes with the wheel of the satellite door 7.1 of the lower hub of the satellite door 7 is pivoted in the lower axle 4.3 concentrically to the axis AA around the first drive shaft 20.
  • the satellite 6 is idly rotated on the satellite carrier 7, the second wheel 6.1 of the satellite 6 is engaged with the first driving wheel 8 while the first wheel 6.2 of the satellite 6 meshes with the drive wheel or second drive wheel 5 which is secured to the lower end of the second drive shaft 22 pivoted on the intermediate bridge 4.2 of the platform 4.
  • This second motor shaft 22 carries the second wheel 9 which is engaged with the pinion 3.2 of the escape wheel 3.
  • the path of the main driving kinematic chain M connecting the third drive wheel 15, connected by the engine train to the barrel, to the escape wheel 3 via the satellite 6 and the second wheel 9 has been highlighted. .
  • the figure 4 is a sectional view of the mechanism shown in figures 1a , 2 and 3 .
  • the second motor shaft 22 is extended beyond the intermediate bridge 4.2 of the platform 4 and is also pivoted in the upper deck 4.1 of this platform 4.
  • the free upper end of the second motor shaft 22 is extended beyond the upper deck 4.1 and carries a second hand 23 cooperating with a second dial 24 carried by the upper face of the upper deck 4.1 of the platform 4.
  • the seconds dial 24 rotates about the axis AA at the mercy of the movements of the platform 4.
  • the display of the hour and minutes is done conventionally from a mobile of the clockwork motor drive, generally the center wheel 11 or the medium wheel 12, by a timer to train the hour and minute hands that cooperate with a fixed dial relative to the watch movement platinum.
  • the figure 5 partially illustrates a second exemplary embodiment of the mechanism avoiding the deviations of the setting device of a watch movement in which the platform 4 is stabilized about an axis of rotation AA orthogonal to the axis of the balance 2.
  • the axis of the balance 2, the axis of the escape wheel 3 and the axis of the onboard second wheel 9 are all three perpendicular to the axis of rotation AA of the platform 4.
  • the correction mechanism comprises a conical return 25 secured to the drive wheel or second drive wheel 5 which meshes with the second wheel 9.
  • the mechanism is identical to that of the first embodiment in its variant described in Figures 1a to 4 .
  • the axis AA around which the platform is rotated may for example be the 3 o'clock - 9 o'clock axis of the watch.
  • the third exemplary embodiment of a mechanism that avoids the gapping of a regulating member of a clock movement illustrated schematically in FIG. figure 6 allows the stabilization of the platform 4 carrying the balance 2 around two axes of rotation AA and BB orthogonal to each other and with respect to the axis of rotation of the balance 2.
  • Such a mechanism makes it possible to maintain the platform 4 carrying the setting device of the watch in a fixed reference plane regardless of the orientation of the plate 1 of the movement of the watch in space and no longer just with respect to a single axis of displacement.
  • This mechanism comprises a cage 30 pivoted on the plate 1 about a second axis of rotation BB.
  • Platform 4 of the figure 5 previously described is, it, rotatably mounted on this cage 30 around the first axis of rotation AA perpendicular to the second axis of rotation BB of the cage 30.
  • the platform 4 carries the balance 2, the escape wheel 3 and the second wheel 9 whose axes are parallel to each other and orthogonal to the first AA and second BB axes of rotation.
  • the second wheel 9 meshes with the conical return 25 secured to the drive wheel or second drive wheel 5 pivoted on the platform 4 concentrically to the first axis of rotation AA around which said platform 4 rotates. Still as previously described , this drive wheel 5 meshes with the first wheel 6.2 of the satellite 6 whose satellite carrier cage 7 pivots about the first axis of rotation AA on the platform 4.
  • the second satellite wheel 6.1 meshes with the first drive wheel 8 concentrically pivoted to the first axis of rotation AA on the cage 30, which itself is pivoted about the second axis of rotation BB on the plate 1.
  • This first drive wheel 8 is integral with the third drive wheel 15 both pivoted on the cage 30 .
  • the satellite gate 7 is engaged by its satellite gate wheel 7.1 with the first wheel 13.1 of the idler mobile 13 pivoted mad on the platform 4, the second wheel 13.2 meshes with the first wheel 32.1 of a corrective mobile 32 whose second wheel 32.2 has a conical toothing.
  • This corrective mobile 32 is pivoted on the platform 4, in particular around the first drive shaft 20, concentrically to its axis of rotation AA on the cage 30.
  • This corrector mobile 32 meshes with its second wheel 32.2 with the fixed wheel 14 secured to the plate 1.
  • the fixed wheel 14 thus has a conical toothing.
  • the third drive wheel 15 also has a conical toothing and meshes with the first bevel gear 34.1 of a second idler wheel 34 rotated crazy on the cage 30.
  • the second wheel 34.2 of the second idler 34 is engaged with a fourth driving wheel 35 pivoted concentrically to the second axis of rotation BB on the cage 30.
  • This fourth drive wheel 35 is integral with a fifth drive wheel 35A kinematically connected to the cylinder 10 by a drive train of the movement may comprise a center wheel 11 and a wheel of high average 12 for example (the latter not being shown in the figure 6 for simplicity).
  • the platform 4 which carries the regulating device 2, 3 thus has two degrees of freedom, rotation about a first axis AA and rotation about a second axis BB orthogonal to the first axis AA .
  • the platform 4 having an unbalance, formed by the regulating device 2, 3 or by additional unbalance can thus move according to the any spatial orientation of the plate 1 of the movement to ensure the maintenance in a fixed reference plane balance 2 and avoid the deviations due to gravity regardless of the position of the watch or movements imposed on them.
  • the main drive train comprises the fifth drive wheel 35A, the fourth drive wheel 35, the second drive wheel 34, the third drive wheel 15, the first drive wheel 8, the satellite 6, the drive wheel drive (or second driving wheel) 5 and the conical return 25 as well as the second wheel 9 and the escape wheel 3.
  • the corrective kinematic chain it comprises in this embodiment the fixed wheel 14, the correction mobile 32, the first mobile crazy 13, the wheel of the satellite door 7.1, and the satellite door.
  • a mechanism according to the invention further comprises a regulator device connecting the platform 4 to a regulating member such as a flywheel 50, preferably through an inertial kinematic chain.
  • This regulating device gives the platform greater rotational inertia, with the aim of making the operation of the balance more even, by opposing jolts due to the accelerations of the wearer.
  • the figures 7 and 8 partially illustrate the mechanism of Figures 1A to 4 equipped with a regulating device.
  • This inertial kinematic chain comprises a toothed ring 51 integral with the platform 4 and coaxial with the latter meshing with a first mobile 52 pivoted on the plate 1 or a bridge of the watch movement.
  • This first mobile 52 drives a flywheel 50 via a second mobile 53 and a third mobile 54 in engagement with a pinion 50.1 of the flywheel.
  • the second movable 53 and third 54 of this inertial kinematic chain are also pivoted on the plate 1 or a bridge of the clockwork movement just like the flywheel 50.
  • the inertial kinematic chain may comprise only one mobile intermediate in between the ring gear 51 and the flywheel 50.
  • the wheel 50 can mesh directly with the ring gear 51, but in this case the steering wheel must be much larger.
  • this regulator device it is possible to better avoid the rebate of the balance by greatly reducing the accelerations of the platform by increasing its inertia without increasing its mass.
  • the regulator device comprising an inertial kinematic chain connecting the platform 4 to the flywheel 50 makes it possible to reduce the variations in acceleration of the movement of the platform 4 and prevents the balance 2 from reshuffling.
  • this inertial kinematic chain driving the regulating member by the relative movements between the platform and the turntable of the watch movement is independent of the motor kinematic or corrective mechanisms of the mechanism as well as of the automatic winding kinematic chain if the platform 4 acts as a winding mass.
  • This device makes it possible to relate to the platform 4 the inertia of the flywheel 50 multiplied by the square of the reduction ratio of the inertial kinematic chain. This solution responds well to the problem of reducing the effects of accelerations of the platform by increasing the inertia without increasing its mass.
  • the multiplication ratio of the inertial kinematic chain is between 50 and 500, preferably equal to 100 for the embodiment previously described with reference to FIGS. figures 7 and 8 .
  • the flywheel's inertia multiplied by the ratio of the inertial kinematic chain squared is from 10 to 50 times the inertia of the platform.
  • a value equal to 20 times the inertia of the platform is obtained.
  • the flywheel 50 and the intermediate mobiles of the inertial kinematic chain can be loaded onto the platform 4, the first intermediate mobile 52 meshing with a wheel fixed on the plate or a bridge of the clockwork movement.
  • the platform 4 is provided with an automatic winding mass 55 and the mechanism comprises a conventional automatic winding kinematic chain (not illustrated) connecting the platform 4 to the barrel ratchet of the watch movement. .
  • the mechanism of the figure 5 is provided with a regulating device comprising an inertial kinematic chain connecting the platform 4 to a flywheel 50, as described above, the platform 4 still carries the toothed ring 51 of the inertial kinematic chain of the regulating device connecting this platform 4 to the flywheel 50.
  • the platform 4 When the regulating device of the present invention is added to a mechanism with two axes of rotation AA and BB such as that of the figure 6 , the platform 4 carries the toothed ring 51 of a first inertial kinematic chain connecting it to the flywheel 50.
  • the cage 30, it carries a second toothed ring 51a of a second inertial kinematic chain connecting the cage 30 to a second flywheel.
  • the platform 4 and the cage 30 can be coupled using a differential whose output drives a single inertial kinematic chain and a single flywheel damping the accelerations of the platform 4 and the the cage 30.
  • the regulating member may be other than a flywheel where the regulation is simply by the rotation of a mass.
  • a regulating member as used in minute repeats where the regulation is by rotation of a mass and friction of this mass on a frame
  • a movable regulator with fins where the viscosity of the air is used
  • a regulating mobile similar to a clockwork escapement can be used.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Micromachines (AREA)
EP11004697.6A 2011-06-09 2011-06-09 Mechanismus zur vermeidung der schwerkraftbedingten gangvariationen auf einer reguliervorrichtung mit spiralunruh, und mit dieser perfektionierung ausgestattete uhr Active EP2533109B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11004697.6A EP2533109B1 (de) 2011-06-09 2011-06-09 Mechanismus zur vermeidung der schwerkraftbedingten gangvariationen auf einer reguliervorrichtung mit spiralunruh, und mit dieser perfektionierung ausgestattete uhr
US14/123,818 US9134702B2 (en) 2011-06-09 2012-05-24 Mechanism preventing rate variations caused by gravity on a balance-spring regulating device and timepiece incorporating this improvement
PCT/IB2012/001008 WO2012168773A1 (fr) 2011-06-09 2012-05-24 Mecanisme evitant les variations de marche dues a la gravitation sur un dispositif reglant a balancier-spiral et piece d'horlogerie incorporant ce perfectionnement
CN201280028354.6A CN103797426B (zh) 2011-06-09 2012-05-24 防止由重力作用于摆轮游丝调节装置上而导致速率变化的机构以及结合该改进的钟表

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11004697.6A EP2533109B1 (de) 2011-06-09 2011-06-09 Mechanismus zur vermeidung der schwerkraftbedingten gangvariationen auf einer reguliervorrichtung mit spiralunruh, und mit dieser perfektionierung ausgestattete uhr

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EP2533109A1 true EP2533109A1 (de) 2012-12-12
EP2533109B1 EP2533109B1 (de) 2019-03-13

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EP11004697.6A Active EP2533109B1 (de) 2011-06-09 2011-06-09 Mechanismus zur vermeidung der schwerkraftbedingten gangvariationen auf einer reguliervorrichtung mit spiralunruh, und mit dieser perfektionierung ausgestattete uhr

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US (1) US9134702B2 (de)
EP (1) EP2533109B1 (de)
CN (1) CN103797426B (de)
WO (1) WO2012168773A1 (de)

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CN110161829A (zh) * 2018-02-12 2019-08-23 斯沃奇集团研究和开发有限公司 对由佩戴引起的角向加速不敏感的钟表振荡器
EP3978383A1 (de) 2020-10-02 2022-04-06 Eppendorf AG Vorrichtung zum bereitstellen von autoklavierbaren reaktionsgefässen

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EP3252545B1 (de) * 2016-06-03 2019-10-16 The Swatch Group Research and Development Ltd. Uhrenmechanismus zum einstellen der unruhträgheit
FR3059792B1 (fr) * 2016-12-01 2019-05-24 Lvmh Swiss Manufactures Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif
EP3382468B1 (de) * 2017-03-30 2020-01-15 The Swatch Group Research and Development Ltd Uhrwerk mit verlängerung der gangreserve
EP3650954A1 (de) * 2018-11-09 2020-05-13 Montres Breguet S.A. Regulierorgan für armbanduhr
EP3770694B1 (de) * 2019-07-23 2021-12-08 Omega SA Anschlagkäfig für uhr mit zwei elastischen anschlagelementen
EP4194958A1 (de) * 2021-12-10 2023-06-14 Blancpain SA Uhrwerk mit einem beweglichen organ, das mit mitteln zur variablen einstellung der neigung versehen ist

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CN110161829A (zh) * 2018-02-12 2019-08-23 斯沃奇集团研究和开发有限公司 对由佩戴引起的角向加速不敏感的钟表振荡器
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EP3978383A1 (de) 2020-10-02 2022-04-06 Eppendorf AG Vorrichtung zum bereitstellen von autoklavierbaren reaktionsgefässen

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CN103797426B (zh) 2016-10-05
WO2012168773A1 (fr) 2012-12-13
US9134702B2 (en) 2015-09-15
US20140098647A1 (en) 2014-04-10
EP2533109B1 (de) 2019-03-13

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