EP2786214B1 - Uhrenteil - Google Patents

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Publication number
EP2786214B1
EP2786214B1 EP12794960.0A EP12794960A EP2786214B1 EP 2786214 B1 EP2786214 B1 EP 2786214B1 EP 12794960 A EP12794960 A EP 12794960A EP 2786214 B1 EP2786214 B1 EP 2786214B1
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EP
European Patent Office
Prior art keywords
wheel
pivoting system
wheels
timepiece according
escapement
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EP12794960.0A
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English (en)
French (fr)
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EP2786214A1 (de
Inventor
Yves Corthesy
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LVMH Swiss Manufactures SA
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LVMH Swiss Manufactures SA
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Publication of EP2786214A1 publication Critical patent/EP2786214A1/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
    • G04B18/00—Mechanisms for setting frequency
    • G04B18/08—Component parts or constructional details
    • 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
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots

Definitions

  • the present invention relates to the field of mechanical watchmaking. It relates, more particularly, to a timepiece comprising an exhaust trim correction system, to reduce the influence of the variations of orientation of said timepiece, on its march. It comprises a frame carrying an energy source, a cage comprising a first pivoting system about a first axis, by means of which a support is pivotally mounted inside said cage, the first pivoting system comprising two shafts. coaxial. An exhaust is further arranged on the support.
  • the cage comprises a second pivoting system about a second axis substantially perpendicular to the first, by means of which the cage is pivotally mounted with reference to the frame.
  • the second pivoting system comprises two shafts, coaxial.
  • a shaft of the first pivoting system carries a wheel forming a first kinematic chain with a wheel carried by a shaft of the second pivoting system.
  • a timepiece as mentioned above is known in particular by the application WO2009 / 026735 .
  • An embodiment is proposed at figure 1 . More specifically, this document discloses a timepiece comprising at least two articulated supports, a first 10 being articulated with reference to the frame along a first axis, the second 12 being articulated with reference to the first support along a second axis orthogonal to the first.
  • the exhaust 14 is mounted on the second support and, thanks to the joint, can maintain a substantially stable orientation, preferably substantially horizontal, regardless of the position of the frame.
  • horizontal orientation it is defined that the planes of the mobiles are horizontal, the axes of these mobiles are vertical.
  • the timepiece comprises a first gear transmission gear 16, kinematically connected to a power source and bringing this energy to the exhaust 14, and a second reference gear train 18, connected to a fixed element of the frame.
  • the two gear trains are arranged in parallel, so that any rotation between the supports and the frame or between the supports themselves, results in identical rotation of the gear trains and reference transmission.
  • the timepiece further comprises an inverter system 20 making it possible for the last mobiles of the transmission and reference gear trains to rotate in opposite directions.
  • a differential correction device 22 makes it possible to cancel all the movements of the supports in order to bring to the exhaust only the energy coming from the energy source.
  • the transmission gear train 16 brings to a first input of the differential correction device, a movement corresponding to the rotation of the supports (R) and to the rotation induced by the torque of the energy source (E).
  • the reference gear train 18 also transmits a movement corresponding to the rotation of the supports (R), to the inverter system 20, the latter thus transmitting an inverse movement (-R) to a second input of the differential correction device.
  • the latter is arranged so as to perform the algebraic mean of the first input and the second input (ie (R-R + E) / 2), so that, at its output, only a rotation induced by the couple of the energy source.
  • the supports carry the two gear trains, respectively transmission 16 and reference 18, an inverter system 20 and a differential correction device 22, in addition to the exhaust system.
  • the present invention aims to reduce the number of parts carried by the media and reduce the volume occupied by the latter.
  • one of the wheels carried by the second pivoting system is kinematically connected to the power source, and the other wheel carried by the pivoting system is fixed relative to the frame.
  • the two wheels carried by the first pivoting system are connected kinematically with an input mobile of a differential arranged to transmit by an output mobile the average of the rotations received at its inputs, said output mobile being kinematically connected. at the exhaust and the mobile input and output of the differential being movable about an axis of rotation parallel to the axis of rotation of the exhaust mobiles.
  • a cage 50 which is advantageously defined by a substantially annular reinforcement to limit the volume it occupies in its movements, as will be seen later.
  • This cage 50 comprises a first pivoting system 52 around a first axis AA, more particularly visible on the figure 3 .
  • This first pivoting system 52 comprises two shafts 54a and 54b, arranged coaxially along the axis AA.
  • the term tree is not limiting and must be understood in a functional sense, that is to say that one could envisage a construction in which the trees are defined by two parts of a tree, on which pivot the elements that will now be described.
  • an index a refers to an element of the shaft 54a and an index b refers to an element of the shaft 54b.
  • Each shaft 54a and 54b comprises a rod 58a and 58b pivoting on two bearings 60a and 60b disposed at the ends of a tube 62a and 62b. These are fixed on a support 64 which will be described in more detail below.
  • Each tube 62a or 62b receives, on its outer periphery, a bearing, for example ball, of which an inner ring 68a, 68b is fixed on the tube 62a, 62b and whose outer ring 70a, 70b is disposed in an opening 72a, 72b of the cage 50.
  • a washer 74a, 74b closes the bearing.
  • This first pivoting system 52 makes it possible to pivot the support 64 inside the cage 50.
  • each rod 58a, 58b receives, at a distal end with reference to the center of the cage 50, a wheel 76a, 76b, and at a second proximal end with reference to the center of the cage 50, a pinion 78a, 78b.
  • the cage 50 also comprises a second pivoting system 152 around a second axis BB, substantially perpendicular to the first axis AA.
  • This second pivoting system comprises two shafts 154a and 154b, arranged coaxially along the axis BB.
  • the construction of the shafts of the second pivot system is similar to that described above.
  • the elements of the second pivot system are designated by reference numbers showing the reference numbers of the first pivot system, preceded by a 1.
  • Each shaft 154a, 154b comprises a rod 158a, 158b pivoting on two bearings 160a, 160b disposed at the ends of a tube 162a, 162b, fixed in an opening 172a, 172b of the cage 50.
  • Each tube 162a, 162b receives, on its outside circumference, a bearing, for example balls, including an inner ring 168a, 168b, is fixed on the tube 162a, 162b, and the outer ring 170a, 170b is disposed in a housing of the frame, not shown.
  • a washer 174a, 174b closes the bearing. This second pivoting system makes it possible to rotate the cage 50 with reference to the frame.
  • each rod 158a, 158b receives, at a proximal end with reference to the center of the cage 50, a wheel 176a, 176b. We will return later to the distal end of rods 158a and 158b.
  • Each wheel 76a, 76b of the first pivot system 52 forms a kinematic chain with a wheel 176a, 176b of the second transmission system. pivoting. There is thus a first kinematic chain between the wheels 76a and 176a of two shafts 54a and 154a, respectively of the first and second pivot systems, and a second kinematic chain between the other wheels 76b and 176b of the two other shafts 54b and 154b.
  • these kinematic links are made respectively by a reference 80a, 80b mounted on the cage 50.
  • the reference 80a, 80b is disposed substantially at 45 ° with reference to the wheels with which it meshes.
  • Such an arrangement allows that only this reference 80a, 80b has a conical type toothing, while the wheels 76a, 176a, respectively 76b, 176b have straight teeth. All these wheels are flat.
  • Such an embodiment is particularly interesting, compared to the configuration of the meshing between the wheels of the transmission and reference chains of the timepiece of the state of the art proposed at the time. figure 1 .
  • the drive ratios of the first driveline and the second drivetrain are identical, so that the wheels 76a and 76b carried by the two shafts 54a and 54b of the first pivoting system 52 are driven to the same speed by the movements of the support 64.
  • the wheels 76a, 76b, 176a and 176b of the pivot systems 52a and 52b and the references 80a and 80b have the same number of teeth. They are also of the same diameter.
  • the wheel 76a and the pinion 78a of a first shaft 54a of the first pivot system 52 face those 76b and 78b of the other shaft 54b of this pivot system. Seen from the center of the cage 50, the pinions 78a and 78b are thus driven in opposite directions of rotation, at the same absolute speed, without however being kinematically connected to each other by a gear train.
  • each of these pinions 78a and 78b meshes with an input of a differential 200, the axes of rotation of the mobiles are parallel to that of the mobiles of the exhaust.
  • the differential 200 is intended to have a substantially constant orientation, typically along a substantially vertical axis.
  • the pinion 78a meshes with a first board 202a provided with teeth to edge.
  • This first plate 202a is integral with a first sun gear 204a meshing with a first satellite 206a pivotally mounted on a planet carrier 208.
  • the latter is coaxial with the first sun gear 204a and is pivotable with reference to the other elements of the differential .
  • the planet carrier 208 is provided with a toothing and defines the output of the differential.
  • the pinion 78b meshes with a second board 202b provided with teeth to sing.
  • This second plate 202b is integral with a second sun gear 204b meshing with a second satellite 206b pivotally mounted on the planet carrier 208.
  • the second satellite 206b is also arranged to mesh with the first satellite 206a.
  • Such a differential configuration 200 allows the output wheel, that is to say the planet carrier 208, to transmit the average of the rotations received at its inputs.
  • the first board 202a and the second board 202b rotate in different directions.
  • the ratios between the pinions 78a, 78b and the boards 202a and 202b are calculated so that the boards rotate at the same absolute speed.
  • the proposed configuration allows a great compactness of the differential. Due to its configuration, it can be easily accommodated in a cavity of the support 64. These space savings offer the possibility of improving the pivoting of the elements of the differential 200.
  • pivots on bearings 210, the second board 202b and the planet carrier 208 are pivoted on bearings, respectively 212 and 214, for example balls, fixed in ad-hoc openings of the support 64.
  • the axis 209a of the first plate 202a is thus pivotally mounted between two bearings 210, typically formed by stones.
  • One is driven into a bridge 216 carried by the support 64 and the other is driven into a tube 218, also fixed on the support 64, typically by a screw 220 inserted into the tube.
  • the second board 202b is secured to a hub 222, comprising a central opening, through which the axis 209b of the second board.
  • the axis 209b of the second board is fitted in this central opening and is freely traversed by the axis 209a of the first board.
  • the axis 209b of the second board has a flange 224 which defines a groove with a flank of the hub 222.
  • An inner ring 226 of the ball bearing 212 is fitted in the groove, while an outer ring 228 of this bearing is fixed. on an additional bridge 230 of the support 64.
  • the second board 202b is thus guided in rotation from outside its axis 209b.
  • the second differential input is thus pivoted directly on the support 64.
  • the planet carrier 208 is provided with a central opening, inside which is fixed an outer ring 232 of the bearing 214.
  • An inner ring 234 is disposed in a groove defined by the support 64 and a collar 236 The planet carrier 208 is thus pivoted directly on the support 64.
  • the bearing 214 is slightly raised relative to the bottom of the cavity of the support 64, so that the planet carrier 208 does not rub on it.
  • One of the wheels carried by one of the shafts is kinematically connected to the power source.
  • it is a pinion 178a located at the distal end of the rod 158a of the second pivoting system which is engaged with the finishing gear train and which thus makes it possible to bring the torque of the power source to one of the inputs (in this case to the first board 202a) of the differential 200.
  • the other input of the differential 200 does not receive the torque from the power source. Since, as mentioned above, the differential 200 averages the rotations received at these inputs and the rotations due to the movement of the carrier 64 cancel each other out, the output of the differential 200, i.e. the planet carrier 208 therefore transmits only one rotation induced by the torque supplied by the energy source.
  • the planet carrier 208 is kinematically connected to the escapement, as can be seen particularly on the figure 4 by means of a rod 240 provided on the one hand with an escape gear 242 meshing with the planet carrier 208 and receiving, on the other hand, the escape wheel 244.
  • the rod 240 passes through the support 64, so that the regulating member 246 and the anchor 248 are located on the upper side of the bridge and are located at the periphery of the cage so as to be visible by a user.
  • the exhaust is of angle type, that is to say that the axes of the regulating member 246, the anchor and the escape wheel, are not aligned. This allows to bring the axis of the regulating member and that of the escape wheel.
  • the shaft 154b that is to say the shaft of the second pivot system opposite to that which is connected to the energy source, comprises a locking system with reference to the frame.
  • a square or a blocker 250 can be fixed on the rod, itself being locked in rotation in the frame. The rotations of the support 64 are well transmitted to the differential.
  • the support 64 can be advantageously ballasted. It defines an unbalance located at a lower level relative to the axes of the pivoting systems, participating in the orientation of the support 64 and the cage 50. Note that the system more generally allows to maintain a constant orientation of the exhaust, regardless of the position of the frame, this orientation may not be horizontal.
  • the timepiece that has just been described allows, compared to the state of the art, an optimization of the construction. Not only, the different rotational movements related to the movements of the support 64, are canceled without resorting to an inverter system, but, in addition, the construction is simplified and improved, to reduce the dimensioning of the cage 50. This is due to the combination of several parameters.
  • the arrangement of the differential 200 along an axis parallel to the axes of the mobiles of the exhaust makes it possible to reduce the diameter of the cage 50. Indeed, it will be possible to see on the figure 1 , that the axis of the differential was previously perpendicular to the axes of the mobiles of the exhaust.
  • the use of an angled escapement also has a positive effect.
  • This arrangement is made possible by the fact that the bridge has a working surface whose size and the free space makes it possible to position in a relatively simple manner the scores of the elements of the assortment.
  • the construction of the cage 50 and its pivoting means is also a factor of improvement. Indeed, the pivoting along the two axes AA and BB are done by means of a single cage 50.
  • the first pivoting system 52 serves as an interface between the cage 50 and the support 64. It is arranged on the side of the Inside the cage 50.
  • the second pivoting system serves as an interface between the cage 50 and the frame. It is disposed on the outside of the cage 50.
  • the cage 50 thus comprises two pairs of openings 72a, 72b and 172a, 172b, each pair being located respectively on one of the axes A-A and B-B.
  • the openings 72a, 72b are integral with the outer rings 70a, 70b of the bearings, while for the axis B-B, the openings 172a, 172b are integral with the inner rings 168a, 168b of the bearings.
  • the figure 5 proposes a variant of a timepiece according to the invention.
  • identical or similar elements have the same reference numbers.
  • the wheels 76a and 76b respectively carried by the shaft 54a and by the shaft 54b of the first pivoting system, are respectively connected to a first input and a second input of a differential 200, in a manner identical to that described above.
  • the wheel 76a forms a first kinematic chain with a first wheel 176a carried by a first shaft 154a of the second pivot system 152.
  • the wheel 176a is connected to the source of energy, as will be detailed below.
  • the wheel 76b forms a second kinematic chain with a second wheel 176b, in this case, coaxial with the first shaft 154a of the second pivot system 152.
  • the wheel 176b is fixed with reference to the frame.
  • the two wheels 176a and 176b are arranged coaxially on the first shaft 154a but are rotatably mounted relative to one another and relative to the cage 50, the wheel 176b being fixed with reference to the frame.
  • the second shaft 154b is a simple pivoting system of the cage 50 with reference to the frame.
  • the wheels 176a and 176b are disposed on either side of the wall of the cage 50.
  • the wheel 176a meshes with a reference 80a, in taken with the wheel 76a, while the wheel 176b meshes with a reference 80b, engaged with the wheel 76b.
  • the cage 50 is arranged so as to leave free the moving gear of the kinematic chains. This makes this variant a little less compact than the first.
  • the wheels 176a and 176b have different dimensions.
  • the drive ratios of the wheels 76a and 76b carried by the two shafts of the first pivoting system 52 are identical.
  • the wheels 76a, 76b and 176a, 176b of the first pivot system 52 and the second pivot system 152 and the references 80a, 80b have the same number of teeth.
  • the wheels 76a and 76b are not driven at the same speed, by adapting the gear ratios at the differential level, that is to say by having gear ratios. different gearing between the first input and the output, on the one hand, and between the second input and the output on the other hand, so that the movements of the cage are well compensated by the differential.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Gear Transmission (AREA)
  • Retarders (AREA)

Claims (17)

  1. Zeitmessgerät, dadurch gekennzeichnet, dass es Folgendes umfasst:
    - ein Gestell mit einer Energiequelle,
    - einen Käfig (50) mit einer Halterung (64), die im Innern des besagten Käfigs (50) über ein erstes Drehsystem (52) mit einer ersten und einer zweiten koaxialen Welle (54a, 54b) drehbar um eine erste Achse montiert ist, wobei besagter Käfig in Bezug auf das Gestell über ein zweites Drehsystem (152) mit einer ersten und einer zweiten koaxialen Welle (154a, 154b) um eine zweite, im Wesentlichen senkrecht zur ersten Achse verlaufende Achse drehbar montiert ist.
    - eine auf besagter Halterung (64) angeordnete Hemmung, deren bewegliche Teile (242, 244) um eine gemeinsame Achse drehbar angeordnet sind,
    in welchem ein erstes, von der ersten Welle (54a) des erstes Drehsystems (52) getragenes Rad (76a) ein erstes Räderwerk mit einem zweiten, von der ersten Welle (154a) des zweiten Drehsystems (152) getragenen Rad (76a) bildet, und ein erstes, von der zweiten Welle (154b) des ersten Drehsystems (52) getragenes Rad (76b) ein zweites Räderwerk mit einem zweiten, von der ersten (154a) oder zweiten (154b) Welle getragenen Rad (176b) des zweiten Drehsystems (152) bildet,
    und in dem:
    - eines der vom zweiten Drehsystem getragenen Räder (176a, 176b) kinetisch mit der Energiequelle verbunden ist, und das andere, von diesem Drehsystem getragene Rad in Bezug auf das Gestell befestigt ist,
    - und die beiden vom ersten Drehsystem getragenen Räder kinetisch mit einem beweglichen Eingangselement (202a, 202b) eines Ausgleichsgetriebes (200) verbunden sind, das so angeordnet ist, dass es über ein bewegliches Ausgangselement (208) das Mittel der an seinen Eingängen aufgenommenen Umdrehungen überträgt, wobei besagtes mobiles Ausgangselement (208) kinematisch mit der Hemmung verbunden ist,
    - wobei die beweglichen Eingangs- und Ausgangselemente des Ausgleichsgetriebes (200) beweglich um einer Drehachse parallel zur Drehachse der beweglichen Elemente der Hemmung angeordnet sind.
  2. Zeitmessgerät nach Anspruch 1, dadurch gekennzeichnet, dass die Übersetzungen dem ersten Räderwerk und dem zweiten Räderwerk identisch sind.
  3. Zeitmessgerät nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass das zweite Rad (176b) dem zweiten Räderwerk von der zweiten Welle (154b) des zweiten Drehsystems (152) getragen wird.
  4. Zeitmessgerät nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass das zweite Rad (176b) von der ersten Welle (154a) des zweiten Drehsystems (152) getragen wird.
  5. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Wellen (54a, 54b) des ersten Drehsystems (52) des Weiteren ein Zahnrad (78a, 78b) umfassen, das in einen Eingang des Ausgleichsgetriebes eingreift.
  6. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eines der Räder (176a, 176b) des zweiten Drehsystems kinematisch mit der Energiequelle verbunden ist.
  7. Zeitmessgerät nach Anspruch 6, dadurch gekennzeichnet, dass das Rad des zweiten Drehsystems, welches nicht kinematisch mit der Energiequelle verbunden ist, ein Sperrsystem (50) in Bezug auf das Gestell umfasst.
  8. Zeitmessgerät nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, dass besagtes mobiles Eingangselement des Ausgleichsgetriebes einen ersten Eingang (202a) und einen zweiten Eingang (202b) des Ausgleichsgetriebes umfasst, die jeweils mit einem ersten Sonnenrad (204a) und einem zweiten Sonnenrad (204b) verbunden sind, und jeweils in ein erstes Planetenrad (206a) und ein zweites Planetenrad (206b) eingreifen, wobei besagte Planetenräder drehbar um einen Planetenradträger (208) montiert sind und ineinander eingreifen, wobei besagter Planetenradträger (208) koaxial zu besagten Sonnenrädern ist und den Ausgang des Ausgleichsgetriebes abgrenzt.
  9. Zeitmessgerät nach Anspruch 8, dadurch gekennzeichnet, dass der Planetenradträger (208) kinematisch mit der Hemmung verbunden ist über einen Stab (240), der zum einen mit einem Zahnrad der Hemmung (242), welches kinematisch mit dem Planetenradträger (208) verbunden ist, versehen ist und zum anderen das Hemmungsrad (244) aufnimmt.
  10. Zeitmessgerät nach Anspruch 9, dadurch gekennzeichnet, dass besagter Stab durch die Halterung (64) führt, sodass ein regulierendes Element (246) und ein Anker (248) der Hemmung am Rand des Käfigs angeordnet sind.
  11. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das erste Räderwerk und das zweite Räderwerk des Weiteren eine Umlenkung (80a, 80b) aufweisen, die auf den Käfig (50) montiert ist, wobei besagte Umlenkung im Wesentlichen in einem Winkel von 45° zu den Rädern (76a, 76b und 176ab, 176b) jeweils des ersten Drehsystems (52) und des zweiten Drehsystems (152) steht.
  12. Zeitmessgerät nach Anspruch 11, dadurch gekennzeichnet, dass besagte Umlenkung (80a, 80b) eine konische Zahnung umfasst, wobei die Räder (76a, 76b und 176ab, 176b) des ersten Drehsystems (52) und des zweiten Drehsystems gerade Zahnungen aufweisen.
  13. Zeitmessgerät nach einem der Ansprüche 9 und 10, dadurch gekennzeichnet, dass die Räder (76a, 76b und 176a, 176b) des ersten Drehsystems (52) und des zweiten Drehsystems (152) und die Umlenkungen (80a, 80b) die gleiche Anzahl von Zähnen umfassen.
  14. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass einer der Eingänge des Ausgleichsgetriebes (200) und der Planetenradträger (208) direkt auf der Halterung (64) gedreht werden.
  15. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Hemmung ein Winkel ist.
  16. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das erste Drehsystem (52) und das zweite Drehsystem mit einem einzigen Käfig (50) zusammenwirken.
  17. Zeitmessgerät nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es so angeordnet ist, dass das durch die Energieübertragung an dem mit der Energiequelle verbundenen Räderwerk induzierte Moment ein Gegenmoment an dem anderen Räderwerk induziert.
EP12794960.0A 2011-12-02 2012-11-30 Uhrenteil Active EP2786214B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH01918/11A CH705836B1 (fr) 2011-12-02 2011-12-02 Pièce d'horlogerie.
CH00624/12A CH705831B1 (fr) 2011-12-02 2012-05-04 Pièce d'horlogerie.
PCT/EP2012/074082 WO2013079657A1 (fr) 2011-12-02 2012-11-30 Piece d'horlogerie

Publications (2)

Publication Number Publication Date
EP2786214A1 EP2786214A1 (de) 2014-10-08
EP2786214B1 true EP2786214B1 (de) 2019-07-03

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EP12794960.0A Active EP2786214B1 (de) 2011-12-02 2012-11-30 Uhrenteil

Country Status (7)

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US (1) US9645550B2 (de)
EP (1) EP2786214B1 (de)
JP (1) JP6246728B2 (de)
CN (1) CN103959180B (de)
CH (2) CH705836B1 (de)
HK (1) HK1201948A1 (de)
WO (1) WO2013079657A1 (de)

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EP3584640B1 (de) * 2016-06-13 2023-01-11 Rolex Sa Oszillator für uhr
USD864781S1 (en) * 2017-03-17 2019-10-29 Lvmh Swiss Manufactures Sa Watch movement
USD847665S1 (en) * 2017-03-17 2019-05-07 Lvmh Swiss Manufactures Sa Watch movement in a watch case
EP3407143A1 (de) * 2017-05-24 2018-11-28 Rolex Sa Mechanische verbindungsvorrichtung
EP3451075B1 (de) * 2017-08-21 2020-06-24 Montres Breguet S.A. Uhrwerk, das ein multiaxiales tourbillon umfasst
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US9645550B2 (en) 2017-05-09
US20140321250A1 (en) 2014-10-30
CH705831A2 (fr) 2013-06-14
CN103959180A (zh) 2014-07-30
HK1201948A1 (en) 2015-09-11
WO2013079657A1 (fr) 2013-06-06
EP2786214A1 (de) 2014-10-08
CH705836B1 (fr) 2016-01-15
CN103959180B (zh) 2017-04-12
JP6246728B2 (ja) 2017-12-13
JP2014533842A (ja) 2014-12-15
CH705836A1 (fr) 2013-06-14
CH705831B1 (fr) 2016-10-31

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