EP1914604A1 - Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique - Google Patents

Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique Download PDF

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Publication number
EP1914604A1
EP1914604A1 EP06122619A EP06122619A EP1914604A1 EP 1914604 A1 EP1914604 A1 EP 1914604A1 EP 06122619 A EP06122619 A EP 06122619A EP 06122619 A EP06122619 A EP 06122619A EP 1914604 A1 EP1914604 A1 EP 1914604A1
Authority
EP
European Patent Office
Prior art keywords
cam
wheel
energy source
movement according
periphery
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.)
Withdrawn
Application number
EP06122619A
Other languages
German (de)
English (en)
French (fr)
Inventor
Alberto Papi
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.)
Girard Perregaux SA
Original Assignee
Girard Perregaux 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 Girard Perregaux SA filed Critical Girard Perregaux SA
Priority to EP06122619A priority Critical patent/EP1914604A1/fr
Priority to CNA2007800388388A priority patent/CN101542400A/zh
Priority to EP07821589A priority patent/EP2076821B1/fr
Priority to AT07821589T priority patent/ATE491171T1/de
Priority to JP2009532818A priority patent/JP5005035B2/ja
Priority to DE602007011091T priority patent/DE602007011091D1/de
Priority to PCT/EP2007/061225 priority patent/WO2008046916A2/fr
Publication of EP1914604A1 publication Critical patent/EP1914604A1/fr
Priority to HK09110065.0A priority patent/HK1132556A1/xx
Withdrawn legal-status Critical Current

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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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/22—Compensation of changes in the motive power of the mainspring

Definitions

  • the present invention relates to a movement for a timepiece comprising a power source mounted on a frame and having a variable output torque depending on its state of charge.
  • the energy source is intended to maintain the oscillatory movement of a mechanical oscillator through a finishing gear comprising a compensation device.
  • the latter has an input kinematically connected to the power source, directly or via at least one mobile, and an output kinematically connected to the mechanical oscillator and is arranged to transmit a substantially constant torque to the mechanical oscillator regardless of the state of charge of the energy source.
  • Such movements have been known for a long time, especially in the field of clocks, to allow the use of a spring with a large power reserve, as a source of energy, while smoothing the inevitable variations in the torque applied by this spring to the work train, these arising from the change in the state of charge of the spring during the operation of the clock. More specifically, it can be generally considered that the more a spring is loaded, the higher the torque that it transmits to the finishing gear train.
  • chain rocket arranged to act further upstream, more precisely in contact with a barrel, compared to the secondary spring mechanisms.
  • These movements comprise a rocket, which is a conically shaped member provided with a helical groove on which a chain connected to the barrel is wound.
  • a rocket which is a conically shaped member provided with a helical groove on which a chain connected to the barrel is wound.
  • the chain wraps around the rocket and the barrel spring stretches.
  • a constant radius wheel is mounted coaxially to the rocket and is provided to transmit the energy of the mainspring from the rocket to the workings of the movement. The energy of the mainspring is thus transmitted with a constant torque to the workings of the movement.
  • the main purpose of the present invention is to propose an alternative to the known mechanisms of the prior art, by proposing a movement for a timepiece comprising a device for compensating the variations of the torque released by a power source whose construction makes it possible to ensure high operating reliability, while providing limited space, reasonable complexity and reasonable manufacturing costs.
  • the present invention more particularly relates to a movement for a timepiece of the type mentioned above, characterized in that the compensation device comprises a cam having a periphery of variable radius extending substantially in a general plane, the variations of the radius of the cam being a function of those of the output torque of the energy source.
  • the compensation device further comprises an intermediate linking mechanism arranged so as to provide a kinematic connection substantially without sliding between the periphery of the cam and the finishing train.
  • the compensation mechanism comprises exclusively constituents having respective rigid general forms.
  • the movement according to the invention has a less bulky structure than the mechanisms of the prior art and less complex and therefore less expensive to manufacture.
  • the compensation device provides great flexibility in its construction, in particular to define the implantation of the cam in the movement.
  • the intermediate link mechanism comprises a rocker pivoting about a fixed shaft on the frame and carrying a pinion having a permanent kinematic connection with a wheel, mounted freely in rotation around the wheel.
  • fixed shaft and arranged in permanent engagement with at least one mobile of the work train, the gear also being arranged in engagement, substantially without sliding, with the periphery of the cam.
  • the shape of the periphery of the cam can be adjusted precisely, with great flexibility, depending on the behavior of the energy source, in terms of the torque transmitted as a function of its state of charge, while ensuring a reliable transmission of energy from the power source to the mechanical oscillator.
  • the periphery of the cam is associated with the input of the compensation device, it is advantageously provided that the pinion is arranged in engagement with a wheel of a reduction gear for tuning the characteristics. of the energy source, especially in the case of a spring, the amplitude of its deformations, with the dimensioning and the number of teeth of the cam.
  • the linking mechanism comprises an additional cam, of variable radius, kinematically connected, by its periphery, at the periphery of the first cam and dimensioned and in such a way that the sum of their respective radii, taken on a segment connecting their respective centers, is constant, the additional cam being integral in rotation with a drive wheel kinematically connected to the energy source.
  • each of the two cams partially compensates for the output torque variations of the energy source, so that the torque delivered at the output of the compensation device is constant regardless of the state of charge of the source. energy, the kinematic connection between the two cams being very safe.
  • the compensation device comprises a differential gear whose cam defines an input and whose output is kinematically connected to the mechanical oscillator.
  • the differential has an additional input through which the load of the energy source can be realized.
  • FIG. 1a shows a simplified top view of a part of a movement for a timepiece having a compensation device according to a first embodiment of the present invention
  • Figure 1b shows a simplified top view of a first detail of the movement of Figure 1a;
  • Figure 2a shows a simplified cross-sectional view of the movement of Figure 1a
  • Figure 2b shows a simplified top view of a second detail of the movement, visible in Figure 2a;
  • FIG. 2c represents a simplified top view of a third detail of the movement, visible in FIG. 2a.
  • FIG. 3 shows a simplified top view of a part of a movement for a timepiece having a compensation device according to a second embodiment of the present invention.
  • Figure 1a shows a simplified top view of a part of a timepiece movement having a compensation device according to a first embodiment of the present invention. More precisely, only the elements of the movement involved in the kinematic chain relating to the transmission of energy, from the energy source to the mechanical oscillator whose oscillations are maintained by this energy, have been illustrated.
  • the energy source takes the form of a barrel 1 housing a barrel spring (visible in Figure 2a), the latter being intended to maintain the oscillations of a pendulum 2, in particular via of a finishing train and an exhaust of which only the wheel 3 and the pinion 4 have been schematized.
  • the finishing gear comprises a compensation device 5 to allow to maintain oscillations of the balance with a constant force and thus improve its accuracy of operation.
  • a toothed output wheel 6 is mounted on the barrel, being integral with it in rotation and, being arranged in engagement with a first mobile 7 of a reduction gear of the compensation device, carried by the frame of the movement. (visible in Figure 2a).
  • a pinion 8 of the first mobile meshes with a first wheel 9 of the wheel, which itself is engaged with a second wheel 10 of the wheel.
  • the second wheel 10 is arranged in engagement with the periphery of a cam 12, toothed, advantageously having a shape substantially following an archimedean curve.
  • the first is mounted on a rocker 13 pivoting relative to the frame of the movement, about the axis 14 of rotation of the first wheel 9
  • the second wheel 10 continuously transmits the movements of the first wheel 9 to the cam 12, whatever the value of the radius of the cam in contact with the second wheel 10.
  • an output wheel 15 of the compensation device is mounted coaxially with the cam 12, in order to provide a constant torque to the finishing gear located downstream, that is to say in the direction of the mechanical oscillator.
  • the structure of the planned mechanical connection between the cam 12 and the output wheel 15 will be discussed in detail below, in connection with Figure 2a.
  • the output wheel meshes with a first mobile 16 of a multiplicative gear train having, after the first mobile 16, a second mobile 17, a large average 18, a third mobile 19 and a second mobile 20 meshing with the pinion. exhaust 4.
  • the number of mobile gear that has just been described is not limiting. It should be noted that the mechanical characteristics of the mainspring as well as the dimensions and the number of teeth of the cam affect the composition of the gear train which connects them to one another. Likewise, the dimensions of the cam and of the output wheel of the compensation device, the nature and the characteristics of the mechanical oscillator supplied with energy influence the composition of the multiplicative gear train.
  • FIG. 2a represents a simplified cross-sectional view of the movement of FIG. 1a, on which the mainspring 22 is apparent, as well as the fact that the drum of the barrel 1 does not have toothing as far as the transmission of the couple of its spring is made from the output wheel 6.
  • the compensation device comprises a differential gear 23 whose cam 12 defines a first input, while the wheel 15 defines its output, at constant torque.
  • the differential gear 23 is mounted on the frame 24 of the movement by a central shaft.
  • the output wheel 15 is screwed onto a core 26, free to rotate on the shaft 25 and having a radial toothing 27.
  • a differential bridge 30 is screwed onto the cam 12, two satellites 31 being rotatably mounted by their respective ends, on the one hand, in the cam 12 and, on the other hand, in the differential bridge 30.
  • satellites 31 comprises a pinion 32 and a wheel 33, the pinion 32 being arranged in engagement with the toothing 27 of the core 26.
  • the differential gear 23 has a second input in the form of a wheel 35 mounted rotatably on the central shaft.
  • the wheel 35 carries a radial toothing 36 directed towards the shaft 25 and arranged in engagement with the wheel 33 of each of the satellites 31.
  • the wheel 35 fulfills the input function of the differential to allow the winding of the mainspring as shown better in FIG. 2b, on which has been schematized the kinematic chain connecting an external control member 40 to this wheel 35.
  • the external control member is arranged so as to drive in rotation a winding pinion 41 meshing with a crown wheel 42, itself engaged with a winding crown 43. This is arranged in engagement with the wheel input 35 of the differential gear 23, the latter ensuring the establishment of a kinematic connection between the external control member 40 and the barrel 1, as will be explained in detail below.
  • a ratchet (not shown) of conventional type is also provided in the winding train to prevent unwanted rotation of the wheels when no winding operation is in progress.
  • Barrel 1 is by consequently driven in rotation, in the counter-clockwise direction in FIG. 1a, reloading its spring 22 whose inner end is integral with the barrel shaft 50, fixed with respect to the frame.
  • the barrel spring 22 transmits its force to the cam 12 tending to rotate it clockwise, in Figures 1a and 1b.
  • This rotation of the cam is however possible only outside the rest phases of the escape wheel 3, namely when the output wheel 15 of the differential is not locked.
  • the satellites 31 being integral with the cam by their respective axes, they are driven in the same rotational movement, which rolls their wheels 33 on the toothing 36 of the input wheel 35. The satellites then turn on their own by transmitting a torque to the core 26, by its toothing 27, thus to the output wheel 15.
  • a carriageway 60 intended to carry a minute hand (not shown) is carried by the shaft of the large average 18 and itself carries a wheel of hours 61, intended to carry an hour hand (not shown), a timer 62 ensuring the necessary multiplication between these two bodies.
  • a time setting train is thus advantageously provided for connecting the external control member to the timer 62.
  • a mechanism for indexing the angular position of the barrel shaft 50 is provided and shown isolated in FIG. 2c, by way of nonlimiting illustration.
  • This mechanism has the shape of a wheel 70 with sawtooth toothing, integral in rotation with the barrel shaft 50 and cooperating with a pawl 71.
  • This indexing mechanism makes it possible to adjust the angular position of the barrel. barrel shaft for controlling the minimum value of the output torque provided by the mainspring 22 which will be associated with the greatest useful radius of the cam 12.
  • This minimum value is predefined during the manufacture of the movement, depending on the mechanical properties the barrel spring 22 used. This value generally defines the beginning of a range in which the torque delivered by the mainspring has regular variations as a function of its state of charge, typically characterized by the number of turns of the barrel.
  • a stop 72 carried by the cam 12 and intended to cooperate with a fixed bearing surface 73 (shown schematically in Figure 1b) of the frame for stopping the rotation of the cam when the minimum value selected in manufacturing for the output torque of the barrel is reached.
  • a similar stop may be provided to limit the reassembly when the minimum radius of the cam is reached, the latter being advantageously associated with a maximum value of the output torque supplied by the mainspring 22. This value then marks the end of the range of use of the mainspring as mentioned above.
  • Those skilled in the art may also provide a torque limiting mechanism of conventional type in the winding train, to avoid damaging the gears, without departing from the scope of the present invention.
  • the gear train namely the wheels 6, 9 and 10 and the mobile 7, can be chosen so that the total number of revolutions of the barrel 1, corresponding to its range of use, is associated with substantially one revolution of the cam 12.
  • FIG. 3 represents a simplified top view of a part of a timepiece movement comprising a compensation device according to a second embodiment of the present invention.
  • This second embodiment illustrates an alternative linking mechanism to that of the first embodiment.
  • the output wheel 6 of the barrel 1 meshes with a first mobile 80 of a gear train, itself engaged with a second mobile 81.
  • the latter drives a mobile link via a wheel 82, mounted integral in rotation with a first cam 83, being coaxial therewith.
  • the first cam 83 is arranged in engagement, by its periphery, with a second cam 84 which, for example, can advantageously fulfill the input function of a differential gear, similar to the differential 23 described in connection with the first embodiment.
  • the two cams 83 and 84 are dimensioned such that their respective peripheries are engaged continuously.
  • their respective rays are such that, when considering the rays located on the segment 85 connecting the centers of the cams, at each moment, their sum is constant.
  • the respective values of their radii are adjusted in such a way that the torque supplied by the second cam 84 is constant regardless of the state of charge of the spring of the barrel 1, therefore whatever the output torque transmitted by the barrel at the exit wheel 6.
  • the radius of the first cam increases to compensate for substantially more than the decrease in the torque that it receives, that is to say to transmit to the second cam 84 a couple whose value tends to increase very slightly.
  • the radius of the second cam 84 decreases progressively so as to compensate exactly for the increase in the torque that the first cam 83 transmits to it, in order to globally provide a constant torque to the mechanical oscillator (not shown) disposed downstream.
  • the present invention is not limited by the nature of the energy source described and shown here.
  • the invention allows the use of barrel springs so-called “slow” or low revolutions.
  • This type of springs is not the most common because the output torque is high and has a significant variation between the two ends of its range of use in torque.
  • they have the particular advantage of limiting the risk of sticking more common turns with springs "high speed” or high revolutions.
  • the present invention can be used to support the significant torque that is transmitted to the gear train by parallel drums.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Springs (AREA)
  • Electromechanical Clocks (AREA)
  • Nitrogen Condensed Heterocyclic Rings (AREA)
  • Control Of Stepping Motors (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Pens And Brushes (AREA)
  • General Electrical Machinery Utilizing Piezoelectricity, Electrostriction Or Magnetostriction (AREA)
EP06122619A 2006-10-19 2006-10-19 Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique Withdrawn EP1914604A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP06122619A EP1914604A1 (fr) 2006-10-19 2006-10-19 Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique
CNA2007800388388A CN101542400A (zh) 2006-10-19 2007-10-19 能量源和机械振荡器间以恒定扭矩传递能量的时钟机芯
EP07821589A EP2076821B1 (fr) 2006-10-19 2007-10-19 Mouvement horloger avec transmission d'energie a couple constant entre la source d'energie et l'oscillateur mecanique
AT07821589T ATE491171T1 (de) 2006-10-19 2007-10-19 Uhrwerk mit konstantdrehmomentübertragung zwischen der energiequelle und dem mechanischen oszillator
JP2009532818A JP5005035B2 (ja) 2006-10-19 2007-10-19 動力源と機械的発振装置との間の動力伝達を一定トルクで行う時計のムーブメント
DE602007011091T DE602007011091D1 (de) 2006-10-19 2007-10-19 Uhrwerk mit konstantdrehmomentübertragung zwischen der energiequelle und dem mechanischen oszillator
PCT/EP2007/061225 WO2008046916A2 (fr) 2006-10-19 2007-10-19 Mouvement horloger avec transmission d'energie a couple constant entre la source d'energie et l'oscillateur mecanique
HK09110065.0A HK1132556A1 (en) 2006-10-19 2009-10-29 Clockwork with constant-torque transmission between the power source and the mechanical oscillator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06122619A EP1914604A1 (fr) 2006-10-19 2006-10-19 Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique

Publications (1)

Publication Number Publication Date
EP1914604A1 true EP1914604A1 (fr) 2008-04-23

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP06122619A Withdrawn EP1914604A1 (fr) 2006-10-19 2006-10-19 Mouvement horloger avec transmission d'energie à couple constant entre la source d'energie et l'oscillateur mécanique
EP07821589A Not-in-force EP2076821B1 (fr) 2006-10-19 2007-10-19 Mouvement horloger avec transmission d'energie a couple constant entre la source d'energie et l'oscillateur mecanique

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07821589A Not-in-force EP2076821B1 (fr) 2006-10-19 2007-10-19 Mouvement horloger avec transmission d'energie a couple constant entre la source d'energie et l'oscillateur mecanique

Country Status (7)

Country Link
EP (2) EP1914604A1 (zh)
JP (1) JP5005035B2 (zh)
CN (1) CN101542400A (zh)
AT (1) ATE491171T1 (zh)
DE (1) DE602007011091D1 (zh)
HK (1) HK1132556A1 (zh)
WO (1) WO2008046916A2 (zh)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975746A3 (en) * 2007-03-27 2009-04-15 Seiko Epson Corporation Timepiece
CH705079A1 (fr) * 2011-06-10 2012-12-14 Haute Ecole Arc Source d'énergie mécanique pour mouvement horloger à couple de sortie prédéfini.
CN102160003B (zh) * 2008-09-18 2013-04-17 阿根豪尔股份公司 包含恒力设备的钟表机芯
CH705967A1 (fr) * 2012-01-09 2013-07-15 Lvmh Swiss Mft Sa Organe réglant pour montre ou chronographe.
DE102013102180A1 (de) 2012-03-07 2013-09-26 Montres Romain Gauthier Sa Uhrwerk mit konstantem Drehmoment
EP2701013A1 (fr) * 2012-08-23 2014-02-26 Audemars Piguet (Renaud et Papi) SA Mouvement d'horlogerie à réserve de marche étendue
EP2876507A1 (en) * 2014-06-23 2015-05-27 Ponomarev, Dmitrij Maksimovich Timepiece
EP3112949A1 (fr) 2015-07-01 2017-01-04 Cartier International AG Source d'energie mecanique pour mouvement horloger
EP3217227A1 (fr) * 2016-03-11 2017-09-13 The Swatch Group Research and Development Ltd. Mecanisme regulateur d'horlogerie a echappement magnetique optimise
WO2021023768A1 (en) * 2019-08-07 2021-02-11 Montre Liquide Ag Compensator train

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008268177A (ja) * 2007-03-27 2008-11-06 Seiko Epson Corp 時計
EP2546706B1 (fr) * 2011-07-13 2017-02-22 ETA SA Manufacture Horlogère Suisse Mouvement d'horlogerie comprenant un module muni d'un mobile engrenant avec un autre mobile pivotant dans une base sur laquelle est monté le module
JP6130773B2 (ja) * 2013-11-27 2017-05-17 シチズン時計株式会社 香箱
JP2015152374A (ja) * 2014-02-13 2015-08-24 シチズンホールディングス株式会社 香箱
EP3312681B1 (fr) * 2016-10-19 2020-01-29 Montres Breguet S.A. Mouvement horloger comportant un dispositif d'égalisation d'un couple moteur

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US594654A (en) * 1897-11-30 Half to thomas j
FR661811A (fr) * 1927-10-10 1929-07-30 Mouvement d'horlogerie à ressort, spécialement pour montres
US2789414A (en) * 1947-08-28 1957-04-23 George S Andrews Automatic regulator for timepieces
CH371742A (de) * 1960-03-18 1963-05-15 Kienzle Uhrenfabriken Ag Vorrichtung zum annähernd Konstanthalten des Antriebsmomentes in Zeitmesswerken, insbesondere in elektrischen Uhren, mit periodisch aufziehbarem Federantrieb

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5692985U (zh) * 1979-12-19 1981-07-24
DE69940727D1 (de) * 1999-08-04 2009-05-28 Piguet Frederic Sa Vorrichtung zur Anzeige der Gangreserve einer Uhr

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US594654A (en) * 1897-11-30 Half to thomas j
FR661811A (fr) * 1927-10-10 1929-07-30 Mouvement d'horlogerie à ressort, spécialement pour montres
US2789414A (en) * 1947-08-28 1957-04-23 George S Andrews Automatic regulator for timepieces
CH371742A (de) * 1960-03-18 1963-05-15 Kienzle Uhrenfabriken Ag Vorrichtung zum annähernd Konstanthalten des Antriebsmomentes in Zeitmesswerken, insbesondere in elektrischen Uhren, mit periodisch aufziehbarem Federantrieb

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1975746A3 (en) * 2007-03-27 2009-04-15 Seiko Epson Corporation Timepiece
US7832924B2 (en) 2007-03-27 2010-11-16 Seiko Epson Corporation Timepiece
CN102160003B (zh) * 2008-09-18 2013-04-17 阿根豪尔股份公司 包含恒力设备的钟表机芯
CH705079A1 (fr) * 2011-06-10 2012-12-14 Haute Ecole Arc Source d'énergie mécanique pour mouvement horloger à couple de sortie prédéfini.
WO2012168443A3 (fr) * 2011-06-10 2013-01-31 Haute Ecole Arc Source d'energie mecanique pour mouvement horloger a couple de sortie predefini
CH705967A1 (fr) * 2012-01-09 2013-07-15 Lvmh Swiss Mft Sa Organe réglant pour montre ou chronographe.
DE102013102180A1 (de) 2012-03-07 2013-09-26 Montres Romain Gauthier Sa Uhrwerk mit konstantem Drehmoment
DE102013102180B4 (de) * 2012-03-07 2020-08-27 Montres Romain Gauthier Sa Uhrwerk mit konstantem Drehmoment
CN103631126A (zh) * 2012-08-23 2014-03-12 爱彼（雷诺和帕皮机芯厂）股份公司 具有用于延长运行的动力储备的计时器机芯
US8956042B2 (en) 2012-08-23 2015-02-17 Audemars Piguet (Renaud Et Papi) Sa Timepiece movement with power reserve for extended operation
CN103631126B (zh) * 2012-08-23 2017-05-31 爱彼（雷诺和帕皮机芯厂）股份公司 具有用于延长运行的动力储备的计时器机芯
EP2701013A1 (fr) * 2012-08-23 2014-02-26 Audemars Piguet (Renaud et Papi) SA Mouvement d'horlogerie à réserve de marche étendue
EP2876507A1 (en) * 2014-06-23 2015-05-27 Ponomarev, Dmitrij Maksimovich Timepiece
EP3112949A1 (fr) 2015-07-01 2017-01-04 Cartier International AG Source d'energie mecanique pour mouvement horloger
EP3217227A1 (fr) * 2016-03-11 2017-09-13 The Swatch Group Research and Development Ltd. Mecanisme regulateur d'horlogerie a echappement magnetique optimise
US10241475B2 (en) 2016-03-11 2019-03-26 The Swatch Group Research And Development Ltd Timepiece regulating mechanism with optimised magnetic escapement
WO2021023768A1 (en) * 2019-08-07 2021-02-11 Montre Liquide Ag Compensator train

Also Published As

Publication number Publication date
HK1132556A1 (en) 2010-02-26
JP5005035B2 (ja) 2012-08-22
CN101542400A (zh) 2009-09-23
WO2008046916A2 (fr) 2008-04-24
WO2008046916A3 (fr) 2008-06-19
ATE491171T1 (de) 2010-12-15
DE602007011091D1 (de) 2011-01-20
JP2010507086A (ja) 2010-03-04
EP2076821B1 (fr) 2010-12-08
EP2076821A2 (fr) 2009-07-08

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