EP3312681A1 - Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst - Google Patents

Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst Download PDF

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Publication number
EP3312681A1
EP3312681A1 EP16194627.2A EP16194627A EP3312681A1 EP 3312681 A1 EP3312681 A1 EP 3312681A1 EP 16194627 A EP16194627 A EP 16194627A EP 3312681 A1 EP3312681 A1 EP 3312681A1
Authority
EP
European Patent Office
Prior art keywords
barrel
magnetic
cam
torque
magnetic element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16194627.2A
Other languages
English (en)
French (fr)
Other versions
EP3312681B1 (de
Inventor
Benoît LÉGERET
Davide Sarchi
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.)
Montres Breguet SA
Original Assignee
Montres Breguet 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 Montres Breguet SA filed Critical Montres Breguet SA
Priority to EP16194627.2A priority Critical patent/EP3312681B1/de
Priority to US15/686,463 priority patent/US10474109B2/en
Priority to JP2017173847A priority patent/JP6381757B2/ja
Priority to CN201710971750.7A priority patent/CN107966893B/zh
Publication of EP3312681A1 publication Critical patent/EP3312681A1/de
Priority to HK18112133.3A priority patent/HK1252772A1/zh
Application granted granted Critical
Publication of EP3312681B1 publication Critical patent/EP3312681B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C5/00—Electric or magnetic means for converting oscillatory to rotary motion in time-pieces, i.e. electric or magnetic escapements
    • G04C5/005—Magnetic or electromagnetic means
    • 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
    • G04B1/16—Barrels; Arbors; Barrel axles
    • 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
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor
    • G04B1/20—Protecting arrangements against rupture or overwinding of the mainspring located in the barrel or attached to the barrel
    • 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
    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C5/00—Electric or magnetic means for converting oscillatory to rotary motion in time-pieces, i.e. electric or magnetic escapements

Definitions

  • the present invention relates to a watch movement comprising a mechanism and a barrel adapted to drive the mechanism via a kinematic link arranged to exert a driving torque on the mechanism, the barrel comprising a drum and an arranged motor-spring in the drum so as to exert on the mechanism a motor torque which varies according to the degree of winding of the mainspring.
  • the watch movement further comprises an equalizing device kinematically connected to the barrel so as to be driven by the barrel and to be able to exert an auxiliary torque which adds to said engine torque to form together said driving torque.
  • the auxiliary torque is provided to vary according to the degree of winding of the mainspring so as to oppose the variations of the engine torque, and thus to substantially equalize the driving torque.
  • An object of the present invention is to overcome the aforementioned drawbacks of the prior art.
  • the invention achieves this goal by providing a watch movement according to the appended claim 1.
  • the formulation according to which the variation of the auxiliary torque opposes the variation of the engine torque, within a useful range of the degree of winding of the mainspring, amounts to saying that the derivative of the auxiliary torque with respect to the degree of winding is of opposite sign to the derivative of the engine torque with respect to the degree of arming. It follows further that the derivative of the auxiliary torque with respect to time is of opposite sign to the derivative of the engine torque with respect to time.
  • the equalizing device comprises a first magnetic element and a second magnetic element which are arranged to exert on one another a variable magnetic force according to their relative position, respectively the degree of arming of the mainspring.
  • the auxiliary torque produced by the equalizing device is generated by this variable magnetic force.
  • at least one of said first and second magnetic elements comprises a permanent magnet.
  • these two magnetic elements are respectively formed by a bipolar permanent magnet and a cam made of material with high magnetic permeability.
  • magnetic cam comprises a magnetic element including at least one physical parameter (radial / lateral or axial as appropriate), active in the magnetic interaction considered between the cam and another magnetic element with which it is associated, varies so as to generate with this other magnetic element a magnetic force between them, in the direction of a relative displacement between the cam and the other magnetic element, whose intensity varies as a function of this relative displacement.
  • the physical parameter in question may be a parameter specific to the cam, for example the intensity of a magnetic flux supplied by a magnetized material forming the cam, or relative to the other magnetic element, in particular the distance between them.
  • the equalizing device has several advantages. In particular, it forms a non-contact system so that the variable auxiliary torque that it provides is generated without friction. In addition, it is known that the magnetic forces that are caused by permanent magnets are conservative forces that derive from a magnetic potential. Thus, the auxiliary torque provided by the equalizing device also derives from a magnetic potential, so that the energy dissipated by the equalization device of the invention during a complete cycle of arming - disarming of the mainspring can theoretically be zero. The advantage conferred by such an equalization device will thus be appreciated without difficulty, bearing in mind that, especially in a device of the 'stackfreed' type, the energy supplied for the auxiliary torque is completely dissipated.
  • the Figures 1A and 1B respectively illustrate two alternative arrangements of the magnetic system, formed of first and second magnetic elements, of an equalization device according to the invention.
  • the first and second magnetic elements are respectively a magnetic cam and a bipolar magnet.
  • the cam is flat and is made of a magnetic material (for example NdFeB, SmCo or PtCo to form a second permanent magnet or a ferromagnetic material).
  • the cam 3A, respectively 3B is arranged to rotate about an axis 5 which is perpendicular to the general plane of the cam.
  • the bipolar magnet is mounted here fixed opposite the cam, with its north-south axis oriented substantially in the direction of the axis of rotation 5.
  • the bipolar magnet 7 is arranged in the same plane as the cam 3A, respectively 3B.
  • This is a magnetic system of the radial type for the cam-magnet assembly.
  • the cam is formed either by a magnet with a substantially radial magnetization, in the same direction as that of the bipolar magnet, so that the magnetic interaction is attraction, or by a high magnetic permeability material which also generates a magnetic attraction interaction with the bipolar magnet.
  • the shape of the cam 3A, respectively 3B is in spiral, the contour facing the fixed bipolar magnet (outer contour also called 'edge' later) of this cam being spiral (this is ie forming a turn of a geometric spiral), so that the distance between the fixed magnet and the cam varies as the latter rotates about the axis 5.
  • the edge of the cam is not quite perpendicular to its radius.
  • the magnetic attraction force (symbolized by the arrow referenced Fm) exerted by the magnet on the cam is not oriented purely radially, this force Fm thus having a tangential component (symbolized by the arrow referenced Ft) .
  • the two configurations illustrated schematically in the Figures 1A and 1B are distinguished by the direction of inclination of the edge of the cam, in other words by the direction of the spiral defined by this edge. Indeed, we can see that in the Figure 1A the distance between the edge of the cam 3A and the magnet 7 increases progressively as it rotates counterclockwise, whereas in the Figure 1B on the other hand, the distance between the edge of the cam 3B and the magnet 7 decreases progressively during the rotation of the cam in the counterclockwise direction as well. Then, the magnetic attraction force varies in intensity. Referring first to the Figure 1A it can be seen that the distance between the edge of the cam and the magnet increases progressively during the aforementioned rotation.
  • the increase in the distance is accompanied by a concomitant decrease in the intensity of the tangential magnetic force exerted on the cam 3A by the magnet 7.
  • a complementary intensity variation can be generated by an angular variation of the intensity of the magnetic flux generated by the cam. This makes it possible to increase the tangential / angular magnetic force which generates the auxiliary torque of the equalization device.
  • the decrease in the distance between the magnet and the cam is accompanied by a concomitant increase in the intensity of the magnetic force.
  • the Figure 1A further shows that the tangential component Ft of the magnetic force is opposed to the direction of rotation of the cam 3A. Conversely, in the Figure 1B , the orientation of the tangential component corresponds to the direction of rotation of the cam 3B.
  • the configuration of the Figure 1A generates a force that opposes the rotation of the cam and whose intensity decreases with rotation
  • the configuration of the Figure 1B generates a force that is allied to the rotation of the cam and whose intensity increases with rotation.
  • the configuration of the Figure 1A generates a torque opposite to that of the rotation of the cam
  • the configuration of the Figure 1B generates a torque in the same direction as that of the rotation of the cam.
  • the arrangement of the magnetic equalizer device does not necessarily include a radial type magnetic system, as illustrated in FIGS. Figures 1A and 1B .
  • the arrangement of the cam-magnet assembly can form an axial-type magnetic system.
  • the second magnetic element (the bipolar magnet) is not arranged in the same plane as the cam, but above or below this cam, so that the magnetic interaction between the magnet and the cam generates a force whose resultant has a principal component which is parallel to the axis of rotation of this last.
  • a radial-type or axial-type arrangement is not always accompanied by a radial or axial magnetization of the elements of the magnetic assembly.
  • the axis of magnetization of the cam when the latter is formed by a magnet, may be axial. It is the same for the magnet associated with the cam.
  • the figure 2 is a partial plan view of a watch movement according to a first particular embodiment of the invention.
  • the partial view only illustrates the motion components that are essential to understanding the invention.
  • the other components, including the work train and the winding mechanism may be conventional and not illustrated.
  • the movement shown in the figure 2 comprises a barrel 11 which comprises a pinion 13 mounted on the shaft of the barrel.
  • the pinion 13 rotates clockwise when the mainspring (not shown) disarms causing at least one movement mechanism.
  • the pinion 13 drives an auxiliary gear wheel first comprising a first wheel formed of a wheel 15 and a pinion 17.
  • the wheel 15 is arranged to mesh with the pinion 13 of the barrel, and the pinion 17 is arranged to mesh with a wheel 19.
  • the wheel 19 carries a bipolar magnet 107 mounted on its board in an eccentric position with a radial magnetic orientation.
  • a magnetic cam 103 spiral is arranged fixedly opposite the wheel 19, concentrically with the latter.
  • the stops 21 and 23 are preferably made of a non-magnetic material and are arranged with on either side of the discontinuity 22 of the edge of the cam so that the magnet 107 never passes in front of this discontinuity.
  • the gear ratio of the gear reducer which has just been described is a function of the number of turns that the barrel makes between its fully armed state and its completely disarmed state. Indeed, this ratio must be greater than the number of turns of the barrel so that the pivot angle of the magnet 107, which is integral with the wheel 19, is always less than 360 °. In other words, it is provided that the wheel 19, carrying the first magnetic element or the second magnetic element, performs less than one turn when the cylinder performs several turns between its fully armed state and its completely disarmed state. In the illustrated example, the barrel shaft performs seven turns to move the barrel spring from the fully armed state to the fully disarmed state, or vice versa. On the other hand, the gear ratio of the gear wheel is 8.4.
  • the wheel 19 performs a little less than 5/6 of a turn clockwise during the operation of the watch. It is the two stops 21 and 23 which determine the two extreme angular positions of the wheel 19 by stopping the magnet 107 when it reaches one or the other end of its race.
  • the wheel 19 rotates in the same direction as the barrel pinion 13. Under these conditions, the wheel 19 and the magnet 107 turn clockwise when the mainspring (not shown) disarms by driving the movement.
  • the variable radius of the cam 103 increases counterclockwise, there is a tangential component Ft of the magnetic attraction force between the magnet 107 and the cam 103, which acts on the movable magnet 107 counterclockwise .
  • Ft the tangential component of the magnetic attraction force between the magnet 107 and the cam 103
  • the equalization device which has just been described provides an auxiliary magnetic torque that is opposite to the engine torque and whose magnitude decreases parallel to the magnitude of the engine torque when the mainspring is disarmed.
  • the equalization device could equally well provide an auxiliary magnetic torque which enhances the engine torque, and whose magnitude increases as that of the engine torque decreases. when the barrel spring disarms.
  • the cylinder of the watch movement is arranged to drive a clock mechanism via a kinematic link providing a driving torque to the mechanism.
  • the kinematic linkage arranged to drive the watchmaking mechanism generally comprises a multiplier gear train (for example, the driven clockwork mechanism is a Swiss lever escapement and the multiplier gear train forms the work train of the watch movement).
  • the finishing gear train (not shown) is driven directly by the barrel pinion 13.
  • the finishing gear train is arranged in parallel with the equalizing device (as with a stackfreed 'classic).
  • a mechanism is driven by the barrel via the equalizing device. In this case, at least a portion of the auxiliary gear of the equalization device forms the kinematic connection between the barrel and the mechanism.
  • the barrel of the barrel 11 has no external toothing. This is this called a smooth cylinder.
  • the equalizing device is wedged angularly on the barrel.
  • the two limit angles, defined by the stops 21 and 23 for the angular travel of the wheel 19 correspond to the states “fully armed” and “completely disarmed” respectively of the mainspring.
  • the bipolar magnet is fixed relative to the support of the barrel (plate)
  • the driving of the mechanism and the winding of the barrel are exerted both by means of the barrel pinion 13, which is also coupled to the equalizing device.
  • the winding can be achieved by means of a winding crown and / or an oscillating mass.
  • the winding mechanism can engrainer either directly with the barrel pinion 13 or with another gear element downstream of the barrel pinion.
  • the bipolar magnet is rotationally integral with the barrel shaft, the winding and disarming of the barrel can be carried out respectively via the shaft and the drum of the barrel, or vice versa.
  • the equalization device which has just been described can be used together with a device for indicating the power reserve.
  • a needle is mounted on an axis of the wheel 19.
  • a lever is associated with the cam 103. This lever defines a cam follower and is arranged in abutment against the lateral surface of the cam.
  • the power reserve indicator can be integral with the lever or be formed by a separate member actuated by this lever.
  • FIG. 3 to 5 Partial views of Figures 3 to 5 illustrate a second embodiment of the invention corresponding to a minute repeater watch movement.
  • the minute repeater is a striking mechanism that is driven by a dedicated barrel.
  • the striking mechanism works by means of hammers which, when they are actuated, repeatedly strike stamp springs.
  • a peculiarity of this kind of mechanism is that the speed at which the ringing occurs is dependent on the magnitude of the driving torque received from the barrel.
  • a barrel (generally referenced 111).
  • the barrel shown is formed of a barrel drum 131 which serves as a housing for a spring 133, a barrel cover 135 (shown in FIG. figure 5 ) which closes the box formed by the drum, and a barrel shaft 137 which passes through the barrel and which is pivoted at its ends between the plate and a bridge (not shown).
  • the barrel shaft 137 is secured to a toothed wheel comprising a pinion 113 and a wheel 139.
  • the Figures 3 and 4 show again a winding rake 141 and a one-way wheel 143.
  • the one-way wheels are known devices as such.
  • the gear train 143 comprises an input wheel 145 which meshes with the rake 141 and an output wheel 147 (visible in FIG. figure 3 ) which meshes with the barrel pinion 113.
  • the gear wheels 145 and 147 are coaxial and can rotate relative to each other.
  • One of these two wheels carries a coaxial ratchet (not shown) which is sandwiched between the input wheel and the output wheel.
  • a pawl (not shown) is pivoted on the board of the wheel which faces the ratchet.
  • This ratchet is Recalled against the circumference of the ratchet by a spring (not shown).
  • the pawl is arranged to cooperate with a ratchet tooth when the input wheel rotates counterclockwise and to slide against the ratchet as the input wheel rotates clockwise.
  • the barrel 111 is arranged to drive the ring gear (not shown) via the teeth of the wheel 139.
  • the wheel 139 is integral with the barrel shaft 137. It will be understood that when the spring barrel disarms gradually, the barrel shaft drives the wheel 139 counterclockwise by transmitting a variable engine torque depending on the degree of winding of the mainspring. In addition, as the torque that drives the striking mechanism is variable depending on the degree of winding of the barrel, the speed at which the ringing occurs is also dependent on the degree of winding of the mainspring. Note that the wheel 139 performs less than one revolution between its fully armed state and its completely disarmed state.
  • the magnet 207 is arranged on the wheel 139 so that it does not cross the discontinuity of the edge of the cam when the barrel disarms between the two extreme states mentioned above.
  • the winding of the barrel is carried out using the rake 141.
  • the wearer of the watch can operate the rake manually using a pusher (not shown) or a lock (not shown) which is located on the watch box.
  • a pusher not shown
  • a lock not shown
  • the wearer of the watch actuates the rake, the latter pivots by driving the input wheel 145 of the one-way train 143 counterclockwise.
  • the output wheel of the one-way train is driven by the input wheel and it itself drives the cylinder pinion 113 which thus makes a little less than one turn in the clockwise direction, causing the winding of the spring of barrel 133.
  • a spring recalls the rake in the opposite direction to that of the arrow of the figure 4 .
  • the return stroke of the rake has the effect of driving the input wheel 145 of the one-way train clockwise. As the one-way train does not transmit rotations clockwise, the barrel shaft is not driven in the opposite direction.
  • the figure 5 is a partial perspective view from below of the second embodiment which is also the subject of the Figures 3 and 4 .
  • certain parts, including the rake and the wheel 139, have been omitted so as to show the two magnetic elements of the equalization device according to the invention.
  • these two magnetic elements are respectively a magnetic cam 203 and a bipolar cylindrical magnet 207.
  • the cam 203 is arranged concentrically with the barrel shaft and is attached to the barrel cap 135.
  • the bipolar magnet 207 for its part, is mounted on the wheel plank 139 away from the axis of rotation. to be arranged opposite the cam.
  • the magnet preferably has an axial magnetization direction (parallel to the axis of rotation of the barrel). It will be understood that, under these conditions, the magnetic interaction between the magnet and the cam has a main direction which is essentially axial. It will therefore be said that the arrangement of the equalization device is here of axial type, which has the advantage of being generally more compact than a device of radial type.
  • the magnet 207 which is secured to the wheel 139, rotates in the same direction as the barrel shaft 137. Under these conditions, the magnet 207 rotates in the counterclockwise relative to the cam when the barrel spring 133 disarms causing the ringing. As shown in figure 5 the radial width of the cam 203 increases as it is traversed counterclockwise. Under these conditions, the intensity of the magnetic interaction between the magnet and the cam increases with the disarming of the mainspring. The resulting magnetic potential generates a tangential force on the magnet.
  • the equalization device which has just been described provides an auxiliary torque which is exerted on the cylinder shaft in the same direction as the engine torque and which increases as the engine torque decreases.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Electromechanical Clocks (AREA)
  • Transmission Devices (AREA)
  • Springs (AREA)
EP16194627.2A 2016-10-19 2016-10-19 Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst Active EP3312681B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP16194627.2A EP3312681B1 (de) 2016-10-19 2016-10-19 Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst
US15/686,463 US10474109B2 (en) 2016-10-19 2017-08-25 Timepiece movement comprising a device for equalising a motor torque
JP2017173847A JP6381757B2 (ja) 2016-10-19 2017-09-11 運動トルクを等化するデバイスを有する計時器用ムーブメント
CN201710971750.7A CN107966893B (zh) 2016-10-19 2017-10-18 包括用于均衡动力扭矩的装置的钟表机芯
HK18112133.3A HK1252772A1 (zh) 2016-10-19 2018-09-20 包括用於均衡動力扭矩的裝置的鐘錶機芯

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16194627.2A EP3312681B1 (de) 2016-10-19 2016-10-19 Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst

Publications (2)

Publication Number Publication Date
EP3312681A1 true EP3312681A1 (de) 2018-04-25
EP3312681B1 EP3312681B1 (de) 2020-01-29

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EP16194627.2A Active EP3312681B1 (de) 2016-10-19 2016-10-19 Uhrwerk, das eine vorrichtung zur einregelung eines motordrehmoments umfasst

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US (1) US10474109B2 (de)
EP (1) EP3312681B1 (de)
JP (1) JP6381757B2 (de)
CN (1) CN107966893B (de)
HK (1) HK1252772A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3992727B1 (de) * 2020-10-30 2024-09-04 ETA SA Manufacture Horlogère Suisse Mechanisches uhrwerk mit erfassung der gangreserve

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001077759A1 (fr) * 2000-04-11 2001-10-18 Detra Sa Dispositif d'echappement pour piece d'horlogerie
EP2735919A1 (de) * 2012-11-27 2014-05-28 Montres Breguet SA Uhrwerk, das eine Schnecke umfasst
CH707743A2 (fr) * 2013-03-12 2014-09-15 Seiko Instr Inc Dispositif d'ajustement de couple, mouvement et pièce d'horlogerie mécanique.

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US161957A (en) * 1875-04-13 Improvement in watch-spring equalizers
JPS4921172A (de) * 1972-06-15 1974-02-25
CH1169075A4 (de) * 1975-09-09 1977-04-15
JPS5692985U (de) * 1979-12-19 1981-07-24
EP1914604A1 (de) * 2006-10-19 2008-04-23 Girard-Perregaux S.A. Uhr mit Kraftübertragung mit konstantem Drehmoment zwischen der Kraftquelle und dem mechanischen Oszillator
WO2009059441A1 (de) * 2007-11-09 2009-05-14 Eterna Ag Uhrenfabrik Mechanische armbanduhr mit konstanter federkraft
EP2450758B1 (de) * 2010-11-09 2017-01-04 Montres Breguet SA Magnetischer Drehzapfen und elektrostatischer Dhrerzapfen
EP2487547B1 (de) * 2011-02-11 2017-08-09 Montres Breguet SA Regulator einer Triebfeder eines Uhrwerks oder eines Schlagwerks
CH706209B1 (fr) * 2012-03-07 2016-06-30 Montres Romain Gauthier Sa Mouvement de montre comprenant un barillet à couple constant.
JP6438112B2 (ja) * 2014-09-25 2018-12-12 ザ・スウォッチ・グループ・リサーチ・アンド・ディベロップメント・リミテッド ２つの計時器用部品の間の相互作用
EP3182224B1 (de) * 2015-12-18 2019-05-22 Montres Breguet S.A. Sicherheitsregulator für uhrhemmung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001077759A1 (fr) * 2000-04-11 2001-10-18 Detra Sa Dispositif d'echappement pour piece d'horlogerie
EP2735919A1 (de) * 2012-11-27 2014-05-28 Montres Breguet SA Uhrwerk, das eine Schnecke umfasst
CH707743A2 (fr) * 2013-03-12 2014-09-15 Seiko Instr Inc Dispositif d'ajustement de couple, mouvement et pièce d'horlogerie mécanique.

Also Published As

Publication number Publication date
JP2018066727A (ja) 2018-04-26
US20180107166A1 (en) 2018-04-19
HK1252772A1 (zh) 2019-05-31
US10474109B2 (en) 2019-11-12
EP3312681B1 (de) 2020-01-29
CN107966893B (zh) 2020-03-27
CN107966893A (zh) 2018-04-27
JP6381757B2 (ja) 2018-08-29

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