EP1925995A1 - Schlagwerk - Google Patents

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Publication number
EP1925995A1
EP1925995A1 EP06124443A EP06124443A EP1925995A1 EP 1925995 A1 EP1925995 A1 EP 1925995A1 EP 06124443 A EP06124443 A EP 06124443A EP 06124443 A EP06124443 A EP 06124443A EP 1925995 A1 EP1925995 A1 EP 1925995A1
Authority
EP
European Patent Office
Prior art keywords
wheel
rotation
mechanism according
input
differential
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
EP06124443A
Other languages
English (en)
French (fr)
Other versions
EP1925995B1 (de
Inventor
Alain Schiesser
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.)
CHRISTOPHE CLARET ENGINEERING SA
Original Assignee
Christophe Claret 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 Christophe Claret SA filed Critical Christophe Claret SA
Priority to EP06124443.0A priority Critical patent/EP1925995B1/de
Priority to PCT/EP2007/061989 priority patent/WO2008061884A1/fr
Priority to US12/514,518 priority patent/US7965585B2/en
Priority to CN200780043261XA priority patent/CN101542401B/zh
Priority to JP2009537592A priority patent/JP2010510506A/ja
Publication of EP1925995A1 publication Critical patent/EP1925995A1/de
Application granted granted Critical
Publication of EP1925995B1 publication Critical patent/EP1925995B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • G04B21/00—Indicating the time by acoustic means
    • G04B21/02—Regular striking mechanisms giving the full hour, half hour or quarter hour
    • G04B21/12—Reiterating watches or clocks
    • 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
    • G04B13/007—Gearwork with differential work
    • G04B13/008—Differentials

Definitions

  • the present invention relates to the field of mechanical watchmaking. More particularly, it relates to a striking mechanism comprising a power source for driving rakes and a gear train connecting the power source to a regulating member.
  • the big ringtones are therefore equipped with a complete gear train for driving the ringing parts.
  • This wheel thus connects a barrel of ringing with its own winding system to a regulating organ.
  • the barrel provides energy to the ringing parts through a control and distribution member disposed in the train, possibly coaxially with the barrel.
  • the control and distribution member comprises a stack of several wheels, free or fixed in rotation relative to each other.
  • the object of the present invention is to propose an advantageous alternative to the devices of the state of the art.
  • the striking pieces are kinematically connected to the energy source via a differential disposed in the gear train.
  • this differential comprises a first input wheel kinematically connected to the wheel and a second input wheel connected to a control member and an output wheel connected to the ringing parts.
  • control member is a camshaft comprising a first cam for blocking or free rotation of the first input wheel, a second cam for locking or free rotation of the second input wheel and at least a driving wheel for pivoting the shaft.
  • the mechanism may comprise a silencer device provided with a latch capable of changing between a first and a second position, in which it co-operates with the driving wheel to block the control organ.
  • This lock can be moved by manual control means, actuated by the carrier, or by automatic control means, for example to prevent a ringing at the passage to be triggered below a certain power reserve.
  • FIG. 1 shows a barrel 10 whose winding system has not been shown, which drives a reduction gear train 12, which terminates in a regulating member, for example a flywheel 14 provided with a drag brake. flyweights as known to the skilled person.
  • a differential 20 kinematically connects the gear 12 to the rakes so that they are driven during the ring by the barrel 10.
  • FIG. 2 An example of a differential 20 particularly adapted to the invention is shown in FIG. 2.
  • a differential 20 On a shaft AA axis, it comprises a first sun gear 22 constituting a first input of the differential and kinematically connected with a wheel of the gear 12.
  • the differential 20 is coaxial and integral with this wheel of the gear 12.
  • This sun gear 22 meshes with at least one, typically three, lower satellites 24 rotatably mounted on a first level of a planet carrier wheel 26 provided with of a peripheral toothing.
  • the latter constitutes a second differential input. It is free in rotation and coaxial with the sun gear 22.
  • the three lower satellites 24 are each mounted coaxial and integral in rotation with at least one, typically three, upper satellites 28 rotatably mounted on a second level of the planet carrier wheel. 26.
  • the upper satellites 28 meshes with an upper solar wheel 30, coaxial and rotationally integral with a reference 32.
  • This upper sun gear 30 is the output of the differential.
  • this reference 32 is engaged with a toothed sector 34 of an hours probe, intended to cooperate with the snail hours.
  • a ratchet of 36 hours intended to actuate a lift to ring the hours, is also integral in rotation of the reference 32.
  • the hour ratchet 36 is therefore directly kinematically connected to the feeler hours.
  • the rakes 18 kinematically connected to the hour sensor can move independently of the gear train 12 and the cylinder 10.
  • This configuration is the one that is used, when the bell is triggered, for allow the feelers of the different rakes, to fall on their respective snail to take information relative to the current time.
  • the second configuration makes it possible to kinematically connect the barrel 10 to the rakes 18. This is the one that is used during the course of the ringing so that the rakes move relative to their lifting to operate the hammers.
  • the third configuration corresponds to the situation in which the rakes 18 are stopped and kept at rest.
  • the blocking of the lower sun gear 22 is, according to the preferred embodiment shown in the drawings, by blocking the unwinding of the ringer barrel 10.
  • this lock is obtained by a stop element 38 arranged to move between a first and a second extreme position, the stop element 38 crossing, in one of these extreme positions, the stroke of a pin 40 projecting on the This is where the torque is the least important and the locking can be done with optimum safety.
  • a latch 42 having the shape of a hook 42a disposed on a latch 42b and capable of changing between a first and second extreme positions, the hook 42a cooperating with the toothing of the planet carrier wheel 26 when it is in one of these extreme positions.
  • a camshaft 50 is pivotally mounted in the frame and comprises a first cam 52 intended to control the locking of the lower sun gear 22 and a second cam 54 controlling the locking of the planet wheel 26.
  • the cams and the stars are shown individually in FIG. 4.
  • the camshaft 50 is positioned by a first star 56 comprising a first level 56a (FIG. 4a) provided with twelve teeth cooperating with a jumper 58 and a second level 56b ( Figure 4b) having only four teeth, regularly distributed on a cut of twelve teeth and superimposed with the teeth of the first level.
  • This star 56 also performs the function of training drive of the shaft 50, as will be described in detail later.
  • the positioning star 56 is numbered in a multiple of three, twelve having an angular pitch between two consecutive advantageous positions with respect to the size of these parts and the available space.
  • the first cam 52 shown in Figure 4c has a succession of projections and hollow portions. As mentioned above and illustrated in FIG. 6, the blocking of the lower sun wheel 22 is at the level of the regulating member 14.
  • the stop element 38 can be arranged at the end of a double rocker 58 , comprising two rockers 58a and 58b articulated with each other by a pin 58c integral with one of them 58a and cooperating with a housing 58d formed in the other 58b.
  • a spring 60 is arranged to support the end of the rocker 58a against the first cam 52.
  • the pivot points of the double rocker 58 are arranged, in the example, so that when the rocker 58a supports against a protruding part of the cam 52, the stop element 38 cooperates with the regulating member 14, which blocks the lower sun gear 22. Conversely, when the cam 52 has a hollow portion at the rocker 58a, the lower sun wheel 22 is free.
  • the cam 52 is provided with a succession of a protruding part, a hollow part and a protruding part, this series being repeated four times according to the example of a shaft. cams 50 to twelve positions.
  • the second cam 54 ( Figure 4d) also has a succession of projecting parts and hollow parts.
  • a spring 62 is arranged to support the end of the latch 42 not carrying the hook 42a against the cam 54.
  • the pivot point of the latch 42 is arranged so that when the Cam 54 has a protruding portion at the latch 42, the hook 42a is outside the toothing of the planet carrier wheel 26 which is free to rotate. Conversely, when the rocker 42 presses against a hollow of the cam, the planet wheel 26 is blocked.
  • the cam 54 is provided with a succession of a protruding part and two hollow parts, this series being repeated four times according to the example of a twelve-position camshaft.
  • Figure 3 shows a flexible finger 70 for cooperating with the second level 56b of the star 56 and rotated by the base movement of the timepiece.
  • the finger 70 moves back and forth under the action of a sleeve 72 whose periphery defines a kind of spiral and has an inclined plane 72a.
  • the finger 70 is held against the cam by a spring 74 at a lug 70a which it is provided.
  • the bushing is driven, counterclockwise with respect to FIG. 3, by the minute wheel of the basic movement, at a rate of one revolution per hour, which makes the finger 70 turn counterclockwise and load the spring 74. Every hour, at the passage of time, the lug passes the inclined plane and the finger 70, under the effect of the spring 74, pivots clockwise and drives the star 56 a step, making thus pass the differential to configuration 1.
  • the sleeve 72 could also include a plurality of inclined planes so as to actuate the finger every quarter of an hour, to ring quarters, an isolator can then be provided if it is desired that the hours are not ringed during the quarter ringing.
  • FIG. 5 For manual triggering, reference is made to FIG. 5. It is proposed that the user actuate a bolt 76 secured to a rack 78, like a conventional minute repeater.
  • the rack 78 meshes with an external toothing of a ring 80, coaxial with the striking barrel 10.
  • This ring 80 is connected to the shaft of the barrel 10 by a radial spring 82 having a hub 82a mounted square on the shaft and typically two blades resilient 82b, exerting a radial pressure towards the outside of the wheel and ending in a toothed portion cooperating with an internal toothing that includes the ring 80.
  • the spring 82 and the internal toothing of the ring 80 are arranged in such a way as to forming a snap between the shaft of the barrel 10 and the rack 78.
  • the pivoting of the ring 80 in one direction drives the barrel shaft in rotation, but neither the pivoting of the barrel shaft in the other sense, for example during disassembly of the movement, nor the drive of the shaft during the manual winding of the barrel of ringing causes displacement of the bolt 76.
  • the outer toothing of the ring 80 transmits the movement of the bolt to a wheel 84 with which it meshes.
  • This wheel 84 is provided with a return system 86, for example a spiral spring, allowing the return of the bolt 76 to its rest position since the latching system mentioned above does not allow this return to be ensured by the energy provided by the barrel 10, as is the case in conventional repetitions.
  • the wheel 84 also carries an arm 88 mounted on its axis and ending with a bearing zone 88a intended to cooperate with a second star 90 (FIG. 4e), also acting as a drive element for the shaft 50. , to advance the camshaft 50 one step and pass the differential to the configuration 1.
  • This star 90 is cut on the number twelve but has only four teeth, that is to say one per cycle of ringtone. It is also clearly visible in FIG.
  • a simple rocker driven by a pusher disposed in the middle part of the watch drives the star 90 by one step, without rearming the barrel.
  • the teeth of the star 90 are likely to cross the path of a transmission wheel 92, rotated permanently by the main wheel of the movement. Typically, this wheel is driven by the wheel of small average at the rate of one turn in thirty seconds approximately.
  • the skilled person will determine the shape of the teeth of the star 90 and the transmission wheel 92 to ensure good torque transmission.
  • the teeth of the star 90 are disposed on the camshaft so as to cross the path of the transmission wheel 92 when the differential is in its first configuration.
  • the camshaft 50 is thus driven slowly by one step and passes the differential 20 to the configuration 2.
  • the rakes 18 are kinematically connected to the barrel 10 so as to allow the ringing to proceed as such.
  • the shaft 50 must therefore move one step further than the end of the ring.
  • one of the rakes 18, preferably the minute rake 18a allows the displacement of a transmission element to the end of the ring.
  • this element may be a finger 94 arranged to cooperate with the first star 56 to advance the camshaft 50 by one step.
  • the rake minutes 18a carries a pin 96 for driving the finger 94.
  • the finger 94 is located at the end of an elastic portion of a flip-flop 98, which improves the safety of the device.
  • a spring 99 holds the rocker 98 against the pin 96.
  • the differential 20 when the ring is at rest, the differential 20 is in its configuration 3, the barrel 10 being locked, and the rakes 18 thus being held in position.
  • the camshaft 50 When triggering the ring, either manually or in passing, the camshaft 50 is driven one step, which allows to bring the differential 20 in its configuration 1.
  • the rakes are then disengaged from the ring gear 12 and then they can freely fall, under the effect of their respective spring, on their snail to take a information relating to the current time. This step is very fast and is done while the transmission wheel 92 drives the second star 90 and passes the differential 20 in its configuration 2.
  • the rakes are then kinematically connected to the barrel 10 which is released.
  • the finger 70 cooperates with the second level 56b of the star 56, if a trip trigger occurs during the course of a ring that has just been triggered manually, then the finger 70 does not will find on its way that a space devoid of teeth and will not abut against the camshaft. This security is particularly advantageous because trying to trigger a ringing in passing while a ringing is already in progress would cause serious damage to the mechanism.
  • the mechanism according to the invention may further comprise a silencer device 100 shown in Figure 7 and allowing the user to prevent the triggering of the ringing.
  • a pusher or corrector not shown is arranged in the middle part of the watch and makes a slide 102 evolve between a first rest position and a second position.
  • This slide 102 is movably mounted in translation on the plate of the striking mechanism and comprises, for this purpose, two oblongs 102a in which pass screws in range.
  • the slide 102 cooperates with a pin 104 disposed on a rocker 106.
  • a latch 108 is pivotally mounted, coaxial with the rocker 106.
  • the latch 108 is arranged to be able to move between a first rest position and a second position in which it cooperates with the second star 90, to prevent the rotation of the shaft 50.
  • the lock 108 has a notch which substantially matches the circumference of the camshaft.
  • the notch defines a finger 108a capable of interacting with the teeth of the star 90. These teeth are shaped so as to bear substantially orthogonally on the finger 108a, to obtain an effective locking.
  • the lock 108 is provided with a rod 110 capable of cooperating with a bearing surface 106a that the rocker 106 presents.
  • a first spring 112 keeps the rod 110 in abutment against the surface 106a. The force exerted by this spring 112 on the lock tends to move it away from the camshaft 50 and bring it back to its first position.
  • a second spring 114 is arranged to press the rocker 106 against the slide 102.
  • the finger 108a blocks the rotation of the shaft 50 when the slide 102 is pulled, i.e. when in its furthest position relative to the shaft 50.
  • the extreme positions of the slide 102 may be marked by a notch system, advantageously obtained at the level of the corrector or the pusher.
  • the rocker 106 pivots and, the spring 112 being less strong than the spring 114, the lock 108 is brought into its second position and blocks the pivoting of the Conversely, when the slide 102 is pushed, the lock 108 returns to its first position under the effect of the spring 112, releasing the camshaft 50.
  • a second flip-flop 116 is also mounted coaxial with respect to the first.
  • This second flip-flop 116 is provided with a probe 116a held by a third spring 118 in abutment against a cam 120 making a turn, substantially in a duration equal to the power reserve of the striking barrel 10.
  • the cam 120 has a recess arranged so as to be at the level of the toggles when the power reserve of the cylinder is below a predetermined threshold.
  • the flip-flop 116 pivots and, the spring 112 being less strong than the spring 118, the latch 108 is brought into its second position and blocks the pivoting of the shaft. 50. Conversely, when the power reserve reverts above the predetermined threshold, the latch returns to its first position under the effect of the spring 112, releasing the camshaft 50.
  • the manual triggering system for ringing can reset the barrel 10
  • the arm 88 actuating the star 90 is arranged to intersect, in its race, the latch 108 if it is in its second position, so as to bring it into its first position. position the time necessary to advance the shaft 50. This clearance must be done before the arm 88 exerts a thrust on the star 90. Then, once the shaft has rotated, since the lock is in Looking at the toothless portions of the star 90, it no longer locks until, at the end of the ring, it cooperates with a next tooth.
  • a cam driven by the base gear wheel at a rate of one revolution per twenty-four hours may define parts of the day during which the ringing pass is engaged and others, for example during the night, during which time she is stuck.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
EP06124443.0A 2006-11-21 2006-11-21 Schlagwerk Active EP1925995B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP06124443.0A EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk
PCT/EP2007/061989 WO2008061884A1 (fr) 2006-11-21 2007-11-07 Mecanisme de sonnerie
US12/514,518 US7965585B2 (en) 2006-11-21 2007-11-07 Ringing mechanism
CN200780043261XA CN101542401B (zh) 2006-11-21 2007-11-07 振铃机构
JP2009537592A JP2010510506A (ja) 2006-11-21 2007-11-07 報時機構

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06124443.0A EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk

Publications (2)

Publication Number Publication Date
EP1925995A1 true EP1925995A1 (de) 2008-05-28
EP1925995B1 EP1925995B1 (de) 2014-06-18

Family

ID=38324119

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06124443.0A Active EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk

Country Status (5)

Country Link
US (1) US7965585B2 (de)
EP (1) EP1925995B1 (de)
JP (1) JP2010510506A (de)
CN (1) CN101542401B (de)
WO (1) WO2008061884A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101923313A (zh) * 2009-06-16 2010-12-22 莎麦普股份有限公司-埃米尔佩基奈特钟表 手表机芯用的差速齿轮
CH705938A1 (fr) * 2011-12-23 2013-06-28 Manuf Et Fabrique De Montres Et Chronometres Ulysse Nardin Le Locle S A Rouage planétaire pour une pièce d'horlogerie.
EP2879006A1 (de) 2013-11-29 2015-06-03 Christophe Claret Engineering S.A. Uhr mit Animation
RU2586201C2 (ru) * 2011-02-17 2016-06-10 Гласхюттер Уренбетриб Гмбх Механизм календаря
EP3096189A1 (de) * 2015-05-21 2016-11-23 Blancpain SA. Sicherheitsmechanismus zum ein- und/oder ausschalten eines schlagwerks einer uhr
EP3435176A1 (de) * 2017-07-25 2019-01-30 Blancpain SA Drehmomentglättung für uhr mit einem schlagwerkmechanismus, insbesondere mit schlagwerkmechanismus
CN109960131A (zh) * 2017-07-25 2019-07-02 布朗潘有限公司 用于特别是具有报时机构的钟表的力矩平滑装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2133758A1 (de) * 2008-06-12 2009-12-16 Blancpain S.A. Uhr mit einem Schlagwerkmechanismus
CH700154B1 (fr) * 2008-12-24 2014-03-14 Complitime Sa Pièce d'horlogerie comprenant un organe de pivotement.
EP2498143B1 (de) * 2011-03-08 2018-05-02 Montres Breguet SA Isolationsmechanismus zwischen Uhrmechanismen zur Auslösung verschiedener Schlagwerkssignale
EP2498149B1 (de) * 2011-03-08 2015-07-01 Montres Breguet SA Zeitbegrenzungsmechanismus für Uhrmechanismus
EP2498146B1 (de) * 2011-03-08 2018-07-18 Montres Breguet SA Weckerwerkmechanismus mit Hilfe des großen Schlagwerks
CH704626A2 (fr) * 2011-03-08 2012-09-14 Montres Breguet Sa Bloc de sonnerie et mécanisme d'entraînement de sonnerie de réveil pour pièce d'horlogerie à sonnerie.
EP2503405B1 (de) * 2011-03-22 2014-07-30 Montres Breguet SA Uhr umfassend einen Schlagwerk sowie einen Mechanismus zur selektiven stoppen dieses Schlagwerks
CN103631127B (zh) * 2012-08-29 2017-06-06 天津海鸥表业集团有限公司 一种带有保险装置的启动结构
EP3108307B1 (de) * 2014-02-19 2018-09-19 Chopard Technologies SA Schlagwerkvorrichtung für eine uhr
JP6485779B2 (ja) * 2014-02-19 2019-03-20 ショパール テクノロジーズ エスエー 計時器用の時打ち機構
EP3306416B1 (de) * 2016-10-04 2019-08-21 ETA SA Manufacture Horlogère Suisse Mechanisches uhrwerk mit erfassung der gangreserve
EP3435174B1 (de) * 2017-07-25 2021-06-16 Blancpain SA Moduswahlschalter für schlagwerk für armbanduhr oder andere uhr
CN109960135B (zh) * 2019-04-28 2023-11-24 烟台持久钟表有限公司 一种用于机械大钟报刻的装置
US11164552B1 (en) * 2021-05-12 2021-11-02 Malmark Inc. Bell and hammer rotational device

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US2000327A (en) * 1929-03-14 1935-05-07 Julius W Hansen Clock
CH689337A5 (fr) * 1996-09-03 1999-02-26 Patek Philippe Sa Pièce d'horlogerie à carillon.

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US4466327A (en) * 1982-09-29 1984-08-21 Hinton E Louis Gas driven music box
CH691147A5 (fr) * 1996-04-04 2001-04-30 Parmigiani Mesure Et Art Du Te Horloge à pendule.
CH696218A5 (fr) * 2001-08-07 2007-02-15 Piguet Frederic Sa Pièce d'horlogerie à quantième comprenant un dispositif d'équation du temps marchante.
SG103916A1 (en) * 2002-04-03 2004-05-26 Lemania Nouvelle Sa Watch including a case of elongated shape
EP1582943B1 (de) * 2004-04-01 2008-09-03 Richemont International S.A. Uhrwerk mit mehreren Federhäusern
ATE470890T1 (de) * 2005-03-30 2010-06-15 Montres Breguet Sa Uhr mit mindenstens zwei reguliersystemen
EP1909149B1 (de) 2006-10-02 2012-09-19 Manufacture Claret SA Uhr mit Schlagwerk

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Publication number Priority date Publication date Assignee Title
US2000327A (en) * 1929-03-14 1935-05-07 Julius W Hansen Clock
CH689337A5 (fr) * 1996-09-03 1999-02-26 Patek Philippe Sa Pièce d'horlogerie à carillon.

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2264551A1 (de) * 2009-06-16 2010-12-22 Samep S.A. - Montres Emile Pequignet Differentialzahnradgetriebe für Uhrwerk
JP2011002451A (ja) * 2009-06-16 2011-01-06 Samep Sa -Montres Emile Pequignet 腕時計機構部のための差動歯車
US8251574B2 (en) 2009-06-16 2012-08-28 Samep S.A.—Montres Emile Pequignet Differential gear for watch movement
CN101923313B (zh) * 2009-06-16 2013-03-20 莎麦普股份有限公司-埃米尔佩基奈特钟表 手表机芯用的差速齿轮
CN101923313A (zh) * 2009-06-16 2010-12-22 莎麦普股份有限公司-埃米尔佩基奈特钟表 手表机芯用的差速齿轮
RU2586201C2 (ru) * 2011-02-17 2016-06-10 Гласхюттер Уренбетриб Гмбх Механизм календаря
CH705938A1 (fr) * 2011-12-23 2013-06-28 Manuf Et Fabrique De Montres Et Chronometres Ulysse Nardin Le Locle S A Rouage planétaire pour une pièce d'horlogerie.
EP2879006A1 (de) 2013-11-29 2015-06-03 Christophe Claret Engineering S.A. Uhr mit Animation
EP3096189A1 (de) * 2015-05-21 2016-11-23 Blancpain SA. Sicherheitsmechanismus zum ein- und/oder ausschalten eines schlagwerks einer uhr
JP2016218052A (ja) * 2015-05-21 2016-12-22 ブランパン・エス アー 計時器の打撃ワークの選択及び／又は発動のための安全機構
EP3435176A1 (de) * 2017-07-25 2019-01-30 Blancpain SA Drehmomentglättung für uhr mit einem schlagwerkmechanismus, insbesondere mit schlagwerkmechanismus
CN109960131A (zh) * 2017-07-25 2019-07-02 布朗潘有限公司 用于特别是具有报时机构的钟表的力矩平滑装置
RU2694787C1 (ru) * 2017-07-25 2019-07-16 Бланпэн Са Обеспечение равномерности крутящего момента для часов, в частности, с механизмом боя
CN109960131B (zh) * 2017-07-25 2021-04-23 布朗潘有限公司 用于特别是具有报时机构的钟表的力矩平滑装置
US11435696B2 (en) 2017-07-25 2022-09-06 Blancpain Sa Torque smoothing for a timepiece, particularly with a striking mechanism

Also Published As

Publication number Publication date
CN101542401A (zh) 2009-09-23
US7965585B2 (en) 2011-06-21
CN101542401B (zh) 2011-08-10
JP2010510506A (ja) 2010-04-02
WO2008061884A1 (fr) 2008-05-29
EP1925995B1 (de) 2014-06-18
US20100054091A1 (en) 2010-03-04

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