EP1925997B1 - Schlagwerk - Google Patents

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Publication number
EP1925997B1
EP1925997B1 EP20060124477 EP06124477A EP1925997B1 EP 1925997 B1 EP1925997 B1 EP 1925997B1 EP 20060124477 EP20060124477 EP 20060124477 EP 06124477 A EP06124477 A EP 06124477A EP 1925997 B1 EP1925997 B1 EP 1925997B1
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EP
European Patent Office
Prior art keywords
striking
triggering
drive wheel
mechanism according
camshaft
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.)
Not-in-force
Application number
EP20060124477
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English (en)
French (fr)
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EP1925997A1 (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
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Manufacture Claret SA
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Filing date
Publication date
Application filed by Manufacture Claret SA filed Critical Manufacture Claret SA
Priority to EP20060124477 priority Critical patent/EP1925997B1/de
Publication of EP1925997A1 publication Critical patent/EP1925997A1/de
Application granted granted Critical
Publication of EP1925997B1 publication Critical patent/EP1925997B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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

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 energy source to a regulating member, the rakes being kinematically connected to the power source via a power source. a ringing drive device arranged in the train and actuated by a control member.
  • the drive comprises a detent ratchet, a drive plate carrying a first pawl.
  • the trigger ratchet is actuated by a second ratchet mounted on a rocker.
  • the rocker makes a sudden jump and the second pawl causes the trigger ratchet, which causes the lifting of the first ratchet and gives freedom to a barrel ratchet, mounted freely and without play on the barrel of the tray.
  • Running parts such as a ratchet of hours, a rack pinion and a quarter room finger are squared fitted on the barrel ratchet.
  • the document CH 689337 proposes a striking mechanism in which the passing ringtones are actuated by arms arranged rigidly on a nut mounted on the roadway and which act, every quarter of an hour, on a release lever which will act further on a similar ratchet at the second pawl of the device described above.
  • a first object of the invention is to provide a system for facilitating the setting of the triggering of the ring.
  • the conduct of a ring has three stages, a first in which the rakes fall on their respective snail to take information on the current time, a second during which the rakes are driven by the source of energy to operate the lifts and hammers, and a third, resting, in which the rakes and the energy source are blocked.
  • the sequence of these steps must of course be coordinated for proper operation of the ring.
  • it is a pin disposed on the rake minutes that activates the locking and unlocking of the power source. It is important that it is released only after the rakes have fallen on their snail. It is also very difficult to coordinate the action of the first pawl on the trigger ratchet and the unlocking of the energy source by the pin.
  • a second object of the invention is to facilitate the coordination of the various stages of the course of a ring.
  • the striking mechanism according to the invention is defined by claim 1.
  • the drive device may be conventional, of the type comprising a trigger ratchet, a drive plate carrying a pawl.
  • the element of link is then arranged to act on the trigger ratchet when triggering the ring.
  • the driving device can also be a differential.
  • the connecting element is arranged to act on a differential input when triggering the ring.
  • the drive mobiles are arranged to allow the camshaft to advance one step when triggering the ring to allow the rakes to fall on their respective snail.
  • the camshaft comprises a second cam for actuating the locking and unlocking of the energy source, the two cams being indexed relative to each other.
  • the camshaft In order to facilitate access to the camshaft for its drive, it may be provided with a second drive wheel, for distributing, in the thickness of the mechanism, the various members cooperating with these mobiles.
  • the drive mobiles are arranged to allow the camshaft to advance a first step during the triggering ring to allow the rakes to fall on their respective snail, a second step after that the rakes fell on their snail, to pass to a second stage of the course of the ringing during which the rakes are driven by the energy source, and of a third step, after the ringing took place, to proceed to a third step in which the rakes and the energy source are blocked.
  • the figure 1 shows a barrel 10 whose winding system has not been shown, which drives a reduction gear train 12, which ends with a regulating member, for example a flywheel 14 provided with a flyweight brake as the knows the skilled person.
  • a regulating member for example a flywheel 14 provided with a flyweight brake as the knows the skilled person.
  • the ring driving device is a differential 20 kinematically connecting the gear 12 to the rakes so that they are driven during the ring by the barrel 10.
  • a differential 20 particularly adapted to the invention is represented on the figure 2 .
  • the differential 20 On a shaft AA axis, it comprises a first sun gear 22 constituting a first differential input and kinematically connected with a wheel of the train 12.
  • the differential 20 is coaxial and integral with the 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 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 return 32 is engaged with a toothed sector 34 of an hours probe, intended to cooperate with the snail hour.
  • a ratchet hour 36 for activating a lift to ring the hours, is also integral in rotation of the reference 32.
  • the ratchet hours 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.
  • the locking planet wheel 26 is made directly via a latch 42, having the shape of a hook 42a disposed on a latch 42b and capable of changing between a first and a 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.
  • the invention provides a particularly advantageous solution to achieve this by controlling how the stop element 38, on the one hand, and the latch 42, on the other hand, each evolve between their first and second extreme positions.
  • a camshaft 50 is pivotally mounted in the frame and has a first cam 52 for controlling the locking of the lower sun gear 22 and a second cam 54 controlling the locking of the planet wheel 26.
  • Cams and stars are represented individually at figure 4 .
  • the camshaft 50 is positioned by a first star 56 having a first level 56a ( figure 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 driving mobile 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 FIG. figure 4c has a succession of projecting parts and hollow parts. As mentioned above and illustrated by the figure 6 , the locking of the lower sun wheel 22 is at the level of the regulating member 14.
  • the stop element 38 can be disposed at the end of a double rocker 58, comprising two rocker bars 58a and 58b hinged one with the other by a pin 58c secured to 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.
  • the shaft comprises a flat part with which a complementary structure 52a, 54a which has the inside diameter of the cams cooperates.
  • a complementary structure 52a, 54a which has the inside diameter of the cams cooperates.
  • they are directly machined so that their protruding and hollow portions are coordinated when they are arranged on the shaft. It may be the same for the training mobile.
  • Another type of indexing for example by a pin passing through the cams, can be envisaged.
  • FIG 3 shows a flexible finger 70 intended to cooperate with the second level 56b of the star 56 and rotated by the basic 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 counter-clockwise from the figure 3 , by the minute wheel of the basic movement, at a rate of one revolution per hour, which rotates the finger 70 counterclockwise and loads 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, rotates clockwise and drives the star 56 one step, thus passing the differential to the 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 figure 5 . It is proposed that the user operates a bolt 76 integral with 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 squarely on the shaft and typically two resilient blades 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 so as to form 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 direction, for example during the 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 ( figure 4e ), also acting as drive element of the shaft 50, to advance the camshaft 50 by one step and pass the differential to the configuration 1.
  • This star 90 is cut to the number twelve but do not has only four teeth, that is one per ringing cycle. It is also clearly visible on the figure 7 .
  • 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, permanently rotated 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 minute rake 18a carries a pin 96 intended to drive the finger 94.
  • this finger 94 is located at the end of an elastic portion of a rocker 98, which which improves the security 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 they can then fall freely, under the effect of their respective spring, on their snail to take information relative 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 unlocking of the energy source can be managed in a conventional manner, as described in the aforementioned work.
  • the camshaft may have only one cam for triggering the ring.
  • the camshaft makes it possible to centralize in one place of movement all the controls of the striking mechanism. It is thus possible, in a very simple way, to have the mechanisms for blocking the ringing or other allowing, on the contrary, to trigger the ring at scheduled times.
  • the mechanism according to the invention may, in addition, comprise a silencer device 100 represented on the 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 mounted movably in translation on the plate of the striking mechanism and comprises, for this purpose, two oblongs 102a in which pass screws.
  • 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 rotation of the shaft 50.
  • the lock 108 has a notch that 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, that is to say when it is 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 feeler 116a held by a third spring 118 in abutment against a cam 120 rotating one round, substantially in a time equal to the power reserve of the striking barrel 10.
  • the cam 120 has a hollow arranged so as to occur at the level of the rocker when the power reserve of the barrel 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.
  • a programmable triggering device of the ring which can find its place as well in a mechanism of large ring that in a mechanism of repetition to minutes managed by a camshaft.
  • This programmable triggering device may consist of an arm intended to cooperate with a driving mobile, such as star 56.
  • the arm is actuated via a GMT type system or by a twenty-four hour wheel. driven by the main movement.
  • An adjustment system coupled with a display by a lanternage makes it possible to define the time at which the arm will cross the driving mobile and trigger a ringing. It is thus possible, very simply, to combine an alarm clock and a repetition.
  • a rocker 120 actuates, via a pawl 120a, a trigger ratchet 122 of a conventional drive device 124, further comprising a drive plate 126 carrying a pawl 128 cooperating with a second ratchet 130.
  • a rocker 120 actuates, via a pawl 120a, a trigger ratchet 122 of a conventional drive device 124, further comprising a drive plate 126 carrying a pawl 128 cooperating with a second ratchet 130.
  • a cam similar to the cam 54 manages the triggering of the ring.
  • Flip-flop 120 is held in abutment on the cam, the hollow and protruding parts of which impart a forward and backward movement to the pawl 120a which, in its movements, can drive trigger ratchet 122 and trigger the ringing, in a similar manner to the conventional operation of this drive mechanism.
  • the pivoting of the camshaft can be controlled as previously described.
  • the unlocking of the energy source can be managed in a conventional manner, as described in the aforementioned work.
  • the camshaft may have only one cam for triggering the ring.
  • Unlocking the barrel can also be managed by a second cam blocking and unlocking the gear through a rocker, as in the previous embodiment.

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

Claims (8)

  1. Schlagwerksmechanismus, der eine Energiequelle aufweist (10), um Rechen (18) anzutreiben, und ein Räderwerk (12), das die Energiequelle (10) mit einem Reglerorgan (14) verbindet, wobei die Rechen (18) mit der Energiequelle (10) über eine in dem Räderwerk (12) angeordnete und von einem Steuerorgan betätigte Schlagwerksvorrichtung (20, 124) kinematisch verbunden ist, wobei die Rechen (18) dazu bestimmt sind, um mit Staffeln zusammenzuarbeiten, um eine Information über die laufende Zeit aufzunehmen, wobei das Steuerorgan eine Nockenwelle (50) ist, die ausgestattet ist mit
    - mindestens einem Nocken, der mit der Antriebsvorrichtung über mindestens ein Verbindungselement zusammenarbeitet, und
    - einem ersten Antriebsdrehteil (56), das ausgebildet ist, um die Nockenwelle bei einem Auslösen beim Vorbeiziehen des Schlagwerks zu drehen, dadurch gekennzeichnet, dass die Nockenwelle (50) ebenfalls mit einem zweiten Antriebsdrehteil (90) ausgestattet ist, das ausgebildet ist, um die Nockenwelle (50) bei einem manuellen Auslösen des Schlagwerks zu drehen.
  2. Schlagwerksmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Antriebsvorrichtung eine Vorrichtung ist, die ein Entspannungs-Sperrrad umfasst, wobei eine Antriebsplatte einen Sperrkegel trägt und dadurch, dass das Verbindungselement ausgebildet ist, um beim Auslösen des Schlagwerks auf das Entspannungs-Sperrrad einzuwirken.
  3. Schlagwerksmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass die Antriebsvorrichtung ein Differential ist und dadurch, dass das Verbindungselement ausgebildet ist, um beim Auslösen des Schlagwerks auf einen Eingang des Differentials einzuwirken.
  4. Schlagwerksmechanismus nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass das erste Antriebsdrehteil (56) und das zweite Antriebsdrehteil (90) derart ausgebildet sind, dass die Nockenwelle imstande ist, beim manuellen Auslösen oder beim Vorbeiziehen des Schlagwerks einen Schritt voranzugehen, um es den Rechen zu erlauben, auf ihre jeweilige Staffel zu fallen.
  5. Schlagwerksmechanismus nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Nockenwelle einen zweiten Nocken umfasst, um die Verriegelung oder die Entriegelung der Energiequelle zu betätigen, wobei die zwei Nocken im Verhältnis zueinander indexiert sind.
  6. Schlagwerksmechanismus nach vorangehendem Anspruch, dadurch gekennzeichnet, dass das erste Antriebsdrehteil (56) und das zweite Antriebsdrehteil (90) derart ausgebildet sind, um es der Nockenwelle zu erlauben, voranzugehen
    um einen Schritt beim Auslösen des Schlagwerks, um es den Rechen zu erlauben, auf ihre jeweilige Staffel zu fallen,
    um einen Schritt, nachdem die Rechen auf ihre Staffel gefallen sind, um zu einem zweiten Schritt des Ablaufs des Schlagens überzugehen, bei dem die Rechen von der Energiequelle angetrieben werden, und
    um einen Schritt, nachdem das Schlagen abgelaufen ist, um zu einem dritten Schritt überzugehen, bei dem die Rechen und die Energiequelle blockiert sind.
  7. Mechanismus nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er eine Geräuschlos-Vorrichtung (100) umfasst, die mit einem Riegel (108) ausgestattet ist, die sich zwischen einer ersten Stellung und einer zweiten Stellung entwickelt, in der sie mit dem zweiten Antriebsdrehteil (90) zusammenarbeitet, um das Steuerorgan (50) zu blockieren.
  8. Mechanismus nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er einstellbare Auslösemittel umfasst, um mit dem Antriebsdrehteil zusammenzuarbeiten und um ein Schlagen zu einer ausgewählten Zeit auszulösen.
EP20060124477 2006-11-21 2006-11-21 Schlagwerk Not-in-force EP1925997B1 (de)

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EP20060124477 EP1925997B1 (de) 2006-11-21 2006-11-21 Schlagwerk

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Application Number Priority Date Filing Date Title
EP20060124477 EP1925997B1 (de) 2006-11-21 2006-11-21 Schlagwerk

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EP1925997A1 EP1925997A1 (de) 2008-05-28
EP1925997B1 true EP1925997B1 (de) 2013-02-27

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CN106030421A (zh) * 2014-02-19 2016-10-12 萧邦科技公司 用于钟表件的响铃机构
RU2690035C1 (ru) * 2017-07-25 2019-05-30 Бланпэн Са Механизм переключения режимов боя для наручных или иных часов
RU2767294C2 (ru) * 2017-07-25 2022-03-17 Бланпэн Са Режим боя и селектор мелодии для наручных или иных часов

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EP2226688B1 (de) * 2009-03-05 2011-09-07 Vaucher Manufacture Fleurier S.A. Uhr
EP2363761B1 (de) 2010-03-05 2016-05-18 Montres Breguet SA Vorrichtung zur Messung des Drehmoments zum Abschalten des Schlagwerks
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.
EP2498143B1 (de) 2011-03-08 2018-05-02 Montres Breguet SA Isolationsmechanismus zwischen Uhrmechanismen zur Auslösung verschiedener Schlagwerkssignale
EP2503405B1 (de) * 2011-03-22 2014-07-30 Montres Breguet SA Uhr umfassend einen Schlagwerk sowie einen Mechanismus zur selektiven stoppen dieses Schlagwerks
EP2615503B1 (de) * 2012-01-13 2014-09-24 Agenhor SA Steuermechanismus eines Federhaus für Uhrwerk
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
CH714362A2 (fr) 2017-11-23 2019-05-31 Blancpain Sa Montre avec mécanisme de sonnerie à régulateur et sécurité de mise à l'heure.
EP3825781B1 (de) * 2019-11-20 2022-05-25 Chopard Technologies SA Schlagwerkmechanismus für uhr

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CH689337A5 (fr) 1996-09-03 1999-02-26 Patek Philippe Sa Pièce d'horlogerie à carillon.

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CN106030421A (zh) * 2014-02-19 2016-10-12 萧邦科技公司 用于钟表件的响铃机构
CN106030421B (zh) * 2014-02-19 2018-11-20 萧邦科技公司 用于钟表件的响铃机构
RU2690035C1 (ru) * 2017-07-25 2019-05-30 Бланпэн Са Механизм переключения режимов боя для наручных или иных часов
RU2767294C2 (ru) * 2017-07-25 2022-03-17 Бланпэн Са Режим боя и селектор мелодии для наручных или иных часов

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