EP3153935B1 - Chronometerhemmungsmechanismus eines uhrwerks mit konstanter kraft - Google Patents

Chronometerhemmungsmechanismus eines uhrwerks mit konstanter kraft Download PDF

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Publication number
EP3153935B1
EP3153935B1 EP15188461.6A EP15188461A EP3153935B1 EP 3153935 B1 EP3153935 B1 EP 3153935B1 EP 15188461 A EP15188461 A EP 15188461A EP 3153935 B1 EP3153935 B1 EP 3153935B1
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EP
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Prior art keywords
balance
escapement
bolt
escapement mechanism
detent
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English (en)
French (fr)
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EP3153935A1 (de
Inventor
Valentin Remontet
Benoît Junod
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Montres Breguet SA
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Montres Breguet SA
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Priority to EP15188461.6A priority Critical patent/EP3153935B1/de
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/10—Escapements with constant impulses for the regulating mechanism
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses

Definitions

  • the invention relates to a detent escapement mechanism for a timepiece, comprising a mechanism for directly or indirectly blocking an escape wheel during the stroke of a pendulum of an oscillating mechanism during its free rotation without impulse. controlled by a release trigger operated by means of an expansion spring, by said rocker, said locking mechanism comprising a pivoting stopper, subjected to the return torque of the first elastic return means, which stop is , during the oscillation stroke of said beam, or without contact with the trigger trigger and can pivot to an armed position under the action of said escape wheel, when it is unlocked, against said first elastic return means, or immobilized in an abutment position in which said retainer is kept armed, waiting for its release by said detent triggering, only once by oscillation of said oscillator, to then transmit to said balance a constant torque corresponding to the arming of said elastic return means.
  • the invention also relates to a watch movement comprising such an escape mechanism.
  • the invention relates to a watch comprising such a movement.
  • the invention relates to the field of high precision escapement mechanisms for watchmaking, and in particular detent escapements.
  • the trigger escapement has been used extensively for marine chronometers due to its high accuracy. However, its use for watch movements, intended to be worn in different positions, and no longer suspended by gimbals or a gyroscopic system, is struggling to develop despite a theoretically superior performance to other traditional solutions such as the escapement anchor Swiss.
  • the galloping phenomenon which corresponds to the triggering of an escape function when the balance has an amplitude greater than a certain limit amplitude value, generally close to 350 ° / 360 °, is a disadvantage that requires the development of anti-gallop systems often complex and inefficient, altering the performance of the exhaust.
  • a traditional detent escapement is characterized by the presence of a lost blow, that is to say with, during each oscillation, alternation without impulse. Often this single impulse is a direct impulse from the escapement wheel to the pendulum. The force transmitted by the escapement wheel to the balance is directly dependent on the torque transmitted to this wheel, which generally varies according to the winding of the barrel and the gear modulations.
  • the amplitude is variable, and generally decreases during disarming of the barrel, and the chronometric properties are affected.
  • the exhaust type Robin mechanisms implement a blocking lever of the escape wheel, but have the disadvantage of a direct transmission of energy from the escapement wheel to the balance, which does not solve the problem of variable amplitude.
  • the demand PCT / EP2013 / 056577 in the name of NIVAROX-FAR SA describes an escape mechanism for movement or timepiece comprising at least one balance and at least one escape wheel, where the transmission of pulses between said at least one balance and said at least one an escape wheel is produced by a one-piece flexible mechanism comprising at least one probe cooperating with said at least one escape wheel or said at least one rocker respectively, and in that said one-piece flexible mechanism is connected by at least one flexible blade to a fixed structure of said timepiece, or respectively to said at least one escape wheel.
  • the invention relates to a new expansion type exhaust system, designed to combine high precision and chronometric regularity by providing an identical impulse to the balance during each oscillation.
  • the transmission of energy is indirect, between the escape wheel and the balance.
  • the invention relates to a detent escapement mechanism for a timepiece, according to claim 1.
  • the invention also relates to a watch movement comprising such an escape mechanism.
  • the invention relates to a watch comprising such a movement.
  • the invention relates to an escapement escapement mechanism 100, with a constant force, for a timepiece 300.
  • This mechanism 100 uses a particular stopper 10 whose rotation is associated with first elastic return means 72 constituted by a flexible blade.
  • This escapement mechanism 100 detent thus comprises a mechanism for direct or indirect blocking of an escape wheel 30, during the stroke of a balance 20 of an oscillating mechanism during its free rotation without pulse, in a pivoting direction, the pulse being only in the other direction of pivoting of the balance.
  • the invention is illustrated with a balance 20 which is a pendulum in the conventional sense of the term, forming part of a balance-type oscillator spiral.
  • the invention is however applicable to other types of oscillator, and the pendulum 20 can then take other forms, such as a pendulum, or other.
  • the escape wheel 30 is conventionally subjected to a torque coming from an energy storage mechanism, and arranged to provide, during each oscillation of the oscillator mechanism, a single pulse to the balance 20.
  • This locking mechanism is controlled by an unlocking trigger 40, which is operated by means of an expansion spring 60, 71, by the rocker 20.
  • This locking mechanism comprises a pivoting stopper 10, subjected to the return torque of elastic return means 16, 18, 72.
  • triggering trigger 40 Maneuvering the triggering trigger 40 is effected, by means of the expansion spring 60, 71, by an anchor 21 and / or a triggering pallet 22 carried by the balance 20.
  • the first elastic return means 16, 18, 72 are themselves, either arranged at the stop 10 or carried by the exhaust mechanism 100.
  • the arming of the first elastic return means 16, 18, 72, in particular of the spring of the retainer 10, is done directly by the escape wheel 30 after each escape function.
  • the stopper 10 is held in the armed position by the trigger trigger 40.
  • this trigger trigger 40 is achieved by means of a trigger pad 22 integral with the rocker 20.
  • This trigger pad 22 is arranged for, in a first pivoting direction of the rocker 20 to push a distal end 61, 79 , which comprises the expansion spring 60, 71, without rotating the trigger trigger 40, and in a second pivoting direction cause the distal end 61, 79, bearing on a detent pin 42 that includes the trigger trigger 40 and rotate the latter and release the stopper 10.
  • Triggering thus occurs as a clearance, at the beginning of the exhaust function, and allows to release the stopper 10, which restores the energy previously accumulated in the first elastic return means 16, 18, 72 to the balance 20 through an ankle 21 of the balance 20, during the pulse phase.
  • the locking mechanism comprises an escape lock 50, 90, which is arranged to immobilize the escapement wheel 30 under the action of second resilient return means 53, 93, which comprises, or this lock of exhaust 50, 90, or the exhaust mechanism 100 itself.
  • the locking mechanism comprises a stop, 10 or 70 according to the embodiment, and an exhaust lock, 50 or 90 according to the embodiment.
  • the locking mechanism is further arranged to release the escape wheel 30 under a thrust action on the exhaust lock 50, 90.
  • This thrust action is either initiated by the stopper 10 during the pivoting movement of the stopper 10 under the action of the first elastic return means 16, 18, 72, just after the application of the pulse to said balance 20, or initiated directly by the balance 20 as in a fourth mode illustrated at Figures 14 to 16 .
  • the exhaust lock 50, 90 comprises an exhaust rest pallet 51, 91, which is arranged to cooperate with one of the teeth 31 that the escape wheel 30 comprises, to effect the locking of this exhaust wheel 30.
  • the exhaust lock is a first lock 50, which is remote from the rocker 20 at any point of its trajectory, and which comprises a lock arm 51 arranged to cooperate with a pusher 17 that includes the stopper 10 for unlocking the escape wheel 30.
  • the exhaust lock is a second lock 90, which comprises an arm arranged substantially radially relative to the pivot axis of the rocker 20, and which carries, in the vicinity of this pivot axis, a lock pin 94 for maintaining a flexible latch blade 92, which is arranged to cooperate with a latch pallet 23 that includes the balance 20 to control the release of the escape wheel 30.
  • the stopper 10 raises an escape lock 50, 90, which blocked the escape wheel 30, and thus releases the escape wheel 30.
  • the latter can thus reset the stop 10 and its first elastic return means 16, 18, 72, for the next exhaust function, a tooth 31 of the escape wheel 30 then push the stopper 10 in its armed position.
  • the figure 1 illustrates the different components of an escape mechanism 100, in a first embodiment whose operation is illustrated in FIGS. Figures 2 to 7 .
  • the stopper 10 is pivoted in a conventional manner
  • the first elastic return means 16 are constituted by a spring fixed to a plate of the mechanism 100, not shown in the figures, which is supported on a bearing surface. 14 of the retainer 10.
  • the latter comprises a spout 11, which, on the figures 1 and 2 is resting on the relaxation rest pallet 41 that comprises the trigger trigger 40.
  • the stop 10 further comprises a pulse arm 12, arranged to cooperate with the pin 21 of the balance 20.
  • the stop 10 further comprises a pallet 13, which is designed to cooperate directly with one of the teeth 31 of the escape wheel 30, in certain angular positions of the stopper 10.
  • the stopper 10 finally comprises a pusher 17, arranged to cooperate with an arm 52 of the first latch 50, to perform the unlocking thereof.
  • the system is initially in the armed position, and the balance 10 is in a position ready to trigger the escape function.
  • the trigger pad 22 of the rocker 20 raises the trigger trigger 40 which releases the stop 10.
  • the trigger pad 22 of the rocker 20 which rotates counterclockwise, pushes the distal end 61 of the expansion spring 60, and thus presses the detent pin 42 that carries the trigger trigger 40, which rotates the latter in the clockwise direction.
  • the spout 11 can then leave the resting rest pallet 41, and the stopper 10 can rotate clockwise, moved by its winding spring 16.
  • the stop 10 under the effect of its armature spring 16 previously armed, gives the impulse to the balance 20, by action of the impulse arm 12 of the stopper 10 on the pin 21.
  • the pusher 17 of the stopper 10 pushes the arm 52 of the first latch 50, and lifts it at the end of its stroke, in the direction of the arrow A.
  • This first latch 50 now releases the escape wheel 30 which can rotate, and will be able to reset the winding spring 16 of the stopper 10.
  • the escape wheel 30 being free, can be reset under the action of the torque transmitted by the finishing train, the winding spring 16, by action of a tooth 31 on the pallet 13 of the stopper 10.
  • the stop 10 is again maintained in the armed position by the trigger release 40, with its spout 11 resting on the rest pallet rest 41, and the escape wheel 30 comes to rest position on the first latch 50, a tooth 31 arriving to cooperate resting on the exhaust rest pallet 51. Meanwhile, the rocker 20 describes its additional arc in a counterclockwise direction.
  • the triggering pallet 22 activates the distal end of the flexible portion 61 of the triggering detent 40 (unclipping) without pressing on the pin 42, and n it does not influence the position of the other elements of the exhaust, the pin 21 not interacting with the pulse arm 12 of the stopper 10 in this position.
  • the figure 8 illustrates another example of an escapement mechanism, according to a second embodiment, wherein the first elastic return means comprise at least a first flexible blade 18 integrated in the stopper 10, and arranged in abutment abutment on a fixed support 19 that includes the exhaust mechanism 100, for example at a platen.
  • the stop 10 with a flexible part, in this case a flexible blade 18, which fulfills the function of the winding spring 16 of the first mode.
  • the retainer 10 is suspended cantilevered with respect to a fixed support that comprises the escape mechanism 100 by at least one flexible blade 18 and is movable in a plane parallel to that of the balance rod. 20, in a substantially pivotal movement about a virtual pivot, dimensioned so that the stopper 10 cooperates with the trigger 40, the pin 21 of the rocker 20, the tooth 31 of the escape wheel 30, and the arm 52 of the first latch 50.
  • the geometry of the retainer is made with a bistable flexible part.
  • the first elastic return means then comprise at least one bistable blade 72 integrated with a bistable stopper 70, which performs the same functions as the stopper 10 of the first and second modes.
  • this bistable blade 72 is arranged in tangential abutment abutment on a tangential bearing surface 75 of a bearing block 74 that includes the exhaust mechanism 100.
  • This bistable blade 72 is prestressed frontally in a state bistable on a front bearing surface 76 of the bearing block 74, with which a distal end 77 of the bistable blade 72 cooperates.
  • the stop 10 comprises a stop arm 78, which constitutes the trigger trigger, and which comprises, on the one hand the pulse arm 12 making a horn, and on the other hand a another horn that carries the detent pin 42, which keeps a first flexible blade 71, which is secured, as the bistable blade 72, a core of the bistable stop numbered 70 for this third mode.
  • This stop arm 78 thus comprises two horns, one formed by the pulse arm 12, and the other carrying the detent pin 42, and which together define a receiving space of the ankle 21.
  • the flexible portion 72 is held in the rest position by abutments (tangential support or pin or geometry of a bridge or plate) in a state of deformation close to the instability position, so that the release of the pendulum 20 allows the system to pass the instability during the exhaust function.
  • the energy accumulated in the flexible portion 72 is transmitted to the balance 20 during this jump and accumulated energy is always the same (it is always a constant force).
  • the bistable stopper 70 pivots about its axis of rotation (via a standard pivot connection or via a flexible pivoting) while the distal end 77 of the flexible portion 72 is pre-armed in compression (buckling) then frozen in this position, for example by a movement of the support block 74, as visible on the figure 10 , where it is passed, according to the arrow B, a free position in broken lines, to a preloaded position of the second flexible blade 72 in solid lines.
  • This support block 74 is then immobilized by clipping, screwing, or the like, depending on the type of embodiment chosen.
  • the figures 11 and 12 respectively illustrate the release and the end of the pulse with this third embodiment.
  • it is directly the pin 21 of the balance 20 which interacts with the distal end 79 of the first flexible blade 71, and not the trigger pad 22 of the first and second modes.
  • This first flexible blade 71 uses the same principle as the trigger since it is blocked in the direction of the release and is free to deform in the direction of the lost blow.
  • the pin 21 of the rocker 20 rotates the stopper 70 through the first flexible blade 71, which allows the flexible portion of the stopper to pass the point of instability.
  • the stopper 70 rotates very quickly to reach its stable position, this is the pulse, characterized by the jump of the bistable system.
  • the elastic potential energy accumulated in the second flexible blade 72 is transmitted to the balance 20, in the form of kinetic energy.
  • the stopper 70 raises the first lock as in the first embodiment (step 3), which allows the escape wheel 30 to reset the bistable system by rotating the retainer 70.
  • the figure 13 shows the step of the lost blow, where the pin 21 of the balance 20 comes into contact with the first flexible blade 71 in the sense that it is free to deform. This step does not cause any change in the position of the exhaust components.
  • the Figures 14 to 16 illustrate a fourth embodiment of the invention, wherein the escape mechanism 100 constitutes an anti-gallop system.
  • This solution uses the blow to let the escape wheel 30 rearm the system with constant force. Indeed, in this case, if the blow has not occurred, the pulse can not be triggered, even if amplitude greater than a limit amplitude, especially in the example illustrated at 360 °, because the system is not reset. Such a system avoids the phenomenon of gallop.
  • the peg 21 of the rocker 20 then comes back against the outside cuff of the stop horn carrying the impulse arm 12.
  • This construction comprises an escape latch 90 which interacts directly with a latch pallet 23 integral with the balance 20, instead of interacting with the stopper when the latter ends its momentum.
  • This exhaust lock is a second lock 90, which comprises an arm arranged substantially radially with respect to the axis of pivoting of the rocker 20, and which carries, in the vicinity of this pivot axis, a lock pin 94 for maintaining a flexible latch blade 92, which is arranged to cooperate with the latch pallet 23 to control the unlocking of the escape wheel 30.
  • the escape function takes place in two stages since the clearance and momentum steps proceed as described previously during the first half-cycle, while the unblocking, rearming, and blocking steps take place during the first half-cycle. the second alternation corresponding previously to the lost blow.
  • the lock pallet 23 first impacts the flexible latch blade 92 of the second latch 90, which is blocked by the latch pin 94, which raises the second latch 90 according to the arrow D, and releases the escape wheel 30, as visible on the figure 15 .
  • the escape wheel can then reset the stop, whether it is a stop 10 of the first and second modes, or a bistable stop 70 of the third mode as visible on the Figures 14 to 16 .
  • the pin 21 of the balance 20 then arrives at the reference level and collides in the non-locking direction with the first flexible blade 71 of the stop 70: this is the blow of the figure 16 If the reset of the stop is made too late compared to the mark, the pin 21 of the balance 20 collides with the horn of the stopper 70, as for a clearance, and it is the balance 20 which resets the stop, which is best avoided.
  • This anti-gallop function certainly represents an additional consumption on the balance 20 but makes it possible to eliminate the part of the unlocking step, where the stopper must raise the lock, which also represented a consumption (less efficient pulse).
  • This fourth mode is compatible with the other three proposed embodiments.
  • the pendulum pin 21 rebates against the back of the horn since the latter has not returned in armed position.
  • FIGS 17 to 22 illustrate a fifth embodiment of the invention, wherein the escape mechanism 100 is an anti-gallop system, and is an improvement of the fourth mode above, the general principles of operation are retained.
  • the lock pallet 23 firstly impacts the flexible lock blade 92 of the second latch 90, which raises the latter according to the arrow D, and releases the escape wheel 30, as visible on the figure 18 .
  • the escape wheel 30 can then reset the stop, whether it is a stop 10 of the first and second modes, or a bistable stop 70 of the third mode as visible on the Figures 14 to 16 .
  • the pin 21 of the balance 20 then arrives at the reference level and collides in the non-locking direction with the first flexible blade 71 of the stop 70: this is the blow of the figure 21 If the reset of the stop is made too late compared to the mark, the pin 21 of the balance 20 collides with the horn of the stopper 70, as for a clearance, and it is the balance 20 which resets the stop, which is best avoided.
  • the first step is clearance, as visible on the figure 17
  • the pin 21 of the rocker 20 pushes the first flexible blade 71 of the stopper 70 in its locked direction, which causes the instability of the second flexible bistable blade 72 associated with the stopper 70, or else, for the first mode embodiment, it is the trigger pad 22 which raises the trigger trigger 40, which releases the stopper 10.
  • the second step relates to the impulse.
  • the stop 70 under the effect of its armed elastic return means, gives, by its pulse arm 12, the pulse to the balance 20 via the pin 21.
  • the stopper 70 also raises, by a pusher 17 that it comprises, a thrust surface 96 that includes a direct lock arm 95, that includes the second latch 90, but not enough to release the escape wheel 30.
  • stop 70 is not reset, but the lifting of the second latch 90 has placed the end of its flexible lock blade 92 in the path of the latch pallet 23 for the next step.
  • the third step, illustrated in figure 19 relates to the unlocking of the escape wheel 30.
  • the latch pallet 23 raises the end of the flexible lock blade 92 of the second latch 90 which in the trajectory of the latch pallet 23, thanks to the stopper 70 which lifted it during the previous stage, at the end of its race.
  • the second latch 90 can then release the escape wheel 30 which will be able to reset the elastic return means of the retainer 70.
  • the fourth step, illustrated by the figure 20 therefore concerns the rearmament.
  • the escape wheel 30 being free, the direct rest pallet 91 having released the tooth 31 which was bearing on it, under the action of the torque transmitted by the finishing train, this escape wheel 30 can rearm the stop 70, by pushing a tooth 31 on a pallet 13 of the stop 70.
  • This rearrangement allows to put back the stop 70 in its initial position just before the arrival of the pin 21 of the balance 20. It is essential that the stopper 70 is completely rearmed before the arrival of the pin 21 of the balance 20, to avoid a collision between the latter and the fork of the stop arm 78, which would correspond to a clearance, while this alternation must be a blow.
  • the fifth and sixth steps, illustrated by figure 21 concern the: blockage and the blow lost.
  • This function certainly represents additional consumption on the balance but prevents the stop 70 must completely lift the second latch 90, which also represents a consumption (less effective pulse).
  • the invention lends itself well to one-piece constructions with silicon components, DLC silicon oxides, or the like.
  • the invention also relates to a watch movement 200 comprising such an escape mechanism 100, and comprising an oscillator mechanism comprising this rocker 20, and at least one energy storage mechanism arranged to apply a driving torque to at least one such exhaust wheel 30.
  • the invention also relates to a watch 300 comprising at least one such movement 200.
  • the invention brings many advantages.
  • the use of a direct arming system on the stopper makes it possible to make the movement of the latter independent of the inertia of the escape wheel and the rest of the finishing gear.
  • the stop can thus come into contact with the ellipse of the rocker very quickly after the release (very short catch-up time), which favors the pulse and therefore the efficiency of the escapement.
  • This system is therefore particularly advantageous for fast escape functions (high frequency oscillator) and for systems in which the equivalent inertia of the escape wheel is important (for example vortices).
  • This solution also has the advantage, as for a traditional expansion exhaust, to give a single pulse oscillation (against two for a Swiss lever escapement) which increases the energy transmitted by exhaust function and so reduce (with equivalent power reserve) the multiplication ratio between the barrel and the exhaust (the lost blow represents, on the other hand, a not insignificant consumption which limits this advantage).
  • the anti-gallop system presented is compatible with all embodiments and avoids counting errors in case of too high amplitude, which is one of the main defects of a traditional expansion exhaust.
  • the illustrated mechanism does not include a stinger, it is therefore achievable on a number of levels limited to two in addition to the level specific to the balance rod, which is favorable for the thickness of the movement.

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Claims (22)

  1. Hemmungsmechanismus (100) mit Gesperr für ein Zeitmessgerät (300), umfassend einen Mechanismus für die direkte oder indirekte Sperrung eines Hemmungsrades (30) während des Laufs einer Unruh (20) eines Schwingungsmechanismus in seiner freien Halbschwingung ohne Impuls, der durch ein Auslösegesperr (40), das mittels einer Gesperrfeder (60, 71) durch die Unruh (20) betätigt wird, entsperrend gesteuert wird, wobei der Sperrmechanismus eine schwenkbare Arretierung (10, 70) umfasst, die einem Rückstelldrehmoment erster elastischer Rückstellmittel (16, 18, 72) unterliegt, wobei die Arretierung (10, 70) während des Schwingungslaufs der Unruh (20) entweder ohne Kontakt mit dem Auslösegesperr (40) ist und in eine gespannte Position schwenkbar ist, die unter der Wirkung des Hemmungsrades (30), wenn es entsperrt ist, entgegen den ersten elastischen Rückstellmitteln (16, 18, 72) gespannt ist, oder in einer Anschlagposition festgesetzt ist, in der die Arretierung (10, 70) gespannt gehalten wird bis zu ihrer einmaligen Freigabe durch das Auslösegesperr (40) pro Schwingung des Oszillators, um dann an die Unruh (20) ein konstantes Drehmoment zu übertragen, das der Spannung der elastischen Rückstellmittel (16, 18, 72) entspricht, dadurch gekennzeichnet, dass die ersten elastischen Rückstellmittel (16, 18, 72) mindestens ein bistabiles Blatt (72) aufweisen, das in die Arretierung (10, 70) integriert ist und sich auf einer tangentialen Abstützfläche (75) eines Abstützblocks (74), den der Hemmungsmechanismus (100) aufweist, tangential anschlagend abstützt, und in einem bistabilen Zustand abgestützt auf einer frontalen Abstützfläche (76) des Abstützblocks (74), mit der ein distales Ende (77) des bistabilen Blatts (72) zusammenwirkt, frontal vorgespannt ist.
  2. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass das Hemmungsrad (30) einem Drehmoment unterliegt, das von einem Energiespeichermechanismus stammt, und dafür ausgelegt ist, bei jeder Schwingung des Schwingungsmechanismus Energie für einen einzelnen Impuls an die Unruh (20) zu liefern, dass das Auslösegesperr (40) mittels der Gesperrfeder (60, 71) durch einen Stift (21) und/oder eine Auslösepalette (22), die die Unruh (20) aufweist, betätigt wird, und dass die ersten elastischen Rückstellmittel (16, 18, 72) an der Arretierung (10, 70) angeordnet sind oder durch den Hemmungsmechanismus (100) getragen werden.
  3. Hemmungsmechanismus (100) nach Anspruch 2, dadurch gekennzeichnet, dass der Sperrmechanismus einen Hemmungsriegel (50, 90) umfasst, der angeordnet ist, um die Sperrung des Hemmungsrades (30) unter der Wirkung zweiter elastischer Rückstellmittel (53, 93), die der Hemmungsriegel (50, 90) oder der Hemmungsmechanismus (100) aufweist, zu bewirken oder um die Entsperrung des Hemmungsrades (30) unter einer Schubwirkung auf den Hemmungsriegel (50, 90) zu bewirken, wobei die Schubwirkung entweder durch die Arretierung (10, 70) während der Schwenkbewegung der Arretierung (10, 70) unter der Wirkung der ersten elastischen Rückstellmittel (16, 18, 72) unmittelbar nach Anlegen des Impulses an die Unruh (20) ausgelöst wird oder direkt durch die Unruh (20) ausgelöst wird.
  4. Hemmungsmechanismus (100) nach Anspruch 3, dadurch gekennzeichnet, dass der Hemmungsriegel (50, 90) einen Hebestein (51, 91) der Hemmung umfasst, der so angeordnet ist, dass er mit einem der Zähne (31), die das Hemmungsrad (30) aufweist, zusammenwirkt, um die Sperrung des Hemmungsrades (30) zu bewirken.
  5. Hemmungsmechanismus (100) nach Anspruch 3, dadurch gekennzeichnet, dass der Hemmungsriegel (50, 90) ein erster Riegel (50) ist, der von der Unruh (20) auf jedem Punkt seiner Bahn beabstandet ist und der einen Verriegelungsarm (51) aufweist, der so angeordnet ist, dass er mit einem Drücker (17) zusammenwirkt, den die Arretierung (10, 70) zum Entsperren des Hemmungsrades (30) aufweist.
  6. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass die Arretierung (10, 70) in ihrer Anschlagposition durch das Auslösegesperr (40) gespannt gehalten wird.
  7. Hemmungsmechanismus (100) nach Anspruch 3, dadurch gekennzeichnet, dass der Hemmungsriegel (50, 90) ein zweiter Riegel (90) ist, der einen Arm aufweist, der im Wesentlichen radial in Bezug auf die Schwenkachse der Unruh (20) angeordnet ist und der in der Nähe der Schwenkachse einen Sicherungsstift (94) trägt, um ein flexibles Verriegelungsblatt (92) zu halten, das so angeordnet ist, dass es mit einer Verriegelungspalette (23) zusammenwirkt, die die Unruh (20) aufweist, um die Entsperrung des Hemmungsrades (30) zu steuern.
  8. Hemmungsmechanismus (100) nach Anspruch 7, dadurch gekennzeichnet, dass der zweite Riegel (90) einen direkten Verriegelungsarm (95) umfasst, der eine Schuboberfläche (96) aufweist, die dafür ausgelegt ist, mit einem Drücker (17) zusammenzuwirken, den die Arretierung (10, 70) aufweist, um das flexible Verriegelungsblatt (92) auf der Bahn der Verriegelungspalette (23) der Unruh (20) anzuordnen.
  9. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass das Auslösegesperr (40) durch einen Arretierungsarm (78) der Arretierung (10, 70) gebildet ist und einen Gesperrstift (42) zum Halten der Gesperrfeder (60, 71) trägt.
  10. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass die Arretierung (10, 70) einen Impulsarm (12) aufweist, der so angeordnet ist, dass er an einen Stift (21), den die Unruh (20) aufweist, einen Impuls abgibt.
  11. Hemmungsmechanismus (100) nach den Ansprüchen 9 und 10, dadurch gekennzeichnet, dass der Arretierungsarm (78) zwei Hörner aufweist, von denen eines durch den Impulsarm (12) gebildet ist und das andere den Gesperrstift (42) trägt und die zusammen einen Raum für die Aufnahme des Stifts (21) begrenzen.
  12. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass die Gesperrfeder (60, 71) gebildet ist durch ein erstes flexibles Blatt (71), das in die Arretierung (10, 70) integriert ist.
  13. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass die Unruh (20) eine Auslösepalette (22) umfasst, die so angeordnet ist, dass sie in einer ersten Schwenkrichtung der Unruh (20) ein distales Ende (61, 79), das die Gesperrfeder (60, 71) aufweist, zurückschiebt, ohne das Auslösegesperr (40) zu schwenken, und in einer zweiten Schwenkrichtung das distale Ende (61, 79) abstützend auf einem Gesperrstift (42), den das Auslösegesperr (40) umfasst, antreibt und dieses Letztere schwenkt und die Arretierung (10, 70) freigibt.
  14. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass der Hemmungsmechanismus (100) eine monolithische Anordnung umfasst, die eine Platte, die Arretierung (10, 70) und eine flexible Verbindung umfasst, die einen virtuellen Schwenkpunkt der Arretierung (10, 70) in Bezug auf die Platte definiert.
  15. Hemmungsmechanismus (100) nach den Ansprüchen 3 und 14, dadurch gekennzeichnet, dass die monolithische Anordnung weiterhin den Hemmungsriegel (50, 90) umfasst, der an der Platte über ein Federblatt, das eines der zweiten elastischen Rückstellmittel (53, 93) bildet, freitragend angehängt ist.
  16. Hemmungsmechanismus (100) nach Anspruch 15, dadurch gekennzeichnet, dass die monolithische Anordnung weiterhin das Auslösegesperr (40) und die Gesperrfeder (60, 71) umfasst.
  17. Hemmungsmechanismus (100) nach Anspruch 1, dadurch gekennzeichnet, dass der Hemmungsmechanismus (100) eine monolithische Anordnung umfasst, die eine Platte, die Arretierung (10, 70), das bistabile Blatt (72) und den Abstützblock (74) umfasst, der an mindestens einem flexiblen Blatt beweglich montiert ist zwischen einer Annäherungsposition, in der das bistabile Blatt (72) frei ist, und einer vorgespannten Position, in der das bistabile Blatt (72) durch Knicken vorgespannt ist, wobei die monolithische Anordnung Befestigungsmittel zum Halten des Abstützblocks (74) in der vorgespannten Position umfasst.
  18. Hemmungsmechanismus (100) nach den Ansprüchen 7 und 14, dadurch gekennzeichnet, dass die monolithische Anordnung weiterhin den zweiten Riegel (90) und das flexible Verriegelungsblatt (92) umfasst.
  19. Hemmungsmechanismus (100) nach Anspruch 18, dadurch gekennzeichnet, dass die monolithische Anordnung weiterhin das Auslösegesperr (40) und die Gesperrfeder (60, 71) umfasst.
  20. Hemmungsmechanismus (100) nach Anspruch 17 oder 18, dadurch gekennzeichnet, dass die monolithische Anordnung weiterhin das bistabile Blatt (72) und den Abstützblock (74) umfasst, der an mindestens einem flexiblen Blatt beweglich montiert ist zwischen einer Annäherungsposition, in der das bistabile Blatt (72) frei ist, und einer vorgespannten Position, in der das bistabile Blatt (72) durch Knicken vorgespannt ist, wobei die monolithische Anordnung Befestigungsmittel zum Halten des Abstützblocks (74) in der vorgespannten Position umfasst.
  21. Uhrwerk (200), umfassend einen Hemmungsmechanismus (100) nach Anspruch 1 und umfassend einen Schwingungsmechanismus, der die Unruh (20) enthält, und mindestens einen Energiespeichermechanismus umfasst, der angeordnet ist, um ein Antriebsdrehmoment auf mindestens ein Hemmungsrad (30) auszuüben.
  22. Uhr (300), umfassend mindestens ein Werk (200) nach Anspruch 21.
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WO2022238524A1 (fr) * 2021-05-12 2022-11-17 Rolex Sa Echappement a energie constante pour piece d'horlogerie
WO2023046841A1 (fr) * 2021-09-23 2023-03-30 Greubel Forsey S.A. Mouvement d'horlogerie

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EP3489762B1 (de) * 2017-11-23 2020-09-09 Gfpi S.A. Betriebssystem für uhr
CH715023A1 (fr) 2018-05-25 2019-11-29 Sa De La Manufacture Dhorlogerie Audemars Piguet & Cie Échappement à détente auto-démarrant et sécurisé pour pièce d'horlogerie
CH716827A1 (fr) * 2019-11-22 2021-05-31 Csem Ct Suisse Delectronique Microtechnique Sa Rech Developpement Régulateur mécanique horloger comportant un échappement à force constante.

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DE42856C (de) * 1900-01-01 P. th. A. rodeck in Amsterdam, Nieuwendyk 116/118 Chronometerhemmung mit konstanter Kraft

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Publication number Priority date Publication date Assignee Title
WO2022238524A1 (fr) * 2021-05-12 2022-11-17 Rolex Sa Echappement a energie constante pour piece d'horlogerie
WO2023046841A1 (fr) * 2021-09-23 2023-03-30 Greubel Forsey S.A. Mouvement d'horlogerie

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