EP3153935A1 - Timepiece detent escapement mechanism with constant force - Google Patents

Abstract

Escaping escapement mechanism (100) comprising a mechanism for direct or indirect blocking of an escape wheel (30) during the travel of a rocker (20) during its free rotation, controlled by an unlocking device triggering (40) operated by means of an expansion spring (60, 71) by the rocker (20). This locking mechanism comprises a pivoting stopper (10, 70), subjected to the elastic return means return torque (16), which is or is not in contact with the triggering trigger (40) and can pivot towards an armed position under the action of the escape wheel (30), when it is unlocked, against the elastic return means (16), or immobilized in an abutment position in which it is kept armed by the trigger of trigger (40), waiting for its release to transmit to the balance (20) a constant torque corresponding to the arming of the elastic return means (16).

Description

Field of the invention

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 in unblocking by a trigger trigger actuated by means of a spring, by said balance.

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.

Background of the invention

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 escape wheel pendulum is directly dependent on the torque transmitted to this wheel, which generally varies according to the winding of the barrel and modulations gear.

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.

Requirement 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.

Summary of the invention

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, according to the invention, is indirect, between the escape wheel and the balance.

For this purpose, 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.

Brief description of the drawings

• la figure 1 représente, de façon schématisée, et en perspective, un mécanisme d'échappement constant à détente selon l'invention, dans un premier mode de réalisation ;
• les figures 2 à 7 représentent, en vue en plan, des étapes successives de fonctionnement de ce premier mode de réalisation, comportant un arrêtoir rappelé par un ressort externe:
• figure 2 : première étape de dégagement ;
• figure 3 : deuxième étape d'impulsion ;
• figure 4 : troisième étape déblocage de la roue d'échappement ;
• figure 5 : quatrième étape de réarmage ;
• figure 6 : cinquième étape de blocage.
• figure 7 : sixième étape correspondant au coup perdu,
• la figure 8 représente, en vue en plan, un deuxième mode de réalisation de l'invention, comportant un arrêtoir flexible, réalisé monobloc avec une lame flexible ;
• les figures 9 à 13 représentent, en vue en plan, un troisième mode de réalisation, comportant un arrêtoir flexible bistable, comportant une lame flexible bistable précontrainte en flambage ;
• la figure 10 illustre la mise en flambage de cet arrêtoir flexible bistable mis en flambage, depuis une première position en trait interrompu, vers une deuxième position en trait plein ;
• la figure 11 illustre l'étape de dégagement ;
• la figure 12 illustre la fin de l'impulsion ;
• la figure 13 illustre le coup perdu ;
• les figures 14 à 16 représentent, en vue en plan, un quatrième mode de réalisation, constituant un système anti-galop, comportant l'arrêtoir flexible bistable du troisième mode, et comportant un mécanisme de verrouillage direct à lame élastique, agencé pour coopérer à la fois avec la denture de la roue d'échappement, et avec une palette de verrou dont est alors équipé le balancier ;
• la figure 15 illustre l'étape de déclenchement réarmage ;
• la figure 16 illustre l'état de l'arrêtoir réarmée avant le coup perdu ;
• les figures 17 à 22 représentent, en vue en plan, un cinquième mode de réalisation, constituant un système anti-galop, comportant l'arrêtoir flexible bistable du troisième mode, et comportant un autre mécanisme de verrouillage direct à lame élastique, agencé pour coopérer à la fois avec la denture de la roue d'échappement, et avec une palette de verrou dont est alors équipé le balancier;
• la figure 17 illustre l'étape de dégagement;
• la figure 18 illustre l'étape d'impulsion;
• la figure 19 illustre l'étape de déblocage ;
• la figure 20 illustre l'étape de réarmage ;
• la figure 21 illustre l'étape de blocage et de coup perdu
• la figure 22 illustre le rebat en cas d'amplitude supérieure à une amplitude limite, par exemple à 350° lors du premier arc supplémentaire ;
• la figure 23 est un schéma-blocs représentant une montre comportant un mouvement qui comporte lui-même un tel mécanisme d'échappement selon l'invention.

Other features and advantages of the invention will appear on reading the detailed description which follows, with reference to the appended drawings, in which:

• the figure 1 represents, schematically, and in perspective, a constant expansion escapement mechanism according to the invention, in a first embodiment;
• the Figures 2 to 7 represent, in plan view, successive steps of operation of this first embodiment, comprising a stop recalled by an external spring:
• figure 2 : first step of release;
• figure 3 : second impulse stage;
• figure 4 : third step unlocking the escape wheel;
• figure 5 : fourth step of rearming;
• figure 6 : fifth blocking step.
• figure 7 : sixth step corresponding to the lost blow,
• the figure 8 represents, in plan view, a second embodiment of the invention, comprising a flexible retainer, integrally formed with a flexible blade;
• the Figures 9 to 13 represent, in plan view, a third embodiment, comprising a bistable flexible retainer, comprising a bistable flexible blade prestressing buckling;
• the figure 10 illustrates the buckling of this flexibly bistable flexible retainer, from a first position in broken lines, to a second position in full line;
• the figure 11 illustrates the disengagement step;
• the figure 12 illustrates the end of the impulse;
• the figure 13 illustrates the lost blow;
• the Figures 14 to 16 show, in plan view, a fourth embodiment, constituting an anti-gallop system, comprising the bistable flexible retainer of the third mode, and comprising a direct locking mechanism with an elastic blade, arranged to cooperate both with the toothing. of the escape wheel, and with a pallet of lock which is then equipped with the balance;
• the figure 15 illustrates the reset triggering step;
• the figure 16 illustrates the state of the rearranged stop before the blow is lost;
• the Figures 17 to 22 show, in plan view, a fifth embodiment, constituting an anti-gallop system, comprising the bistable flexible retainer of the third mode, and comprising another direct locking mechanism to elastic blade, arranged to cooperate with both the teeth of the escape wheel, and with a pallet lock which is then equipped with the balance;
• the figure 17 illustrates the disengagement step;
• the figure 18 illustrates the impulse step;
• the figure 19 illustrates the unblocking step;
• the figure 20 illustrates the re-arming step;
• the figure 21 illustrates the blocking and losing step
• the figure 22 illustrates the rebate in case of amplitude greater than a limit amplitude, for example at 350 ° during the first additional arc;
• the figure 23 is a block diagram representing a watch comprising a movement which itself comprises such an exhaust mechanism according to the invention.

Detailed Description of the Preferred Embodiments

The invention relates to an escapement escapement mechanism 100, with a constant force, for a timepiece 300. This mechanism 100 uses a particular retainer 10, whose rotation is associated with first elastic return means 16, 18, 72, in particular but not limited to an armature spring, or a flexible blade, or the like.

Its operation is based on the general principles of detent exhausts, which are not detailed here.

Four non-limiting embodiments are illustrated by the figures and will be detailed below.

This escapement mechanism 100 with detent thus comprises a mechanism for directly or indirectly blocking an escape wheel 30, during the stroke of a balance 20 of an oscillating mechanism during its free rotation without impulse, in a direction of pivoting, 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, when of each oscillation of the oscillator mechanism, a single impulse to the pendulum 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.

According to the invention, this locking mechanism comprises a pivoting stopper 10, subjected to the return torque of elastic return means 16, 18, 72.

• ou bien sans contact avec la détente de déclenchement 40, et peut alors pivoter vers une position armée sous l'action de la roue d'échappement 30, quand celle-ci est débloquée, à l'encontre des moyens de rappel élastique 16, 18, 72 ;
• ou bien immobilisé dans une position de butée dans laquelle l'arrêtoir 10 est maintenu armé, notamment dans un mode de réalisation particulier par la détente de déclenchement 40, en attente de sa libération par la détente de déclenchement 40, une seule fois par oscillation de l'oscillateur, pour transmettre alors au balancier 20 un couple constant correspondant à l'armage des moyens de rappel élastique 16, 18, 72.

This stop 10 is, during the oscillating stroke of the balance 20:

• or without contact with the trigger trigger 40, and can then pivot to an armed position under the action of the escape wheel 30, when the latter is released, against the elastic return means 16, 18 , 72;
• or else immobilized in an abutment position in which the stopper 10 is kept armed, in particular in a particular embodiment by the triggering trigger 40, waiting for its release by the triggering trigger 40, only once per oscillation of the oscillator, to then transmit to the balance 20 a constant torque corresponding to the arming of the elastic return means 16, 18, 72.

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 the spring of the retainer 10, is done directly by the escape wheel 30 after each exhaust function. In a particular embodiment, the stopper 10 is held in the armed position by the trigger trigger 40.

In certain non-limiting embodiments, in particular as visible on the Figures 1 to 8 , the release of 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 includes the expansion spring 60, 71, without rotating the trigger trigger 40, and in a second pivoting direction to cause the distal end 61, 79, in pressing on a detent pin 42 that includes trigger trigger 40 and rotate the latter and release the retainer 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.

In sum, according to the invention, 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 .

More particularly, 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.

In the first three embodiments illustrated in Figures 1 to 13 , 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.

In the fourth embodiment of the Figures 14 to 16 , and in the fifth mode of Figures 17 to 22 , the exhaust lock is a second lock 90, which comprises an arm arranged substantially radially relative to the pivot axis of the balance 20, and which carries, in the vicinity of this axis of pivoting, a lock pin 94 for holding a flexible latch blade 92, which is arranged to cooperate with a latch pallet 23 that includes the rocker 20 to control the release of the escape wheel 30.

At the end of the exhaust function, 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 various components of the exhaust mechanism 100 of the invention, in a first embodiment whose operation is illustrated in FIGS. Figures 2 to 7 . In this first mode, 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.

On the figure 1 , the system is initially in the armed position, and the balance 10 is in a position ready to trigger the escape function.

During the clearance step, illustrated in figure 2 , the trigger pad 22 of the rocker 20 raises the trigger trigger 40 which releases the stop 10. To do this, 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. Beak 11 can then leave the relaxation rest pallet 41, and the stopper 10 can rotate clockwise, moved by its winding spring 16.

During the impulse step, illustrated in figure 3 , 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.

During the unblocking step, illustrated in figure 4 , 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.

During the rearming step, illustrated in figure 5 , 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.

During the blocking step, illustrated in figure 6 , 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.

In the lost shot stage, illustrated in figure 7 during the return of the balance in the opposite direction of rotation, in this hourly time, 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 a second embodiment, wherein the first resilient return means comprise at least a first flexible blade 18 integrated with the stopper 10, and arranged in abutment abutment on a fixed support 19 that includes the exhaust mechanism 100, by example at a platinum level. This produces 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. This allows to have one component less, knowing that this type of component is easily achievable by manufacturing processes such as "LIGA" (nickel alloy) or "DRIE" (silicon), or the like.

More particularly, 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.

In a third embodiment of the invention, illustrated in Figures 9 to 13 , we realize the geometry of the stop 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. Advantageously, 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.

This solution uses the bistability of the flexible portion 72 of the retainer 10 to maintain the latter in the rest position. This makes it possible to dispense with an independent trigger trigger. On the non-limiting variant shown, 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 maintains a first flexible blade 71, which is integral, as the bistable blade 72, a core of the bistable stopper 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.

It is the escape wheel 30, after the escape function, which resets the system until passing the point of instability. 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 balance 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).

To obtain a bistable state of the bistable stopper 70, it 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. In this case, 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.

Upon disengagement, 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. Once the instability point passed, the stopper 70 rotates very quickly to reach its stable position, this is the pulse, characterized by the jump of the bistable system. During this jump, the elastic potential energy accumulated in the second flexible blade 72 is transmitted to the balance 20, in the form of kinetic energy.

At the end of the impulse, that is to say at the end of the jump, 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.

In this case, 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.

During the second alternation and before the passage of the mark, 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-blocking 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. In case of higher amplitudes (greater than a limit amplitude, in particular 330 ° / 350 ° for conventional balance sprung oscillators) the pendulum pin 21 rebates against the back of the horn since the latter has not returned in armed position.

The Figures 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.

As for the fourth mode, during the second half-cycle and before the passage of the mark, 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 realization, it is the trigger pad 22 which raises the trigger trigger 40, which releases the stopper 10.

The second step, illustrated in figure 18 , 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. At the end of the pulse l 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. During the second alternation of the balance 20 (which normally corresponds to the lost blow), 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 rearming allows to put the stopper 70 in its initial position just before the arrival of the pin 21 of the balance 20. It is essential that the stop 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 release, while this alternation must be a lost shot.

The fifth and sixth steps, illustrated by figure 21 , concern the: blockage and the blow lost. Once the escape wheel 30 has completely reset the stop 70, it comes into rest position by pressing a tooth 31 on the direct pallet 91 of the second lock 90. Meanwhile, the pin 21 of the balance 20 collides with the first flexible blade 71 of the stop 70 in the flexible direction, which does not change the position of the components of the exhaust.

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).

This mechanism is compatible with the first three proposed embodiments. In the case of amplitudes higher than the limiting amplitude, for example greater than 330 ° / 350 °, the rocker pin 21 rests against the reverse of the stop horn formed by the pulse arm 12, during the first additional arc (before the blow lost) since the stop 70 is not yet returned in the armed position, as visible on the figure 22 . In addition, during the second additional arc, after the blow lost, the balance 20 can travel up to the limit amplitude, without unlocking the second latch 90, since it is no longer in the path of the pallet lock 23.

The invention lends itself well to one-piece constructions with silicon components, DLC silicon oxides, or the like.

• le mécanisme d'échappement 100 comporte un ensemble monolithique comportant une platine, ledit arrêtoir 10, et une lame flexible 18 de suspension en porte-à-faux dudit arrêtoir 10 à ladite platine ;
  • ∘ et ensemble monolithique comporte encore ledit verrou d'échappement 50, 90 qui est suspendu en porte-à- faux à ladite platine par une lame-ressort constituant un desdits deuxièmes moyens de rappel élastique 53, 93 ;
  • ∘ cet ensemble monolithique comporte encore ladite détente de déclenchement 40 et ledit ressort de détente 60, 71.
• le mécanisme d'échappement 100 comporte un ensemble monolithique comportant une platine, ledit arrêtoir 10, et une liaison flexible définissant un pivot virtuel dudit arrêtoir 10 par rapport à ladite platine ;
  • ∘ cet ensemble monolithique comporte encore ledit verrou d'échappement 50, 90 qui est suspendu en porte-à-faux à ladite platine par une lame-ressort constituant un desdits deuxièmes moyens de rappel élastique 53, 93 ;
  • ∘ cet ensemble monolithique comporte encore ladite détente de déclenchement 40 et ledit ressort de détente 60, 71.
• le mécanisme d'échappement 100 comporte un ensemble monolithique comportant une platine, ledit arrêtoir 10, ladite lame bistable 72 et ledit bloc d'appui 74 lequel est monté mobile sur au moins une lame flexible entre une position d'approche dans laquelle ladite lame bistable 72 est libre, et une position de précontrainte dans laquelle ladite lame bistable 72 est précontrainte en flambage, ledit ensemble monolithique comportant des moyens de fixation pour le maintien dudit bloc d'appui 74 dans ladite position de précontrainte ;
  • ∘ cet ensemble monolithique comporte encore ledit deuxième verrou 90 et ladite lame flexible de verrou 92 ;
  • ∘ cet ensemble monolithique comporte encore ladite détente de déclenchement 40 et ledit ressort de détente 60, 71 ;
  • ∘ cet ensemble monolithique comporte encore ladite lame bistable 72 et ledit bloc d'appui 74 lequel est monté mobile sur au moins une lame flexible entre une position d'approche dans laquelle ladite lame bistable 72 est libre, et une position de précontrainte dans laquelle ladite lame bistable 72 est précontrainte en flambage, ledit ensemble monolithique comportant des moyens de fixation pour le maintien dudit bloc d'appui 74 dans ladite position de précontrainte.

More particularly, we list here some non-limiting achievements:

• the escape mechanism 100 comprises a monolithic assembly comprising a plate, said retainer 10, and a flexible blade 18 for cantilevered suspension of said retainer 10 to said plate;
  • ∘ and monolithic assembly further comprises said exhaust lock 50, 90 which is suspended cantilever said platen by a leaf spring constituting one of said second elastic return means 53, 93;
  • This monolithic assembly further comprises said triggering trigger 40 and said expansion spring 60, 71.
• the escape mechanism 100 comprises a monolithic assembly comprising a plate, said retainer 10, and a flexible link defining a virtual pivot of said retainer 10 relative to said plate;
  • This monolithic assembly further comprises said exhaust latch 50, 90 which is suspended cantilevered to said plate by a leaf spring constituting one of said second elastic return means 53, 93;
  • This monolithic assembly further comprises said triggering trigger 40 and said expansion spring 60, 71.
• the escapement mechanism 100 comprises a monolithic assembly comprising a plate, said retainer 10, said bistable blade 72 and said support block 74 which is movably mounted on at least one flexible blade between an approach position in which said bistable blade 72 is free, and a prestressing position in which said bistable blade 72 is prestressing in buckling, said monolithic assembly comprising fastening means for maintaining said support block 74 in said prestressing position;
  • This monolithic assembly further comprises said second latch 90 and said flexible latch blade 92;
  • This monolithic assembly further comprises said triggering trigger 40 and said expansion spring 60, 71;
  • This monolithic assembly further comprises said bistable blade 72 and said support block 74 which is movably mounted on at least one flexible blade between an approach position in which said bistable blade 72 is free, and a prestressing position in which said Bistable blade 72 is prestressing in buckling, said monolithic assembly comprising fastening means for holding said support block 74 in said prestressing position.

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.

Indeed, the solutions proposed above all allow to have a constant force transmitted to the balance, and thus to ensure a constant amplitude during disarming, and without the influence of gear modulations that disrupt chronometry in a traditional system .

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.

However this mechanism can be equipped with a dart for extra security.

• démonstrateur d'échappement ;
• chronomètre de marine ;
• mouvement haute fréquence ;
• mouvement à très grande réserve de marche ;
• tourbillon.

The invention can be used particularly, and not exclusively, for:

• exhaust demonstrator;
• marine chronometer;
• high frequency movement;
• movement with a very large power reserve;
• whirlwind.

Claims (28)

Exhaust mechanism (100) for a timepiece (300) having a mechanism for direct or indirect locking of an escape wheel (30) during the travel of a balance (20) of a mechanism oscillator during its free rotation without pulse, controlled in release by a trigger trigger (40) manipulated, via an expansion spring (60, 71), by said rocker (20), characterized in that said mechanism blocking device comprises a pivoting stopper (10, 70) subjected to the return torque of first elastic return means (16, 18, 72), which stopper (10, 70) is, during the oscillation stroke of said balance (20), or without contact with the trigger trigger (40) and can pivot to an armed position under the action of said escape wheel (30), when it is unlocked, against said first elastic return means (16, 18, 72), or immobilized in a stop position d when said stopper (10, 70) is kept armed, waiting for its release by said triggering trigger (40), only once by oscillation of said oscillator, to then transmit to said balance (20) a constant torque corresponding to the arming said elastic return means (16, 18, 72). Exhaust mechanism (100) according to claim 1, characterized in that said escape wheel (30) is subjected to a torque from an energy storage mechanism and arranged to provide, during each oscillation of said mechanism oscillator, the energy for a single pulse of said balance (20), in that said triggering trigger (40) is operated, via said expansion spring (60, 71), by an ankle (21) or / and a trigger pad (22) carried by said rocker (20), in that said first elastic return means (16, 18, 72) are arranged at said stop (10, 70) or are carried by said rocker arm exhaust (100). Exhaust mechanism (100) according to claim 2, characterized in that said locking mechanism comprises an exhaust lock (50, 90) arranged to effect the locking of said escape wheel (30) under the action of second elastic return means (53, 93) provided by said exhaust lock (50, 90) or said exhaust mechanism (100), or for unlocking said escape wheel (30) under pushing on said exhaust lock (50, 90), said pushing action being, or initiated by said retainer (10, 70) during the pivoting movement of said retainer (10, 70) under the action of said first elastic return means (16, 18, 72) immediately after the application of said impulse to said balance (20), or initiated directly by said balance (20). Exhaust mechanism (100) according to claim 3, characterized in that said exhaust lock (50, 90) comprises an exhaust rest pallet (51, 91) arranged to cooperate with one of the teeth (31). ) that includes said escape wheel (30) for effecting the locking of said escape wheel (30). Exhaust mechanism (100) according to claim 3 or 4, characterized in that said exhaust lock (50, 90) is a first latch (50) which is remote from said beam (20) at any point of its trajectory, and which comprises a latch arm (51) arranged to cooperate with a pusher (17) that comprises said retainer (10, 70) for unlocking said escape wheel (30). Exhaust mechanism (100) according to one of claims 1 to 5, characterized in that said retainer (10, 70) is held armed in said stop position by said trigger release (40). Exhaust mechanism (100) according to claim 3 or 4, characterized in that said exhaust lock (50, 90) is a second latch (90) which comprises an arm arranged substantially radially with respect to the axis pivoting said balance (20) and which carries, in the vicinity of said pivot axis, a locking pin (94) for holding a flexible locking blade (92) arranged to cooperate with a latch pallet (23) that comprises said rocker (20) for controlling the unlocking of said escape wheel (30). Exhaust mechanism (100) according to claim 7, characterized in that said second latch (90) comprises a direct lock arm (95) which has a thrust surface (96) arranged to cooperate with a pusher (17) that comprises said retainer (10, 70) for placing said flexible lock blade (92) in the path of said latch pallet (23) of said rocker (20). Exhaust mechanism (100) according to one of claims 1 to 8, characterized in that said first elastic return means (16, 18, 72) comprise at least a first flexible blade (18) integrated with said retainer (10, 70) and arranged in abutment abutment on a fixed support (19) that includes said exhaust mechanism (100). Exhaust mechanism (100) according to one of claims 1 to 8, characterized in that said first elastic return means (16, 18, 72) comprise at least one bistable blade (72) integrated with said retainer (10, 70 ) and arranged in tangential abutment abutment on a tangential bearing surface (75) of a bearing block (74) that comprises said exhaust mechanism (100), and preloading frontally in a bistable state in abutment on a frontal bearing surface (76) of said bearing block (74) with which a distal end (77) of said bistable blade (72) cooperates. Exhaust mechanism (100) according to one of claims 1 to 10, characterized in that said trigger trigger (40) is constituted by a stop arm (78) of said retainer (10, 70) and carries a pin detent (42) for maintaining said expansion spring (60, 71). Exhaust mechanism (100) according to one of claims 1 to 11, characterized in that said retainer (10, 70) comprises a pulse arm (12) arranged to give an impulse to a said pin (21) that carries said balance (20). Exhaust mechanism (100) according to claims 11 and 12, characterized in that said stop arm (78) comprises two horns, one formed by said pulse arm (12), and the other carrying said trigger pin (42), and which together define a receiving space of said pin (21). Exhaust mechanism (100) according to one of claims 1 to 13, characterized in that said expansion spring (60, 71) is constituted by a first flexible blade (71) integrated with said retainer (10, 70). Exhaust mechanism (100) according to one of claims 1 to 13, characterized in that said rocker (20) comprises a release paddle (22) arranged for, in a first pivoting direction of said rocker (20) push a distal end (61, 79) that comprises said expansion spring (60, 71) without rotating said trigger trigger (40), and in a second pivoting direction causing said distal end (61, 79) resting on a pin trigger (42) that includes said trigger trigger (40) and rotate the latter and release said stop (10, 70). Exhaust mechanism (100) according to one of claims 1 to 15, characterized in that said retainer (10, 70) is suspended cantilever with respect to a fixed support that comprises said exhaust mechanism ( 100) by at least one flexible blade (18), and is movable in a plane parallel to that of the serge of said balance (20), in a substantially pivotal movement about a virtual pivot. Exhaust mechanism (100) according to one of claims 1 to 16, characterized in that said exhaust mechanism (100) comprises a monolithic assembly comprising a plate, said retainer (10, 70), and a flexible blade ( 18) suspension cantilever said retainer (10, 70) to said platen. Exhaust mechanism (100) according to claims 3 and 17, characterized in that said monolithic assembly further comprises said exhaust latch (50, 90) which is suspended cantilevered to said plate by a leaf-spring constituting one of said second elastic return means (53, 93). Exhaust mechanism (100) according to claim 18, characterized in that said monolithic assembly further comprises said trigger trigger (40) and said trigger spring (60, 71). Exhaust mechanism (100) according to one of claims 1 to 16, characterized in that said exhaust mechanism (100) comprises a monolithic assembly comprising a plate, said retainer (10, 70), and a flexible connection defining a virtual pivot of said retainer (10, 70) relative to said platen. Exhaust mechanism (100) according to claims 3 and 20, characterized in that said monolithic assembly further comprises said exhaust lock (50, 90) which is suspended cantilevered to said plate by a leaf-spring constituting one of said second elastic return means (53, 93). Exhaust mechanism (100) according to claim 21, characterized in that said monolithic assembly further comprises said triggering trigger (40) and said expansion spring (60, 71). Exhaust mechanism (100) according to claim 10 and one of claims 1 to 16, characterized in that said exhaust mechanism (100) comprises a monolithic assembly comprising a plate, said retainer (10, 70), said bistable blade (72) and said support block (74) which is movably mounted on at least one flexible blade between an approach position in which said bistable blade (72) is free, and a prestressing position in which said bistable blade (72) is prestressing in buckling, said monolithic assembly comprising fixing means for maintaining said support block (74) in said preload position. Exhaust mechanism (100) according to claims 7 and 20, characterized in that said monolithic assembly further comprises said second latch (90) and said flexible latch blade (92). Exhaust mechanism (100) according to claim 24, characterized in that said monolithic assembly further comprises said triggering trigger (40) and said expansion spring (60, 71). Exhaust mechanism (100) according to claim 10 and one of claims 23 or 24, characterized in that said monolithic assembly further comprises said bistable blade (72) and said support block (74) which is mounted movably on at least one flexible blade between an approach position in which said bistable blade (72) is free, and a prestressing position in which said bistable blade (72) is prestressing in buckling, said monolithic assembly comprising fixing means for the maintaining said support block (74) in said prestressing position. A watch movement (200) comprising an escape mechanism (100) according to one of claims 1 to 26, and comprising an oscillator mechanism comprising said balance (20), and at least one energy storage mechanism arranged to apply a driving torque to at least one said escape wheel (30). Watch (300) having at least one movement (200) according to claim 27.

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