CH711608A2

CH711608A2 - Escapement mechanism with a constant force clutch.

Info

Publication number: CH711608A2
Application number: CH01441/15A
Authority: CH
Inventors: Remontet Valentin; Junod Benoît
Original assignee: Montres Breguet Sa
Priority date: 2015-10-06
Filing date: 2015-10-06
Publication date: 2017-04-13

Abstract

The invention relates to a trigger escapement mechanism (100) for a timepiece, comprising a mechanism for directly or indirectly locking an escapement wheel (30) during the stroke of a balance (20) during its stroke (40) which is actuated by means of an expansion spring (60) by means of the rocker arm (20). Said locking mechanism comprises a pivotable retainer (10) which is subjected to the return torque of the resilient return means (16) and which is either not in contact with the trigger trigger (40) and is pivotable to a position under armature (30), when it is unlocked, against the resilient return means (16), or immobilized in an abutment position in which it is held by the release trigger (40) ,

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates to a trigger escapement mechanism for a timepiece comprising a mechanism for directly or indirectly locking an escapement wheel during the stroke of a pendulum of a Oscillator mechanism during its free alternation without pulse, controlled by unlocking by a release trigger maneuvered, by means of an expansion spring, by said balance.

[0002] The invention also relates to a timepiece movement comprising such an escapement mechanism.

[0003] The invention relates to a watch comprising such a movement.

BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates to the field of high-precision escapement mechanisms for watchmaking, and in particular trigger escapements.

BACKGROUND OF THE INVENTION [0005] Trigger escapement has been used extensively for marine chronometers because of its high precision. However, its use for watch movements intended to be carried in different positions and no longer suspended by gimbals or a gyroscopic system, is difficult to develop despite a theoretically better yield than other traditional solutions such as anchor escapement Swiss. The phenomenon of galloping, which corresponds to the triggering of an exhaust function when the balance has an amplitude greater than a certain limit amplitude value, generally close to 3507360 °, is a disadvantage which necessitates the development of anti- Gallop often complex and inefficient, altering the efficiency of the exhaust.

[0006] A traditional trigger escapement is characterized by the presence of a lost blow, that is to say with each oscillation alternating without a pulse. Often this single impulse is a direct impulse from the escapement wheel to the balance. The force transmitted by the exhaust wheel to the balance wheel is directly dependent on the torque transmitted to this wheel, which generally varies as a function of the barrel wrapping and of the gear train modulations.

The amplitude is thus variable, and generally decreases during disarming of the barrel, and the chronometric properties are therefore affected.

[0008] Robin exhaust mechanisms use a locking rocker of the exhaust wheel but have the drawback of direct transmission of energy from the escapement wheel to the balance wheel, which does not solve The problem of variable amplitude.

The application PCT / EP 2013/056 577 in the name of NIVAROX-FAR SA describes an exhaust mechanism for a movement or a timepiece comprising at least one balance and at least one exhaust wheel, wherein the transmission d Pulse between said at least one rocker arm and said at least one escape wheel is provided by a one-piece flexible mechanism including at least one cooperating feeler with said at least one exhaust wheel or respectively said at least one rocker and Said single-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 escapement wheel. SUMMARY OF THE INVENTION [0010] The invention relates to a new exhaust system of the expansion type,

[0011] The transmission of energy, according to the invention, is indirect between the escapement wheel and the balance.

To this end, the invention relates to a trigger escapement mechanism for a timepiece according to claim 1.

[0013] The invention also relates to a timepiece movement comprising such an escapement mechanism.

[0014] The invention relates to a watch comprising such a movement.

BRIEF DESCRIPTION OF THE DRAWINGS Other characteristics and advantages of the invention will appear on reading the following detailed description, with reference to the accompanying drawings, in which: FIG. 1 schematically shows, in perspective, a constant displacement exhaust mechanism according to the invention, in a first embodiment; Figs. 2 to 7 show, in plan view, successive steps of operation of this first embodiment, comprising a stopper recalled by an external spring: FIG. 2: first release step; Fig. 3: second pulse step; Fig. 4: third step of unlocking the exhaust wheel; Fig. 5: fourth resetting step; Fig. 6: fifth blocking step. Fig. 7: sixth step corresponding to the lost shot, FIG. 8 shows, in plan view, A second embodiment of the invention, comprising a flexible retainer, made in one piece with a flexible blade; Figs. 9 to 13 represent, in plan view, a third embodiment, comprising a flexible bis-table retainer, comprising a bistable flexible blade prestressed in buckling; FIG. 10 illustrates the buckling of this bistable flexible stopper which has been flexed from a first position in broken line to a second position in solid line; FIG. 11 illustrates the disengagement step; FIG. 12 illustrates the end of the pulse; FIG. 13 illustrates the lost blow; Figs. 14 to 16 represent, in plan view, a fourth embodiment constituting an anti-gallop system comprising the bistable flexible stop of the third mode and comprising a direct locking mechanism with an elastic blade, Arranged to co-operate with both the teeth of the exhaust wheel and with a locking pallet, of which the balance is then equipped; FIG. 15 illustrates the reset triggering step; FIG. 16 illustrates the state of the reset stop before the hit; Figs. 17 to 22 show, in plan view, a fifth embodiment, constituting an anti-gallop system, comprising the bistable flexible stopper of the third mode, and including another direct locking mechanism with an elastic blade, arranged to cooperate with the Times with the teeth of the escapement wheel, and with a locking pallet of which the balance is then equipped; FIG. 17 illustrates the disengagement step; FIG. 18 illustrates the pulse step; FIG. 19 illustrates the unblocking step; FIG. 20 illustrates the resetting step; FIG. 21 illustrates the blocking and kick-off step in FIG. 22 illustrates the rebound in the case of an amplitude greater than a limiting amplitude, for example at 350 ° during the first additional arc; FIG. 23 is a block diagram showing a watch including a movement which itself comprises such an escapement mechanism according to the invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The invention relates to a constant-force release mechanism 100 for a timepiece 300. This mechanism 100 uses a particular retainer 10, the rotation of which is associated with First elastic return means 16, 18, 72, in particular but not limited to a wearing spring, or a flexible blade, or the like.

[0017] Its operation reproduces the general principles specific to expansion exhausts, which are not detailed here.

Four non-limiting embodiments are illustrated by the figures and will be described in detail below.

[0019] Ce mécanisme d’échappement 100 à détente comporte ainsi un mécanisme de blocage direct ou indirect d’une roue d’échappement 30, pendant la course d’un balancier 20 d’un mécanisme oscillateur pendant sa libre alternance sans impulsion, dans un sens de pivotement, l’impulsion ne se faisant que dans l’autre sens de pivotement du balancier.

[0020] L’invention est illustrée avec un balancier 20 qui est un balancier au sens classique du terme, faisant partie d’un oscillateur de type balancier-spiral. L’invention est toutefois applicable à d’autres types d’oscillateur, et le balancier 20 peut alors prendre d’autres formes, comme un pendule, ou autre.

The exhaust wheel 30 is conventionally subjected to a torque coming from an energy storage mechanism and is designed to provide, at each oscillation of the oscillator mechanism, a single impulse to the balance 20.

This locking mechanism is controlled by unlocking by a release trigger 40, which is actuated by means of the balance 20 by means of an expansion spring 60, 71.

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

In the course of the oscillation stroke of the rocker arm 20, this retainer 10 is either: - or without contact with the trigger trigger 40, and can then pivot to an armed position under the action of the escapement wheel 30, when the latter is unlocked, against the elastic return means 16, 18, 72; Or immobilized in an abutment position in which the retainer 10 is kept armed, in particular in a particular embodiment by the release trigger 40, waiting to be released by the trigger trigger 40, only once per oscillation Of the oscillator, to then transmit to the balance 20 a constant torque corresponding to the armoring of the elastic return means 16, 18, 72.

Actuation of the trigger trigger 40 is effected by means of the expansion spring 60, 71 by a pin 21 and / or a triggering pallet 22 carried by the balance 20.

The first elastic return means 16, 18, 72 are either arranged at the level of the retainer 10 or are carried by the exhaust mechanism 100.

The first elastic return means 16, 18, 72, in particular of the spring of the retainer 10, are wound directly by the exhaust wheel 30 after each exhaust function. In a particular embodiment, the retainer 10 is held in the cocked position by the trigger trigger 40.

[0028] In certain non-limiting embodiments, in particular as shown in FIGS. 1 to 8, triggering of this triggering trigger 40 is carried out by means of a triggering paddle 22 integral with the balance 20. This triggering pallet 22 is designed so that, in a first pivoting direction of the balance 20, a distal end 61, 79, which comprises the expansion spring 60, 71, without pivoting the trigger trigger 40, and in a second pivoting direction drive this distal end 61, 79, bearing against an expansion pin 42 which the trigger And to pivot the latter and release the retainer 10.

The triggering thus takes place as a release at the beginning of the exhaust function and makes it possible to release the retainer 10 which restores the energy previously accumulated in the first elastic return means 16, 18, 72, To the balance 20 via a pin 21 of the balance 20 during the pulse phase.

The locking mechanism comprises an escapement latch 50, 90, which is arranged to effect the locking of the escapement wheel 30 under the action of second elastic return means 53, 93, which comprises, or else This exhaust latch 50, 90, or the exhaust mechanism 100 itself.

In short, according to the invention, the locking mechanism comprises a retainer, 10 or 70 according to the embodiment, and an escapement latch, 50 or 90 according to the embodiment.

The locking mechanism is also arranged to effect the release of the exhaust wheel 30 under a thrust action on this exhaust latch 50, 90. This thrust action is either initiated by the retainer 10 during the pivoting movement of the retainer 10 under the action of the first elastic return means 16, 18, 72, just after applying the impulse to said balance 20, or directly initiated by the balance 20 as in A fourth embodiment illustrated in FIGS. 14 to 16.

More specifically, the exhaust latch 50, 90 comprises an escape rest pallet 51, 91 which is designed to cooperate with one of the teeth 31 which the escapement wheel 30 comprises, The blocking of this exhaust wheel 30.

[0034] In the first three embodiments illustrated in FIGS. 1 to 13, the escapement latch is a first latch 50 which is distant from the balance 20 at all points along its trajectory and which comprises a latch arm 51 arranged to cooperate with a pusher 17 which the retainer 10 comprises for The unlocking of the escapement wheel 30.

[0035] In the fourth embodiment of FIGS. 14 to 16, and in the fifth mode of FIGS. 17 to 22, the escapement latch is a second latch 90, which has an arm arranged substantially radially with respect to the pivot axis of the balance 20 and which, in the vicinity of this pivot axis, carries a pin Of latch 94 for holding a flexible latch blade 92 which is arranged to cooperate with a latch pallet 23 which comprises the balance 20 for controlling the release of the escapement wheel 30.

At the end of the exhaust function, the retainer 10 raises an escapement latch 50, 90, which blocks the exhaust wheel 30, and thus releases the escapement wheel 30. The escapement wheel 30 can thereby Resetting the retainer 10 and its first elastic return means 16, 18, 72 for the next exhaust function, a tooth 31 of the exhaust wheel 30 then pushing the retainer 10 into its armed position.

Lafig. 1 illustrates the various components of the exhaust mechanism 100 of the invention, in a first embodiment whose operation is illustrated in FIGS. 2 to 7. In this first mode, the retainer 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 rests on A bearing surface 14 of the retainer 10. The latter comprises a lug 11, which, in FIGS. 1 and 2, rests on the trigger rest pad 41 which the trigger trigger 40 comprises.

The retainer 10 also comprises an impulse arm 12, arranged to cooperate with the pin 21 of the balance 20.

The retainer 10 also comprises a pallet 13 which is designed to cooperate directly with one of the teeth 31 of the exhaust wheel 30 in certain angular positions of the retainer 10.

The retainer 10 finally comprises a pusher 17, arranged to cooperate with an arm 52 of the first lock 50, in order to release the latter.

[0041] In FIG. 1, the system is initially in the cocked position, and the balance 10 is in a position ready to trigger the escape function.

[0042] During the disengagement step, illustrated in FIG. 2, the triggering pallet 22 of the balance 20 raises the release trigger 40, which releases the retainer 10. In order to do this, the triggering pallet 22 of the balance wheel 20 which rotates counterclockwise pushes the distal end 61 of the detent spring 60, and thus presses on the trigger pin 42 which the trigger trigger 40 carries, thereby causing the latter to pivot in the clockwise direction. The spout 11 can then leave the detent rest paddle 41 and the retainer 10 can be pivoted in the clockwise direction by its wearing spring 16.

During the pulse step, illustrated in FIG. 3, the retainer 10, by virtue of its armed spring 16 previously armed, gives the impulse to the balance 20 by the action of the pulse arm 12 of the retainer 10 on the pin 21.

During the unblocking step, illustrated in FIG. 4, the pusher 17 of the retainer 10 pushes the arm 52 of the first latch 50 and lifts the latter at the end of its stroke in the direction of the arrow A. This first latch 50 now releases the escapement wheel Which can rotate, and can be used to reset the winding spring 16 of the retainer 10.

During the resetting step, illustrated in FIG. 5, the exhaust wheel 30 being free, can reset, under the action of the torque transmitted by the finishing train, this winding spring 16 by the action of a tooth 31 on the pallet 13 of the retainer 10.

[0046] During the locking step, illustrated in FIG. 6, the retainer 10 is again retained in the cocked position by the trigger trigger 40 with its lug 11 bearing against the detent rest pad 41 and the exhaust wheel 30 comes into rest position on the first Lock 50, a tooth 31 arriving to cooperate in abutment on the exhaust resting pallet 51. During this time, the balance 20 describes its additional arc in a counterclockwise direction.

[0061] During the step of the shot lost, illustrated in FIG. 7, when the balance is returned, in the opposite direction of rotation, here clockwise, the triggering pallet 22 activates the distal end of the flexible portion 61 of the trigger trigger 40 (release) without bearing on the pin 42, and Does not influence the position of the other elements of the exhaust, the pin 21 not interacting with the pulse arm 12 of the retainer 10 in this position.

[0048] FIG. 8 illustrates a second embodiment, in which the first elastic return means comprise at least a first flexible blade 18 integrated in the retainer 10 and arranged in abutment bearing on a fixed support 19 which comprises the exhaust mechanism 100, For example at a platen. The retainer 10 is thus made with a flexible part, in this case a flexible blade 18, which fulfills the function of the wearing spring 16 of the first mode. This makes it possible to have one component less, knowing that this type of component is easily realizable by manufacturing processes such as "LIGA" (nickel alloy) or "DRE" (silicon), or the like.

More particularly, the retainer 10 is suspended in cantilever fashion with respect to a fixed support which the exhaust mechanism 100 comprises by at least one flexible blade 18 and is movable in a plane parallel to that of the In a substantially pivoting movement about a virtual pivot, dimensioned so that the retainer 10 cooperates with the trigger 40, the peg 21 of the balance 20, the tooth 31 of the escapement wheel 30, and The arm 52 of the first lock 50.

[0050] In a third embodiment of the invention, illustrated in FIGS. 9 to 13, the geometry of the retainer is produced with a flexible bistable part.

The first elastic return means then comprise at least one bistable blade 72 integrated in a bistable stop 70, which fulfills the same functions as the stop 10 of the first and second modes. Advantageously, this bistable blade 72 is arranged in tangential abutment bearing on a tangential bearing surface 75 of a support block 74 which comprises the exhaust mechanism 100. This bistable blade 72 is pretensioned frontally in a state Bistable on a front bearing surface 76 of the bearing block 74, with which cooperates a distal end 77 of the bistable blade 72.

This solution uses the bistability of the flexible part 72 of the retainer 10 in order to keep the latter in the rest position. This makes it possible to dispense with an independent trip trigger. In the non-limiting variant illustrated, the retainer 10 comprises a retaining arm 78 which constitutes the trigger trigger and which comprises, on the one hand, the pulse arm 12 forming a horn and on the other hand a Which carries the expansion pin 42, which holds a first flexible blade 71, which is integral, like the bistable blade 72, with a core of the bistable stopper numbered 70 for this third mode. This retaining arm 78 thus comprises two horns, one formed by the pulse arm 12 and the other carrying the relief pin 42 and which together define a space for receiving the pin 21.

It is the exhaust wheel 30, after the exhaust function, which resets the system until the point of instability has passed. The flexible part 72 is held in the rest position by stops (tangential support or pin or geometry of a bridge or of the plate) in a state of deformation close to the instability position, so that the release of the Balance system 20 allows the system to pass instability during the exhaust function. The energy accumulated in the flexible part 72 is therefore transmitted to the balance 20 during this jump and this accumulated energy is always the same (and this is therefore always a constant force).

In order to obtain a bistable state of the bistable stop 70, the bistable stop 70 pivots about its axis of rotation (via a standard pivot connection or by flexible pivoting) while the distal end 77 of the flexible portion 72 is Pre-armed in compression (buckling) and then fixed in this position, for example by a movement of the support block 74, as can be seen in FIG. 10, where it is caused to pass, according to the arrow B, from a free position in broken line to a prestressed position of the second flexible strip 72 in solid line. This support block 74 is then immobilized by clipping, screwing, or the like, depending on the type of embodiment chosen.

[0055] FIGS. 11 and 12 illustrate respectively the disengagement 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 strip 71 uses the same principle as the trigger since it is blocked in the direction of the release and it is free to be deformed in the direction of the shot lost.

During disengagement, the peg 21 of the balance 20 sets the retainer 70 in rotation by means of the first flexible blade 71, which allows the flexible part of the retainer to pass the point of instability. Once the point of instability has passed, the retainer 70 starts to rotate very rapidly to reach its stable position, this being the pulse, characterized by the jump of the bistable system. During this jump, the elastic potential energy accumulated in the second flexible plate 72 is transmitted to the rocker 20 in the form of kinetic energy.

At the end of the pulse, that is to say at the end of the jump, the stop 70 raises the first bolt as in the first embodiment (step 3), which allows the wheel To reset the bistable system by rotating the retainer 70.

[0058] FIG. 13 shows the step of the blow, where the peg 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 change the position of the exhaust components.

[0059] FIGS. 14 to 16 illustrate a fourth embodiment of the invention, in which the exhaust mechanism 100 constitutes an anti-gallop system. This solution uses the lost blow to allow the exhaust wheel to re-arm the system with constant force. Indeed, in this case, if the lost stroke has not taken place, the pulse can not be triggered, even in the case of amplitude greater than a limiting amplitude, in particular in the example illustrated at 360 °, since The system is not reset. Such a system thus avoids the phenomenon of galloping. The peg 21 of the balance 20 then comes to rest on the outer reverse of the retaining horn bearing the pulse arm 12.

This construction comprises an escapement latch 90 which interacts directly with a latch pallet 23 secured to the balance 20, instead of interacting with the retainer when the latter ends its pulse.

This escapement latch is a second latch 90, which comprises an arm arranged substantially radially with respect to the pivot axis of the balance 20 and which carries, in the vicinity of this pivot axis, a locking pin Latch 94 for holding a flexible latch blade 92 which is arranged to cooperate with the latch pallet 23 to control the release of the exhaust wheel 30.

In this case, the escape function takes place in two stages since the release and pulse steps take place as described previously during the first half-cycle, while the unlocking, resetting and blocking steps Take place during the second alternation corresponding to the lost shot.

During the second alternation and prior to the passage of the mark, the latch pallet 23 first impinges on the flexible release latch 92 of the second latch 90, which is locked by the latch pin 94, which raises This second latch 90 in the direction of the arrow D, and releases the escapement wheel 30, as can be seen in FIG. 15. The exhaust 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 shown in FIGS. 14 to 16.

The peg 21 of the balance 20 then reaches the level of the reference mark and collides in the non-locking direction with the first flexible blade 71 of the retainer 70: this is the loss of FIG. If the re-arresting of the retainer takes place too late with respect to the reference mark, the pin 21 of the balance 20 collides with the horn of the retainer 70, as for a release, and it is the balance 20 which rearm 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, in which the retainer must raise the latch, which also represented a consumption (pulse less effective).

This fourth mode is compatible with the three other embodiments proposed. In the case of higher amplitudes (greater than a limiting amplitude, in particular 3307350 ° for conventional pendulum oscillators), the balance peg 21 comes to rebound against the reverse side of the horn since the latter has not returned to the cocked position .

FIGS. 17 to 22 illustrate a fifth embodiment of the invention, in which the exhaust mechanism 100 constitutes an anti-gallop system, and is an improvement of the above fourth mode, the general operating principles of which are preserved.

As for the fourth mode, during the second alternation and before the passage of the mark, the locking pallet 23 first impinges on the flexible release latch 92 of the second latch 90, which raises the latter according to Arrow D, and releases the escapement wheel 30, as can be seen in FIG. 18. The exhaust 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 can be seen in FIGS. 14 to 16.

[0069] La cheville 21 du balancier 20 arrive alors au niveau de repère et entre en collision dans le sens non bloquant avec la première lame flexible 71 de l’arrêtoir 70: c’est le coup perdu de la fig. 21 Si le réarmage de l’arrêtoir s’effectue trop tard par rapport au repère, la cheville 21 du balancier 20 entre en collision avec la corne de l’arrêtoir 70, comme pour un dégagement, et c’est le balancier 20 qui réarme l’arrêtoir, ce qu’il vaut mieux éviter.

[0070] The first step concerns the release, as can be seen in FIG. The peg 21 of the balance 20 pushes the first flexible blade 71 of the retainer 70 in its locked direction, causing the instability of the second bistable flexible blade 72 associated with the retainer 70 to pass, or else for the first It is the triggering pallet 22 which raises the release trigger 40, which releases the retainer 10.

[0071] The second step, illustrated in FIG. 18, concerns the impulse. The retainer 70, by virtue of its armed resilient return means, gives, by its pulse arm 12, the pulse to the balance 20 via the pin 21. At the end of the pulse 1 The retainer 70 also raises by a pusher 17 which it comprises a pushing surface 96 which comprises a direct locking arm 95 which is included in the second lock 90 but not sufficiently to release the escapement wheel 30. Stop 70 is not reset but the raising of the second latch 90 has made it possible to place the end of its flexible latch blade 92 in the path of the latch pallet 23 for the next step.

[0072] The third step, illustrated in FIG. 19 relates to the release of the exhaust wheel 30. During the second alternation of the balance 20 (which normally corresponds to the lost stroke), the latch pallet 23 lifts the end of the flexible latch plate 92 of the second latch 90 which, in the trajectory of the locking pallet 23, thanks to the catch 70 which lifted it in the preceding step at the end of its stroke. The second latch 90 can then release the escapement wheel 30 which can reset the elastic return means of the retainer 70.

[0073] The fourth step, illustrated in FIG. 20, relates to re-armament. Since the exhaust wheel 30 is free, the direct rest pallet 91 having released the tooth 31 which was in contact therewith under the action of the torque transmitted by the finishing train, this exhaust wheel 30 can re- By pushing a tooth 31 onto a pallet 13 of the retainer 70. This resetting makes it possible to put the retainer 70 back into its initial position just before the pin 21 of the pendulum 20 arrives. The retainer 70 is completely reset before the pin 21 of the balance 20 arrives, in order to avoid a collision between the latter and the fork of the retaining arm 78, which would correspond to a disengagement, whereas this alternation must be a Lost shot.

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

This function certainly represents an additional consumption on the balance but makes it possible to prevent the stop 70 from completely lifting the second lock 90, which also represents a consumption (less efficient pulse).

This mechanism is compatible with the first three embodiments proposed. In the case of amplitudes greater than the limiting amplitude, for example greater than 3307350 °, the balance peg 21 comes to rebound against the reverse of the retaining horn constituted by the pulse arm 12 during the first additional arc (Before the lost blow) since the retainer 70 is not yet returned to the armed position, as can be seen in FIG. 22. In addition, during the second additional arc, after the lost stroke, the balance 20 can travel up to the limiting amplitude without, however, disengaging the second lock 90, since the latter is no longer in the trajectory of The locking pallet 23.

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

More particularly, some nonlimiting embodiments are listed here: the exhaust mechanism 100 comprises a monolithic assembly comprising a plate, said retainer 10, and a flexible blade 18 for suspending in cantilever of said retainer 10 to Said platen; And said monolithic assembly further comprises said exhaust latch 50, 90 which is suspended in cantilever fashion to said plate by a leaf spring constituting one of said second elastic return means 53, 93; This monolithic assembly further comprises said trigger relief 40 and said expansion spring 60, 71. The exhaust 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 platen; This monolithic assembly also includes said exhaust latch 50, 90 which is suspended in cantilever fashion to said plate by a leaf spring constituting one of said second elastic return means 53, 93; This monolithic assembly further comprises said trigger relief 40 and said expansion spring 60, 71. The exhaust 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 pre-stressed position in which said bistable blade 72 is preloaded in buckling, Said monolithic assembly comprising fixing means for holding said bearing block 74 in said prestressed position; This monolithic assembly further comprises said second latch 90 and said flexible latch plate 92; This monolithic assembly further includes said trigger relief 40 and said expansion spring 60, 71; This monolithic assembly further comprises said bistable blade 72 and said bearing 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 pre-stressed position in which said The said bistable blade 72 is prestressed in buckling, the said monolithic assembly comprising fixing means for the retention of the said bearing block 74 in the said prestressing position. This monolithic assembly further comprises said second latch 90 and said flexible latch plate 92; This monolithic assembly further includes said trigger relief 40 and said expansion spring 60, 71; This monolithic assembly further comprises said bistable blade 72 and said bearing 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 pre-stressed position in which said Said monolithic assembly comprising fastening means for holding said bearing block 74 in said prestressed position. This monolithic assembly further comprises said second latch 90 and said flexible latch plate 92; This monolithic assembly further includes said trigger relief 40 and said expansion spring 60, 71; This monolithic assembly further comprises said bistable blade 72 and said bearing 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 pre-stressed position in which said The said bistable blade 72 is prestressed in buckling, the said monolithic assembly comprising fixing means for the retention of the said bearing block 74 in the said prestressing position. This monolithic assembly further includes said trigger relief 40 and said expansion spring 60, 71; This monolithic assembly further comprises said bistable blade 72 and said bearing 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 pre-stressed position in which said The said bistable blade 72 is prestressed in buckling, the said monolithic assembly comprising fixing means for the retention of the said bearing block 74 in the said prestressing position. This monolithic assembly further includes said trigger relief 40 and said expansion spring 60, 71; This monolithic assembly further comprises said bistable blade 72 and said bearing 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 pre-stressed position in which said The said bistable blade 72 is prestressed in buckling, the said monolithic assembly comprising fixing means for the retention of the said bearing block 74 in the said prestressing position.

The invention also relates to a timepiece movement 200 comprising such an escapement mechanism 100, and comprising an oscillator mechanism comprising this balance 20, and at least one energy storage mechanism arranged to apply a driving torque to the Less such an escape wheel 30.

[0080] The invention also relates to a watch 300 comprising at least one such movement 200.

[0081] The invention brings numerous advantages.

In fact, the solutions proposed above all make it possible to have a constant force transmitted to the balance, and thus to guarantee a constant amplitude during disarming, and without the influence of the modulations of the train which disrupt the chronometry in A traditional system.

The use of a direct weaving system on the retainer makes it possible to make the movement of the latter independent of the inertia of the exhaust wheel and of the rest of the finishing train. The retainer can thus come into contact with the elbow of the balance very rapidly after release (very short recovery time), which promotes the impulse and therefore the efficiency of the exhaust.

This system is therefore particularly advantageous for fast exhaust functions (high-frequency oscillator) and for systems with an equivalent inertia of the exhaust wheel (for example vortices).

This solution also has the advantage, as for a conventional trigger escapement, of giving a single impulse per oscillation (against two for a Swiss anchor escapement), which makes it possible to increase the energy transmitted by the function of an oscillation, Exhaust and thus decrease the ratio of multiplication between the barrel and the exhaust (the lost hit represents a significant consumption which limits this advantage).

Claims

The anti-gallop system shown is compatible with all the variant embodiments and makes it possible to avoid counting errors in case of excessive amplitude, which is one of the main defects of a conventional trigger escapement. The mechanism illustrated does not include any dart, it is therefore feasible over a number of levels limited to two in addition to the level proper to the beam serge, which is favorable for the thickness of the movement. However, this mechanism can be equipped with a dart for additional safety. The invention can be used in particular, and not limitatively, for: an exhaust demonstrator; - marine chronometer; - high frequency motion; - movement with very large power reserve; - whirlwind. claims

1. A timepiece expansion device (100) for a timepiece (300), comprising a mechanism for directly or indirectly locking an exhaust wheel (30) during the stroke of a rocker arm (20) An oscillator mechanism during its non-pulse free alternation, controlled by a trigger trigger (40) actuated by means of an expansion spring (60, 71) by said rocker arm (20), characterized in that In that said locking mechanism comprises a pivoting retainer (10, 70) subjected to the return torque of first resilient return means (16, 18, 72), which retainer (10, 70) (20) or without contact with the trigger trigger (40) and is pivotable to an armed position under the action of said exhaust wheel (30), when the latter is released,(16, 18, 72), or immobilized in a stop position in which said retainer (10, 70) is kept armed, awaiting its release by said release trigger (40) , Once only by oscillation of said oscillator, for then transmitting to said balance (20) a constant torque corresponding to the armoring of said elastic return means (16, 18, 72).

2. The exhaust mechanism (100) as claimed in claim 1, characterized in that said exhaust wheel (30) is subjected to a torque coming from an energy storage mechanism and arranged to provide, during each oscillation Of said oscillator mechanism, the energy for a single pulse to said balance (20), in that said trigger trigger (40) is actuated by a pin (21) via said expansion spring (60, 71) And / or a trigger pallet (22) carried by said balance (20), in that said first elastic return means (16, 18, 72) are arranged at said retainer (10, 70) Exhaust mechanism (100).

3. The exhaust mechanism according to claim 2, wherein said locking mechanism comprises an escapement latch designed to effect the locking of said exhaust wheel, (50, 90) or said exhaust mechanism (100), or to effect the unlocking of said exhaust wheel (30) under a second elastic return means (53, 93) (50, 90), said thrust action being initiated by said retainer (10, 70) during the pivoting movement of said retainer (10, 70) under the action of said first (16, 18, 72) just after the application of said pulse to said balance (20), or directly initiated by said balance (20).

4. The exhaust mechanism (100) as claimed in claim 3, wherein said exhaust latch (50, 90) comprises an escape rest pallet (51, 91) arranged to cooperate with one of the teeth (31) in said exhaust wheel (30) to effect blocking of said exhaust wheel (30).

5. The exhaust mechanism according to claim 3, wherein said exhaust latch is a first latch that is distant from said balance at any point in its length, (51) arranged to cooperate with a pusher (17) included in said retainer (10, 70) for releasing said exhaust wheel (30).

6. The exhaust mechanism according to claim 1, wherein said stop is held in said stop position by said release trigger.

7. The exhaust mechanism according to claim 3, wherein said exhaust latch is a second latch which comprises an arm arranged substantially radially with respect to the latch. (20) and which, in the vicinity of said pivot axis, carries a latch pin (94) for holding a flexible latch blade (92) arranged to cooperate with a latch pallet ) Which said balance (20) comprises for controlling the unlocking of said exhaust wheel (30).

8. The exhaust mechanism according to claim 7, wherein said second latch comprises a direct latch arm which has a pushing surface arranged to cooperate with a pusher, ) Of said stop (10, 70) for placing said flexible latch blade (92) in the path of said latch pallet (23) of said balance (20).

9. The exhaust mechanism as claimed in claim 1, wherein said first elastic return means comprise at least one first flexible blade incorporated in said retainer, 10, 70) and arranged abuttingly on a fixed support (19) which said exhaust mechanism (100) comprises.

10. The exhaust mechanism according to claim 1, wherein said first resilient return means comprise at least one bistable blade integrated in said retainer, , 70) and arranged in tangential abutment on a tangential bearing surface (75) of a bearing block (74) which comprises said exhaust mechanism (100), and prestressed frontally in a bistable state in abutment (76) of said bearing block (74) with which a distal end (77) of said bistable blade (72) cooperates.

11. The exhaust mechanism according to claim 1, wherein said trigger trigger is constituted by a retaining arm of said retainer and a door, An expansion pin (42) for holding said expansion spring (60, 71).

12. The exhaust mechanism as claimed in claim 1, wherein said stop comprises a pulse arm arranged to give a pulse to a said pin. ) Carried by said balance (20).

13. The exhaust mechanism as claimed in claim 11, wherein said retaining arm comprises two horns, one formed by said pulse arm and the other, Carrying said detent pin (42), and which together define a space for receiving said pin (21).

14. The exhaust mechanism according to claim 1, wherein said expansion spring is constituted by a first flexible blade integrated into said retainer, .

15. The exhaust mechanism as claimed in claim 1, wherein said rocker arm comprises a triggering pad arranged in a first pivoting direction of said rocker, Biasing a distal end (61,79) of said detent spring (60,71) without pivoting said trigger trigger (40), and in a second pivotal direction causing said distal end (61, 79) to bear against A trigger pin (42) included in said trigger trigger (40) and pivotable and releasing said trigger (10, 70).

16. The exhaust mechanism according to claim 1, wherein said stop is suspended in a cantilevered manner relative to a fixed support provided by 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 pivoting movement about a virtual pivot.

17. The exhaust mechanism according to claim 1, wherein said exhaust mechanism comprises a monolithic assembly comprising a plate, said retainer and a blade, Flexible hanger (18) for cantilevering said retainer (10, 70) to said platen.

18. The exhaust mechanism (100) as claimed in claim 3, wherein said monolithic assembly further comprises said exhaust latch (50, 90) which is suspended in cantilever fashion to said plate by a blade Said spring constituting one of said second elastic return means (53, 93).

19. The exhaust mechanism according to claim 18, wherein said monolithic assembly further comprises said trigger relief and said expansion spring.

20. The exhaust mechanism according to claim 1, wherein said exhaust mechanism comprises a monolithic assembly comprising a plate, said retainer and a linkage, Flexible means defining a virtual pivot of said stopper (10, 70) relative to said plate.

21. The exhaust mechanism (100) as claimed in claim 3, wherein said monolithic assembly further comprises said exhaust latch (50, 90) which is suspended in cantilevered manner to said plate by a blade Said spring constituting one of said second elastic return means (53, 93).

22. The exhaust mechanism (100) as claimed in claim 21, wherein said monolithic assembly further comprises said trigger relief (40) and said expansion spring (60, 71).

23. The exhaust mechanism as claimed in claim 10, wherein the exhaust mechanism comprises a monolithic assembly comprising a plate, the said retainer, , Said bistable blade (72) and said bearing block (74) being movably mounted on at least one flexible blade between an approach position in which said bistable blade (72) is free and a pre-stressing position in which Said bistable blade (72) is prestressed in buckling, said monolithic assembly comprising fixing means for holding said bearing block (74) in said prestressed position.

24. An exhaust mechanism according to claim 7, wherein said monolithic assembly further comprises said second latch and said flexible latch blade.

25. An exhaust mechanism according to claim 24, wherein said monolithic assembly further comprises said trigger relief and said expansion spring.

26. The exhaust mechanism (100) as claimed in claim 10, and one of claims 23 or 24, characterized in that said monolithic assembly further comprises said bistable blade (72) and said bearing block (74) which is mounted Movable 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 buckling preloaded, said monolithic assembly comprising fastening means For holding said bearing block (74) in said prestressing position.

27. A timepiece movement comprising an exhaust mechanism according to claim 1, comprising an oscillator mechanism including said balance and at least one energy storage mechanism For applying a driving torque to at least one said exhaust wheel (30).

28. A watch (300) comprising at least one movement (200) according to claim 27.