EP3623875B1 - Exhaust mechanism with bistable leaf spring - Google Patents

Exhaust mechanism with bistable leaf spring Download PDF

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Publication number
EP3623875B1
EP3623875B1 EP18193657.6A EP18193657A EP3623875B1 EP 3623875 B1 EP3623875 B1 EP 3623875B1 EP 18193657 A EP18193657 A EP 18193657A EP 3623875 B1 EP3623875 B1 EP 3623875B1
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EP
European Patent Office
Prior art keywords
winding
locking
lever
rocker
pin
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EP18193657.6A
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German (de)
French (fr)
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EP3623875A1 (en
Inventor
Matthieu Kummer
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Sowind SA
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Sowind SA
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Priority to EP18193657.6A priority Critical patent/EP3623875B1/en
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel

Definitions

  • the present invention relates to the field of mechanical watchmaking. It relates, more particularly, to an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a inflection point.
  • an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring is well known. working in buckling around a point of inflection. Mention may be made here by way of example of the various patents of the Applicant WO 2009118310 A1 , CH 710925 A1 or WO 2018015146 A1 .
  • Such an escapement mechanism makes it possible in particular to maintain the oscillations of the balance constantly over the entire duration of the power reserve independently of the source of energy.
  • these escapement mechanisms result in a drawback linked to the alternating locking of the winding wheels by hooking a peripheral hook of the winding wheels onto the winding pegs of the winding rocker at the end of the winding phases.
  • armament Indeed, such picking tends to provide rebound effects between winding wheels and winding rocker with corresponding energy losses and untimely unlocking.
  • such a mode of locking the winding wheels is more sensitive, and therefore less reliable, in the event of accelerations undergone by the escapement mechanism during impacts.
  • the object of the present invention is to remedy these drawbacks and to make the locking of the winding wheels more reliable in a bistable leaf spring escapement mechanism working in buckling.
  • this escapement mechanism is arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a point of inflection, said leaf spring being capable, via a winding rocker, of accumulating the energy from the driving source during a winding phase, of then remaining in a metastable state close to instability during a locking phase, then to restore the energy accumulated to said oscillating regulator during a pulse phase by means of a detent rocker.
  • the winding rocker is arranged to cooperate with at least one winding wheel so as to wind the leaf spring during the winding phases, the or each winding wheel comprising on a periphery a plurality of winding cams each defining a cam surface.
  • the winding rocker further comprises at least one winding peg forming a cam follower such that each winding peg slides on the cam surface of one of the winding cams during the winding phases of the spring -blade.
  • the escapement mechanism of the invention finally comprises a locking rocker arranged to lock said winding rocker in a locking position at the end of each winding phase.
  • the locking rocker comprises two locking pallets arranged to cooperate with locking members complementary, in particular lugs, on said winding rocker and in that the at least one said winding wheel and said winding rocker are arranged respectively such that the or each winding wheel is stopped by wedging between a winding peg and a cam surface of a said winding cam and between a said locking pallets and a said complementary locking member at the end of each winding phase and during the locking phases.
  • the mechanism according to the invention makes it possible to eliminate the risk of accidental unlocking of a winding wheel and of the winding rocker during all the phases of locking, unlocking and relaxation, and to position in an identical manner and repeatable the winding rocker at each locking by eliminating all the rebounds.
  • this arrangement makes it possible to increase the energy transmitted to the balance because the blade no longer needs to unlock the winding rocker.
  • This mechanism also makes it possible to have distinct unlocking and relaxation phases.
  • the winding mobiles of the inventive mechanism are stopped by jamming a winding cam on a pin of the winding rocker, which is at the end of the winding phase and in the locking phase therefore “sandwiched” between a winding mobile and the locking rocker.
  • the winding cams of the winding mobiles of the mechanism of the invention are therefore configured to have a sufficient length to push the winding rocker into abutment against the locking rocker thus determining the end of the winding phase, the driving torque of the driving source sufficient to operate the wedging of a winding mobile on a winding peg once the winding rocker is in abutment.
  • this arrangement makes it possible to have a positioning of the winding rocker which is identical and very repeatable from one locking to another because the moving parts which form the abutment are rockers whose parts forming the wedging are always the same from lock to lock.
  • each pulse in turn becomes identical, providing a perfectly balanced operation of the mechanism and optimization of the energy consumed and transmitted to the balance wheel, and therefore of the efficiency of the escapement.
  • the escapement mechanism of the invention thus avoids all the rebounds of the winding wheels, of the winding rocker and of the locking rocker by mutual wedging of the latter and guaranteeing an identical positioning of the winding rocker. , backlash-free and perfectly repeatable on each locking.
  • This arrangement makes it possible to position the blade in its state closest to instability and also prevents any untimely unlocking of the escapement, this in a repetitive and identical manner at each locking even during external shocks.
  • the locking rocker intervenes only as a safety device in the event of failure of the hooking between the winding mobile and the winding rocker.
  • the mechanism of the invention secures the locking of the winding rocker and the winding mobiles and solves the dynamic problems encountered during rebounds of the winding wheels on the winding pegs as proposed in the prior art. .
  • the energy necessary for unlocking the winding rocker and the winding mobiles is also reduced by the inventive mechanism, which restores a greater part of the available energy transmitted to the regulator during the pulses.
  • the pendulum by its kinetic energy, triggers the unlocking phases of the driving force due to the kinematic connection of the detent rocker to the bistable leaf spring and the locking rocker.
  • each winding wheel comprises at least three identical winding cams regularly distributed over the periphery of said winding wheels.
  • the mechanism of the invention comprises two winding wheels arranged mobile in rotation around an individual pivot axis in a symmetrical position on either side of a straight line passing through the axis of rotation of the regulator and the point of inflection of the bistable leaf spring and are indexed in rotation with respect to each other so that the winding rocker is in contact on a said winding pin only 'with a single winding wheel alternating on one of the regulator and the other.
  • the locking rocker of the winding rocker is rotatable on a pivot axis and kinematically connected to the trigger rocker.
  • the locking rocker comprises a bar provided at a first end with a fork for connection to said trigger rocker and two locking arms extending symmetrically from each other from said bar and provided each at its free end of a locking pallet arranged to cooperate with a complementary locking member on said winding rocker.
  • the locking pallets are arcs of a circle concentric with the pivot point of the locking rocker. No pulling is thus caused on the locking rocker.
  • the complementary locking member on said winding rocker comprises one or two locking lugs of shape and orientation suitable for hooking a said locking pallet of the locking rocker.
  • This locking lug is advantageously arranged contiguous to the spouts supporting the winding pegs, between said spouts and the pallets of the locking rocker.
  • the fork of the locking rocker may comprise two horns defining a space between the horns with which an unlocking pin integral with the trigger rocker cooperates.
  • the locking rocker is arranged so that a locking pallet hooks a said locking lug of the winding rocker arranged on a first beak of the winding rocker following the displacement winding rocker pushed by a winding wheel thus causing jamming of a winding wheel on a winding peg arranged on the second beak of the winding rocker.
  • the invention also relates, according to a second aspect, to a timepiece comprising an escapement mechanism as defined above.
  • an escapement mechanism 1 in a preferred embodiment.
  • This mechanism in a conventional way, makes it possible to maintain the oscillations of an oscillating regulator, composed for example of a balance wheel 4 associated with a hairspring, by delivering to it energy received from a driving source, such as a barrel by example, not visible on the figure 1 , via a bistable leaf spring 2 working in buckling around a central point of inflection I, and whose ends are secured to a frame 9 for fixing to a watch movement frame such that it occupies a stable position corresponding to a first mode buckling.
  • a driving source such as a barrel by example
  • the leaf spring 2 cooperates with a winding rocker 3, a trigger rocker 5 and a locking rocker 8 in order to accumulate the energy from the driving source during winding phases, to remain in an armed state during locking phases and to restore the energy accumulated to said oscillating regulator 4 during pulse phases.
  • the trigger rocker 5 is kinematically linked to the leaf spring 2 substantially at its central point of inflection and thus pivots around this point of inflection. It comprises, at one end, a fork 51 and a stinger 53 intended to cooperate with a double plate 41, 42 of the rocker arm 4 and a plate pin 43 driven onto the large plate 41 of the double plate. It also comprises an unlocking pin 52 which cooperates with the fork 83 of a locking rocker 8 presented below.
  • the winding rocker 3 comprises a central portion 33 and two symmetrical winding arms 31, 32 whose ends are kinematically linked to the leaf spring 2, in particular in the example represented by winding tenons 31a, 32a inserted with sufficient clearance in the eyelets 2a, 2b of the bistable leaf spring 2.
  • the winding rocker 3 is rotatable around a coincident axis passing through the point of inflection I.
  • the winding rocker 3, the rocker trigger 5 and leaf spring 2 therefore all pivot around the same axis perpendicular to the plane of the figures 1 to 7 .
  • the winding 3 and trigger 4 rockers are mounted free to rotate with respect to their common axis of rotation.
  • the central portion 33 of the winding rocker 3 comprises at a rear end or tail two beaks 34a, 34b or projections symmetrical to each other with respect to a median axis of said central portion 33, each beak 34a, 34b carrying a winding pin 35a, 35b integral with said beak 34a, 34b and intended to cooperate with a winding wheel 6, 7.
  • the winding wheels 6, 7 each comprise a winding pinion 62, 72 meshing with a mobile end of the going train (not shown) so that the winding wheels 6, 7 pivot in a synchronized manner.
  • the winding wheels 6, 7 each comprise on their periphery a plurality of winding cams 61, 71, in this case three winding cams, angularly distributed in a regular manner with respect to the center of the winding wheels, these winding cams 61, 71 being identical to one another on the two wheels 6, 7 and each defining a cam surface 611, 711 whose shape and length are adapted to cooperate with the winding pins 35a, 35b of the rocker winding 3 in order to transmit the driving energy to the winding rocker 3 on the one hand and to block the rotation of the winding wheels 6, 7 during the locking phases on the other hand, according to the operation described above -After.
  • each winding pin 35a, 35b is made of a material with a low coefficient of friction such as ruby, corundum or even silicon and has a contact surface 351 with the cam track of the winding cams 61, 71 adapted to slide with reduced friction on said cam tracks.
  • the mechanism 1 further comprises a locking rocker 8 of the winding rocker 3, represented individually in figure 9 .
  • This locking rocker 8 is rotatably mounted on a pivot axis 86 on the frame of the watch movement and kinematically connected to the trigger rocker 5.
  • it comprises a bar 84 extending from a central body 85 , said bar 84 being provided at its free end with a connecting fork 83 to said trigger lever 5 by means of an unlocking pin 52 cooperating with the two horns 83a, 83b of the fork 83.
  • the locking lever 8 also comprises two locking arms extending symmetrically l each other from the central body 85 and each provided at its free end with a locking pallet 81, 82 in the form of a circular hook concentric with the axis of rotation of the locking rocker arranged to cooperate with a lug locking 36a, 36b of the winding rocker 3. This is so as not to cause pulling on the locking rocker and thus not inducing any geometric and dynamic recoil on the winding rocker and the winding wheels.
  • the locking lugs 36a, 36b and the pallets 81, 82 of the locking rocker are of shape and orientation suitable for hooking together when the winding rocker reaches one of its two locking positions, respectively dexter ( fig. 1 ) or sinister ( fig. 7 ), at the end of the winding phase of the bistable leaf spring 2 corresponding to the extreme positions occupied by the winding rocker 3 and the trigger rocker 4 as will be described later and so as not to cause pulling on the lock toggle.
  • the winding wheels 6, 7 and said winding rocker 3 are arranged respectively such that each winding mobile 6, 7 is stopped by jamming of a winding pin 35a, 35b on a cam surface of a winding cam 61, 71 of one of the winding wheels during the locking phases of the escapement mechanism, the locking rocker 8 further being arranged so that the locking pallets 81 , 82 hook a said locking pin 36a and 36b of the winding rocker 3 following the jamming of a winding wheel 6, 7 on a said winding peg 35a, 35b.
  • This combined locking mode of the winding wheels 6, 7 and the winding rocker 3 at the end of the winding of the bistable leaf spring 2 and during the locking phases is described below with reference to the figures 1 to 7 .
  • the configuration of the figure 1 corresponds to a locking phase subsequent to a dextral winding phase, in which the leaf spring 2 is armed in a state close to instability.
  • the stopping of the winding wheel 6 at the end of the winding takes place without rebound because the geometry of the winding cam surface 61 causes wedging between the left hand winding pin 35a of the winding rocker 3 and the winding cam surface 61 of the winding wheel 6 of a either side between the dexter locking lug 36b of the winding rocker and the pallet 82 of the locking rocker 8 on the other hand.
  • Pendulum 4 completes its ascending arc clockwise.
  • the leaf spring 2 transmits the energy accumulated during the previous winding to the balance and changes from a state close to instability to a stable state.
  • the locking rocker 8 is still in contact with the winding rocker 3 and the winding wheels 6, 7, and therefore the going train, are still stopped.
  • the trigger rocker 5 pivots around the point of inflection and drives the locking rocker 8 in rotation around its axis 86, which releases the locking pallet 82 from the lug 36 and thus releases the winding rocker 3 this without causing geometric recoil of the winding rocker.
  • the plate pin 43 has left the fork 52 of the trigger rocker 5 and the leaf spring 2 has transmitted all its energy to the rocker arm 4, and the winding rocker 3 is free.
  • the winding wheel 6 is also released from its support on the pin 35 of the winding rocker but has not yet started to rotate because of its inertia which is non-zero.
  • Pendulum 4 begins its ascending anti-clockwise arc.
  • the locking rocker 8 is already in the sinister locking position for the next winding. This is followed by the rotation of the winding wheels under the driving torque of the going train transmitted to the pinions 62, 72, as shown in figure 4 .
  • the pendulum 4 continues its anti-clockwise ascending arc during this interval.
  • the left arming phase is shown in figures 5 to 7 .
  • the initial phase is represented in the figure 5
  • the final winding and sinister locking phase being shown at figure 7 .
  • the initial phase of the left winding begins when a winding cam 71 of the winding wheel 7 comes into contact with the dexter winding pin 35b of the winding rocker 3.
  • the two winding wheels armature 6, 7 are then in rotational motion in a clockwise direction.
  • the engagement of the winding cam 71 against the pin 35b causes a pivoting of the winding rocker 3 counterclockwise, which induces a force of the arms 31, 32 on the leaf spring 2 on either side of its point of inflection, and the elastic loading thereof.
  • the balance wheel 4 is still continuing its ascending arc in the counterclockwise direction.
  • the device according to the invention thus makes it possible to eliminate the effects of contact rebound between the winding rocker 3 and the winding wheels such as encountered with the configurations of the prior art.
  • unlocking is also simplified because there is no longer any picking between the winding rocker and the winding wheel.
  • the jamming between the winding rocker and the locking rocker is easily released by the unlocking effect of the winding rocker during the relaxation phase, following the rotation of the trigger rocker 5, which suffices to pivot the locking rocker 8 and therefore release the winding rocker 3 from its counter-bearing force on the winding cams 61, 71.
  • This support being substantially punctual and the mutual friction forces being reduced because the wheels winding 6, 7 only have to overcome their own inertia to resume their rotation once the locking rocker is released, without the winding rocker 3 opposing an additional resistance force.
  • the locking rocker 8 then pivots on its axis on a portion corresponding to the spur of the trigger rocker 5, during this movement, in normal training (by the plate pin 43 of the balance) or in the event of an external shock, the trigger rocker 5 has not yet reached its point of instability and the locking rocker 8 has not yet released the locking lugs 36a, 36b of the winding rocker 3. Continuing the rotation of the plate pin, it still pushes the trigger rocker 5 to its point of instability. At this moment, the leaf spring 2 tends to return to its first buckling mode and it is at this moment that the impulse of the detent rocker 5 begins. At this moment, the winding cam 6, 7 is still locked by the locking rocker 8.
  • the rocker arm 4 is the source of energy which must overcome the frictional forces which are between the locking rocker 8 and the lugs 36a, 36b of the winding rocker 3 as well that the pressing force of the trigger rocker 5 against the stokers caused by the buckling of the leaf spring 2.
  • the pallets 81, 82 of the locking rocker 8 are concentric at its pivot point, this in order not to cause any pulling and to take as little energy as possible from the rocker arm 4 when unlocking the the driving force.

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  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
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Description

Domaine techniqueTechnical area

La présente invention se rapporte au domaine de l'horlogerie mécanique. Elle concerne, plus particulièrement un mécanisme d'échappement agencé pour transmettre des impulsions d'énergie mécanique d'une source motrice à un régulateur oscillant de pièce d'horlogerie par l'intermédiaire d'un ressort-lame travaillant en flambage autour d'un point d'inflexion.The present invention relates to the field of mechanical watchmaking. It relates, more particularly, to an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a inflection point.

Etat de la techniqueState of the art

Dans le domaine de l'horlogerie, il est bien connu un mécanisme d'échappement agencé pour transmettre des impulsions d'énergie mécanique d'une source motrice à un régulateur oscillant de pièce d'horlogerie par l'intermédiaire d'un ressort-lame travaillant en flambage autour d'un point d'inflexion. On peut citer ici à titre d'exemple les différents brevets de la Demanderesse WO 2009118310 A1 , CH 710925 A1 ou encore WO 2018015146 A1 .In the field of watchmaking, an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring is well known. working in buckling around a point of inflection. Mention may be made here by way of example of the various patents of the Applicant WO 2009118310 A1 , CH 710925 A1 or WO 2018015146 A1 .

Un tel mécanisme d'échappement permet notamment d'entretenir les oscillations du balancier de manière constante sur toute la durée de la réserve de marche indépendamment de la source d'énergie. Cependant, il découle de ces mécanismes d'échappement un inconvénient lié au verrouillage alterné des roues d'armage par crochetage d'un crochet périphérique des roues d'armage sur les chevilles d'armage de la bascule d'armage en fin de phases d'armage. En effet, un tel crochetage tend à procurer des effets de rebonds entre roues d'armage et bascule d'armage avec des pertes d'énergie correspondantes et des déverrouillages intempestifs. De plus, un tel mode de blocage des roues d'armage est plus sensible, et donc moins fiable, en cas d'accélérations subies par le mécanisme d'échappement lors de chocs. Ce dernier défaut a été partiellement compensé par l'utilisation d'une bascule de verrouillage qui empêche un déverrouillage intempestif des roues d'armage. Cependant un défaut corollaire découle du positionnement différent de la bascule d'armage à chaque verrouillage. De ce fait, l'énergie nécessaire au déverrouillage n'est pas identique dans chaque position verrouillée de la bascule.Such an escapement mechanism makes it possible in particular to maintain the oscillations of the balance constantly over the entire duration of the power reserve independently of the source of energy. However, these escapement mechanisms result in a drawback linked to the alternating locking of the winding wheels by hooking a peripheral hook of the winding wheels onto the winding pegs of the winding rocker at the end of the winding phases. armament. Indeed, such picking tends to provide rebound effects between winding wheels and winding rocker with corresponding energy losses and untimely unlocking. In addition, such a mode of locking the winding wheels is more sensitive, and therefore less reliable, in the event of accelerations undergone by the escapement mechanism during impacts. This last defect has been partially compensated by the use of a locking rocker which prevents untimely unlocking of the winding wheels. However, a corollary defect arises from the different positioning of the winding rocker at each locking. Therefore, the energy required for unlocking is not identical in each locked position of the rocker.

Un autre inconvénient, provient du tirage sur la bascule d'armage qui est provoqué par les ergots de verrouillage des roues d'armage. Ce tirage provoque un couple que la lame via ses oeillets sur les goupilles de la bascule d'armage doit vaincre lors de la phase de détente pour déverrouiller la bascule d'armage. Ce qui signifie que le balancier ne reçoit pas toute l'énergie délivrée par la lame lors de l'impulsion.Another drawback comes from the pulling on the winding rocker which is caused by the locking lugs of the winding wheels. This pulling causes a torque that the blade via its eyelets on the winding rocker pins must overcome during the relaxation phase to unlock the winding rocker. This means that the balance wheel does not receive all the energy delivered by the blade during the impulse.

La présente invention a pour but de remédier à ces inconvénients et fiabiliser le verrouillage des roues d'armage dans un mécanisme d'échappement à ressort-lame bistable travaillant en flambage.The object of the present invention is to remedy these drawbacks and to make the locking of the winding wheels more reliable in a bistable leaf spring escapement mechanism working in buckling.

Divulgation de l'inventionDisclosure of Invention

Ces buts sont atteints grâce à un mécanisme d'échappement tel que défini à la revendication 1.These objects are achieved by an escapement mechanism as defined in claim 1.

Ainsi ce mécanisme d'échappement est agencé pour transmettre des impulsions d'énergie mécanique d'une source motrice à un régulateur oscillant de pièce d'horlogerie par l'intermédiaire d'un ressort-lame travaillant en flambage autour d'un point d'inflexion, ledit ressort-lame étant susceptible, par l'intermédiaire d'une bascule d'armage, d'accumuler l'énergie issue de la source motrice lors d'une phase d'armage, de demeurer ensuite dans un état métastable proche de l'instabilité lors d'une phase de verrouillage, puis de restituer l'énergie accumulée audit régulateur oscillant lors d'une phase d'impulsion par l'intermédiaire d'une bascule de détente. La bascule d'armage est agencée pour coopérer avec au moins une roue d'armage de manière à armer le ressort-lame lors des phases d'armage, la ou chaque roue d'armage comportant sur une périphérie une pluralité de cames d'armage définissant chacune une surface de came. La bascule d'armage comporte de plus au moins une cheville d'armage formant suiveur de came de telle sorte que chaque cheville d'armage glisse sur la surface de came d'une des cames d'armage lors des phases d'armage du ressort-lame. Le mécanisme d'échappement de l'invention comporte enfin une bascule de verrouillage agencée pour verrouiller ladite bascule d'armage dans une position de verrouillage à la fin de chaque phase d'armage.Thus this escapement mechanism is arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a point of inflection, said leaf spring being capable, via a winding rocker, of accumulating the energy from the driving source during a winding phase, of then remaining in a metastable state close to instability during a locking phase, then to restore the energy accumulated to said oscillating regulator during a pulse phase by means of a detent rocker. The winding rocker is arranged to cooperate with at least one winding wheel so as to wind the leaf spring during the winding phases, the or each winding wheel comprising on a periphery a plurality of winding cams each defining a cam surface. The winding rocker further comprises at least one winding peg forming a cam follower such that each winding peg slides on the cam surface of one of the winding cams during the winding phases of the spring -blade. The escapement mechanism of the invention finally comprises a locking rocker arranged to lock said winding rocker in a locking position at the end of each winding phase.

Conformément à l'invention, la bascule de verrouillage comporte deux palettes de verrouillage agencées pour coopérer avec des organe de verrouillage complémentaire, notamment des ergots, sur ladite bascule d'armage et en ce que le au moins une dite roue d'armage et ladite bascule d'armage sont agencées respectivement de telle sorte que la ou chaque roue d'armage soit stoppée par coincement entre une cheville d'armage et une surface de came d'une dite came d'armage et entre une dite palettes de verrouillage et un dit organe de verrouillage complémentaire à la fin de chaque phase d'armage et durant les phases de verrouillage.According to the invention, the locking rocker comprises two locking pallets arranged to cooperate with locking members complementary, in particular lugs, on said winding rocker and in that the at least one said winding wheel and said winding rocker are arranged respectively such that the or each winding wheel is stopped by wedging between a winding peg and a cam surface of a said winding cam and between a said locking pallets and a said complementary locking member at the end of each winding phase and during the locking phases.

Ainsi, le mécanisme selon l'invention permet d'éliminer le risque de déverrouillage accidentel d'une roue d'armage et de la bascule d'armage lors de toutes les phases de verrouillage de déverrouillage et de détente, et de positionner de manière identique et répétable la bascule d'armage à chaque verrouillage en supprimant tous les rebonds. De plus, cet agencement permet d'augmenter l'énergie transmise au balancier car la lame n'a plus besoin de déverrouiller la bascule d'armage. Ce mécanisme permet également d'avoir des phases de déverrouillage et de détente bien distinctes.Thus, the mechanism according to the invention makes it possible to eliminate the risk of accidental unlocking of a winding wheel and of the winding rocker during all the phases of locking, unlocking and relaxation, and to position in an identical manner and repeatable the winding rocker at each locking by eliminating all the rebounds. In addition, this arrangement makes it possible to increase the energy transmitted to the balance because the blade no longer needs to unlock the winding rocker. This mechanism also makes it possible to have distinct unlocking and relaxation phases.

Ainsi, contrairement aux mécanismes de l'art antérieur les mobiles d'armage du mécanisme inventif sont arrêtés par coincement d'une came d'armage sur une cheville de la bascule d'armage, qui se trouve en fin de phase d'armage et en phase de verrouillage donc prise « en sandwich » entre un mobile d'armage et la bascule de verrouillage. Les cames d'armage des mobiles d'armage du mécanisme de l'invention sont donc configurées pour présenter une longueur suffisante pour repousser la bascule d'armage en butée contre la bascule de verrouillage déterminant ainsi la fin de la phase d'armage, le couple moteur de la source motrice suffisant à opérer le coincement d'un mobile d'armage sur une cheville d'armage une fois la bascule d'armage en butée.Thus, unlike the mechanisms of the prior art, the winding mobiles of the inventive mechanism are stopped by jamming a winding cam on a pin of the winding rocker, which is at the end of the winding phase and in the locking phase therefore “sandwiched” between a winding mobile and the locking rocker. The winding cams of the winding mobiles of the mechanism of the invention are therefore configured to have a sufficient length to push the winding rocker into abutment against the locking rocker thus determining the end of the winding phase, the driving torque of the driving source sufficient to operate the wedging of a winding mobile on a winding peg once the winding rocker is in abutment.

De plus, cette agencement permet d'avoir un positionnement de la bascule d'armage identique et très répétable d'un verrouillage à l'autre car les pièces en mouvement qui forment la butée sont des bascules dont les parties formant le coincement sont toujours les mêmes d'un verrouillage à l'autre. La lame étant armée à chaque verrouillage de manière identique, chaque impulsion devient à son tour identique, procurant un fonctionnement parfaitement équilibré du mécanisme et une optimisation de l'énergie consommée et transmise au balancier, donc du rendement de l'échappement.In addition, this arrangement makes it possible to have a positioning of the winding rocker which is identical and very repeatable from one locking to another because the moving parts which form the abutment are rockers whose parts forming the wedging are always the same from lock to lock. As the blade is cocked identically at each lock, each pulse in turn becomes identical, providing a perfectly balanced operation of the mechanism and optimization of the energy consumed and transmitted to the balance wheel, and therefore of the efficiency of the escapement.

Le mécanisme d'échappement de l'invention évite ainsi tous les rebonds des roues d'armage, de la bascule d'armage et de la bascule de verrouillage par un coincement mutuel de ces dernières et garantissant un positionnement de la bascule d'armage identique, sans jeu et parfaitement répétable à chaque verrouillage. Cet agencement permet de positionner la lame dans son état au plus proche de l'instabilité et empêche également tout déverrouillage intempestif de l'échappement, ceci de façon répétitive et identique à chaque verrouillage même lors de chocs extérieurs.The escapement mechanism of the invention thus avoids all the rebounds of the winding wheels, of the winding rocker and of the locking rocker by mutual wedging of the latter and guaranteeing an identical positioning of the winding rocker. , backlash-free and perfectly repeatable on each locking. This arrangement makes it possible to position the blade in its state closest to instability and also prevents any untimely unlocking of the escapement, this in a repetitive and identical manner at each locking even during external shocks.

Par opposition dans les mécanismes antérieurs, la bascule de verrouillage n'intervient que comme sécurité en cas de défaillance du crochetage entre mobile d'armage et bascule d'armage.In contrast to the prior mechanisms, the locking rocker intervenes only as a safety device in the event of failure of the hooking between the winding mobile and the winding rocker.

Le mécanisme de l'invention sécurise le verrouillage de la bascule d'armage et des mobiles d'armage et résout les problèmes de dynamique rencontrés lors de rebonds des roues d'armage sur les chevilles d'armage tel que proposé dans l'art antérieur. De plus, l'énergie nécessaire au déverrouillage de la bascule d'armage et des mobiles d'armage est également diminuée par le mécanisme inventif, ce qui restitue une plus grande partie de l'énergie disponible transmise au régulateur lors des impulsions. Le balancier par son énergie cinétique, déclenche les phases de déverrouillage de la force motrice en raison de la liaison cinématique de la bascule de détente au ressort lame bistable et la bascule de verrouillage.The mechanism of the invention secures the locking of the winding rocker and the winding mobiles and solves the dynamic problems encountered during rebounds of the winding wheels on the winding pegs as proposed in the prior art. . In addition, the energy necessary for unlocking the winding rocker and the winding mobiles is also reduced by the inventive mechanism, which restores a greater part of the available energy transmitted to the regulator during the pulses. The pendulum by its kinetic energy, triggers the unlocking phases of the driving force due to the kinematic connection of the detent rocker to the bistable leaf spring and the locking rocker.

D'autres caractéristiques particulières du mécanisme de l'invention font également l'objet des revendications dépendantes.Other particular characteristics of the mechanism of the invention are also the subject of the dependent claims.

Selon un mode de réalisation, chaque roue d'armage comporte au moins trois cames d'armage identiques régulièrement réparties sur la périphérie desdites roues d'armage.According to one embodiment, each winding wheel comprises at least three identical winding cams regularly distributed over the periphery of said winding wheels.

Dans un mode de réalisation particulier, le mécanisme de l'invention comporte deux roues d'armage agencées mobiles en rotation autour d'un axe de pivotement individuel dans une position symétrique de part et d'autre d'une droite passant par l'axe de rotation du régulateur et le point d'inflexion du ressort-lame bistable et sont indexées en rotation l'une par rapport à l'autre de manière à ce que la bascule d'armage ne soit en contact sur une dite cheville d'armage qu'avec une seule roue d'armage sur une alternance du régulateur et l'autre.In a particular embodiment, the mechanism of the invention comprises two winding wheels arranged mobile in rotation around an individual pivot axis in a symmetrical position on either side of a straight line passing through the axis of rotation of the regulator and the point of inflection of the bistable leaf spring and are indexed in rotation with respect to each other so that the winding rocker is in contact on a said winding pin only 'with a single winding wheel alternating on one of the regulator and the other.

Selon une forme de réalisation, la bascule de verrouillage de la bascule d'armage est mobile en rotation sur un axe pivot et reliée cinématiquement à la bascule de détente.According to one embodiment, the locking rocker of the winding rocker is rotatable on a pivot axis and kinematically connected to the trigger rocker.

Dans une forme de réalisation, la bascule de verrouillage comporte une barrette munie à une première extrémité d'une fourchette de liaison à ladite bascule de détente et deux bras de verrouillage s'étendant symétriquement l'un de l'autre depuis ladite barrette et muni chacun à son extrémité libre d'une palette de verrouillage agencée pour coopérer avec un organe de verrouillage complémentaire sur ladite bascule d'armage.In one embodiment, the locking rocker comprises a bar provided at a first end with a fork for connection to said trigger rocker and two locking arms extending symmetrically from each other from said bar and provided each at its free end of a locking pallet arranged to cooperate with a complementary locking member on said winding rocker.

De façon avantageuse, les palettes de verrouillages sont des arcs de cercle concentrique au point de pivotement de la bascule de verrouillage. Aucun tirage n'est ainsi provoqué sur la bascule de verrouillage.Advantageously, the locking pallets are arcs of a circle concentric with the pivot point of the locking rocker. No pulling is thus caused on the locking rocker.

De préférence, l'organe de verrouillage complémentaire sur ladite bascule d'armage comporte un ou deux ergots de verrouillage de forme et d'orientation adaptée pour crocheter une dite palette de verrouillage de la bascule de verrouillage. Cet ergot de verrouillage est avantageusement disposé de manière contiguë aux becs supportant les chevilles d'armage, entre lesdits becs et les palettes de la bascule de verrouillage.Preferably, the complementary locking member on said winding rocker comprises one or two locking lugs of shape and orientation suitable for hooking a said locking pallet of the locking rocker. This locking lug is advantageously arranged contiguous to the spouts supporting the winding pegs, between said spouts and the pallets of the locking rocker.

Selon cette forme de réalisation la fourchette de la bascule de verrouillage peut comporter deux cornes délimitant un espace entre-cornes avec lequel coopère une cheville de déverrouillage solidaire de la bascule de détente.According to this embodiment, the fork of the locking rocker may comprise two horns defining a space between the horns with which an unlocking pin integral with the trigger rocker cooperates.

Dans une forme de réalisation particulière de l'invention, la bascule de verrouillage est agencée pour qu'une palette de verrouillage crochète un dit ergot de verrouillage de la bascule d'armage disposé sur un premier bec de la bascule d'armage suite au déplacement de bascule d'armage poussé par une roue d'armage provoquant ainsi un coincement d'une roue d'armage sur une cheville d'armage disposé sur le deuxième bec de la bascule d'armage.In a particular embodiment of the invention, the locking rocker is arranged so that a locking pallet hooks a said locking lug of the winding rocker arranged on a first beak of the winding rocker following the displacement winding rocker pushed by a winding wheel thus causing jamming of a winding wheel on a winding peg arranged on the second beak of the winding rocker.

Dans un mode de réalisation de l'invention, le mécanisme d'échappement selon l'invention peut ne comporter qu'un seul mobile d'armage. Dans un mode de réalisation de l'invention, le mobile d'armage peut être agencé mobile en rotation autour d'un axe de pivotement individuel, auquel cas :

  • cet axe de pivotement individuel peut être disposé sur une droite passant par l'axe de rotation du régulateur et le point d'inflexion du ressort-lame bistable,
  • les chevilles d'armage peuvent être agencées sur une paroi interne d'un anneau solidaire de la bascule d'armage dans lequel le mobile d'armage est agencé de manière qu'une dite cheville d'armage ne soit en contact qu'avec une seule came d'armage du mobile d'armage sur une alternance du régulateur.
In one embodiment of the invention, the escapement mechanism according to the invention may comprise only one winding mobile. In one embodiment of the invention, the winding mobile can be arranged mobile in rotation around an individual pivot axis, in which case:
  • this individual pivot axis can be arranged on a straight line passing through the axis of rotation of the regulator and the point of inflection of the bistable leaf spring,
  • the winding pegs can be arranged on an internal wall of a ring integral with the winding rocker in which the winding mobile is arranged so that a said winding peg is only in contact with a single winding cam of the winding mobile on an alternation of the regulator.

L'invention concerne également selon un second aspect une pièce d'horlogerie comportant un mécanisme d'échappement tel que précédemment défini.The invention also relates, according to a second aspect, to a timepiece comprising an escapement mechanism as defined above.

Brève description des dessinsBrief description of the drawings

D'autres caractéristiques de la présente invention apparaîtront plus clairement à la lecture de la description qui va suivre, faite en référence aux dessins annexés, parmi lesquels :

  • La figure 1 représente une vue de dessus du mécanisme d'échappement de l'invention dans un mode préféré de réalisation, dans une première position de verrouillage, dite verrouillage dextre, la lame est armée dans un état proche de l'instabilité ;
  • La figure 2 représente l'instant ou la lame est passée de son état instable à son état stable. Dès cet instant, l'impulsion commence pour transmettre son énergie au balancier, à cet instant le rouage est toujours verrouillé par sécurité, une fois cette sécurité dépassé, le rouage sera libéré.
  • La figure 3 représente la fin de la phase d'impulsion au balancier, la bascule d'armage est libre et le rouage est libéré mais n'a pas encore commencé à tourner car il doit vaincre son inertie.
  • La figure 4 représente une phase intermédiaire dans laquelle les mobiles d'armage du mécanisme de l'invention sont libres en rotation et ont dégagé la bascule d'armage.
  • Les figures 5 à 7 représentent une phase d'armage sénestre du ressort lame bistable du mécanisme de l'invention, jusqu'à une deuxième position de verrouillage, dite sénestre, de la bascule d'armage ;
  • La figure 8 représente un mobile d'armage tel que mis en oeuvre dans le mécanisme des figures 1 à 7 ;
  • La figure 9 représente une bascule de verrouillage telle que mise en oeuvre dans le mécanisme des figures 1 à 7.
Other characteristics of the present invention will appear more clearly on reading the following description, made with reference to the appended drawings, among which:
  • There figure 1 shows a top view of the escapement mechanism of the invention in a preferred embodiment, in a first locking position, called dexter locking, the blade is armed in a state close to instability;
  • There figure 2 represents the moment when the blade went from its unstable state to its stable state. From this moment, the impulse begins to transmit its energy to the balance wheel, at this moment the gear train is still locked for safety, once this safety has been exceeded, the gear train will be released.
  • There picture 3 represents the end of the balance wheel impulse phase, the winding rocker is free and the gear train is released but has not yet started to turn because it must overcome its inertia.
  • There figure 4 represents an intermediate phase in which the winding mobiles of the mechanism of the invention are free to rotate and have released the winding rocker.
  • THE figures 5 to 7 represent a sinister winding phase of the bistable leaf spring of the mechanism of the invention, up to a second locking position, called sinister, of the winding rocker;
  • There figure 8 represents a winding mobile as implemented in the mechanism of the figures 1 to 7 ;
  • There figure 9 represents a latching flip-flop as implemented in the mechanism of the figures 1 to 7 .

Mode(s) de réalisation de l'inventionEmbodiment(s) of the Invention

On a représenté sur les figures 1 à 7 un mécanisme d'échappement 1 selon l'invention dans un mode préféré de réalisation. Ce mécanisme, de façon classique permet d'entretenir les oscillations d'un régulateur oscillant, composé par exemple par un balancier 4 associé à un spiral, en lui délivrant de l'énergie reçue d'une source motrice, telle qu'un barillet par exemple, non visible sur la figure 1, via un ressort-lame bistable 2 travaillant en flambage autour d'un point d'inflexion central I, et dont les extrémités sont solidaires d'un cadre 9 de fixation sur un bâti de mouvement horloger tel qu'il occupe une position stable correspondant à un flambage de premier mode.We represented on the figures 1 to 7 an escapement mechanism 1 according to the invention in a preferred embodiment. This mechanism, in a conventional way, makes it possible to maintain the oscillations of an oscillating regulator, composed for example of a balance wheel 4 associated with a hairspring, by delivering to it energy received from a driving source, such as a barrel by example, not visible on the figure 1 , via a bistable leaf spring 2 working in buckling around a central point of inflection I, and whose ends are secured to a frame 9 for fixing to a watch movement frame such that it occupies a stable position corresponding to a first mode buckling.

Le ressort-lame 2 coopère avec une bascule d'armage 3, une bascule de détente 5 et une bascule de verrouillage 8 afin d'accumuler l'énergie issue de la source motrice lors de phases d'armage, de demeurer dans un état armé lors de phases de verrouillage et de restituer l'énergie accumulée audit régulateur oscillant 4 lors de phases d'impulsion.The leaf spring 2 cooperates with a winding rocker 3, a trigger rocker 5 and a locking rocker 8 in order to accumulate the energy from the driving source during winding phases, to remain in an armed state during locking phases and to restore the energy accumulated to said oscillating regulator 4 during pulse phases.

La bascule de détente 5 est liée cinématiquement au ressort-lame 2 sensiblement au niveau de son point d'inflexion central et pivote ainsi autour de ce point d'inflexion. Elle comporte, à une extrémité, une fourchette 51 et un dard 53 destinée à coopérer avec un double-plateau 41, 42 du balancier 4 et une cheville de plateau 43 chassée sur le grand plateau 41 du double plateau. Elle comporte également une cheville de déverrouillage 52 qui coopère avec la fourchette 83 d'une bascule de verrouillage 8 présentée ci-après.The trigger rocker 5 is kinematically linked to the leaf spring 2 substantially at its central point of inflection and thus pivots around this point of inflection. It comprises, at one end, a fork 51 and a stinger 53 intended to cooperate with a double plate 41, 42 of the rocker arm 4 and a plate pin 43 driven onto the large plate 41 of the double plate. It also comprises an unlocking pin 52 which cooperates with the fork 83 of a locking rocker 8 presented below.

La bascule d'armage 3 comporte une portion centrale 33 et deux bras d'armage symétriques 31, 32 dont les extrémités sont liés cinématiquement au ressort-lame 2, notamment dans l'exemple représenté par des tenons d'armage 31a, 32a insérés avec un jeu suffisant dans des oeillets 2a, 2b du ressort-lame bistable 2. La bascule d'armage 3 est mobile en rotation autour d'un axe confondu passant par le point d'inflexion I. La bascule d'armage 3, la bascule de détente 5 et le ressort-lame 2 pivotent donc tous autour d'un même axe perpendiculaire au plan des figures 1 à 7. Toutefois, les bascules d'armage 3 et de détente 4 sont montées libres en rotation l'une en référence à l'autre de leur axe de rotation commun.The winding rocker 3 comprises a central portion 33 and two symmetrical winding arms 31, 32 whose ends are kinematically linked to the leaf spring 2, in particular in the example represented by winding tenons 31a, 32a inserted with sufficient clearance in the eyelets 2a, 2b of the bistable leaf spring 2. The winding rocker 3 is rotatable around a coincident axis passing through the point of inflection I. The winding rocker 3, the rocker trigger 5 and leaf spring 2 therefore all pivot around the same axis perpendicular to the plane of the figures 1 to 7 . However, the winding 3 and trigger 4 rockers are mounted free to rotate with respect to their common axis of rotation.

La portion centrale 33 de la bascule d'armage 3 comporte au niveau d'une extrémité postérieure ou queue deux becs 34a, 34b ou projections symétriques l'un de l'autre par rapport à un axe médian de ladite portion centrale 33, chaque bec 34a, 34b portant une cheville d'armage 35a, 35b solidaire dudit bec 34a, 34b et destinée à coopérer avec une roue d'armage 6, 7.The central portion 33 of the winding rocker 3 comprises at a rear end or tail two beaks 34a, 34b or projections symmetrical to each other with respect to a median axis of said central portion 33, each beak 34a, 34b carrying a winding pin 35a, 35b integral with said beak 34a, 34b and intended to cooperate with a winding wheel 6, 7.

Les roues d'armage 6, 7 comportent chacune un pignon d'armage 62, 72 engrenant avec un mobile terminal du rouage de finissage (non représenté) de sorte que les roues d'armage 6, 7 pivotent de façon synchronisée.The winding wheels 6, 7 each comprise a winding pinion 62, 72 meshing with a mobile end of the going train (not shown) so that the winding wheels 6, 7 pivot in a synchronized manner.

Les roues d'armage 6, 7 comportent chacune sur leur périphérie une pluralité de cames d'armage 61, 71, en l'espèce trois cames d'armage, réparties angulairement de manière régulière par rapport au centre des roues d' armage , ces cames d'armage 61, 71 étant identiques entre elles sur les deux roues 6, 7 et définissant chacune une surface de came 611, 711 dont la forme et la longueur sont adaptées pour coopérer avec les chevilles d'armage 35a, 35b de la bascule d'armage 3 afin de transmettre l'énergie motrice à la bascule d'armage 3 d'une part et de bloquer la rotation des roues d'armage 6, 7 lors des phases de verrouillage d'autre part, selon le fonctionnement décrit ci-après. Avantageusement, chaque cheville d'armage 35a, 35b est constituée d'un matériau à faible coefficient de frottement tel que du rubis, du corindon ou encore du silicium et présente une surface de contact 351 au chemin de came des cames d'armage 61, 71 adapté pour glisser avec des frottements réduits sur lesdits chemins de came.The winding wheels 6, 7 each comprise on their periphery a plurality of winding cams 61, 71, in this case three winding cams, angularly distributed in a regular manner with respect to the center of the winding wheels, these winding cams 61, 71 being identical to one another on the two wheels 6, 7 and each defining a cam surface 611, 711 whose shape and length are adapted to cooperate with the winding pins 35a, 35b of the rocker winding 3 in order to transmit the driving energy to the winding rocker 3 on the one hand and to block the rotation of the winding wheels 6, 7 during the locking phases on the other hand, according to the operation described above -After. Advantageously, each winding pin 35a, 35b is made of a material with a low coefficient of friction such as ruby, corundum or even silicon and has a contact surface 351 with the cam track of the winding cams 61, 71 adapted to slide with reduced friction on said cam tracks.

Le mécanisme 1 selon l'invention comporte en outre une bascule de verrouillage 8 de la bascule d'armage 3, représentée individuellement à la figure 9. Cette bascule de verrouillage 8 est montée mobile en rotation sur un axe pivot 86 sur le bâti du mouvement horloger et reliée cinématiquement à la bascule de détente 5. Elle comporte dans le mode de réalisation représenté une barrette 84 s'étendant depuis un corps central 85, ladite barrette 84 étant munie à son extrémité libre d'une fourchette de liaison 83 à ladite bascule de détente 5 par l'intermédiaire d'une cheville 52 de déverrouillage coopérant avec les deux cornes 83a, 83b de la fourchette 83. La bascule de verrouillage 8 comporte également deux bras de verrouillage s'étendant symétriquement l'un de l'autre depuis le corps central 85 et muni chacun à son extrémité libre d'une palette de verrouillage 81, 82 en forme de crochet circulaire concentrique à l'axe de rotation de la bascule de verrouillage agencée pour coopérer avec un ergot de verrouillage 36a, 36b de la bascule d'armage 3. Ceci afin de ne pas provoquer de tirage sur la bascule de verrouillage et ne n'induisant ainsi aucun recul géométrique et dynamique sur la bascule d'armage et les roues d'armage.The mechanism 1 according to the invention further comprises a locking rocker 8 of the winding rocker 3, represented individually in figure 9 . This locking rocker 8 is rotatably mounted on a pivot axis 86 on the frame of the watch movement and kinematically connected to the trigger rocker 5. In the embodiment shown, it comprises a bar 84 extending from a central body 85 , said bar 84 being provided at its free end with a connecting fork 83 to said trigger lever 5 by means of an unlocking pin 52 cooperating with the two horns 83a, 83b of the fork 83. The locking lever 8 also comprises two locking arms extending symmetrically l each other from the central body 85 and each provided at its free end with a locking pallet 81, 82 in the form of a circular hook concentric with the axis of rotation of the locking rocker arranged to cooperate with a lug locking 36a, 36b of the winding rocker 3. This is so as not to cause pulling on the locking rocker and thus not inducing any geometric and dynamic recoil on the winding rocker and the winding wheels.

Avantageusement les ergots de verrouillage 36a, 36b et les palettes 81, 82 de la bascule de verrouillage sont de forme et d'orientation adaptées pour crocheter entre eux lorsque la bascule d'armage atteint une de ses deux positions de verrouillage, respectivement dextre (fig. 1) ou sénestre (fig. 7), en fin de phase d'armage du ressort-lame bistable 2 correspondant aux positions extrêmes occupées par les bascule d'armage 3 et bascule de détente 4 comme il sera décrit par la suite et de façon à ne pas provoquer de tirage sur la bascule de verrouillage.Advantageously, the locking lugs 36a, 36b and the pallets 81, 82 of the locking rocker are of shape and orientation suitable for hooking together when the winding rocker reaches one of its two locking positions, respectively dexter ( fig. 1 ) or sinister ( fig. 7 ), at the end of the winding phase of the bistable leaf spring 2 corresponding to the extreme positions occupied by the winding rocker 3 and the trigger rocker 4 as will be described later and so as not to cause pulling on the lock toggle.

Conformément à la présente invention, les roues d'armage 6, 7 et ladite bascule d'armage 3 sont agencés respectivement de telle sorte que chaque mobile d'armage 6, 7 soit stoppé par coincement d'une cheville d'armage 35a, 35b sur une surface de came d'une came d'armage 61, 71 d'une des roues d'armage durant les phases de verrouillage du mécanisme d'échappement, la bascule de verrouillage 8 étant en outre agencée pour que les palettes de verrouillage 81, 82 crochètent un dit ergot de verrouillage 36a et 36b de la bascule d'armage 3 suite au coincement d'une roue d'armage 6, 7 sur une dite cheville d'armage 35a, 35b. Ce mode de verrouillage combiné des roues d'armage 6, 7 et de la bascule d'armage 3 en fin d'armage du ressort-lame bistable 2 et lors des phases de verrouillage est décrit par la suite en référence aux figures 1 à 7.In accordance with the present invention, the winding wheels 6, 7 and said winding rocker 3 are arranged respectively such that each winding mobile 6, 7 is stopped by jamming of a winding pin 35a, 35b on a cam surface of a winding cam 61, 71 of one of the winding wheels during the locking phases of the escapement mechanism, the locking rocker 8 further being arranged so that the locking pallets 81 , 82 hook a said locking pin 36a and 36b of the winding rocker 3 following the jamming of a winding wheel 6, 7 on a said winding peg 35a, 35b. This combined locking mode of the winding wheels 6, 7 and the winding rocker 3 at the end of the winding of the bistable leaf spring 2 and during the locking phases is described below with reference to the figures 1 to 7 .

La configuration de la figure 1 correspond à une phase de verrouillage postérieure à une phase d'armage dextre, dans laquelle le ressort-lame 2 est armé dans un état proche de l'instabilité. L'arrêt de la roue d'armage 6 en fin d'armage s'effectue sans rebond car la géométrie de la surface de came d'armage 61 provoque un coincement entre la cheville d'armage sénestre 35a de la bascule d'armage 3 et la surface de came d'armage 61 de la roue d'armage 6 d'une part et d'autre part entre l'ergot de verrouillage dextre 36b de la bascule d'armage et la palette 82 de la bascule de verrouillage 8 d'autre part. Le balancier 4 fini son arc ascendant dans le sens horaire.The configuration of the figure 1 corresponds to a locking phase subsequent to a dextral winding phase, in which the leaf spring 2 is armed in a state close to instability. The stopping of the winding wheel 6 at the end of the winding takes place without rebound because the geometry of the winding cam surface 61 causes wedging between the left hand winding pin 35a of the winding rocker 3 and the winding cam surface 61 of the winding wheel 6 of a either side between the dexter locking lug 36b of the winding rocker and the pallet 82 of the locking rocker 8 on the other hand. Pendulum 4 completes its ascending arc clockwise.

Après l'arc descendant du balancier 4, celui-ci revient, comme représenté à la figure 2 en sens antihoraire et la cheville de plateau 43 entre dans la fourchette 52 de la bascule de détente 5 pour entamer le déverrouillage. A l'impulsion, le ressort-lame 2 transmet l'énergie accumulée lors de l'armage précédent au balancier et passe d'un état proche de l'instabilité à un état stable. Au début de l'impulsion, la bascule de verrouillage 8 est toujours en contact avec la bascule d'armage 3 et les roues d'armage 6, 7, et donc le rouage de finissage, sont toujours arrêtés. Lors de l'impulsion, la bascule de détente 5 pivote autour du point d'inflexion et entraine la bascule de verrouillage 8 en rotation autour de son axe 86, ce qui libère la palette de verrouillage 82 de l'ergot 36 et ainsi libère la bascule d'armage 3 ceci sans provoquer de recul géométrique de la bascule d'armage.After the descending arc of balance wheel 4, the latter returns, as shown in picture 2 counterclockwise and the plate pin 43 enters the fork 52 of the trigger lever 5 to start unlocking. On impulse, the leaf spring 2 transmits the energy accumulated during the previous winding to the balance and changes from a state close to instability to a stable state. At the start of the pulse, the locking rocker 8 is still in contact with the winding rocker 3 and the winding wheels 6, 7, and therefore the going train, are still stopped. During the impulse, the trigger rocker 5 pivots around the point of inflection and drives the locking rocker 8 in rotation around its axis 86, which releases the locking pallet 82 from the lug 36 and thus releases the winding rocker 3 this without causing geometric recoil of the winding rocker.

A la fin de l'impulsion, représentée à la Figure 3, la cheville de plateau 43 a quitté la fourchette 52 de la bascule de détente 5 et le ressort-lame 2 a transmis toute son énergie au balancier 4, et la bascule d'armage 3 est libre. La roue d'armage 6 est également libérée de son appui sur la cheville 35 de la bascule d'armage mais n'a pas encore commencé à tourner à cause de son inertie qui est non nulle. Le balancier 4 commence son arc ascendant antihoraire. La bascule de verrouillage 8 se trouve déjà dans la position de verrouillage sénestre pour le prochain armage. S'en suit la mise en rotation des roues d'armage sous le couple moteur du rouage de finissage transmis aux pignons 62, 72, comme représenté à la figure 4. La roue d'armage 6 en tournant pousse encore la bascule d'armage 3 dans le même sens par l'intermédiaire de la cheville d'armage 35a vers la roue 7 et attend la prochaine montée d'une came d'armage 71 à l'encontre de la cheville d'armage 35b la plus proche pour engager une nouvelle phase d'armage, sénestre cette fois, du ressort-lame bistable 2. Le balancier 4 continue son arc ascendant antihoraire durant cet intervalle.At the end of the pulse, shown in Figure 3 , the plate pin 43 has left the fork 52 of the trigger rocker 5 and the leaf spring 2 has transmitted all its energy to the rocker arm 4, and the winding rocker 3 is free. The winding wheel 6 is also released from its support on the pin 35 of the winding rocker but has not yet started to rotate because of its inertia which is non-zero. Pendulum 4 begins its ascending anti-clockwise arc. The locking rocker 8 is already in the sinister locking position for the next winding. This is followed by the rotation of the winding wheels under the driving torque of the going train transmitted to the pinions 62, 72, as shown in figure 4 . The winding wheel 6, while turning, pushes the winding rocker 3 again in the same direction via the winding pin 35a towards the wheel 7 and waits for the next rise of a winding cam 71 at the against the closest winding peg 35b to initiate a new phase of winding, sinister this time, of the bistable leaf spring 2. The pendulum 4 continues its anti-clockwise ascending arc during this interval.

La phase d'armage sénestre est représentée aux figures 5 à 7. La phase initiale est représentée à la figure 5, la phase médiane à la figure 6 et la phase finale d'armage et de verrouillage sénestre étant représentée à la figure 7.The left arming phase is shown in figures 5 to 7 . The initial phase is represented in the figure 5 , the middle phase at the figure 6 and the final winding and sinister locking phase being shown at figure 7 .

La phase initiale de l'armage senestre débute dès lors qu'une came d'armage 71 de la roue d'armage 7 entre en contact avec la cheville d'armage dextre 35b de la bascule d'armage 3. Les deux roues d'armage 6, 7 sont alors en mouvement en rotation dans un sens horaire. L'engagement de la came d'armage 71 contre la cheville 35b provoque un pivotement de la bascule d'armage 3 dans le sens antihoraire, qui induit un effort des bras 31, 32 sur le ressort-lame 2 de part et d'autre de son point d'inflexion, et la mise en charge élastique de celui-ci. A cet instant le balancier 4 poursuit toujours son arc ascendant dans le sens antihoraire. Cette rotation de la bascule d'armage 3, des roues d'armage 6, 7 et du balancier 4 se poursuit (figure 6) jusqu'à ce que la bascule d'armage 3 ait parcouru un arc suffisant pour que l'ergot de verrouillage sénestre 36a vienne rencontrer la palette de verrouillage 81 de la bascule de verrouillage (figure 7), une petite portion de came 71 restant alors à parcourir sur la roue d'armage 7, s'en suit le coincement de la roue d'armage contre la cheville d'armage 35b suite à l'arrêt de la rotation de la bascule d'armage 3 et des rotations respectives des roues d'armage 6, 7, donc du rouage. Cet arrêt marque la fin de la phase d'armage et de verrouillage de la bascule d'armage en position sénestre, le ressort-lame 2 étant alors dans son état d'armage métastable proche de l'instabilité et les roues 6,7, et la bascule d'armage 3 à l'état de verrouillage, coincée entre la bascule de verrouillage 8 et la roue 7. Le balancier finit son arc ascendant dans le sens antihoraire puis revient vers son point mort dans le sens horaire pour engager une nouvelle alternance au cours de laquelle les phases décrites ci-dessus se reproduisent symétriquement par rapport au plan passant par les axes de rotation du balancier 4 des bascules de détente 5 et d'armage 3 et par le point d'inflexion du ressort-lame 2.The initial phase of the left winding begins when a winding cam 71 of the winding wheel 7 comes into contact with the dexter winding pin 35b of the winding rocker 3. The two winding wheels armature 6, 7 are then in rotational motion in a clockwise direction. The engagement of the winding cam 71 against the pin 35b causes a pivoting of the winding rocker 3 counterclockwise, which induces a force of the arms 31, 32 on the leaf spring 2 on either side of its point of inflection, and the elastic loading thereof. At this moment the balance wheel 4 is still continuing its ascending arc in the counterclockwise direction. This rotation of the winding rocker 3, the winding wheels 6, 7 and the pendulum 4 continues ( figure 6 ) until the winding rocker 3 has traversed a sufficient arc for the sinister locking lug 36a to meet the locking pallet 81 of the locking rocker ( figure 7 ), a small portion of cam 71 then remaining to be traversed on the winding wheel 7, this results in the wedging of the winding wheel against the winding pin 35b following the stoppage of the rotation of the rocker winding 3 and the respective rotations of the winding wheels 6, 7, therefore of the gear train. This stop marks the end of the winding and locking phase of the winding rocker in the sinister position, the leaf spring 2 then being in its state of metastable winding close to instability and the wheels 6.7, and the winding rocker 3 in the locking state, wedged between the locking rocker 8 and the wheel 7. The balance completes its ascending arc in the anticlockwise direction then returns to its neutral point in the clockwise direction to engage a new alternation during which the phases described above are reproduced symmetrically with respect to the plane passing through the axes of rotation of the balance 4 of the trigger 5 and winding 3 rockers and through the point of inflection of the leaf spring 2.

Le dispositif selon l'invention permet ainsi de supprimer les effets de rebond de contact entre la bascule d'armage 3 et les roues d'armage tels que rencontrés avec les configurations de l'art antérieur.The device according to the invention thus makes it possible to eliminate the effects of contact rebound between the winding rocker 3 and the winding wheels such as encountered with the configurations of the prior art.

En outre le déverrouillage est également simplifié car il n'existe plus de crochetage entre bascule d'armage et roue d'armage. Le coincement entre la bascule d'armage et la bascule de verrouillage est aisément libéré par l'effet de déverrouillage de la bascule d'armage lors de la phase de détente, consécutive à la rotation de la bascule de détente 5, qui suffit à faire pivoter la bascule de verrouillage 8 et donc libérer la bascule d'armage 3 de sa force de contre-appui sur les cames d'armage 61, 71. Cet appui étant sensiblement ponctuel et les forces de frottements mutuelles étant réduites du fait, les roues d'armage 6, 7 n'ont qu'à vaincre leur inertie propre pour reprendre leur rotation une fois la bascule de verrouillage libérée, sans que la bascule d'armage 3 n'oppose une force de résistance additionnelle.In addition, unlocking is also simplified because there is no longer any picking between the winding rocker and the winding wheel. The jamming between the winding rocker and the locking rocker is easily released by the unlocking effect of the winding rocker during the relaxation phase, following the rotation of the trigger rocker 5, which suffices to pivot the locking rocker 8 and therefore release the winding rocker 3 from its counter-bearing force on the winding cams 61, 71. This support being substantially punctual and the mutual friction forces being reduced because the wheels winding 6, 7 only have to overcome their own inertia to resume their rotation once the locking rocker is released, without the winding rocker 3 opposing an additional resistance force.

Cette configuration et le mode de verrouillage en découlant permettent d'avoir une position de verrouillage où la bascule d'armage 3 est maintenue et toutes les pièces sont sécurisées. Lors de la phase de déverrouillage, la cheville de plateau 43 du balancier 4 vient en contact avec la fourchette 51 de la bascule de détente 5 et entraine celle-ci. Durant cette phase, la bascule de détente 5 entraine la bascule de verrouillage 8 par l'intermédiaire de la cheville de déverrouillage 52 et la fourchette de liaison 83 de la bascule de verrouillage 8. La bascule de verrouillage 8 pivote alors sur son axe sur une portion correspondante à l'ébat de dard de la bascule de détente 5, durant ce déplacement, en entrainement normal (par la cheville de plateau 43 du balancier) ou en cas de choc extérieur, la bascule de détente 5 n'a pas encore atteint son point d'instabilité et la bascule de verrouillage 8 n'a pas encore libérée les ergots de verrouillage 36a, 36b de la bascule d'armage 3. En continuant la rotation de la cheville de plateau, elle pousse encore la bascule de détente 5 jusque à son point d'instabilité. A cet instant, le ressort-lame 2 tend à retrouver son premier mode de flambage et c'est à ce moment que l'impulsion de la bascule de détente 5 commence. A cet instant, la came d'armage 6, 7 est toujours verrouillée par la bascule de verrouillage 8.This configuration and the resulting locking mode make it possible to have a locking position where the winding rocker 3 is maintained and all the parts are secure. During the unlocking phase, the plate pin 43 of the rocker arm 4 comes into contact with the fork 51 of the trigger rocker 5 and drives the latter. During this phase, the detent rocker 5 drives the locking rocker 8 via the unlocking pin 52 and the connecting fork 83 of the locking rocker 8. The locking rocker 8 then pivots on its axis on a portion corresponding to the spur of the trigger rocker 5, during this movement, in normal training (by the plate pin 43 of the balance) or in the event of an external shock, the trigger rocker 5 has not yet reached its point of instability and the locking rocker 8 has not yet released the locking lugs 36a, 36b of the winding rocker 3. Continuing the rotation of the plate pin, it still pushes the trigger rocker 5 to its point of instability. At this moment, the leaf spring 2 tends to return to its first buckling mode and it is at this moment that the impulse of the detent rocker 5 begins. At this moment, the winding cam 6, 7 is still locked by the locking rocker 8.

Durant toute la phase de déverrouillage de la force motrice, le balancier 4 est la source d'énergie qui doit vaincre les forces de frottement qui se trouvent entre la bascule de verrouillage 8 et les ergots 36a, 36b de la bascule d'armage 3 ainsi que la force d'appui de la bascule de détente 5 contre les étoqueaux provoquée par le flambage du ressort-lame 2. En effet, les palettes 81, 82 de la bascule de verrouillage 8 sont concentriques à son point de pivotement ceci afin de ne provoquer aucun tirage et prendre le moins d'énergie possible au balancier 4 lors du déverrouillage de la force motrice.Throughout the driving force unlocking phase, the rocker arm 4 is the source of energy which must overcome the frictional forces which are between the locking rocker 8 and the lugs 36a, 36b of the winding rocker 3 as well that the pressing force of the trigger rocker 5 against the stokers caused by the buckling of the leaf spring 2. In fact, the pallets 81, 82 of the locking rocker 8 are concentric at its pivot point, this in order not to cause any pulling and to take as little energy as possible from the rocker arm 4 when unlocking the the driving force.

L'impulsion commencée, les ergots de verrouillage 36a, 36b sont libérés et le balancier 4 reçoit toute l'énergie fournie par le ressort-lame 2 car les oeillets de la lame n'entrent plus en contact avec les goupilles de la bascule d'armage 3. Durant la phase de déverrouillage, les roue d'armage 6, 7 ont été libérés de leur appui contre les chevilles 35a, 35b de la bascule d'armage 3, mais n'ont pas encore commencé à tourner car la force motrice doit vaincre leur inertie. Une fois que la cheville 43 du balancier a quitté la fourchette 51 de la bascule de détente à la fin de l'impulsion, la force motrice ayant vaincu l'inertie des roues d'armage, elles se mettent à tourner pour entamer un nouveau cycle d'armage du système.The pulse started, the locking lugs 36a, 36b are released and the balance 4 receives all the energy supplied by the leaf spring 2 because the eyelets of the blade no longer come into contact with the pins of the rocker. winding 3. During the unlocking phase, the winding wheels 6, 7 have been released from their support against the pins 35a, 35b of the winding rocker 3, but have not yet started to rotate because the driving force must overcome their inertia. Once the pin 43 of the pendulum has left the fork 51 of the trigger rocker at the end of the impulse, the driving force having overcome the inertia of the winding wheels, they begin to turn to begin a new cycle. system arming.

Claims (12)

  1. An escapement mechanism (1) arranged to transmit mechanical energy impulses from a driving source to a timepiece oscillating regulator (4) by way of a leaf spring (2) working in buckling mode around an inflexion point (I), said leaf spring (2) being likely, by way of a winding lever (3) and a detent lever (5), to accumulate the energy originating from the driving source during a winding phase, to then remain in a wound state during a locking phase, and to then restore the accumulated energy to said oscillating regulator (4) during a detent phase, the winding lever (3) being arranged to cooperate with at least one winding wheel (6, 7) so as to wind the leaf spring (2) during winding phases, the winding wheel or each winding wheel (6, 7) having on a periphery a plurality of winding cams (61, 71), each defining a cam surface and the winding lever (3) having at least one winding pin (35a, 35b) forming a cam follower in such a way that each winding pin (35a, 35b) slides on the cam surface (611, 711) of one of the winding cams (61, 71) during winding phases of the leaf spring, the mechanism additionally having a locking lever (8) for the winding lever (3) during locking phases at least, a mechanism in which the locking lever (8) has two locking pallets (81, 82) arranged to cooperate with additional locking members (36a, 36b), in particular catches, on said winding lever (3), and characterized in that the at least one said winding wheel (6, 7) and said winding lever (3) are arranged respectively in such a way that the winding wheel or each winding wheel (6, 7) is stopped by being wedged between a winding pin (35a, 35b) and a cam surface of a said winding cam (61, 71) and between a said locking pallet (81, 82) and a said additional locking member (36a, 36b) at the end of each winding phase and during the locking phases.
  2. The mechanism according to Claim 1, characterized in that each winding pin (35a, 35b) features a contact surface (351) with the cam path of the winding cams (61, 71) having a circular section, each said pin being arranged on a beak (34a, 34b) of the lever.
  3. The mechanism according to Claim 1 or 2, characterized in that each winding wheel (6, 7) has at least three identical winding cams (61, 71) which are evenly distributed on the periphery of said winding wheels.
  4. The mechanism according to any one of Claims 1 to 3, characterized in that it has at least one winding wheel (6, 7) arranged to be rotationally movable around an individual pivot axis which can be disposed on a straight line which passes through the axis of rotation of the regulator (4) and the inflexion point of the bistable leaf spring (2) and that the winding pins (35a, 35b) are arranged on an internal wall of a ring which is rigidly connected to the winding lever (3) in which the winding wheel is arranged so that a said winding pin (35a, 35b) is only in contact with a single winding cam of the winding wheel on a vibration of the regulator (4).
  5. The mechanism according to any one of Claims 1 to 3, characterized in that it has two winding wheels (6, 7) arranged to be rotationally movable around an individual pivot axis in a symmetrical position on each side of a straight line which can pass through the axis of rotation of the regulator (4) and the inflexion point of the bistable leaf spring (2) and are indexed in rotation in relation to one another so that the winding lever (3) is only in contact on a said winding pin (35a, 35b) with a single winding wheel on a vibration of the regulator (4).
  6. The mechanism according to any one of Claims 1 to 5, characterized in that the locking lever (8) of the winding lever (3) is rotationally movable on a pivot axis (86) and kinematically linked to the detent lever (5).
  7. The mechanism according to any one of Claims 1 to 6, characterized in that the locking lever (8) has a bar equipped at a first end with a linking fork to said detent lever (5) and two locking arms extending symmetrically to one another from said bar and each equipped at its free end with a said locking pallet (81, 82).
  8. The mechanism according to Claim 7, characterized in that each locking pallet is composed of a circular segment which is concentric with the axis of rotation of the locking lever.
  9. The escapement mechanism according to any one of Claims 1 to 8, characterized in that the additional locking member on said winding lever (3) has a locking catch (36a, 36b) having a shape and orientation adapted to hook a said locking pallet (81, 82) of the locking lever.
  10. The escapement mechanism according to any one of Claims 7 to 9, characterized in that the fork of the locking lever (8) has two horns (83a, 83b) delimiting an inter-horn space in which an unlocking pin (52) which is rigidly connected to the detent lever (5) cooperates.
  11. The mechanism according to Claims 5 and 9, characterized in that the locking lever (8) is arranged so that a locking pallet (81,82) hooks a said locking catch (36a, 36b) of the winding lever (3) disposed on a first beak of the winding lever substantially simultaneously with the wedging of a winding wheel (6, 7) on a winding pin (33) disposed on the second beak of the winding lever.
  12. A timepiece having an escapement mechanism according to any one of Claims 1 to 11.
EP18193657.6A 2018-09-11 2018-09-11 Exhaust mechanism with bistable leaf spring Active EP3623875B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18193657.6A EP3623875B1 (en) 2018-09-11 2018-09-11 Exhaust mechanism with bistable leaf spring

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Application Number Priority Date Filing Date Title
EP18193657.6A EP3623875B1 (en) 2018-09-11 2018-09-11 Exhaust mechanism with bistable leaf spring

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EP3623875A1 EP3623875A1 (en) 2020-03-18
EP3623875B1 true EP3623875B1 (en) 2023-04-26

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Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2105806B1 (en) 2008-03-27 2013-11-13 Sowind S.A. Escapement mechanism
CH710685B1 (en) 2015-01-30 2019-07-15 Sowind S A Escape mechanism.
EP3273308B1 (en) 2016-07-18 2019-06-12 Sowind S.A. Exhaust mechanism

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