EP3510449B1 - Escapement mechanism - Google Patents

Escapement mechanism Download PDF

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Publication number
EP3510449B1
EP3510449B1 EP17761283.5A EP17761283A EP3510449B1 EP 3510449 B1 EP3510449 B1 EP 3510449B1 EP 17761283 A EP17761283 A EP 17761283A EP 3510449 B1 EP3510449 B1 EP 3510449B1
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EP
European Patent Office
Prior art keywords
release
escape
mobile
wheel
release mobile
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EP17761283.5A
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German (de)
French (fr)
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EP3510449A1 (en
Inventor
Dominique Renaud
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Freymond Eric
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Dominique Renaud SA
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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
    • 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 watchmaking. It relates to an escape mechanism and, more particularly, to a direct impulse free escape mechanism.
  • the escapement is an essential part of mechanical watch movements. It is generally placed between a gear train and an oscillator.
  • the cog transmits to the exhaust a torque coming from the energy source, which maintains and counts the oscillations of the oscillator.
  • the detent escapement is the one of the two that has the best energy efficiency.
  • Different examples of detent escapements are for example described in the documents CH 704 151 B1 , EP 1,538,491 A1 our still EP 1,710,636 A1 .
  • the detent escapements are sensitive to strong accelerations and to shocks with significant risks of galloping and tripping. As a result, the detent escapement is not widespread because it can not bear being worn and difficult to couple with high frequency oscillators, which today tend to impose themselves because of their better precision.
  • the anchor escapement does not know these risks but has the drawback of higher energy consumption because of the more numerous shocks, inertia and greater friction at the level of the anchor.
  • the present invention aims to remedy the aforementioned drawbacks by proposing an exhaust which is compatible with strong accelerations of an oscillator at high frequency and to the constraints of carrying on the wrist while maintaining a low energy consumption.
  • the exhaust mechanism of the invention is designed so that the release mobile and the unidirectional drive device are arranged to cooperate with means configured to accumulate only a portion of the energy supplied by a pulse from the oscillator during the disengagement of the disengagement mobile on the one hand and to restore it in the form of an acceleration of the escape wheel during a transmission by the escape wheel of a pulse at the oscillator on the other hand.
  • the release mobile and the wheeled mobile are arranged relative to each other so that there is a zero or negative draft between the two.
  • the gear train and the release mobile are arranged so that said portion of energy transmitted by the oscillator during the release phase is accumulated in elastic form before contributing to the acceleration of said wheel exhaust.
  • the exhaust mechanism comprises a positioning stop capable of positioning the release mobile in the engagement position, said stop being if necessary fixed with reference to the axis of rotation of the release mobile.
  • the axes of rotation of the gear train, of the escapement wheel and of the release gear are parallel and coplanar.
  • the oscillator is movable in rotation about an axis and in that the axes of rotation of the oscillator, of the gear train, of the escape wheel and of the release motive are parallel and coplanar when the engagement mobile is in the engagement position.
  • the unidirectional drive device comprises a plurality of flexible blades each arranged in abutment on a ratchet stop, said flexible blades and ratchet stops being arranged radially in a regular angular distribution.
  • the unidirectional drive device is integral with the release mobile or the oscillator.
  • the release mobile is coaxial with the escape wheel.
  • the exhaust mechanism comprises an elastic member, in particular a return spring, mounted between the release mobile and the escape wheel, and which tends to bring the mobile back in its engagement position, preferably against the positioning stop in the engagement position.
  • the release mobile comprises rest pins, in that the gear mobile includes rest pads, in that the trajectories of the rest pads and rest pins are intersecting and in that the mechanism is arranged so that the rest studs meet the rest pins by causing the gear train to stop when the engagement mobile is in the engagement position.
  • the unidirectional drive device is integral with the escape wheel.
  • the escapement wheel is mounted movable on the release movable and the escapement wheel comprises rest teeth intended to come into abutment against a fixed rest pallet with reference to the frame of the timepiece.
  • the release mobile also advantageously consists of a rocker pivoted on the axis of the gear train.
  • the springs of the trigger flip-flops are designed to exert a low restoring force.
  • the increase in this restoring force would make it possible to reduce the sensitivity to shock and to support high frequencies by accelerating the return of the rocker in its rest position but would have the disadvantage of increasing the energy consumption during the release.
  • the present invention implements a particular escape mechanism in which it is sought to recover the energy necessary for the release rather than to reduce it. Like any detent escapement, this mechanism has a single rest position, the release and the impulse take place alternately in two, the other being a knockout.
  • the mechanism comprises a gear train 1 kinematically connected to an escape wheel 2 and forming with it a train driven by a drive member not shown, typically a barrel.
  • the escape wheel has impulse teeth 3 intended to periodically give impulse to an oscillator here taking the form of a pendulum of which only the plate 4 and the pin 5 are represented.
  • the gear train 1 comprises rest pads 6 arranged in a circle at the end of the arm extending radially.
  • the exhaust mechanism further comprises a release mobile 7 taking the form of a wheel pivoted on the same axis as the wheel. exhaust.
  • the release mobile 7 comprises rest pins 8 and a unidirectional drive device formed by flexible blades 9 extending radially and bearing against ratchet stops 10 in their rest position.
  • the pawl stops 10 are adjacent to the rest pins but it could be otherwise as will be seen later.
  • the angular amplitude of the rotation of the release mobile 7 relative to the escape wheel 2 is limited by a positioning stop 11, integral with the release mobile 7.
  • a return spring 12 disposed between the escape wheel 2 and the release mobile 7 tends to return the release mobile 7 to an angular position defined with reference to the escape wheel 2.
  • the figure 2 represents the exhaust mechanism at rest, the balance coming from freely traversing the additional arc and the pin 5 preparing to come into contact with a flexible blade 9 of the release mobile 7.
  • the train is stopped, a rest pad 6 of the gear train bearing against a rest pin 8 of the release track 7.
  • the figure 3 represents the escape mechanism during the disengagement phase during which the disengagement mobile 7 moves from an engagement position to a disengagement position under the impulse of the pendulum transmitted via the flexible blade 9.
  • the flexible blade 9 is in abutment against the pawl stop 10 by forming a pawl mechanism so that the impulse of the pendulum causes the release mobile 7 to rotate counterclockwise as shown in the figures.
  • the bearing surfaces of the rest pad 6 and the rest pin 8 slide against one another.
  • the contact surfaces of the rest pegs 8 are cylinder portions with a circular base coaxial with the pivot axis of the release mobile 7 so that the release of the release mobile 7 does not cause advance nor of retraction of the gear train 1. This configuration corresponds to a zero pulling angle.
  • the surface of the rest pegs could have a positive pull angle to secure the blocking of the release mobile 7 or on the contrary a negative pull angle to facilitate its release.
  • the flexible arms 9 and the rest pins 8 are arranged radially at a regular angular distribution so that the release mobile 7 is balanced on its axis of rotation and, therefore, not very sensitive to the accelerations undergone by the timepiece. Furthermore, the return spring 12 tends to keep the release mobile 7 in abutment against the escape wheel 2 in its engagement position. Thus, it is not necessary to provide a positive pull angle to further secure the release mobile 7, which makes it possible to minimize the disturbances caused to the oscillator during the release.
  • the figure 4 represents the escape mechanism in the impulse phase.
  • the figure 5 represents the escape mechanism at the end of the impulse phase and immediately before stopping the train caused by the meeting of a rest pad 6 with a rest pin 8.
  • the circular paths of the rest pads and rest pins are intersecting and the mechanism is arranged so that a stud 6 meets a pin 8 when the release mobile 7 is in the engagement position, that is to say when the escape wheel 2 has caught up the release mobile 7, the positioning stop 11 pressing against the escape wheel 2. Consequently, the advance of the train is limited when the release mobile is in the engagement position.
  • the figure 6 represents the exhaust mechanism at rest at the time of the blow lost during the next alternation.
  • the balance pivots counterclockwise and the pin 5 spreads the flexible arm 9 without driving the release mobile 7 in rotation.
  • the flexible blade 9 constitutes, with the ratchet stop 10, a ratchet-type unidirectional drive system.
  • the back of the impulse teeth has a circular profile conforming to the shape of the balance plate to prevent accidental retraction of the escape wheel while the balance traverses the additional arc.
  • the train is driven by a double motorization: the motor member which propels the train in a conventional manner, and the return spring 12 which tows the escape wheel 2 when it starts up.
  • the action of the return spring 12 is all the more effective when it is fixed on the release mobile 7 which is itself driven in rotation by the oscillator. A portion of the energy contributing to the acceleration of the train therefore comes from the oscillator which goes against the generally accepted idea that it is necessary to avoid braking the oscillator so as not to disturb its isochronism and limit energy consumption.
  • the transfer of energy from the oscillator to the gear train is optimized thanks to the movable release 7 and the return spring 12 which acts as a shock absorber and limits the loss of energy when the ankle hits the flexible arm.
  • the acceleration of the train is therefore given smoothly, but since it is stronger than that which would be given by a single drive member, the time required for the escape wheel 2 to catch up with the ankle 5 of the balance wheel is reduced.
  • the device can operate at higher frequencies but also that the pulse angle traveled by the balance in the pulse phase is greater.
  • the stopping of the train is caused by the meeting of two mobile elements with reference to the frame, kinematically linked in a discontinuous manner.
  • the release mobile Unlike a trigger rocker which performs a back and forth movement by dissipating the energy it receives from the balance, the release mobile always pivots in the same direction which is also that of the impulse given by the oscillator as well as the displacement of the escape wheel.
  • the energy accumulated in elastic form at each release in the return spring is restored when the escape wheel starts.
  • the recovery of part of the energy taken from the oscillator in the release phase characterizes a new type of exhaust that can be designated by the term of "turbo-expansion", This one presenting interesting performances in terms of energy efficiency as well as frequency and dependability.
  • the balance plate comprises a pin which performs the release and a pulse pallet, distinct from the pin, arranged to receive the pulse of the escape wheel.
  • the respective angular and radial positions of the dowel and the pallet with respect to the pendulum axis define the start of the release and impulse phases and the angular speeds of release and impulse.
  • the angular speed of the escape wheel is higher than the speed reached by the escape wheel at the start of the pulse.
  • the mechanism of exhaust according to the invention can be arranged so that the kinetic energy acquired by the release mobile during the release phase is at least partially restored and contributes to the acceleration of the train.
  • the unidirectional drive device could be placed on the oscillator.
  • the release mobile could be connected to the escape wheel by flexible elements.
  • the disengagement movement of the disengagement mobile under the action of the oscillator could be assimilated to a rotation or to any other trajectory adapted to the disengagement of the rest pins.
  • These same flexible elements could also play the role of return spring.
  • the Figures 7 to 12 represent a second embodiment of an exhaust mechanism according to the invention.
  • the mechanism also includes a unidirectional drive device composed of a plurality of flexible blades 9 abutting on ratchet stops 10.
  • the unidirectional drive device is here mounted integral with the escape wheel 2. In an original way the wheel is not pivoted on the frame of the timepiece but on the release mobile 7 which here takes the form of a rocker pivoted on the same axis as the gear train 1.
  • the mechanism also includes a positioning stop 11 able to position the release mobile 7 in an engagement position in which the rotation of the escape wheel is limited.
  • a positioning stop 11 able to position the release mobile 7 in an engagement position in which the rotation of the escape wheel is limited.
  • the figure 9 represents the escape mechanism in the release phase.
  • the plate pin 5 struck a flexible blade 9 bearing on a ratchet stop 10.
  • the rotation of the escape wheel 2 being hampered by the rest pallet 13, it is the assembly composed of the release mobile 7 , of the escape wheel 2 and of the gear train 1 which is rotated counterclockwise around the pivot axis of the gear train.
  • the retraction of the train in the disengagement phase causes the motor organ to be rearmed so that the energy supplied by the oscillator during the disengagement is stored in elastic form by the motor organ before being returned to propel the cog.
  • the escape wheel 2 and the gear train are released.
  • the train accelerates and the release mobile 7 returns to its position of engagement against the positioning stop 11.
  • the rest plane of the rest pallet is preferably an orthoradial plane with reference to the axis of rotation of the release mobile which corresponds to a zero drawing angle. Alternatively, the rest plane may have a different inclination or a non-rectilinear profile.
  • the figure 10 represents the escape mechanism in the impulse phase after the release mobile 7 has returned to its engagement position in abutment against the positioning stop 11 and that a pulse tooth 3 of the escape wheel 2 caught up with the pendulum pin 5.
  • the figure 11 represents the mechanism at the end of the pulse phase and just before stopping the train caused by the meeting of the next pulse tooth 3 with the rest pallet 13.
  • the figure 12 shows the mechanism at rest during the lost blow when the pendulum returns when the ratchet passes.
  • the energy supplied by the oscillator during the release is at least partially returned to drive the train.
  • this second embodiment directly uses the motor member to temporarily store, in elastic form, the energy coming from the oscillator during the release. It is also the driving force which keeps the release mobile 7 in the engagement position. Note that in the exhausts of the prior art, the gear train recedes slightly during the release when the pull angle is positive, this arrangement having the aim of securing the trigger and not of recovering energy.
  • the unidirectional drive device could comprise only one pawl and be secured to the release mobile or to the oscillator.
  • the release and impulse functions could be provided by separate teeth on the escape wheel and by separate paddles on the oscillator.
  • the exhaust mobile could be translated rather than rotated. It could also be connected to the frame by a flexible element.
  • the release mobile could have a counterweight so that the mobile assembly that it composes with the escape wheel is balanced on its axis of rotation.
  • the mechanism could include a second stop to limit the amplitude of the movement of the release mobile as well as a return spring to accelerate the return of the release mobile to its engagement position.
  • the mechanism could also include a safety device which would limit the movement of the release mobile in the free oscillation phases of the oscillator.

Description

Domaine techniqueTechnical area

La présente invention se rapporte au domaine de l'horlogerie. Elle concerne, un mécanisme d'échappement et, plus particulièrement, un mécanisme d'échappement libre à impulsions directes.The present invention relates to the field of watchmaking. It relates to an escape mechanism and, more particularly, to a direct impulse free escape mechanism.

Etat de la techniqueState of the art

L'échappement est une partie essentielle des mouvements d'horlogerie mécanique. Il est généralement placé entre un rouage et un oscillateur. Le rouage transmet à l'échappement un couple provenant de la source d'énergie, qui entretient et compte les oscillations de l'oscillateur.The escapement is an essential part of mechanical watch movements. It is generally placed between a gear train and an oscillator. The cog transmits to the exhaust a torque coming from the energy source, which maintains and counts the oscillations of the oscillator.

Il existe principalement deux types d'échappement libre, les échappements à ancre à impulsions indirectes qui possèdent deux positions de repos et les échappements à détente à impulsions directes qui n'ont qu'une seule position de repos et un coup perdu.There are mainly two types of free escapement, indirect impulse escapements which have two rest positions and detent direct impulse escapements which have only one rest position and a knockout.

L'échappement à détente est celui des deux qui a le meilleur rendement énergétique. Différents exemples d'échappements à détente sont par exemple décrits dans les documents CH 704 151 B1 , EP 1 538 491 A1 our encore EP 1 710 636 A1 . Toutefois, les échappements à détente sont sensibles aux fortes accélérations et aux chocs avec des risques importants de galop et de trébuchement. Il en résulte que l'échappement à détente est peu répandu car il supporte mal d'être porté et s'accouple difficilement avec les oscillateurs à fréquence élevée, qui tendent aujourd'hui à s'imposer en raison de leur meilleure précision.The detent escapement is the one of the two that has the best energy efficiency. Different examples of detent escapements are for example described in the documents CH 704 151 B1 , EP 1,538,491 A1 our still EP 1,710,636 A1 . However, the detent escapements are sensitive to strong accelerations and to shocks with significant risks of galloping and tripping. As a result, the detent escapement is not widespread because it can not bear being worn and difficult to couple with high frequency oscillators, which today tend to impose themselves because of their better precision.

L'échappement à ancre ne connait pas ces risques mais présente comme inconvénient une consommation énergétique plus élevée à cause des chocs plus nombreux, de l'inertie et des frottements plus importants au niveau de l'ancre.The anchor escapement does not know these risks but has the drawback of higher energy consumption because of the more numerous shocks, inertia and greater friction at the level of the anchor.

La présente invention a pour but de remédier aux inconvénients précités en proposant un échappement qui soit compatible avec les fortes accélérations d'un oscillateur à fréquence élevée et aux contraintes d'un portage au poignet tout en conservant une faible consommation d'énergie.The present invention aims to remedy the aforementioned drawbacks by proposing an exhaust which is compatible with strong accelerations of an oscillator at high frequency and to the constraints of carrying on the wrist while maintaining a low energy consumption.

Divulguation de l'inventionDisclosure of invention

L'invention concerne un mécanisme d'échappement libre à coup perdu pour pièce d'horlogerie tel que défini à la revendication 1, ladite pièce d'horlogerie comportant :

  • un rouage destiné à être entrainé par un organe moteur et comportant un mobile de rouage mobile en rotation autour d'un axe de rotation et agencé en liaison cinématique avec au moins une roue d'échappement du mécanisme d'échappement,
  • un oscillateur apte à recevoir une impulsion de ladite roue d'échappement afin d'entretenir ses oscillations.
The invention relates to a blow-by-blow escapement mechanism for a timepiece as defined in claim 1, said timepiece comprising:
  • a cog intended to be driven by a drive member and comprising a cog mobile movable in rotation about an axis of rotation and arranged in kinematic connection with at least one escape wheel of the escape mechanism,
  • an oscillator capable of receiving a pulse from said escape wheel in order to maintain its oscillations.

Le mécanisme d'échappement de l'invention comporte en outre :

  • un mobile de dégagement agencé pour coopérer en rotation avec la roue d'échappement et se déplacer, lors d'une phase de dégagement, sous une impulsion de l'oscillateur, entre une position d'engagement dans laquelle l'avance du rouage est bloquée et une position de dégagement dans laquelle l'avance du rouage est libre, et
  • un dispositif d'entrainement unidirectionnel du mobile de dégagement agencé pour transmettre ladite impulsion de l'oscillateur au mobile de dégagement pour le faire passer de la position d'engagement à la position de dégagement.
The exhaust mechanism of the invention further comprises:
  • a release mobile arranged to cooperate in rotation with the escape wheel and to move, during a release phase, under an impulse from the oscillator, between an engagement position in which the advance of the gear train is blocked and a release position in which the advance of the gear train is free, and
  • a unidirectional drive device of the release mobile arranged to transmit said pulse from the oscillator to the release mobile to move it from the engagement position to the release position.

De façon caractéristique, le mécanisme d'échappement de l'invention est conçu de telle sorte que le mobile de dégagement et le dispositif d'entrainement unidirectionnel sont agencés pour coopérer avec des moyens configurés pour accumuler qu'une portion de l'énergie fournie par une impulsion de l'oscillateur lors du dégagement du mobile de dégagement d'une part et pour la restituer sous la forme d'une accélération de la roue d'échappement lors d'une transmission par la roue d'échappement d'une impulsion à l'oscillateur d'autre part.Characteristically, the exhaust mechanism of the invention is designed so that the release mobile and the unidirectional drive device are arranged to cooperate with means configured to accumulate only a portion of the energy supplied by a pulse from the oscillator during the disengagement of the disengagement mobile on the one hand and to restore it in the form of an acceleration of the escape wheel during a transmission by the escape wheel of a pulse at the oscillator on the other hand.

Les revendications dépendantes proposent d'autres caractéristiques particulières du mécanisme d'échappement de l'invention.The dependent claims provide other particular features of the escape mechanism of the invention.

Ainsi, dans une forme de réalisation, le mobile de dégagement et le mobile de rouage sont agencés l'un par rapport à l'autre de telle sorte qu'il existe un tirage nul ou négatif entre les deux.Thus, in one embodiment, the release mobile and the wheeled mobile are arranged relative to each other so that there is a zero or negative draft between the two.

Selon un mode de réalisation, le mobile de rouage et le mobile de dégagement sont agencés pour que ladite portion d'énergie transmise par l'oscillateur lors de la phase de dégagement soit accumulée sous forme élastique avant de contribuer à l'accélération de ladite roue d'échappement.According to one embodiment, the gear train and the release mobile are arranged so that said portion of energy transmitted by the oscillator during the release phase is accumulated in elastic form before contributing to the acceleration of said wheel exhaust.

Selon un mode de réalisation, le mécanisme d'échappement comporte une butée de positionnement apte à positionner le mobile de dégagement dans la position d'engagement, ladite butée étant le cas échéant fixe en référence à l'axe de rotation du mobile de dégagement.According to one embodiment, the exhaust mechanism comprises a positioning stop capable of positioning the release mobile in the engagement position, said stop being if necessary fixed with reference to the axis of rotation of the release mobile.

Selon un mode de réalisation, les axes de rotation du mobile de rouage, de la roue d'échappement et du mobile de dégagement sont parallèles et coplanaires.According to one embodiment, the axes of rotation of the gear train, of the escapement wheel and of the release gear are parallel and coplanar.

Selon un mode de réalisation, l'oscillateur est mobile en rotation autour d'un axe et en ce que les axes de rotation de l'oscillateur, du mobile de rouage, de la roue d'échappement et du mobile de dégagement sont parallèles et coplanaires lorsque le mobile d'engagement est dans la position d'engagement.According to one embodiment, the oscillator is movable in rotation about an axis and in that the axes of rotation of the oscillator, of the gear train, of the escape wheel and of the release motive are parallel and coplanar when the engagement mobile is in the engagement position.

Selon un mode de réalisation, le dispositif d'entrainement unidirectionnel comporte une pluralité de lames flexibles agencées chacune en appui sur une butée de cliquets, lesdites lames flexibles et butées de cliquet étant disposées de façon radiale selon une répartition angulaire régulière.According to one embodiment, the unidirectional drive device comprises a plurality of flexible blades each arranged in abutment on a ratchet stop, said flexible blades and ratchet stops being arranged radially in a regular angular distribution.

Selon des modes de réalisation, le dispositif d'entrainement unidirectionnel est solidaire du mobile de dégagement ou de l'oscillateur.According to embodiments, the unidirectional drive device is integral with the release mobile or the oscillator.

Dans un mode particulier de réalisation, le mobile de dégagement est coaxial avec la roue d'échappement.In a particular embodiment, the release mobile is coaxial with the escape wheel.

Selon un mode de réalisation, le mécanisme d'échappement comporte un organe élastique, en particulier un ressort de rappel, monté entre le mobile de dégagement et la roue d'échappement, et qui tend à ramener le mobile de dégagement dans sa position d'engagement, de préférence contre la butée de positionnement dans la position d'engagement.According to one embodiment, the exhaust mechanism comprises an elastic member, in particular a return spring, mounted between the release mobile and the escape wheel, and which tends to bring the mobile back in its engagement position, preferably against the positioning stop in the engagement position.

Dans une forme de réalisation particulière, le mobile de dégagement comporte des chevilles de repos, en ce que le mobile de rouage comporte des plots de repos, en ce que les trajectoires des plots de repos et des chevilles de repos sont sécantes et en ce que le mécanisme est agencé pour que les plots de repos rencontrent les goupilles de repos en provocant l'arrêt du rouage lorsque le mobile d'engagement est dans la position d'engagement.In a particular embodiment, the release mobile comprises rest pins, in that the gear mobile includes rest pads, in that the trajectories of the rest pads and rest pins are intersecting and in that the mechanism is arranged so that the rest studs meet the rest pins by causing the gear train to stop when the engagement mobile is in the engagement position.

Dans une variante de réalisation, le dispositif d'entrainement unidirectionnel est solidaire de la roue d'échappement.In an alternative embodiment, the unidirectional drive device is integral with the escape wheel.

Avantageusement dans ce cas la roue d'échappement est montée mobile sur le mobile de dégagement et la roue d'échappement comporte des dents de repos destinés à venir en appui contre une palette de repos fixe en référence au bâti de la pièce d'horlogerie.Advantageously in this case the escapement wheel is mounted movable on the release movable and the escapement wheel comprises rest teeth intended to come into abutment against a fixed rest pallet with reference to the frame of the timepiece.

Dans cette variante de réalisation toujours le mobile de dégagement est par ailleurs avantageusement constitué d'une bascule pivotée sur l'axe du mobile de rouage.In this alternative embodiment, the release mobile also advantageously consists of a rocker pivoted on the axis of the gear train.

Brève description des dessinsBrief description of the drawings

D'autres détails de l'invention apparaîtront plus clairement à la lecture de la description qui suit, faite en référence au dessin annexé dans lequel :

  • les figures 1 à 6 représentent un premier mode de réalisation d'un mécanisme d'échappement à turbo détente selon l'invention,
  • la figure 1 représente une vue en perspective du premier mode de réalisation,
  • les figures 2 à 6 proposent des vues chronologiques de l'ensemble de la figure 1, à différentes étapes de son fonctionnement,
  • la figure 7 représente une vue en perspective d'un deuxième mode de réalisation de l'invention,
  • les figures 8 à 12 proposent des vues chronologiques de l'ensemble de la figure 7, à différentes étapes de son fonctionnement.
Other details of the invention will appear more clearly on reading the description which follows, given with reference to the appended drawing in which:
  • the Figures 1 to 6 represent a first embodiment of a turbo expansion exhaust mechanism according to the invention,
  • the figure 1 represents a perspective view of the first embodiment,
  • the figures 2 to 6 offer chronological views of the entire figure 1 , at different stages of its operation,
  • the figure 7 represents a perspective view of a second embodiment of the invention,
  • the Figures 8 to 12 offer chronological views of the entire figure 7 , at different stages of its operation.

Mode de réalisation de l'inventionMode of carrying out the invention

Afin de réduire l'énergie perdue lors du dégagement et de perturber le moins possible l'isochronisme de l'oscillateur, les ressorts des bascules de détente sont conçus pour exercer une faible force de rappel. L'augmentation de cette force de rappel permettrait de réduire la sensibilité au choc et de supporter des fréquences élevées en accélérant le retour de la bascule dans sa position de repos mais aurait pour inconvénient d'accroitre la consommation d'énergie lors du dégagement. D'une façon originale, la présente invention met en oeuvre un mécanisme d'échappement particulier dans lequel on cherche à récupérer l'énergie nécessaire au dégagement plutôt qu'à la réduire. Comme tout échappement à détente, ce mécanisme possède une seule position de repos, le dégagement et l'impulsion s'effectuent une alternance sur deux, l'autre étant un coup perdu.In order to reduce the energy lost during disengagement and to disturb the isochronism of the oscillator as little as possible, the springs of the trigger flip-flops are designed to exert a low restoring force. The increase in this restoring force would make it possible to reduce the sensitivity to shock and to support high frequencies by accelerating the return of the rocker in its rest position but would have the disadvantage of increasing the energy consumption during the release. In an original way, the present invention implements a particular escape mechanism in which it is sought to recover the energy necessary for the release rather than to reduce it. Like any detent escapement, this mechanism has a single rest position, the release and the impulse take place alternately in two, the other being a knockout.

On notera que les figures servent simplement à illustrer les principes de fonctionnement de l'invention. L'homme du métier saura dimensionner les différents éléments de façon à conférer au mécanisme les performances désirées.It will be noted that the figures serve simply to illustrate the operating principles of the invention. Those skilled in the art will be able to size the various elements so as to give the mechanism the desired performance.

Un premier mode de réalisation d'un mécanisme d'échappement selon l'invention est présenté sur les figures 1 à 6. Le mécanisme comporte un mobile de rouage 1 relié cinématiquement à une roue d'échappement 2 et formant avec elle un rouage entrainé par un organe moteur non représenté, typiquement un barillet. La roue d'échappement comporte des dents d'impulsion 3 destinées à donner périodiquement une impulsion à un oscillateur prenant ici la forme d'un balancier dont seul le plateau 4 et la cheville 5 sont représentés. Le mobile de rouage 1 comporte des plots de repos 6 disposés en cercle à l'extrémité de bras s'étendant radialement. Le mécanisme d'échappement comporte en outre un mobile de dégagement 7 prenant la forme d'une roue pivotée sur le même axe que la roue d'échappement. Le mobile de dégagement 7 comporte des chevilles de repos 8 et un dispositif d'entrainement unidirectionnel formé par des lames flexibles 9 s'étendant radialement et venant en appui contre des butées de cliquet 10 dans leur position de repos. Dans le mode de réalisation présenté, les butées de cliquet 10 sont adjacentes aux chevilles de repos mais il pourrait en être autrement comme on le verra par la suite. L'amplitude angulaire de la rotation du mobile de dégagement 7 par rapport à la roue d'échappement 2 est limitée par une butée de positionnement 11, solidaire du mobile de dégagement 7. Un ressort de rappel 12 disposé entre la roue d'échappement 2 et le mobile de dégagement 7 tend à ramener le mobile de dégagement 7 dans une position angulaire définie en référence à la roue d'échappement 2.A first embodiment of an exhaust mechanism according to the invention is presented on the Figures 1 to 6 . The mechanism comprises a gear train 1 kinematically connected to an escape wheel 2 and forming with it a train driven by a drive member not shown, typically a barrel. The escape wheel has impulse teeth 3 intended to periodically give impulse to an oscillator here taking the form of a pendulum of which only the plate 4 and the pin 5 are represented. The gear train 1 comprises rest pads 6 arranged in a circle at the end of the arm extending radially. The exhaust mechanism further comprises a release mobile 7 taking the form of a wheel pivoted on the same axis as the wheel. exhaust. The release mobile 7 comprises rest pins 8 and a unidirectional drive device formed by flexible blades 9 extending radially and bearing against ratchet stops 10 in their rest position. In the embodiment presented, the pawl stops 10 are adjacent to the rest pins but it could be otherwise as will be seen later. The angular amplitude of the rotation of the release mobile 7 relative to the escape wheel 2 is limited by a positioning stop 11, integral with the release mobile 7. A return spring 12 disposed between the escape wheel 2 and the release mobile 7 tends to return the release mobile 7 to an angular position defined with reference to the escape wheel 2.

La figure 2 représente le mécanisme d'échappement au repos, le balancier venant de parcourir librement l'arc supplémentaire et la cheville 5 s'apprêtant à entrer en contact avec une lame flexible 9 du mobile de dégagement 7. Le rouage est à l'arrêt, un plot de repos 6 du mobile de rouage étant en appui contre une cheville de repos 8 du mobile de dégagement 7.The figure 2 represents the exhaust mechanism at rest, the balance coming from freely traversing the additional arc and the pin 5 preparing to come into contact with a flexible blade 9 of the release mobile 7. The train is stopped, a rest pad 6 of the gear train bearing against a rest pin 8 of the release track 7.

La figure 3 représente le mécanisme d'échappement durant la phase de dégagement lors de laquelle le mobile de dégagement 7 se déplace d'une position d'engagement vers une position de dégagement sous l'impulsion du balancier transmise par l'intermédiaire de la lame flexible 9. La lame flexible 9 est en appui contre la butée de cliquet 10 en formant un mécanisme de cliquet de sorte que l'impulsion du balancier provoque la rotation du mobile de dégagement 7 dans le sens antihoraire tel que représenté sur les figures. Pendant la phase de dégagement, les surfaces d'appui du plot de repos 6 et de la cheville de repos 8 glissent l'une contre l'autre. De préférence, les surfaces de contact des chevilles de repos 8 sont des portions de cylindre à base circulaire coaxiales avec l'axe de pivot du mobile de dégagement 7 de façon à ce que le dégagement du mobile de dégagement 7 ne provoque pas d'avance ni de recul du mobile de rouage 1. Cette configuration correspond à un angle de tirage nul. Alternativement la surface des chevilles de repos pourrait présenter un angle de tirage positif pour sécuriser le blocage du mobile de dégagement 7 ou au contraire un angle de tirage négatif pour faciliter son dégagement. Pendant toute la phase de dégagement jusqu'au dégagement complet de la cheville de repos 8, le mobile de rouage 1 est entravé dans sa rotation et ne transmet pas de couple moteur à la roue d'échappement 2 qui reste dans sa position d'attente. Pendant le dégagement, le mobile de dégagement 7 pivote en référence à la roue d'échappement 2 et le ressort de rappel 12 accumule, sous forme élastique, de l'énergie cinétique provenant du balancier.The figure 3 represents the escape mechanism during the disengagement phase during which the disengagement mobile 7 moves from an engagement position to a disengagement position under the impulse of the pendulum transmitted via the flexible blade 9. The flexible blade 9 is in abutment against the pawl stop 10 by forming a pawl mechanism so that the impulse of the pendulum causes the release mobile 7 to rotate counterclockwise as shown in the figures. During the release phase, the bearing surfaces of the rest pad 6 and the rest pin 8 slide against one another. Preferably, the contact surfaces of the rest pegs 8 are cylinder portions with a circular base coaxial with the pivot axis of the release mobile 7 so that the release of the release mobile 7 does not cause advance nor of retraction of the gear train 1. This configuration corresponds to a zero pulling angle. Alternately the surface of the rest pegs could have a positive pull angle to secure the blocking of the release mobile 7 or on the contrary a negative pull angle to facilitate its release. During the entire disengagement phase until the disengagement pin 8 is completely disengaged, the gear train 1 is hampered in its rotation and does not transmit engine torque to the escape wheel 2 which remains in its standby position . During disengagement, the disengagement mobile 7 pivots with reference to the escape wheel 2 and the return spring 12 accumulates, in elastic form, kinetic energy coming from the pendulum.

De façon avantageuse, les bras flexibles 9 et les chevilles de repos 8 sont disposés radialement selon une répartition angulaire régulière de sorte que le mobile de dégagement 7 est équilibré sur son axe de rotation et, de ce fait, peu sensible aux accélérations subies par la pièce d'horlogerie. Par ailleurs, le ressort de rappel 12 tend à maintenir le mobile de dégagement 7 en butée contre la roue d'échappement 2 dans sa position d'engagement. Ainsi il n'est pas nécessaire de prévoir un angle de tirage positif pour sécuriser davantage le mobile de dégagement 7 ce qui permet de minimiser les perturbations causées à l'oscillateur lors du dégagement.Advantageously, the flexible arms 9 and the rest pins 8 are arranged radially at a regular angular distribution so that the release mobile 7 is balanced on its axis of rotation and, therefore, not very sensitive to the accelerations undergone by the timepiece. Furthermore, the return spring 12 tends to keep the release mobile 7 in abutment against the escape wheel 2 in its engagement position. Thus, it is not necessary to provide a positive pull angle to further secure the release mobile 7, which makes it possible to minimize the disturbances caused to the oscillator during the release.

La figure 4 représente le mécanisme d'échappement dans la phase d'impulsion. Une fois que le mobile de dégagement 7 a atteint la position de dégagement, le mobile de rouage est libéré et le rouage démarre sous l'action de l'organe moteur. La roue d'impulsion accélère et la dent d'impulsion 3 la plus proche rattrape la cheville 5 du balancier à qui il transmet alors une parcelle d'énergie pour entretenir son oscillation. Durant au moins une partie de la phase d'accélération de la roue d'échappement, la cheville 5 continue à entrainer le mobile de dégagement 7 par l'intermédiaire de la lame flexible 9 si bien que le mobile de dégagement 7 continue à pivoter à une vitesse sensiblement constante dans le sens antihoraire malgré l'action du ressort de rappel 12. Ainsi, l'énergie stockée sous forme élastique dans le ressort de rappel 12 est-elle restituée et contribue à l'accélération du rouage, le ressort de rappel 12 exerçant un couple moteur sur la roue d'échappement 2 pour la faire accélérer et rattraper le mobile de dégagement 7.The figure 4 represents the escape mechanism in the impulse phase. Once the release mobile 7 has reached the release position, the train mobile is released and the train starts under the action of the drive member. The impulse wheel accelerates and the nearest impulse tooth 3 catches the ankle 5 of the balance wheel to which it then transmits a bit of energy to maintain its oscillation. During at least part of the phase of acceleration of the escape wheel, the pin 5 continues to drive the release mobile 7 by means of the flexible blade 9 so that the release mobile 7 continues to pivot at a substantially constant speed counterclockwise despite the action of the return spring 12. Thus, the energy stored in elastic form in the return spring 12 is it restored and contributes to the acceleration of the train, the return spring 12 exercising a engine torque on the escape wheel 2 to make it accelerate and catch up with the release wheel 7.

La figure 5 représente le mécanisme d'échappement à la fin de la phase d'impulsion et immédiatement avant l'arrêt du rouage provoqué par la rencontre d'un plot de repos 6 avec une cheville de repos 8. Les trajectoires circulaires des plots de repos et des chevilles de repos sont sécantes et le mécanisme est agencé pour qu'un plot 6 rencontre une goupille 8 lorsque le mobile de dégagement 7 est dans la position d'engagement, c'est-à-dire quand la roue d'échappement 2 a rattrapé le mobile de dégagement 7, la butée de positionnement 11 en appui contre la roue d'échappement 2. Par conséquent, l'avance du rouage est limitée lorsque le mobile de dégagement est dans la position d'engagement.The figure 5 represents the escape mechanism at the end of the impulse phase and immediately before stopping the train caused by the meeting of a rest pad 6 with a rest pin 8. The circular paths of the rest pads and rest pins are intersecting and the mechanism is arranged so that a stud 6 meets a pin 8 when the release mobile 7 is in the engagement position, that is to say when the escape wheel 2 has caught up the release mobile 7, the positioning stop 11 pressing against the escape wheel 2. Consequently, the advance of the train is limited when the release mobile is in the engagement position.

La figure 6 représente le mécanisme d'échappement au repos au moment du coup perdu lors de l'alternance suivante. Le balancier pivote dans le sens antihoraire et la cheville 5 écarte le bras flexible 9 sans entrainer en rotation le mobile de dégagement 7. La lame flexible 9 constitue avec la butée de cliquet 10 un système d'entrainement unidirectionnel de type cliquet.The figure 6 represents the exhaust mechanism at rest at the time of the blow lost during the next alternation. The balance pivots counterclockwise and the pin 5 spreads the flexible arm 9 without driving the release mobile 7 in rotation. The flexible blade 9 constitutes, with the ratchet stop 10, a ratchet-type unidirectional drive system.

D'une façon connue, le dos des dents d'impulsion possède un profil circulaire épousant la forme du plateau du balancier pour empêcher le recul accidentel de la roue d'échappement pendant que le balancier parcourt l'arc supplémentaire.In a known manner, the back of the impulse teeth has a circular profile conforming to the shape of the balance plate to prevent accidental retraction of the escape wheel while the balance traverses the additional arc.

De façon originale, le rouage est animé par une double motorisation : l'organe moteur qui propulse le rouage d'une façon conventionnelle, et le ressort de rappel 12 qui tracte la roue d'échappement 2 lors de son démarrage. L'action du ressort de rappel 12 est d'autant plus efficace qu'il est fixé sur le mobile de dégagement 7 qui est lui-même entrainé en rotation par l'oscillateur. Une portion de l'énergie contribuant à l'accélération du rouage provient donc de l'oscillateur ce qui va à l'encontre de l'idée généralement admise qu'il faut éviter de freiner l'oscillateur pour ne pas perturber son isochronisme et limiter la consommation d'énergie. Le transfert de l'énergie de l'oscillateur vers le rouage est optimisé grâce au mobile de dégagement 7 et au ressort de rappel 12 qui joue le rôle d'amortisseur et limite la perte d'énergie au moment du choc de la cheville sur le bras flexible. L'accélération du rouage est donc donnée sans à-coup mais comme elle est plus forte que celle qui serait donnée par un seul organe moteur, le temps nécessaire à la roue d'échappement 2 pour rattraper la cheville 5 du balancier est réduit. Cela signifie que le dispositif peut fonctionner à des fréquences plus élevées mais aussi que l'angle d'impulsion parcouru par le balancier dans la phase d'impulsion est plus grand. Alternativement il est possible de profiter de la double motorisation et de l'angle d'impulsion élargi pour réduire la puissance de l'organe moteur afin d'augmenter son autonomie.In an original way, the train is driven by a double motorization: the motor member which propels the train in a conventional manner, and the return spring 12 which tows the escape wheel 2 when it starts up. The action of the return spring 12 is all the more effective when it is fixed on the release mobile 7 which is itself driven in rotation by the oscillator. A portion of the energy contributing to the acceleration of the train therefore comes from the oscillator which goes against the generally accepted idea that it is necessary to avoid braking the oscillator so as not to disturb its isochronism and limit energy consumption. The transfer of energy from the oscillator to the gear train is optimized thanks to the movable release 7 and the return spring 12 which acts as a shock absorber and limits the loss of energy when the ankle hits the flexible arm. The acceleration of the train is therefore given smoothly, but since it is stronger than that which would be given by a single drive member, the time required for the escape wheel 2 to catch up with the ankle 5 of the balance wheel is reduced. This means that the device can operate at higher frequencies but also that the pulse angle traveled by the balance in the pulse phase is greater. Alternatively, it is possible to take advantage of the dual motorization and the widened pulse angle to reduce the power of the motor unit in order to increase its autonomy.

De façon originale, l'arrêt du rouage est causé par la rencontre de deux éléments mobiles en référence au bâti, cinématiquement liés de façon discontinue.In an original way, the stopping of the train is caused by the meeting of two mobile elements with reference to the frame, kinematically linked in a discontinuous manner.

Contrairement à une bascule de détente qui effectue un mouvement de va-et-vient en dissipant l'énergie qu'elle reçoit du balancier, le mobile de dégagement pivote toujours dans le même sens qui est également celui de l'impulsion donnée par l'oscillateur ainsi que celui du déplacement de la roue d'échappement. L'énergie accumulée sous forme élastique à chaque dégagement dans le ressort de rappel est restituée lors du démarrage de la roue d'échappement. La récupération d'une partie de l'énergie prise à l'oscillateur dans la phase de dégagement caractérise un nouveau type d'échappement que l'on peut désigner par le terme de « turbo-détente », Celui-ci présentant des performances intéressantes en termes de rendement énergétique ainsi que de fréquence et de sureté de fonctionnement.Unlike a trigger rocker which performs a back and forth movement by dissipating the energy it receives from the balance, the release mobile always pivots in the same direction which is also that of the impulse given by the oscillator as well as the displacement of the escape wheel. The energy accumulated in elastic form at each release in the return spring is restored when the escape wheel starts. The recovery of part of the energy taken from the oscillator in the release phase characterizes a new type of exhaust that can be designated by the term of "turbo-expansion", This one presenting interesting performances in terms of energy efficiency as well as frequency and dependability.

Selon une variante non représentée du premier mode de réalisation, le plateau du balancier comporte une cheville qui effectue le dégagement et une palette d'impulsion, distincte de la cheville, agencée pour recevoir l'impulsion de la roue d'échappement. Les positions angulaires et radiales respectives de la cheville et de la palette par rapport à l'axe du balancier, définissent le début des phases de dégagement et d'impulsion et les vitesses angulaires de dégagement et d'impulsion. Pour raccourcir la phase de dégagement il est par exemple possible d'augmenter la vitesse angulaire du mobile de dégagement en éloignant la cheville 5 de l'axe du balancier alors que la palette d'impulsion en reste proche. Dans cette configuration, la vitesse angulaire du mobile d'échappement est plus élevée que la vitesse atteinte par la roue d'échappement au début de l'impulsion. L'homme du métier saura configurer le mécanisme de sorte que l'entrainement du mobile de dégagement 7 prenne fin avant le début de l'impulsion. Dans le laps de temps précédent l'impulsion où le mobile d'échappement n'est plus entrainé, ce dernier ralentit sous l'action du ressort de rappel en contribuant à l'accélération du rouage. A l'instar d'un relais entre deux coureurs d'américaine, le transfert d'énergie cinétique entre le mobile de dégagement et le rouage s'opère sans choc grâce à l'action du ressort de rappel 12. Ainsi le mécanisme d'échappement selon l'invention peut être agencé de manière à ce que l'énergie cinétique acquise par le mobile de dégagement lors de la phase de dégagement soit au moins partiellement restituée et contribue à l'accélération du rouage.According to a variant not shown of the first embodiment, the balance plate comprises a pin which performs the release and a pulse pallet, distinct from the pin, arranged to receive the pulse of the escape wheel. The respective angular and radial positions of the dowel and the pallet with respect to the pendulum axis, define the start of the release and impulse phases and the angular speeds of release and impulse. To shorten the release phase, it is for example possible to increase the angular speed of the release mobile by moving the pin 5 away from the pendulum axis while the impulse palette remains close to it. In this configuration, the angular speed of the escape wheel is higher than the speed reached by the escape wheel at the start of the pulse. Those skilled in the art will be able to configure the mechanism so that the drive of the release mobile 7 ends before the start of the pulse. In the period of time preceding the impulse where the exhaust mobile is no longer driven, the latter slows down under the action of the return spring, contributing to the acceleration of the train. Like a relay between two American runners, the transfer of kinetic energy between the release mobile and the gear train operates without shock thanks to the action of the return spring 12. Thus the mechanism of exhaust according to the invention can be arranged so that the kinetic energy acquired by the release mobile during the release phase is at least partially restored and contributes to the acceleration of the train.

L'homme du métier saura apporter d'autres variantes d'exécution à ce premier mode de réalisation sans sortir du cadre des revendications. En particulier, le dispositif d'entrainement unidirectionnel pourrait être placé sur l'oscillateur. Plutôt que d'être pivoté sur le bâti, Le mobile de dégagement pourrait être relié à la roue d'échappement par des éléments flexibles. Dans ce cas, le mouvement de dégagement du mobile de dégagement sous l'action de l'oscillateur pourrait être assimilé à une rotation où à toute autre trajectoire adaptée au dégagement des chevilles de repos. Ces mêmes éléments flexibles pourraient également jouer le rôle de ressort de rappel.Those skilled in the art will be able to provide other alternative embodiments to this first embodiment without departing from the scope of the claims. In particular, the unidirectional drive device could be placed on the oscillator. Rather than being pivoted on the frame, the release mobile could be connected to the escape wheel by flexible elements. In this case, the disengagement movement of the disengagement mobile under the action of the oscillator could be assimilated to a rotation or to any other trajectory adapted to the disengagement of the rest pins. These same flexible elements could also play the role of return spring.

Les figures 7 à 12 représentent un deuxième mode de réalisation d'un mécanisme d'échappement selon l'invention. Comme dans le premier mode de réalisation on retrouve un rouage formé d'un mobile de rouage 1 et d'une roue d'échappement 2 reliés cinématiquement l'un à l'autre ainsi qu'un balancier dont est visible le plateau 4 muni de sa cheville 5. Le mécanisme comporte également un dispositif d'entrainement unidirectionnel composé d'une pluralité de lames flexibles 9 en butée sur des butées de cliquet 10. Le dispositif d'entrainement unidirectionnel est ici monté solidaire de la roue d'échappement 2. De façon originale la roue d'échappement n'est pas pivotée sur le bâti de la pièce d'horlogerie mais sur le mobile de dégagement 7 qui prend ici la forme d'une bascule pivotée sur le même axe que le mobile de rouage 1. Le mécanisme comporte également une butée de positionnement 11 apte à positionner le mobile de dégagement 7 dans une position d'engagement dans laquelle la rotation de la roue d'échappement est limitée. Lorsque le mobile de dégagement est dans sa position d'engagement, les axes de rotation du mobile de rouage 1, de la roue d'échappement et du balancier sont coplanaires. L'organe moteur, non représenté, tend à entrainer le mobile de rouage 1 dans le sens horaire en référence aux figures.The Figures 7 to 12 represent a second embodiment of an exhaust mechanism according to the invention. As in the first embodiment, there is a cog formed of a cog wheel 1 and an escape wheel 2 kinematically connected to each other as well as a balance of which the plate 4 provided with his ankle 5. The mechanism also includes a unidirectional drive device composed of a plurality of flexible blades 9 abutting on ratchet stops 10. The unidirectional drive device is here mounted integral with the escape wheel 2. In an original way the wheel is not pivoted on the frame of the timepiece but on the release mobile 7 which here takes the form of a rocker pivoted on the same axis as the gear train 1. The mechanism also includes a positioning stop 11 able to position the release mobile 7 in an engagement position in which the rotation of the escape wheel is limited. When the disengaging mobile is in its engagement position, the axes of rotation of the driving mobile 1, of the escape wheel and of the balance are coplanar. The drive member, not shown, tends to drive the gear train 1 clockwise with reference to the figures.

Dans la configuration de la figure 8, le balancier parcourt librement l'arc supplémentaire et le rouage est à l'arrêt, une dent d'impulsion 3 de la roue d'échappement étant en appui contre une palette de repos 13 fixe en référence au bâti.In the configuration of the figure 8 , the pendulum travels freely through the additional arc and the gear train is stopped, a pulse tooth 3 of the escapement wheel being in abutment against a fixed rest pallet 13 with reference to the frame.

La figure 9 représente le mécanisme d'échappement dans la phase de dégagement. La cheville de plateau 5 a percuté une lame flexible 9 en appui sur une butée de cliquet 10. La rotation de la roue d'échappement 2 étant entravée par la palette de repos 13, c'est l'ensemble composé du mobile de dégagement 7, de la roue d'échappement 2 et du mobile de rouage 1 qui est entrainé en rotation dans le sens antihoraire autour de l'axe de pivot du mobile de rouage. Le recul du rouage dans la phase de dégagement entraine le ré-armage de l'organe moteur si bien que l'énergie fournie par l'oscillateur lors du dégagement est stockée sous forme élastique par l'organe moteur avant d'être restituée pour propulser le rouage. Dès que la dent en prise quitte la palette de repos 13, la roue d'échappement 2 et le rouage sont libérés. Le rouage accélère et le mobile de dégagement 7 revient dans sa position d'engagement contre la butée de positionnement 11. Le plan de repos de la palette de repos est de préférence un plan orthoradial en référence à l'axe de rotation du mobile de dégagement qui correspond à un angle de tirage nul. Alternativement, le plan de repos peut avoir une inclinaison différente ou un profil non rectiligne.The figure 9 represents the escape mechanism in the release phase. The plate pin 5 struck a flexible blade 9 bearing on a ratchet stop 10. The rotation of the escape wheel 2 being hampered by the rest pallet 13, it is the assembly composed of the release mobile 7 , of the escape wheel 2 and of the gear train 1 which is rotated counterclockwise around the pivot axis of the gear train. The retraction of the train in the disengagement phase causes the motor organ to be rearmed so that the energy supplied by the oscillator during the disengagement is stored in elastic form by the motor organ before being returned to propel the cog. As soon as the engaged tooth leaves the rest pallet 13, the escape wheel 2 and the gear train are released. The train accelerates and the release mobile 7 returns to its position of engagement against the positioning stop 11. The rest plane of the rest pallet is preferably an orthoradial plane with reference to the axis of rotation of the release mobile which corresponds to a zero drawing angle. Alternatively, the rest plane may have a different inclination or a non-rectilinear profile.

La figure 10 représente le mécanisme d'échappement dans la phase d'impulsion après que le mobile de dégagement 7 est revenu dans sa position d'engagement en appui contre la butée de positionnement 11 et qu'une dent d'impulsion 3 de la roue d'échappement 2 a rattrapé la cheville 5 du balancier.The figure 10 represents the escape mechanism in the impulse phase after the release mobile 7 has returned to its engagement position in abutment against the positioning stop 11 and that a pulse tooth 3 of the escape wheel 2 caught up with the pendulum pin 5.

La figure 11 représente le mécanisme à la fin de la phase d'impulsion et juste avant l'arrêt du rouage provoqué par la rencontre de la dent d'impulsion 3 suivante avec la palette de repos 13.The figure 11 represents the mechanism at the end of the pulse phase and just before stopping the train caused by the meeting of the next pulse tooth 3 with the rest pallet 13.

La figure 12 montre le mécanisme au repos lors du coup perdu au retour du balancier au moment du passage du cliquet.The figure 12 shows the mechanism at rest during the lost blow when the pendulum returns when the ratchet passes.

Comme dans le premier mode de réalisation, l'énergie fournit par l'oscillateur lors du dégagement est au moins partiellement restituée pour entrainer le rouage. De façon originale ce deuxième mode de réalisation utilise directement l'organe moteur pour stocker temporairement, sous forme élastique, l'énergie provenant de l'oscillateur lors du dégagement. C'est aussi la force motrice qui maintient le mobile de dégagement 7 dans la position d'engagement. A noter que dans les échappements de l'art antérieur, le rouage recule légèrement lors du dégagement lorsque l'angle de tirage est positif, cette disposition ayant pour but de sécuriser la détente et non pas de récupérer de l'énergie.As in the first embodiment, the energy supplied by the oscillator during the release is at least partially returned to drive the train. In an original way, this second embodiment directly uses the motor member to temporarily store, in elastic form, the energy coming from the oscillator during the release. It is also the driving force which keeps the release mobile 7 in the engagement position. Note that in the exhausts of the prior art, the gear train recedes slightly during the release when the pull angle is positive, this arrangement having the aim of securing the trigger and not of recovering energy.

De façon originale c'est le déplacement de l'axe de la roue d'échappement et non le déplacement de la palette de repos, qui provoque le dégagement.In an original way it is the displacement of the axis of the escape wheel and not the displacement of the rest pallet, which causes the release.

L'homme du métier saura apporter des variantes d'exécution à ce deuxième mode de réalisation sans sortir du cadre des revendications. En particulier, le dispositif d'entrainement unidirectionnel pourrait ne comporter qu'un seul cliquet et être solidaire du mobile de dégagement ou de l'oscillateur. Les fonctions de dégagement et d'impulsion pourraient être assurées par des dents distinctes sur la roue d'échappement et par des palettes distinctes sur l'oscillateur. Le mobile d'échappement pourrait être translaté plutôt qu'être pivoté. Il pourrait également être relié au bâti par un élément flexible. Le mobile de dégagement pourrait comporter un contre poids afin que l'ensemble mobile qu'il compose avec la roue d'échappement soit équilibré sur son axe de rotation. Le mécanisme pourrait comporter une deuxième butée pour limiter l'amplitude du déplacement du mobile de dégagement ainsi qu'un ressort de rappel pour accélérer le retour du mobile de dégagement dans sa position d'engagement. Le mécanisme pourrait également comporter un dispositif de sécurité qui limiterait le déplacement du mobile de dégagement dans les phases de libre oscillation de l'oscillateur.Those skilled in the art will be able to provide alternative embodiments to this second embodiment without departing from the scope of the claims. In particular, the unidirectional drive device could comprise only one pawl and be secured to the release mobile or to the oscillator. The release and impulse functions could be provided by separate teeth on the escape wheel and by separate paddles on the oscillator. The exhaust mobile could be translated rather than rotated. It could also be connected to the frame by a flexible element. The release mobile could have a counterweight so that the mobile assembly that it composes with the escape wheel is balanced on its axis of rotation. The mechanism could include a second stop to limit the amplitude of the movement of the release mobile as well as a return spring to accelerate the return of the release mobile to its engagement position. The mechanism could also include a safety device which would limit the movement of the release mobile in the free oscillation phases of the oscillator.

Ainsi est proposé un type nouveau de mécanisme d'échappement pour montre mécanique, qui présente les avantages des échappements à ancre et des échappements à détente sans en posséder les inconvénients.Thus a new type of escapement mechanism for a mechanical watch is proposed, which has the advantages of anchor escapements and detent escapements without having the disadvantages.

Claims (15)

  1. Free lost-shot escape mechanism for a timepiece, said timepiece comprising:
    - a gearwheel intended to be driven by a drive member and comprising a gear wheel (1) which is rotatable about an axis of rotation and arranged in kinematic connection with at least one escape wheel of the escape mechanism,
    - an oscillator adapted to receive an impulse from said escape wheel (2) in order to sustain its oscillations, said escape mechanism further comprising:
    - a release mobile (7) arranged to cooperate in rotation with the escape wheel and to move, during a release phase, under an impulse from the oscillator, between an engagement position in which the advance of the gear is blocked and a release position in which the advance of the gear is free, and
    - a unidirectional drive device for the release mobile (7) arranged to transmit said oscillator impulse to the release mobile (7) from the engagement position to the release position,
    the escape mechanism being characterised in that the release mobile (7) and the unidirectional drive device are arranged to cooperate with means (10, 12) configured to accumulate a portion of the energy supplied by an oscillator impulse upon release of the release mobile (7) on the one hand and to restore it in the form of an acceleration of the escape wheel (2) upon transmission by the escape wheel (2) of a impulse to the oscillator on the other hand.
  2. Escape mechanism according to claim 1, characterised in that the release mobile (7) and the gear wheel (1) are arranged relative to each other in such a way that there is a zero or negative draft between them.
  3. Escape mechanism according to one of claims 1 or 2, characterised in that the gear wheel (1) and the release mobile (7) are arranged so that said portion of energy transmitted by the oscillator in the release phase is accumulated in an elastic form before contributing to the acceleration of said escape wheel (2).
  4. Escape mechanism according to one of the preceding claims, characterised in that it comprises a positioning stop (11) capable of positioning the release mobile (7) in the engagement position.
  5. Escape mechanism according to one of the preceding claims, characterised in that the axes of rotation of the gear wheel (1), the escape wheel (2) and the release mobile (7) are parallel and coplanar.
  6. Escape mechanism according to one of the preceding claims, characterised in that the oscillator is rotatable about an axis and in that the axes of rotation of the oscillator, of the gear wheel (1), of the escape wheel (2) and of the release mobile (7) are parallel and coplanar when the release mobile (7) is in the engagement position.
  7. Escape mechanism according to one of the preceding claims, characterised in that the unidirectional drive device comprises a plurality of flexible blades (9) each arranged to bear on a pawl stop (10), said flexible blades (9) and pawl stops (10) being arranged radially in a regular angular distribution.
  8. Escape mechanism according to one of claims 1 to 7, characterised in that the unidirectional drive is integral with the release (7) or oscillator.
  9. Escape mechanism according to one of the preceding claims, characterised in that the release mobile (7) is coaxial with the escape wheel (2).
  10. Escape mechanism according to claim 9 and claim 4, characterised in that it comprises a resilient member, in particular a return spring (12), mounted between the release mobile (7) and the escape wheel (2), and which tends to return the release mobile (7) to its engagement position, preferably against the positioning stop (11) in the engagement position.
  11. Escape mechanism according to one of claims 9 or 10, characterised in that the release mobile (7) has rest pins (8), in that the gear wheel (1) has rest studs (6), in that the trajectories of the rest studs (6) and of the rest pins (8) are intersecting and in that the mechanism is arranged so that the rest studs (6) meet the rest pins (8) causing the gearing to stop when the release mobile (7) is in the engagement position.
  12. Escape mechanism according to one of claims 1 to 7, characterised in that the unidirectional drive is integral with the escape wheel (2).
  13. Escape mechanism according to one of claims 1 to 10 or claim 12, characterised in that the escape wheel (2) is mounted movably on the release mobile (7) and in that the escape wheel (2) comprises rest teeth (3) intended to come to rest against a rest pallet (13) fixed with reference to the frame of the timepiece.
  14. Escape mechanism according to claim 13, characterised in that the release mobile (7) is a rocker pivoted on the axis of the gear wheel (1).
  15. Escape mechanism according to claims 4 and 14, characterised in that the positioning stop (11) is fixed with reference to the rotation axis of the release mobile (7) .
EP17761283.5A 2016-09-07 2017-09-06 Escapement mechanism Active EP3510449B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16187711.3A EP3293583A1 (en) 2016-09-07 2016-09-07 Escapement mechanism
PCT/EP2017/072392 WO2018046563A1 (en) 2016-09-07 2017-09-06 Escapement mechanism

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EP3510449A1 EP3510449A1 (en) 2019-07-17
EP3510449B1 true EP3510449B1 (en) 2020-07-08

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Application Number Title Priority Date Filing Date
EP16187711.3A Withdrawn EP3293583A1 (en) 2016-09-07 2016-09-07 Escapement mechanism
EP17761283.5A Active EP3510449B1 (en) 2016-09-07 2017-09-06 Escapement mechanism

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Application Number Title Priority Date Filing Date
EP16187711.3A Withdrawn EP3293583A1 (en) 2016-09-07 2016-09-07 Escapement mechanism

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EP (2) EP3293583A1 (en)
WO (1) WO2018046563A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020007619A2 (en) * 2018-07-02 2020-01-09 Complitime Sa Timepiece escapement mechanism
DE102018212113A1 (en) * 2018-07-20 2020-01-23 Creaditive Ag Inhibitor system and the inhibitor system comprehensive measuring device
EP4250019A1 (en) * 2022-03-21 2023-09-27 Patek Philippe SA Genève Timepiece oscillator for extra-flat movement

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1538490B1 (en) * 2003-12-04 2007-05-30 Montres Breguet S.A. Detent escapement for wrist-watches
ATE487963T1 (en) * 2003-12-04 2010-11-15 Montres Breguet Sa CHRONOMETER ESCAPEMENT FOR WATCHES
EP1710636A1 (en) * 2005-04-06 2006-10-11 Daniel Rochat Escapement for a watch
EP1770452A1 (en) * 2005-09-30 2007-04-04 Peter Baumberger Detent escapement for timepieces
EP2199875B1 (en) * 2008-12-16 2014-09-24 Rolex Sa Detent escapement
JP5366319B2 (en) * 2009-09-14 2013-12-11 セイコーインスツル株式会社 Detent escapement and mechanical watch having the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
EP3510449A1 (en) 2019-07-17
EP3293583A1 (en) 2018-03-14
WO2018046563A1 (en) 2018-03-15

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