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EP3869278A1 - Vertical clutch device for a timepiece - Google Patents

Vertical clutch device for a timepiece Download PDF

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Publication number
EP3869278A1
EP3869278A1 EP20217971.9A EP20217971A EP3869278A1 EP 3869278 A1 EP3869278 A1 EP 3869278A1 EP 20217971 A EP20217971 A EP 20217971A EP 3869278 A1 EP3869278 A1 EP 3869278A1
Authority
EP
European Patent Office
Prior art keywords
vertical
clutch device
force
wheel
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20217971.9A
Other languages
German (de)
French (fr)
Other versions
EP3869278B1 (en
Inventor
M. Polychronis Nakis KARAPATIS
Marc Stranczl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Montres Breguet SA
Original Assignee
Montres Breguet SA
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Publication date
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Publication of EP3869278A1 publication Critical patent/EP3869278A1/en
Application granted granted Critical
Publication of EP3869278B1 publication Critical patent/EP3869278B1/en
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Classifications

    • 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
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/006—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices)
    • G04B11/008—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices) with friction members, e.g. click springs or jumper
    • 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
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/001—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power
    • G04B11/003—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power with friction member, e.g. with spring action
    • 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
    • G04B19/00—Indicating the time by visual means
    • G04B19/02—Back-gearing arrangements between gear train and hands
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C9/00—Alloys based on copper
    • C22C9/01—Alloys based on copper with aluminium as the next major constituent
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C9/00—Alloys based on copper
    • C22C9/04—Alloys based on copper with zinc as the next major constituent
    • 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
    • G04B19/00—Indicating the time by visual means
    • G04B19/04—Hands; Discs with a single mark or the like
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G—PHYSICS
    • G04—HOROLOGY
    • G04F—TIME-INTERVAL MEASURING
    • G04F7/00—Apparatus for measuring unknown time intervals by non-electric means
    • G04F7/04—Apparatus for measuring unknown time intervals by non-electric means using a mechanical oscillator
    • G04F7/08—Watches or clocks with stop devices, e.g. chronograph
    • G04F7/0823—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement
    • G04F7/0833—Watches or clocks with stop devices, e.g. chronograph with couplings between the chronograph mechanism and the base movement acting perpendicular to the plane of the movement

Definitions

  • the present invention relates to a vertical clutch device for a timepiece, more particularly for a chronograph.
  • Disengaging devices are used in the field of watchmaking and in particular for chronographs.
  • the chronograph wheel which carries the chronograph hand is connected to the seconds wheel via a clutch.
  • the clutch can occupy an engaged position, corresponding to the chronograph running position, where the chronograph wheel is driven by the seconds wheel, and a disengaged position, corresponding to the chronograph stop position, where the chronograph wheel. chronograph is not driven by the seconds wheel.
  • the operation of a vertical clutch device 1 within a partially shown chronograph mechanism 8 is illustrated in figures 1a and 1b for the disengaged position and the engaged position respectively.
  • the clutch device generally comprises on the same axis a first wheel 3, a second wheel 2 and a clutch disc 4.
  • the first wheel 3 is the driving element which rotates continuously and which is in mesh with the control wheel.
  • seconds 9. The second wheel 2 is engaged with the chronograph wheel 10.
  • the clutch disc 4 cooperates with a pair of grippers 5, the opening and closing of which is controlled by a column wheel (not shown). Closing the clamps 5 raises the clutch disc 4 against the action of a spring 6 as shown diagrammatically on figure 1a . In this disengaged position, the clutch disc 4 is not in contact with the first wheel 3 with the corollary that the second wheel 2 is not driven. When opening the clamps 5, the disc clutch 4 comes to press against the first wheel 3 under the action of the spring 6 ( fig.1b ). In this engaged position, the first wheel 3 drives the second wheel 2 by friction. In order for the friction to be sufficient, the engaged force F must be large, i.e. that a significant preload must be applied to the spring.
  • the springs are made from standard materials such as steel which exhibit elastic behavior over a few tenths of a percent before entering the plastics field.
  • the spring In operation, the spring must work within its elastic range to avoid any irreversible deformation. In this elastic range, the spring has a linear behavior with a return force proportional to the displacement.
  • the figure 2 typically represents the force-displacement curve in the elastic domain.
  • the engaged force (F e ) is fixed by the preload applied (displacement p) on the spring and the disengaged force (F d ) is fixed by the displacement (d) required to move the clutch disc away from the first wheel.
  • the spring works at the limit of its elastic capacities because it is subjected to a significant preload with a risk of plastic deformation during movement when disengaged. Besides the risk of inducing irreversible deformation of the spring, these large deformations cause premature fatigue of the spring. Moreover, the behavior of the spring being linear in the elastic range, any increase in the engaged force leads to an increase in the disengaged force which will have to be supplied by the clamps.
  • the distance of the clutch disc from the first wheel by a distance d requires a significant force F d of 1.5 N to counter the spring return force.
  • the disengaged force F d is thus more than two times greater than the engaged force F e .
  • the object of the present invention is to provide a clutch device providing a maximized engaged force for a disengaged force which, in turn, is minimized.
  • the object of the invention is to reduce the ratio between the disengaged force and the engaged force.
  • the present invention provides a clutch device comprising a spring made of a shape memory alloy used at room temperature for its superelasticity properties.
  • the spring made of a shape memory alloy has a nonlinear behavior in the elastic domain with a stress which peaks at an almost constant value over a wide range of deformation. These properties of superelasticity and this nonlinear behavior make it possible to easily adjust the disengaged force and the engaged force according to the required operating conditions. Thus, a significant preload can be applied to the spring without the risk of entering the plastic domain when the mechanism is disengaged.
  • the spring is no longer stressed to the limit of its elastic capacities unlike the spring of the prior art, which makes it possible to avoid premature fatigue of the spring in use.
  • the disengaged force can be minimized by requesting the spring in the field where the constraint, and therefore the force, tops out at an almost constant value.
  • the spring can be sized to increase the engaged force while maintaining an equivalent disengaged force or conversely be dimensioned to reduce the disengaged force while maintaining an equivalent engaged force.
  • the ratio between the disengaged force and the engaged force is between 1.1 and 2.0.
  • the invention relates to a clutch device comprising a spring made of a shape memory alloy. It relates more specifically to a clutch device intended to equip a chronograph mechanism 8 with a timepiece 11 ( fig.7 ).
  • the superelasticity properties of the shape memory alloy are used to reduce the difference between the engaged force and the disengaged force.
  • the figure 3 illustrates the superelastic behavior of a shape memory alloy which exhibits at room temperature an austenitic structure which transforms into martensite under the application of a stress ⁇ , which makes it possible to deform the material in a reversible manner by several percent.
  • the tensile curve first presents an elastic linear behavior up to a critical stress where the martensitic transformation induces a superelastic behavior with an increasing strain under an almost constant stress. This is the plateau that we observe on the figure 3 . As soon as the stress is released, the reverse transformation from martensite to austenite takes place and the alloy returns to its original dimension.
  • a spring made of this material makes it possible to obtain a stress, and therefore a force, as a function of the displacement which is not proportional but tops out at a certain value on the plateau of the curve unlike a conventional material such as l 'steel.
  • the nickel-titanium-based alloy consists of nickel, with a weight percentage between 52.5 and 63%, and titanium with a percentage by weight between 36.5 and 47%, for a total percentage of 100% and a possible impurity content less than or equal to 0.5%.
  • This alloy exhibits at room temperature, in the absence of constraints, an austenitic microstructure.
  • the spring 6 comprises a central annular part 6a and several tabs 6b starting from said central annular part 6a as illustrated in figure 5a .
  • the number of tabs can be 3.
  • the thickness of the spring is between 0.05 and 0.4 mm.
  • the tabs 6b are inclined relative to the plane defined by the central annular part 6a as shown diagrammatically in figures 1a and 1b . Depending on the level of preload applied to the dropouts in the engaged position ( fig.1b ), the latter are more or less inclined with respect to the plane of the annular part.
  • the spring 6 is arranged within the clutch device 1 as previously described with reference to figures 1a and 1b with the clutch disc 4, the first wheel 3 and the second wheel 2.
  • the sizing of the spring namely the number of legs, the active length of each leg and the section of the legs will define the corresponding force-displacement curve of the spring produced. in this material as shown schematically on figure 6 for the dotted curve.
  • the spring is sized to work with a disengaged force F d which is on the upper bearing of the hysteresis and with an engaged force F e which is on the lower bearing of the hysteresis.
  • F d disengaged force which is on the upper bearing of the hysteresis
  • an engaged force F e which is on the lower bearing of the hysteresis.
  • the shape of the hysteresis can vary depending on the shade chosen for the shape memory alloy.
  • the force on the upper bearing and the lower bearing can be more or less constant depending on the chosen shade.
  • the spring operates in a pre-stressed mode with the deformation of the spring, and advantageously of the legs of the spring, which defines the engaged force F e on the lower bearing.
  • the engaged force can thus be adjusted depending on the preload applied to the spring. As the material is superelastic, a significant pre-stress can be applied without the risk of plastically deforming the spring.
  • the disengaged force F d can be adjusted according to the minimum displacement d required to avoid any contact between the clutch disc and the first wheel.
  • the ratio between the disengaged force and the engaged force is minimized and between 1.1 and 2.0, preferably between 1.3 and 1.6.
  • the vertical force F d is between 1 and 3 N and the vertical force F e is between 0.5 and 2 N, with F d greater than F e , for a vertical displacement d between the engaged position and the disengaged position between 0.05 and 0.3 mm.
  • Another way to define the nonlinear superelastic behavior of the spring in use is to characterize it as a function of its rigidity which is not constant during deformation.
  • the slope of the line connecting the origin of the XY axes to the point (F e , p) is greater than the slope of the line connecting the origin of the XY axes to the point (F d , p + d).
  • the angle ⁇ 2 is greater than the angle ⁇ 1 .
  • the present invention is illustrated with the aid of an example and figures 4 to 6 .
  • the figure 4 represents the mechanical properties of the shape memory alloy based on nickel and titanium with the aforementioned composition.
  • the figure 6 represents the corresponding force-displacement curve for a spring made of this alloy and having the dimensions related to the figure 5a .
  • This spring has a thickness of 0.2 mm and has three tabs with a length of 0.85 mm for a width of 0.06 mm. After insertion between the sleeve 7 of the chronograph axis and the second wheel 2, the active length of each tab is approximately 0.5 mm ( fig.5b ).
  • a disengaged force F d of 1.5 N was chosen with the same disengagement stroke d of 0.1 mm.
  • the engaged force F e could be maximized at 1.05 N, corresponding to a preload distance p 0.15 mm, compared to 0.67 N for steel, which ensures that the clutch does not slip.
  • the ratio of disengaged force to engaged force amounts to 1.4 compared to 2.2 for steel.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Materials Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Mechanical Operated Clutches (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
  • Springs (AREA)

Abstract

La présente invention concerne un dispositif d'embrayage vertical (1) pour une pièce d'horlogerie, comprenant le long d'un axe vertical (12) une première roue (3) montée rotative autour dudit axe vertical (12), un disque d'embrayage (4), un ressort (6) et une seconde roue (2) montée rotative autour dudit axe vertical (12), ledit dispositif d'embrayage vertical (1) pouvant adopter une position embrayée où la seconde roue (2) est entraînée en rotation par la première roue (3) sous l'action du ressort (6) exerçant une force verticale Fe pour plaquer le disque d'embrayage (4) contre la première roue (3) et une position débrayée où le disque d'embrayage (4) est soumis contre l'action du ressort (6) à une force verticale Fd l'écartant de la première roue (3) de manière que la seconde roue (2) ne soit pas entraînée en rotation par la première roue (3), ledit dispositif d'embrayage vertical (1) étant caractérisé en ce que le ressort (6) est réalisé dans un alliage à mémoire de forme.

Figure imgaf001
The present invention relates to a vertical clutch device (1) for a timepiece, comprising along a vertical axis (12) a first wheel (3) rotatably mounted around said vertical axis (12), a disc of 'clutch (4), a spring (6) and a second wheel (2) rotatably mounted about said vertical axis (12), said vertical clutch device (1) being able to assume an engaged position where the second wheel (2) is driven in rotation by the first wheel (3) under the action of the spring (6) exerting a vertical force F e to press the clutch disc (4) against the first wheel (3) and a disengaged position where the disc d the clutch (4) is subjected against the action of the spring (6) to a vertical force F d away from the first wheel (3) so that the second wheel (2) is not rotated by the first wheel (3), said vertical clutch device (1) being characterized in that the spring (6) is made of a shape memory alloy.
Figure imgaf001

Description

Domaine de l'inventionField of the invention

La présente invention concerne un dispositif d'embrayage vertical pour une pièce d'horlogerie, plus particulièrement pour un chronographe.The present invention relates to a vertical clutch device for a timepiece, more particularly for a chronograph.

Arrière-plan de l'inventionBackground of the invention

Des dispositifs de débrayage sont utilisés dans le domaine de l'horlogerie et en particulier pour les chronographes. Dans un chronographe, la roue de chronographe qui porte l'aiguille de chronographe est reliée à la roue de secondes par l'intermédiaire d'un embrayage. L'embrayage peut occuper une position embrayée, correspondant à la position de marche du chronographe, où la roue de chronographe est entraînée par la roue de secondes, et une position débrayée, correspondant à la position d'arrêt du chronographe, où la roue de chronographe n'est pas entraînée par la roue de secondes. Le fonctionnement d'un dispositif d'embrayage vertical 1 au sein d'un mécanisme de chronographe 8 partiellement représenté, est illustré aux figures 1a et 1b pour respectivement la position débrayée et la position embrayée. Le dispositif d'embrayage comprend généralement sur un même axe une première roue 3, une seconde roue 2 et un disque d'embrayage 4. La première roue 3 est l'élément moteur qui tourne en permanence et qui est en prise avec la roue de secondes 9. La seconde roue 2 est en prise avec la roue de chronographe 10. Le disque d'embrayage 4 coopère avec une paire de pinces 5 dont l'ouverture et la fermeture est commandée par une roue à colonnes (non représentée). La fermeture des pinces 5 vient soulever le disque d'embrayage 4 contre l'action d'un ressort 6 comme schématisé à la figure 1a. Dans cette position débrayée, le disque d'embrayage 4 n'est pas en contact avec la première roue 3 avec pour corollaire que la seconde roue 2 n'est pas entraînée. Lors de l'ouverture des pinces 5, le disque d'embrayage 4 vient se plaquer contre la première roue 3 sous l'action du ressort 6 (fig.1b). Dans cette position embrayée, la première roue 3 entraîne la seconde roue 2 par friction. Afin que la friction soit suffisante, la force embrayée Fedoit être importante, c.à.d. qu'une précontrainte importante doit être appliquée sur le ressort.Disengaging devices are used in the field of watchmaking and in particular for chronographs. In a chronograph, the chronograph wheel which carries the chronograph hand is connected to the seconds wheel via a clutch. The clutch can occupy an engaged position, corresponding to the chronograph running position, where the chronograph wheel is driven by the seconds wheel, and a disengaged position, corresponding to the chronograph stop position, where the chronograph wheel. chronograph is not driven by the seconds wheel. The operation of a vertical clutch device 1 within a partially shown chronograph mechanism 8 is illustrated in figures 1a and 1b for the disengaged position and the engaged position respectively. The clutch device generally comprises on the same axis a first wheel 3, a second wheel 2 and a clutch disc 4. The first wheel 3 is the driving element which rotates continuously and which is in mesh with the control wheel. seconds 9. The second wheel 2 is engaged with the chronograph wheel 10. The clutch disc 4 cooperates with a pair of grippers 5, the opening and closing of which is controlled by a column wheel (not shown). Closing the clamps 5 raises the clutch disc 4 against the action of a spring 6 as shown diagrammatically on figure 1a . In this disengaged position, the clutch disc 4 is not in contact with the first wheel 3 with the corollary that the second wheel 2 is not driven. When opening the clamps 5, the disc clutch 4 comes to press against the first wheel 3 under the action of the spring 6 ( fig.1b ). In this engaged position, the first wheel 3 drives the second wheel 2 by friction. In order for the friction to be sufficient, the engaged force F must be large, i.e. that a significant preload must be applied to the spring.

Selon l'art antérieur, les ressorts sont réalisés dans des matériaux standards tels que l'acier qui présentent un comportement élastique sur quelques dixièmes de pourcent avant d'entrer dans le domaine plastique. En fonctionnement, le ressort doit travailler dans son domaine élastique pour éviter toute déformation irréversible. Dans ce domaine élastique, le ressort a un comportement linéaire avec une force de rappel proportionnelle au déplacement. La figure 2 représente typiquement la courbe force-déplacement dans le domaine élastique. La force embrayée (Fe) est fixée par la précontrainte appliquée (déplacement p) sur le ressort et la force débrayée (Fd) est fixée par le déplacement (d) requis pour écarter le disque d'embrayage de la première roue. En pratique, le ressort travaille à la limite de ses capacités élastiques car il est soumis à une précontrainte importante avec un risque de déformation plastique lors du déplacement au débrayage. Outre le risque d'induire une déformation irréversible du ressort, ces grandes déformations provoquent une fatigue prématurée du ressort. Par ailleurs, le comportement du ressort étant linéaire dans le domaine élastique, toute augmentation de la force embrayée entraîne une augmentation de la force débrayée qui va devoir être fournie par les pinces.According to the prior art, the springs are made from standard materials such as steel which exhibit elastic behavior over a few tenths of a percent before entering the plastics field. In operation, the spring must work within its elastic range to avoid any irreversible deformation. In this elastic range, the spring has a linear behavior with a return force proportional to the displacement. The figure 2 typically represents the force-displacement curve in the elastic domain. The engaged force (F e ) is fixed by the preload applied (displacement p) on the spring and the disengaged force (F d ) is fixed by the displacement (d) required to move the clutch disc away from the first wheel. In practice, the spring works at the limit of its elastic capacities because it is subjected to a significant preload with a risk of plastic deformation during movement when disengaged. Besides the risk of inducing irreversible deformation of the spring, these large deformations cause premature fatigue of the spring. Moreover, the behavior of the spring being linear in the elastic range, any increase in the engaged force leads to an increase in the disengaged force which will have to be supplied by the clamps.

Dans l'exemple illustré, partant d'une force embrayée Fe suffisante pour que l'embrayage ne patine pas, à savoir 0.67 N dans l'exemple, l'éloignement du disque d'embrayage de la première roue d'une distance d, égale à 0.1 mm dans l'exemple, nécessite une force Fd importante de 1.5 N pour contrer la force de rappel du ressort. Typiquement, la force débrayée Fd est ainsi plus de deux fois supérieure à la force embrayée Fe.In the example illustrated, starting from a clutched force F e sufficient so that the clutch does not slip, namely 0.67 N in the example, the distance of the clutch disc from the first wheel by a distance d , equal to 0.1 mm in the example, requires a significant force F d of 1.5 N to counter the spring return force. Typically, the disengaged force F d is thus more than two times greater than the engaged force F e .

Résumé de l'inventionSummary of the invention

L'objet de la présente invention est de proposer un dispositif d'embrayage fournissant une force embrayée maximisée pour une force débrayée qui, quant à elle, est minimisée. En d'autres mots, l'objet de l'invention est de réduire le rapport entre la force débrayée et la force embrayée.The object of the present invention is to provide a clutch device providing a maximized engaged force for a disengaged force which, in turn, is minimized. In other words, the object of the invention is to reduce the ratio between the disengaged force and the engaged force.

A cet effet, la présente invention propose un dispositif d'embrayage comprenant un ressort réalisé dans un alliage à mémoire de forme utilisé à température ambiante pour ses propriétés de superélasticité. Le ressort réalisé dans un alliage à mémoire de forme a un comportement non linéaire dans le domaine élastique avec une contrainte qui plafonne à une valeur quasi constante sur une large plage de déformation. Ces propriétés de superélasticité et ce comportement non linéaire permettent d'ajuster aisément la force débrayée et la force embrayée en fonction des conditions de fonctionnement requises. Ainsi, une précontrainte importante peut être appliquée sur le ressort sans risque d'entrer dans le domaine plastique lors du débrayage du mécanisme. En corollaire, le ressort n'est plus sollicité à la limite de ses capacités élastiques contrairement au ressort de l'art antérieur, ce qui permet d'éviter une fatigue prématurée du ressort en utilisation. Par ailleurs, la force débrayée peut être minimisée en sollicitant le ressort dans le domaine où la contrainte, donc la force, plafonne à une valeur quasi constante.To this end, the present invention provides a clutch device comprising a spring made of a shape memory alloy used at room temperature for its superelasticity properties. The spring made of a shape memory alloy has a nonlinear behavior in the elastic domain with a stress which peaks at an almost constant value over a wide range of deformation. These properties of superelasticity and this nonlinear behavior make it possible to easily adjust the disengaged force and the engaged force according to the required operating conditions. Thus, a significant preload can be applied to the spring without the risk of entering the plastic domain when the mechanism is disengaged. As a corollary, the spring is no longer stressed to the limit of its elastic capacities unlike the spring of the prior art, which makes it possible to avoid premature fatigue of the spring in use. Furthermore, the disengaged force can be minimized by requesting the spring in the field where the constraint, and therefore the force, tops out at an almost constant value.

Selon l'invention, le ressort peut être dimensionné pour augmenter la force embrayée tout en maintenant une force débrayée équivalente ou inversement être dimensionné pour réduire la force débrayée tout en maintenant une force embrayée équivalente. Avantageusement, le rapport entre la force débrayée et la force embrayée est compris entre 1.1 et 2.0.According to the invention, the spring can be sized to increase the engaged force while maintaining an equivalent disengaged force or conversely be dimensioned to reduce the disengaged force while maintaining an equivalent engaged force. Advantageously, the ratio between the disengaged force and the engaged force is between 1.1 and 2.0.

Brève description des figuresBrief description of the figures

D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture de la description détaillée qui va suivre, en référence aux dessins annexés.

  • Les figures 1 a et 1 b illustrent schématiquement le fonctionnement d'un dispositif d'embrayage avec ce dernier en position débrayée à la figure 1a et en position embrayée à la figure 1 b. Ces figures se rapportent à l'art antérieur mais elles sont également d'application pour un dispositif d'embrayage selon l'invention.
  • La figure 2 représente la courbe force-déplacement pour un alliage standard utilisé dans un dispositif d'embrayage selon l'art antérieur.
  • La figure 3 représente la courbe de traction (contrainte-déformation) typique d'un alliage à mémoire de forme.
  • La figure 4 représente la courbe de traction d'un alliage à mémoire de forme en Ni-Ti utilisé dans le dispositif d'embrayage selon l'invention.
  • La figure 5a représente la géométrie du ressort, selon une variante de l'invention, utilisé dans le dispositif d'embrayage selon l'invention. La figure 5b représente à l'aide d'une vue en plan les dimensions respectives de la seconde roue, de la douille de l'axe du chronographe et du ressort.
  • La figure 6 représente la courbe force-déplacement pour le ressort ayant les propriétés mécaniques de la figure 4 et la géométrie des figures 5a et 5b.
  • La figure 7 représente une montre munie d'un mécanisme de chronographe selon l'invention.
Other characteristics and advantages of the invention will become apparent on reading the detailed description which follows, with reference to the appended drawings.
  • The figures 1 a and 1 b schematically illustrate the operation of a clutch device with the latter in the disengaged position at the figure 1a and in the engaged position figure 1 b. These figures relate to the prior art but they also apply to a clutch device according to the invention.
  • The figure 2 represents the force-displacement curve for a standard alloy used in a clutch device according to the prior art.
  • The figure 3 represents the typical tensile (stress-strain) curve of a shape memory alloy.
  • The figure 4 represents the traction curve of an Ni-Ti shape memory alloy used in the clutch device according to the invention.
  • The figure 5a shows the geometry of the spring, according to a variant of the invention, used in the clutch device according to the invention. The figure 5b shows with the help of a plan view the respective dimensions of the second wheel, the chronograph axle sleeve and the spring.
  • The figure 6 represents the force-displacement curve for the spring having the mechanical properties of the figure 4 and the geometry of figures 5a and 5b .
  • The figure 7 shows a watch provided with a chronograph mechanism according to the invention.

Description de l'inventionDescription of the invention

L'invention concerne un dispositif d'embrayage comprenant un ressort réalisé dans un alliage à mémoire de forme. Elle se rapporte plus spécifiquement à un dispositif d'embrayage destiné à équiper un mécanisme de chronographe 8 d'une pièce d'horlogerie 11 (fig.7).The invention relates to a clutch device comprising a spring made of a shape memory alloy. It relates more specifically to a clutch device intended to equip a chronograph mechanism 8 with a timepiece 11 ( fig.7 ).

Selon l'invention, les propriétés de superélasticité de l'alliage à mémoire de forme sont mises à profit pour réduire l'écart entre la force embrayée et la force débrayée. La figure 3 illustre le comportement superélastique d'un alliage à mémoire de forme qui présente à température ambiante une structure austénitique qui se transforme en martensite sous l'application d'une contrainte σ, ce qui permet de déformer le matériau de façon réversible de plusieurs pourcents. La courbe de traction présente d'abord un comportement linéaire élastique jusqu'à une contrainte critique où la transformation martensitique induit un comportement superélastique avec une déformation croissante sous une contrainte quasi constante. C'est le plateau qu'on observe sur la figure 3. Dès que la contrainte est relâchée, la transformation inverse de la martensite vers l'austénite s'opère et l'alliage reprend sa dimension première. Ainsi, un ressort réalisé dans ce matériau permet d'obtenir une contrainte, et donc une force, en fonction du déplacement qui n'est pas proportionnelle mais plafonne à une certaine valeur sur le plateau de la courbe contrairement à un matériau conventionnel tel que l'acier.According to the invention, the superelasticity properties of the shape memory alloy are used to reduce the difference between the engaged force and the disengaged force. The figure 3 illustrates the superelastic behavior of a shape memory alloy which exhibits at room temperature an austenitic structure which transforms into martensite under the application of a stress σ, which makes it possible to deform the material in a reversible manner by several percent. The tensile curve first presents an elastic linear behavior up to a critical stress where the martensitic transformation induces a superelastic behavior with an increasing strain under an almost constant stress. This is the plateau that we observe on the figure 3 . As soon as the stress is released, the reverse transformation from martensite to austenite takes place and the alloy returns to its original dimension. Thus, a spring made of this material makes it possible to obtain a stress, and therefore a force, as a function of the displacement which is not proportional but tops out at a certain value on the plateau of the curve unlike a conventional material such as l 'steel.

Préférentiellement, l'alliage à mémoire de forme selon l'invention est un alliage à base de cuivre ou un alliage à base de nickel et de titane. L'alliage à base de cuivre est un des alliages ayant, pour un pourcentage total de 100% et une teneur en impuretés éventuelles inférieure ou égale à 0.5%, la composition suivante en poids :

  • Cu entre 64.5 et 85%, Zn entre 9.5 et 25% et Al entre 4.5 et 10%,
  • Cu entre 79.5 et 84%, Al entre 12.5 et 14% et Ni entre 2.5 et 6%,
  • Cu entre 87 et 88%, Al entre 11 et 12% et Be entre 0.3 et 0.7%.
Preferably, the shape memory alloy according to the invention is a copper-based alloy or an alloy based on nickel and titanium. The copper-based alloy is one of the alloys having, for a total percentage of 100% and a possible impurity content less than or equal to 0.5%, the following composition by weight:
  • Cu between 64.5 and 85%, Zn between 9.5 and 25% and Al between 4.5 and 10%,
  • Cu between 79.5 and 84%, Al between 12.5 and 14% and Ni between 2.5 and 6%,
  • Cu between 87 and 88%, Al between 11 and 12% and Be between 0.3 and 0.7%.

L'alliage à base de nickel et de titane est constitué de nickel, avec un pourcentage en poids compris entre 52.5 et 63%, et de titane avec un pourcentage en poids compris entre 36.5 et 47%, pour un pourcentage total de 100% et une teneur en impuretés éventuelles inférieure ou égale à 0.5%.The nickel-titanium-based alloy consists of nickel, with a weight percentage between 52.5 and 63%, and titanium with a percentage by weight between 36.5 and 47%, for a total percentage of 100% and a possible impurity content less than or equal to 0.5%.

Cet alliage présente à température ambiante, en l'absence de contraintes, une microstructure austénitique.This alloy exhibits at room temperature, in the absence of constraints, an austenitic microstructure.

Préférentiellement, le ressort 6 comporte une partie annulaire centrale 6a et plusieurs pattes 6b partant de ladite partie annulaire centrale 6a comme illustré à la figure 5a. Par exemple, le nombre de pattes peut être de 3. Typiquement, l'épaisseur du ressort est comprise entre 0.05 et 0.4 mm. Préférentiellement, les pattes 6b sont inclinées par rapport au plan défini par la partie annulaire centrale 6a comme schématisé aux figures 1a et 1b. Selon le niveau de précontrainte appliqué sur les pattes en position embrayée (fig.1b), ces dernières sont plus ou moins inclinées par rapport au plan de la partie annulaire.Preferably, the spring 6 comprises a central annular part 6a and several tabs 6b starting from said central annular part 6a as illustrated in figure 5a . For example, the number of tabs can be 3. Typically, the thickness of the spring is between 0.05 and 0.4 mm. Preferably, the tabs 6b are inclined relative to the plane defined by the central annular part 6a as shown diagrammatically in figures 1a and 1b . Depending on the level of preload applied to the dropouts in the engaged position ( fig.1b ), the latter are more or less inclined with respect to the plane of the annular part.

Le ressort 6 est agencé au sein du dispositif d'embrayage 1 tel que précédemment décrit en référence aux figures 1a et 1b avec le disque d'embrayage 4, la première roue 3 et la seconde roue 2.The spring 6 is arranged within the clutch device 1 as previously described with reference to figures 1a and 1b with the clutch disc 4, the first wheel 3 and the second wheel 2.

Partant de la courbe contrainte-déformation du matériau en alliage à mémoire de forme, le dimensionnement du ressort, à savoir le nombre de pattes, la longueur active de chaque patte et la section des pattes va définir la courbe correspondante force-déplacement du ressort réalisé dans ce matériau tel que schématisé à la figure 6 pour la courbe en pointillés. En utilisation, le ressort est dimensionné pour travailler avec une force débrayée Fd qui se trouve sur le palier supérieur de l'hystérèse et avec une force embrayée Fe qui se trouve sur le palier inférieur de l'hystérèse. On précisera que la forme de l'hystérèse peut varier en fonction de la nuance choisie pour l'alliage à mémoire de forme. Ainsi, la force sur le palier supérieur et le palier inférieur peut être plus ou moins constante selon la nuance choisie.Starting from the stress-strain curve of the shape memory alloy material, the sizing of the spring, namely the number of legs, the active length of each leg and the section of the legs will define the corresponding force-displacement curve of the spring produced. in this material as shown schematically on figure 6 for the dotted curve. In use, the spring is sized to work with a disengaged force F d which is on the upper bearing of the hysteresis and with an engaged force F e which is on the lower bearing of the hysteresis. It should be noted that the shape of the hysteresis can vary depending on the shade chosen for the shape memory alloy. Thus, the force on the upper bearing and the lower bearing can be more or less constant depending on the chosen shade.

Le ressort fonctionne dans un mode précontraint avec la déformation du ressort, et avantageusement des pattes du ressort, qui définit la force embrayée Fe sur le palier inférieur. La force embrayée peut ainsi être ajustée en fonction de la précontrainte appliquée sur le ressort. Le matériau étant superélastique, une précontrainte importante peut être appliquée sans risque de déformer plastiquement le ressort. En outre, la force débrayée Fd peut être ajustée en fonction du déplacement d minimum requis pour éviter tout contact entre le disque d'embrayage et la première roue.The spring operates in a pre-stressed mode with the deformation of the spring, and advantageously of the legs of the spring, which defines the engaged force F e on the lower bearing. The engaged force can thus be adjusted depending on the preload applied to the spring. As the material is superelastic, a significant pre-stress can be applied without the risk of plastically deforming the spring. In addition, the disengaged force F d can be adjusted according to the minimum displacement d required to avoid any contact between the clutch disc and the first wheel.

Selon l'invention, le rapport entre la force débrayée et la force embrayée est minimisé et compris entre 1.1 et 2.0, de préférence entre 1.3 et 1.6. Exprimée en valeur absolue, la force verticale Fd est comprise entre 1 et 3 N et la force verticale Fe est comprise entre 0.5 et 2 N, avec Fd supérieur à Fe, pour un déplacement vertical d entre la position embrayée et la position débrayée compris entre 0.05 et 0.3 mm. Une autre manière de définir le comportement superélastique non linéaire du ressort en utilisation est de le caractériser en fonction de sa rigidité qui est non constante en cours de déformation. Ainsi, faisant référence à la figure 6, la pente de la droite reliant l'origine des axes X-Y au point (Fe, p) est supérieure à la pente de la droite reliant l'origine des axes X-Y au point (Fd, p+d). En d'autres mots, l'angle α2 est supérieur à l'angle α1.According to the invention, the ratio between the disengaged force and the engaged force is minimized and between 1.1 and 2.0, preferably between 1.3 and 1.6. Expressed as an absolute value, the vertical force F d is between 1 and 3 N and the vertical force F e is between 0.5 and 2 N, with F d greater than F e , for a vertical displacement d between the engaged position and the disengaged position between 0.05 and 0.3 mm. Another way to define the nonlinear superelastic behavior of the spring in use is to characterize it as a function of its rigidity which is not constant during deformation. Thus, referring to the figure 6 , the slope of the line connecting the origin of the XY axes to the point (F e , p) is greater than the slope of the line connecting the origin of the XY axes to the point (F d , p + d). In other words, the angle α 2 is greater than the angle α 1 .

Pour finir, la présente invention est illustrée à l'aide d'un exemple et des figures 4 à 6. La figure 4 représente les propriétés mécaniques de l'alliage à mémoire de forme à base de nickel et titane avec la composition précitée. La figure 6 représente la courbe force-déplacement correspondante pour un ressort réalisé dans cet alliage et ayant les dimensions rapportées à la figure 5a. Ce ressort a une épaisseur de 0.2 mm et comporte trois pattes avec une longueur de 0.85 mm pour une largeur de 0.06 mm. Après insertion entre la douille 7 de l'axe du chronographe et la seconde roue 2, la longueur active de chaque patte est d'environ 0.5 mm (fig.5b).Finally, the present invention is illustrated with the aid of an example and figures 4 to 6 . The figure 4 represents the mechanical properties of the shape memory alloy based on nickel and titanium with the aforementioned composition. The figure 6 represents the corresponding force-displacement curve for a spring made of this alloy and having the dimensions related to the figure 5a . This spring has a thickness of 0.2 mm and has three tabs with a length of 0.85 mm for a width of 0.06 mm. After insertion between the sleeve 7 of the chronograph axis and the second wheel 2, the active length of each tab is approximately 0.5 mm ( fig.5b ).

Pour être comparable aux conditions de fonctionnement de la figure 2, une force débrayée Fd de 1.5 N a été choisie avec une même course de débrayage d de 0.1 mm. Pour ces valeurs Fd et d, la force embrayée Fe a pu être maximisée à 1.05 N, correspondant à une distance de précontrainte p de 0.15 mm, comparé à 0.67 N pour un acier, ce qui permet de garantir que l'embrayage ne patine pas. Ainsi, on a pu avantageusement rehausser la force embrayée sans augmenter la force débrayée tout en conservant une même course de débrayage. En conséquence, le rapport force débrayée sur force embrayée s'élève à 1.4 comparé à 2.2 pour l'acier.To be comparable to the operating conditions of the figure 2 , a disengaged force F d of 1.5 N was chosen with the same disengagement stroke d of 0.1 mm. For these values F d and d, the engaged force F e could be maximized at 1.05 N, corresponding to a preload distance p 0.15 mm, compared to 0.67 N for steel, which ensures that the clutch does not slip. Thus, it has been possible to advantageously increase the engaged force without increasing the disengaged force while maintaining the same disengagement travel. Consequently, the ratio of disengaged force to engaged force amounts to 1.4 compared to 2.2 for steel.

Avec un acier ayant un comportement linéaire selon la figure 2, augmenter la force embrayée jusqu'à 1.05 N aurait nécessité une précontrainte p importante sur le ressort avec pour corollaire une force débrayée nettement supérieure à 1.5 N, qui aurait mené à une déformation plastique du ressort.With a steel having a linear behavior according to the figure 2 , increasing the engaged force up to 1.05 N would have required a significant preload p on the spring with the corollary of a disengaged force clearly greater than 1.5 N, which would have led to plastic deformation of the spring.

Se référant à la courbe de la figure 6, il est également envisageable d'appliquer un déplacement de précontrainte p inférieur à 0.15 mm, ce qui pour un même déplacement d au débrayage, mène à une force de débrayage moins importante que 1.5 N.Referring to the curve of the figure 6 , it is also conceivable to apply a preload displacement p less than 0.15 mm, which for the same displacement d when disengaging, leads to a disengagement force less than 1.5 N.

LégendeLegend

  1. (1) Dispositif d'embrayage vertical(1) Vertical clutch device
  2. (2) Second mobile aussi appelé seconde roue(2) Second mobile also called second wheel
  3. (3) Premier mobile aussi appelé première roue(3) First mobile also called first wheel
  4. (4) Disque d'embrayage(4) Clutch disc
  5. (5) Pince(5) Clamp
  6. (6) Ressort
    1. a. Partie annulaire centrale
    2. b. Patte
    (6) Spring
    1. To. Central annular part
    2. b. Paw
  7. (7) Douille de l'axe de chronographe(7) Chronograph axle sleeve
  8. (8) Mécanisme de chronographe(8) Chronograph mechanism
  9. (9) Roue de secondes(9) Seconds wheel
  10. (10) Roue de chronographe(10) Chronograph wheel
  11. (11) Montre ou pièce d'horlogerie(11) Watch or timepiece
  12. (12) Axe vertical(12) Vertical axis
  13. (13) Pierre(13) Stone
  14. (14) Axe central
    • Fe : force embrayée
    • Fd : force débrayée
    • d : distance de débrayage
    • p : déplacement pour la précontrainte du ressort
    (14) Central axis
    • F e : engaged force
    • F d : force disengaged
    • d: disengagement distance
    • p: displacement for spring preload

Claims (14)

Dispositif d'embrayage vertical (1) pour une pièce d'horlogerie, comprenant le long d'un axe vertical (12) une première roue (3) montée rotative autour dudit axe vertical (12), un disque d'embrayage (4), un ressort (6) et une seconde roue (2) montée rotative autour dudit axe vertical (12), ledit dispositif d'embrayage vertical (1) pouvant adopter une position embrayée où la seconde roue (2) est entraînée en rotation par la première roue (3) sous l'action du ressort (6) exerçant une force verticale Fe pour plaquer le disque d'embrayage (4) contre la première roue (3) et une position débrayée où le disque d'embrayage (4) est soumis contre l'action du ressort (6) à une force verticale Fd l'écartant de la première roue (3) de manière que la seconde roue (2) ne soit pas entraînée en rotation par la première roue (3), ledit dispositif d'embrayage vertical (1) étant caractérisé en ce que le ressort (6) est réalisé dans un alliage à mémoire de forme.Vertical clutch device (1) for a timepiece, comprising along a vertical axis (12) a first wheel (3) rotatably mounted about said vertical axis (12), a clutch disc (4) , a spring (6) and a second wheel (2) rotatably mounted around said vertical axis (12), said vertical clutch device (1) being able to assume an engaged position where the second wheel (2) is rotated by the first wheel (3) under the action of the spring (6) exerting a vertical force F e to press the clutch disc (4) against the first wheel (3) and a disengaged position where the clutch disc (4) is subjected against the action of the spring (6) to a vertical force F d away from the first wheel (3) so that the second wheel (2) is not rotated by the first wheel (3), said vertical clutch device (1) being characterized in that the spring (6) is made of a shape memory alloy. Dispositif d'embrayage vertical (1) selon la revendication 1, caractérisé en ce que l'alliage à mémoire de forme est un alliage à base de cuivre ou un alliage à base de nickel et de titane.Vertical clutch device (1) according to claim 1, characterized in that the shape memory alloy is a copper-based alloy or a nickel-titanium-based alloy. Dispositif d'embrayage vertical (1) selon la revendication précédente, caractérisé en ce que l'alliage à base de cuivre est un des alliages ayant, pour un pourcentage total de 100% et un pourcentage en impuretés éventuelles inférieur ou égal à 0.5%, la composition suivante en poids : - Cu entre 64.5 et 85%, Zn entre 9.5 et 25% et Al entre 4.5 et 10%, - Cu entre 79.5 et 84%, Al entre 12.5 et 14% et Ni entre 2.5 et 6%, - Cu entre 87 et 88%, Al entre 11 et 12% et Be entre 0.3 et 0.7%. Vertical clutch device (1) according to the preceding claim, characterized in that the copper-based alloy is one of the alloys having, for a total percentage of 100% and a percentage of possible impurities less than or equal to 0.5%, the following composition by weight: - Cu between 64.5 and 85%, Zn between 9.5 and 25% and Al between 4.5 and 10%, - Cu between 79.5 and 84%, Al between 12.5 and 14% and Ni between 2.5 and 6%, - Cu between 87 and 88%, Al between 11 and 12% and Be between 0.3 and 0.7%. Dispositif d'embrayage vertical (1) selon la revendication 2, caractérisé en ce que l'alliage à base de nickel et de titane est constitué, en poids, de nickel avec un pourcentage compris entre 52.5 et 63% et de titane avec un pourcentage compris entre 36.5 et 47%, pour un pourcentage total de 100% et un pourcentage en impuretés éventuelles inférieur ou égal à 0.5%.Vertical clutch device (1) according to Claim 2, characterized in that the alloy based on nickel and titanium consists, by weight, of nickel with a percentage between 52.5 and 63% and of titanium with a percentage between 36.5 and 47%, for a total percentage of 100% and a percentage of possible impurities less than or equal to 0.5%. Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce que l'alliage à mémoire de forme a une microstructure austénitique à température ambiante lui conférant des propriétés superélastiques à la température ambiante.Vertical clutch device (1) according to any one of the preceding claims, characterized in that the shape memory alloy has an austenitic microstructure at room temperature giving it superelastic properties at room temperature. Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce qu'il est dimensionné pour avoir en utilisation un rapport entre la force verticale Fd et la force verticale Fe compris entre 1.1 et 2.0.Vertical clutch device (1) according to any one of the preceding claims, characterized in that it is dimensioned to have in use a ratio between the vertical force F d and the vertical force F e of between 1.1 and 2.0. Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce qu'il est dimensionné pour avoir en utilisation un rapport entre la force verticale Fd et la force verticale Fe compris entre 1.3 et 1.6.Vertical clutch device (1) according to any one of the preceding claims, characterized in that it is dimensioned to have in use a ratio between the vertical force F d and the vertical force F e of between 1.3 and 1.6. Dispositif d'embrayage vertical (1) selon la revendication 6 ou 7, caractérisé en ce que la force verticale Fd est comprise entre 1 et 3 N et en ce que la force verticale Fe est comprise entre 0.5 et 2 N pour un déplacement vertical d entre la position embrayée et la position débrayée compris entre 0.05 et 0.3 mm, ladite force verticale Fd étant supérieure à ladite force verticale Fe.Vertical clutch device (1) according to claim 6 or 7, characterized in that the vertical force F d is between 1 and 3 N and in that the vertical force F e is between 0.5 and 2 N for a displacement vertical d between the engaged position and the disengaged position between 0.05 and 0.3 mm, said vertical force F d being greater than said vertical force F e . Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce que le ressort (6) comporte une partie annulaire centrale (6a) et plusieurs pattes (6b) partant de ladite partie annulaire centrale (6a).Vertical clutch device (1) according to any one of the preceding claims, characterized in that the spring (6) comprises a central annular part (6a) and several tabs (6b) extending from said central annular part (6a). Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce que l'épaisseur du ressort (6) est comprise entre 0.05 et 0.4 mm.Vertical clutch device (1) according to any one of the preceding claims, characterized in that the thickness of the spring (6) is between 0.05 and 0.4 mm. Dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes, caractérisé en ce que, sur une courbe force-déplacement dudit ressort (6), avec la force définissant l'axe Y, et le déplacement définissant l'axe X, l'angle α2 par rapport à l'axe X de la droite reliant l'origine des axes X-Y à la force verticale Fe, est supérieur à l'angle α1 par rapport à l'axe X de la droite reliant l'origine des axes X-Y à la force verticale Fd.Vertical clutch device (1) according to any one of the preceding claims, characterized in that , on a force-displacement curve of said spring (6), with the force defining the Y axis, and the displacement defining the X axis, the angle α 2 with respect to the X axis of the line connecting the origin of the XY axes to the vertical force F e , is greater than the angle α 1 with respect to the X axis of the line connecting the origin of the XY axes to the vertical force F d . Mécanisme de chronographe (8) caractérisé en ce qu'il comprend le dispositif d'embrayage vertical (1) selon une quelconque des revendications précédentes.Chronograph mechanism (8) characterized in that it comprises the vertical clutch device (1) according to any one of the preceding claims. Montre (11) caractérisée en ce qu'elle comprend le mécanisme de chronographe (8) selon la revendication précédente.Watch (11) characterized in that it comprises the chronograph mechanism (8) according to the preceding claim. Utilisation d'un ressort (6) en alliage à mémoire de forme, pour ses propriétés de superélasticité à température ambiante, dans un dispositif d'embrayage vertical (1) d'une pièce d'horlogerie.Use of a shape memory alloy spring (6), for its superelasticity properties at room temperature, in a vertical clutch device (1) of a timepiece.
EP20217971.9A 2020-02-21 2020-12-31 Vertical clutch device for a timepiece Active EP3869278B1 (en)

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Publication number Priority date Publication date Assignee Title
EP4451068A1 (en) 2023-04-21 2024-10-23 Greubel Forsey S.A. Clutch for a chronograph
WO2024218183A1 (en) 2023-04-21 2024-10-24 Greubel Forsey S.A. Coupling for chronograph

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EP3869278B1 (en) 2023-03-08
CN113296383A (en) 2021-08-24
JP2021135287A (en) 2021-09-13
US20210271205A1 (en) 2021-09-02
US11353826B2 (en) 2022-06-07

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