EP2529278B1 - Automatic winding system - Google Patents

Automatic winding system Download PDF

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Publication number
EP2529278B1
EP2529278B1 EP11701103.1A EP11701103A EP2529278B1 EP 2529278 B1 EP2529278 B1 EP 2529278B1 EP 11701103 A EP11701103 A EP 11701103A EP 2529278 B1 EP2529278 B1 EP 2529278B1
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EP
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Prior art keywords
wheel
ratchet
exit
winding system
solar
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EP11701103.1A
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German (de)
French (fr)
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EP2529278A1 (en
Inventor
Jean-François Mojon
Xavier Clement
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MPS Micro Precision Systems AG
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Mps Micro Precision Systems AG
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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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch

Definitions

  • the self-winding watches are well known to those skilled in the art and include a gear train kinematically connecting a pinion integral with an oscillating mass, the ratchet of a barrel.
  • This gear train is intended to increase the torque transmitted to the ratchet and straighten the direction of rotation of the gear train, so that the ratchet is driven unidirectionally.
  • the gear ratio that this gear must perform is important because the mainspring is powerful.
  • the reduction ratios generally encountered are of the order of 100 or more.
  • an automatic winding system comprising an oscillating mass thanks to a ball bearing of large diameter.
  • two satellites are pivotally mounted on the central portion of the oscillating mass and respectively drive a first and a second sun gear, alternately depending on the direction of rotation of the oscillating mass.
  • These solar gears are themselves respectively connected cinematically to a first and a second mobile of the automatic gear train, ensuring the reduction.
  • Such a system does not solve the congestion problem related to the reduction gear train.
  • the document CH307687 proposes an interesting automatic winding system, in particular by its configuration and the thickness obtained, without however proposing an optimal reduction ratio.
  • the document DE1254088 describes an automatic winding system using a ring which is toothed internally and externally.
  • the present invention aims to provide an automatic winding system improving the size or reduction ratio of existing systems.
  • the invention relates to an automatic winding system according to two possible alternative embodiments, respectively defined in claims 1 and 3.
  • an oscillating mass 10 is pivotally mounted around an axis AA, by means of a ball bearing 12.
  • this bearing 12 is of unidirectional type (one way), that is to say that is to say that it comprises a first inlet ring 12a, on which is integrally mounted for example by driving or screwing the oscillating mass 10, and a second output ring 12b arranged to be driven by the first input ring 12a only in one direction.
  • Eccentricity e is defined as the distance between the axis AA and the axis of the center of the second output ring 12b.
  • a bearing 14 is driven on the outer face of the second output ring and is thus driven eccentrically with reference to the axis AA.
  • This bearing 14 allows the rotation and the positioning in height of a first wheel 18 of a gearbox 16.
  • the first wheel 18 is of annular shape and is integrally mounted on the bearing 14.
  • the first wheel 18 comprises a toothing of N1 teeth on its outer portion and is thus driven eccentrically about the axis AA.
  • the gearbox 16 further comprises means for guiding the first wheel 18 which is free around the axis AA.
  • These guide means may, for example, consist of pins 20 of circular section, integral with the first wheel 18 and arranged projecting with reference to the surface of the first wheel 18.
  • the pins 20 take place in circular openings 22 fixed , formed in a bridge of the movement, called automatic bridge 24.
  • These circular openings 22 are of diameter greater than that of the pins 20. According to the theory, the diameter of the circular openings is equal to the diameter of the pins plus twice the eccentricity e.
  • the pins 20 on the one hand and the openings 22 in correspondence, on the other hand, are distributed concentrically around the axis AA.
  • the reducer 16 is further composed of a second wheel 26, director, ring-shaped. It is located in the same plane as the first wheel 18.
  • the second wheel 26 is pivotally guided about the axis AA.
  • a flange 24a formed on the automatic bridge 24 with which a shoulder 26a and a bearing 26b of the second wheel 26 cooperate.
  • a holding plate 28 is fixed on the automatic bridge 24 and overflows by above the second wheel 26 to maintain it in height.
  • the inside diameter of the second wheel 26 is greater than the outside diameter of the first wheel 18 so that the first wheel 18 is located inside the second wheel 26.
  • the second wheel 26 is provided with an internal toothing of N2 teeth, with N2 greater than N1 of at least one tooth, arranged to cooperate with the external toothing of the first wheel 18.
  • e m * (N2-N1) / 2, where m is the gear module.
  • the first wheel 18 rolls without slipping on the internal toothing of the second wheel 26. It further comprises an external toothing kinematically connected to the ratchet 30 of a barrel, as will be explained by the after.
  • the first wheel 18 meshes with the second wheel 26, at a point which moves along the internal toothing of the second wheel 26.
  • the latter is so trained.
  • a point on the pitch circle of the first wheel 18 will describe a hypocycloid during the rotation of the first wheel 18.
  • the difference in toothing between the first 18 and second 26 wheels makes it possible to obtain a sharp reduction in the speed of rotation between the input of the gearbox 16 and the output.
  • the winding system according to the invention can be mounted on a module plate, to be adapted to an existing movement or to replace an existing automatic module, with almost no adaptation to the basic movement.
  • the external toothing of the second wheel 26 is connected kinematically with the ratchet 30 of the barrel.
  • it meshes with a return 32 which itself is in connection with an intermediate ratchet wheel 36 in engagement with the ratchet 30.
  • it is still possible to introduce a reduction ratio into the workings between the second wheel 26 and the ratchet.
  • the very strong reduction of the system makes it possible to ensure the irreversibility of the mechanism.
  • it can have a clutch mobile, not shown in the drawing, which would engage with the reference 32. This clutch mobile allows the barrel, via the reference 32, not to empty during the phases of assembly and disassembly of the automatic module.
  • a second embodiment is shown on the figure 4 .
  • the oscillating mass 10 pivoting on the axis AA, the unidirectional bearing 12 and the gear 16 kinematically connecting the second ring 12b of the unidirectional bearing to the ratchet 30 of the barrel.
  • the gearbox 16 comprises a first sun gear 38 provided with teeth N1 teeth and guided in rotation about the axis AA.
  • the reducer 16 further comprises a second sun gear 40, director, provided with a toothing of N2 teeth, with N2> N1, that is to say with at least one tooth of difference.
  • This second sun gear 40 is fixed on the platen of the movement or the automatic module. It is superimposed coaxially with the first sun gear 38. Despite the difference in teeth between the two wheels, they have a pitch circle of identical size, or at least very close, so that their pitch circle is superimposed.
  • the gearbox 16 further comprises a satellite 42 rotatably mounted on the output ring 12b.
  • the satellite is decomposed into a first 42a and a second 42b satellites arranged coaxially.
  • the satellite 42a is in engagement with the second sun wheel 40, which is fixed, while the satellite 42b is in engagement with the first sun wheel 38.
  • the two sun wheels advantageously have different diameters, which allows a bigger difference between the teeth. A greater reduction can be obtained than with the devices of the state of the art using a simple satellite.
  • the gearbox 16 further comprises an output wheel 44 integral with the first sun gear 38 and kinematically connected to the ratchet of the barrel.
  • this second embodiment makes it possible to obtain greater reduction ratios than the first, with equivalent bulk.
  • a clutch mobile as proposed above can also be arranged in engagement with the reference 32, to prevent the barrel to empty during the assembly and disassembly phases of the automatic module.
  • the unidirectional bearing can be replaced by other unidirectional drive systems that would not transmit to the reducer mass movements for a direction of rotation.
  • a snap connection or an asymmetrical profile wheel may also allow such a result.
  • It may further be considered to decenter the oscillating mass 10 with respect to the movement and implement a mass of the micro-rotor type.
  • the automatic winding system according to the invention can, in addition, perfectly be coupled with a display of the power reserve which would connect, for example, on the return or on the intermediate ratchet wheel.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Winding Of Webs (AREA)

Description

Domaine techniqueTechnical area

La présente invention concerne un système de remontage automatique comprenant :

  • une masse oscillante pivotant sur un axe,
  • un système d'entraînement unidirectionnel comportant une entrée, sur laquelle est montée solidairement la masse oscillante, et une sortie agencée pour n'être entraînée par l'entrée que dans un seul sens,
  • un réducteur reliant cinématiquement la sortie du système d'entraînement unidirectionnel au rochet d'un barillet.
The present invention relates to an automatic winding system comprising:
  • an oscillating mass pivoting on an axis,
  • a unidirectional drive system having an input, on which the oscillating mass is integrally mounted, and an output arranged to be driven by the input in only one direction,
  • a gearbox kinematically connecting the output of the unidirectional drive system to the ratchet of a barrel.

Etat de la techniqueState of the art

Les montres à remontage automatique sont bien connues de l'homme du métier et comportent un train de rouage reliant cinématiquement un pignon solidaire d'une masse oscillante, au rochet d'un barillet. Ce train de rouage a pour but d'augmenter le couple transmis au rochet et de redresser le sens de rotation du train de rouage, de manière à ce que le rochet soit entraîné de manière unidirectionnelle. La démultiplication que doit effectuer ce rouage est importante, car le ressort de barillet est puissant. Les rapports de réduction généralement rencontrés sont de l'ordre de 100, voire plus.The self-winding watches are well known to those skilled in the art and include a gear train kinematically connecting a pinion integral with an oscillating mass, the ratchet of a barrel. This gear train is intended to increase the torque transmitted to the ratchet and straighten the direction of rotation of the gear train, so that the ratchet is driven unidirectionally. The gear ratio that this gear must perform is important because the mainspring is powerful. The reduction ratios generally encountered are of the order of 100 or more.

De manière générale, cette réduction est obtenue par l'engrènement de plusieurs mobiles en série, ce qui a évidement l'inconvénient d'être relativement encombrant et gourmand en énergie consommée par les frottements des différents mobiles.In general, this reduction is obtained by the meshing of several mobiles in series, which obviously has the disadvantage of being relatively bulky and greedy energy consumed by the friction of different mobiles.

On connaît notamment du document EP1046965 , un système de remontage automatique comprenant une masse oscillant grâce à un roulement à billes de grand diamètre. Pour assurer le redressement du sens de rotation de la masse, deux satellites sont montés pivotant sur la partie centrale de la masse oscillante et entraînent respectivement un premier et un deuxième pignons solaires, en alternance en fonction du sens de rotation de la masse oscillante. Ces pignons solaires sont eux-mêmes respectivement reliés cinématiquement à un premier et à un deuxième mobile du train de rouage automatique, assurant la réduction. Un tel système ne résout donc pas le problème d'encombrement lié au train de rouage de réduction.We know in particular of the document EP1046965 , an automatic winding system comprising an oscillating mass thanks to a ball bearing of large diameter. To ensure the recovery of the direction of rotation of the mass, two satellites are pivotally mounted on the central portion of the oscillating mass and respectively drive a first and a second sun gear, alternately depending on the direction of rotation of the oscillating mass. These solar gears are themselves respectively connected cinematically to a first and a second mobile of the automatic gear train, ensuring the reduction. Such a system does not solve the congestion problem related to the reduction gear train.

Le document CH307687 propose un système de remontage automatique intéressant, notamment de par sa configuration et l'épaisseur obtenue, sans toutefois proposer un rapport de réduction optimal.The document CH307687 proposes an interesting automatic winding system, in particular by its configuration and the thickness obtained, without however proposing an optimal reduction ratio.

Le document DE1254088 décrit un système de remontage automatique utilisant un anneau qui est denté intérieurement et extérieurement.The document DE1254088 describes an automatic winding system using a ring which is toothed internally and externally.

La présente invention a pour but de proposer un système de remontage automatique améliorant l'encombrement ou le rapport de réduction des systèmes existants.The present invention aims to provide an automatic winding system improving the size or reduction ratio of existing systems.

Divulgation de l'inventionDisclosure of the invention

De façon plus précise, l'invention concerne un système de remontage automatique selon deux alternatives possibles de mise en oeuvre, définies respectivement dans les revendications 1 et 3.More specifically, the invention relates to an automatic winding system according to two possible alternative embodiments, respectively defined in claims 1 and 3.

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 3 montrent un premier mode de réalisation, en perspective et en transparence pour les figures 1 et 2, et en coupe pour la figure 3, et
  • la figure 4 illustre un deuxième mode de réalisation.
Other details of the invention will emerge more clearly on reading the description which follows, made with reference to the appended drawing in which:
  • the Figures 1 to 3 show a first embodiment, in perspective and in transparency for the figures 1 and 2 , and in section for the figure 3 , and
  • the figure 4 illustrates a second embodiment.

Mode(s) de réalisation de l'inventionMode (s) of realization of the invention

Par souci de clarté, on n'a représenté sur les dessins que les éléments essentiels à la compréhension de l'invention. Les autres éléments de la pièce d'horlogerie n'étant pas en lien avec le système de remontage automatique ne sont pas visibles.For the sake of clarity, only the elements essential to the understanding of the invention have been shown in the drawings. The other elements of the timepiece not being related to the automatic winding system are not visible.

Une masse oscillante 10 est montée pivotante autour d'un axe AA, au moyen d'un roulement à billes 12. Selon l'exemple particulier illustré au dessin, ce roulement 12 est de type unidirectionnel (one way), c'est-à-dire qu'il comporte une première bague d'entrée 12a, sur laquelle est montée solidairement par exemple par chassage ou vissage la masse oscillante 10, et une deuxième bague de sortie 12b agencée pour n'être entraînée par la première bague d'entrée 12a que dans un seul sens.An oscillating mass 10 is pivotally mounted around an axis AA, by means of a ball bearing 12. According to the particular example illustrated in the drawing, this bearing 12 is of unidirectional type (one way), that is to say that is to say that it comprises a first inlet ring 12a, on which is integrally mounted for example by driving or screwing the oscillating mass 10, and a second output ring 12b arranged to be driven by the first input ring 12a only in one direction.

Comme on peut le voir sur la figure 3, la face extérieure de la deuxième bague de sortie 12b est disposée de manière excentrique par rapport à l'axe AA. On définit l'excentricité e comme étant la distance entre l'axe AA et l'axe du centre de la deuxième bague de sortie 12b.As can be seen on the figure 3 the outer face of the second output ring 12b is eccentrically disposed with respect to the axis AA. Eccentricity e is defined as the distance between the axis AA and the axis of the center of the second output ring 12b.

Un palier 14 est chassé sur la face extérieure de la deuxième bague de sortie et est donc entraîné de manière excentrique en référence à l'axe AA. Ce palier 14 permet la rotation et le positionnement en hauteur d'une première roue 18 d'un réducteur 16. La première roue 18 est de forme annulaire et est montée solidairement sur le palier 14. La première roue 18 comprend une denture de N1 dents sur sa portion extérieure et est donc entraînée de manière excentrique autour de l'axe AA.A bearing 14 is driven on the outer face of the second output ring and is thus driven eccentrically with reference to the axis AA. This bearing 14 allows the rotation and the positioning in height of a first wheel 18 of a gearbox 16. The first wheel 18 is of annular shape and is integrally mounted on the bearing 14. The first wheel 18 comprises a toothing of N1 teeth on its outer portion and is thus driven eccentrically about the axis AA.

Le réducteur 16 comprend encore des moyens de guidage de la première roue 18 qui est libre autour de l'axe AA. Ces moyens de guidage peuvent, par exemple, consister en des goupilles 20 de section circulaire, solidaires de la première roue 18 et disposées en saillie en référence à la surface de la première roue 18. Les goupilles 20 prennent place dans des ouvertures circulaires 22 fixes, ménagées dans un pont du mouvement, appelé pont d'automatique 24. Ces ouvertures circulaires 22 sont de diamètre supérieur à celui des goupilles 20. Selon la théorie, le diamètre des ouvertures circulaires est égal au diamètre des goupilles plus deux fois l'excentricité e. Les goupilles 20 d'une part et les ouvertures 22 en correspondance, d'autre part, sont réparties concentriquement autour de l'axe AA.The gearbox 16 further comprises means for guiding the first wheel 18 which is free around the axis AA. These guide means may, for example, consist of pins 20 of circular section, integral with the first wheel 18 and arranged projecting with reference to the surface of the first wheel 18. The pins 20 take place in circular openings 22 fixed , formed in a bridge of the movement, called automatic bridge 24. These circular openings 22 are of diameter greater than that of the pins 20. According to the theory, the diameter of the circular openings is equal to the diameter of the pins plus twice the eccentricity e. The pins 20 on the one hand and the openings 22 in correspondence, on the other hand, are distributed concentrically around the axis AA.

Le réducteur 16 est en outre composé d'une deuxième roue 26, directrice, de forme annulaire. Elle est située dans le même plan que la première roue 18. La deuxième roue 26 est guidée en pivotement autour de l'axe AA. On peut notamment voir sur la figure 2, un rebord 24a ménagé sur le pont d'automatique 24, avec lequel coopèrent un épaulement 26a et une portée 26b de la deuxième roue 26. En outre, une plaque de maintien 28 est fixée sur le pont d'automatique 24 et déborde par-dessus la deuxième roue 26 pour la maintenir en hauteur.The reducer 16 is further composed of a second wheel 26, director, ring-shaped. It is located in the same plane as the first wheel 18. The second wheel 26 is pivotally guided about the axis AA. We can see on the figure 2 , a flange 24a formed on the automatic bridge 24, with which a shoulder 26a and a bearing 26b of the second wheel 26 cooperate. In addition, a holding plate 28 is fixed on the automatic bridge 24 and overflows by above the second wheel 26 to maintain it in height.

Le diamètre intérieur de la deuxième roue 26 est supérieur au diamètre extérieur de la première roue 18 de sorte que la première roue 18 est située à l'intérieur de la deuxième roue 26. La deuxième roue 26 est dotée d'une denture intérieure de N2 dents, avec N2 supérieur à N1 d'au moins une dent, agencée pour coopérer avec la denture extérieure de la première roue 18. Par rapport à l'excentricité e, on a e = m*(N2-N1) / 2, où m est le module des roues dentées. Plus particulièrement, grâce aux moyens de guidage, la première roue 18 roule sans glissement sur la denture intérieure de la deuxième roue 26. Elle comporte en outre une denture extérieure reliée cinématiquement au rochet 30 d'un barillet, comme on l'expliquera par la suite.The inside diameter of the second wheel 26 is greater than the outside diameter of the first wheel 18 so that the first wheel 18 is located inside the second wheel 26. The second wheel 26 is provided with an internal toothing of N2 teeth, with N2 greater than N1 of at least one tooth, arranged to cooperate with the external toothing of the first wheel 18. With respect to the eccentricity e , we have e = m * (N2-N1) / 2, where m is the gear module. More particularly, thanks to the guide means, the first wheel 18 rolls without slipping on the internal toothing of the second wheel 26. It further comprises an external toothing kinematically connected to the ratchet 30 of a barrel, as will be explained by the after.

Ainsi, grâce aux moyens de guidage, et à l'entraînement par le palier 14, la première roue 18 engrène avec la deuxième roue 26, en un point qui se déplace le long de la denture intérieure de la deuxième roue 26. Cette dernière est ainsi entraînée. Par ailleurs, pour caractériser le déplacement de la première roue 18 par rapport à la deuxième, on peut relever qu'un point situé sur le cercle primitif de la première roue 18 décrira une hypocycloïde au cours de la rotation de la première roue 18. La différence de denture entre les première 18 et deuxième 26 roues permet d'obtenir une forte réduction de la vitesse de rotation entre l'entrée du réducteur 16 et la sortie. Ce rapport est r = (N2-N1)/N1. Ainsi, avec N1=92 et N1=90, la vitesse de sortie est 45 fois plus faible que la vitesse d'entrée.Thus, thanks to the guide means, and to the drive by the bearing 14, the first wheel 18 meshes with the second wheel 26, at a point which moves along the internal toothing of the second wheel 26. The latter is so trained. Furthermore, to characterize the displacement of the first wheel 18 relative to the second, it can be noted that a point on the pitch circle of the first wheel 18 will describe a hypocycloid during the rotation of the first wheel 18. The difference in toothing between the first 18 and second 26 wheels makes it possible to obtain a sharp reduction in the speed of rotation between the input of the gearbox 16 and the output. This ratio is r = (N2-N1) / N1. Thus, with N1 = 92 and N1 = 90, the output speed is 45 times lower than the input speed.

De manière avantageuse, le système de remontage selon l'invention peut être monté sur une platine de module, pour être adapté sur un mouvement existant ou pour remplacer un module automatique existant, avec quasiment aucune adaptation sur le mouvement de base.Advantageously, the winding system according to the invention can be mounted on a module plate, to be adapted to an existing movement or to replace an existing automatic module, with almost no adaptation to the basic movement.

La denture extérieure de la deuxième roue 26 est reliée cinématiquement avec le rochet 30 du barillet. De manière avantageuse, elle engrène avec un renvoi 32 qui lui-même est en liaison avec une roue intermédiaire de rochet 36 en prise avec le rochet 30. Le cas échéant, on peut encore introduire un rapport de réduction dans les rouages situés entre la deuxième roue 26 et le rochet. La très forte réduction du système permet d'assurer l'irréversibilité du mécanisme. De manière avantageuse, on peut avoir un mobile d'embrayage, non représenté au dessin, qui viendrait en prise avec le renvoi 32. Ce mobile d'embrayage permet au barillet, via le renvoi 32, de ne pas se vider lors des phases de montage et de démontage du module automatique.The external toothing of the second wheel 26 is connected kinematically with the ratchet 30 of the barrel. Advantageously, it meshes with a return 32 which itself is in connection with an intermediate ratchet wheel 36 in engagement with the ratchet 30. Where appropriate, it is still possible to introduce a reduction ratio into the workings between the second wheel 26 and the ratchet. The very strong reduction of the system makes it possible to ensure the irreversibility of the mechanism. Advantageously, it can have a clutch mobile, not shown in the drawing, which would engage with the reference 32. This clutch mobile allows the barrel, via the reference 32, not to empty during the phases of assembly and disassembly of the automatic module.

On obtient ainsi un système de remontage automatique particulièrement compact, avec une modularité très avantageuse. En outre, il est peu sensible aux chocs, facile à mettre en oeuvre. Le choix des dentures des roues du réducteur 16 permet d'adapter aisément le rapport de réduction.This gives a particularly compact automatic winding system, with a very advantageous modularity. In addition, it is insensitive to shocks, easy to implement. The choice of the gear teeth of the gearbox 16 makes it easy to adapt the gear ratio.

Un deuxième mode de réalisation est représenté sur la figure 4. On retrouve en commun avec le premier mode de réalisation, la masse oscillante 10 pivotant sur l'axe AA, le roulement unidirectionnel 12 ainsi que le réducteur 16 reliant cinématiquement la deuxième bague 12b du roulement unidirectionnel au rochet 30 du barillet.A second embodiment is shown on the figure 4 . We find in common with the first embodiment, the oscillating mass 10 pivoting on the axis AA, the unidirectional bearing 12 and the gear 16 kinematically connecting the second ring 12b of the unidirectional bearing to the ratchet 30 of the barrel.

Dans ce deuxième mode de réalisation, le réducteur 16 comprend une première roue solaire 38 munie d'une denture de N1 dents et guidée en rotation autour de l'axe AA. Le réducteur 16 comprend encore une deuxième roue solaire 40, directrice, dotée d'une denture de N2 dents, avec N2>N1, c'est-à-dire avec au moins une dent de différence. Cette deuxième roue solaire 40 est fixée sur la platine du mouvement ou du module automatique. Elle est superposée de manière coaxiale à la première roue solaire 38. Malgré la différence de denture entre les deux roues, celles-ci présentent un cercle primitif de dimension identique, ou en tout cas très proche, de sorte que leur cercle primitif se superpose.In this second embodiment, the gearbox 16 comprises a first sun gear 38 provided with teeth N1 teeth and guided in rotation about the axis AA. The reducer 16 further comprises a second sun gear 40, director, provided with a toothing of N2 teeth, with N2> N1, that is to say with at least one tooth of difference. This second sun gear 40 is fixed on the platen of the movement or the automatic module. It is superimposed coaxially with the first sun gear 38. Despite the difference in teeth between the two wheels, they have a pitch circle of identical size, or at least very close, so that their pitch circle is superimposed.

Le réducteur 16 comprend encore un satellite 42 monté à rotation sur la bague de sortie 12b. Le satellite est décomposé en un premier 42a et un deuxième 42b satellites disposés de manière coaxiale. Le satellite 42a est en prise avec la deuxième roue solaire 40, qui est fixe, tandis que le satellite 42b est en prise avec la première roue solaire 38. Dans cette variante, les deux roues solaires ont avantageusement des diamètres différents, ce qui permet une plus grande différence entre les dentures. On peut obtenir une réduction plus importante qu'avec les dispositifs de l'état de la technique mettant en oeuvre un satellite simple.The gearbox 16 further comprises a satellite 42 rotatably mounted on the output ring 12b. The satellite is decomposed into a first 42a and a second 42b satellites arranged coaxially. The satellite 42a is in engagement with the second sun wheel 40, which is fixed, while the satellite 42b is in engagement with the first sun wheel 38. In this variant, the two sun wheels advantageously have different diameters, which allows a bigger difference between the teeth. A greater reduction can be obtained than with the devices of the state of the art using a simple satellite.

Le réducteur 16 comporte encore une roue de sortie 44 solidaire de la première roue solaire 38 et reliée cinématiquement au rochet du barillet.The gearbox 16 further comprises an output wheel 44 integral with the first sun gear 38 and kinematically connected to the ratchet of the barrel.

Ainsi, lorsque les satellites 42a et 42b sont entraînés en révolution autour des roues solaires par la rotation de la masse oscillante 10 et de la bague de sortie 12b du roulement unidirectionnel 12, le satellite 42a est entraîné en rotation sur lui-même par son engrènement avec la deuxième roue solaire 40. Le satellite 42a met ainsi en rotation le deuxième satellite 42b qui transmet cette rotation à la première roue solaire 38 qui est libre. Ainsi, avec N1 et N2, le nombre de dents des première et deuxième roues solaires, et N3 et N4, respectivement le nombre de dents des premier 42a et deuxième 42b satellites, le rapport de réduction du réducteur 16 est r=1-(N2xN4)/(N3xN1).Thus, when the satellites 42a and 42b are driven in revolution around the solar wheels by the rotation of the oscillating mass 10 and the output ring 12b of the unidirectional bearing 12, the satellite 42a is rotated on itself by its meshing with the second sun gear 40. The satellite 42a thus rotates the second satellite 42b which transmits this rotation to the first sun gear 38 which is free. Thus, with N1 and N2, the number of teeth of the first and second sun wheels, and N3 and N4, respectively the number of teeth of the first 42a and second 42b satellites, the reduction ratio of the gear reducer 16 is r = 1- (N2xN4 ) / (N3xN1).

Outre les mêmes avantages que ceux décrits ci-dessus à propos du premier mode de réalisation, ce deuxième mode de réalisation permet d'obtenir des rapports de réduction plus importants que le premier, à encombrement équivalent. Un mobile d'embrayage tel que proposé ci-dessus, peut aussi est agencé en prise avec le renvoi 32, afin d'éviter au barillet de se vider lors des phases de montage et de démontage du module automatique.In addition to the same advantages as those described above with regard to the first embodiment, this second embodiment makes it possible to obtain greater reduction ratios than the first, with equivalent bulk. A clutch mobile as proposed above, can also be arranged in engagement with the reference 32, to prevent the barrel to empty during the assembly and disassembly phases of the automatic module.

La présente description a été donnée à titre d'exemple non limitatif de l'invention. L'homme du métier pourra envisager d'autres variantes sans sortir du cadre de l'invention telle que définie dans les revendications. Ainsi, le roulement unidirectionnel peut être remplacé par d'autres systèmes d'entraînement unidirectionnel qui permettraient de ne transmettre au réducteur les mouvements de la masse que pour un sens de rotation. Une liaison par encliquetage ou par une roue à profil asymétrique peut également permettre un tel résultat. On pourra encore envisager de décentrer la masse oscillante 10 par rapport au mouvement et mettre en oeuvre une masse de type micro-rotor. Le système de remontage automatique selon l'invention peut, en outre, parfaitement être couplé avec un affichage de la réserve de marche qui viendrait se connecter, par exemple, sur le renvoi ou sur la roue intermédiaire de rochet.The present description has been given by way of non-limiting example of the invention. Those skilled in the art may consider other variants without departing from the scope of the invention as defined in the claims. Thus, the unidirectional bearing can be replaced by other unidirectional drive systems that would not transmit to the reducer mass movements for a direction of rotation. A snap connection or an asymmetrical profile wheel may also allow such a result. It may further be considered to decenter the oscillating mass 10 with respect to the movement and implement a mass of the micro-rotor type. The automatic winding system according to the invention can, in addition, perfectly be coupled with a display of the power reserve which would connect, for example, on the return or on the intermediate ratchet wheel.

Claims (7)

  1. Automatic winding system comprising:
    ∘ An oscillating weight (10) pivoting on an axis (AA),
    ∘ a unidirectional carrier system (12) comprising an entry, on which the oscillating weight (10) is firmly fixed, and an exit arranged to be driven by the entry in only one direction,
    ∘ a reducer (16) kinematically linking the exit of the unidirectional carrier system to the ratchet (30) of a barrel, and comprising a first wheel (18) driven, via said outlet, in an eccentric manner around said axis (AA), and comprising an exterior toothing of N1 teeth, characterised in that the said reducer (16) further comprises:
    ∘ a second directional wheel (26) fitted with an interior toothing of N2 teeth, with N2>N1 and with an external toothing linked kinematically to said ratchet,
    ∘ means of guidance set up so that said first wheel (18) rolls without sliding on the interior toothing of the second wheel (26).
  2. Automatic winding system according to claim 1, characterised in that said means of guidance consist of pins (20) of circular section, integral with the first wheel (18) and projecting from the surface of said first wheel (18), said pins being arranged to take their place in fixed circular openings (22), set up in a bridge of the movement, said fixed circular openings (22) being of a superior diameter to that of the pins (20).
  3. Automatic winding system comprising:
    ∘ an oscillating weight (10) pivoting on an axis (AA),
    ∘ a unidirectional carrier system (12) comprising an entry, on which is firmly mounted the oscillating weight (10), and an exit arranged to be driven by the entry in only one direction,
    ∘ A reducer (16) linking said kinematic exit to the ratchet (30) of a barrel,
    said reducer (16) comprising:
    ∘ A first solar wheel (38) fitted with a toothing of N1 teeth and mounted to rotate around the axis (AA),
    ∘ A second driving solar wheel (40) fitted with a toothing of N2 teeth, with N2>N1, fixed and superimposed in a coaxial manner to said first solar wheel,
    ∘ A satellite (42) mounted to rotate on said exit and simultaneously coupled with said first solar wheel (38) and said second solar driving wheel (40),
    an exit wheel (44) attached to the first solar wheel (38) and linked kinematically to said rachet (30),
    characterised in that said satellite is decomposed in a first (42a) and a second satellite (42b) set up in a coaxial manner, a first satellite (42a) being in direct contact with the second solar wheel (40), while a second satellite (42b) is in direct contact with the first solar wheel (38), said first (42a) and second (42b) satellites having different diameters.
  4. Winding system according to any one of claims 1 to 3, characterised in that said reducer is linked to said ratchet by an intermediate wheel (32) that is itself in relationship with an intermediate ratchet wheel (36) in direct contact with the ratchet (30).
  5. Winding system according to any one of claims 1 to 4, characterised in that it is set up on the plate of a module, to be coupled with a basic movement.
  6. Winding system according to any one of the previous claims,
    characterised in that the unidirectional driving system is a unidirectional bearing (12) comprising a first entry ring (12a) forming the entry of the unidirectional driving system and on which the oscillating weight (10) is firmly mounted, and a second outlet ring (12b) forming the exit of the unidirectional driving system and arranged to be driven by the first ring in only one direction.
  7. Winding system according to any one of the claims 4 to 6, characterised in that it comprises a coupling mobile coupled with the intermediate wheel (32), arranged to allow the barrel, via the intermediate wheel (32), not to unload during phases of assembly and disassembly of the automatic module.
EP11701103.1A 2010-01-26 2011-01-25 Automatic winding system Active EP2529278B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH00094/10A CH702590B1 (en) 2010-01-26 2010-01-26 automatic winding system.
PCT/EP2011/050956 WO2011092153A1 (en) 2010-01-26 2011-01-25 Automatic winding system

Publications (2)

Publication Number Publication Date
EP2529278A1 EP2529278A1 (en) 2012-12-05
EP2529278B1 true EP2529278B1 (en) 2018-08-22

Family

ID=43920954

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11701103.1A Active EP2529278B1 (en) 2010-01-26 2011-01-25 Automatic winding system

Country Status (3)

Country Link
EP (1) EP2529278B1 (en)
CH (1) CH702590B1 (en)
WO (1) WO2011092153A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2860590B1 (en) 2013-10-10 2016-04-06 Patek Philippe SA Genève Automatic winding device for a timepiece

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH268216A (en) * 1948-08-18 1950-05-15 Ebauches Sa Self-winding watch with a weight swinging in the center of the movement.
CH307687A (en) * 1953-03-19 1955-06-15 Erard Raoul Henri Automatic winding mechanism with oscillating weight for watch movement.
DE1141953B (en) * 1953-06-23 1962-12-27 Friedrich Mauthe G M B H Self-winding device for clocks, in particular wristwatches
US3104517A (en) * 1962-01-29 1963-09-24 United States Time Corp Planetary gear winding mechanism
CH426651A (en) * 1964-12-10 1966-05-14 Zenith Montres Self-winding watch
CH533326A (en) * 1968-10-07 1972-10-13 Omega Brandt & Freres Sa Louis Self-winding alarm clock
CH552843A (en) * 1971-07-22 1974-08-15
SU1118956A1 (en) * 1982-02-01 1984-10-15 Пензенский Политехнический Институт Wrist watch winding mechanism
DE69919509T2 (en) 1999-04-23 2005-09-01 Rolex Sa Clockwork with inertia self-winding
CH699325A2 (en) * 2008-08-14 2010-02-15 Temps Fab Du Movement timepiece a device for winding board.

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
CH702590A1 (en) 2011-07-29
WO2011092153A1 (en) 2011-08-04
CH702590B1 (en) 2015-03-13
EP2529278A1 (en) 2012-12-05

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