EP2420899A1 - Barrel for automatically winding timepiece - Google Patents

Barrel for automatically winding timepiece Download PDF

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Publication number
EP2420899A1
EP2420899A1 EP10173354A EP10173354A EP2420899A1 EP 2420899 A1 EP2420899 A1 EP 2420899A1 EP 10173354 A EP10173354 A EP 10173354A EP 10173354 A EP10173354 A EP 10173354A EP 2420899 A1 EP2420899 A1 EP 2420899A1
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EP
European Patent Office
Prior art keywords
friction surfaces
respect
angle
barrel according
drum
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
EP10173354A
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German (de)
French (fr)
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EP2420899B1 (en
Inventor
Serge Nicoud
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ETA Manufacture Horlogere Suisse SA
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ETA Manufacture Horlogere Suisse SA
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Application filed by ETA Manufacture Horlogere Suisse SA filed Critical ETA Manufacture Horlogere Suisse SA
Priority to EP10173354.1A priority Critical patent/EP2420899B1/en
Priority to JP2011177395A priority patent/JP5877668B2/en
Priority to US13/212,764 priority patent/US8573832B2/en
Priority to CN201110237465.5A priority patent/CN102375398B/en
Publication of EP2420899A1 publication Critical patent/EP2420899A1/en
Priority to HK12108933.9A priority patent/HK1168428A1/en
Priority to JP2015248238A priority patent/JP6138899B2/en
Application granted granted Critical
Publication of EP2420899B1 publication Critical patent/EP2420899B1/en
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/16—Barrels; Arbors; Barrel axles
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor
    • G04B1/185—Friction clutch between spring and spring cylinder
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/02—Centrifuges consisting of a plurality of separate bowls rotating round an axis situated between the bowls
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor

Abstract

The barrel (1) has a circular drum (10) including an inner side wall (11) whose friction surfaces (12) rotate with blocking structures forming round and square active projecting corners (15a, 15b) or an active returning corner at edges of the surfaces, where the structures are formed of notches (13). A drive spring (20) forms a coil comprising an outer turn (21). The spring is frictionably coupled with the wall, and freely slides against the wall in case of overtension of the spring. The surfaces are limited at downstream side with respect to a turn sliding direction by the round corner. An independent claim is also included for a timepiece comprising an automatic winding movement.

Description

La présente invention se rapporte au domaine de l'horlogerie. Elle concerne plus précisément un barillet destiné à équiper une pièce d'horlogerie à remontage automatique. Elle concerne également une pièce d'horlogerie équipée d'un tel barillet.The present invention relates to the field of watchmaking. It relates more specifically to a barrel for equipping a timepiece with automatic winding. It also relates to a timepiece equipped with such a barrel.

Des barillets pour pièces d'horlogerie à remontage automatique comportent classiquement un tambour dans lequel est logé un ressort moteur enroulé en spirale autour d'un arbre de barillet. Pour éviter toute surtension du ressort moteur, pouvant le faire céder ou endommager le rouage du dispositif de remontage automatique, le ressort moteur n'est pas fixé à la paroi latérale du tambour, mais accouplé à friction, par l'intermédiaire de sa dernière spire, à l'aide d'une lame élastique appelée bride glissante. L'accouplement à friction entre le ressort moteur et la paroi latérale du tambour doit être calculé pour qu'au-delà d'un couple moteur maximum déterminé, la dernière spire glisse le long de ladite paroi et diminue ainsi la tension du ressort moteur. L'état de surface de la paroi latérale intérieure du tambour ainsi que sa lubrification sont des facteurs influençant fortement le fonctionnement de cet accouplement à friction. Un autre facteur déterminant concerne la géométrie de la paroi latérale intérieure.Barrels for timepieces with automatic winding conventionally comprise a drum in which is housed a motor spring wound spirally around a barrel shaft. To avoid any overvoltage of the mainspring, which can cause it to yield or damage the gear of the automatic winding device, the mainspring is not fixed to the side wall of the drum, but frictionally coupled, by means of its last turn , using an elastic blade called sliding flange. The friction coupling between the mainspring and the side wall of the drum must be calculated so that beyond a determined maximum driving torque, the last turn slides along said wall and thus reduces the tension of the mainspring. The surface condition of the inner side wall of the drum as well as its lubrication are factors that strongly influence the operation of this friction clutch. Another determining factor is the geometry of the inner sidewall.

Selon l'état de la technique, la paroi latérale intérieure du tambour comporte des surfaces de frottement, alternant avec des découpes en forme d'encoches dans lesquelles l'extrémité du ressort moteur vient buter. La combinaison des effets de frottement et de butée de la dernière spire sur la paroi latérale, permet d'atteindre des couples moteurs maximums élevés, et donc une réserve de marche importante.According to the state of the art, the inner side wall of the drum has friction surfaces, alternating with cutouts in the form of notches in which the end of the mainspring abuts. The combination of friction and abutment effects of the last turn on the side wall, achieves maximum driving torque, and therefore a large power reserve.

Toutefois, une difficulté liée à la présence d'encoches dans la paroi latérale intérieure du tambour, est celle de l'usure. Le problème de l'usure est particulièrement gênant car il s'auto-amplifie et peut conduire à des dégâts importants, des dysfonctionnements ou même la rupture d'une pièce. Lorsque le frottement de la dernière spire du ressort moteur arrache des fines particules à la paroi, celles-ci rendent le frottement encore plus abrasif, ce qui produit encore plus de particules et accélère le phénomène d'usure. A la longue, l'accouplement à friction entre le ressort moteur et la paroi latérale du barillet peut être sérieusement affecté.However, a difficulty related to the presence of notches in the inner side wall of the drum is that of wear. The problem of wear is particularly troublesome because it self-amplifies and can lead to significant damage, malfunctions or even the breakage of a room. When the friction of the last turn of the mainspring pulls fine particles from the wall, these make the friction even more abrasive, which produces even more particles and accelerates the phenomenon of wear. In the long run, the friction coupling between the mainspring and the sidewall of the cylinder can be seriously affected.

Il est connu que la présence d'encoches dans la paroi latérale intérieure du tambour participe au phénomène d'usure du barillet. En effet, les encoches forment des angles vifs saillants situés en limite amont et aval des surfaces de frottement par rapport au sens de glissement de la dernière spire, c'est-à-dire en sortie et en entrée, respectivement, d'encoche. Sur ces angles vifs saillants, les pressions du ressort moteur sont très élevées. Ils peuvent alors s'émousser rapidement.It is known that the presence of notches in the inner side wall of the drum contributes to the wear phenomenon of the barrel. Indeed, the notches form sharp sharp corners located in the upstream and downstream limit of the friction surfaces with respect to the direction of sliding of the last turn, that is to say at the exit and entry, respectively, notch. On these sharp sharp angles, the pressures of the mainspring are very high. They can then dull quickly.

Selon un préjugé largement répandu chez l'homme de métier, les angles vifs saillants limitant les surfaces de frottement côté amont par rapport au sens de glissement de la dernière spire, sont principalement responsables de la génération, par usure, de particules accélérant le phénomène d'usure. En effet, ces angles jouent un rôle actif dans l'accouplement à friction, puisque l'extrémité de la dernière spire vient buter contre ces angles saillants en sortie d'encoche, contrairement aux angles vifs saillants en entrée d'encoche, qui sont pratiquement passifs dans l'accouplement à friction.According to a widespread prejudice to those skilled in the art, sharp sharp angles limiting the friction surfaces upstream side with respect to the sliding direction of the last turn, are mainly responsible for the generation, by wear, particles accelerating the phenomenon of 'wear. Indeed, these angles play an active role in the friction coupling, since the end of the last turn abuts against these protruding angles out of notch, in contrast to sharp angles protruding notch entry, which are virtually passive in the friction coupling.

Or, les observations menées dans le cadre de la présente invention montrent que, contrairement à ce qui est communément admis, les angles vifs saillants limitant les surfaces de frottement côté aval par rapport au sens de glissement de la dernière spire, jouent également un rôle important en étant précurseurs, par usure, de la génération de particules accélérant le phénomène d'usure. L'explication qui en est donnée est la suivante : Le mouvement de glissement de la dernière spire contre les surfaces de frottement est globalement lent en raison du quasi-équilibre permanent entre le couple moteur et le couple de friction. L'extrémité de la dernière spire du ressort moteur arrive donc lentement en entrée d'encoche et vient frotter contre l'angle vif saillant qui limite la surface de frottement côté aval, avec une vitesse faible. Or, à vitesse faible, l'efficacité de la lubrification est médiocre et le frottement est important. L'usure de l'angle vif saillant en entrée d'encoche est donc importante. La situation est légèrement différente pour ce qui est de l'angle vif saillant qui limite la surface de frottement côté amont par rapport au sens de glissement de la dernière spire. En effet, l'extrémité de la dernière spire du ressort moteur vient buter contre cet angle vif en sortie d'encoche, ce qui permet d'augmenter sensiblement sa tension jusqu'à la valeur de couple moteur maximum déterminée. Lorsque la tension du ressort moteur augmente au-delà de cette valeur, l'extrémité du ressort moteur sort de l'encoche en rompant brutalement le quasi-équilibre entre le couple moteur et le couple de friction. La sortie d'encoche se fait alors très rapidement. Or, à vitesse élevée, l'efficacité de la lubrification est bonne, ce qui limite fortement le frottement. Au final, aussi bien l'usure des angles vifs saillants en entrée d'encoche qu'en sortie d'encoche ont un rôle important dans la dégradation de la surface par usure, même si les premiers ne jouent pas de rôle actif de butée dans l'accouplement à friction entre la dernière spire du ressort moteur et la paroi latérale intérieure du tambour.However, the observations made in the context of the present invention show that, contrary to what is commonly admitted, sharp sharp angles limiting downstream friction surfaces with respect to the sliding direction of the last turn, also play an important role. being precursors, by wear, the generation of particles accelerating the phenomenon of wear. The explanation given is as follows: The sliding movement of the last turn against the friction surfaces is generally slow because of the quasi-permanent balance between the engine torque and the friction torque. The end of the last turn of the mainspring thus slowly arrives at the entrance of the notch and rubs against the protruding sharp angle which limits the friction surface on the downstream side, with a low speed. However, at low speed, the effectiveness of the lubrication is poor and the friction is important. The wear of the sharp angle protruding notch entry is important. The situation is slightly different with respect to the sharp protruding angle which limits the friction surface upstream with respect to the sliding direction of the last turn. Indeed, the end of the last turn of the motor spring abuts against this sharp angle at the exit of the notch, which allows to substantially increase its voltage up to the maximum determined motor torque value. When the tension of the mainspring increases beyond this value, the end of the motor spring comes out of the notch by breaking suddenly the quasi-equilibrium between the engine torque and the friction torque. The notch output is then very quickly. However, at high speed, the lubrication efficiency is good, which greatly limits the friction. In the end, both the sharp edges protruding at the notch entry and notch exit have an important role in the degradation of the surface by wear, even if the first do not play an active stop in the friction coupling between the last turn of the motor spring and the inner side wall of the drum.

Les investigations menées dans le cadre de cette invention, montrent donc clairement l'existence d'un problème d'usure méconnu en entrée d'encoche, et une explication est avancée pour expliquer ce phénomène. La présente invention a pour but de remédier à ce problème d'usure, en proposant une géométrie de paroi latérale intérieure de tambour ne comportant pas d'angles vifs saillants passifs. Plus précisément, l'invention concerne un barillet pour pièce d'horlogerie à remontage automatique comprenant un tambour d'axe AA muni d'une paroi latérale intérieure comportant des surfaces de frottement alternant avec des structures formant des angles saillants ou rentrants en limite des surfaces de frottement, et un ressort moteur formant un enroulement comportant une spire extérieure, laquelle est accouplée à friction avec la paroi latérale intérieure et libre de glisser contre la paroi latérale intérieure en cas de surtension du ressort moteur. Selon l'invention, les surfaces de frottement sont limitées, côté aval par rapport au sens de glissement de la spire extérieure, par un angle saillant arrondi ou un angle rentrant.The investigations carried out in the context of this invention, therefore clearly show the existence of an unknown wear problem at the entrance of notch, and an explanation is advanced to explain this phenomenon. The object of the present invention is to remedy this wear problem by proposing an internal drum side wall geometry that does not include passive sharp edges. More specifically, the invention relates to a cylinder for a timepiece with winding machine comprising an axle drum AA having an inner side wall having friction surfaces alternating with structures forming salient or reentrant angles at the boundary of the friction surfaces, and a motor spring forming a coil having an outer turn, which is frictionally coupled to the inner side wall and free to slide against the inner side wall in case of overvoltage of the mainspring. According to the invention, the friction surfaces are limited, downstream side with respect to the direction of sliding of the outer coil, by a rounded protruding angle or a re-entrant angle.

Grâce à la caractéristique précitée du barillet selon l'invention, la composante non directement utile de l'usure du tambour, c'est-à-dire celle concernant les angles vifs saillants passifs, est éliminée, et l'usure est limitée aux angles vifs saillants actifs. Le phénomène d'auto-entretien de l'usure et, par conséquent l'usure générale, s'en trouvent réduits. D'autres caractéristiques et avantages de la présente invention ressortiront plus clairement de la description détaillée qui suit d'un exemple de réalisation d'un barillet selon l'invention, cet exemple étant donné à titre purement illustratif et non limitatif seulement, en liaison avec le dessin annexé sur lequel :

  • les figures 1 et 2 sont des vues schématiques en coupe transversale d'un premier et d'un deuxième modes de réalisation d'un barillet selon l'invention en position armé.
Thanks to the aforementioned characteristic of the barrel according to the invention, the non-directly useful component of the wear of the drum, that is to say that concerning the sharp sharp angles passive, is eliminated, and the wear is limited to the angles bright, active highlights. The phenomenon of self-maintenance of wear and, consequently, general wear, are reduced. Other features and advantages of the present invention will emerge more clearly from the detailed description which follows of an exemplary embodiment of a cylinder according to the invention, this example being given purely by way of illustration and not only limiting, in conjunction with the appended drawing in which:
  • the Figures 1 and 2 are schematic cross-sectional views of first and second embodiments of a barrel according to the invention in the armed position.

Le barillet pour pièce d'horlogerie à remontage automatique représenté en figure 1 et référencé dans son ensemble 1, comporte classiquement un tambour 10 circulaire d'axe AA, muni d'une paroi latérale intérieure 11, dans lequel est logé un ressort moteur 20 formant un enroulement à spirales autour d'un arbre de barillet 30. Le ressort moteur 20 est fixé par son extrémité intérieure à une bonde 31, solidaire en rotation de l'arbre de barillet 30. A cet effet, la bonde 31 est munie d'un crochet de fixation 32.The timepiece cylinder with automatic winding represented in figure 1 and referenced as a whole 1, conventionally comprises a circular drum AA with axis, provided with an inner side wall 11, in which is housed a motor spring 20 forming a spiral winding around a barrel shaft 30. motor spring 20 is fixed by its inner end to a bung 31, integral in rotation with the barrel shaft 30. For this purpose, the bung 31 is provided with a fixing hook 32.

Pour éviter toute éventuelle surtension du ressort moteur 20 due au remontage automatique, son extrémité extérieure n'est pas fixée à la paroi latérale intérieure 11 du tambour 10. Le ressort moteur 20 comporte une spire extérieure 21, laquelle est accouplée à friction avec la paroi latérale intérieure 11. A cet effet, une lame élastique 40, appelée bride glissante, est fixée à l'extrémité extérieure du ressort moteur 20, par soudage, rivetage ou tout autre procédé connu de l'homme de métier. Interposée entre la spire extérieure 21 et l'avant dernière spire du ressort moteur 20, la bride glissante 40 exerce, sur la spire extérieure 21, une contrainte tendant à la plaquer contre la paroi latérale intérieure 11 du tambour 10. En variante, la bride glissante 40 est interposée entre la paroi latérale intérieure 11 du tambour 10 et la spire extérieure 21 du ressort moteur 20, et est elle-même plaquée contre ladite paroi. L'accouplement à friction ainsi réalisé entre le ressort moteur 20 et le tambour 10 permet d'armer le ressort moteur 20 jusqu'à un couple maximum déterminé. Au-delà de cette valeur limite, la spire extérieure 21 glisse contre la paroi 11, réduisant ainsi la tension et les risques de rupture du ressort moteur 20.To avoid any overvoltage of the motor spring 20 due to automatic winding, its outer end is not fixed to the inner side wall 11 of the drum 10. The motor spring 20 has an outer turn 21, which is frictionally coupled to the wall In this embodiment, an elastic blade 40, called sliding flange, is fixed to the outer end of the motor spring 20 by welding, riveting or any other method known to those skilled in the art. Interposed between the outer turn 21 and the penultimate turn of the motor spring 20, the sliding flange 40 exerts on the outer turn 21 a stress tending to press against the inner side wall 11 of the drum 10. In a variant, the flange sliding 40 is interposed between the inner side wall 11 of the drum 10 and the outer turn 21 of the motor spring 20, and is itself pressed against said wall. The friction coupling thus formed between the motor spring 20 and the drum 10 makes it possible to arm the motor spring 20 to a maximum determined torque. Beyond this limit value, the outer turn 21 slides against the wall 11, thus reducing the tension and the risks of rupture of the mainspring 20.

La paroi latérale intérieure 11 du tambour 10 comporte des surfaces de frottement 12 alternant avec des structures de blocage en forme d'encoches 13. Les surfaces de frottement 12 s'étendent circulairement par rapport à l'axe AA du tambour 10. Les encoches 13 comportent deux flancs 14a et 14b, respectivement en entrée et en sortie d'encoche, venant couper les surfaces de frottement 12. On précise que l'entrée et la sortie des encoches 13 sont définies par rapport au sens de glissement de la spire extérieure 21 du ressort moteur 20 contre la paroi 11, indiqué par une flèche sur les figures 1 et 2. Lorsque la spire extérieure 21 du ressort moteur 20 glisse contre la paroi 11, son extrémité entre ainsi dans une encoche 13 par le flanc 14a et en sort par le flanc 14b.The inner sidewall 11 of the drum 10 has friction surfaces 12 alternating with notch-shaped locking structures 13. The friction surfaces 12 extend circularly with respect to the axis AA of the drum 10. The notches 13 comprise two flanks 14a and 14b, respectively at the entrance and at the notch exit, cutting the friction surfaces 12. It is specified that the entry and the exit of the notches 13 are defined with respect to the direction of sliding of the outer turn 21 of the motor spring 20 against the wall 11, indicated by an arrow on the Figures 1 and 2 . When the outer turn 21 of the motor spring 20 slides against the wall 11, its end thus enters a notch 13 by the sidewall 14a and leaves the side 14b.

Les flancs 14b en sortie d'encoches 13 sont actifs dans l'accouplement à friction entre le ressort moteur 20 et le tambour 10. Ils sont destinés à s'opposer au mouvement de glissement de l'extrémité du ressort moteur 20 le long de la paroi latérale intérieure 11, en formant des surfaces de blocage contre lesquelles l'extrémité du ressort moteur 20 vient buter. Leur inclinaison est optimisée à cet effet. Les flancs 14b en sortie d'encoches 13 coupent les surfaces de frottement 12 côté amont par rapport au sens de glissement de la spire extérieure 21, en formant un angle saillant 15b dont la fonction est également de retenir le glissement du ressort moteur 20. Les angles saillants 15b sont, de préférence, des angles vifs car ils agissent sur le glissement du ressort moteur 20 par effet de frottement, lequel est d'autant plus élevé que l'angle est vif. Par angle vif, on entend un angle ayant un rayon de courbure nul ou faible. A titre indicatif, le rayon de courbure d'un tel angle est compris entre 0.02 et 0.1 mm L'angle saillant 15b, qui limite les surfaces de frottement 12, peut, en variante, être légèrement arrondi. Son effet d'opposition au mouvement de glissement du ressort moteur 20 est alors sensiblement réduit, en raison de la diminution du frottement.The flanks 14b at the outlet of notches 13 are active in the friction coupling between the mainspring 20 and the drum 10. They are intended to oppose the sliding movement of the end of the motor spring 20 along the inner side wall 11, forming locking surfaces against which the end of the motor spring 20 abuts. Their inclination is optimized for this purpose. The flanks 14b at the outlet of the notches 13 intersect the friction surfaces 12 on the upstream side with respect to the sliding direction of the outer turn 21, forming a projecting angle 15b whose function is also to retain the sliding of the motor spring 20. The protruding angles 15b are preferably sharp corners because they act on the sliding of the motor spring 20 by friction effect, which is even higher than the angle is sharp. By sharp angle is meant an angle having a radius of curvature zero or low. As an indication, the radius of curvature of such an angle is between 0.02 and 0.1 mm The salient angle 15b, which limits the friction surfaces 12, may alternatively be slightly rounded. Its effect of opposition to the sliding movement of the motor spring 20 is then substantially reduced, due to the decrease in friction.

Contrairement aux flancs 14b en sortie d'encoches 13, les flancs 14a en entrée d'encoches 13 sont passifs dans l'accouplement à friction entre le ressort moteur 20 et le tambour 10. Ils coupent les surfaces de frottement 12 côté aval par rapport au sens de glissement de la spire extérieure 21, en formant un angle saillant 15a. Selon l'invention, les angles saillants 15a sont arrondis. Par angle arrondi, on entend un angle ayant un rayon de courbure élevé par rapport à l'angle vif. A titre indicatif, les angles 15a en entrée d'encoches 13 possèdent un rayon de courbure supérieur à 0.15mm Cette caractéristique du barillet 1 selon l'invention permet de réduire l'usure générale de la paroi latérale intérieure 11 et du ressort moteur 20. En effet, le frottement du ressort moteur 20, et en particulier de son extrémité, est faible sur ces angles arrondis 15a en comparaison du frottement sur les angles vifs 15b, car la pression de contact est plus faible. L'usure des angles 15a en entrée d'encoches 13 et le phénomène d'auto-amplification de l'usure s'en trouvent réduits.. L'augmentation du rayon de courbure de l'angle permet également une meilleure répartition du lubrifiant en évitant la formation d'un dépôt non fonctionnel dans l'angle formé par le flanc d'entrée d'encoche 14a et le fond d'encoche 13. Il est à noter que l'accouplement à friction entre le ressort moteur 20 et la paroi latérale intérieure 11 n' est pas affecté par le profil arrondi des angles 15a en entrée d'encoches 13, car ceux-ci sont passifs dans l'accouplement à friction. Sur le long terme, l'effet est même positif puisque la réduction de l'usure du ressort moteur 20 et de la paroi latérale intérieure 11, freine la dégradation de l'accouplement à friction dans le temps. La longévité du barillet 1 en est augmentée.Contrary to the flanks 14b at the exit of notches 13, the flanks 14a at the entrance of notches 13 are passive in the friction coupling between the mainspring 20 and the drum 10. They cut the friction surfaces 12 downstream side with respect to the direction of sliding of the outer turn 21, forming a projecting angle 15a. According to the invention, the projecting angles 15a are rounded. By rounded corner is meant an angle having a high radius of curvature with respect to the sharp angle. As an indication, the angles 15a at the entrance of notches 13 have a radius of curvature greater than 0.15 mm This characteristic of the cylinder 1 according to the invention reduces the general wear of the inner side wall 11 and the mainspring 20. Indeed, the friction of the motor spring 20, and in particular of its end, is small on these rounded corners 15a in comparison with the friction on the sharp corners 15b, because the contact pressure is lower. The wear of the angles 15a at the entrance of notches 13 and the phenomenon of self-amplification of the wear are reduced. The increase in the radius of curvature of the angle also allows a better distribution of the lubricant. avoiding the formation of a deposit functional in the angle formed by the notch inlet flank 14a and the notch bottom 13. It should be noted that the friction coupling between the motor spring 20 and the inner side wall 11 is not affected by the rounded profile angles 15a at the entrance of notches 13, because they are passive in the friction coupling. In the long run, the effect is even positive since the reduction of the wear of the motor spring 20 and the inner side wall 11, hinders the degradation of the friction coupling over time. The longevity of the barrel 1 is increased.

On se réfère maintenant à la figure 2, qui représente un deuxième mode de réalisation du barillet selon l'invention. Le barillet pour pièce d'horlogerie à remontage automatique représenté en figure 2 et référencé dans son ensemble 1, se distingue du barillet décrit précédemment par la géométrie de la paroi latérale intérieure 11 du tambour 10.We now refer to the figure 2 , which represents a second embodiment of the barrel according to the invention. The timepiece cylinder with automatic winding represented in figure 2 and referenced as a whole 1, is distinguished from the barrel described above by the geometry of the inner side wall 11 of the drum 10.

Comme précédemment, la paroi latérale intérieure 11 comporte des surfaces de frottement 12 alternant avec des structures de blocage. Celles-ci forment des marches 16, et non des encoches 13, comportant un flanc 17. Les surfaces de frottement 12 s'étendent légèrement en spirale par rapport à l'axe AA du tambour 10. Les flancs 17 coupent les surfaces de frottement 12 en formant un angle saillant 18a, qui les limite côté amont par rapport au sens de glissement de la spire extérieure 21, et un angle rentrant 18b, qui les limite côté aval. Les flancs 17 et les angles saillants 18a sont actifs dans l'accouplement à friction entre le ressort moteur 20 et le tambour 10. Pour cette raison, et comme explicité précédemment, les angles saillants 18a sont de préférence des angles vifs, mais peuvent également être, en variante, légèrement arrondis.As before, the inner side wall 11 has friction surfaces 12 alternating with locking structures. These form steps 16, not notches 13, having a flank 17. The friction surfaces 12 extend slightly spirally with respect to the axis AA of the drum 10. The flanks 17 intersect the friction surfaces 12 forming a projecting angle 18a, which limits them upstream side with respect to the sliding direction of the outer turn 21, and a re-entrant angle 18b, which limits them downstream side. The flanks 17 and the projecting angles 18a are active in the friction coupling between the motor spring 20 and the drum 10. For this reason, and as explained above, the projecting angles 18a are preferably sharp corners, but can also be alternatively, slightly rounded.

En revanche, dans ce mode de réalisation, les angles saillants passifs vis-à-vis de l'accouplement à friction entre le ressort moteur 20 et la paroi latérale intérieure 11 du tambour 10, sont totalement absents. Les surfaces de frottement 12 sont limitées côté aval par rapport sens de glissement de la spire extérieure 21, par un angle rentrant 18b, vif ou arrondi, n'ayant aucune fonction dans l'accouplement à friction. Ce mode de réalisation représente un cas limite du mode de réalisation décrit précédemment, dans lequel les angles saillants 15a en entrée d'encoche 13 ont un rayon de courbure infini et l'entrée d'encoche 13 est totalement éliminée. Le barillet 1 ainsi décrit possède les mêmes avantages de réduction de l'usure et d'augmentation de la longévité, que le barillet 1 décrit en regard de la figure 1.On the other hand, in this embodiment, the passive protruding angles with respect to the friction coupling between the motor spring 20 and the inner side wall 11 of the drum 10, are totally absent. The friction surfaces 12 are limited on the downstream side with respect to the sliding direction of the outer turn 21, by a re-entrant angle 18b, sharp or rounded, having no function in the friction coupling. This mode embodiment represents a limiting case of the embodiment described above, in which the projecting angles 15a at the notch inlet 13 have an infinite radius of curvature and the notch inlet 13 is completely eliminated. The barrel 1 thus described has the same advantages of reducing wear and increasing longevity, that the barrel 1 described next to the figure 1 .

Ainsi a été décrit un barillet pour pièce d'horlogerie à remontage automatique dont la géométrie permet est étudiée pour réduire son usure. Bien entendu, le barillet selon l'invention ne se limite pas au mode de réalisation qui vient d'être décrit et diverses modifications et variantes simples peuvent être envisagées par l'homme du métier sans sortir du cadre de l'invention tel que défini par les revendications annexées.Thus has been described a barrel for timepiece with automatic winding whose geometry allows is studied to reduce its wear. Of course, the barrel according to the invention is not limited to the embodiment which has just been described and various simple modifications and variants can be envisaged by those skilled in the art without departing from the scope of the invention as defined by the appended claims.

Claims (9)

Barillet pour pièce d'horlogerie à remontage automatique comprenant un tambour (10) d'axe AA muni d'une paroi latérale intérieure (11) comportant des surfaces de frottement (12) alternant avec des structures de blocage (13, 16) formant des angles saillants (15a, 15b, 17a) ou rentrants en limite des surfaces de frottement (12), et un ressort moteur (20) formant un enroulement comportant une spire extérieure (21), laquelle est accouplée à friction avec ladite paroi latérale intérieure (11) et libre de glisser contre la paroi latérale intérieure (11) en cas de surtension du ressort moteur (20), caractérisé en ce que lesdites surfaces de frottement (12) sont limitées, côté aval par rapport au sens de glissement de ladite spire extérieure (21), par un angle saillant arrondi (15a) ou un angle rentrant (18b).Self-winding timepiece cylinder comprising a drum (10) of axis AA provided with an inner side wall (11) having friction surfaces (12) alternating with locking structures (13, 16) forming protruding angles (15a, 15b, 17a) or recesses at the limit of the friction surfaces (12), and a driving spring (20) forming a winding having an outer turn (21), which is frictionally coupled to said inner side wall ( 11) and free to slide against the inner side wall (11) in case of overvoltage of the mainspring (20), characterized in that said friction surfaces (12) are limited, downstream side with respect to the sliding direction of said coil outer portion (21), by a rounded projecting angle (15a) or a re-entrant angle (18b). Barillet selon la revendication 1, caractérisé en ce que lesdites structures forment des encoches (13) comportant un flanc (14a) en entrée venant couper les surfaces de frottement (12) côté aval par rapport au sens de glissement de ladite spire extérieure (21), en formant un angle saillant arrondi (15a).Barrel according to claim 1, characterized in that said structures form notches (13) having an inlet flank (14a) for cutting the friction surfaces (12) on the downstream side with respect to the sliding direction of said outer turn (21). forming a rounded protruding angle (15a). Barillet selon la revendication 2, caractérisé en ce que ledit angle saillant (15a) possède un rayon de courbure supérieur à 0.15 mmBarrel according to claim 2, characterized in that said projecting angle (15a) has a radius of curvature greater than 0.15 mm Barillet selon l'une des revendications 2 et 3, caractérisé en ce que lesdites surfaces de frottement (12) s'étendent circulairement par rapport à l'axe AA du tambour (10).Barrel according to one of claims 2 and 3, characterized in that said friction surfaces (12) extend circularly with respect to the axis AA of the drum (10). Barillet selon l'une des revendications 2 à 4, caractérisé en ce que lesdites encoches (13) comportent un flanc (14b) en sortie venant couper lesdites surfaces de frottement (12) côté amont par rapport au sens de glissement de ladite spire extérieure (21), en formant un angle saillant vif (15b).Barrel according to one of claims 2 to 4, characterized in that said notches (13) comprise an outlet flank (14b) cutting said friction surfaces (12) upstream side with respect to the sliding direction of said outer turn ( 21), forming a sharp protruding angle (15b). Barillet selon la revendication 1, caractérisé en ce que lesdites structures forment des marches (16) comportant un flanc (17) venant couper lesdites surfaces de frottement (12) côté aval par rapport au sens de glissement de ladite spire extérieure (21), en formant un angle rentrant (18b).Barrel according to claim 1, characterized in that said structures form steps (16) having a flank (17) cutting said friction surfaces (12) on the downstream side with respect to the sliding direction of said outer turn (21), forming a reentrant angle (18b). Barillet selon la revendication 6, caractérisé en ce que lesdites surfaces de frottement (12) s'étendent en spirale par rapport à l'axe AA du tambour (10).Barrel according to claim 6, characterized in that said friction surfaces (12) extend spirally with respect to the axis AA of the drum (10). Barillet selon l'une des revendications 6 et 7, caractérisé en ce que ledit flanc (17) vient couper lesdites surfaces de frottement (12) côté amont par rapport au sens de glissement de ladite spire extérieure (21), en formant un angle saillant (18a).Barrel according to one of claims 6 and 7, characterized in that said flank (17) cuts said friction surfaces (12) upstream side with respect to the sliding direction of said outer turn (21), forming a salient angle (18a). Pièce d'horlogerie munie d'un mouvement à remontage automatique, alimentée par un barillet selon les revendications 1 à 8.Timepiece provided with a self-winding movement, powered by a barrel according to claims 1 to 8.
EP10173354.1A 2010-08-19 2010-08-19 Barrel for automatically winding timepiece Active EP2420899B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP10173354.1A EP2420899B1 (en) 2010-08-19 2010-08-19 Barrel for automatically winding timepiece
JP2011177395A JP5877668B2 (en) 2010-08-19 2011-08-15 Automatic watch barrel
US13/212,764 US8573832B2 (en) 2010-08-19 2011-08-18 Barrel for a self winding timepiece
CN201110237465.5A CN102375398B (en) 2010-08-19 2011-08-18 Barrel for a self winding timepiece
HK12108933.9A HK1168428A1 (en) 2010-08-19 2012-09-12 Barrel for a self-winding timepiece
JP2015248238A JP6138899B2 (en) 2010-08-19 2015-12-21 Automatic watch barrel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10173354.1A EP2420899B1 (en) 2010-08-19 2010-08-19 Barrel for automatically winding timepiece

Publications (2)

Publication Number Publication Date
EP2420899A1 true EP2420899A1 (en) 2012-02-22
EP2420899B1 EP2420899B1 (en) 2018-12-19

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Application Number Title Priority Date Filing Date
EP10173354.1A Active EP2420899B1 (en) 2010-08-19 2010-08-19 Barrel for automatically winding timepiece

Country Status (5)

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US (1) US8573832B2 (en)
EP (1) EP2420899B1 (en)
JP (2) JP5877668B2 (en)
CN (1) CN102375398B (en)
HK (1) HK1168428A1 (en)

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Publication number Priority date Publication date Assignee Title
EP2977827A1 (en) * 2014-07-22 2016-01-27 Montres Breguet SA Clock barrel with improved force transmission
EP3220206A1 (en) 2016-03-16 2017-09-20 Rolex Sa Clock transmission device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2657794B1 (en) * 2012-04-25 2017-02-01 ETA SA Manufacture Horlogère Suisse Barrel spring and arbour

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US1522073A (en) * 1923-10-13 1925-01-06 Daniel E Odom Spring motor
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DE1252591B (en) * 1967-10-19 W Schwab-Feller Uhrfederfabrik ,Phma", Buren/Aare (Schweiz) Spring fence for the mainspring of clockworks
US1522073A (en) * 1923-10-13 1925-01-06 Daniel E Odom Spring motor
CH280369A (en) * 1949-03-08 1952-01-15 Zodiac Motor spring development indicator device for a self-winding watch.

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2977827A1 (en) * 2014-07-22 2016-01-27 Montres Breguet SA Clock barrel with improved force transmission
US9513601B2 (en) 2014-07-22 2016-12-06 Montres Breguet S.A. Timepiece barrel with improved transmission of force
EP3220206A1 (en) 2016-03-16 2017-09-20 Rolex Sa Clock transmission device
US10222745B2 (en) 2016-03-16 2019-03-05 Rolex Sa Watch transmission device

Also Published As

Publication number Publication date
JP5877668B2 (en) 2016-03-08
US8573832B2 (en) 2013-11-05
JP2012042469A (en) 2012-03-01
CN102375398B (en) 2014-03-19
US20120044789A1 (en) 2012-02-23
HK1168428A1 (en) 2012-12-28
CN102375398A (en) 2012-03-14
EP2420899B1 (en) 2018-12-19
JP2016075701A (en) 2016-05-12
JP6138899B2 (en) 2017-05-31

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