EP1213626A1 - Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch - Google Patents

Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch Download PDF

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Publication number
EP1213626A1
EP1213626A1 EP00204370A EP00204370A EP1213626A1 EP 1213626 A1 EP1213626 A1 EP 1213626A1 EP 00204370 A EP00204370 A EP 00204370A EP 00204370 A EP00204370 A EP 00204370A EP 1213626 A1 EP1213626 A1 EP 1213626A1
Authority
EP
European Patent Office
Prior art keywords
spring
central shaft
generator
oscillating mass
notch
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
EP00204370A
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German (de)
French (fr)
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EP1213626B1 (en
Inventor
Jean-Philippe Rebeaud
Denis Burdet
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.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
Ebauchesfabrik ETA AG
Eta SA Fabriques dEbauches
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ebauchesfabrik ETA AG, Eta SA Fabriques dEbauches filed Critical Ebauchesfabrik ETA AG
Priority to DE60042597T priority Critical patent/DE60042597D1/en
Priority to EP00204370A priority patent/EP1213626B1/en
Priority to US09/987,997 priority patent/US6587401B2/en
Priority to JP2001371011A priority patent/JP4188589B2/en
Priority to CNB011435313A priority patent/CN1239968C/en
Publication of EP1213626A1 publication Critical patent/EP1213626A1/en
Priority to HK02109068A priority patent/HK1047322A1/en
Application granted granted Critical
Publication of EP1213626B1 publication Critical patent/EP1213626B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C10/00—Arrangements of electric power supplies in time pieces

Definitions

  • the present invention relates to an anti-shock transmission device for driving the rotor of an electric generator by an oscillating mass in a portable device, comprising a central shaft and an intermediate gear, of which one is likely to be rotated by mass movements oscillating and the other is coupled to the generator rotor by a kinematic link, the central shaft and the intermediate wheel having a common axis of rotation, and a spring spiral shaped having an inner end coupled to the central shaft and a outer end coupled to the intermediate wheel.
  • the invention also relates to a wristwatch with an electric generator driven by a mass oscillating via such a transmission device.
  • Such a device can be used in particular in a device of small volume worn by a user whose movements will cause the mass to swing oscillating, which is usually rotary.
  • This is for example, but not limitatively, of a wristwatch whose watch movement and / or others functional elements are powered by an energy accumulator charged by the electric generator.
  • the oscillating mass generally rotates at a speed fairly low in normal operation and the generator rotor should rotate at high speed to produce sufficient electrical voltage it is necessary to use a multiplying transmission between these two organs.
  • the required transmission ratio is in the range of 100 and it is usually obtained by means of a two-stage gear transmission.
  • Such an arrangement may be damaged in the event of an impact caused by example by an accidental fall of the device and producing a very strong acceleration of the oscillating mass.
  • their inertia creates a non-resistant torque negligible, due to the high transmission ratio.
  • Such a shock can thus permanently damage the transmission or generator. This is why various anti-shock devices have been proposed for such a transmission.
  • the object of the present invention is to improve a transmission device anti-shock of this kind, avoiding the need for friction damping and creating a simple and inexpensive construction that prevents breakage of the spring or its attachments when the device is struck by a certain amount of force, for example example (but not limited to) up to the value of 5,000 g prescribed by the standard ISO 1413.
  • the invention relates to an anti-shock transmission device for genre indicated in the preamble, characterized in that the central shaft has a series notches distributed around its periphery and in that the inner end of the spring is arranged to engage in any one of said notches by the elasticity of the spring and being able to free itself from the notch when it is subjected to sufficient force in at least one direction of rotation of the device.
  • each notch has an inclined flank and the inner end of the spring has an inward projecting portion, capable of abutting against said inclined flank for receive said force and slide over it as soon as said force exceeds a limit value.
  • Mechanism 1 is constructed in a conventional manner. Its bearing support central 6, fixed to the plate 3 by means of a screw 7 and a tubular nut 8, supports a toothed wheel 10 by a ball bearing 11.
  • the semi-circular oscillating mass 2 is fixed to the toothed wheel 10 by means of a ring 12 and can rotate around of the central axis 13 of the watch.
  • the rotor 4 of the generator comprises a permanent magnet 14 fixed on a shaft 15 provided with a pinion 16.
  • the pivots at the end of the shaft 15 are mounted by respective stones 17 and 18 in the plate 3 and in a bridge 19 which is fixed to the stator 20 of the generator by means of feet 21.
  • the magnet 14 of the rotor rotates in a recess 22 of the stator.
  • the transmission device 5 carries a central shaft 24 provided with a pinion 25 and which meshes with the teeth 26 of the wheel 10, an intermediate wheel formed by a barrel 27 provided with an external toothing 28 which meshes with the pinion 16 of the rotor 4, and a spiral spring 30 which connects elastically in rotation the shaft 24 and the barrel 27.
  • the shaft 24 is rotatably mounted in the plate 3 and the bridge 19 by stones respectively 31 and 32 to rotate around an axis 33.
  • the barrel 27 will be described in more detail with reference to Figures 2 to 6.
  • the figure 3 shows the shape of the spiral spring 30 in the rest state, before it is mounted in the barrel 27.
  • Its inner end has a bent portion 34 at an angle obtuse 35 of about 135 ° with the adjacent part of the first inner turn 36 of the spring.
  • the bent part 34 has a free end 37.
  • the outer end 38 of the spring is welded to an anchor plate 39.
  • the spring 30 is formed of a steel blade with a section of 0.04 x 0.5 mm and present at rest between its two ends, 8.5 turns which are separated from each other by an interval.
  • the inner coil 36 has a diameter of about 1.3 mm and the outer coil 40 has a diameter of about 3.4 mm.
  • spiral springs of this kind are usually made in groups of three to obtain the desired interval between the turns at rest.
  • the springs are formed by winding the three blades around a mandrel with three pliers to hold the ends interior of the springs, then removing internal tensions by treatment thermal. This process automatically creates the bent part 34 at the end of each spring, i.e. obtaining this end shape requires no additional operation.
  • the barrel 27 has a part molded plastic comprising a cylindrical drum 41, a flat bottom 42 which pivots around a cylindrical seat 43 of the shaft 24, the toothing 28 around the periphery of the barrel 41, as well as three feet 44 used to fix a cover 45 which constitutes the face upper barrel and which pivots around a bearing 46 of the shaft 24.
  • the courvercle is deleted in Figures 5 to 6 to show the inside of the barrel.
  • the plaque anchor 39 of the spring 30 is locked in a recess 47 of the drum 41.
  • the central shaft 24 has an enlarged part 50 provided with a series of notches 51 distributed around its periphery.
  • four notches 51 are provided having, in a plane perpendicular to the shaft 24, an asymmetrical profile substantially V-shaped, the most branch long forms an inclined flank 52 (FIG. 5), while its other flank 53 extends approximately radially to an edge 54 of the notch.
  • the spring 30 can rest on spans 55 in an arc of a circle which are bordered by two flanges 56 ( Figure 2) to guide the spring.
  • the defined diameter by the spans 55 is slightly larger than that of the first turn 36 of the spring at rest, so that the elasticity of the spring tends to engage its end angled 34 in any one of the notches 51 and to lightly tighten the first turn 36 on the bearing surfaces 55 of the tree.
  • the oscillating mass 2 When the watch does not undergo movement, the oscillating mass 2 is stopped and the transmission device 5 does not transmit any torque to the rotor 4 of the generator, except possibly a low magnet positioning torque 14 relative to the stator 20. The device 5 is then in the equilibrium position shown in Figure 4.
  • the mass oscillating 2 starts to rotate in any direction and causes the shaft to rotate 24 via the toothing 26 and the pinion 25.
  • the spring 30 is then energized and transmits a torque to the barrel 27, which also starts to rotate and causes it to rotate fast the rotor 4 via the toothing 28 and the pinion 16.
  • the device reaches the position shown in FIG. 7, where the inclined flank 52 exerts a force F, approximately perpendicular to the sidewall 52, on the end 37 of the spring. If the force F exceeds a certain limit capable of pushing the end 37 outwards, it slides on the inclined flank 52 towards the outside and escapes from the notch from the position of Figure 8, so that the spring and the barrel rotate slower than the tree.
  • the end 37 of the spring thanks to the elasticity of the latter, will tend to automatically engage in one of the following notches 51 and there remain engaged to transmit torque again to the spring when the dynamic conditions will allow this.
  • FIG. 6 represents a situation where the torque applied by the shaft 24 to the spring in direction B has such a high value that all the turns are pressed against the shaft, except the end part of the outer coil.
  • the absolute value of this torque is substantially the same as in the case illustrated in Figure 5, but the force resulting between the outer end 38 of the spring and the anchor plate 39 is that a fraction of the force to be transmitted for the same torque at the spans 55 of the tree, because it acts with a much larger lever arm.
  • a rupture of the weld between the elements 38 and 39 is not to fear for such a value of the torque to be transmitted.
  • a sliding flange system of the type well known for barrels driving mechanical watch movements.
  • the scope of the present invention is not limited to watches and can be extended in particular to all portable devices fitted with a generator electric, for example mobile phones, measuring devices or medical devices.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Electric Clocks (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

An anti shock drive for a watch electric generator has an oscillating mass driving a generator rotor through a spring (30) connected to the toothed intermediate wheel (28) with end engaging asymmetric V-shaped serrations (51) in the central shaft (24)

Description

La présente invention concerne un dispositif de transmission antichoc pour l'entraínement du rotor d'une génératrice électrique par une masse oscillante dans un appareil portable, comportant un arbre central et une roue intermédiaire dentée, dont l'un est susceptible d'être entraíné en rotation par des mouvements de la masse oscillante et l'autre est couplé au rotor de la génératrice par une liaison cinématique, l'arbre central et la roue intermédiaire ayant un axe de rot ation commun, et un ressort en forme de spirale ayant une extrémité intérieure couplée à l'arbre central et une extrémité extérieure couplée à la roue intermédiaire. L'invention concerne aussi une montre-bracelet comportant une génératrice électrique entraínée par une masse oscillante via un tel dispositif de transmission.The present invention relates to an anti-shock transmission device for driving the rotor of an electric generator by an oscillating mass in a portable device, comprising a central shaft and an intermediate gear, of which one is likely to be rotated by mass movements oscillating and the other is coupled to the generator rotor by a kinematic link, the central shaft and the intermediate wheel having a common axis of rotation, and a spring spiral shaped having an inner end coupled to the central shaft and a outer end coupled to the intermediate wheel. The invention also relates to a wristwatch with an electric generator driven by a mass oscillating via such a transmission device.

Un tel dispositif est utilisable en particulier dans un appareil de petit volume porté par un usager dont les mouvements provoqueront le balancement de la masse oscillante, qui est habituellement rotative. Il s'agit par exemple, mais non limitativement, d'une montre-bracelet dont le mouvement d'horlogerie et/ou d'autres éléments fonctionnels sont alimentés par un accumulateur d'énergie chargé par la génératrice électrique. Comme la masse oscillante tourne généralement à une vitesse assez faible en fonctionnement normal et que le rotor de la génératrice doit tourner à une vitesse élevée pour produire une tension électrique suffisante, il est nécessaire d'utiliser une transmission multiplicatrice entre ces deux organes. Dans les cas où le rotor de la génératrice comporte un seul élément permanent tournant sur lui-même, le rapport de transmission nécessaire est de l'ordre de 100 et il est habituellement obtenu au moyen d'une transmission à deux étages d'engrenages.Such a device can be used in particular in a device of small volume worn by a user whose movements will cause the mass to swing oscillating, which is usually rotary. This is for example, but not limitatively, of a wristwatch whose watch movement and / or others functional elements are powered by an energy accumulator charged by the electric generator. As the oscillating mass generally rotates at a speed fairly low in normal operation and the generator rotor should rotate at high speed to produce sufficient electrical voltage it is necessary to use a multiplying transmission between these two organs. In cases where the generator rotor has a single permanent element rotating on itself, the required transmission ratio is in the range of 100 and it is usually obtained by means of a two-stage gear transmission.

Un tel agencement peut subir des dommages en cas de choc causé par exemple par une chute accidentelle de l'appareil et produisant une très forte accélération de la masse oscillante. En dépit de la faible masse du rotor et du deuxième étage de la transmission, leur inertie crée un couple résistant non négligeable, à cause du rapport de transmission élevé. Un tel choc peut ainsi endommager définitivement la transmission ou la génératrice. C'est pourquoi divers dispositifs anti-choc ont été proposés pour une transmission de ce genre.Such an arrangement may be damaged in the event of an impact caused by example by an accidental fall of the device and producing a very strong acceleration of the oscillating mass. Despite the low mass of the rotor and the second stage of the transmission, their inertia creates a non-resistant torque negligible, due to the high transmission ratio. Such a shock can thus permanently damage the transmission or generator. This is why various anti-shock devices have been proposed for such a transmission.

Dans la demande de brevet EP 0 326 312, il est prévu une transmission à friction entre la masse oscillante et le rotor de la génératrice électrique. La friction est calculée de façon que la roue d'un mobile intermédiaire patine sur son arbre quand le couple à transmettre dépasse une valeur admissible. Toutefois, avec un tel dispositif à friction, la valeur du couple limite peut varier considérablement, d'une part à cause de la difficulté d'obtenir une friction de valeur constante dans une fabrication en grande série, et d'autre part à cause des inévitables variations des conditions de friction à l'usage.In patent application EP 0 326 312, a transmission is provided to friction between the oscillating mass and the rotor of the electric generator. Friction is calculated so that the wheel of an intermediate mobile slips on its shaft when the torque to be transmitted exceeds an admissible value. However, with such a device to friction, the value of the limit torque can vary considerably, on the one hand because of the difficulty of obtaining friction of constant value in large-scale manufacturing because of the inevitable variations in friction conditions at use.

Dans la demande de brevet EP 0 791 867, il est proposé un dispositif de transmission du genre indiqué en préambule ci-dessus. Dans une forme de réalisation illustrée par les figures 16 à 18 du document cité, l'extrémité intérieure d'un ressort plat en forme de spirale est fixée rigidement à l'arbre central entraíné par la masse oscillante, tandis que son extrémité extérieure est fixée rigidement à la roue intermédiaire qui est en prise avec le pignon du rotor de la génératrice. Le ressort a une rigidité suffisante pour ne subir pratiquement aucune déformation en fonctionnement normal. Lors d'un entraínement de la masse oscillante un peu supérieur à la normale, par exemple à l'occasion d'un mouvement brusque d'une montre portée au poignet, le ressort peut se déformer suffisamment pour éviter des dommages aux engrenages. Lors d'une accélération plus importante de la masse oscillante, par exemple si la montre tombe par terre, il est vraisemblable que les fixations du ressort spiral résisteront. Par contre, les contraintes subies par le ressort spiral lui-même risquent de conduire à une déformation irréversible ou à la rupture du ressort ou de ses attaches.In patent application EP 0 791 867, a device is proposed. transmission of the kind indicated in the preamble above. In one embodiment illustrated by Figures 16 to 18 of the cited document, the inner end of a spring flat in the form of a spiral is rigidly fixed to the central shaft driven by the mass oscillating, while its outer end is rigidly fixed to the wheel intermediate which engages the pinion of the generator rotor. The spring has sufficient rigidity to undergo practically no deformation in normal running. During a training of the oscillating mass a little higher than normal, for example during a sudden movement of a watch worn on the wrist, the spring can be deformed enough to avoid damage to gears. During a greater acceleration of the mass oscillating, for example if the watch falls on the ground, it is likely that the spiral spring fixings will resist. On the other hand, the stresses undergone by the spring hairspring itself may lead to irreversible deformation or rupture of the spring or its fasteners.

La présente invention a pour but de perfectionner un dispositif de transmission anti-choc de ce genre, en évitant de recourir à un amortissement par friction et en créant une construction simple et peu coûteuse qui permet d'éviter une rupture du ressort ou de ses attaches lorsque l'appareil subit un choc d'une certaine ampleur, par exemple (mais non limitativement) jusqu'à la valeur de 5'000 g prescrite par la norme ISO 1413.The object of the present invention is to improve a transmission device anti-shock of this kind, avoiding the need for friction damping and creating a simple and inexpensive construction that prevents breakage of the spring or its attachments when the device is struck by a certain amount of force, for example example (but not limited to) up to the value of 5,000 g prescribed by the standard ISO 1413.

A cet effet, l'invention concerne un dispositif de transmission anti-choc du genre indiqué en préambule, caractérisé en ce que l'arbre central comporte une série d'échancrures réparties sur son pourtour et en ce que l'extrémité intérieure du ressort est agencée pour s'engager dans l'une quelconque desdites échancrures par l'élasticité du ressort et pouvoir se dégager de l'échancrure lorsqu'elle est soumise à une force suffisante dans au moins un sens de rotation du dispositif.To this end, the invention relates to an anti-shock transmission device for genre indicated in the preamble, characterized in that the central shaft has a series notches distributed around its periphery and in that the inner end of the spring is arranged to engage in any one of said notches by the elasticity of the spring and being able to free itself from the notch when it is subjected to sufficient force in at least one direction of rotation of the device.

On peut ainsi considérer que l'extrémité intérieure est couplée à l'arbre central par encliquetage, grâce à l'élasticité du ressort lui-même, cet encliquetage pouvant se dégager lorsque la rotation de l'arbre dans un sens a repoussé les spires du ressort suffisamment vers l'extérieur pour que le ressort ne puisse plus maintenir son extrémité intérieure dans l'échancrure où elle était en prise. Cette extrémité formant une sorte de cliquet va alors sauter hors de l'échancrure et pour ensuite s'engager à nouveau dans une échancrure suivante dès que les conditions le permettront. Pour faciliter le dégagement de l'extrémité du ressort, on peut prévoir de préférence que chaque échancrure comporte un flanc incliné et que l'extrémité intérieure du ressort comporte une partie saillante vers l'intérieur, apte à buter contre ledit flanc incliné pour recevoir ladite force et glisser sur lui dès que ladite force dépasse une valeur limite.We can thus consider that the inner end is coupled to the central shaft by snap-fastening, thanks to the elasticity of the spring itself, this snap-fitting can be disengage when the rotation of the shaft in one direction pushed back the coils of the spring outward enough that the spring can no longer maintain its inner end in the notch where it was engaged. This end forming a kind of pawl will then jump out of the notch and then commit to again in a next notch as soon as conditions allow. For facilitate the release of the end of the spring, provision may preferably be made for each notch has an inclined flank and the inner end of the spring has an inward projecting portion, capable of abutting against said inclined flank for receive said force and slide over it as soon as said force exceeds a limit value.

D'autres caractéristiques et avantages de l'invention apparaítront dans la description suivante d'un mode de réalisation préféré, présenté à titre d'exemple non limitatif en référence aux dessins annexés, dans lesquels :

  • la figure 1 est une vue en coupe verticale d'un ensemble générateur électrique pour une montre, dans lequel un dispositif de transmission anti-choc selon l'invention est interposé entre un mécanisme à masse oscillante et une micro-génératrice électrique;
  • la figure 2 est une vue en coupe agrandie du dispositif de transmission, suivant la ligne II-II de la figure 4;
  • la figure 3 représente le ressort à l'état de repos;
  • la figure 4 est une vue en plan de l'objet de la figure 2, après enlèvement du couvercle de barillet, et montre le dispositif de transmission en position d'équilibre;
  • la figure 5 est une vue analogue à la figure 4 et montre le dispositif de transmission lorsqu'il transmet un couple maximal dans un premier sens;
  • la figure 6 est une vue analogue à la figure 4 et montre le dispositif de transmission lorsqu'il transmet un couple maximal dans le sens opposé; et
  • les figures 7 et 8 sont des vues analogues à la figure 5 et illustrent le fonctionnement du dispositif de transmission lorsque le couple maximal dans le premier sens tend à être dépassé.
Other characteristics and advantages of the invention will appear in the following description of a preferred embodiment, presented by way of nonlimiting example with reference to the appended drawings, in which:
  • Figure 1 is a vertical sectional view of an electric generator assembly for a watch, in which an anti-shock transmission device according to the invention is interposed between an oscillating mass mechanism and an electric micro-generator;
  • Figure 2 is an enlarged sectional view of the transmission device, taken along line II-II of Figure 4;
  • Figure 3 shows the spring in the rest state;
  • Figure 4 is a plan view of the object of Figure 2, after removal of the barrel cover, and shows the transmission device in the equilibrium position;
  • Figure 5 is a view similar to Figure 4 and shows the transmission device when it transmits maximum torque in a first direction;
  • Figure 6 is a view similar to Figure 4 and shows the transmission device when it transmits maximum torque in the opposite direction; and
  • Figures 7 and 8 are views similar to Figure 5 and illustrate the operation of the transmission device when the maximum torque in the first direction tends to be exceeded.

Comme on le voit à la figure 1, un mécanisme 1 à masse oscillante rotative 2, monté sur une platine 3 du mouvement d'horlogerie de la montre, entraíne en rotation le rotor 4 d'une micro-génératrice électrique par l'intermédiaire d'un dispositif de transmission anti-choc 5 qui multiplie la vitesse de rotation.As can be seen in FIG. 1, a mechanism 1 with a rotating oscillating mass 2, mounted on a plate 3 of the clockwork movement of the watch, drives in rotation the rotor 4 of an electric micro-generator by means of a anti-shock transmission 5 which multiplies the speed of rotation.

Le mécanisme 1 est construit de manière classique. Son support de palier central 6, fixé à la platine 3 au moyen d'une vis 7 et d'un écrou tubulaire 8, supporte une roue dentée 10 par un roulement à billes 11. La masse oscillante semi-circulaire 2 est fixée à la roue dentée 10 par l'intermédiaire d'un anneau 12 et peut tourner autour de l'axe central 13 de la montre.Mechanism 1 is constructed in a conventional manner. Its bearing support central 6, fixed to the plate 3 by means of a screw 7 and a tubular nut 8, supports a toothed wheel 10 by a ball bearing 11. The semi-circular oscillating mass 2 is fixed to the toothed wheel 10 by means of a ring 12 and can rotate around of the central axis 13 of the watch.

Le rotor 4 de la génératrice comporte un aimant permanent 14 fixé sur un arbre 15 muni d'un pignon 16. Les pivots à l'extrémité de l'arbre 15 sont montés par des pierres respectives 17 et 18 dans la platine 3 et dans un pont 19 qui est fixé au stator 20 de la génératrice au moyen de pieds 21. L'aimant 14 du rotor tourne dans un évidement 22 du stator.The rotor 4 of the generator comprises a permanent magnet 14 fixed on a shaft 15 provided with a pinion 16. The pivots at the end of the shaft 15 are mounted by respective stones 17 and 18 in the plate 3 and in a bridge 19 which is fixed to the stator 20 of the generator by means of feet 21. The magnet 14 of the rotor rotates in a recess 22 of the stator.

Le dispositif de transmission 5 porte un arbre central 24 muni d'un pignon 25 et qui s'engrène sur la denture 26 de la roue 10, une roue intermédiaire formée par un barillet 27 muni d'une denture extérieure 28 qui s'engrène sur le pignon 16 du rotor 4, et un ressort spiral 30 qui relie élastiquement en rotation l'arbre 24 et le barillet 27. L'arbre 24 est monté rotatif dans la platine 3 et le pont 19 grâce à des pierres respectives 31 et 32 pour tourner autour d'un axe 33.The transmission device 5 carries a central shaft 24 provided with a pinion 25 and which meshes with the teeth 26 of the wheel 10, an intermediate wheel formed by a barrel 27 provided with an external toothing 28 which meshes with the pinion 16 of the rotor 4, and a spiral spring 30 which connects elastically in rotation the shaft 24 and the barrel 27. The shaft 24 is rotatably mounted in the plate 3 and the bridge 19 by stones respectively 31 and 32 to rotate around an axis 33.

On décrira plus en détail le barillet 27 en référence aux figures 2 à 6. La figure 3 montre la forme du ressort spiral 30 à l'état de repos, avant qu'il soit monté dans le barillet 27. Son extrémité intérieure présente une partie coudée 34 faisant un angle obtus 35 d'environ 135° avec la partie adjacente de la première spire intérieure 36 du ressort. La partie coudée 34 a une extrémité libre 37. L'extrémité extérieure 38 du ressort est soudée à une plaque d'ancrage 39. Dans cet exemple, le ressort 30 est formé d'une lame d'acier à section de 0,04 x 0,5 mm et présente au repos, entre ses deux extrémités, 8,5 spires qui sont séparées les unes des autres par un intervalle. Au repos, la spire intérieure 36 a un diamètre d'environ 1,3 mm et la spire extérieure 40 a un diamètre d'environ 3,4 mm. On notera que les ressorts spiraux de ce genre sont généralement fabriqués par groupe de trois pour obtenir l'intervalle voulu entre les spires au repos. Le formage des ressorts s'effectue en enroulant les trois lames correspondantes autour d'un mandrin muni de trois pinces pour tenir les extrémités intérieures des ressorts, puis en supprimant les tensions internes par un traitement thermique. Ce procédé crée automatiquement la partie coudée 34 à l'extrémité de chaque ressort, c'est-à-dire que l'obtention de cette forme d'extrémité n'exige aucune opération supplémentaire.The barrel 27 will be described in more detail with reference to Figures 2 to 6. The figure 3 shows the shape of the spiral spring 30 in the rest state, before it is mounted in the barrel 27. Its inner end has a bent portion 34 at an angle obtuse 35 of about 135 ° with the adjacent part of the first inner turn 36 of the spring. The bent part 34 has a free end 37. The outer end 38 of the spring is welded to an anchor plate 39. In this example, the spring 30 is formed of a steel blade with a section of 0.04 x 0.5 mm and present at rest between its two ends, 8.5 turns which are separated from each other by an interval. At rest, the inner coil 36 has a diameter of about 1.3 mm and the outer coil 40 has a diameter of about 3.4 mm. Note that spiral springs of this kind are usually made in groups of three to obtain the desired interval between the turns at rest. The springs are formed by winding the three blades around a mandrel with three pliers to hold the ends interior of the springs, then removing internal tensions by treatment thermal. This process automatically creates the bent part 34 at the end of each spring, i.e. obtaining this end shape requires no additional operation.

En référence aux figures 2 et 4, on voit que le barillet 27 comporte une pièce moulée en plastique comprenant un tambour cylindrique 41, un fond plat 42 qui pivote autour d'une portée cylindrique 43 de l'arbre 24, la denture 28 sur le pourtour du barillet 41, ainsi que trois pieds 44 servant à fixer un couvercle 45 qui constitue la face supérieure du barillet et qui pivote autour d'une portée 46 de l'arbre 24. Le courvercle est supprimé dans les figures 5 à 6 pour laisser voir l'intérieur du barillet. La plaque d'ancrage 39 du ressort 30 est bloquée dans un évidement 47 du tambour 41.Referring to Figures 2 and 4, we see that the barrel 27 has a part molded plastic comprising a cylindrical drum 41, a flat bottom 42 which pivots around a cylindrical seat 43 of the shaft 24, the toothing 28 around the periphery of the barrel 41, as well as three feet 44 used to fix a cover 45 which constitutes the face upper barrel and which pivots around a bearing 46 of the shaft 24. The courvercle is deleted in Figures 5 to 6 to show the inside of the barrel. The plaque anchor 39 of the spring 30 is locked in a recess 47 of the drum 41.

A l'intérieur du barillet 27, l'arbre central 24 présente une partie élargie 50 pourvue d'une série d'échancrures 51 réparties sur son pourtour. Dans le présent exemple, il est prévu quatre échancrures 51 ayant, dans un plan perpendiculaire à l'arbre 24, un profil dissymétrique sensiblement en forme de V dont la branche la plus longue forme un flanc incliné 52 (figure 5), tandis que son autre flanc 53 s'étend approximativement radialement jusqu'à un bord 54 de l'échancrure. Entre les échancrures 51, le ressort 30 peut s'appuyer sur des portées 55 en arc de cercle qui sont bordés de deux rebords 56 (figure 2) pour guider le ressort. Le diamètre défini par les portées 55 est légèrement plus grand que celui de la première spire 36 du ressort au repos, de sorte que l'élasticité du ressort tend à engager son extrémité coudée 34 dans l'une quelconque des échancrures 51 et à serrer légèrement la première spire 36 sur les portées 55 de l'arbre.Inside the barrel 27, the central shaft 24 has an enlarged part 50 provided with a series of notches 51 distributed around its periphery. In the present example, four notches 51 are provided having, in a plane perpendicular to the shaft 24, an asymmetrical profile substantially V-shaped, the most branch long forms an inclined flank 52 (FIG. 5), while its other flank 53 extends approximately radially to an edge 54 of the notch. Between the notches 51, the spring 30 can rest on spans 55 in an arc of a circle which are bordered by two flanges 56 (Figure 2) to guide the spring. The defined diameter by the spans 55 is slightly larger than that of the first turn 36 of the spring at rest, so that the elasticity of the spring tends to engage its end angled 34 in any one of the notches 51 and to lightly tighten the first turn 36 on the bearing surfaces 55 of the tree.

Lorsque la montre ne subit pas de mouvement, la masse oscillante 2 est arrêtée et le dispositif de transmission 5 ne transmet aucun couple au rotor 4 de la génératrice, sauf éventuellement un faible couple de positionnement de l'aimant 14 par rapport au stator 20. Le dispositif 5 se trouve alors dans la position d'équilibre représentée à la figure 4. Lorsqu'un mouvement est imposé à la montre, la masse oscillante 2 se met à tourner dans un sens quelconque et entraíne en rotation l'arbre 24 via la denture 26 et le pignon 25. Le ressort 30 est alors mis sous tension et transmet un couple au barillet 27, qui se met aussi à tourner et entraíne en rotation rapide le rotor 4 via la denture 28 et le pignon 16.When the watch does not undergo movement, the oscillating mass 2 is stopped and the transmission device 5 does not transmit any torque to the rotor 4 of the generator, except possibly a low magnet positioning torque 14 relative to the stator 20. The device 5 is then in the equilibrium position shown in Figure 4. When a movement is imposed on the watch, the mass oscillating 2 starts to rotate in any direction and causes the shaft to rotate 24 via the toothing 26 and the pinion 25. The spring 30 is then energized and transmits a torque to the barrel 27, which also starts to rotate and causes it to rotate fast the rotor 4 via the toothing 28 and the pinion 16.

Quand l'arbre 24 applique au ressort 30 un couple dans un premier sens représenté par la flèche A dans les figures 5, 7 et 8, les spires du ressort augmentent de diamètre jusqu'à qu'elles s'appliquent successivement contre le tambour 41 du barillet, si le couple résistant de la génératrice est suffisant. En pratique, la position extrême du ressort, qui est représentée à la figure 5 et dans laquelle toutes les spires, sauf une partie de la première, sont appliquées contre le tambour 41, ne peut être atteinte que lors d'une très forte accélération de la masse oscillante 2, par exemple à cause d'un choc sur la montre. Cette position correspond à un couple maximal que le ressort 30 peut transmettre dans le sens A. L'extrémité libre 37 du ressort bute alors contre le flanc incliné 52 de l'échancrure 51.When the shaft 24 applies to the spring 30 a torque in a first direction represented by arrow A in figures 5, 7 and 8, the turns of the spring increase in diameter until they are applied successively against the drum 41 of the barrel, if the resistant torque of the generator is sufficient. In practice, the position end of the spring, which is shown in FIG. 5 and in which all the turns, except part of the first, are applied against the drum 41, cannot be reached only during a very strong acceleration of the oscillating mass 2, for example at because of a shock on the watch. This position corresponds to a maximum torque that the spring 30 can transmit in direction A. The free end 37 of the spring then abuts against the inclined flank 52 of the notch 51.

Si le couple exercé par l'arbre 24 tend encore à augmenter, le dispositif atteint la position représentée en figure 7, où le flanc incliné 52 exerce une force F, approximativement perpendiculaire au flanc 52, sur l'extrémité 37 du ressort. Si la force F dépasse une certaine limite apte à repousser vers l'extérieur l'extrémité 37, celle-ci glisse sur le flanc incliné 52 en direction de l'extérieur et s'échappe de l'échancrure à partir de la position de la figure 8, de sorte que le ressort et le barillet tournent moins vite que l'arbre. L'extrémité 37 du ressort, grâce à l'élasticité de celui-ci, tendra à s'engager automatiquement dans l'une des échancrures 51 suivantes et y rester engagée pour transmettre à nouveau un couple au ressort lorsque les conditions dynamiques le permettront. On obtient ainsi un découplage automatique du dispositif de transmission dès que le couple atteint une valeur qui dépasse la capacité de déformation du ressort par expansion dans le barillet, ce qui permet de prévenir des dommages non seulement au ressort 30, mais aussi aux dentures et aux paliers des différents mobiles. De plus, le couplage se rétablit automatiquement et permet au dispositif de fonctionner normalement par la suite.If the torque exerted by the shaft 24 still tends to increase, the device reaches the position shown in FIG. 7, where the inclined flank 52 exerts a force F, approximately perpendicular to the sidewall 52, on the end 37 of the spring. If the force F exceeds a certain limit capable of pushing the end 37 outwards, it slides on the inclined flank 52 towards the outside and escapes from the notch from the position of Figure 8, so that the spring and the barrel rotate slower than the tree. The end 37 of the spring, thanks to the elasticity of the latter, will tend to automatically engage in one of the following notches 51 and there remain engaged to transmit torque again to the spring when the dynamic conditions will allow this. There is thus obtained an automatic decoupling of the transmission device as soon as the torque reaches a value which exceeds the capacity deformation of the spring by expansion in the barrel, which prevents damage not only to spring 30, but also to teeth and bearings of different mobiles. In addition, the coupling is re-established automatically and allows the device to operate normally thereafter.

Lorsque la masse oscillante 2 tourne dans l'autre sens, elle entraíne l'arbre 24 dans le sens de la flèche B de la figure 6, de sorte que le couple transmis tend à serrer successivement les spires du ressort 30 sur la partie élargie 50 de l'arbre. Ce serrage maintient la partie coudée 34 du ressort dans l'échancrure 51 où elle est engagée. L'angle 35 du ressort prend alors appui sur le bord 54 de l'échancrure.When the oscillating mass 2 rotates in the other direction, it drives the shaft 24 in the direction of arrow B in Figure 6, so that the transmitted torque tends to successively tighten the turns of the spring 30 on the enlarged part 50 of the shaft. This tightening keeps the bent part 34 of the spring in the notch 51 where it is engaged. The angle 35 of the spring then bears on the edge 54 of the notch.

La figure 6 représente une situation où le couple appliqué par l'arbre 24 au ressort dans le sens B a une valeur si élevée que toutes les spires sont appuyées contre l'arbre, sauf la partie terminale de la spire extérieure. La valeur absolue de ce couple est sensiblement la même que dans le cas illustré par la figure 5, mais la force qui en résulte entre l'extrémité extérieure 38 du ressort et la plaque d'ancrage 39 n'est qu'une fraction de la force à transmettre pour le même couple au niveau des portées 55 de l'arbre, parce qu'elle agit avec un bras de levier bien plus grand. En conséquence, une rupture de la soudure entre les éléments 38 et 39 n'est pas à craindre pour une telle valeur du couple à transmettre. Toutefois, si l'on voulait absolument se prémunir contre le risque de rupture de l'ancrage extérieur du ressort, on pourrait aussi utiliser un système à bride glissante du type bien connu pour les barillets entraínant les mouvements de montres mécaniques.FIG. 6 represents a situation where the torque applied by the shaft 24 to the spring in direction B has such a high value that all the turns are pressed against the shaft, except the end part of the outer coil. The absolute value of this torque is substantially the same as in the case illustrated in Figure 5, but the force resulting between the outer end 38 of the spring and the anchor plate 39 is that a fraction of the force to be transmitted for the same torque at the spans 55 of the tree, because it acts with a much larger lever arm. In consequently, a rupture of the weld between the elements 38 and 39 is not to fear for such a value of the torque to be transmitted. However, if we wanted to absolutely to guard against the risk of rupture of the external anchoring of the spring, one could also use a sliding flange system of the type well known for barrels driving mechanical watch movements.

Le cas échéant, une autre façon de se prémunir contre le risque de dommages dans la situation représentée à la figure 6 consisterait à entraíner l'arbre 24 uniquement dans le sens A représenté à la figure 5, grâce à un mécanisme à sens unique interposé entre la masse oscillante 2 et le dispositif de transmission 5. Toutefois cela impliquerait un surcroít de complexité et d'encombrement du mécanisme.Another way to guard against the risk of damage in the situation represented in figure 6 would consist in driving the tree 24 only in direction A represented in FIG. 5, by means of a direction mechanism single interposed between the oscillating mass 2 and the transmission device 5. However, this would imply additional complexity and bulk of the mechanism.

Le champ d'application de la présente invention n'est pas limité aux montres et peut s'étendre notamment à tous les appareils portables équipés d'une génératrice électrique, par exemple des téléphones portables, des appareils de mesure ou des appareils médicaux.The scope of the present invention is not limited to watches and can be extended in particular to all portable devices fitted with a generator electric, for example mobile phones, measuring devices or medical devices.

Claims (11)

Dispositif de transmission antichoc pour l'entraínement du rotor (4) d'une génératrice électrique par une masse oscillante (2) dans un appareil portable, comportant : un arbre central (24) et une roue intermédiaire dentée (28), dont l'un est susceptible d'être entraíné en rotation par des mouvements de la masse oscillante et l'autre est couplé au rotor de la génératrice par une liaison cinématique, l'arbre central et la roue intermédiaire ayant un axe de rotation commun (33), et un ressort (30) en forme de spirale ayant une extrémité intérieure couplée à l'arbre central et une extrémité extérieure couplée à la roue intermédiaire,    caractérisé en ce que l'arbre central (24) comporte une série d'échancrures (51) réparties sur son pourtour et en ce que l'extrémité intérieure (37) du ressort est agencée pour s'engager dans l'une quelconque desdites échancrures (51) par l'élasticité du ressort et pouvoir se dégager de l'échancrure lorsqu'elle est soumise à une force suffisante dans au moins un sens de rotation (A) du dispositif.Shockproof transmission device for driving the rotor (4) of an electric generator by an oscillating mass (2) in a portable device, comprising: a central shaft (24) and an intermediate toothed wheel (28), one of which is capable of being rotated by movements of the oscillating mass and the other is coupled to the rotor of the generator by a kinematic connection, the central shaft and the intermediate wheel having a common axis of rotation (33), and a spiral-shaped spring (30) having an inner end coupled to the central shaft and an outer end coupled to the intermediate wheel, characterized in that the central shaft (24) has a series of notches (51) distributed around its periphery and in that the inner end (37) of the spring is arranged to engage in any one of said notches (51) by the elasticity of the spring and being able to disengage from the notch when it is subjected to a sufficient force in at least one direction of rotation (A) of the device. Dispositif selon la revendication 1, caractérisé en ce que chaque échancrure (51) comporte un flanc incliné (52) et en ce que l'extrémité intérieure du ressort comporte une partie (34) saillante vers l'intérieur, apte à buter contre ledit flanc incliné pour recevoir ladite force et à glisser sur lui lorsque ladite force dépasse une valeur limite.Device according to claim 1, characterized in that each notch (51) has an inclined flank (52) and in that the inner end of the spring has a part (34) projecting inwards, capable of abutting against said flank inclined to receive said force and to slide over it when said force exceeds a limit value. Dispositif selon la revendication 2, caractérisé en ce que la partie saillante du ressort est formée par une partie coudée (34) ayant une extrémité libre (37) apte à buter contre ledit flanc incliné.Device according to claim 2, characterized in that the projecting part of the spring is formed by a bent part (34) having a free end (37) capable of abutting against said inclined flank. Dispositif selon la revendication 3, caractérisé en ce que la partie coudée (34) forme un angle obtus (35) avec la partie adjacente du ressort, la face intérieure dudit angle étant agencée pour prendre appui contre un bord (54) de l'échancrure.Device according to claim 3, characterized in that the bent part (34) forms an obtuse angle (35) with the adjacent part of the spring, the internal face of said angle being arranged to bear against an edge (54) of the notch . Dispositif selon la revendication 2, caractérisé en ce que chaque échancrure (51) a, dans un plan perpendiculaire à l'arbre, un profil dissymétrique sensiblement en forme de V dont la branche la plus longue forme ledit flanc incliné (52).Device according to claim 2, characterized in that each notch (51) has, in a plane perpendicular to the shaft, an asymmetrical profile substantially V-shaped, the longest branch of which forms said inclined flank (52). Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que l'arbre central est muni d'un pignon (25) couplé par engrènement à la masse oscillante et en ce que la roue intermédiaire (28) est couplée par engrènement au rotor de la génératrice.Device according to one of claims 1 to 5, characterized in that the central shaft is provided with a pinion (25) coupled by meshing to the oscillating mass and in that the intermediate wheel (28) is coupled by meshing with generator rotor. Dispositif selon la revendication 6, caractérisé en ce que le ressort (30) est logé dans un barillet (27) comportant un tambour (41) muni d'un fond et d'un couvercle, l'extrémité extérieure (38) du ressort étant ancrée dans le tambour, et en ce que la roue intermédiaire est formée par une denture extérieure (28) sur ledit tambour.Device according to claim 6, characterized in that the spring (30) is housed in a barrel (27) comprising a drum (41) provided with a bottom and a cover, the outer end (38) of the spring being anchored in the drum, and in that the intermediate wheel is formed by an external toothing (28) on said drum. Dispositif selon la revendication 7, caractérisé en ce que l'arbre central (24) comporte, à l'intérieur du barillet, une partie élargie (50) dans laquelle sont ménagées lesdites échancrures (51) et comportant, entre les échancrures, des portées (55) en arcs de cercle pour l'appui du ressort.Device according to claim 7, characterized in that the central shaft (24) has, inside the barrel, an enlarged part (50) in which are formed said notches (51) and comprising, between the notches, bearing surfaces (55) in circular arcs for the support of the spring. Dispositif selon la revendication 8, caractérisé en ce qu'une première spire intérieure (36) du ressort présente, au repos lorsque le ressort n'est pas monté sur l'arbre central, un plus petit diamètre que le diamètre défini par lesdites portées (55).Device according to claim 8, characterized in that a first internal turn (36) of the spring has, at rest when the spring is not mounted on the central shaft, a smaller diameter than the diameter defined by said bearing surfaces ( 55). Dispositif selon l'une des revendications 1 à 9, caractérisé en ce que l'arbre central est susceptible d'être entraíné dans les deux sens (A et B) par la masse oscillante.Device according to one of claims 1 to 9, characterized in that the central shaft is capable of being driven in both directions (A and B) by the oscillating mass. Montre-bracelet comportant une génératrice électrique entraínée par une masse oscillante via un dispositif de transmission (5) selon l'une des revendications 1 à 10.Wristwatch comprising an electric generator driven by a oscillating mass via a transmission device (5) according to one of claims 1 to 10.
EP00204370A 2000-12-07 2000-12-07 Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch Expired - Lifetime EP1213626B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE60042597T DE60042597D1 (en) 2000-12-07 2000-12-07 Shockproof transmission means for driving a generator by a flywheel, in particular in a clock
EP00204370A EP1213626B1 (en) 2000-12-07 2000-12-07 Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch
US09/987,997 US6587401B2 (en) 2000-12-07 2001-11-16 Anti-shock transmission device for driving a generator by an oscillating weight in particular in a watch
JP2001371011A JP4188589B2 (en) 2000-12-07 2001-12-05 Anti-shock transmission device for driving a generator with a vibrating weight, especially in a watch
CNB011435313A CN1239968C (en) 2000-12-07 2001-12-06 Shockproof driving mechanism for pendulum mass to drive power generator in watch
HK02109068A HK1047322A1 (en) 2000-12-07 2002-12-13 Anti-shock transmission device for driving a generator by an oscillating weight in particular in a watch

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00204370A EP1213626B1 (en) 2000-12-07 2000-12-07 Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch

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EP1213626A1 true EP1213626A1 (en) 2002-06-12
EP1213626B1 EP1213626B1 (en) 2009-07-22

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EP00204370A Expired - Lifetime EP1213626B1 (en) 2000-12-07 2000-12-07 Impact resistant transmission means for driving a generator by an oscilating mass, in particular in a watch

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US (1) US6587401B2 (en)
EP (1) EP1213626B1 (en)
JP (1) JP4188589B2 (en)
CN (1) CN1239968C (en)
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HK (1) HK1047322A1 (en)

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US9298162B2 (en) * 2010-10-01 2016-03-29 Rolex Sa Timepiece barrel with thin disks
DE102011106785B4 (en) * 2011-07-06 2015-07-23 JuB-Creative Product GmbH Kinetic transducer
EP2701013B1 (en) * 2012-08-23 2019-06-12 Audemars Piguet (Renaud et Papi) SA Clock movement with extended power reserve
EP2765462B1 (en) * 2013-02-12 2018-04-04 ETA SA Manufacture Horlogère Suisse Anti-impact centre wheel
EP2799937B1 (en) * 2013-05-01 2020-09-16 Rolex Sa Shock-proof bearing for an horological balance
CN106586945B (en) * 2017-01-07 2018-02-09 杭州电子科技大学 The miniature jump bit of low driving voltage
CN107957670B (en) * 2017-10-13 2020-03-24 烟台职业学院 Intelligent winding mechanism of large mechanical watch
NL2021361B1 (en) * 2018-07-20 2020-01-29 Kinetron Bv Electric low-power supply system for devices and device comprising such a low-power supply system

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GB662225A (en) * 1949-07-25 1951-12-05 Junghans Geb Ag Improvements in or relating to spring mountings for pivots in precision gears
EP0681228A1 (en) * 1994-05-04 1995-11-08 Eta SA Fabriques d'Ebauches Means for coupling a mechanical energy source with an electric generator in a time piece
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US20020071348A1 (en) 2002-06-13
JP2002250781A (en) 2002-09-06
US6587401B2 (en) 2003-07-01
DE60042597D1 (en) 2009-09-03
HK1047322A1 (en) 2003-02-14
JP4188589B2 (en) 2008-11-26
EP1213626B1 (en) 2009-07-22
CN1239968C (en) 2006-02-01
CN1357804A (en) 2002-07-10

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