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EP2181362B1 - Timepiece - Google Patents

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Publication number
EP2181362B1
EP2181362B1 EP08783457.8A EP08783457A EP2181362B1 EP 2181362 B1 EP2181362 B1 EP 2181362B1 EP 08783457 A EP08783457 A EP 08783457A EP 2181362 B1 EP2181362 B1 EP 2181362B1
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EP
European Patent Office
Prior art keywords
wheel
differential
transmission
timepiece
coaxial
Prior art date
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Application number
EP08783457.8A
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German (de)
French (fr)
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EP2181362A2 (en
Inventor
Yves Corthesy
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.)
LVMH Swiss Manufactures SA
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LVMH Swiss Manufactures SA
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Publication date
Application filed by LVMH Swiss Manufactures SA filed Critical LVMH Swiss Manufactures SA
Priority to EP08783457.8A priority Critical patent/EP2181362B1/en
Publication of EP2181362A2 publication Critical patent/EP2181362A2/en
Application granted granted Critical
Publication of EP2181362B1 publication Critical patent/EP2181362B1/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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels
    • 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
    • G04B13/00—Gearwork
    • G04B13/007—Gearwork with differential work

Definitions

  • the present invention relates to a timepiece comprising a frame, a transmission mechanism having a transmission gear train driven from a mobile mounted on the frame, and comprising two upstream portions, respectively downstream, distributed on at least two supports pivotally mounted around two axes of respective joints, one of which is situated between the frame and a support and the other of which is situated between the two supports, a differential correction device for neutralizing the induced angular displacements in the transmission train by the movements of said supports around their respective axes.
  • a differential is a device that occupies space and causes a loss of energy transmitted. Now, in a timepiece, especially when it comes to a wristwatch, both the space and the energy available are reduced.
  • the object of the present invention is to overcome, at least in part, these disadvantages.
  • the present invention relates to a timepiece as defined in claim 1.
  • this correction device it is possible not only to neutralize the movements of the transmission train about two axes of articulation with a single differential, but to neutralize the movements of the transmission train around any number of axes. help of a single differential. Thanks to this feature, the invention is not limited to the only correction of the attitude of the regulating device, even if this correction is of obvious interest, but offers other possibilities still unknown so far.
  • an inverter train and a differential with a reversing satellite make it possible to cancel the rotations of the articulations at one time, transmitting at the output only the movement generated by the transmission.
  • the figure 1 is a very schematic representation of a part of the finishing gear of a timepiece, from the seconds wheel to the escape wheel.
  • the large average or center wheel, the average wheel and the barrel, on the one hand and the escapement and the sprung balance, on the other hand have not been represented.
  • the timepiece comprises a frame 1 on which a first support frame 2 is pivotally mounted about an axis A 1 .
  • a first shaft 3 centered on the axis A 1 is integral with the frame 1 and is freely engaged in an opening which passes through a first face of the frame 2.
  • a pivot 4 is secured to a second opposite face of the frame 2. This pivot 4 occupies on the second face of the frame 2 a corresponding position to that occupied by the opening crossing the first face.
  • This pivot 4 is engaged freely in an opening 5 of the frame 1, centered on the axis A 1 .
  • a second support frame 6 is mounted on the first support frame 2 around a pivot axis A 2 orthogonal to the axis A 1 .
  • a pivot 7 secured to a first face of the second support frame 6 is freely engaged in an opening centered on the axis A 2 , formed in a face of the first support frame 2 perpendicular to the two opposite faces traversed by the axis A 1 .
  • the end of a tubular element 8 integral with the face opposite the first face of the support frame 6 and occupying on this opposite face a position corresponding to that occupied by the pivot 7 on the first face, is engaged freely in a centered opening on the axis A 2 and formed in the face of the first support frame 2 opposite to that in which the pivot 7 is engaged.
  • the first gear is that of the transmission of the movement generated by the motor spring housed in the barrel (not shown) and controlled by the associated exhaust the sprung balance (not shown), to which is added the movement of the support frames 2, 6 around the axes A 1 , A 2 .
  • the second gear train is the one that makes it possible to totalize the angular movements generated by the pivoting of the support frames 2, 6 around the axes A 1 , A 2 and constitutes the reference gearing of the rotations of the supports 2, 6 relative to the built 1.
  • the first gear train comprises a first transmission wheel 9 mounted freely around the integral shaft 3 of the frame 1 and coaxial with the axis A 1 .
  • This first transmission wheel 9 corresponds to the second wheel of the finishing train and has a pinion 9a intended to mesh with the average wheel (not shown), mounted on the frame 1.
  • This first transmission wheel 9 meshes with a second transmission wheel 10 freely mounted in the tubular element 8 centered on the second pivot axis A 2 of the second support frame 6.
  • this second transmission wheel 10 is integral with a shaft 10b which is pivotally mounted in the tubular element 8 of the second support frame 6. At its end opposite to that integral with the second transmission wheel 10, the shaft 10b carries a pinion 10a.
  • the first wheel 11 of this gear train reference which will be called the first reference wheel 11, is integral with the shaft 3, itself integral with the frame 1.
  • This first reference wheel 11 is also coaxial with the first wheel 9 of the first gear train of transmission of the work train. It meshes with a second reference wheel 12 pivotally mounted about the axis A 2 .
  • the ratio between the transmission wheels 9 and 10 is identical to the ratio between the reference wheels 11 and 12.
  • the wheel 9 of the gear train for transmitting the force of the mainspring to the exhaust is driven in successive steps to the frequency at which the escape wheel releases the energy of the mainspring under the control of the engine. balance-spiral, this regular sequential rotation of the wheel 10 is added to the random rotation of the support frames 2, 6 around the axes A 1 , respectively A 2 .
  • the shaft 10b of the second wheel of the first energy transmission gear train of the exhaust motor spring serves as a pivoting member to a sun gear 13 which constitutes the output of the differential.
  • This planetary wheel meshes with a pinion 14a of a wheel 14, here corresponding to the seconds wheel, meshing with a pinion 15a of a wheel 15 corresponding to the escape wheel.
  • the sun gear 13 carries two satellites 16, 17 meshing with each other, the satellite 16 also meshing with the pinion 10a of the second wheel of the drive gear transmission gear.
  • This pinion 10a constitutes a first input through which the differential is connected to the transmission gear train of the driving force.
  • the second satellite 17 meshes with a return 18 mounted free around the tubular element 8 centered on the second axis A 2 .
  • This reference 18 is connected to a pinion 12a of the wheel 12 of the second reference gear train, by two referrals 19, 20 meshing with each other.
  • the axes of these references 19, 20 are integral with the second support frame 6.
  • the first reference 19 meshes with the return 18 and the second meshes with the pinion 12a.
  • references 18, 19, 20 the angular displacements of the support frames 2, 6 around the axes A 1 , A 2 are transmitted to the second satellite 17 and as these references are in odd number, the angular movement transmitted to the second satellite 17 is inverted, which makes it possible to neutralize at the output 13 of the differential, the angular movements induced in the first transmission train by the angular displacements of the support frames 2 and 6.
  • These references 18, 19, 20 therefore constitute reversing mobiles
  • this differential correction device makes it possible to deduce all the movements of the supports 2, 6 using a single differential and an inverter system and this, whatever the number of supports and axes. of articulation, as will be seen in the embodiment of the figure 2 .
  • the part 6a of the support frame 6, opposite the part 6b with respect to the axis A 2 is designed to form or to carry a counterweight in order to maintain the attitude of the surface 6b carrying the system regulating in a constant position whatever the position of the frame 1.
  • the axis of the seconds wheel 14, carried by the support 6 which is held in a constant position may advantageously carry a pointer, as illustrated in particular in the figure 1 .
  • the rotations generated by the joints between the supports 2, 6 are subjected to identical way by the two gear trains.
  • the second reference gear train starting from a wheel 11 integral with the frame 1, the rotations of the second reference wheel 12 are only due to the rotation of the supports 2, 6 around the axes A 1 , A 2 .
  • the corrector device must therefore subtract from the rotation of the second transmission wheel 10 the rotations of the second reference wheel 12 to keep only the rotation coming from the first transmission wheel 9.
  • the rotation transmitted by one of the second wheels of the transmission gear train 10 or the reference gear train 12 must be reversed to be subtracted. In the example illustrated by the figure 1 it is the rotation of the second reference wheel 12 which is reversed, but it would also be possible to reverse the rotation of the second transmission wheel 10.
  • the advantage of the proposed solution is that the energy absorbed by the friction due to the reversing gears is generated by the combined action of the counterweight and the gravity and not subtracted from the energy transmitted from the frame and that this absorption of energy dampens any oscillations of the frames around their respective axes. This absorption also prevents untimely rotation of the frames when the axis A1 is substantially vertical. Adjustment of this absorption is therefore possible and desirable.
  • this correction device is that the rotations around the axes A 1 , A 2 add up, so that we can have a number of axes of any joint, their total rotations relative to the frame 1 s add up algebraically. Indeed supposing that two supports rotate in opposite directions about parallel axes, the rotation relative to the frame will be their relative rotation.
  • the figure 2 illustrates an embodiment in which three supports 2, 6 and 21 rotate around three axes A 1 , A 2 , A 3 , whose two axes A 2 , A 3 are orthogonal to the axis A 1 , the two supports 6 and 21 being mounted pivoting about two axes combined, but being independent relative to each other.
  • the axis A 1 is not necessarily orthogonal to the axes A 2 , A 3 , but that these axes could be parallel or occupy other angular positions between them, without changing the principle of neutralization. rotations of the supports about the axes on the transmission of a rotation through a gear transmission gear, distributed on the different supports articulated to each other, on which the invention is based.
  • the first transmission gear train comprises an additional wheel 22 coaxial with the pivot axis A 3 .
  • This wheel carries a pinion 22a intended to be connected to a driving source, in particular a spring housed in a barrel (not shown).
  • This wheel can be here the wheel of seconds. It meshes with the wheel 9 'coaxial with the pivot axis A 1 , which is here secured to a pinion 9'a which meshes with the wheel 10.
  • the additional wheel 22 of the first gear transmission gear is coaxial with an additional wheel 23 of the second reference gear train, which is integral with the frame 1 and which meshes with a wheel 11'a coaxial with the pivot axis A 1 .
  • This second wheel 11'a is secured to one end of a shaft 11'b which is pivotally mounted through the support frames 21 and 2, and through the wheel 9 'of the first gear.
  • the shaft 11'b is integral with a wheel 11'c which meshes with the wheel 12. All the rest of the mechanism is identical to that of the figure 1 to which we can refer.
  • the figure 3 is a variant of the embodiment of the figure 1 in which the differential is off-center with respect to the axis A 2 .
  • the sun wheel 13 is no longer coaxial with the axis A 2 of pivoting of the support frame 6 ', but of the axis of a deflection wheel 26 meshing with the pinion 10a integral with the transmission wheel 10 coaxial with the axis A 2 .
  • This reference 26 is integral with a pinion 26a which meshes with the satellite 16 of the differential.
  • the reference 18 is also coaxial with this deflection wheel 26 and more than the axis A 2 . It is in kinematic connection with the pinion 12a of the reference mobile 12 by a single reference 20 secured to the support frame 6 '.
  • the form of execution illustrated by the figure 4 differs from the preceding embodiments essentially in that the differential correction device is mounted on the frame 1 of the timepiece and more on the supports mounted pivoting about the axes A 1 and A 2 . Thanks to this arrangement, it is possible to reduce the number of elements mounted on the pivoting supports 2 and 6, so that it is possible to reduce their size and make the device more compact.
  • organs having functions similar to those of the embodiment of the figure 1 have the same references with the sign *.
  • supports 2 * and 6 * pivotally mounted about the axes A 1 , respectively A 2 .
  • the support 2 * pivots around the tubular element 1 * a of the frame 1, coaxial with the axis A 1 and a pivot 4 * is engaged freely in an opening 5 * of the frame 1 *, centered on the axis A 1 .
  • One face of the support 6 * comprises a pivot 7 * centered on the axis A 2 by an axial opening of the support 2 * in which this pivot is mounted.
  • the opposite face of the support 6 * comprises a tubular element 8 * whose outer face is engaged in an axial opening of the support 2 *.
  • the face of the support 2 * opposite that carrying the pivot 4 * has an axial opening in which a tubular element 1 * of the frame 1 * is engaged.
  • the two satellites 16 * and 17 * meshing with each other are carried by a planetary mobile 9 * integral with a pinion 9 * for meshing with the upstream portion of the transmission train the movement generated by the motor spring housed in the barrel (not shown) and controlled by the escapement associated with the sprung balance (not shown), of which only the wheel 15 * is shown.
  • the satellite 16 * meshes with a pinion 12 * integral with the reference wheel 12 * of the reference wheel of the pivoting support frames 2 *, 6 * around the axes A 1 , A 2 , while the satellite 17 * meshes with the reference 18 * pivotally mounted on the tubular element 1 * a of the frame 1 *.
  • This reference meshes with a 19 * reference which meshes with a 20 * reference both mounted pivoting on the frame 1 *.
  • the reference 20 * meshes with a pinion 13 * a wheel 13 * which is the output of the differential and which is in kinematic connection with the downstream part of the first gear train of the movement generated by the mainspring. This downstream part comprises the second wheel 14 * and the escape wheel 15 * carried by the second support 6 *.
  • This wheel 13 * is coaxial with the first wheel 9 * of the first transmission train and is mounted around the tubular element 1 * integral with the frame 1 *. This wheel 13 * meshes with the third wheel 10 * of the first transmission train, whose pinion 10 * meshes directly with the pinion 14 * a of the seconds wheel 14 *.
  • the reference wheel 12 * integral with the pinion 12 * has the reference wheel of the rotation of the supports 2 *, 6 * around the axes A 1 , A 2 relative to the frame 1 *, it meshes with the reference wheel 11 * which is secured to the second support 6 * and no longer the frame as in the embodiment of the figure 1 .
  • the principle of deducing the angular displacements generated by the rotation of the supports 2 * and 6 * around the axes A 1 , A 2 is the same as in the previous embodiments.
  • the differential device with the inverters makes it possible to deduce the movements resulting from the rotation of the supports 2 *, 6 * of the transmission of the movement generated by the mainspring regardless of the number of pivot axes and the number of supports, as we have seen in the form of execution illustrated by the figure 2 .
  • the differential correction device can be arranged either at the beginning or at the end of the kinematic chain of the second reference wheel, since this reference wheel makes it possible to add the sum of the angular displacements of the supports 2 * algebraically, 6 * and that it introduces this value to an input of the correction device to differential whose other input receives the movement of the first gear train to which is added the movement of the supports 2 *, 6 * that it is necessary to subtract to transmit to the output of the differential that the movement of the first gear only of transmission.
  • the correction device must be located at the opposite end of the mobile secured to the axis of rotation between two supports.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
  • General Details Of Gearings (AREA)
  • Electric Clocks (AREA)

Abstract

The time piece has a differential correction device for neutralizing angular movements generated in a transmission gear by movements of bearing frames (2, 6). The device has reference wheels (11, 12) coaxial to orthogonal articulation axes (A1, A2). A setting wheel (19) is arranged in a kinematic link between the reference wheel (12) and a reference side inlet of a differential gear for reversing rotations relative to the inlet of the differential gear. An outlet of the differential gear is in a kinematic link with a wheel (14) and an escapement wheel (15) of the transmission gear.

Description

La présente invention se rapporte à une pièce d'horlogerie comprenant un bâti, un mécanisme de transmission présentant un train d'engrenage de transmission entraîné à partir d'un mobile monté sur le bâti, et comprenant deux parties amont, respectivement aval, réparties sur au moins deux supports montés pivotants autour de deux axes d'articulations respectifs dont l'un est situé entre le bâti et un support et dont l'autre est situé entre les deux supports, un dispositif de correction à différentiel pour neutraliser les déplacements angulaires induits dans le rouage de transmission par les déplacements desdits supports autour de leurs axes respectifs.The present invention relates to a timepiece comprising a frame, a transmission mechanism having a transmission gear train driven from a mobile mounted on the frame, and comprising two upstream portions, respectively downstream, distributed on at least two supports pivotally mounted around two axes of respective joints, one of which is situated between the frame and a support and the other of which is situated between the two supports, a differential correction device for neutralizing the induced angular displacements in the transmission train by the movements of said supports around their respective axes.

On a déjà proposé dans le EP 1 615 085 un mécanisme de correction d'assiette d'un dispositif réglant balancier-spiral qui est inspiré des dispositifs de correction d'assiette à double cardan utilisés dans les chronomètres de marine pour le maintenir constamment en position horizontale.We have already proposed in the EP 1 615 085 a trim correction mechanism of a sprung-balance adjusting device which is inspired by the dual cardan trim devices used in marine chronometers to keep it constantly in a horizontal position.

Le mécanisme décrit dans ce document a besoin d'un différentiel de correction associé à chaque axe d'articulation. Un différentiel est un dispositif qui occupe de la place et qui entraîne une perte d'énergie transmise. Or, dans une pièce d'horlogerie, en particulier lorsqu'il s'agit d'une montre bracelet la place et l'énergie disponible sont toutes deux réduites.The mechanism described in this document needs a correction differential associated with each axis of articulation. A differential is a device that occupies space and causes a loss of energy transmitted. Now, in a timepiece, especially when it comes to a wristwatch, both the space and the energy available are reduced.

Pour que la transmission d'énergie perturbe peu la position horizontale du support il est nécessaire d'avoir une certaine masse du contrepoids et donc un certain volume de ce contrepoids. Le fait d'ajouter de nombreuses roues et un différentiel sur le support médian qui doit pouvoir décrire un cercle complet autour du support interne augmente le volume global occupé par le système. De plus le train d'engrenage de la transmission et celui de la correction sont très différents, les jeux et les rattrapages de jeux lors des changements de sens de rotation ne se font pas forcément dans le même sens, créant des variations perturbatrices de la correction.In order for the transmission of energy to disturb little the horizontal position of the support, it is necessary to have a certain mass of the counterweight and thus a certain volume of this counterweight. Adding many wheels and a differential to the medial support that must be able to describe a complete circle around the internal support increases the overall volume occupied by the system. In addition the gear train of the transmission and the one of the correction are very different, the games and the compensations of games during the changes of direction of rotation are not necessarily in the same direction, creating disruptive variations of the correction.

Le but de la présente invention est de remédier, au moins en partie, à ces inconvénients.The object of the present invention is to overcome, at least in part, these disadvantages.

A cet effet, la présente invention a pour objet une pièce d'horlogerie telle que définie à la revendication 1.For this purpose, the present invention relates to a timepiece as defined in claim 1.

Grâce à ce dispositif de correction, il est possible non seulement de neutraliser les mouvements du rouage de transmission autour de deux axes d'articulation avec un seul différentiel, mais de neutraliser les mouvements du rouage de transmission autour d'un nombre quelconque d'axes à l'aide d'un seul différentiel. Grâce à cette particularité, l'invention n'est pas limitée à la seule correction de l'assiette du dispositif régulateur, même si cette correction présente un intérêt évident, mais offre d'autres possibilités encore inconnues jusqu'ici.With this correction device, it is possible not only to neutralize the movements of the transmission train about two axes of articulation with a single differential, but to neutralize the movements of the transmission train around any number of axes. help of a single differential. Thanks to this feature, the invention is not limited to the only correction of the attitude of the regulating device, even if this correction is of obvious interest, but offers other possibilities still unknown so far.

Avantageusement, un rouage inverseur et un différentiel avec satellite inverseur permettent d'annuler en une fois les rotations des articulations, ne transmettant à la sortie que le mouvement généré par la transmission.Advantageously, an inverter train and a differential with a reversing satellite make it possible to cancel the rotations of the articulations at one time, transmitting at the output only the movement generated by the transmission.

Les particularités du dispositif de correction de la pièce d'horlogerie objet de la présente invention apparaîtront plus clairement au cours de la description suivante, qui sera faite à l'aide des dessins annexés qui illustrent, schématiquement et à titre d'exemple, trois formes d'exécution ainsi qu'une variante de cette pièce d'horlogerie.

  • La figure 1 est une vue en coupe selon les deux axes d'articulation d'un schéma de principe de la première forme d'exécution;
  • la figure 2 est une vue en coupe semblable à la figure 1 d'une deuxième forme d'exécution;
  • la figure 3 est une vue en coupe semblable aux vues précédentes d'une variante de la figure 1;
  • la figure 4 est une vue en coupe semblable aux vues précédentes d'une troisième forme d'exécution.
The particularities of the correction device of the timepiece object of the present invention will appear more clearly in the following description, which will be made with the aid of the accompanying drawings which illustrate, schematically and by way of example, three forms. execution and a variant of this timepiece.
  • The figure 1 is a sectional view along the two axes of articulation of a schematic diagram of the first embodiment;
  • the figure 2 is a sectional view similar to the figure 1 a second embodiment;
  • the figure 3 is a sectional view similar to the previous views of a variant of the figure 1 ;
  • the figure 4 is a sectional view similar to the previous views of a third embodiment.

La figure 1 est une représentation très schématique d'une partie du rouage de finissage d'une pièce d'horlogerie, de la roue des secondes à la roue d'échappement. La grande moyenne ou roue de centre, la roue de moyenne et le barillet, d'une part et l'échappement et le balancier-spiral, d'autre part n'ont pas été représentés.The figure 1 is a very schematic representation of a part of the finishing gear of a timepiece, from the seconds wheel to the escape wheel. The large average or center wheel, the average wheel and the barrel, on the one hand and the escapement and the sprung balance, on the other hand have not been represented.

La pièce d'horlogerie comporte un bâti 1 sur lequel un premier cadre support 2 est monté pivotant autour d'un axe A1. A cet effet, un premier arbre 3 centré sur l'axe A1 est solidaire du bâti 1 et est librement engagé dans une ouverture qui traverse une première face du cadre 2. Un pivot 4, est solidaire d'une seconde face opposée du cadre 2. Ce pivot 4 occupe sur la seconde face du cadre 2 une position correspondant à celle occupée par l'ouverture traversant la première face. Ce pivot 4 est engagé librement dans une ouverture 5 du bâti 1, centrée sur l'axe A1.The timepiece comprises a frame 1 on which a first support frame 2 is pivotally mounted about an axis A 1 . For this purpose, a first shaft 3 centered on the axis A 1 is integral with the frame 1 and is freely engaged in an opening which passes through a first face of the frame 2. A pivot 4 is secured to a second opposite face of the frame 2. This pivot 4 occupies on the second face of the frame 2 a corresponding position to that occupied by the opening crossing the first face. This pivot 4 is engaged freely in an opening 5 of the frame 1, centered on the axis A 1 .

Un second cadre support 6 est monté sur le premier cadre support 2 autour d'un axe de pivotement A2 orthogonal à l'axe A1. A cet effet, un pivot 7 solidaire d'une première face du second cadre support 6 est engagé librement dans une ouverture centrée sur l'axe A2, ménagée dans une face du premier cadre support 2 perpendiculaire aux deux faces opposées traversées par l'axe A1. L'extrémité d'un élément tubulaire 8 solidaire de la face opposée à la première face du cadre support 6 et occupant sur cette face opposée une position correspondant à celle occupée par le pivot 7 sur la première face, est engagé librement dans une ouverture centrée sur l'axe A2 et ménagée dans la face du premier cadre support 2 opposée à celle dans laquelle est engagé le pivot 7.A second support frame 6 is mounted on the first support frame 2 around a pivot axis A 2 orthogonal to the axis A 1 . For this purpose, a pivot 7 secured to a first face of the second support frame 6 is freely engaged in an opening centered on the axis A 2 , formed in a face of the first support frame 2 perpendicular to the two opposite faces traversed by the axis A 1 . The end of a tubular element 8 integral with the face opposite the first face of the support frame 6 and occupying on this opposite face a position corresponding to that occupied by the pivot 7 on the first face, is engaged freely in a centered opening on the axis A 2 and formed in the face of the first support frame 2 opposite to that in which the pivot 7 is engaged.

Deux trains d'engrenages parallèles sont répartis sur les deux cadres supports 2 et 6. Le premier train d'engrenage est celui de la transmission du mouvement engendré par le ressort moteur logé dans le barillet (non représenté) et contrôlé par l'échappement associé au balancier-spiral (non représentés), auquel vient s'ajouter le mouvement des cadres supports 2, 6 autour des axes A1, A2. Le second train d'engrenage est celui qui permet de totaliser les mouvements angulaires engendré par le pivotement des cadres supports 2, 6 autour des axes A1, A2 et constitue l'engrenage de référence des rotations des supports 2, 6 par rapport au bâti 1.Two parallel gear trains are distributed on the two support frames 2 and 6. The first gear is that of the transmission of the movement generated by the motor spring housed in the barrel (not shown) and controlled by the associated exhaust the sprung balance (not shown), to which is added the movement of the support frames 2, 6 around the axes A 1 , A 2 . The second gear train is the one that makes it possible to totalize the angular movements generated by the pivoting of the support frames 2, 6 around the axes A 1 , A 2 and constitutes the reference gearing of the rotations of the supports 2, 6 relative to the built 1.

Le premier train d'engrenage comporte une première roue de transmission 9 montée librement autour de l'arbre 3 solidaire du bâti 1 et coaxial à l'axe A1. Cette première roue de transmission 9 correspond à la roue des secondes du rouage de finissage et présente un pignon 9a destiné à engrener avec la roue de moyenne (non représentée), montée sur le bâti 1. Cette première roue de transmission 9 engrène avec une deuxième roue de transmission 10 montée librement dans l'élément tubulaire 8 centré sur le second axe A2 de pivotement du second cadre support 6. A cet effet, cette deuxième roue de transmission 10 est solidaire d'un arbre 10b qui est monté pivotant dans l'élément tubulaire 8 du second cadre support 6. A son extrémité opposée à celle solidaire de la seconde roue de transmission 10, l'arbre 10b porte un pignon 10a.The first gear train comprises a first transmission wheel 9 mounted freely around the integral shaft 3 of the frame 1 and coaxial with the axis A 1 . This first transmission wheel 9 corresponds to the second wheel of the finishing train and has a pinion 9a intended to mesh with the average wheel (not shown), mounted on the frame 1. This first transmission wheel 9 meshes with a second transmission wheel 10 freely mounted in the tubular element 8 centered on the second pivot axis A 2 of the second support frame 6. For this purpose, this second transmission wheel 10 is integral with a shaft 10b which is pivotally mounted in the tubular element 8 of the second support frame 6. At its end opposite to that integral with the second transmission wheel 10, the shaft 10b carries a pinion 10a.

Avant de poursuivre la description du train d'engrenage de transmission, on veut décrire ici le train d'engrenage de référence de la rotation des cadres supports 2, 6, par rapport au bâti 1. La première roue 11 de ce train d'engrenage de référence que l'on appellera première roue de référence 11, est solidaire de l'arbre 3, lui-même solidaire du bâti 1. Cette première roue de référence 11 est aussi coaxiale à la première roue 9 du premier train d'engrenage de transmission du rouage de finissage. Elle engrène avec une seconde roue de référence 12 montée pivotante autour de l'axe A2. Le rapport entre les roues de transmission 9 et 10 est identique au rapport entre les roues de références 11 et 12.Before continuing with the description of the transmission gear train, it is desired to describe here the reference gear train of the rotation of the support frames 2, 6 relative to the frame 1. The first wheel 11 of this gear train reference which will be called the first reference wheel 11, is integral with the shaft 3, itself integral with the frame 1. This first reference wheel 11 is also coaxial with the first wheel 9 of the first gear train of transmission of the work train. It meshes with a second reference wheel 12 pivotally mounted about the axis A 2 . The ratio between the transmission wheels 9 and 10 is identical to the ratio between the reference wheels 11 and 12.

Il résulte de cette disposition des deux trains d'engrenages en parallèles que toute rotation entre le cadre support 2 et le bâti 1 autour de l'axe A1 ainsi qu'entre les cadres supports 2 et 6 autour de l'axe A2 se traduit par une rotation identique des roues 10 et 12 si la roue 9 du premier train d'engrenage de transmission est immobile comme l'est la roue 11 du second train d'engrenage de transmission de la seule rotation des cadres supports 2, 6.It follows from this arrangement of the two gear trains in parallel that any rotation between the support frame 2 and the frame 1 about the axis A 1 and between the support frames 2 and 6 around the axis A 2 is translated by an identical rotation of the wheels 10 and 12 if the wheel 9 of the first gear transmission gear is immobile as is the wheel 11 of the second transmission gear transmission of the only rotation of the support frames 2, 6.

Comme dans la réalité la roue 9 du train d'engrenage de transmission de la force du ressort moteur à l'échappement est entraînée par pas successifs à la fréquence à laquelle la roue d'échappement libère l'énergie du ressort moteur sous le contrôle du balancier-spiral, cette rotation séquentielle régulière de la roue 10 s'ajoute à la rotation aléatoire des cadres supports 2, 6 autour des axes A1, respectivement A2.As in the real world, the wheel 9 of the gear train for transmitting the force of the mainspring to the exhaust is driven in successive steps to the frequency at which the escape wheel releases the energy of the mainspring under the control of the engine. balance-spiral, this regular sequential rotation of the wheel 10 is added to the random rotation of the support frames 2, 6 around the axes A 1 , respectively A 2 .

Le rôle du dispositif de correction différentiel que nous allons décrire maintenant est précisément de neutraliser ces rotations aléatoires provenant de la rotation des cadres supports 2, 6 qui se superposent à la rotation du premier rouage de transmission 9, 10 contrôlé par le dispositif réglant de la pièce d'horlogerie.The role of the differential correction device that we will now describe is precisely to neutralize these random rotations resulting from the rotation of the support frames 2, 6 which are superimposed on the rotation of the first transmission train 9, 10 controlled by the control device of the timepiece.

L'arbre 10b de la deuxième roue du premier train d'engrenage de transmission de l'énergie du ressort moteur à l'échappement sert d'élément de pivotement à une roue planétaire 13 qui constitue la sortie du différentiel. Cette roue planétaire engrène avec un pignon 14a d'une roue 14, ici correspondant à la roue des secondes, engrenant avec un pignon 15a d'une roue 15 correspondant à la roue d'échappement.The shaft 10b of the second wheel of the first energy transmission gear train of the exhaust motor spring serves as a pivoting member to a sun gear 13 which constitutes the output of the differential. This planetary wheel meshes with a pinion 14a of a wheel 14, here corresponding to the seconds wheel, meshing with a pinion 15a of a wheel 15 corresponding to the escape wheel.

La roue planétaire 13 porte deux satellites 16, 17 engrenant l'un avec l'autre, le satellite 16 engrenant aussi avec le pignon 10a de la deuxième roue du train d'engrenage de transmission de la force motrice. Ce pignon 10a constitue une première entrée par laquelle le différentiel est relié au train d'engrenage de transmission de la force motrice. Le second satellite 17 engrène avec un renvoi 18 monté libre autour de l'élément tubulaire 8 centré sur le second axe A2. Ce renvoi 18 est relié à un pignon 12a de la roue 12 du second train d'engrenage de référence, par deux renvois 19, 20 engrenant l'un avec l'autre. Les axes de ces renvois 19, 20 sont solidaires du second cadre support 6. Le premier renvoi 19 engrène avec le renvoi 18 et le second 20 engrène avec le pignon 12a.The sun gear 13 carries two satellites 16, 17 meshing with each other, the satellite 16 also meshing with the pinion 10a of the second wheel of the drive gear transmission gear. This pinion 10a constitutes a first input through which the differential is connected to the transmission gear train of the driving force. The second satellite 17 meshes with a return 18 mounted free around the tubular element 8 centered on the second axis A 2 . This reference 18 is connected to a pinion 12a of the wheel 12 of the second reference gear train, by two referrals 19, 20 meshing with each other. The axes of these references 19, 20 are integral with the second support frame 6. The first reference 19 meshes with the return 18 and the second meshes with the pinion 12a.

Par ces renvois 18, 19, 20, les déplacements angulaires des cadres supports 2, 6 autour des axes A1, A2 sont transmis au second satellite 17 et comme ces renvois sont en nombre impair, le mouvement angulaire transmis au second satellite 17 est inversé, ce qui permet de neutraliser à la sortie 13 du différentiel, les mouvements angulaires induits dans le premier rouage de transmission par les déplacement angulaires des cadres supports 2 et 6. Ces renvois 18, 19, 20 constituent donc des mobiles inverseursBy these references 18, 19, 20, the angular displacements of the support frames 2, 6 around the axes A 1 , A 2 are transmitted to the second satellite 17 and as these references are in odd number, the angular movement transmitted to the second satellite 17 is inverted, which makes it possible to neutralize at the output 13 of the differential, the angular movements induced in the first transmission train by the angular displacements of the support frames 2 and 6. These references 18, 19, 20 therefore constitute reversing mobiles

Comme on peut le constater, ce dispositif de correction différentiel permet de déduire tous les mouvements des supports 2, 6 à l'aide d'un seul différentiel et d'un système inverseur et ceci quel que soit le nombre de supports et d'axes d'articulation, comme on le verra dans la forme d'exécution de la figure 2.As can be seen, this differential correction device makes it possible to deduce all the movements of the supports 2, 6 using a single differential and an inverter system and this, whatever the number of supports and axes. of articulation, as will be seen in the embodiment of the figure 2 .

Dans le cas où le système de deux supports 2, 6 montés pivotant autour de deux axes orthogonaux est utilisé pour maintenir l'assiette de la partie 6b du cadre support 6 portant la roue d'échappement 15 associée à l'échappement et au balancier-spiral (non représentés) formant le système réglant, ayant une assiette sensiblement constante, la partie 6a du cadre support 6, opposée à la partie 6b par rapport à l'axe A2, est conçue pour former ou pour porter un contrepoids afin de maintenir l'assiette de la surface 6b portant le système réglant en position constante quelle que soit la position du bâti 1. L'axe de la roue de secondes 14, portée par le support 6 qui est maintenu dans une position constante, peut avantageusement porter une aiguille indicatrice, comme illustré notamment sur la figure 1.In the case where the system of two supports 2, 6 mounted pivoting about two orthogonal axes is used to maintain the attitude of the part 6b of the support frame 6 carrying the escape wheel 15 associated with the escapement and the pendulum- spiral (not shown) forming the regulating system, having a substantially constant attitude, the part 6a of the support frame 6, opposite the part 6b with respect to the axis A 2 , is designed to form or to carry a counterweight in order to maintain the attitude of the surface 6b carrying the system regulating in a constant position whatever the position of the frame 1. The axis of the seconds wheel 14, carried by the support 6 which is held in a constant position, may advantageously carry a pointer, as illustrated in particular in the figure 1 .

Selon le principe de l'invention, les rotations générées par les articulations entre les supports 2, 6 sont subies de manière identique par les deux trains d'engrenages. Le second train d'engrenage dit de référence partant d'une roue 11 solidaire du bâti 1, les rotations de la seconde roue de référence 12 ne sont dus qu'à la rotation des supports 2, 6 autour des axes A1, A2. Le dispositif correcteur doit donc soustraire de la rotation de la deuxième roue de transmission 10 les rotations de la seconde roue de référence 12 pour ne garder que la rotation provenant de la première roue de transmission 9.According to the principle of the invention, the rotations generated by the joints between the supports 2, 6 are subjected to identical way by the two gear trains. The second reference gear train starting from a wheel 11 integral with the frame 1, the rotations of the second reference wheel 12 are only due to the rotation of the supports 2, 6 around the axes A 1 , A 2 . The corrector device must therefore subtract from the rotation of the second transmission wheel 10 the rotations of the second reference wheel 12 to keep only the rotation coming from the first transmission wheel 9.

La rotation transmise par l'une des deuxièmes roues du train d'engrenage de transmission 10 ou du train d'engrenage de référence 12 doit être inversée pour être soustraite. Dans l'exemple illustré par la figure 1 c'est la rotation de la seconde roue de référence 12 qui est inversée, mais il serait aussi possible d'inverser la rotation de la deuxième roue de transmission 10.The rotation transmitted by one of the second wheels of the transmission gear train 10 or the reference gear train 12 must be reversed to be subtracted. In the example illustrated by the figure 1 it is the rotation of the second reference wheel 12 which is reversed, but it would also be possible to reverse the rotation of the second transmission wheel 10.

L'avantage de la solution proposée est que l'énergie absorbée par les frottements dus aux pignons inverseurs est générée par l'action combinée du contrepoids et de la gravité et non soustraite à l'énergie transmise depuis le bâti et que cette absorption d'énergie amortit d'éventuelles oscillations des bâtis autour de leurs axes respectifs. Cette absorption évite également une mise en rotation intempestive des cadres lorsque l'axe A1 est sensiblement vertical. L'ajustement de cette absorption est donc possible et souhaitable.The advantage of the proposed solution is that the energy absorbed by the friction due to the reversing gears is generated by the combined action of the counterweight and the gravity and not subtracted from the energy transmitted from the frame and that this absorption of energy dampens any oscillations of the frames around their respective axes. This absorption also prevents untimely rotation of the frames when the axis A1 is substantially vertical. Adjustment of this absorption is therefore possible and desirable.

Etant donné que nous avons une rotation directe et l'autre inversée, la différence est obtenue par un différentiel. Puisque l'on désir que les influences des deux entrées du différentiel soient égales, nous avons choisi d'utiliser deux satellites 16, 17 engrenant l'un avec l'autre, l'un 16 engrenant avec une entrée 10a côté transmission du différentiel et l'autre 17 engrenant avec une entrée 18 côté référence du différentiel. Avec un tel différentiel la vitesse d'entrée est divisée par deux et nécessite une adaptation du rapport entre la roue planétaire 13 et le pignon 14a de la roue de seconde 14.Since we have a direct rotation and the other inverted, the difference is obtained by a differential. Since it is desired that the influences of the two inputs of the differential be equal, we have chosen to use two satellites 16, 17 meshing with each other, one 16 meshing with an input 10a on the transmission side of the differential and the other 17 meshing with an input 18 reference side of the differential. With such a differential the speed of entry is divided by two and requires an adaptation of the ratio between the sun gear 13 and the pinion 14a of the second wheel 14.

La particularité de ce dispositif de correction fait que les rotations autour des axes A1, A2 s'additionnent, en sorte que l'on peut avoir un nombre d'axes d'articulations quelconque, leurs rotations totales par rapport au bâti 1 s'additionnent algébriquement. En effet à supposer que deux supports tournent en sens inverse autour d'axes parallèles, la rotation par rapport au bâti sera leur rotation relative.The particularity of this correction device is that the rotations around the axes A 1 , A 2 add up, so that we can have a number of axes of any joint, their total rotations relative to the frame 1 s add up algebraically. Indeed supposing that two supports rotate in opposite directions about parallel axes, the rotation relative to the frame will be their relative rotation.

Dans la forme d'exécution illustrée par la figure 2 qui va être décrite, les organes identiques à ceux de la figure 1 ont les mêmes références, les organes homologues ont la même référence assortie d'un prime et les nouveaux organes ont de nouvelles références.In the embodiment illustrated by the figure 2 which will be described, the identical organs to those of the figure 1 have the same references, the homologous bodies have the same reference with a premium and the new organs have new references.

La figure 2 illustre une forme d'exécution dans laquelle trois supports 2, 6 et 21 tournent autour de trois axes A1, A2, A3, dont les deux axes A2, A3 sont orthogonaux à l'axe A1, les deux supports 6 et 21 étant montés pivotant autour de deux axes confondus, mais étant indépendants l'un par rapport à l'autre. Il faut d' ailleurs préciser ici que l'axe A1 n' est pas nécessairement orthogonal aux axes A2, A3, mais que ces axes pourraient être parallèles ou occuper d'autres positions angulaires entre eux, sans changer le principe de neutralisation des rotations des supports autour des axes sur la transmission d'une rotation à travers un train d'engrenage de transmission, réparti sur les différents supports articulés les uns aux autre, sur lequel est basée l'invention.The figure 2 illustrates an embodiment in which three supports 2, 6 and 21 rotate around three axes A 1 , A 2 , A 3 , whose two axes A 2 , A 3 are orthogonal to the axis A 1 , the two supports 6 and 21 being mounted pivoting about two axes combined, but being independent relative to each other. It should be noted here that the axis A 1 is not necessarily orthogonal to the axes A 2 , A 3 , but that these axes could be parallel or occupy other angular positions between them, without changing the principle of neutralization. rotations of the supports about the axes on the transmission of a rotation through a gear transmission gear, distributed on the different supports articulated to each other, on which the invention is based.

La forme d'exécution de la figure 2 n'est destinée qu'à montrer que le dispositif de correction selon l'invention est opérant quel que soit le nombre de supports articulés les uns aux autres. Par souci de simplification, l'axe de pivotement A3 est confondu à l'axe A2. En réalité, ces deux axes ne le seraient très vraisemblablement pas.The form of execution of the figure 2 is intended only to show that the correction device according to the invention is operative regardless of the number of supports articulated to each other. For the sake of simplicity, the pivot axis A 3 coincides with the axis A 2 . In fact, these two axes would very likely not be.

Dans cette forme d'exécution, le premier train d'engrenage de transmission comporte une roue supplémentaire 22 coaxiale à l'axe de pivotement A3. Cette roue porte un pignon 22a destiné à être relié à une source motrice, notamment un ressort logé dans un barillet (non représentés). Cette roue peut être ici la roue des secondes. Elle engrène avec la roue 9' coaxiale à l'axe de pivotement A1, laquelle est ici solidaire d'un pignon 9'a qui engrène avec la roue 10.In this embodiment, the first transmission gear train comprises an additional wheel 22 coaxial with the pivot axis A 3 . This wheel carries a pinion 22a intended to be connected to a driving source, in particular a spring housed in a barrel (not shown). This wheel can be here the wheel of seconds. It meshes with the wheel 9 'coaxial with the pivot axis A 1 , which is here secured to a pinion 9'a which meshes with the wheel 10.

La roue supplémentaire 22 du premier train d'engrenage de transmission est coaxiale à une roue supplémentaire 23 du second train d'engrenage de référence, qui est solidaire du bâti 1 et qui engrène avec une roue 11'a coaxiale à l'axe de pivotement A1. Cette deuxième roue 11'a est solidaire d'une extrémité d'un arbre 11'b qui est monté pivotant à travers les cadres supports 21 et 2, ainsi qu'à travers la roue 9' du premier train d'engrenage. A son autre extrémité, l'arbre 11'b est solidaire d'une roue 11'c qui engrène avec la roue 12. Tout le reste du mécanisme est identique à celui de la figure 1 auquel on pourra se reporter.The additional wheel 22 of the first gear transmission gear is coaxial with an additional wheel 23 of the second reference gear train, which is integral with the frame 1 and which meshes with a wheel 11'a coaxial with the pivot axis A 1 . This second wheel 11'a is secured to one end of a shaft 11'b which is pivotally mounted through the support frames 21 and 2, and through the wheel 9 'of the first gear. At its other end, the shaft 11'b is integral with a wheel 11'c which meshes with the wheel 12. All the rest of the mechanism is identical to that of the figure 1 to which we can refer.

Grâce au second train d'engrenage de référence 23, 11'a, 11'c, 12, tous les déplacements angulaires des cadres supports 2, 6 et 21 autour de leurs axes respectifs A1, A2, A3, sont additionnés algébriquement par rapport au bâti 1 et à la roue de référence 23 solidaire de ce bâti. Comme dans l'exemple de la figure 1, tous les déplacements angulaires de la roue de référence 12 sont inversés par les renvois 18, 19, 20 et le déplacement angulaire inversé est introduit à une entrée du différentiel dont l'autre entrée reçoit le déplacement angulaire du premier train d'engrenage amené par le pignon 10a, en sorte que le déplacement angulaire de la sortie 13 du différentiel ne correspond plus qu'aux déplacements angulaires engendrés par le premier rouage de transmission quel que soit les déplacement angulaires des supports autours des axes A1, A2, A3.With the second reference gear 23, 11'a, 11'c, 12, all the angular displacements of the support frames 2, 6 and 21 around their respective axes A 1 , A 2 , A 3 , are added algebraically. relative to the frame 1 and the reference wheel 23 integral with this frame. As in the example of figure 1 , all the angular displacements of the reference wheel 12 are inverted by the references 18, 19, 20 and the inverted angular displacement is introduced to a differential input whose other input receives the angular displacement of the first gear set brought by the pinion 10a, so that the angular displacement of the output 13 of the differential no longer corresponds to displacements angular generated by the first transmission train whatever the angular displacement of the supports around the axes A 1 , A 2 , A 3 .

La figure 3 est une variante de la forme d'exécution de la figure 1 dans lequel le différentiel est décentré par rapport à l'axe A2. Dans ce cas, la roue planétaire 13 n'est plus coaxiale à l'axe A2 de pivotement du cadre support 6', mais de l'axe d'un mobile de renvoi 26 engrenant avec le pignon 10a solidaire du mobile de transmission 10 coaxial à l'axe A2. Ce renvoi 26 est solidaire d'un pignon 26a qui engrène avec le satellite 16 du différentiel. Le renvoi 18 est aussi coaxial à ce mobile de renvoi 26 et plus de l'axe A2. Il est en liaison cinématique avec le pignon 12a du mobile de référence 12 par un seul renvoi 20 solidaire du cadre support 6'.The figure 3 is a variant of the embodiment of the figure 1 in which the differential is off-center with respect to the axis A 2 . In this case, the sun wheel 13 is no longer coaxial with the axis A 2 of pivoting of the support frame 6 ', but of the axis of a deflection wheel 26 meshing with the pinion 10a integral with the transmission wheel 10 coaxial with the axis A 2 . This reference 26 is integral with a pinion 26a which meshes with the satellite 16 of the differential. The reference 18 is also coaxial with this deflection wheel 26 and more than the axis A 2 . It is in kinematic connection with the pinion 12a of the reference mobile 12 by a single reference 20 secured to the support frame 6 '.

En effet, étant donné que le satellite 16 du différentiel n'engrène plus directement avec le pignon 10a du mobile de transmission 10 coaxial à l'axe A2, mais par l'intermédiaire d'un mobile de renvoi 26, la rotation transmise au satellite 16 est inversée par rapport à la forme d'exécution de la figure 1. Ce mobile de renvoi 26 est donc un mobile inverseur. Il est donc nécessaire que la rotation transmise au satellite 17 par le renvoi 18 soit aussi inversée, pour permettre au différentiel de déduire les rotations engendrée dans le rouage de transmission par les déplacements angulaires des cadres supports 2, 6' autrement, les déplacements angulaires de ces cadres supports 2, 6' s'ajouterait au lieu de se soustraire.Indeed, since the satellite 16 of the differential meshes more directly with the pinion 10a of the transmission wheel 10 coaxial with the axis A 2 , but by means of a mobile 26, the rotation transmitted to the satellite 16 is reversed with respect to the embodiment of the figure 1 . This return mobile 26 is a mobile inverter. It is therefore necessary that the rotation transmitted to the satellite 17 by the reference 18 is also reversed, to allow the differential to derive the rotations generated in the transmission train by the angular displacements of the support frames 2, 6 'otherwise, the angular displacements of these support frames 2, 6 'would be added instead of subtracting.

La forme d'exécution illustrée par la figure 4 diffère des formes d'exécutions précédentes essentiellement par le fait que le dispositif de correction différentiel est monté sur le bâti 1 de la pièce d'horlogerie et plus sur les supports montés pivotants autour des axes A1 et A2. Grâce à cette disposition, il est possible de réduire le nombre d'éléments montés sur les supports pivotants 2 et 6, en sorte qu'il est possible de réduire leur taille et de rendre le dispositif plus compact.The form of execution illustrated by the figure 4 differs from the preceding embodiments essentially in that the differential correction device is mounted on the frame 1 of the timepiece and more on the supports mounted pivoting about the axes A 1 and A 2 . Thanks to this arrangement, it is possible to reduce the number of elements mounted on the pivoting supports 2 and 6, so that it is possible to reduce their size and make the device more compact.

Pour faciliter la lecture, les organes ayant des fonctions homologues à celles de la forme d'exécution de la figure 1 ont les mêmes références accompagnées du signe *.For ease of reading, organs having functions similar to those of the embodiment of the figure 1 have the same references with the sign *.

Dans cette forme d'exécution, on retrouve les supports 2* et 6* montés pivotant autour des axes A1, respectivement A2. Le support 2* pivote autour de l'élément tubulaire 1*a du bâti 1, coaxial à l'axe A1 et un pivot 4* est engagé librement dans une ouverture 5* du bâti 1*, centrée sur l'axe A1. Une face du support 6* comporte un pivot 7* centré sur l'axe A2 par une ouverture axiale du support 2* dans laquelle ce pivot est monté. La face opposée du support 6* comporte un élément tubulaire 8* dont la face externe est engagée dans une ouverture axiale du support 2*.In this embodiment, there are supports 2 * and 6 * pivotally mounted about the axes A 1 , respectively A 2 . The support 2 * pivots around the tubular element 1 * a of the frame 1, coaxial with the axis A 1 and a pivot 4 * is engaged freely in an opening 5 * of the frame 1 *, centered on the axis A 1 . One face of the support 6 * comprises a pivot 7 * centered on the axis A 2 by an axial opening of the support 2 * in which this pivot is mounted. The opposite face of the support 6 * comprises a tubular element 8 * whose outer face is engaged in an axial opening of the support 2 *.

La face du support 2* opposée à celle portant le pivot 4* présente une ouverture axiale dans laquelle un élément tubulaire 1*a du bâti 1* est engagé. Dans cette forme d'exécution, les deux satellites 16* et 17* engrenant l'un avec l'autre sont portés par un mobile planétaire 9* solidaire d'un pignon 9*a destiné à engrener avec la partie amont du rouage de transmission du mouvement engendré par le ressort moteur logé dans le barillet (non représenté) et contrôlé par l'échappement associé au balancier-spiral (non représentés), dont seule la roue 15* est représentée. Le satellite 16* engrène avec un pignon 12*a solidaire de la roue de référence 12* du rouage de référence du pivotement des cadres supports 2*, 6* autour des axes A1, A2, alors que le satellite 17* engrène avec le renvoi 18* monté pivotant sur l'élément tubulaire 1*a du bâti 1*. Ce renvoi engrène avec un renvoi 19* qui engrène avec un renvoi 20* tous deux montés pivotants sur le bâti 1*. Le renvoi 20* engrène avec un pignon 13*a d'une roue 13* qui constitue la sortie du différentiel et qui est en liaison cinématique avec la partie aval du premier rouage de transmission du mouvement engendré par le ressort moteur. Cette partie aval comporte la roue de seconde 14* et la roue d'échappement 15* portées par le second support 6*.The face of the support 2 * opposite that carrying the pivot 4 * has an axial opening in which a tubular element 1 * of the frame 1 * is engaged. In this embodiment, the two satellites 16 * and 17 * meshing with each other are carried by a planetary mobile 9 * integral with a pinion 9 * for meshing with the upstream portion of the transmission train the movement generated by the motor spring housed in the barrel (not shown) and controlled by the escapement associated with the sprung balance (not shown), of which only the wheel 15 * is shown. The satellite 16 * meshes with a pinion 12 * integral with the reference wheel 12 * of the reference wheel of the pivoting support frames 2 *, 6 * around the axes A 1 , A 2 , while the satellite 17 * meshes with the reference 18 * pivotally mounted on the tubular element 1 * a of the frame 1 *. This reference meshes with a 19 * reference which meshes with a 20 * reference both mounted pivoting on the frame 1 *. The reference 20 * meshes with a pinion 13 * a wheel 13 * which is the output of the differential and which is in kinematic connection with the downstream part of the first gear train of the movement generated by the mainspring. This downstream part comprises the second wheel 14 * and the escape wheel 15 * carried by the second support 6 *.

Cette roue 13* est coaxiale à la première roue 9* du premier rouage de transmission et est montée autour de l'élément tubulaire 1*a solidaire du bâti 1*. Cette roue 13* engrène avec la troisième roue 10* du premier rouage de transmission, dont le pignon 10*a engrène directement avec le pignon 14*a de la roue de secondes 14*.This wheel 13 * is coaxial with the first wheel 9 * of the first transmission train and is mounted around the tubular element 1 * integral with the frame 1 *. This wheel 13 * meshes with the third wheel 10 * of the first transmission train, whose pinion 10 * meshes directly with the pinion 14 * a of the seconds wheel 14 *.

Quant à la roue de référence 12* solidaire du pignon 12*a du rouage de référence de la rotation des supports 2*, 6* autour des axes A1, A2 par rapport au bâti 1*, elle engrène avec la roue de référence 11* qui est solidaire du second support 6* et non plus du bâti comme dans la forme d'exécution de la figure 1.As for the reference wheel 12 * integral with the pinion 12 * has the reference wheel of the rotation of the supports 2 *, 6 * around the axes A 1 , A 2 relative to the frame 1 *, it meshes with the reference wheel 11 * which is secured to the second support 6 * and no longer the frame as in the embodiment of the figure 1 .

Le principe de la déduction des déplacements angulaires engendrés par la rotation des supports 2* et 6* autour des axes A1, A2 est le même que dans les formes d'exécutions précédentes. Le dispositif différentiel avec les inverseurs permettent de déduire les mouvements issus de la rotation des supports 2*, 6* de la transmission du mouvement engendré par le ressort moteur et ceci quel que soit le nombre d'axes de pivotements et le nombre de supports, comme on a pu le voir dans la forme d'exécution illustrée par la figure 2. Ceci montre que le dispositif de correction à différentiel peut être disposé soit au début, soit à la fin de la chaîne cinématique du second rouage de référence, puisque ce rouage de référence permet d'additionner algébriquement la somme des déplacements angulaires des supports 2*, 6* et qu'il introduit cette valeur à une entrée du dispositif de correction à différentiel dont l'autre entrée reçoit le mouvement du premier rouage de transmission auquel s'ajoute le mouvement des supports 2*, 6* qu'il s'agit de soustraire pour ne transmettre à la sortie du différentiel que le mouvement du seul premier rouage de transmission. En fait, le dispositif de correction doit se situer à l'extrémité opposée du mobile solidaire de l'axe de rotation entre deux supports.The principle of deducing the angular displacements generated by the rotation of the supports 2 * and 6 * around the axes A 1 , A 2 is the same as in the previous embodiments. The differential device with the inverters makes it possible to deduce the movements resulting from the rotation of the supports 2 *, 6 * of the transmission of the movement generated by the mainspring regardless of the number of pivot axes and the number of supports, as we have seen in the form of execution illustrated by the figure 2 . This shows that the differential correction device can be arranged either at the beginning or at the end of the kinematic chain of the second reference wheel, since this reference wheel makes it possible to add the sum of the angular displacements of the supports 2 * algebraically, 6 * and that it introduces this value to an input of the correction device to differential whose other input receives the movement of the first gear train to which is added the movement of the supports 2 *, 6 * that it is necessary to subtract to transmit to the output of the differential that the movement of the first gear only of transmission. In fact, the correction device must be located at the opposite end of the mobile secured to the axis of rotation between two supports.

Claims (8)

  1. A timepiece comprising a frame (1), a transmission gear train driven by a wheel unit (9) mounted on the frame, and comprising two parts, one upstream and one downstream (14, 15), distributed on at least two supporting shells (2, 6; 21) pivoting about respective pivot axes (A1, A2) between the frame (1) and one of said supporting shells (2; 21) on the one hand, and between two supporting shells (2, 6) on the other, and a differential correction device neutralizing the angular movements produced in the transmission train by the movements of said supporting shells (2, 6; 21) about their respective axes (A1, A2), the differential correction device comprising reference wheel units (11, 12) coaxial with said respective pivot axes (A1, A2), each of them also being coaxial with a wheel unit (9, 10) of the transmission gear train, and further comprising a geared connection between the two reference wheel units (11, 12, 23, 11a) and a geared connection between the two transmission wheel units (9, 10), the gear ratios between each gearing of these two geared connections being equal, one (11; 23) of said reference wheel units being fixed and coaxial to one of said pivoting axis (A1), and the other (12; 11'a) pivoting about the pivoting axis to which it is coaxial, said correction device further comprising a geared connection between this other reference wheel unit (12) and an input (18) of the differential whose other input (10a) is linked by geared connection to the upstream part of the transmission gear train of one of said supporting shells, and one or more reversing wheel units (19; 26) in one of said geared connections being adapted for reversing the relative rotations at the two inputs (18, 10a) of the differential, whose output (13) is connected kinematically to the downstream part (14, 15) of the transmission train of the other of said supporting shells.
  2. The timepiece as claimed in claim 1, in which the differential comprises a sun wheel unit (13) connected to two planet gears (16, 17) adapted for meshing with each other, one of the planet gears adapted for meshing with a wheel unit (10a, 26a) of the transmission gear train, coaxial with the sun wheel unit (13), the other adapted for meshing with a wheel unit (18) of the differential correction device coaxial with the sun wheel unit (13) and connected by a kinematic connection (19, 20) to the reference wheel unit (12a) pivoting about the pivot axis (A2).
  3. The timepiece as claimed in one of the preceding claims, in which the pivot axes (A1, A2) are orthogonal to each other.
  4. The timepiece as claimed in one of the preceding claims, in which the differential (9*, 12*, 16*, 17*, 18*) of the correction device is mounted on the frame (1*).
  5. The timepiece as claimed in one of the preceding claims, in which the differential of the correction device is coaxial with one of the pivot axes (A1, A2) of said supporting shells (2, 6, 21).
  6. The timepiece as claimed in one of claims 1-4, in which the differential of the correction device is eccentric with respect to the pivot axes (A1, A2) of said supporting shells (2, 6, 21).
  7. The timepiece as claimed in one of the preceding claims, in which an indicator member is connected to the arbor of one of the wheel units (14) of the downstream part of the transmission train.
  8. The timepiece as claimed in one of the preceding claims, in which that part (6a) of the supporting shell (6) which is located opposite the part (6b) of this supporting shell carrying the downstream part of the transmission train is provided with a counterweight.
EP08783457.8A 2007-08-29 2008-08-25 Timepiece Active EP2181362B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08783457.8A EP2181362B1 (en) 2007-08-29 2008-08-25 Timepiece

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP07405254A EP2031465A1 (en) 2007-08-29 2007-08-29 Clock piece
PCT/CH2008/000357 WO2009026735A2 (en) 2007-08-29 2008-08-25 Time piece
EP08783457.8A EP2181362B1 (en) 2007-08-29 2008-08-25 Timepiece

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EP2181362A2 EP2181362A2 (en) 2010-05-05
EP2181362B1 true EP2181362B1 (en) 2013-11-20

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EP07405254A Withdrawn EP2031465A1 (en) 2007-08-29 2007-08-29 Clock piece
EP08783457.8A Active EP2181362B1 (en) 2007-08-29 2008-08-25 Timepiece

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Application Number Title Priority Date Filing Date
EP07405254A Withdrawn EP2031465A1 (en) 2007-08-29 2007-08-29 Clock piece

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EP (2) EP2031465A1 (en)
JP (1) JP5389805B2 (en)
CN (1) CN101939707B (en)
WO (1) WO2009026735A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2124111B1 (en) 2008-04-30 2010-11-17 Cartier Création Studio S.A. Mechanism preventing movement variations due to gravity on a sprung balance and timepiece equipped with such a mechanism
EP2533109B1 (en) * 2011-06-09 2019-03-13 Cartier International AG Mechanism preventing rate variations due to gravitation on an adjusting device with a spiral balance and timepiece equipped with such an improvement
CH705244B1 (en) * 2011-07-07 2016-06-30 Gfpi S A Timepiece.
CH705836B1 (en) 2011-12-02 2016-01-15 Lvmh Swiss Mft Sa Timepiece.
JP6143185B2 (en) * 2013-09-04 2017-06-07 セイコーインスツル株式会社 Operation stabilization mechanism, movement and mechanical watch

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH189470A (en) * 1935-04-17 1937-02-28 Frantisek Ing Hejduk Variable transmission gear.
US6548771B1 (en) * 1999-08-12 2003-04-15 Seiko Instruments Inc. Multipole attitude detector switch with liquid contact
DE602004016137D1 (en) * 2004-07-08 2008-10-09 Audemars Piguet Renaud Et Papi Correction mechanism of a plate of a regulating device for a Uhruh coil spring
DE602005021748D1 (en) * 2005-03-30 2010-07-22 Montres Breguet Sa Watch with at least two regulating systems

Also Published As

Publication number Publication date
WO2009026735A4 (en) 2009-07-09
JP5389805B2 (en) 2014-01-15
WO2009026735A2 (en) 2009-03-05
JP2010537205A (en) 2010-12-02
WO2009026735A3 (en) 2009-05-28
CN101939707A (en) 2011-01-05
EP2181362A2 (en) 2010-05-05
EP2031465A1 (en) 2009-03-04
CN101939707B (en) 2013-06-12

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