EP2786214B1 - Timepiece part - Google Patents

Timepiece part Download PDF

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Publication number
EP2786214B1
EP2786214B1 EP12794960.0A EP12794960A EP2786214B1 EP 2786214 B1 EP2786214 B1 EP 2786214B1 EP 12794960 A EP12794960 A EP 12794960A EP 2786214 B1 EP2786214 B1 EP 2786214B1
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EP
European Patent Office
Prior art keywords
wheel
pivoting system
wheels
timepiece according
escapement
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EP12794960.0A
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German (de)
French (fr)
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EP2786214A1 (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 of EP2786214A1 publication Critical patent/EP2786214A1/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
    • G04B18/00—Mechanisms for setting frequency
    • G04B18/08—Component parts or constructional details
    • 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 unbalance 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
    • G04B13/02—Wheels; Pinions; Spindles; Pivots

Definitions

  • the present invention relates to the field of mechanical watchmaking. It relates, more particularly, to a timepiece comprising an exhaust trim correction system, to reduce the influence of the variations of orientation of said timepiece, on its march. It comprises a frame carrying an energy source, a cage comprising a first pivoting system about a first axis, by means of which a support is pivotally mounted inside said cage, the first pivoting system comprising two shafts. coaxial. An exhaust is further arranged on the support.
  • the cage comprises a second pivoting system about a second axis substantially perpendicular to the first, by means of which the cage is pivotally mounted with reference to the frame.
  • the second pivoting system comprises two shafts, coaxial.
  • a shaft of the first pivoting system carries a wheel forming a first kinematic chain with a wheel carried by a shaft of the second pivoting system.
  • a timepiece as mentioned above is known in particular by the application WO2009 / 026735 .
  • An embodiment is proposed at figure 1 . More specifically, this document discloses a timepiece comprising at least two articulated supports, a first 10 being articulated with reference to the frame along a first axis, the second 12 being articulated with reference to the first support along a second axis orthogonal to the first.
  • the exhaust 14 is mounted on the second support and, thanks to the joint, can maintain a substantially stable orientation, preferably substantially horizontal, regardless of the position of the frame.
  • horizontal orientation it is defined that the planes of the mobiles are horizontal, the axes of these mobiles are vertical.
  • the timepiece comprises a first gear transmission gear 16, kinematically connected to a power source and bringing this energy to the exhaust 14, and a second reference gear train 18, connected to a fixed element of the frame.
  • the two gear trains are arranged in parallel, so that any rotation between the supports and the frame or between the supports themselves, results in identical rotation of the gear trains and reference transmission.
  • the timepiece further comprises an inverter system 20 making it possible for the last mobiles of the transmission and reference gear trains to rotate in opposite directions.
  • a differential correction device 22 makes it possible to cancel all the movements of the supports in order to bring to the exhaust only the energy coming from the energy source.
  • the transmission gear train 16 brings to a first input of the differential correction device, a movement corresponding to the rotation of the supports (R) and to the rotation induced by the torque of the energy source (E).
  • the reference gear train 18 also transmits a movement corresponding to the rotation of the supports (R), to the inverter system 20, the latter thus transmitting an inverse movement (-R) to a second input of the differential correction device.
  • the latter is arranged so as to perform the algebraic mean of the first input and the second input (ie (R-R + E) / 2), so that, at its output, only a rotation induced by the couple of the energy source.
  • the supports carry the two gear trains, respectively transmission 16 and reference 18, an inverter system 20 and a differential correction device 22, in addition to the exhaust system.
  • the present invention aims to reduce the number of parts carried by the media and reduce the volume occupied by the latter.
  • one of the wheels carried by the second pivoting system is kinematically connected to the power source, and the other wheel carried by the pivoting system is fixed relative to the frame.
  • the two wheels carried by the first pivoting system are connected kinematically with an input mobile of a differential arranged to transmit by an output mobile the average of the rotations received at its inputs, said output mobile being kinematically connected. at the exhaust and the mobile input and output of the differential being movable about an axis of rotation parallel to the axis of rotation of the exhaust mobiles.
  • a cage 50 which is advantageously defined by a substantially annular reinforcement to limit the volume it occupies in its movements, as will be seen later.
  • This cage 50 comprises a first pivoting system 52 around a first axis AA, more particularly visible on the figure 3 .
  • This first pivoting system 52 comprises two shafts 54a and 54b, arranged coaxially along the axis AA.
  • the term tree is not limiting and must be understood in a functional sense, that is to say that one could envisage a construction in which the trees are defined by two parts of a tree, on which pivot the elements that will now be described.
  • an index a refers to an element of the shaft 54a and an index b refers to an element of the shaft 54b.
  • Each shaft 54a and 54b comprises a rod 58a and 58b pivoting on two bearings 60a and 60b disposed at the ends of a tube 62a and 62b. These are fixed on a support 64 which will be described in more detail below.
  • Each tube 62a or 62b receives, on its outer periphery, a bearing, for example ball, of which an inner ring 68a, 68b is fixed on the tube 62a, 62b and whose outer ring 70a, 70b is disposed in an opening 72a, 72b of the cage 50.
  • a washer 74a, 74b closes the bearing.
  • This first pivoting system 52 makes it possible to pivot the support 64 inside the cage 50.
  • each rod 58a, 58b receives, at a distal end with reference to the center of the cage 50, a wheel 76a, 76b, and at a second proximal end with reference to the center of the cage 50, a pinion 78a, 78b.
  • the cage 50 also comprises a second pivoting system 152 around a second axis BB, substantially perpendicular to the first axis AA.
  • This second pivoting system comprises two shafts 154a and 154b, arranged coaxially along the axis BB.
  • the construction of the shafts of the second pivot system is similar to that described above.
  • the elements of the second pivot system are designated by reference numbers showing the reference numbers of the first pivot system, preceded by a 1.
  • Each shaft 154a, 154b comprises a rod 158a, 158b pivoting on two bearings 160a, 160b disposed at the ends of a tube 162a, 162b, fixed in an opening 172a, 172b of the cage 50.
  • Each tube 162a, 162b receives, on its outside circumference, a bearing, for example balls, including an inner ring 168a, 168b, is fixed on the tube 162a, 162b, and the outer ring 170a, 170b is disposed in a housing of the frame, not shown.
  • a washer 174a, 174b closes the bearing. This second pivoting system makes it possible to rotate the cage 50 with reference to the frame.
  • each rod 158a, 158b receives, at a proximal end with reference to the center of the cage 50, a wheel 176a, 176b. We will return later to the distal end of rods 158a and 158b.
  • Each wheel 76a, 76b of the first pivot system 52 forms a kinematic chain with a wheel 176a, 176b of the second transmission system. pivoting. There is thus a first kinematic chain between the wheels 76a and 176a of two shafts 54a and 154a, respectively of the first and second pivot systems, and a second kinematic chain between the other wheels 76b and 176b of the two other shafts 54b and 154b.
  • these kinematic links are made respectively by a reference 80a, 80b mounted on the cage 50.
  • the reference 80a, 80b is disposed substantially at 45 ° with reference to the wheels with which it meshes.
  • Such an arrangement allows that only this reference 80a, 80b has a conical type toothing, while the wheels 76a, 176a, respectively 76b, 176b have straight teeth. All these wheels are flat.
  • Such an embodiment is particularly interesting, compared to the configuration of the meshing between the wheels of the transmission and reference chains of the timepiece of the state of the art proposed at the time. figure 1 .
  • the drive ratios of the first driveline and the second drivetrain are identical, so that the wheels 76a and 76b carried by the two shafts 54a and 54b of the first pivoting system 52 are driven to the same speed by the movements of the support 64.
  • the wheels 76a, 76b, 176a and 176b of the pivot systems 52a and 52b and the references 80a and 80b have the same number of teeth. They are also of the same diameter.
  • the wheel 76a and the pinion 78a of a first shaft 54a of the first pivot system 52 face those 76b and 78b of the other shaft 54b of this pivot system. Seen from the center of the cage 50, the pinions 78a and 78b are thus driven in opposite directions of rotation, at the same absolute speed, without however being kinematically connected to each other by a gear train.
  • each of these pinions 78a and 78b meshes with an input of a differential 200, the axes of rotation of the mobiles are parallel to that of the mobiles of the exhaust.
  • the differential 200 is intended to have a substantially constant orientation, typically along a substantially vertical axis.
  • the pinion 78a meshes with a first board 202a provided with teeth to edge.
  • This first plate 202a is integral with a first sun gear 204a meshing with a first satellite 206a pivotally mounted on a planet carrier 208.
  • the latter is coaxial with the first sun gear 204a and is pivotable with reference to the other elements of the differential .
  • the planet carrier 208 is provided with a toothing and defines the output of the differential.
  • the pinion 78b meshes with a second board 202b provided with teeth to sing.
  • This second plate 202b is integral with a second sun gear 204b meshing with a second satellite 206b pivotally mounted on the planet carrier 208.
  • the second satellite 206b is also arranged to mesh with the first satellite 206a.
  • Such a differential configuration 200 allows the output wheel, that is to say the planet carrier 208, to transmit the average of the rotations received at its inputs.
  • the first board 202a and the second board 202b rotate in different directions.
  • the ratios between the pinions 78a, 78b and the boards 202a and 202b are calculated so that the boards rotate at the same absolute speed.
  • the proposed configuration allows a great compactness of the differential. Due to its configuration, it can be easily accommodated in a cavity of the support 64. These space savings offer the possibility of improving the pivoting of the elements of the differential 200.
  • pivots on bearings 210, the second board 202b and the planet carrier 208 are pivoted on bearings, respectively 212 and 214, for example balls, fixed in ad-hoc openings of the support 64.
  • the axis 209a of the first plate 202a is thus pivotally mounted between two bearings 210, typically formed by stones.
  • One is driven into a bridge 216 carried by the support 64 and the other is driven into a tube 218, also fixed on the support 64, typically by a screw 220 inserted into the tube.
  • the second board 202b is secured to a hub 222, comprising a central opening, through which the axis 209b of the second board.
  • the axis 209b of the second board is fitted in this central opening and is freely traversed by the axis 209a of the first board.
  • the axis 209b of the second board has a flange 224 which defines a groove with a flank of the hub 222.
  • An inner ring 226 of the ball bearing 212 is fitted in the groove, while an outer ring 228 of this bearing is fixed. on an additional bridge 230 of the support 64.
  • the second board 202b is thus guided in rotation from outside its axis 209b.
  • the second differential input is thus pivoted directly on the support 64.
  • the planet carrier 208 is provided with a central opening, inside which is fixed an outer ring 232 of the bearing 214.
  • An inner ring 234 is disposed in a groove defined by the support 64 and a collar 236 The planet carrier 208 is thus pivoted directly on the support 64.
  • the bearing 214 is slightly raised relative to the bottom of the cavity of the support 64, so that the planet carrier 208 does not rub on it.
  • One of the wheels carried by one of the shafts is kinematically connected to the power source.
  • it is a pinion 178a located at the distal end of the rod 158a of the second pivoting system which is engaged with the finishing gear train and which thus makes it possible to bring the torque of the power source to one of the inputs (in this case to the first board 202a) of the differential 200.
  • the other input of the differential 200 does not receive the torque from the power source. Since, as mentioned above, the differential 200 averages the rotations received at these inputs and the rotations due to the movement of the carrier 64 cancel each other out, the output of the differential 200, i.e. the planet carrier 208 therefore transmits only one rotation induced by the torque supplied by the energy source.
  • the planet carrier 208 is kinematically connected to the escapement, as can be seen particularly on the figure 4 by means of a rod 240 provided on the one hand with an escape gear 242 meshing with the planet carrier 208 and receiving, on the other hand, the escape wheel 244.
  • the rod 240 passes through the support 64, so that the regulating member 246 and the anchor 248 are located on the upper side of the bridge and are located at the periphery of the cage so as to be visible by a user.
  • the exhaust is of angle type, that is to say that the axes of the regulating member 246, the anchor and the escape wheel, are not aligned. This allows to bring the axis of the regulating member and that of the escape wheel.
  • the shaft 154b that is to say the shaft of the second pivot system opposite to that which is connected to the energy source, comprises a locking system with reference to the frame.
  • a square or a blocker 250 can be fixed on the rod, itself being locked in rotation in the frame. The rotations of the support 64 are well transmitted to the differential.
  • the support 64 can be advantageously ballasted. It defines an unbalance located at a lower level relative to the axes of the pivoting systems, participating in the orientation of the support 64 and the cage 50. Note that the system more generally allows to maintain a constant orientation of the exhaust, regardless of the position of the frame, this orientation may not be horizontal.
  • the timepiece that has just been described allows, compared to the state of the art, an optimization of the construction. Not only, the different rotational movements related to the movements of the support 64, are canceled without resorting to an inverter system, but, in addition, the construction is simplified and improved, to reduce the dimensioning of the cage 50. This is due to the combination of several parameters.
  • the arrangement of the differential 200 along an axis parallel to the axes of the mobiles of the exhaust makes it possible to reduce the diameter of the cage 50. Indeed, it will be possible to see on the figure 1 , that the axis of the differential was previously perpendicular to the axes of the mobiles of the exhaust.
  • the use of an angled escapement also has a positive effect.
  • This arrangement is made possible by the fact that the bridge has a working surface whose size and the free space makes it possible to position in a relatively simple manner the scores of the elements of the assortment.
  • the construction of the cage 50 and its pivoting means is also a factor of improvement. Indeed, the pivoting along the two axes AA and BB are done by means of a single cage 50.
  • the first pivoting system 52 serves as an interface between the cage 50 and the support 64. It is arranged on the side of the Inside the cage 50.
  • the second pivoting system serves as an interface between the cage 50 and the frame. It is disposed on the outside of the cage 50.
  • the cage 50 thus comprises two pairs of openings 72a, 72b and 172a, 172b, each pair being located respectively on one of the axes A-A and B-B.
  • the openings 72a, 72b are integral with the outer rings 70a, 70b of the bearings, while for the axis B-B, the openings 172a, 172b are integral with the inner rings 168a, 168b of the bearings.
  • the figure 5 proposes a variant of a timepiece according to the invention.
  • identical or similar elements have the same reference numbers.
  • the wheels 76a and 76b respectively carried by the shaft 54a and by the shaft 54b of the first pivoting system, are respectively connected to a first input and a second input of a differential 200, in a manner identical to that described above.
  • the wheel 76a forms a first kinematic chain with a first wheel 176a carried by a first shaft 154a of the second pivot system 152.
  • the wheel 176a is connected to the source of energy, as will be detailed below.
  • the wheel 76b forms a second kinematic chain with a second wheel 176b, in this case, coaxial with the first shaft 154a of the second pivot system 152.
  • the wheel 176b is fixed with reference to the frame.
  • the two wheels 176a and 176b are arranged coaxially on the first shaft 154a but are rotatably mounted relative to one another and relative to the cage 50, the wheel 176b being fixed with reference to the frame.
  • the second shaft 154b is a simple pivoting system of the cage 50 with reference to the frame.
  • the wheels 176a and 176b are disposed on either side of the wall of the cage 50.
  • the wheel 176a meshes with a reference 80a, in taken with the wheel 76a, while the wheel 176b meshes with a reference 80b, engaged with the wheel 76b.
  • the cage 50 is arranged so as to leave free the moving gear of the kinematic chains. This makes this variant a little less compact than the first.
  • the wheels 176a and 176b have different dimensions.
  • the drive ratios of the wheels 76a and 76b carried by the two shafts of the first pivoting system 52 are identical.
  • the wheels 76a, 76b and 176a, 176b of the first pivot system 52 and the second pivot system 152 and the references 80a, 80b have the same number of teeth.
  • the wheels 76a and 76b are not driven at the same speed, by adapting the gear ratios at the differential level, that is to say by having gear ratios. different gearing between the first input and the output, on the one hand, and between the second input and the output on the other hand, so that the movements of the cage are well compensated by the differential.

Description

Domaine techniqueTechnical area

La présente invention se rapporte au domaine de l'horlogerie mécanique. Elle concerne, plus particulièrement, une pièce d'horlogerie comportant un système de correction d'assiette de l'échappement, visant à réduire l'influence des variations d'orientation de ladite pièce d'horlogerie, sur sa marche. Elle comprend un bâti portant une source d'énergie, une cage comprenant un premier système de pivotement autour d'un premier axe, au moyen duquel un support est monté pivotant à l'intérieur de ladite cage, le premier système de pivotement comprenant deux arbres coaxiaux. Un échappement est en outre agencé sur le support.The present invention relates to the field of mechanical watchmaking. It relates, more particularly, to a timepiece comprising an exhaust trim correction system, to reduce the influence of the variations of orientation of said timepiece, on its march. It comprises a frame carrying an energy source, a cage comprising a first pivoting system about a first axis, by means of which a support is pivotally mounted inside said cage, the first pivoting system comprising two shafts. coaxial. An exhaust is further arranged on the support.

La cage comporte un deuxième système de pivotement autour d'un deuxième axe sensiblement perpendiculaire au premier, au moyen duquel la cage est montée pivotante en référence au bâti. Le deuxième système de pivotement comprend deux arbres, coaxiaux. Un arbre du premier système de pivotement porte une roue formant une première chaine cinématique avec une roue portée par un arbre du deuxième système de pivotement.The cage comprises a second pivoting system about a second axis substantially perpendicular to the first, by means of which the cage is pivotally mounted with reference to the frame. The second pivoting system comprises two shafts, coaxial. A shaft of the first pivoting system carries a wheel forming a first kinematic chain with a wheel carried by a shaft of the second pivoting system.

Etat de la techniqueState of the art

Une pièce d'horlogerie telle que mentionnée ci-dessus est notamment connue par la demande WO2009/026735 . Un mode de réalisation est proposé à la figure 1. Plus précisément, ce document divulgue une pièce d'horlogerie comprenant au moins deux supports articulés, un premier 10 étant articulé en référence au bâti selon un premier axe, le deuxième 12 étant articulé en référence au premier support selon un deuxième axe orthogonal au premier. L'échappement 14 est monté sur le deuxième support et, grâce à l'articulation, peut conserver une orientation sensiblement stable, de préférence sensiblement horizontale, indépendamment de la position du bâti. Par orientation horizontale, on définit que les plans des mobiles sont horizontaux, les axes de ces mobiles sont verticaux.A timepiece as mentioned above is known in particular by the application WO2009 / 026735 . An embodiment is proposed at figure 1 . More specifically, this document discloses a timepiece comprising at least two articulated supports, a first 10 being articulated with reference to the frame along a first axis, the second 12 being articulated with reference to the first support along a second axis orthogonal to the first. The exhaust 14 is mounted on the second support and, thanks to the joint, can maintain a substantially stable orientation, preferably substantially horizontal, regardless of the position of the frame. By horizontal orientation, it is defined that the planes of the mobiles are horizontal, the axes of these mobiles are vertical.

La pièce d'horlogerie comprend un premier train d'engrenages de transmission 16, relié cinématiquement à une source d'énergie et amenant cette énergie à l'échappement 14, et un deuxième train d'engrenages de référence 18, relié à élément fixe du bâti. Les deux trains d'engrenages sont agencés en parallèle, de sorte que toute rotation entre les supports et le bâti ou entre les supports eux-mêmes, se traduit par une rotation identique des trains d'engrenages de transmission et de référence.The timepiece comprises a first gear transmission gear 16, kinematically connected to a power source and bringing this energy to the exhaust 14, and a second reference gear train 18, connected to a fixed element of the frame. The two gear trains are arranged in parallel, so that any rotation between the supports and the frame or between the supports themselves, results in identical rotation of the gear trains and reference transmission.

La pièce d'horlogerie comprend encore un système d'inverseur 20 permettant de faire que, les derniers mobiles des trains d'engrenages de transmission et de référence tournent dans des sens opposés. Enfin, un dispositif de correction différentiel 22 permet d'annuler tous les mouvements des supports pour n'amener à l'échappement que l'énergie issue de la source d'énergie. En effet, le train d'engrenages de transmission 16 amène à une première entrée du dispositif de correction différentiel, un mouvement correspondant à la rotation des supports (R) et à la rotation induite par le couple de la source d'énergie (E). Le train d'engrenages de référence 18 transmet également un mouvement correspondant à la rotation des supports (R), au système d'inverseur 20, ce dernier transmettant donc un mouvement inverse (-R) à une deuxième entrée du dispositif de correction différentiel. Ce dernier est agencé de manière à effectuer la moyenne algébrique de la première entrée et de la deuxième entrée (soit (R-R+E)/2), de sorte que, à sa sortie, ne reste qu'une rotation induite par le couple de la source d'énergie.The timepiece further comprises an inverter system 20 making it possible for the last mobiles of the transmission and reference gear trains to rotate in opposite directions. Finally, a differential correction device 22 makes it possible to cancel all the movements of the supports in order to bring to the exhaust only the energy coming from the energy source. Indeed, the transmission gear train 16 brings to a first input of the differential correction device, a movement corresponding to the rotation of the supports (R) and to the rotation induced by the torque of the energy source (E). . The reference gear train 18 also transmits a movement corresponding to the rotation of the supports (R), to the inverter system 20, the latter thus transmitting an inverse movement (-R) to a second input of the differential correction device. The latter is arranged so as to perform the algebraic mean of the first input and the second input (ie (R-R + E) / 2), so that, at its output, only a rotation induced by the couple of the energy source.

Ainsi, les supports portent les deux trains d'engrenages, respectivement de transmission 16 et de référence 18, un système d'inverseur 20 et un dispositif de correction différentiel 22, en plus du système d'échappement. La présente invention a pour but de réduire le nombre de pièces portées par les supports et de réduire le volume occupé par ces derniers.Thus, the supports carry the two gear trains, respectively transmission 16 and reference 18, an inverter system 20 and a differential correction device 22, in addition to the exhaust system. The present invention aims to reduce the number of parts carried by the media and reduce the volume occupied by the latter.

Divulgation de l'inventionDisclosure of the invention

De façon plus précise, l'invention concerne une pièce d'horlogerie telle que définie à la revendication 1, comportant :

  • un bâti portant une source d'énergie,
  • une cage comprenant :
    • un premier système de pivotement autour d'un premier axe, au moyen duquel un support est monté pivotant à l'intérieur de la cage, le premier système de pivotement comprenant des premier et second arbres coaxiaux, et
    • un deuxième système de pivotement autour d'un deuxième axe sensiblement perpendiculaire au premier, au moyen duquel la cage est montée pivotante en référence au bâti, le deuxième système de pivotement comprenant des premier et second arbres coaxiaux,
  • un échappement agencé sur ledit support et dont les mobiles sont agencés mobiles en rotation autour d'un axe commun,
  • une première chaine cinématique comprenant :
    • une première roue portée par le premier arbre du premier système de pivotement,
    • une seconde roue portée par le premier arbre du second système de pivotement, et
  • une seconde chaine cinématique comprenant :
    • une première roue portée par le second arbre du premier système de pivotement,
    • une seconde roue portée par le premier ou le second arbre du second système de pivotement.
More specifically, the invention relates to a timepiece as defined in claim 1, comprising:
  • a frame carrying a source of energy,
  • a cage comprising:
    • a first pivoting system about a first axis, by means of which a support is pivotally mounted within the cage, the first pivoting system comprising first and second coaxial shafts, and
    • a second pivoting system about a second axis substantially perpendicular to the first, by means of which the cage is pivotally mounted with reference to the frame, the second pivoting system comprising first and second coaxial shafts,
  • an escapement arranged on said support and whose mobiles are arranged mobile in rotation around a common axis,
  • a first kinematic chain comprising:
    • a first wheel carried by the first shaft of the first pivoting system,
    • a second wheel carried by the first shaft of the second pivoting system, and
  • a second kinematic chain comprising:
    • a first wheel carried by the second shaft of the first pivoting system,
    • a second wheel carried by the first or second shaft of the second pivoting system.

Dans la pièce d'horlogerie selon l'invention, une des roues portée par le second système de pivotement est reliée cinématiquement à la source d'énergie, et l'autre roue portée par ce système de pivotement est fixe par rapport au bâti. De plus, les deux roues portées par le premier système de pivotement sont reliées cinématiquement avec un mobile d'entrée d'un différentiel agencé pour transmettre par un mobile de sortie la moyenne des rotations reçues à ses entrées, ledit mobile de sortie étant relié cinématiquement à l'échappement et les mobiles d'entrée et de sortie du différentiel étant disposés mobiles autour d'un axe de rotation parallèle à l'axe de rotation des mobiles d'échappement.In the timepiece according to the invention, one of the wheels carried by the second pivoting system is kinematically connected to the power source, and the other wheel carried by the pivoting system is fixed relative to the frame. In addition, the two wheels carried by the first pivoting system are connected kinematically with an input mobile of a differential arranged to transmit by an output mobile the average of the rotations received at its inputs, said output mobile being kinematically connected. at the exhaust and the mobile input and output of the differential being movable about an axis of rotation parallel to the axis of rotation of the exhaust mobiles.

Brève description des dessinsBrief description of the drawings

D'autres détails de l'invention apparaîtront plus clairement à la lecture de la description qui suit, faite en référence aux figures suivantes :

  • la figure 1 illustre une pièce d'horlogerie selon l'état de la technique,
  • la figure 2 représente une vue en trois dimensions d'une pièce d'horlogerie selon l'invention,
  • les figures 3 et 4 sont des vues en coupe selon les deux axes des systèmes de rotation, d'une pièce d'horlogerie selon l'invention, et
  • la figure 5 propose une vue en trois dimension d'une variante de l'invention.
Other details of the invention will appear more clearly on reading the description which follows, made with reference to the following figures:
  • the figure 1 illustrates a timepiece according to the state of the art,
  • the figure 2 represents a three-dimensional view of a timepiece according to the invention,
  • the figures 3 and 4 are views in section along the two axes of the rotation systems of a timepiece according to the invention, and
  • the figure 5 proposes a three-dimensional view of a variant of the invention.

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

On n'a représenté sur les figures que les éléments qui se rapportent à l'invention. L'homme du métier saura adapter l'enseignement technique fourni par la présente description à un mouvement horloger comportant un bâti, une source d'énergie et un rouage de finissage et une minuterie pour, respectivement, amener l'énergie à un échappement et afficher une information horaire.Only the elements which relate to the invention are shown in the figures. Those skilled in the art will be able to adapt the technical teaching provided by the present description to a watch movement comprising a frame, a source of energy and a finishing gear and a timer for, respectively, bringing the energy to an escapement and displaying hourly information.

On peut donc voir, sur les figures, une cage 50 qui est avantageusement définie par une armature sensiblement annulaire afin de limiter le volume qu'elle occupe dans ses mouvements, comme on le verra par la suite.We can see in the figures, a cage 50 which is advantageously defined by a substantially annular reinforcement to limit the volume it occupies in its movements, as will be seen later.

Cette cage 50 comprend un premier système de pivotement 52 autour d'un premier axe A-A, plus particulièrement visible sur la figure 3. Ce premier système de pivotement 52 comprend deux arbres 54a et 54b, disposés coaxialement selon l'axe A-A. Le terme de arbre n'est pas limitatif et doit s'entendre dans un sens fonctionnel, c'est-à-dire qu'on pourrait envisager une construction dans laquelle les arbres sont définis par deux parties d'un arbre, sur lequel pivotent les éléments qui vont maintenant être décrits.This cage 50 comprises a first pivoting system 52 around a first axis AA, more particularly visible on the figure 3 . This first pivoting system 52 comprises two shafts 54a and 54b, arranged coaxially along the axis AA. The term tree is not limiting and must be understood in a functional sense, that is to say that one could envisage a construction in which the trees are defined by two parts of a tree, on which pivot the elements that will now be described.

Ci-après, un indice a se rapporte à un élément du arbre 54a et un indice b se rapporte à un élément du arbre 54b. Chaque arbre 54a et 54b comprend une tige 58a et 58b pivotant sur deux paliers 60a et 60b disposés aux extrémités d'un tube 62a et 62b. Ces derniers sont fixés sur un support 64 qui sera décrit plus en détails ci-après. Chaque tube 62a ou 62b reçoit, sur son pourtour extérieur, un roulement, par exemple à billes, dont une bague intérieure 68a, 68b est fixée sur le tube 62a, 62b et dont la bague extérieure 70a, 70b est disposée dans une ouverture 72a, 72b de la cage 50. Une rondelle 74a, 74b ferme le roulement. Ce premier système de pivotement 52 permet de faire pivoter le support 64 à l'intérieur de la cage 50.Hereinafter, an index a refers to an element of the shaft 54a and an index b refers to an element of the shaft 54b. Each shaft 54a and 54b comprises a rod 58a and 58b pivoting on two bearings 60a and 60b disposed at the ends of a tube 62a and 62b. These are fixed on a support 64 which will be described in more detail below. Each tube 62a or 62b receives, on its outer periphery, a bearing, for example ball, of which an inner ring 68a, 68b is fixed on the tube 62a, 62b and whose outer ring 70a, 70b is disposed in an opening 72a, 72b of the cage 50. A washer 74a, 74b closes the bearing. This first pivoting system 52 makes it possible to pivot the support 64 inside the cage 50.

En outre, chaque tige 58a, 58b reçoit, à une extrémité distale en référence au centre de la cage 50, une roue 76a, 76b, et à une deuxième extrémité proximale en référence au centre de la cage 50, un pignon 78a, 78b.In addition, each rod 58a, 58b receives, at a distal end with reference to the center of the cage 50, a wheel 76a, 76b, and at a second proximal end with reference to the center of the cage 50, a pinion 78a, 78b.

Comme le montre plus particulièrement la figure 4, la cage 50 comporte également un deuxième système de pivotement 152 autour d'un deuxième axe B-B, sensiblement perpendiculaire au premier axe A-A. Ce deuxième système de pivotement comprend deux arbres 154a et 154b, disposés coaxialement selon l'axe B-B. La construction des arbres du deuxième système de pivotement est similaire à celle décrite ci-dessus. Les éléments du deuxième système de pivotement sont désignés par des numéros de référence reprenant les numéros de référence du premier système de pivotement, précédés d'un 1.As shown more particularly in figure 4 , the cage 50 also comprises a second pivoting system 152 around a second axis BB, substantially perpendicular to the first axis AA. This second pivoting system comprises two shafts 154a and 154b, arranged coaxially along the axis BB. The construction of the shafts of the second pivot system is similar to that described above. The elements of the second pivot system are designated by reference numbers showing the reference numbers of the first pivot system, preceded by a 1.

Chaque arbre 154a, 154b comprend une tige 158a, 158b pivotant sur deux paliers 160a, 160b disposés aux extrémités d'un tube 162a, 162b, fixé dans une ouverture 172a, 172b de la cage 50. Chaque tube 162a, 162b reçoit, sur son pourtour extérieur, un roulement, par exemple à billes, dont une bague intérieure 168a, 168b, est fixée sur le tube 162a, 162b, et dont la bague extérieure 170a, 170b est disposée dans un logement du bâti, non représenté. Une rondelle 174a, 174b ferme le roulement. Ce deuxième système de pivotement permet de faire pivoter la cage 50 en référence au bâti.Each shaft 154a, 154b comprises a rod 158a, 158b pivoting on two bearings 160a, 160b disposed at the ends of a tube 162a, 162b, fixed in an opening 172a, 172b of the cage 50. Each tube 162a, 162b receives, on its outside circumference, a bearing, for example balls, including an inner ring 168a, 168b, is fixed on the tube 162a, 162b, and the outer ring 170a, 170b is disposed in a housing of the frame, not shown. A washer 174a, 174b closes the bearing. This second pivoting system makes it possible to rotate the cage 50 with reference to the frame.

En outre, chaque tige 158a, 158b reçoit, à une extrémité proximale en référence au centre de la cage 50, une roue 176a, 176b. Nous reviendrons plus loin sur l'extrémité distale des tiges 158a et 158b.In addition, each rod 158a, 158b receives, at a proximal end with reference to the center of the cage 50, a wheel 176a, 176b. We will return later to the distal end of rods 158a and 158b.

Chaque roue 76a, 76b du premier système de pivotement 52 forme une chaine cinématique avec une roue 176a, 176b du deuxième système de pivotement. On a ainsi une première chaine cinématique entre les roues 76a et 176a de deux arbres 54a et 154a, respectivement des premier et deuxième systèmes de pivotement, et une deuxième chaine cinématique entre les autres roues 76b et 176b des deux autres arbres 54b et 154b.Each wheel 76a, 76b of the first pivot system 52 forms a kinematic chain with a wheel 176a, 176b of the second transmission system. pivoting. There is thus a first kinematic chain between the wheels 76a and 176a of two shafts 54a and 154a, respectively of the first and second pivot systems, and a second kinematic chain between the other wheels 76b and 176b of the two other shafts 54b and 154b.

De manière avantageuse, ces liaisons cinématiques sont réalisées respectivement par un renvoi 80a, 80b monté sur la cage 50. Le renvoi 80a, 80b est disposé sensiblement à 45° en référence aux roues avec lesquelles il engrène. Une telle disposition permet que seul ce renvoi 80a, 80b comporte une denture de type conique, alors que les roues 76a, 176a, respectivement 76b, 176b présentent des dentures droites. Toutes ces roues sont planes. Une telle réalisation est particulièrement intéressante, comparativement à la configuration des engrènements entre les roues des chaines de transmission et de référence de la pièce d'horlogerie de l'état de la technique proposée à la figure 1.Advantageously, these kinematic links are made respectively by a reference 80a, 80b mounted on the cage 50. The reference 80a, 80b is disposed substantially at 45 ° with reference to the wheels with which it meshes. Such an arrangement allows that only this reference 80a, 80b has a conical type toothing, while the wheels 76a, 176a, respectively 76b, 176b have straight teeth. All these wheels are flat. Such an embodiment is particularly interesting, compared to the configuration of the meshing between the wheels of the transmission and reference chains of the timepiece of the state of the art proposed at the time. figure 1 .

De préférence, les rapports d'entraînement de la première chaîne cinématique et de la deuxième chaîne cinématique sont identiques, de manière à ce que les roues 76a et 76b portées par les deux arbres 54a et 54b du premier système de pivotement 52 soient entraînées à la même vitesse par les déplacements du support 64. Dans une configuration avantageuse, les roues 76a, 76b, 176a et 176b des systèmes de pivotement 52a et 52b et les renvois 80a et 80b, comportent le même nombre de dents. Ils sont en outre de même diamètre. De par cette configuration, la roue 76a et le pignon 78a d'un premier arbre 54a du premier système de pivotement 52 font face à ceux 76b et 78b de l'autre arbre 54b de ce système de pivotement. Vu depuis le centre de la cage 50, les pignons 78a et 78b sont ainsi entraînés dans des sens de rotation opposés, à la même vitesse absolue, sans toutefois être liés cinématiquement l'un à l'autre par un train d'engrenage.Preferably, the drive ratios of the first driveline and the second drivetrain are identical, so that the wheels 76a and 76b carried by the two shafts 54a and 54b of the first pivoting system 52 are driven to the same speed by the movements of the support 64. In an advantageous configuration, the wheels 76a, 76b, 176a and 176b of the pivot systems 52a and 52b and the references 80a and 80b, have the same number of teeth. They are also of the same diameter. By this configuration, the wheel 76a and the pinion 78a of a first shaft 54a of the first pivot system 52 face those 76b and 78b of the other shaft 54b of this pivot system. Seen from the center of the cage 50, the pinions 78a and 78b are thus driven in opposite directions of rotation, at the same absolute speed, without however being kinematically connected to each other by a gear train.

Ainsi, les rotations relatives du support 64 selon l'axe A-A en référence à la cage 50 et les rotations relatives de la cage 50 en référence au bâti, selon l'axe B-B, sont toutes transmises aux pignons 78a et 78b, soit directement, soit au travers des chaînes cinématiques.Thus, the relative rotations of the support 64 along the axis AA with reference to the cage 50 and the relative rotations of the cage 50 with reference to the frame, along the axis BB, are all transmitted to the pinions 78a and 78b, either directly, either through kinematic chains.

Chacun de ces pignons 78a et 78b engrène avec une entrée d'un différentiel 200, dont les axes de rotation des mobiles sont parallèles à celui des mobiles de l'échappement. Autrement dit, grâce aux systèmes de pivotement 52 et 152, le différentiel 200 est destiné à avoir une orientation sensiblement constante, typiquement selon un axe sensiblement vertical. Plus particulièrement, le pignon 78a engrène avec une première planche 202a munie d'une denture en chant. Cette première planche 202a est solidaire d'une première roue solaire 204a engrenant avec un premier satellite 206a monté pivotant sur un porte-satellites 208. Ce dernier est coaxial à la première roue solaire 204a et est susceptible de pivoter en référence aux autres éléments du différentiel. Le porte-satellites 208 est doté d'une denture et définit la sortie du différentiel.Each of these pinions 78a and 78b meshes with an input of a differential 200, the axes of rotation of the mobiles are parallel to that of the mobiles of the exhaust. In other words, thanks to the pivot systems 52 and 152, the differential 200 is intended to have a substantially constant orientation, typically along a substantially vertical axis. More particularly, the pinion 78a meshes with a first board 202a provided with teeth to edge. This first plate 202a is integral with a first sun gear 204a meshing with a first satellite 206a pivotally mounted on a planet carrier 208. The latter is coaxial with the first sun gear 204a and is pivotable with reference to the other elements of the differential . The planet carrier 208 is provided with a toothing and defines the output of the differential.

Parallèlement, le pignon 78b engrène avec une deuxième planche 202b munie d'une denture en chant. Cette deuxième planche 202b est solidaire d'une deuxième roue solaire 204b engrenant avec un deuxième satellite 206b monté pivotant sur le porte-satellites 208. Le deuxième satellite 206b est également agencé pour engrener avec le premier satellite 206a.Meanwhile, the pinion 78b meshes with a second board 202b provided with teeth to sing. This second plate 202b is integral with a second sun gear 204b meshing with a second satellite 206b pivotally mounted on the planet carrier 208. The second satellite 206b is also arranged to mesh with the first satellite 206a.

Une telle configuration de différentiel 200 permet à la roue de sortie, c'est-à-dire au porte-satellites 208, de transmettre la moyenne des rotations reçues à ses entrées. Vu les sens de rotation des pignons 78a et 78b expliqués ci-dessus, la première planche 202a et la deuxième planche 202b tournent dans des sens différents. Les rapports entre les pignons 78a, 78b et les planches 202a et 202b sont calculés pour que les planches tournent à la même vitesse absolue. Ainsi, à la sortie du différentiel 200, les rotations dues aux mouvements du support 64 s'annulent, sans avoir recours à un inverseur spécifique, la construction proposée selon l'invention produisant directement deux rotations opposées aux entrées du différentiel 200.Such a differential configuration 200 allows the output wheel, that is to say the planet carrier 208, to transmit the average of the rotations received at its inputs. Given the directions of rotation of the gears 78a and 78b explained above, the first board 202a and the second board 202b rotate in different directions. The ratios between the pinions 78a, 78b and the boards 202a and 202b are calculated so that the boards rotate at the same absolute speed. Thus, at the output of the differential 200, the rotations due to the movements of the support 64 cancel each other out, without resorting to a specific inverter, the construction proposed according to the invention directly producing two opposite rotations to the inputs of the differential 200.

On pourra relever que la configuration proposée permet une grande compacité du différentiel. Grâce à sa configuration, il peut être aisément logé dans une cavité du support 64. Ces gains de place offrent la possibilité d'améliorer les pivotements des éléments du différentiel 200. En effet, si la première planche 202a dont l'axe correspondant est situé au centre du différentiel, pivote sur des paliers 210, la deuxième planche 202b et le porte-satellites 208 sont pivotés sur des roulements, respectivement 212 et 214, par exemple à billes, fixés dans des ouvertures ad-hoc du support 64.It can be noted that the proposed configuration allows a great compactness of the differential. Due to its configuration, it can be easily accommodated in a cavity of the support 64. These space savings offer the possibility of improving the pivoting of the elements of the differential 200. In fact, if the first board 202a whose corresponding axis is located in the center of differential, pivots on bearings 210, the second board 202b and the planet carrier 208 are pivoted on bearings, respectively 212 and 214, for example balls, fixed in ad-hoc openings of the support 64.

L'axe 209a de la première planche 202a est ainsi monté pivotant entre deux paliers 210, typiquement formé par des pierres. L'une est chassée dans un pont 216 porté par le support 64 et l'autre est chassée dans un tube 218, également fixé sur le support 64, typiquement par une vis 220 insérée dans le tube.The axis 209a of the first plate 202a is thus pivotally mounted between two bearings 210, typically formed by stones. One is driven into a bridge 216 carried by the support 64 and the other is driven into a tube 218, also fixed on the support 64, typically by a screw 220 inserted into the tube.

La deuxième planche 202b est solidaire d'un moyeu 222, comprenant une ouverture centrale, traversée par l'axe 209b de la deuxième planche. L'axe 209b de la deuxième planche est ajusté dans cette ouverture centrale et est traversé librement par l'axe 209a de la première planche. L'axe 209b de la deuxième planche présente une collerette 224 qui définit une gorge avec un flanc du moyeu 222. Une bague intérieure 226 du roulement à billes 212 est ajustée dans la gorge, tandis qu'une bague extérieure 228 de ce roulement est fixée sur un pont supplémentaire 230 du support 64. La deuxième planche 202b est ainsi guidée en rotation depuis l'extérieur de son axe 209b. La deuxième entrée du différentiel est ainsi pivotée directement sur le support 64.The second board 202b is secured to a hub 222, comprising a central opening, through which the axis 209b of the second board. The axis 209b of the second board is fitted in this central opening and is freely traversed by the axis 209a of the first board. The axis 209b of the second board has a flange 224 which defines a groove with a flank of the hub 222. An inner ring 226 of the ball bearing 212 is fitted in the groove, while an outer ring 228 of this bearing is fixed. on an additional bridge 230 of the support 64. The second board 202b is thus guided in rotation from outside its axis 209b. The second differential input is thus pivoted directly on the support 64.

Par ailleurs, le porte-satellites 208 est doté d'une ouverture centrale, à l'intérieur de laquelle est fixée une bague externe 232 du roulement 214. Une bague interne 234 est disposée dans une gorge définie par le support 64 et une collerette 236 que comporte le tube 218. Le porte-satellites 208 est ainsi pivoté directement sur le support 64. Le roulement 214 est légèrement surélevé par rapport au fond de la cavité du support 64, afin que le porte-satellites 208 ne frotte pas sur lui. Une telle construction du différentiel permet d'améliorer les conditions de travail des différents éléments. Le rendement obtenu est très bon.Furthermore, the planet carrier 208 is provided with a central opening, inside which is fixed an outer ring 232 of the bearing 214. An inner ring 234 is disposed in a groove defined by the support 64 and a collar 236 The planet carrier 208 is thus pivoted directly on the support 64. The bearing 214 is slightly raised relative to the bottom of the cavity of the support 64, so that the planet carrier 208 does not rub on it. Such a construction of the differential makes it possible to improve the working conditions of the various elements. The yield obtained is very good.

L'une des roues portées par l'un des arbres est reliée cinématiquement à la source d'énergie. Dans l'exemple proposé, c'est un pignon 178a situé à l'extrémité distale de la tige 158a du deuxième système de pivotement qui est en prise avec le rouage de finissage et qui permet donc d'amener le couple de la source d'énergie à l'une des entrées (en l'occurrence à la première planche 202a) du différentiel 200. L'autre entrée du différentiel 200 ne reçoit pas le couple venant de la source d'énergie. Etant donné que, comme mentionné ci-dessus, le différentiel 200 fait la moyenne des rotations reçues à ces entrées et que les rotations dues au mouvement du support 64 s'annulent, la sortie du différentiel 200, c'est-à-dire le porte-satellites 208 ne transmet donc qu'une rotation induite par le couple fourni par la source d'énergie.One of the wheels carried by one of the shafts is kinematically connected to the power source. In the proposed example, it is a pinion 178a located at the distal end of the rod 158a of the second pivoting system which is engaged with the finishing gear train and which thus makes it possible to bring the torque of the power source to one of the inputs (in this case to the first board 202a) of the differential 200. The other input of the differential 200 does not receive the torque from the power source. Since, as mentioned above, the differential 200 averages the rotations received at these inputs and the rotations due to the movement of the carrier 64 cancel each other out, the output of the differential 200, i.e. the planet carrier 208 therefore transmits only one rotation induced by the torque supplied by the energy source.

Le porte-satellites 208 est relié cinématiquement à l'échappement, comme on peut particulièrement le voir sur la figure 4, au moyen d'une tige 240, munie d'une part d'un pignon d'échappement 242 engrenant avec le porte-satellites 208 et recevant, d'autre part, la roue d'échappement 244. La tige 240 traverse le support 64, de sorte que l'organe réglant 246 et l'ancre 248 sont situés du côté supérieur, du pont et sont situés à la périphérie de la cage de manière à être visibles par un utilisateur. Pour améliorer la compacité du système, l'échappement est de type à angle, c'est-à-dire que les axes de l'organe réglant 246, de l'ancre et de la roue d'échappement, ne sont pas alignés. Cela permet de rapprocher l'axe de l'organe réglant et celui de la roue d'échappement.The planet carrier 208 is kinematically connected to the escapement, as can be seen particularly on the figure 4 by means of a rod 240 provided on the one hand with an escape gear 242 meshing with the planet carrier 208 and receiving, on the other hand, the escape wheel 244. The rod 240 passes through the support 64, so that the regulating member 246 and the anchor 248 are located on the upper side of the bridge and are located at the periphery of the cage so as to be visible by a user. To improve the compactness of the system, the exhaust is of angle type, that is to say that the axes of the regulating member 246, the anchor and the escape wheel, are not aligned. This allows to bring the axis of the regulating member and that of the escape wheel.

On pourra encore relever que le arbre 154b, c'est-à-dire le arbre du deuxième système de pivotement opposé à celui qui est connecté à la source d'énergie, comporte un système de blocage en référence au bâti. Un carré ou un bloqueur 250 peut être fixé sur la tige, lui-même étant bloqué en rotation dans le bâti. Les rotations du support 64 sont ainsi bien transmises au différentiel.It can further be noted that the shaft 154b, that is to say the shaft of the second pivot system opposite to that which is connected to the energy source, comprises a locking system with reference to the frame. A square or a blocker 250 can be fixed on the rod, itself being locked in rotation in the frame. The rotations of the support 64 are well transmitted to the differential.

Pour aider le maintien horizontal de l'échappement, le support 64 peut être avantageusement lesté. Il définit un balourd situé à un niveau inférieur par rapport aux axes des systèmes de pivotement, participant à l'orientation du support 64 et de la cage 50. On notera que le système permet plus généralement de conserver une orientation constante de l'échappement, indépendamment de la position du bâti, cette orientation pouvant ne pas être horizontale.To help the horizontal maintenance of the exhaust, the support 64 can be advantageously ballasted. It defines an unbalance located at a lower level relative to the axes of the pivoting systems, participating in the orientation of the support 64 and the cage 50. Note that the system more generally allows to maintain a constant orientation of the exhaust, regardless of the position of the frame, this orientation may not be horizontal.

Ainsi, la pièce d'horlogerie qui vient d'être décrite permet, par rapport à l'état de la technique, une optimisation de la construction. Non seulement, les différents mouvements de rotation liés aux déplacements du support 64, sont annulés sans avoir recours à un système d'inverseur, mais, en plus, la construction est simplifiée et améliorée, permettant de réduire le dimensionnement de la cage 50. Ceci est notamment dû à la combinaison de plusieurs paramètres.Thus, the timepiece that has just been described allows, compared to the state of the art, an optimization of the construction. Not only, the different rotational movements related to the movements of the support 64, are canceled without resorting to an inverter system, but, in addition, the construction is simplified and improved, to reduce the dimensioning of the cage 50. This is due to the combination of several parameters.

La disposition du différentiel 200 selon un axe parallèle aux axes des mobiles de l'échappement permet de réduire le diamètre de la cage 50. En effet, on pourra constater sur la figure 1, que l'axe du différentiel était préalablement perpendiculaire aux axes des mobiles de l'échappement.The arrangement of the differential 200 along an axis parallel to the axes of the mobiles of the exhaust makes it possible to reduce the diameter of the cage 50. Indeed, it will be possible to see on the figure 1 , that the axis of the differential was previously perpendicular to the axes of the mobiles of the exhaust.

Par ailleurs, le recours à un échappement à angle a également un effet positif. Cette disposition est rendue possible par le fait que le pont présente une surface de travail dont la taille et l'espace libre permet de positionner de manière relativement simple les pointages des éléments de l'assortiment.In addition, the use of an angled escapement also has a positive effect. This arrangement is made possible by the fact that the bridge has a working surface whose size and the free space makes it possible to position in a relatively simple manner the scores of the elements of the assortment.

De plus, la construction de la cage 50 et de ses moyens de pivotement, est également un facteur d'amélioration. En effet, les pivotements selon les deux axes A-A et B-B se font au moyen d'une seule cage 50. Le premier système de pivotement 52 sert d'interface entre la cage 50 et le support 64. Il est disposé du côté de l'intérieur de la cage 50. Le deuxième système de pivotement sert d'interface entre la cage 50 et le bâti. Il est disposé du côté de l'extérieur de la cage 50. La cage 50 comporte donc deux paires d'ouvertures 72a, 72b et 172a, 172b, chaque paire étant respectivement situées sur l'un des axes A-A et B-B. Pour l'axe A-A, les ouvertures 72a, 72b sont solidaires des bagues extérieures 70a, 70b des roulements, tandis que pour l'axe B-B, les ouvertures 172a, 172b sont solidaires des bagues intérieures 168a, 168b des roulements.In addition, the construction of the cage 50 and its pivoting means is also a factor of improvement. Indeed, the pivoting along the two axes AA and BB are done by means of a single cage 50. The first pivoting system 52 serves as an interface between the cage 50 and the support 64. It is arranged on the side of the Inside the cage 50. The second pivoting system serves as an interface between the cage 50 and the frame. It is disposed on the outside of the cage 50. The cage 50 thus comprises two pairs of openings 72a, 72b and 172a, 172b, each pair being located respectively on one of the axes A-A and B-B. For the axis A-A, the openings 72a, 72b are integral with the outer rings 70a, 70b of the bearings, while for the axis B-B, the openings 172a, 172b are integral with the inner rings 168a, 168b of the bearings.

La figure 5 propose une variante d'une pièce d'horlogerie selon l'invention. Pour faciliter la compréhension du lecteur et la comparaison entre les deux variantes, les éléments identiques ou analogues reprennent les mêmes numéros de référence. Les roues 76a et 76b portées respectivement par le arbre 54a et par le arbre 54b du premier système de pivotement, sont respectivement reliées à une première entrée et à une deuxième entrée d'un différentiel 200, de manière identique à ce qui a été décrit ci-dessus.The figure 5 proposes a variant of a timepiece according to the invention. To facilitate the understanding of the reader and the comparison between the two variants, identical or similar elements have the same reference numbers. The wheels 76a and 76b respectively carried by the shaft 54a and by the shaft 54b of the first pivoting system, are respectively connected to a first input and a second input of a differential 200, in a manner identical to that described above.

A l'instar de la première variante, la roue 76a forme une première chaine cinématique avec une première roue 176a portée par un premier arbre 154a du deuxième système de pivotement 152. Dans le mode de réalisation proposé, la roue 176a est reliée à la source d'énergie, comme on le détaillera ci-après.Like the first variant, the wheel 76a forms a first kinematic chain with a first wheel 176a carried by a first shaft 154a of the second pivot system 152. In the proposed embodiment, the wheel 176a is connected to the source of energy, as will be detailed below.

La roue 76b forme une deuxième chaine cinématique avec une deuxième roue 176b, dans ce cas, coaxiale au premier arbre 154a du deuxième système de pivotement 152. Dans le mode de réalisation proposé, la roue 176b est fixe en référence au bâti. Autrement dit, les deux roues 176a et 176b sont disposées coaxialement sur le premier arbre 154a mais sont montées libres en rotation l'une en référence à l'autre et par rapport à la cage 50, la roue 176b étant fixe en référence au bâti.The wheel 76b forms a second kinematic chain with a second wheel 176b, in this case, coaxial with the first shaft 154a of the second pivot system 152. In the proposed embodiment, the wheel 176b is fixed with reference to the frame. In other words, the two wheels 176a and 176b are arranged coaxially on the first shaft 154a but are rotatably mounted relative to one another and relative to the cage 50, the wheel 176b being fixed with reference to the frame.

On retrouve ainsi, sur le premier arbre 154a, un pignon 178a relié cinématiquement à la source d'énergie et solidaire en rotation de la roue 176a. On notera que l'on pourrait inverser les fonctions des roues 176a et 176b et avoir la roue 176b reliée cinématiquement à la source d'énergie et la roue 176a fixe en référence au bâti. Dans ce mode de réalisation, le deuxième arbre 154b est un simple système de pivotement de la cage 50 en référence au bâti.Thus, on the first shaft 154a, there is a pinion 178a kinematically connected to the energy source and integral in rotation with the wheel 176a. Note that one could reverse the functions of the wheels 176a and 176b and have the wheel 176b kinematically connected to the power source and the wheel 176a fixed with reference to the frame. In this embodiment, the second shaft 154b is a simple pivoting system of the cage 50 with reference to the frame.

Dans l'exemple proposé à la figure 5 et de manière non limitative, les roues 176a et 176b sont disposées de part et d'autre de la paroi de la cage 50. Selon une configuration similaire à ce qui été décrit ci-dessus, la roue 176a engrène avec un renvoi 80a, en prise avec la roue 76a, tandis que la roue 176b engrène avec un renvoi 80b, en prise avec la roue 76b. Le cas échéant, la cage 50 est aménagée de manière à laisser libre l'engrenage des mobiles des chaines cinématiques. Cela rend cette variante un peu moins compacte que la première. On relèvera encore que, dans l'exemple proposé, les roues 176a et 176b présentent des dimensions différentes. Toutefois, de préférence, les rapports d'entraînement des roues 76a et 76b portées par les deux arbres du premier système de pivotement 52 sont identiques de manière à ce qu'elles soient entraînées à la même vitesse absolue par les déplacements du support 64. Il est également possible de prévoir que les roues 76a, 76b et 176a, 176b du premier système de pivotement 52 et du deuxième système de pivotement 152 et les renvois 80a, 80b comportent le même nombre de dents.In the example proposed at figure 5 and without limitation, the wheels 176a and 176b are disposed on either side of the wall of the cage 50. In a configuration similar to that described above, the wheel 176a meshes with a reference 80a, in taken with the wheel 76a, while the wheel 176b meshes with a reference 80b, engaged with the wheel 76b. Where appropriate, the cage 50 is arranged so as to leave free the moving gear of the kinematic chains. This makes this variant a little less compact than the first. It will be noted again that, in the proposed example, the wheels 176a and 176b have different dimensions. However, preferably, the drive ratios of the wheels 76a and 76b carried by the two shafts of the first pivoting system 52 are identical. so that they are driven at the same absolute speed by the movements of the support 64. It is also possible to provide that the wheels 76a, 76b and 176a, 176b of the first pivot system 52 and the second pivot system 152 and the references 80a, 80b have the same number of teeth.

Dans les deux variantes ci-dessus, on pourrait prévoir que les roues 76a et 76b ne soient pas entraînées à la même vitesse, en adaptant les rapports d'engrenage au niveau du différentiel, c'est-à-dire en ayant des rapports d'engrenage différents entre la première entrée et la sortie, d'une part, et entre la seconde entrée et la sortie d'autre part, afin que les déplacements de la cage soient bien compensés par le différentiel.In the two variants above, it could be provided that the wheels 76a and 76b are not driven at the same speed, by adapting the gear ratios at the differential level, that is to say by having gear ratios. different gearing between the first input and the output, on the one hand, and between the second input and the output on the other hand, so that the movements of the cage are well compensated by the differential.

Ainsi est proposée une pièce d'horlogerie dont la marche est affranchie de l'influence de ses variations d'orientation, dont la construction est améliorée par rapport à l'état de la technique. On peut encore relever que l'un des avantages du système proposé, est qu'il est auto-équilibré. En effet, tout couple induit par la transmission d'énergie au niveau de la chaine cinématique qui est reliée à la source d'énergie, induit un contre-couple au niveau de l'autre chaine cinématique. Ainsi, si la cage devait être dans une position verticale selon l'axe B-B, dans laquelle le contrepoids ne pourrait équilibrer la cage, l'auto-équilibrage permet d'éviter que la cage se mette à tourner autour de l'axe B-B. La présente description n'a été donnée qu'à titre d'illustration de l'invention. Notamment, pour ce qui concerne les renvois des chaines cinématiques, on pourrait très bien envisager de relier directement les roues 76a et 176a, d'une part, et les roues 76b et 176b, d'autre part, ou au contraire d'augmenter le nombre de renvois.Thus is proposed a timepiece whose march is free from the influence of its orientation variations, whose construction is improved compared to the state of the art. It can still be noted that one of the advantages of the proposed system is that it is self-balancing. Indeed, any torque induced by the transmission of energy at the kinematic chain which is connected to the energy source, induces a counter-torque at the other kinematic chain. Thus, if the cage were to be in a vertical position along the axis B-B, in which the counterweight could not balance the cage, self-balancing prevents the cage from rotating around the axis B-B. The present description has been given by way of illustration of the invention. In particular, as regards the references of the kinematic chains, one could very well consider directly connecting the wheels 76a and 176a, on the one hand, and the wheels 76b and 176b, on the other hand, or on the contrary to increase the number of referrals.

Claims (17)

  1. A timepiece, characterized in that it comprises:
    - a frame supporting an energy source,
    - a carriage (50) comprising a support (64) being pivotably mounted inside said carriage (50) about a first axis of a first pivoting system (52) comprising first and second (54a, 54b) coaxial arbors, said carriage being pivotably mounted in reference to the frame about a second axis substantially perpendicular to the first axis by means of a second pivoting system (152) comprising first and second coaxial arbors (154a, 154b),
    - an escapement arranged on said support (64) and comprising wheels (242, 244) rotatably arranged about a common axis,
    wherein, a first wheel (76a) supported by the first arbor (54a) of the first pivoting system forms a first gear train with a second wheel supported by the first arbor (154a) of the second pivoting system (152), and a first wheel (76b) supported by the second arbor (54b) of the first pivoting system forms a second gear train with a second wheel (176b) supported by the first (154a) or the second (154b) arbor of the second pivoting system (152), and
    wherein:
    - one of the wheels (176a, 176b) supported by the second pivoting system is kinematically connected to the energy source, and the other wheel supported by that pivoting system is stationary relative to the frame,
    - and both wheels supported by the first pivoting system are kinematically connected with an input wheel (202a, 202b) of a differential gear (200) arranged to transmit, at an output wheel (208), the average of the rotations received at its inputs, said output wheel (208) being kinematically connected to the escapement,
    - the input and output wheels of the differential gear (200) being pivotably arranged about an axis of rotation that is parallel to the axis of rotation of the escapement wheels.
  2. Timepiece according to claim 1, characterized in that the drive ratios of the first gear train and the second gear train are identical.
  3. Timepiece according to claim 1 et 2, characterized in that the second wheel (176b) of the second gear train is supported by the second arbor (154b) of the second pivoting system (152).
  4. Timepiece according to claim 1 et 2, characterized in that the second wheel (176b) of the second gear train is supported by the first arbor (154a) of the second pivoting system (152).
  5. Timepiece according to one of the preceding claims, characterized in that the arbors (54a, 54b) of the first pivoting system (52) further comprise a pinion (78a, 78b) engaged with an input of the differential.
  6. Timepiece to one of the preceding claims, characterized in that one of the wheels (176a, 176b) of the second pivoting system is kinematically connected to the energy source.
  7. Timepiece according to claim 6, characterized in that the wheel of the second pivoting system that is not kinematically connected to the energy source comprises a blocking system (50) in reference to the frame.
  8. Timepiece according to any of claims 5 to 7, characterized in that said input wheel of the differential gear comprises a first input (202a) and a second input (202b) of the differential gear respectively secured to a first sun wheel (204a) and a second sun wheel (204b), respectively meshing with a first satellite (206a) and with a second satellite (206b), said satellites being pivotably mounted on a satellites carrier (208) and meshing with each other, said satellites carrier (208) being coaxial with said sun wheels and defining the output of the differential.
  9. Timepiece according to claim 8, characterized in that the satellites carrier (208) is kinematically connected to the escapement, using a shaft (240), provided on the one hand with an escapement pinion (242) kinematically connected with the satellites carrier (208), and on the other hand receiving the escapement wheel (244).
  10. Timepiece according to claim 9, characterized in that said shaft crosses through the support (64), such that a regulating organ (246) and pallets (248) of the escapement are positioned at the periphery of the carriage.
  11. Timepiece according to one of the preceding claims, characterized in that the first gear train and the second gear train further include an intermediate wheel (80a, 80b) mounted on the carriage (50), said intermediate wheel being positioned substantially at 45° relative to the wheels (76a, 76b and 176a, 176b) of the first pivoting system (52) and the second pivoting system (152), respectively.
  12. Timepiece according to claim 11, characterized in that said intermediate wheel (80a, 80b) comprises a conical-type toothing, the wheels (76a, 76b and 176a, 176b) of the first pivoting system (52) and the second pivoting system, respectively, having straight teeth.
  13. Timepiece according to one of claims 9 and 10, characterized in that the wheels (76a, 76b and 176a, 176b) of the first pivoting system (52) and the second pivoting system (152) and the intermediate wheels (80a, 80b) include the same number of teeth.
  14. Timepiece according to one of the preceding claims, characterized in that one of the inputs of the differential gear (200) and the satellites carrier (208) are pivoted directly on the support (64).
  15. Timepiece according to one of the preceding claims, characterized in that the escapement is an angle escapement.
  16. Timepiece according to one of the preceding claims, characterized in that the first pivoting system (52) and the second pivoting system (152) cooperate with a single carriage (50).
  17. Timepiece according to one of the preceding claims, characterized in that it is arranged such that any torque induced by the transmission of energy at a gear train that is connected to the energy source induces a counter-torque at the other gear train.
EP12794960.0A 2011-12-02 2012-11-30 Timepiece part Active EP2786214B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH01918/11A CH705836B1 (en) 2011-12-02 2011-12-02 Timepiece.
CH00624/12A CH705831B1 (en) 2011-12-02 2012-05-04 Timepiece.
PCT/EP2012/074082 WO2013079657A1 (en) 2011-12-02 2012-11-30 Timepiece part

Publications (2)

Publication Number Publication Date
EP2786214A1 EP2786214A1 (en) 2014-10-08
EP2786214B1 true EP2786214B1 (en) 2019-07-03

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EP12794960.0A Active EP2786214B1 (en) 2011-12-02 2012-11-30 Timepiece part

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US (1) US9645550B2 (en)
EP (1) EP2786214B1 (en)
JP (1) JP6246728B2 (en)
CN (1) CN103959180B (en)
CH (2) CH705836B1 (en)
HK (1) HK1201948A1 (en)
WO (1) WO2013079657A1 (en)

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EP4177677A1 (en) * 2016-06-13 2023-05-10 Rolex Sa Clock axis
USD864781S1 (en) * 2017-03-17 2019-10-29 Lvmh Swiss Manufactures Sa Watch movement
USD847665S1 (en) * 2017-03-17 2019-05-07 Lvmh Swiss Manufactures Sa Watch movement in a watch case
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Also Published As

Publication number Publication date
CH705831B1 (en) 2016-10-31
WO2013079657A1 (en) 2013-06-06
CN103959180B (en) 2017-04-12
CN103959180A (en) 2014-07-30
HK1201948A1 (en) 2015-09-11
JP2014533842A (en) 2014-12-15
EP2786214A1 (en) 2014-10-08
US9645550B2 (en) 2017-05-09
CH705831A2 (en) 2013-06-14
CH705836B1 (en) 2016-01-15
JP6246728B2 (en) 2017-12-13
US20140321250A1 (en) 2014-10-30
CH705836A1 (en) 2013-06-14

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