Classifications

• • 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

Definitions

• the present invention relates to mechanical timepieces. It relates more particularly to a timepiece comprising a frame, at least one driving mobile, such as a mobile of a finishing train, and at least one tourbillon mechanism comprising:
• a first cage movable in rotation about a first axis and on which are mounted pivoting a rocker arm and an escape wheel formed of an escape wheel and an exhaust pinion,
• a third cage movable in rotation about a third axis, said third cage carrying said first and second cages and driving them kinematically.
• a vortex mechanism is a device for averaging the gait of the positions of the balance of a timepiece.
• a vortex mechanism comprises, for this purpose, a support, (for example a cage in the case of the traditional tourbillon) pivotally mounted on the frame, generally an assembly formed of a bridge and a plate and, mounted pivoting on this support, a balance spring and an exhaust comprising in particular an escape wheel with a wheel and a pinion.
• the support comprises a gear connected kinematically to the work train of the timepiece, in general to the average wheel.
• a toothed wheel mounted fixed on the frame, meshes with the exhaust pinion.
• the torque applied by the average wheel on the gear slightly rotates the support, the pendulum pulse being given by the exhaust whose mobile rotates by meshing of its pinion with the gear wheel.
• the wheels and gears are, in general, arranged and numbered so that the vortex performs one revolution per minute. So when the timepiece is arranged vertically, the position of the neutral point of the pendulum is therefore one revolution per minute, which means the differences in walking in the vertical positions. On the other hand, the difference between horizontal and vertical positions remains.
• a triaxial vortex described in the application EP 1 574 916, comprising a cage containing the balance and the escapement in rotation along an axis, the cage being mounted in a second cage so as to rotate around another axis, the second cage being rotatably mounted in a third cage rotating about a fixed axis relative to the timepiece, the three axes being perpendicular to one another.
• the triaxial vortex is driven by a drive wheel mounted on the turntable of the timepiece, which drives a pinion integral with the third cage, and rotates said cage about its axis thereby rotating a pinion meshing with a fixed crown on the turntable of the timepiece, which causes the cage to rotate about its axis, the second cage rotating the first cage around its axis via a crown and the second pinion secured to the third cage, and thus transmit the energy from the drive wheel to the assembly formed by the exhaust pinion, the escape wheel and the balance placed in the first cage.
• Such a mechanism has the disadvantage of being bulky and unattractive due to the presence of several toothed crowns appearing in particular dial face.
• Known triaxial vortex mechanisms therefore have elements that are harmful and contrary to the expected characteristics of a vortex, namely to have a system as light as possible to have as little inertia as possible, as well as good visibility of the last.
• An object of the present invention is therefore to overcome these disadvantages, by providing a timepiece comprising a vortex mechanism to reduce the moment of inertia of the system.
• Another object of the present invention is to provide a timepiece comprising a robust tourbillon mechanism, having a small footprint and improved aesthetic appearance.
• a timepiece comprising a frame, at least one driving mobile, such as a mobile of a finishing train and at least one vortex mechanism.
• driving mobile such as a mobile of a finishing train
• vortex mechanism comprising:
• first cage movable in rotation about a first axis and on which are mounted pivoting a rocker and an escapement mobile formed of an escape wheel and an exhaust pinion, a second mobile cage in rotation about a second axis and carrying said first cage,
• a third cage movable in rotation about a third axis, said third cage carrying said first and second cages and driving them kinematically.
• two prennier, second and third axes are perpendicular to each other, the remaining axis of the first, second and third axes forming an angle different from 0 ° and 90 ° with one of the other two first, second and third axes.
• This construction reduces the size of the tourbillon mechanism and its moment of inertia.
• FIG. 1 represents a perspective view of a tourbillon mechanism of the invention
• FIG. 2 represents a sectional view of said tourbillon mechanism of the invention
• FIG. 3 shows a perspective view of the tourbillon mechanism of the invention, the outer cage having been removed.
• the term "cooperate” means both a direct kinematic connection between two elements that an indirect kinematic connection between two elements, references or intermediate part (s) being provided between said two elements .
• a vortex mechanism 1 mounted on a frame of a timepiece according to the invention.
• the frame is a set of a bridge and a plate, but it is obvious that the frame can include any support element of the timepiece organs.
• a driving carrier 2 such as a mobile of a work train, for example the wheel of average.
• the vortex mechanism comprises a first cage 4 rotatable about a first axis A and on which are mounted pivoting a rocker 6 and an exhaust mobile, comprising an escape wheel and an exhaust pinion (not shown)
• first cage 4 rotatable about a first axis A and on which are mounted pivoting a rocker 6 and an exhaust mobile, comprising an escape wheel and an exhaust pinion (not shown)
• the vortex mechanism also comprises a second cage 8 rotatable about a second axis B and on which said first cage 4 is pivotally mounted about the first axis A.
• the vortex mechanism also comprises a third cage 10 rotatably mounted on the frame about a third axis C, said third cage 10 carrying said first and second cages, 4 and 8, and driving them kinematically.
• the third cage 10 is pivoted by the center, not by its periphery. This allows on the one hand to reduce the size of the system and on the other hand to reduce the torque to be applied to the system to rotate it.
• two of the first A, second B and third C axes are perpendicular to each other, the remaining axis of the first
• A, second B and third C axes forming an angle different from 0 ° and 90 ° with one of the other two first A, second B and third C axes.
• the remaining axis of the first A, second B and third C axes form an angle of between 1 ° and 89 °, preferably between 46 ° and 89 °, and more preferably between 60 ° and 85 °, with one of the other two first A, second B and third C axes.
• the second axis B of the second cage 8 is perpendicular to the third axis C of the third cage 10, the first axis A of the first cage 4 forming with the second axis B of the second cage a angle between 1 ° and 89 °, preferably between 46 ° and 89 °, and more preferably between 60 ° and 85 °.
• the remaining axis of the first A, second B and third C axes, and more specifically the axis A forms an angle of between 1 ° and 89 °, preferably between 5 ° and 85 °, of preferably between 10 ° and 80 °, preferably between 30 ° and 80 °, more preferably between 46 ° and 80 °, and even more preferably between 60 ° and 80 °, with one of the other two first A, second B and third axis C, and more specifically with the axis B.
• the rocker 6 is pivotally mounted about a fourth axis D, said fourth axis D of the beam 6 forming with the first axis A of the first cage 4 an angle of 0 °.
• the rocker 6 is pivotally mounted about a fourth axis D, said fourth axis D of the beam forming 6 with the first axis A of the first cage 4 at an angle other than 0 °.
• a first fixed wheel 12 is integral with the second cage 8, said first fixed wheel 12 cooperating with the exhaust pinion mounted in the first cage 4.
• the first cage 4 comprises a first shaft 14 extending along the first axis A, said first shaft 14 being pivotally mounted on the second cage 8 and being integral with a first drive wheel 16 of the first cage 4
• a second fixed wheel 18 is mounted integral with the third cage 10, said first drive wheel 16 of the first cage 4 cooperating with said second fixed wheel 18. This cooperation can be direct or indirect.
• At least one intermediate gear 20 which is pivotally mounted on the second cage 8, said intermediate gear 20 kinematically connecting the second fixed wheel 18 to the first drive wheel 16 of the first cage 4.
• the second fixed wheel 18 and the intermediate gear 20 form a bevel gear.
• the axis of rotation E of the intermediate gear 20 may be parallel to the axis D of the balance 6, as shown in Figure 2.
• the axis of rotation E of the intermediate gear 20 may be inclined with respect to said axis D of the pendulum 6.
• the second cage 8 comprises a second shaft 22 extending along the second axis B, said second shaft 22 being pivotally mounted on the third cage 10 and being secured to a second drive wheel 24 of the second cage 8
• a third fixed wheel 26 is mounted integral with the frame, said second drive wheel 24 of the second cage 8 cooperating with said third fixed wheel 26.
• the second driving wheel 24 of the second cage 8 and the third fixed wheel 26 form a bevel gear. It is obvious that depending on the configuration of the mechanism, other types of non-conical gearing can be used.
• the third cage 10 comprises a third shaft 28 extending along the third axis C, said third shaft 28 being pivotally mounted on the frame and being integral with a third drive wheel 30 of the third cage 10 cooperating with the mobile trainer 2 of the work train.
• the third cage could be mounted pivoted cantilever, that is to say that its shaft 28 would be pivotally mounted on the frame of one side, typically the lower side, for example by means of a ball bearing.
• the shaft 28 is pivotally mounted on the frame by its two ends.
• the third cage 10 comprises a central portion 10a flowing over the third fixed wheel 26, and a lower portion 10b arranged so that the third drive wheel 30, positioned here at the end of said lower portion 10b, cooperates with the driving mobile 2 of the work train. It is obvious that an inverted configuration can also be envisaged, according to which the toothing of the third fixed wheel 26 would be directed towards the lower part 10b, the central part then flowing beneath said third fixed wheel 26.
• the third cage 10 also comprises an upper portion 10c advantageously having, in the variant shown here, the shape of an arch attached to the central portion 10a. The arch is of small width, but rigid enough to maintain the system during an impact, which allows to leave visible the first and second cages 4 and 8 placed inside the third cage 10.
• the third fixed wheel 26 is dimensioned so that the lower part 10b of the third cage 10 and the second cage 8 and the elements carried by the second cage 8 can pivot and circulate inside said third fixed wheel 26.
• the axis C of the third cage 10 may be parallel or inclined with the axis of rotation of one of the mobile of the work train, and in particular the driving mobile 2.
• the axis of rotation of the driving wheel of the work train may be perpendicular or not to the frame, the vortex mechanism is then arranged accordingly.
• the mobile driving 2 of the finishing train is driven in a rotational manner so as to subject the first cage 4 to a motor torque by meshing with the third drive wheel 26 of the third cage 10.
• the second drive wheel 24 of the second cage 8 carried by the third cage 10 is capable of meshing with the third fixed wheel 26 to drive the second cage 8 in rotation.
• the intermediate gear 20 carried by the second cage 8 is capable of meshing with the second fixed wheel 18 secured to the third cage 10, to drive in rotation the first drive wheel 16 of the first cage 4 and thus the rotation of the first cage 4.
• the engine torque can cause a displacement of the first cage 4 when the exhaust gives a driving impulse to the pendulum, according to the classic operation of an exhaust.
• the construction according to the invention allows for a tourbillon mechanism having a reduced moment of inertia compared to the axis B. Indeed, the fact of having an angle different from 90 ° between the axes of the first cage 4 and the second cage 8 has the effect of bringing the system to the center of gravity of the vortex mechanism. Considering the configuration of the mechanism according to the invention, it is found that there is more weight in the lower part of the system and that by tilting it (that is to say having the angle between the axes A and B different from 0 ° and 90 °), the moment of inertia is reduced with respect to the B axis.
• the moment of inertia with respect to the axis B is 14.95 g. mm 2 .
• the moment of inertia with respect to the axis B is 14.25 g. mm 2
• a decrease of the moment of inertia with respect to the B axis is 14.8%. This is to reduce the resistance to rotation of the second cage 8 and thus to promote the operation of the system relative to known systems in which the axes are all perpendicular to each other.
• the cage 8 will rotate about its axis B with greater ease than if its axis of rotation B was perpendicular to the axis A of the cage 4.
• the construction according to the invention also makes it possible to produce a tourbillon mechanism having a reduced bulk, in particular because of the inclination of the axis E of the intermediate gear 20 with respect to the axis C of the third cage 10. Indeed, if the axis E is inclined with respect to the axis C, then the diameter of the second fixed wheel 18 can be reduced. In addition, by inclining the axis D of the balance 6 relative to the axis A of the first cage 4, it is possible, by finding the right compromise between the size of the balance and the distance between the balance and the cage, of further reduce the size of the first cage 4 and thus make the system even more compact.
• the tourbillon mechanism of the invention is robust and also has a very good impact resistance.
• the present invention is not limited to the embodiment described.
• the shape of the cages can vary, as well as the type of exhaust, such as a detent escapement, for example.

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Applications Claiming Priority (2)

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• 2012
  • 2012-10-15 CH CH01422/15A patent/CH711316B1/fr unknown
  • 2012-10-15 CH CH02003/12A patent/CH707079B1/fr unknown
• 2013
  • 2013-10-14 HU HUE13774694A patent/HUE038217T2/hu unknown
  • 2013-10-14 EP EP13774694.7A patent/EP2906996B1/de active Active
  • 2013-10-14 WO PCT/EP2013/071410 patent/WO2014060346A1/fr active Application Filing
  • 2013-10-14 CN CN201380053500.5A patent/CN104737081B/zh active Active
  • 2013-10-14 US US14/434,088 patent/US9268308B2/en active Active
• 2016
  • 2016-02-15 HK HK16101630.6A patent/HK1213649A1/zh unknown

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