EP2124111B1 - Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr - Google Patents

Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr Download PDF

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Publication number
EP2124111B1
EP2124111B1 EP08008217A EP08008217A EP2124111B1 EP 2124111 B1 EP2124111 B1 EP 2124111B1 EP 08008217 A EP08008217 A EP 08008217A EP 08008217 A EP08008217 A EP 08008217A EP 2124111 B1 EP2124111 B1 EP 2124111B1
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EP
European Patent Office
Prior art keywords
wheel
platform
axis
mechanism according
planetary
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EP08008217A
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English (en)
French (fr)
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EP2124111A1 (de
Inventor
Carole Kasapi
Patrick Pichot
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Cartier Creation Studio SA
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Cartier Creation Studio SA
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Priority to DE602008003534T priority Critical patent/DE602008003534D1/de
Priority to EP08008217A priority patent/EP2124111B1/de
Priority to US12/260,193 priority patent/US7815364B2/en
Publication of EP2124111A1 publication Critical patent/EP2124111A1/de
Priority to US12/905,495 priority patent/US8075177B2/en
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Publication of EP2124111B1 publication Critical patent/EP2124111B1/de
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/18—Supports, suspensions or guide arrangements, for oscillating weights
    • G04B5/187—Bearing, guide arrangements or suspension allowing movement in more than one plane, e.g. there is more than one moving weight, or more than one plane in which the weight moves, and it can change place relative to the clockwork

Definitions

  • the subject of the present invention is a mechanism that avoids the variations, or deviations, of travel due to the effect of gravitation on a spiral balance adjusting device as well as a timepiece comprising such a mechanism.
  • the movements of the cage can theoretically statistically compensate for the differences in walking.
  • the watch when worn on the wrist it undergoes random movements and the deviations can not be fully offset by the constant regular movements imposed on the sprung balance by the rotating cage.
  • Document is known EP 1615085 a trim correction mechanism of a balance-sprung adjusting device which is held horizontal by the action of a counterweight.
  • the balance spring is carried by a platform secured to a counterweight rotatably mounted about a first axis, pivoted in a cage rotatably mounted about a second axis perpendicular to the first.
  • the escapement wheel of the regulating device is engaged with a driving wheel integral with the first axis and forming the output of a first differential gear train using three conical satellites, and therefore comprises two bevel gears.
  • the inputs of this differential are a first corrective kinematic chain and a second drive kinematic chain itself connected to the output of a second differential gear train having at the input the barrel wheel and a second corrective kinematic chain engaged with a wheel integral with the cage.
  • This second differential still uses three conical satellites, including two bevel gears, and in total the gear train has at least six bevel gears. Note also that all the wheels of the first corrective kinematic chain pivot on the platform is concentrically to its axis of rotation or on a fixed axis which is parallel to the latter. Similarly, all the wheels of the second corrective kinematic chain pivot on the cage either concentrically to its axis of rotation or on a fixed axis which is parallel to this axis.
  • a major disadvantage of this mechanism is the complexity of its gear train containing two corrective kinematic chains and a high number of bevel gears, in particular in its gear differential gears, which causes significant power losses and therefore requires the presence of a large counterweight and a large power reserve.
  • the weight of this balanced system is high which reduces the stabilization effect of the counterweight.
  • the object of the present invention is to provide a mechanism that avoids the gait deviations due to the effect of gravitation on a regulating member, in particular a timepiece, such as a balance-spring that allows said balance to be maintained.
  • a regulating member in particular a timepiece, such as a balance-spring that allows said balance to be maintained.
  • a timepiece such as a balance-spring that allows said balance to be maintained.
  • the subject of the present invention is a mechanism that avoids variations or variations in operation due to the effects of gravitation on a regulating device, sprung balance and a timepiece provided with such a device that obviates the aforementioned drawbacks of the existing devices.
  • This mechanism avoids the deviations due to the effect of gravitation on a regulating member of a watch movement of a timepiece, whose regulating member comprises a balance spring and an escape wheel mounted on a platform, said platform having an unbalance and being mounted in free rotation around at least a first axis (AA) relative to a movement plate so that said unbalance maintains said balance-spring in a plane fixed reference when said platform rotates about said first axis (AA) under the effect of terrestrial gravitation; is distinguished by the fact that the mechanism comprises a train comprising a driving kinematic chain connecting the escape wheel to a barrel system of the timepiece and a corrective kinematic chain which compensates for the movements and speed of the platform.
  • this work train comprising one or more epicyclic gear trains and each of said trains in said work train containing mobiles that mesh rightly only.
  • the invention also relates to a mechanism that avoids gait deviations due to the effect of gravitation on a regulating member of a timepiece movement of a timepiece, the regulating member of which comprises a balance-spring and an escape wheel mounted on a platform, said platform having an unbalance and being mounted in free rotation about at least a first axis by relative to a platen of movement so that said unbalance maintains said sprung balance in a fixed reference plane when said platform rotates about said first axis under the effect of earth gravitation; which is distinguished by the fact that the escape wheel is connected on the one hand to a barrel system of the timepiece by a driving kinematic chain and on the other hand to the platen of the movement by a corrective kinematic chain.
  • the invention also relates to a mechanism that avoids gait deviations due to the effect of gravitation on a regulating member of a timepiece movement of a timepiece, the regulating member of which comprises a balance-spring and an escape wheel mounted on a platform, said platform having an unbalance and being mounted in free rotation about at least a first axis relative to a platen of the movement so that said unbalance maintains said balance-spring in a fixed reference plane when this platform rotates about said first axis under the effect of earth gravitation; said mechanism comprising a driving kinematic chain connecting the escape wheel to a barrel system of the timepiece and a corrective kinematic chain compensating the movements and the speed of the platform relative to a platinum of the movement of watchmaker for these movements of the platform do not disrupt the chronometry of the timepiece, and wherein the second wheel of the clockwork of the clockwork is embarked on the platform.
  • the invention also relates to a timepiece provided with such a mechanism.
  • the subject of the present invention is a mechanism that avoids the variations or variations of a setting device of the spiral-balance type of a timepiece such as a wristwatch or a pocket watch due to the effect of the Earth gravitation resulting from changes in spatial orientation of the regulating device.
  • the mechanism according to the invention comprises means allowing the regulating device to remain in a stable spatial position despite the movements imposed by the wearer to the timepiece while avoiding disrupting the display of time.
  • the stable spatial position of the regulating device is a position for which the balance remains in a horizontal or vertical reference plane whatever the position of the watch.
  • the principle of the mechanism avoiding gait deviations consists in mounting the regulating member, generally the sprung balance, the anchor and the escape wheel on a mobile platform rotated along one or two orthogonal axes. relative to the platen of the watch movement, this platform being subjected to the action of an unbalance which thus makes it possible to maintain said platform in a fixed reference plane (either horizontal, vertical or possibly inclined), by the action of Earth's gravity whatever the position of the watch and therefore its movement.
  • a mechanism of this mechanism includes a driving kinematic chain connecting the escape wheel to the barrel system and a corrective kinematic chain that compensates the movements and speeds of the platform relative to the plate so that these movements of the plate -form do not disturb the chronometry of the timepiece.
  • this corrective kinematic chain when the platform rotates under the effect of its unbalance, it is possible to completely cancel the effect of the displacements and the speed of the platform on the main drive train.
  • a reference plane for example horizontal
  • the gear train and in particular the motor and corrective kinematic chains, has the particularity of including only epicyclic gear trains whose wheels mesh in a straight manner.
  • the gear thus excluded any epicyolo ⁇ dal train containing conical gears whose performance is very unfavorable.
  • the gearing includes bevel gears elsewhere in these motor and corrective kinematic chains, the latter are still of a reduced number compared to comparable gear systems of the state of the art.
  • a mobile main drive kinematic chain is mounted in a satellite door rotating about two coaxial motor axes embarked or not on a mobile unit comprising the platform carrying the balance and a cage pivoted on the plate of the movement on which is pivoted said platform.
  • a mechanism which avoids the operating deviations of the regulating member which consumes little energy, which makes it possible to reduce the weight of the unbalance of the platform and not to reduce significantly the power reserve of the movement of the watchmaking.
  • the corrective kinematic chain connects the escape wheel to the plate and comprises at least one mobile which pivots on the plate, which advantageously reduces the effect of the weight of this correction chain on the unbalanced platform.
  • the second wheel is on board the platform, which greatly minimizes the influence that the rotation of the platform may have on the torque transmitted to the exhaust by the driving main kinematic chain.
  • FIG. figure 1 The first embodiment of the mechanism avoiding the deviations of a clocking device is illustrated in FIG. figure 1 .
  • This is a simplified mechanism in that the platform carrying the regulating device is mounted free to rotate on the platen of the movement along a single axis of rotation AA perpendicular to the plane of the plate 1 of the clockwork movement.
  • the regulating device comprising a rocker 2, an anchor (not shown) and an escape wheel 3 is carried by a platform 4 pivoted on the plate 1 of the movement concentrically to the axis A-A.
  • the axis of rotation AA of the platform 4 comprises a first motor shaft 20 and a second motor shaft 22, the platform being constructed so that these two motor shafts rotate around the same axis AA .
  • the axis of the balance 2 is parallel to this axis of rotation A-A of the platform 4.
  • the escape wheel 3, rotated coaxially with the axis AA on the platform 4, is secured to a drive wheel or second driving wheel 5 connected to the escape wheel by the second drive shaft 22.
  • This second driving wheel 5 is engaged with the first mobile 6.2 of a satellite 6 rotated crazy in a satellite holder 7 which is itself pivoted on the platform 4 and rotated about the axis AA by a wheel of satellite door 7.1.
  • the satellite gate 7 effectively constitutes a cage rotating concentrically with the platform 4 and in which the satellite mobile 6 is mounted crazy.
  • the rotational speed of this satellite carrier 7 is a function of the speed of rotation of the platform 4 about the axis A-A.
  • the second mobile 6.1 of the satellite 6, integral and coaxial with the first mobile 6.2 of the satellite 6 is engaged with a first driving wheel 8 integral with the first motor shaft 20 pivoted on the plate 1 of the movement.
  • the wheel 8 and the tree 20 are integral with the second wheel 9 of the clockwork of the watch movement.
  • this second wheel 9 is kinematically connected to the barrel system 10 of the clockwork movement via the middle wheel 12 and the center wheel 11 all pivoted on the plate 1 of the following watch movement axes parallel to the AA axis.
  • the escape wheel 3 is thus connected to the barrel 10 by a main driving kinematic chain comprising a straight epicyclic gear train formed of the drive wheel 5, the first 6.1 and second 6.2 mobile satellite 6, the first wheel 8, of the second wheel 9, the average wheel 12, the center wheel 11 and the cylinder 10.
  • This drive main drive train has no conical return and therefore has a very good performance, for example a yield which is substantially equal to the engine power of a conventional mechanical watch.
  • a mobile of the main driving driveline in this case the mobile 6, is mounted idle in the satellite holder 7, the latter being part of a correction kinematic chain also comprising the satellite gate wheel 7.1, a mobile idler 13, pivoted crazy on the platform 4 along an axis parallel to the axis AA, and a fixed wheel 14 concentric with the axis AA and integral with the plate 1 of the movement.
  • the idler 13 comprises a first wheel 13.1 meshing with the satellite gate wheel 7.1 and a second wheel 13.2 (integral and coaxial with the wheel 13.1) engaged with the fixed wheel 14.
  • Rx being the number of teeth of wheel X.
  • V 9 a speed of the average wheel at the output of the platform and V u the useful speed transmitted to the exhaust (these speeds being still relative to a fixed reference)
  • V 9 1 k 2 ⁇ V u + k 1 + k 2 - k 1 . k 2 .
  • V 4 or k 2 R 8 .
  • R 6.2 R 6.1
  • the corrective kinematic chain comprises a right epicyclic gear train excluding any conical gear that consumes a lot of energy.
  • the gear train of this mechanism therefore comprises only spur gear trains, and is therefore particularly powerful, which allows to obtain a better performance and reduce the weight of the unbalance of the platform 4 and therefore its size and therefore allows not to reduce the power reserve of the watch movement.
  • the unbalance of the platform 4 can be constituted by the regulating device, sprung balance and escapement, itself since it can be mounted on the platform 4 offset from the axis of rotation AA of it. This avoids weighing down the watch movement.
  • a weight or mass could be attached eccentrically to the axis A-A on the platform 4 to increase the unbalance thereof.
  • the figure 1a illustrates a variant of the mechanism described with reference to the figure 1 .
  • the second wheel 9 of the work train is loaded on the platform 4 and meshes with the pinion of the escape wheel 3.
  • the axis of the escape wheel 3 which coincides with the axis AA of rotation of the platform 4, but the axis of the second wheel 9, the rocker 2 and the escape wheel 3 being pivoted on the platform 4 parallel to the axis AA.
  • the second wheel 9 which is integral and concentric with the drive wheel 5 via the second drive shaft 22.
  • the first drive wheel 8 is secured to it by the first drive shaft 20, a third drive wheel 15 engaged with the average wheel 12.
  • FIGS. 2, 3 and 4 illustrate by way of example a practical execution of the embodiment of the mechanism described with reference to the diagram of the figure 1a , that is to say for a stabilization around a single axis AA of the platform 4 carrying the regulating device 2, 3 and the second wheel 9.
  • the platform 4 is formed of an upper bridge 4.1, an intermediate bridge 4.2 carrying an exhaust bridge 3.1 and a lower bridge 4.3 pivoted on the plate 1 concentrically to the axis A-A.
  • the three bridges 4.1, 4.2 and 4.3 of the platform 4 are integrally connected together by columns 4.4 which ensures that all these elements of the platform rotate together freely in rotation relative to the plate.
  • the third drive wheel 15 is secured to the lower end of the first drive shaft 20 pivoted by a bearing 21 in the plate 1, the shaft 20 being free to rotate relative to the plate as indicated above.
  • This first motor shaft 20 has at its upper end the first drive wheel 8.
  • the fixed wheel 14 of the plate 1 meshes with the second wheel 13.2 of the idler 13 while the first wheel 13.1 of this idler, rotated crazy on the lower bridge 4.3, meshes with the wheel of the satellite door 7.1 of the lower hub of the door satellite 7 pivoted in the lower bridge 4.3 concentrically to the axis AA around the first motor shaft 20.
  • the satellite 6 is pivoted crazy on the satellite door 7, the second wheel 6.1 of the satellite 6 is engaged with the first driving wheel 8 while that the first wheel 6.2 of the satellite 6 meshes with the drive wheel or second drive wheel 5 which is integral with the lower end of the second drive shaft 22 pivoted on the intermediate bridge 4.2 of the platform 4.
  • This second motor shaft 22 carries the second wheel 9 which is engaged with the pinion 3.2 of the escape wheel 3.
  • the path of the main driving kinematic chain M linking has been highlighted the third driving wheel 15, connected by the engine train to the barrel, to the escape wheel 3 via the satellite 6 and the second wheel 9.
  • the figure 4 is a sectional view of the mechanism shown in figures 1a , 2 and 3 .
  • the second motor shaft 22 is extended beyond the intermediate bridge 4.2 of the platform 4 and is also pivoted in the upper deck 4.1 of this platform 4.
  • the free upper end of the second motor shaft 22 is extended beyond the upper deck 4.1 and carries a second hand 23 cooperating with a second dial 24 carried by the upper face of the upper deck 4.1 of the platform 4.
  • the seconds dial 24 rotates about the axis AA at the mercy of the movements of the platform 4.
  • the display of the hour and minutes is done conventionally from a mobile of the clockwork motor drive, generally the center wheel 11 or the medium wheel 12, by a timer to train the hour and minute hands that cooperate with a fixed dial relative to the watch movement platinum.
  • the kinematic and corrective drive chains comprise exclusively geared planetary gear trains with a very good efficiency making it possible not to reduce the power reserve of the movement and of minimize the weight and bulkiness of platform 4 unbalance.
  • a constant force escapement can be installed on the platform in order to avoid the influence that the rotation of the platform can have on the torque transmitted to the exhaust.
  • the figure 5 illustrates an embodiment of the mechanism avoiding the deviations of the setting device of a watch movement in which the platform 4 is stabilized about an axis of rotation AA orthogonal to the axis of the 2.
  • the axis of the balance 2, the axis of the escape wheel 3 and the axis of the second wheel embedded 9 are all three perpendicular to the axis of rotation AA of the platform 4.
  • the correction mechanism comprises a conical return 25 secured to the drive wheel or second driving wheel 5 which meshes with the second wheel 9.
  • the mechanism is identical to that of the first embodiment in its variant described in figures 1
  • the axis AA around which the platform is rotated can for example be the 3 o'clock - 9 o'clock axis of the watch.
  • FIG. figure 6 The embodiment of the mechanism avoiding gait deviations of a regulating member of a clockwork movement schematically illustrated in FIG. figure 6 allows the stabilization of the platform 4 carrying the balance 2 around two axes of rotation AA and BB orthogonal to each other and with respect to the axis of rotation of the balance 2.
  • Such a mechanism makes it possible to maintain the platform 4 carrying the setting device of the watch in a fixed reference plane regardless of the orientation of the plate 1 of the movement of the watch in space and no longer just with respect to a single axis of displacement.
  • Figures 7 to 10 A practical embodiment or construction of such an embodiment is illustrated in Figures 7 to 10 for example.
  • the mechanism represented differs from that illustrated schematically in figure 6 by adding mobiles 36; 37.1; 37.2 and 15.2 to reduce the bulk of the third drive wheel 15.
  • This mechanism comprises a cage 30 pivoted on the plate 1 about a second axis of rotation BB.
  • Platform 4 of the figure 5 previously described is, it, rotatably mounted on this cage 30 around the first axis of rotation AA perpendicular to the second axis of rotation BB of the cage 30.
  • the platform 4 carries the balance 2, the escape wheel 3 and the second wheel 9 of which the axes are parallel to each other and orthogonal to the first AA and second BB axes of rotation.
  • the second wheel 9 meshes with the conical return 25 secured to the drive wheel or second drive wheel 5 pivoted on the platform 4 concentrically to the first axis of rotation AA around which said platform 4 rotates. Still as previously described , this drive wheel 5 meshes with the first wheel 6.2 of the satellite 6 whose satellite carrier cage 7 pivots about the first axis of rotation AA on the platform 4.
  • the second satellite wheel 6.1 meshes with the first drive wheel 8 concentrically pivoted to the first axis of rotation AA on the cage 30, which itself is pivoted about the second axis of rotation BB on the plate 1.
  • This first drive wheel 8 is integral with the third drive wheel 15 both pivoted on the cage 30 .
  • the satellite gate 7 is engaged by its satellite gate wheel 7.1 with the first wheel 13.1 of the idler mobile 13 pivoted mad on the platform 4, the second wheel 13.2 meshes with the first wheel 32.1 of a corrective mobile 32 whose second wheel 32.2 has a conical toothing.
  • This corrective mobile 32 is pivoted on the platform 4, in particular around the first drive shaft 20, concentrically to its axis of rotation AA on the cage 30.
  • This corrector mobile 32 meshes with its second wheel 32.2 with the fixed wheel 14 secured to the plate 1.
  • the fixed wheel 14 thus has a conical toothing.
  • the third drive wheel 15 also has a conical toothing and meshes with the first bevel gear 34.1 of a second idler wheel 34 rotated crazy on the cage 30.
  • the second wheel 34.2 of the second idler 34 is engaged with a fourth driving wheel 35 pivoted concentrically to the second axis of rotation BB on the cage 30.
  • This fourth drive wheel 35 is integral with a fifth drive wheel 35A kinematically connected to the cylinder 10 by a drive train of the movement may comprise a center wheel 11 and a wheel of high average 12 for example (the latter not being shown in the figure 6 for simplicity).
  • the platform 4 which carries the regulating device 2, 3 thus has two degrees of freedom, rotation about a first axis A-A and rotation about a second axis B-B orthogonal to the first axis A-A.
  • the platform 4 having an unbalance, formed by the regulating device 2, 3 or by an additional unbalance can thus move according to the any spatial orientation of the plate 1 of the movement to ensure the maintenance in a fixed reference plane balance 2 and avoid all deviations due to gravity regardless of the position of the watch or movements imposed on them.
  • the main drive train comprises the fifth drive wheel 35A, the fourth drive wheel 35, the second drive wheel 34, the third drive wheel 15, the first drive wheel 8, the satellite 6, the drive wheel drive (or second driving wheel) 5 and the conical return 25 as well as the second wheel 9 and the escape wheel 3.
  • the corrective kinematic chain it comprises in this embodiment the fixed wheel 14, the correction mobile 32, the first mobile crazy 13, the wheel of the satellite door 7.1, and the satellite door.
  • the workings of this mechanism including including these two motor and corrective kinematic chains comprise only gear trains epicyclic right with good efficiency.
  • the mechanism gear includes bevel gears elsewhere in these kinematic and corrective drive chains, these gears are still of a reduced number compared to comparable gear systems of the state of the art.
  • that of the figure 6 comprises considerably fewer links and in particular half the number of bevel gears used in the mechanism of EP 1615085 .
  • correction of the displacements of the cage 30 and the platform 4 are made using a single continuous correction kinematic chain.
  • the figure 12 illustrates yet another embodiment of the mechanism with two axes of rotation in which part of the correction kinematic chain, including in particular the mobile 6 and its satellite door 7, is located outside the platform 4 and the cage 30.
  • the platform 4 carrying the regulating device, sprung balance 2 and escape wheel 3 is, just as in the figure 6 , pivoted on the cage 30 along a first axis of rotation AA perpendicular to the axes of the balance 2 and the escape wheel 3. Also, the cage 30, it is rotated on the plate 1 along a second axis of rotation BB perpendicular at the first axis of rotation AA of the platform 4 on the cage 30 and perpendicular to the axes of the balance 2 and the escape wheel 3.
  • a second wheel 9 secured to a first drive shaft 40 is connected to the barrel by the usual engine gear of the watch movement.
  • This first motor shaft 40 is pivoted on the plate 1 and one of its ends carries a second hand 39 cooperating with a second fixed dial relative to the plate 1.
  • the conical return 25 meshes with the escape wheel 3 and meshes with the first wheel 41.1 of a first driving mobile 41 pivoted on the platform 4 coaxially with the axis of rotation AA of the platform 4.
  • the second 41.2 wheel of the first driving mobile meshes with the first wheel 42.1 of a second driving mobile 42 pivoted on the cage 30 and the plate 1 coaxially with the axis of rotation BB of the cage 30.
  • the second wheel 42.2 of the second mobile coach 42 meshes with a third driving wheel 43 secured to a second motor shaft 44 pivoted on the plate 1 in a direction parallel to the axis of rotation BB of the cage 30 on the plate 1.
  • This second motor shaft 44 is integral with a second drive wheel 45 in engagement with the first satellite wheel 6.1 of the satellite 6 whose second wheel 6.2 meshes with a first drive wheel 46 integral with a first drive shaft 40 and thus the second wheel 9.
  • These first and second trees mo 40, 44 are coaxial.
  • the satellite 6 is rotated crazy in the satellite carrier 7 concentrically to the first and second motor shafts 40, 44 on the plate 1.
  • the satellite gate wheel 7.1 is engaged with the first wheel 47.1 of a mobile corrector 47 pivoted on the plate 1 concentrically to the pivot axis BB of the cage 30 on the plate 1, the second wheel 47.2 is engaged with a correction wheel 48 secured to the platform 4 and concentric to the axis AA of rotation of this platform 4 on the cage 30.
  • the main drive train comprises the second wheel 9, the first drive shaft 40, the first driving wheel 46, the satellite 6, the second driving wheel 45, the second driving shaft 44, the third wheel 43, the second driving mobile 42, the first driving mobile 41 and the conical return 25 secured to the escape wheel 3.
  • this drive main drive train comprises bevel gears, all epicyclic gear trains which constitute it are straight and therefore of high efficiency.
  • the number of bevel gears used elsewhere in the gear train is still of a reduced number compared to the state of the art.
  • the corrective kinematic chain comprises the correction wheel 48, the correction wheel 47, the satellite gate wheel 7.1, and the satellite gate 7.
  • This correction chain also comprises only a limited number of bevel gears as well as planetary gear trains which meshes in a straight manner only (excluding any epicyclic bevel gear train); this chain is still relatively good.
  • the second wheel 9 can also be embarked on the platform 4 reducing or canceling the effects of the movements of the platform 4 on the torque transmitted to the regulating device 2, 3.
  • the mechanism comprises only one and the same correction kinematic chain which is continuous.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Gears, Cams (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Claims (18)

  1. Mechanismus, der Gangvariationen aufgrund der Einwirkung der Schwerkraft auf ein Regulierorgan (2, 3) in einem Uhrwerk einer Uhr verhindert, wobei dieser Mechanismus ein Regulierorgan umfasst, dass eine Spiralunruh (2) und ein Hemmungsrad (3) umfasst, die auf einer Plattform (4) montiert sind, wobei die Plattform (4) eine Unwucht umfasst und frei um mindestens eine erste Achse (A-A) im Verhältnis zu einer Uhrwerkplatte (1) drehend montiert ist, damit die Plattform (4), die sich um die erste Achse (A-A) dreht, unter der Einwirkung der Erdschwerkraft steht; wobei der Mechanismus ein Räderwerk, das eine antreibende kinematische Kette (M) umfasst, die dazu eingerichtet ist, das Hemmungsrad (3) mit einem Federgehäusesystem (10) der Uhr zu verbinden, sowie eine korrigierende kinematische Kette (C), um die Auswirkung von Verlagerungen und der Geschwindigkeit der Plattform (4) im Verhältnis zu der Platte (1) auf die antreibende kinematische Kette (M) aufzuheben, umfasst, wobei die antreibende kinematische Kette (M) ein erstes Triebrad (8, 46), das mit einer ersten Motorwelle (20, 40) fest verbunden ist, und ein zweites Triebrad (5, 45), das mit einer zweiten Motorwelle (22, 44), die zu der ersten Motorwelle (20, 40) koaxial ist, fest verbunden ist, umfasst, dadurch gekennzeichnet, dass das Räderwerk ein oder mehrere Umlaufgetriebe umfasst, wobei jedes der Getriebe in dem Räderwerk Zahnräder mit ausschließlich Geradverzahnung enthält, und dass das erste Triebrad (8, 46) gerade mit dem zweiten Rad (6.1) eines Ausgleichkegelrads (6) einspurt, dessen erstes Rad (6.2) gerade mit dem zweiten Triebrad (5, 45) einspurt.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass das Ausgleichkegelrad (6) frei um eine Ausgleichkegelradhalterung (7) gedreht wird, die sich selbst koaxial um die erste und die zweite Motorwelle (20, 22; 40, 44) dreht, und dass die Ausgleichkegelradhalterung (7) ein Rad (7.1) der Ausgleichkegelradhalterung umfasst, die einen Teil der korrigierenden kinematischen Kette (C) bildet.
  3. Mechanismus nach Anspruch 2, dadurch gekennzeichnet, dass die korrigierende kinematische Kette (C) das Rad (7.1) der Ausgleichkegelradhalterung (7) mit einem feststehenden Rad (14) verbindet, das mit der Platte (1) des Uhrwerks fest verbunden ist.
  4. Mechanismus nach Anspruch 3, dadurch gekennzeichnet, dass das feststehende Rad (14) koaxial zur Drehachse (A-A) der Plattform (4) ist.
  5. Mechanismus nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die korrigierende kinematische Kette (C) ein Ausgleichkegelradzahnrad (13) umfasst, das auf der Plattform (4) parallel zur Achse A-A frei gedreht wird und ein erstes Rad (13.1), das mit dem Rad der Ausgleichkegelradhalterung (7.1) einspurt, und ein zweites Rad (13.2), das mit dem feststehenden Rad (14) einspurt, umfasst.
  6. Mechanismus nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Plattform (4) in einem Käfig (30) aufgehängt ist, der auf der Platte (1) um eine zweite Drehachse (B-B), die zu der ersten Drehachse (A-A) orthogonal ist, frei gedreht wird.
  7. Mechanismus nach Anspruch 6, dadurch gekennzeichnet, dass die korrigierende kinematische Kette (C) das Rad (7.1) der Ausgleichkegelradhalterung (7) mit einem feststehenden Rad (14) verbindet, das mit der Platte (1) fest verbunden und zu der zweiten Drehachse (B-B) des Käfigs (30) koaxial ist.
  8. Mechanismus nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass die korrigierende kinematische Kette (C) das Rad (7.1) der Ausgleichkegelradhalterung (7) mit einem Korrekturzahnrad (32) verbindet, das mit der Platte (4) fest verbunden und zu der ersten Drehachse (A-A) dieser koaxial ist.
  9. Mechanismus nach Anspruch 8, dadurch gekennzeichnet, dass die korrigierende kinematische Kette (C) ein Ausgleichkegelradzahnrad (13) umfasst, das auf der Plattform (4) längs der Achse A-A frei gedreht wird und ein erstes Rad (13.1), das mit dem Rad der Ausgleichkegelradhalterung (7.1) einspurt, und ein zweites Rad (13.2), das mit einem ersten Rad (32.1) des Korrekturzahnrads (32) einspurt, umfasst, und dass ein zweites Rad (32.2) des Korrekturzahnrads (32) mit dem feststehenden Rad (14) einspurt.
  10. Mechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Achse der Unruh (2) zur ersten Drehachse (A-A) der Plattform (4) parallel ist.
  11. Mechanismus nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Achse der Unruh (2) zur ersten Drehachse (A-A) der Plattform (4) senkrecht ist.
  12. Mechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Sekundenrad (9) des Motorräderwerks des Uhrwerks auf der Plattform (4) verstaut ist.
  13. Mechanismus nach Anspruch 12, dadurch gekennzeichnet, dass das Sekundenrad (9) mit dem Hemmungszahnrad (3) einspurt und dass seine Achse zu der der Unruh (2) und des Hemmungszahnrads (3) parallel ist.
  14. Mechanismus nach Anspruch 13, dadurch gekennzeichnet, dass die Achse des Sekundenrads (9) mit der zweiten Motorwelle (22) zusammengenommen ist, wobei das freie Ende dieser einen Sekundenzeiger (23) trägt, der mit einem Sekundenzifferblatt (24) zusammenwirkt, das mit der Plattform (4) fest verbunden und zu dem Sekundenrad (9) koaxial ist.
  15. Mechanismus nach einem der Ansprüche 2 bis 14, dadurch gekennzeichnet, dass die Ausgleichkegelradhalterung (7) auf der Plattform (4) gedreht wird.
  16. Mechanismus nach einem der Ansprüche 1 oder 6, dadurch gekennzeichnet, dass die Ausgleichkegelradhalterung (7) auf der Platte (1) des Uhrwerks gedreht wird.
  17. Mechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Zahnradeinheit, die von der Plattform (4) oder der Plattform (4) und dem Käfig (30) gebildet wird, als ein Aufzuggewicht für ein automatisches Aufzugsystem der Uhr verwendet wird.
  18. Uhr, die mit einem Mechanismus nach einem der Ansprüche 1 bis 17 ausgestattet ist.
EP08008217A 2008-04-30 2008-04-30 Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr Active EP2124111B1 (de)

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DE602008003534T DE602008003534D1 (de) 2008-04-30 2008-04-30 Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr
EP08008217A EP2124111B1 (de) 2008-04-30 2008-04-30 Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr
US12/260,193 US7815364B2 (en) 2008-04-30 2008-10-29 Mechanism to avoid rate variations due to gravitation in a sprung balance regulating organ, and timepiece provided with such a mechanism
US12/905,495 US8075177B2 (en) 2008-04-30 2010-10-15 Mechanism to avoid rate variations due to gravitation in a sprung balance regulating organ, and timepiece provided with such a mechanism

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EP08008217A EP2124111B1 (de) 2008-04-30 2008-04-30 Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr

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RU2710974C1 (ru) * 2018-07-24 2020-01-14 Гарри Уинстон Са Часовой приводной механизм
RU2712959C1 (ru) * 2018-07-24 2020-02-03 Гарри Уинстон Са Ретроградный турбийон или карусель для часов
RU2742378C1 (ru) * 2018-07-24 2021-02-05 Гарри Уинстон Са Часовой ретроградный турбийон или карусель

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CH702707B1 (fr) * 2007-04-05 2011-08-31 Complitime Sa Mouvement de pièce d'horlogerie à tourbillon.
CH700222B1 (fr) * 2009-01-15 2015-04-15 Temps Sa Fab Du Mouvement horloger automatique à échappement monté sur la masse oscillante.
CH701239A2 (fr) * 2009-06-10 2010-12-15 Olivier Schneider Mecanisme de remontage automatique pour mouvement horloger.
EP2264551B1 (de) * 2009-06-16 2013-08-07 Samep S.A. - Montres Emile Pequignet Differentialzahnradgetriebe für Uhrwerk
CH701490A1 (fr) * 2009-07-17 2011-01-31 Franck Mueller Watchland S A Tourbillon a roue d'echappement fixe.
EP2397920A1 (de) * 2010-06-17 2011-12-21 Blancpain S.A. Mechanismus für springendes Tourbillon-Gestell oder Karussell-Gestell
EP2533109B1 (de) 2011-06-09 2019-03-13 Cartier International AG Mechanismus zur vermeidung der schwerkraftbedingten gangvariationen auf einer reguliervorrichtung mit spiralunruh, und mit dieser perfektionierung ausgestattete uhr
CH705244B1 (fr) * 2011-07-07 2016-06-30 Gfpi S A Pièce d'horlogerie.
CH705836B1 (fr) * 2011-12-02 2016-01-15 Lvmh Swiss Mft Sa Pièce d'horlogerie.
US20160108191A1 (en) * 2014-10-20 2016-04-21 Fina Technology, Inc. Opaque pp/pla bopp films with broad processing window
CH711790B1 (fr) * 2015-11-17 2021-03-31 Complitime Sa Mouvement d'horlogerie.
CN105652630B (zh) * 2016-03-15 2018-04-03 北表表业（北京）有限公司 一种陀飞轮及其适用的陀飞轮钟表
CH713757B1 (fr) * 2017-05-05 2020-12-15 Gfpi Sa Mouvement d'horlogerie comprenant une pluralité de systèmes réglants.

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CH699838B1 (fr) * 2004-03-09 2010-05-14 Franck Muller Watchland Sa Tourbillon tri-axial pour pièce d'horlogerie, notamment montre-bracelet.
JP4555336B2 (ja) * 2004-04-15 2010-09-29 モントレー ブレゲ・エス アー ２つのタービロンを備える腕時計
ATE406603T1 (de) 2004-07-08 2008-09-15 Audemars Piguet Renaud Et Papi Korrekturmechanismus von einem teller einer regulierungsvorrichtung für ein uhruh-spiralfeder
DE602005009316D1 (de) * 2005-01-28 2008-10-09 Richemont Int Sa Uhr mit Tourbillon
DE602005021748D1 (de) * 2005-03-30 2010-07-22 Montres Breguet Sa Uhr mit mindenstens zwei Reguliersystemen
ATE462159T1 (de) 2005-07-13 2010-04-15 Artisans Horlogers Sarl Uhr
EP2275879B1 (de) * 2007-02-08 2019-12-11 CompliTime SA Einsatzhemmung
EP2031465A1 (de) * 2007-08-29 2009-03-04 Zenith International SA Uhr

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RU2710974C1 (ru) * 2018-07-24 2020-01-14 Гарри Уинстон Са Часовой приводной механизм
RU2712959C1 (ru) * 2018-07-24 2020-02-03 Гарри Уинстон Са Ретроградный турбийон или карусель для часов
RU2742378C1 (ru) * 2018-07-24 2021-02-05 Гарри Уинстон Са Часовой ретроградный турбийон или карусель

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US20090274012A1 (en) 2009-11-05
EP2124111A1 (de) 2009-11-25
US7815364B2 (en) 2010-10-19
US8075177B2 (en) 2011-12-13
US20110026373A1 (en) 2011-02-03
DE602008003534D1 (de) 2010-12-30

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