EP2583143B1 - Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge - Google Patents

Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge Download PDF

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Publication number
EP2583143B1
EP2583143B1 EP11725119.9A EP11725119A EP2583143B1 EP 2583143 B1 EP2583143 B1 EP 2583143B1 EP 11725119 A EP11725119 A EP 11725119A EP 2583143 B1 EP2583143 B1 EP 2583143B1
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EP
European Patent Office
Prior art keywords
cage
escape
pivoting
wheel
retaining means
Prior art date
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EP11725119.9A
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English (en)
French (fr)
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EP2583143A1 (de
Inventor
Edmond Capt
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Blancpain SA
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Blancpain SA
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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
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/15—Intermittent grip type mechanical movement
    • Y10T74/1502—Escapement

Definitions

  • the invention more particularly relates to a mechanism for advancing the jump of a vortex or carousel cage to a second dead.
  • the invention further relates to a vortex comprising a vortex cage and such a mechanism.
  • the invention also relates to a carousel comprising a carousel cage and such a mechanism.
  • the invention also relates to a timepiece comprising such a mechanism, or such a carousel, or such a tourbillon.
  • the invention relates to the field of watchmaking.
  • the Swiss patent CH 47 297 in the name of Pellaton-Schild describes, from 1907 , a second lightning dead, with two field wheels connected to each other by a spiral spring, and one of which drives the exhaust pinion, which is coaxial and fixed to a star with protruding teeth.
  • the engine cylinder drives, through a gear, a pinion carrying a whip, which bears each time on a tooth of the star, their relative pivoting generating a position where the whip escapes the tooth, of way lightning, and performs a complete turn before coming back abut another tooth of the star.
  • EP 1 319 997 on behalf of Richemont International SA, which describes a vortex mechanism incorporating a constant force device.
  • This tourbillon mechanism comprises a pivoting cage driven by a drive wheel, this tourbillon cage is coaxial with a pivoting beam provided with a balance spring balance and with a fixed second wheel, and is carrier, in three separate eccentric positions, an eccentric escapement wheel, a first anchor, and a stop wheel which meshes with this fixed second wheel.
  • the escape wheel cooperates with this first anchor provided with two pallets.
  • a constant force device comprises a spiral escapement spring, integral at one end with the escape wheel, and at a second end with a force compensation disc. The latter is integral in rotation with an armature ring of the exhaust spring, and a pinion of armoring ring which is associated with it and which cooperates with the fixed second wheel.
  • a Reuleaux cam of substantially triangular shape cooperates with a fork that includes a second anchor coaxial with the balance, which pivots about the axis of the tourbillon cage.
  • This second anchor comprises a cam arranged to cooperate with a fork and a dart carried by the first anchor.
  • the second anchor comprises two vanes arranged to cooperate with radially projecting teeth that includes the stop wheel.
  • the balance is driven under the effect of the preload of the exhaust spring, and is returned by the balance spring spiral.
  • the balance carries a number of alternations, for example five with a wheel of fifteen teeth, before the stop wheel and the tourbillon cage are released by the cam Reuleaux and the second anchor focused on the pendulum.
  • the stop wheel performs a given angular deflection, for example 90 °, before being stopped again by one of the pallets of the second anchor focused on the balance.
  • this pivoting of the stopwheel drives that of the tourbillon cage. .
  • this pivoting also causes the pivoting of the arming ring which is fixed on the cage and also meshes with the seconds wheel, resulting in the re-tensioning of the spiral escapement spring, because the escape wheel is then blocked by the first anchor.
  • the exhaust spring is periodically extended. It thus accumulates enough energy to deliver a sufficient torque to maintain oscillations of the balance.
  • This compensation mechanism is intended to deliver a constant torque.
  • the first end of the spiral escapement spring is fixed on a first pin secured to a first ferrule of exhaust spiral spring connected to the escape wheel.
  • the second end of the spiral escapement spring is fixed on a second pin integral with a second movable spiral escapement spring ferrule.
  • the spiral exhaust spring once tensioned, exerts a force on the first pin, and thus exerts a torque on a first arm that includes the force compensation disk that includes the constant force device.
  • the latter comprises a first and a second arm, arranged to bear respectively on the first and the second pin, and the bearing faces of these arms are aligned with each other but in an off-axis direction relative to the axis of the escape wheel.
  • the second arm presses on the second pin and transmits the torque to the fixed shell spiral spring and the escape wheel.
  • the leverage forces exerted by and on the pins are variable depending on the angular position of the force compensation disk, which ensures a constant torque on the escape wheel, despite the loss of tension of the exhaust spring during the stop of the entire gear train from the spring to the stop wheel.
  • the escape wheel is released from the first anchor, and pivots at an angle, under the action of the spiral spring exhaust, as the first spiral spring ferrule and the disc of force compensation, while the arming ring and the stopwheel are blocked.
  • the stopwheel and the tourbillon cage are released.
  • the patent application EP 1 772 783 in the name of WATCHES BREGUET SA describes a watch movement comprising a constant force device, and a dead-band display on the center wheel, which is capable of driving a vortex under good conditions with the constant-force device. It comprises a mobile of average, which makes a turn in several minutes, and which constitutes the input element of a device with constant force.
  • the output element of this spiral spring device is constituted by a second wheel of average, which meshes with the pinion of seconds, which is secured to a tourbillon cage
  • This second wheel of medium is integral with a star, which releases periodically , in this case once a minute, a stop gear meshed with the mobile input average, which cooperates with the center wheel, which makes a jump per minute. This mechanism minimizes the transmission of shocks between the constant force device and the exhaust.
  • EP 1 528 443 A1 in the name of JOURNE, which describes a device of constant force, to second dead.
  • An energy storage spring tends to rotate a rocker.
  • a pinion of a first second wheel of the movement meshes with a pivotally mounted return on this rocker.
  • This return meshes with the pinion of a second seconds wheel, whose axis is integral with a tourbillon exhaust.
  • the rocker carries a finger, which is arranged to cooperate with a ratchet toothing of a stop wheel which meshes with the first wheel seconds. When the finger is engaged with a radial flank of the ratchet, the gear is stopped and there is no transmission of force between the first wheel seconds and the return.
  • the constant force device provides an advantage, which is to ensure a relatively constant engine torque to the exhaust, but which necessarily represents a large footprint and cost.
  • the invention proposes to provide a more economical alternative of carousel or tourbillon to second dead, using the simplicity of star and whip devices, but reducing shocks, and requiring the less possible additional components, and under the smallest possible volume.
  • said retaining means and said stopping means are arranged so as to make said cage a jump per second.
  • the invention more particularly relates to a mechanism for advancing the jump of a vortex or carousel cage to a second dead.
  • Such a mechanism according to the invention offers the advantage of a great compactness and a reduced number of components.
  • the entire system is integrated into the cage, which frees space in the timepiece for other complications.
  • the invention further relates to a vortex comprising a vortex cage and such a mechanism.
  • the invention also relates to a carousel comprising a carousel cage and such a mechanism.
  • the invention also relates to a timepiece comprising such a mechanism, or such a tourbillon, or such a carousel.
  • the invention relates to the field of watchmaking.
  • It relates more particularly to the field of complicated watches, and more particularly that of the display with a jump, said second dead, or dead minute, or with any other time interval.
  • the mechanism according to the invention is a periodic jump feed mechanism 100 of a display means of a temporal magnitude, in particular of the second, and then called "second dead".
  • the invention is here described in the preferred application where the display means is a cage 10 pivoting about a cage axis, either a tourbillon cage as described and illustrated here, or a carousel cage, that includes the mechanism 100, or a timepiece in which the mechanism 100 is incorporated.
  • the carousel or tourbillon cage 10 is parallel to the axis of a balance-spring, and may in particular, in a particular version, be coaxial with this balance.
  • the cage 10 carries, preferably eccentric, an escape wheel 11 and an exhaust pinion 12, and an anchor 13 which cooperates with said wheel 11 and said balance.
  • escape wheel 11 and the exhaust pinion 12 are coaxial.
  • escape wheel 11 and the exhaust pinion 12 are eccentric with respect to the cage 10.
  • the retaining means 20 and the stop means 30 are carried by the cage 10.
  • the mechanism 100 comprises a constant-force device 40 which periodically and directly co-operates with each other, on the one hand, the retaining means 20 connected by direct mechanical connection to its inlet, and on the other hand the means stop 30 linked by direct mechanical connection to its output, these retaining means 20 having a trajectory interfering with that of these stop means 30, to rotate the cage 10 when the stop means 30 release in movement, in particular in pivotal movement, the retaining means 20, and to stop the cage 10 when the stop means 30 block the retaining means 20.
  • the retaining means 20 are linked by direct mechanical connection to the input of the constant-force device 40, in the embodiment described here this direct mechanical connection is a meshing, but it could equally well be carried out by another mechanical transmission direct, without departing from the invention.
  • direct mechanical connection we mean here both continuous link and synchronous link.
  • the stop means 30 are linked by direct mechanical connection to the output of the constant-force device 40. In the preferred example described here, they are integral with an escape wheel 11 which constitutes this output. They are, in this case, directly related to this output.
  • this constant force device 40 is of the spiral spring type, and will be explained later.
  • the intermediate mechanisms of the prior art are thus freed, which, in particular in the form of an anchor, were interposed between the retaining means connected to one end of the constant force device as a cam on the one hand, and the stop means connected to the other end of the constant force device as a stop wheel to another go.
  • the overpressure of this intermediate is a big advantage of the invention, because it greatly simplifies the mechanism, makes it less expensive, and eliminates the delicate adjustment of an anchor mechanism.
  • the removal of this anchor allows to bring in direct contact the retaining means 20 and the stop means 30, and thus to gain volume at the cage.
  • we will call here "cage volume” the volume of the smallest cylinder circumscribed in this cage 10, and centered on the same axis of pivoting as this cage 10.
  • the mechanism 100 according to the invention is extremely compact, and occupies, including exhaust, less than a third, and in particular less than a quarter of the volume of the cage 10, which leaves room for other complications.
  • the retaining means 20 and the stop means 30 are arranged to make the cage 10 a jump per second.
  • the mechanism according to the invention which is described here for the jump display of a second dead, is applicable to the display of another dead magnitude, minute or other, the calculation of the different gears and wheels being performed in result.
  • the retaining means 20 comprise a whip 21, and the stop means 30 comprise a star 31.
  • This star 31 has a trajectory interfering with that of the whip 21, to rotate the cage 10 when the star 31 releases the whip 21, and stop it otherwise, that is to say when the star 31 blocks the whip 21.
  • the retaining means 20 comprise a retaining device 22, which comprises the whip 21, integral with the input of the constant-force device 40.
  • the stop means 30 comprise a retaining star 31, integral with the output of the constant-force device 40, each tooth 32 of which is arranged to cooperate with this whip 21, and to stop and periodically release this whip 21, according to the angular position of the retaining star 31.
  • the pivoting retaining means 20 are constituted, in the example of the figures, by a retaining device 22 comprising a whip pinion 23, and at least one whip 21, arranged to cooperate with the retaining pin 31: in certain positions , such as that shown on the figure 1 , the whip 21 is kept under tension, resting on a flange 32 of the retaining star 31, until the latter reaches an angular position allowing the release of the whip 21, or the whip arm if the whip 21 is with multiple arms, double arm as visible on the Figures 1 and 3 , or star for example.
  • the whip 21 is pivotally movable about the axis of the whipstock 22, and is an element arranged to perform complete turns. The choice of a constant pivoting solution guarantees a long life of the mechanism, and a catch of the games which is always done in the same direction. The realization is particularly simple and economical.
  • the whip 21 when the whip 21 is released by the tooth 32 of the star 31 which held it stationary, that is to say every second in the case in point, it authorizes the pivoting of the whipstock 22, here a half-turn, until the whip 21 returns to abut on another wing of the retaining star 31. If the whip 21 is single-arm, the whip mobile 22 makes a complete turn. If the whip 21 is multi-arm, the pivoting amplitude is reduced accordingly, for example a half-turn if the whip 21 has two opposing arms.
  • the periodic jump feed mechanism 100 of a carousel cage or a tourbillon cage of a timepiece comprises, pivotally movable relative to a plate, a gear train. motion transmission driven by energy storage means.
  • This transmission train is not shown in the figures, it can take conventionally the form of a second gear axially driving the cage 10, or any other similar configuration.
  • the cage 10 is pivotable about a cage axis, it comprises a point of attachment of a first end of a balance spring spiral, the other end is fixed to a rocker movable pivoting about an axis balancer parallel or confused with this axis of cage.
  • the cage 10 is mounted coaxially with the sprung balance which is constituted by the balance and the spiral balance spring.
  • the cage 10 carries this exhaust mechanism 40 eccentrically.
  • the cage 10 carries this pivoting anchor 13 eccentrically.
  • the exhaust gear 12 meshes directly or indirectly with a second wheel 24.
  • this second wheel 24 is fixed.
  • the axis of the second wheel 24 is preferably merged with the axis of pivoting of the cage 10, which carries the axis of pivoting of the exhaust pinion 12.
  • this exhaust pinion 12 constitutes the only point of contact of the mechanism 100 with this second wheel 24 fixed, and coaxial with the cage 10, that includes the movement or the timepiece , on which or in which is incorporated the mechanism 100.
  • the cage 10 tends to rotate permanently under the action of the motion transmission train.
  • the constant force device 40 cooperates periodically with the retaining means 20 with the stop means 30, so that the cage 10 pivots about the shaft axis by rotation of the exhaust pinion 12 around the second wheel 24 when the stop means 30 pivotally release the retaining means 20.
  • the constant-force device keeps the cage 10 stopped when the stop means 30 block the retaining means 20 .
  • the constant-force device 40 causes the whip 21 to periodically cooperate with the star 31, so that the cage 10 pivots about the cage axis when the star 31 releases the whip 21, and the cage 10 is kept stopped when the star 31 blocks the whip 21.
  • the constant-force device 40 comprises a spiral spring 41 whose first end is connected to the escape wheel 11 which carries the stop means 30 and in particular the star 31, and whose second end is connected to a second escape wheel 42.
  • This second escape wheel 42 meshes with the whip gear 23 secured to the retaining means 20, and in particular the whip 21.
  • the exhaust pinion 12 is preferably integral. and coaxial with the second escape wheel 42.
  • the second escape wheel 42 is coaxial with the caliber 11 escape wheel.
  • the principle of the invention is to constrain the pivoting movement of the cage at a certain period, which is not necessarily determined by the frequency of the oscillator as is usually the case, but which is chosen at a particular rate, for example in the embodiment described below where the cage passes from second to second by marking the second.
  • the cage 10 can not rotate, the driving force reaches the exhaust pinion 12 only.
  • the anchor 13 allows the spring to be cocked spiral 41.
  • the system is constant force, because spiral spring 41 is always armed with the same value.
  • the cage 10 can rotate and thus makes a jump, the release of the whip 21 being instantaneous.
  • the mechanism 100 according to the invention is extremely compact, and occupies, including the exhaust, an angular sector less than a quarter of the volume of the cage 10, which leaves room for other complications.
  • the radial resulting from the axis of pivoting of the cage 10 carrying the axis of pivoting of the anchor 13 is substantially symmetrical to the radial end of the axis of pivoting of the cage 10 bearing the axis of pivoting of the whip 21, with respect to the radial resulting from the axis of pivoting of the cage 10 carrying the axis of pivoting of the exhaust pinion 12 and the star 31.
  • the whip 21 is connected to the inlet of the constant force device 40, by the exhaust pinion 12, the second escape wheel 42, and the whip gear 23.
  • the star 31 is linked to the output of the constant-force device 40, by the caliber 11 escape wheel. The whip 21 and the star 31 cooperate directly with each other without intermediary.
  • the invention relates more particularly to a mechanism 100 for advancing by jumping a vortex or carousel cage to a second dead.
  • the invention also relates to a vortex comprising a vortex cage 10 and such a mechanism 100.
  • the invention also relates to a carousel comprising a carousel cage 10 and such a mechanism 100.
  • the invention also relates to a timepiece comprising such a mechanism 100, or such a tourbillon, or such a carousel.
  • the mechanism according to the invention offers the advantage of a great compactness, a reduced number of components.
  • the entire system is integrated into the cage, which frees space in the timepiece for other complications.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
  • Toys (AREA)
  • Handcart (AREA)
  • Rolling Contact Bearings (AREA)

Claims (20)

  1. Mechanismus (100) zum Periodensprungvorschub eines drehbaren Gestells (10), welches Gestell (10) ein Hemmungsrad (11) und einen Hemmungstrieb (12) sowie einen Anker (13) umfasst, der mit dem Hemmungsrad (11) und mit einer Unruh-Spiralfeder zusammenwirkt, wobei der Mechanismus (100) folgende Elemente umfasst:
    - drehbare Haltemittel (20), die derart beschaffen sind, dass sie mit dem Gestell (10) zusammenwirken, um je nachdem, ob sie drehen oder stillstehen, die Drehung des Gestells (10) zuzulassen oder zu untersagen;
    - drehbare Anhaltmittel (30), die derart beschaffen sind, dass sie mit den Haltemitteln (20) zusammenwirken, um je nach Drehwinkelposition der drehbaren Anhaltmittel (30) die Drehung der Haltemittel (20) zuzulassen oder zu untersagen,
    wo:
    - die Haltemittel (20) und die Anhaltmittel (30) vom Gestell (10) getragen sind;
    - der Mechanismus (100) eine Vorrichtung mit konstanter Kraft (40) umfasst, welche Vorrichtung einerseits die Haltemittel (20), die durch direkte mechanische Verbindung mit einem zur Vorrichtung mit konstanter Kraft (40) gehörigen Eingang verbunden sind, mit andererseits den Anhaltmitteln (30), die durch direkte mechanische Verbindung mit einem zur Vorrichtung mit konstanter Kraft (40) gehörigen Ausgang verbunden sind, periodisch und direkt miteinander zusammenwirken lässt, wobei die Haltemittel (20) eine Bahn aufweisen, die mit derjenigen der Anhaltmittel (30) interferiert, um das Gestell (10) drehen zu lassen, wenn die Anhaltmittel (30) die Haltemittel (20) zum Drehen freigeben, und um das Gestell (10) anzuhalten, wenn die Anhaltmittel (30) die Haltemittel (20) blockieren,
    dadurch gekennzeichnet, dass die Haltemittel (20) eine Peitsche (21) am Eingang der Vorrichtung mit konstanter Kraft (40) umfassen, welche Peitsche (21) derart beschaffen ist, dass sie vollständige Umdrehungen ausführt, und dass die Anhaltmittel (30) einen Stern (31) am Ausgang der Vorrichtung mit konstanter Kraft (40) umfassen, wobei dieser Stern (31) eine Bahn aufweist, die mit derjenigen der Peitsche (21) interferiert, um das Gestell (10) drehen zu lassen, wenn der Stern (31) die Peitsche (21) freigibt, oder um es sonst anzuhalten.
  2. Mechanismus (100) nach vorhergehendem Anspruch, dadurch gekennzeichnet, dass die Haltemittel (20) und die Anhaltmittel (30) derart beschaffen sind, dass sie das Gestell (10) einen Sprung pro Sekunde ausführen lassen.
  3. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Gestell (10) koaxial zur Unruh-Spiralfeder ist.
  4. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Hemmungsrad (11) und der Hemmungstrieb (12) koaxial sind.
  5. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Hemmungsrad (11) und der Hemmungstrieb (12) exzentrisch im Verhältnis zum Gestell (10) sind.
  6. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass dieser Mechanismus (100) ein Bewegungsübertragungs-Räderwerk umfasst, das drehbeweglich im Verhältnis zu einer Werkplatte ist und von Energiespeichermitteln angetrieben wird, und dass das Gestell (10) drehbeweglich um eine Gestell-Achse ist und einen Punkt zum Befestigen eines ersten Endes einer Unruh-Spiralfeder umfasst, deren anderes Ende an einer Unruh befestigt ist, die drehbeweglich um eine Unruhachse ist, die parallel zur Gestell-Achse oder mit dieser Letzteren zusammenfallend ist, wobei das Gestell (10) einerseits einen Hemmungsmechanismus trägt, der ein Hemmungsrad (11) umfasst, das um eine Hemmungsachse dreht, die parallel zur Gestell-Achse sowie zur Achse eines Hemmungstriebs (12) ist, mit dem dieses Hemmungsrad über die Vorrichtung mit konstanter Kraft (40) verbunden ist, und wobei es einen Anker (13) trägt, der um eine Ankerachse, die parallel zur Gestell-Achse ist, dreht und derart beschaffen ist, dass er einerseits mit dem Hemmungsrad (11) und andererseits mit der Unruh zusammenwirkt.
  7. Mechanismus (100) nach vorhergehendem Anspruch, dadurch gekennzeichnet, dass der Hemmungstrieb (12) direkt oder indirekt mit einem Sekundenrad (24) kämmt, und dass das Gestell (10) unter der Einwirkung vom Bewegungsübertragungs-Räderwerk ständig dazu tendiert zu drehen, und dass die Vorrichtung mit konstanter Kraft (40) periodisch die Haltemittel (20) mit den Anhaltmitteln (30) derart zusammenwirken lässt, dass das Gestell (10), durch Drehung des Hemmungstriebs (12) um das Sekundenrad (24), um die Gestell-Achse dreht, wenn die Anhaltmittel (30) die Haltemittel (20) zum Drehen freigeben, und dass das Gestell (10) stillgesetzt ist, wenn die Anhaltmittel (30) die Haltemittel (20) blockieren.
  8. Mechanismus (100) nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass das Gestell (10) den Hemmungsmechanismus (40) in exzentrischer Weise trägt.
  9. Mechanismus (100) nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, dass das Gestell (10) den drehbaren Anker (13) in exzentrischer Weise trägt.
  10. Mechanismus (100) nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass das Hemmungsrad (11) koaxial zum Hemmungstrieb (12) ist.
  11. Mechanismus (100) nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, dass die Vorrichtung mit konstanter Kraft (40) eine Spiralfeder (41) umfasst, deren erstes Ende einen sogenannten Ausgang der Vorrichtung mit konstanter Kraft (40) bildet, welcher Ausgang mit dem die Anhaltmittel (30) tragenden Hemmungsrad (11) verbunden ist, und deren zweites Ende einen sogenannten Eingang der Vorrichtung mit konstanter Kraft (40) bildet, welcher Eingang mit einem zweiten Hemmungsrad (42) verbunden ist, das mit einem Peitschentrieb (23) kämmt, der mit den Haltemitteln (20) fest verbunden ist, wobei der Hemmungstrieb (12) mit dem zweiten Hemmungsrad (42) fest verbunden und koaxial zu diesem Letzteren ist.
  12. Mechanismus (100) nach Anspruch 7, dadurch gekennzeichnet, dass das Sekundenrad (24) koaxial zum Gestell (10) ist.
  13. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Achse der Unruh und die Gestell-Achse zusammenfallend sind.
  14. Mechanismus (100) nach Anspruch 11, dadurch gekennzeichnet, dass das zweite Hemmungsrad (42) koaxial zum Hemmungsrad (11) ist.
  15. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Hemmungstrieb (12) den einzigen Kontaktpunkt des Mechanismus (100) mit einem Sekundenrad (24) bildet, das starr und koaxial zum Gestell (10) ist, das zum Uhrwerk oder zum Zeitmessgerät gehört, auf dem bzw. in dem der Mechanismus (100) eingebaut ist.
  16. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Radiallinie, die aus der die Drehachse des Ankers (13) tragenden Drehachse des Gestells (10) hervorgeht, merklich symmetrisch zur Radiallinie, die aus der die Drehachse der Peitsche (21) tragenden Drehachse des Gestells (10) hervorgeht, im Verhältnis zur Radialen, die aus der die Drehachse des Hemmungstriebs (12) und des Sterns (31) tragenden Drehachse des Gestells (10) hervorgeht, ist.
  17. Mechanismus (100) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass er, inbegriffen Hemmung, weniger als einen Viertel des Umhüllungsvolumen des Gestells (10) des kleinsten Zylinders, der das Gestell (10) umschreibt und auf die gleiche Drehachse ausgerichtet ist wie das Gestell (10), einnimmt.
  18. Tourbillon, das ein Tourbillon-Gestell (10) und einen Mechanismus (100) nach einem der Ansprüche 1 bis 17 umfasst.
  19. Karussell, das ein Karussell-Gestell (10) und einen Mechanismus (100) nach einem der Ansprüche 1 bis 17 umfasst.
  20. Zeitmessgerät, das einen Mechanismus nach einem der Ansprüche 1 bis 17, oder ein Tourbillon nach Anspruch 18, oder ein Karussell nach Anspruch 19 umfasst.
EP11725119.9A 2010-06-17 2011-06-16 Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge Active EP2583143B1 (de)

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EP11725119.9A EP2583143B1 (de) 2010-06-17 2011-06-16 Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge

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EP10166350A EP2397920A1 (de) 2010-06-17 2010-06-17 Mechanismus für springendes Tourbillon-Gestell oder Karussell-Gestell
EP11725119.9A EP2583143B1 (de) 2010-06-17 2011-06-16 Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge
PCT/EP2011/060038 WO2011157797A1 (fr) 2010-06-17 2011-06-16 Mécanisme d'avance par saut périodique d'une cage de tourbillon ou d'une cage de carrousel

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EP2583143A1 EP2583143A1 (de) 2013-04-24
EP2583143B1 true EP2583143B1 (de) 2015-03-25

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EP10166350A Withdrawn EP2397920A1 (de) 2010-06-17 2010-06-17 Mechanismus für springendes Tourbillon-Gestell oder Karussell-Gestell
EP11725119.9A Active EP2583143B1 (de) 2010-06-17 2011-06-16 Mechanismus für den vorschub eines tourbillonkäfigs oder einer karussellkäfigs über regelmässige sprünge

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EP (2) EP2397920A1 (de)
JP (1) JP5551309B2 (de)
CN (1) CN103038712B (de)
HK (1) HK1184238A1 (de)
WO (1) WO2011157797A1 (de)

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EP2397921B1 (de) * 2010-06-17 2017-08-30 Blancpain S.A. Mechanismus für springendes Karussell-Gestell
JP6355102B2 (ja) * 2013-09-04 2018-07-11 セイコーインスツル株式会社 定力装置、ムーブメントおよび機械式時計
JP6143185B2 (ja) * 2013-09-04 2017-06-07 セイコーインスツル株式会社 動作安定機構、ムーブメントおよび機械式時計
CN104570683B (zh) * 2013-10-23 2017-04-19 天津海鸥表业集团有限公司 一种陀飞轮机械手表的定时停秒机构
EP3032349B1 (de) * 2014-12-11 2023-02-22 Blancpain SA. Antriebsmechanismus eines organs, das sich in sprüngen bewegt
EP3032348A1 (de) * 2014-12-11 2016-06-15 Blancpain SA. Antriebsmechanismus eines organs, das sich in sprüngen bewegt
EP3136186B1 (de) * 2015-08-31 2018-11-28 Glashütter Uhrenbetrieb GmbH Mechanisches uhrwerk mit einem einstellbaren tourbillon
EP3136187B1 (de) * 2015-08-31 2018-02-28 Glashütter Uhrenbetrieb GmbH Mechanisches uhrwerk mit einem tourbillon
DE102015122613B4 (de) * 2015-12-22 2020-07-23 Lange Uhren Gmbh Sekundensprungeinrichtung einer Uhr
CN105607459B (zh) * 2016-03-24 2018-07-10 深圳市天洲计时科技有限公司 一种陀飞轮部件与秒齿轴之间的传动结构以及一种手表
JP7485506B2 (ja) * 2018-10-12 2024-05-16 ロレックス・ソシエテ・アノニム 小型時計ムーブメント用の調速装置
EP3770696B1 (de) * 2019-07-23 2021-12-01 Omega SA Anschlagkäfig für uhr mit aufzugstift und anschlagstift
EP3770695B1 (de) * 2019-07-23 2022-01-12 Omega SA Anschlagkäfig für uhr mit käfiganschlagblatt
EP3770693B1 (de) 2019-07-23 2022-08-31 Omega SA Anschlagmechanismus für uhrenkäfig mit anschlagrad
EP3979007A1 (de) 2020-10-02 2022-04-06 Montres Breguet S.A. Armbanduhr mit mechanischem uhrwerk mit kraftsteuerungsmechanismus
EP4002016A1 (de) 2020-11-20 2022-05-25 Montres Breguet S.A. Armbanduhr mit mechanischem uhrwerk mit kraftsteuerungsmechanismus

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TWI727830B (zh) * 2019-07-23 2021-05-11 瑞士商奧米茄公司 包含二彈性停止元件之鐘錶支架停止件
US11586148B2 (en) 2019-07-23 2023-02-21 Omega Sa Horological carriage-stop comprising two resilient stop elements

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EP2583143A1 (de) 2013-04-24
JP2013528812A (ja) 2013-07-11
HK1184238A1 (en) 2014-01-17
EP2397920A1 (de) 2011-12-21
CN103038712B (zh) 2014-09-10
WO2011157797A1 (fr) 2011-12-22
CN103038712A (zh) 2013-04-10
US20130194900A1 (en) 2013-08-01
JP5551309B2 (ja) 2014-07-16
US9052692B2 (en) 2015-06-09

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