EP2397921A1 - Mechanismus für springendes Karussell-Gestell - Google Patents

Mechanismus für springendes Karussell-Gestell Download PDF

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Publication number
EP2397921A1
EP2397921A1 EP10166367A EP10166367A EP2397921A1 EP 2397921 A1 EP2397921 A1 EP 2397921A1 EP 10166367 A EP10166367 A EP 10166367A EP 10166367 A EP10166367 A EP 10166367A EP 2397921 A1 EP2397921 A1 EP 2397921A1
Authority
EP
European Patent Office
Prior art keywords
cage
teeth
gear
wheel
star
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10166367A
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English (en)
French (fr)
Other versions
EP2397921B1 (de
Inventor
Marco Rochat
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.)
Blancpain SA
Original Assignee
Blancpain SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to EP10166367.2A priority Critical patent/EP2397921B1/de
Application filed by Blancpain SA filed Critical Blancpain SA
Priority to US13/702,192 priority patent/US9058020B2/en
Priority to PCT/EP2011/059349 priority patent/WO2011157591A1/fr
Priority to EP11725048.0A priority patent/EP2583142B1/de
Priority to CN201180029768.6A priority patent/CN103038711B/zh
Priority to JP2013514635A priority patent/JP5425340B2/ja
Publication of EP2397921A1 publication Critical patent/EP2397921A1/de
Priority to HK13111450.5A priority patent/HK1183944A1/xx
Application granted granted Critical
Publication of EP2397921B1 publication Critical patent/EP2397921B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • G04B15/00—Escapements
    • G04B15/12—Adjusting; Restricting the amplitude of the lever or the like
    • 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

Definitions

  • the invention relates to a skip advance mechanism of a second dead carousel cage.
  • the invention also relates to a carousel comprising a carousel cage and such a mechanism.
  • the invention relates to the field of watchmaking.
  • 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 secured in rotation an armature ring of the exhaust spring, and a ring gear associated with it and cooperating 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 lever arms of the 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 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 meshing with the average input moving, which cooperates with the center wheel, which thus makes a jump per minute. This mechanism minimizes the transmission of shocks between the constant force device and the exhaust.
  • 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 economic alternative carousel second dead, using the simplicity of star and whip devices, but reducing shocks, and requiring the least possible additional components, and in the smallest possible volume .
  • said stop means comprise a star integral with a permanently driven star gear, and in that said retaining means comprise a whip secured to a whip gear meshing directly or indirectly. with said cage, the trajectory of said whip interfering with that of said star, to rotate said cage when said star releases said whip, and stop it otherwise.
  • said star gear is permanently driven by a star drive train which is connected to said motion transmission train, directly or via said exhaust pinion.
  • said retaining means and said stop means are arranged so as to make said cage one jump per second.
  • the invention relates to a skip advance mechanism of a second dead carousel cage.
  • This new achievement is distinguished by its simplicity, the low number and low cost of additional components, and their very small footprint.
  • 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.
  • the motion transmission train 20 is arranged to permanently pivot the exhaust pinion 41 and the cage 30 when the latter is free to rotate.
  • 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 the case usually, 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 retaining means 70 have a trajectory interfering with that of the stop means 60.
  • the retaining means and the stop means 60 are arranged outside the cage 30, that is to say that they are not worn by the cage 30.
  • the motion transmission train 20 meshes permanently with the exhaust gear 41 to rotate it about an exhaust axis carried by the cage 30, and it tends to drive the cage 30 to pivot about the axis of cage through the exhaust shaft.
  • the cage 30 constantly pushes, under the action of the motion transmission train 20, the retaining means 70 against the stop means 60, to rotate the cage 30 when the means of stop 60 release, in particular pivoting, the retaining means 70, and to stop the cage 30 when the stop means 60 block these retaining means 70.
  • the input drive means 10 is conventionally arranged to receive energy in the form of a torque transmitted by energy storage means such as barrel, weight, or the like.
  • this input drive means 10 is a wheel of medium 11, which performs one revolution per hour, and comprises N1 teeth, for example here 96 teeth.
  • This medium wheel 11 rotates continuously, as long as the energy storage means are able to deliver energy to the mechanism.
  • the motion transmission train 20 is of very variable composition. It comprises here a pinion of average 21 and a wheel of average 22, respectively of N2 and N3 teeth, in Example 8 and 90 teeth.
  • the average gear 21 meshes with the medium wheel 11.
  • This retaining star 65 therefore rotates continuously under the action
  • This second gear 23 is secured to a second wheel 24 having N9 teeth.
  • This second wheel 24 meshes classically with an exhaust pinion 41 having N10 teeth.
  • the cage 30 is preferably a carousel cage, as visible in the figures and has a toothing 31 with N7 teeth, and is pivotable about a cage axis.
  • This cage 30 comprises a point of attachment of a first end of a balance spring balance 82 whose other end is fixed to a rocker 81 pivotally movable, preferably around this shaft axis, in the latter case the cage 30 is thus mounted coaxial with the sprung balance 80 which is constituted by the balance 81 and the spiral balance spring 82.
  • the pivot axis of the second wheel 24 coincides with the axis of pivoting of the cage 30 which carries the axis of pivoting of the escape gear 41.
  • the pivoting of the second wheel 24 therefore tends to always lead to a pivoting of the cage 30 in the same direction as that of the second wheel 24, here in the clockwise direction. Therefore, if an obstacle prevents the pivoting of the cage 30, only the pivoting movement of the exhaust pinion 41 about its axis takes place, the regulation of the oscillator is never interrupted. If we release the pivoting of the cage 30 by removing the obstacle, both the cage 30 pivots in the same direction as the second wheel 24, and the exhaust pinion 41 pivots about its axis in the same way as in the previous case.
  • the retaining means 70 are arranged to cooperate with the cage 30 for, depending on whether they are in motion or are at a standstill, allow or prohibit the pivoting of the cage 30; in the present embodiment, they comprise a retaining mobile 77.
  • This retaining mobile 77 comprises a wheel or a pinion meshing with the toothing 31 that includes the cage 30.
  • the stop means 60 are arranged to cooperate with these retaining means 70, for, according to the angular position of pivoting of these stop means 60 when they are pivoting, allow or prohibit the pivoting of the retaining means 70.
  • these stop means 60 comprise a retaining star 65, integral with a star pinion 64, as described above, permanently pivoted and each tooth 66 is arranged to cooperate with this whip 76, and stop and periodically release the whip 76, according to the angular position of the retaining star 65.
  • This drive of the star gear 64 can be performed, preferably as visible in the present embodiment, by the transmission train 20, directly or via the exhaust pinion 41.
  • the pivoting retaining means 70 consist, in the example of the figures, of a whipstock 74 comprising a whip pin 75 comprising N14 teeth, and which carries at least one whip 76, able to pivot about the axis of the whip.
  • movable whip 74 and arranged to cooperate with a retaining star 65.
  • the trajectory of the whip 76 interferes with that of the star 65, to rotate the cage 30 when the star 65 releases the whip 76, and stop it otherwise .
  • the whip gear 75 meshes directly or indirectly with the toothing 31 of the cage 30.
  • the whip 76 is kept under tension, resting on a flange 66 of the retaining star 65, until it reaches an angular position allowing the release of the whip 76, or the whip arm if the whip 76 is with multiple arms, double arm or star for example.
  • the retaining mobile 77 comprises an inverting mobile 71 in engagement with the toothing 31 on the one hand, this inverting mobile 71 consisting of an inverter gear 72 meshing with the wheel 31, and an inverter wheel 73 integral with this pinion inverter 72, and with the whipstock 74 on the other hand.
  • the whipless gear 75 meshes with the reversing wheel 73.
  • the whip gear 75 then co-operates with the toothing 31 of the cage 30 via the inverting mobile 71.
  • the whip 76 when the whip 76 is released by the tooth 66 of the star 65 which held it stationary, that is to say every second in the case in point, it authorizes the pivoting of the whipstock 74, here a complete revolution, until the whip 76 returns to abutment on another wing of the retaining star 65. If the whip 76 is multi-arm, the pivoting amplitude is reduced accordingly, by example a half-turn if the whip 76 has two opposing arms as in the example of the figure 3 .
  • the inverting mobile 72 makes it possible to rotate the whipstock 74 in the same direction as the cage 30.
  • This design is advantageous because it makes it easy to choose the size that you want to display with a jump, whether it is for example the fifth of a second, the ten seconds, the minute, or other, by a simple judicious calculation of the train. It also allows a derivative design with a cage turn in a duration other than a minute, for example in thirty seconds.
  • the gear examples presented here correspond to a frequency of the oscillator of 3 Hz, with a cage 30 equipped with a gear 31 of 180 teeth, and rotating in one minute.
  • the figures 2 and 3 illustrate a second embodiment, without an inverting gear, and with a whip with two whip arms, the whipstock 74 then makes a U-turn before a whip arm returns to bear on a wing 66 of the star 65.
  • the figure 3 illustrates the very small dimension of the star 65 and the whipstock 74 relative to the gear train and to the cage 30.
  • the gear train 20 is identical to that of the figure 1 as well as the exhaust mechanism 40.
  • this variant embodiment does not include an inverting mobile 71, the whipstock 74 comes into direct contact with the toothing 31 of the cage 30.
  • the period T is identical to that of the figure 1 .
  • the invention relates more particularly to a mechanism 100 for advance by jumping a carousel cage to a second dead.
  • 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 carousel.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
  • Gear Transmission (AREA)
EP10166367.2A 2010-06-17 2010-06-17 Mechanismus für springendes Karussell-Gestell Not-in-force EP2397921B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP10166367.2A EP2397921B1 (de) 2010-06-17 2010-06-17 Mechanismus für springendes Karussell-Gestell
PCT/EP2011/059349 WO2011157591A1 (fr) 2010-06-17 2011-06-07 Mécanisme d'avance par saut périodique d'une cage de carrousel
EP11725048.0A EP2583142B1 (de) 2010-06-17 2011-06-07 Mechanismus für den vorschub eines karussellkäfigs über regelmässige sprünge
CN201180029768.6A CN103038711B (zh) 2010-06-17 2011-06-07 通过周期性跳变推进卡罗素框架的机构
US13/702,192 US9058020B2 (en) 2010-06-17 2011-06-07 Mechanism for advancing a karussel cage by periodic jumps
JP2013514635A JP5425340B2 (ja) 2010-06-17 2011-06-07 周期的ジャンプによりカルーセルキャリッジを前進させるための機構
HK13111450.5A HK1183944A1 (en) 2010-06-17 2013-10-10 Mechanism for advancing a karrusel cage by periodic jumps

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10166367.2A EP2397921B1 (de) 2010-06-17 2010-06-17 Mechanismus für springendes Karussell-Gestell

Publications (2)

Publication Number Publication Date
EP2397921A1 true EP2397921A1 (de) 2011-12-21
EP2397921B1 EP2397921B1 (de) 2017-08-30

Family

ID=43086699

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10166367.2A Not-in-force EP2397921B1 (de) 2010-06-17 2010-06-17 Mechanismus für springendes Karussell-Gestell
EP11725048.0A Active EP2583142B1 (de) 2010-06-17 2011-06-07 Mechanismus für den vorschub eines karussellkäfigs über regelmässige sprünge

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP11725048.0A Active EP2583142B1 (de) 2010-06-17 2011-06-07 Mechanismus für den vorschub eines karussellkäfigs über regelmässige sprünge

Country Status (6)

Country Link
US (1) US9058020B2 (de)
EP (2) EP2397921B1 (de)
JP (1) JP5425340B2 (de)
CN (1) CN103038711B (de)
HK (1) HK1183944A1 (de)
WO (1) WO2011157591A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105319942A (zh) * 2014-06-19 2016-02-10 钟表制作有限公司 用于时计的倾斜联接装置

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2397920A1 (de) * 2010-06-17 2011-12-21 Blancpain S.A. Mechanismus für springendes Tourbillon-Gestell oder Karussell-Gestell
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
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
CH712973B1 (de) * 2016-09-23 2023-12-29 Bucherer Ag Tourbillon und Uhr mit Tourbillon.
USD879623S1 (en) * 2018-03-20 2020-03-31 Lvmh Swiss Manufactures Sa Watch
EP3599517B1 (de) 2018-07-24 2021-03-10 Harry Winston SA Retrogrades tourbillon oder karussell eines uhrwerks
EP3599515B1 (de) * 2018-07-24 2022-07-06 Harry Winston SA Antriebsmechanismus für uhrwerk
EP3770696B1 (de) * 2019-07-23 2021-12-01 Omega SA Anschlagkäfig für uhr mit aufzugstift und anschlagstift
EP3979007A1 (de) * 2020-10-02 2022-04-06 Montres Breguet S.A. Armbanduhr mit mechanischem uhrwerk mit kraftsteuerungsmechanismus

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH47297A (fr) 1909-06-07 1910-06-16 Pellaton Schild A Mécanisme perfectionné de seconde morte aux pièces d'horlogerie
EP1319997A1 (de) 2001-12-15 2003-06-18 Richemont International S.A. Konstantkraftvorrichtung
EP1528443A1 (de) * 2003-10-28 2005-05-04 Francois-Paul Journe Konstantkraftvorrichtung für eine Uhr
EP1772783A1 (de) 2005-10-10 2007-04-11 Montres Breguet S.A. Uhrwerkvorrichtung mit konstanter Kraft

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4092846B2 (ja) * 2000-03-14 2008-05-28 いすゞ自動車株式会社 車両の変速装置
CH699813B1 (fr) * 2004-03-25 2010-05-14 Pierre Kunz S A Roue destinée à venir en contact avec un élément mobile ou fixe et son procédé de fabrication.
EP2175327A1 (de) * 2005-07-13 2010-04-14 Les Artisans Horlogers Sàrl Uhr
DE602006007807D1 (de) * 2006-04-07 2009-08-27 Eta Sa Mft Horlogere Suisse Mechanischer Wechsler zum Drehantreiben eines Rades aus einer einzelnen Richtung
EP2315081B1 (de) * 2009-10-26 2012-08-29 Blancpain S.A. Tourbillon und Uhrwerk, das mit einem Tourbillon ausgestattet ist
EP2397920A1 (de) * 2010-06-17 2011-12-21 Blancpain S.A. Mechanismus für springendes Tourbillon-Gestell oder Karussell-Gestell

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH47297A (fr) 1909-06-07 1910-06-16 Pellaton Schild A Mécanisme perfectionné de seconde morte aux pièces d'horlogerie
EP1319997A1 (de) 2001-12-15 2003-06-18 Richemont International S.A. Konstantkraftvorrichtung
EP1528443A1 (de) * 2003-10-28 2005-05-04 Francois-Paul Journe Konstantkraftvorrichtung für eine Uhr
EP1772783A1 (de) 2005-10-10 2007-04-11 Montres Breguet S.A. Uhrwerkvorrichtung mit konstanter Kraft

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105319942A (zh) * 2014-06-19 2016-02-10 钟表制作有限公司 用于时计的倾斜联接装置
CN105319942B (zh) * 2014-06-19 2019-03-26 钟表制作有限公司 用于时计的倾斜联接装置

Also Published As

Publication number Publication date
JP2013532282A (ja) 2013-08-15
EP2397921B1 (de) 2017-08-30
US9058020B2 (en) 2015-06-16
EP2583142A1 (de) 2013-04-24
JP5425340B2 (ja) 2014-02-26
WO2011157591A1 (fr) 2011-12-22
CN103038711A (zh) 2013-04-10
US20130155820A1 (en) 2013-06-20
EP2583142B1 (de) 2015-01-07
HK1183944A1 (en) 2014-01-10
CN103038711B (zh) 2014-09-10

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