EP2031465A1 - Uhr - Google Patents

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Publication number
EP2031465A1
EP2031465A1 EP07405254A EP07405254A EP2031465A1 EP 2031465 A1 EP2031465 A1 EP 2031465A1 EP 07405254 A EP07405254 A EP 07405254A EP 07405254 A EP07405254 A EP 07405254A EP 2031465 A1 EP2031465 A1 EP 2031465A1
Authority
EP
European Patent Office
Prior art keywords
differential
wheel
mobile
transmission
supports
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.)
Withdrawn
Application number
EP07405254A
Other languages
English (en)
French (fr)
Inventor
Yves Corthesy
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Zenith International SA
Original Assignee
Zenith International 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
Application filed by Zenith International SA filed Critical Zenith International SA
Priority to EP07405254A priority Critical patent/EP2031465A1/de
Priority to EP08783457.8A priority patent/EP2181362B1/de
Priority to CN200880104548.3A priority patent/CN101939707B/zh
Priority to JP2010522155A priority patent/JP5389805B2/ja
Priority to PCT/CH2008/000357 priority patent/WO2009026735A2/fr
Publication of EP2031465A1 publication Critical patent/EP2031465A1/de
Withdrawn legal-status Critical Current

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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
    • 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
    • G04B13/00—Gearwork
    • G04B13/007—Gearwork with differential work

Definitions

  • the present invention relates to a timepiece comprising a frame, a transmission mechanism having a transmission gear train driven from a mobile mounted on the frame, and comprising two upstream portions, respectively downstream, distributed on at least two supports pivotally mounted around two axes of respective joints, one of which is situated between the frame and a support and the other of which is situated between the two supports, a differential correction device for neutralizing the induced angular displacements in the transmission train by the movements of said supports around their respective axes.
  • a differential is a device that occupies space and causes a loss of energy transmitted. Now, in a timepiece, especially when it comes to a wristwatch, both the space and the energy available are reduced.
  • the object of the present invention is to overcome, at least in part, these disadvantages.
  • the subject of the present invention is a timepiece of the type mentioned above in which the differential correction device comprises a reference mobile coaxial with each of said articulation axes, each of which is also coaxial with a mobile gear train transmission, a kinematic connection between the two reference mobiles and a kinematic link between the two transmission mobiles, the gear ratios being equal in all points between these two kinematic links, one of said mobile reference being secured to the hinge axis which it is coaxial and the other being pivotally mounted about the hinge axis of which it is coaxial, a kinematic connection between the other mobile reference and a differential input whose other input is in kinematic connection with the upstream portion of the transmission gear train associated with one of said supports, an inverting mobile in one of said kinematic links for reversing the rotations relative to the two inputs of the differential, the output of which is in kinematic connection with the downstream portion of the transmission train associated with the other of said supports.
  • this correction device it is possible not only to neutralize the movements of the transmission train about two axes of articulation with a single differential, but to neutralize the movements of the transmission train around any number of axes. using a single differential. Thanks to this feature, the invention is not limited to the only correction of the attitude of the regulating device, even if this correction is of obvious interest, but offers other possibilities still unknown so far.
  • an inverter train and a differential with a reversing satellite make it possible to cancel the rotations of the articulations at one time, transmitting at the output only the movement generated by the transmission.
  • the figure 1 is a very schematic representation of a part of the finishing gear of a timepiece, the average wheel to the escape wheel.
  • the large medium or center wheel and the barrel, on the one hand and the escapement and balance sprung, on the other hand were not represented.
  • the timepiece comprises a frame 1 on which a first support frame 2 is pivotally mounted about an axis A 1 .
  • a first shaft 3 centered on the axis A 1 is integral with the frame 1 and is freely engaged in an opening which passes through a first face of the frame 2.
  • a pivot 4 is secured to a second opposite face of the frame 2. This pivot 4 occupies on the second face of the frame 2 a position corresponding to that occupied by the opening passing through the first face.
  • This pivot 4 is engaged freely in an opening 5 of the frame 1, centered on the axis A 1 .
  • a second support frame 6 is mounted on the first support frame 2 around a pivot axis A 2 orthogonal to the axis A 1 .
  • a pivot 7 integral with a first face of the second support frame 6 is freely engaged in an opening centered on the axis A 2 , formed in a face of the first support frame 2 perpendicular to the two opposite faces crossed by the axis A 1 .
  • the end of a tubular element 8 secured to the face opposite to the first face of the support frame 6 and occupying on this opposite face a position corresponding to that occupied by the pivot 7 on the first face, is engaged in an opening centered on the axis A 2 and formed in the face of the first support frame 2 opposite that in which the pivot 7 is engaged.
  • the first gear is that of the transmission of the movement generated by the motor spring housed in the barrel (not shown) and controlled by the associated exhaust the sprung balance (not shown), to which is added the movement of the support frames 2, 6 around the axes A 1 , A 2 .
  • the second gear train is the one that makes it possible to totalize the angular movements generated by the pivoting of the support frames 2, 6 around the axes A 1 , A 2 and constitutes the reference gearing of the rotations of the supports 2, 6 relative to the built 1.
  • the first gear train comprises a first transmission wheel 9 freely mounted around the shaft 3 integral with the frame 1 and coaxial with the axis A 1 .
  • This first transmission wheel 9 corresponds to the average wheel of the finishing train and has a pinion 9a intended to mesh with the center wheel or medium (not shown), mounted on the frame 1.
  • This first transmission wheel 9 meshes with a second transmission wheel 10 mounted around the second pivot axis A 2 of the second support frame 6.
  • this second transmission wheel 10 is integral with a shaft 10b which is pivotally mounted in the tubular element 8 of the second support frame 6. At its end opposite to that secured to the second transmission wheel 10, the shaft 10b carries a pinion 10a.
  • the first wheel 11 of this gear train reference which will be called the first reference wheel 11, is integral with the shaft 3, itself integral with the frame 1.
  • This first reference wheel 11 is also coaxial with the first wheel 9 of the first gear train of transmission of the work train. It meshes with a second reference wheel 12 pivotally mounted about the axis A 2 .
  • the ratio between the transmission wheels 9 and 10 is identical to the ratio between the reference wheels 11 and 12.
  • the wheel 9 of the gear train for transmitting the force of the mainspring to the exhaust is driven in successive steps to the frequency at which the escape wheel releases the energy of the mainspring under the control of the engine. balance-spiral, this regular sequential rotation of the wheel 10 is added to the random rotation of the support frames 2, 6 around the axes A 1 , respectively A 2 .
  • the shaft 10b of the second wheel of the first energy transmission gear train of the exhaust motor spring serves as a pivoting member to a sun gear 13 which constitutes the output of the differential.
  • This planetary wheel meshes with a pinion 14a of a wheel 14, here corresponding to the seconds wheel, meshing with a pinion 15a of a wheel 15 corresponding to the escape wheel.
  • the sun gear 13 carries two satellites 16, 17 meshing with each other, the satellite 16 also meshing with the pinion 10a of the second wheel of the drive gear transmission gear.
  • This pinion 10a constitutes a first input through which the differential is connected to the transmission gear train of the driving force.
  • the second satellite 17 meshes with a return 18 mounted free around the shaft 10b of the second wheel 10 of the first gear.
  • This reference 18 is connected to a pinion 12a of the wheel 12 of the second reference gear train, by two referrals 19, 20 meshing with each other.
  • the axes of these references 19, 20 are integral with the second support frame 6.
  • the first gear 19 meshes with the gear 18 and the second meshes with the gear 12a.
  • references 18, 19, 20 the angular displacements of the support frames 2, 6 around the axes A 1 , A 2 are transmitted to the second satellite 17 and as these references are in odd number, the angular movement transmitted to the second satellite 17 is inverted, which makes it possible to neutralize at the output 13 of the differential, the angular movements induced in the first transmission train by the angular displacements of the support frames 2 and 6.
  • These references 18, 19, 20 therefore constitute reversing mobiles
  • this differential correction device makes it possible to deduce all the movements of the supports 2, 6 using a single differential and a system reverser and this regardless of the number of supports and articulation axes, as will be seen in the embodiment of the figure 2 .
  • the part 6a of the support frame 6, opposite the part 6b with respect to the axis A 2 is designed to form or to carry a counterweight in order to maintain the attitude of the surface 6b carrying the system regulating in a constant position whatever the position of the frame 1.
  • the axis of the seconds wheel 14, carried by the support 6 which is held in a constant position may advantageously carry a pointer, as illustrated in particular in the figure 1 .
  • the rotations generated by the joints between the supports 2, 6 are suffered identically by the two gear trains.
  • the second reference gear train starting from a wheel 11 integral with the frame 1, the rotations of the second reference wheel 12 are only due to the rotation of the supports 2, 6 around the axes A 1 , A 2 .
  • the corrector device must therefore subtract from the rotation of the second transmission wheel 10 the rotations of the second reference wheel 12 to keep only the rotation coming from the first transmission wheel 9.
  • the rotation transmitted by one of the second wheels of the transmission gear train 10 or the reference gear train 12 must be reversed to be subtracted. In the example illustrated by the figure 1 it is the rotation of the second reference wheel 12 which is reversed, but it would be also possible to reverse the rotation of the second transmission wheel 10.
  • this correction device is that the rotations around the axes A 1 , A 2 add up, so that we can have a number of axes of any joint, their total rotations relative to the frame 1 s add up algebraically. Indeed supposing that two supports rotate in opposite directions about parallel axes, the rotation relative to the frame will be their relative rotation.
  • the figure 2 illustrates an embodiment in which three supports 2, 6 and 21 rotate around three axes A 1 , A 2 , A 3 , whose two axes A 2 , A 3 are orthogonal to the axis A 1 , the two supports 6 and 21 being mounted pivoting about two axes combined, but being independent relative to each other.
  • the axis A 1 is not necessarily orthogonal to the axes A 2 , A 3 , but that these axes could be parallel or occupy other angular positions between them, without changing the principle of neutralization.
  • rotations of the supports around the axes on the transmission a rotation through a gear transmission gear, distributed on the different supports articulated to each other, on which the invention is based.
  • the first transmission gear train comprises an additional wheel 22 coaxial with the pivot axis A 2 .
  • This wheel carries a pinion 22a intended to be connected to a driving source, in particular a spring housed in a barrel (not shown).
  • This wheel can be here the big average. It meshes with the wheel 9 'coaxial with the pivot axis A 1 , which is here secured to a pinion 9'a which meshes with the wheel 10.
  • the additional wheel 22 of the first gear transmission gear is coaxial with an additional wheel 23 of the second reference gear train, which is integral with the frame 1 and which meshes with a wheel 11'a coaxial with the pivot axis A 1 .
  • This second wheel 11'a is secured to one end of a shaft 11'b which is pivotally mounted through the support frames 21 and 2, and through the wheel 9 'of the first gear.
  • the shaft 11'b is integral with a wheel 11'c which meshes with the wheel 12. All the rest of the mechanism is identical to that of the figure 1 to which we can refer.
  • the figure 3 is a variant of the embodiment of the figure 1 in which the differential is off-center with respect to the axis A 2 .
  • the sun wheel 13 is no longer coaxial with the axis A 2 of pivoting of the support frame 6 ', but of the axis of a deflection wheel 26 meshing with the pinion 10a integral with the transmission wheel 10 coaxial with the axis A 2 .
  • This reference 26 is integral with a pinion 26a which meshes with the satellite 16 of the differential.
  • the reference 18 is also coaxial with this deflection wheel 26 and more than the axis A 2 . It is in kinematic connection with the pinion 12a of the reference mobile 12 by a single reference 20 secured to the support frame 6 '.
  • the form of execution illustrated by the figure 4 differs from the preceding embodiments essentially in that the differential correction device is mounted on the frame 1 of the timepiece and more on the supports mounted pivoting about the axes A 1 and A 2 . With this arrangement, it is possible to reduce the number of elements mounted on the pivoting supports 2 and 6, so that it is possible to reduce their size and make the device more compact.
  • organs having functions similar to those of the embodiment of the figure 1 have the same references with the sign *.
  • supports 2 * and 6 * pivotally mounted about the axes A 1 , respectively A 2 .
  • the frame 1 * comprises a shaft 3 * coaxial with the axis A 1 and a pivot 4 * freely engaged in an opening 5 * of the frame 1 *, centered on the axis A 1 .
  • One face of the support 6 * comprises a pivot 7 * centered on the axis A 2 by an axial opening of the support 2 * in which this pivot is mounted.
  • the opposite face of the support 6 * comprises a tubular element 8 * whose outer face is engaged in an axial opening of the support 2 *.
  • the face of the support 2 * opposite that carrying the pivot 4 * has an axial opening in which a tubular element 1 * of the frame 1 * is engaged.
  • the two satellites 16 * and 17 * meshing with each other are carried by a planetary mobile 9 * integral with a pinion 9 * for meshing with the upstream portion of the transmission train the movement generated by the motor spring housed in the barrel (not shown) and controlled by the escapement associated with the sprung balance (not shown), of which only the wheel 15 * is shown.
  • the satellite 16 * meshes with a pinion 12 * integral with the reference wheel 12 * of the reference wheel of the pivoting support frames 2 *, 6 * around the axes A 1 , A 2 , while the satellite 17 * meshes with the reference 18 * pivotally mounted on the tubular element 1 * a of the frame 1 *.
  • This return meshes with a 19 * reference which meshes with a reference 20 * both mounted pivoting on the frame 1 *.
  • the reference 20 * meshes with a pinion 13 * a wheel 13 * which is the output of the differential and which is in kinematic connection with the downstream part of the first gear train of the movement generated by the mainspring. This downstream part comprises the second wheel 14 * and the escape wheel 15 * carried by the second support 6 *.
  • This wheel 13 * is coaxial with the first wheel 9 * of the first transmission train and is mounted around the tubular element 1 * integral with the frame 1 *. This wheel 13 * meshes with the third wheel 10 * of the first transmission train, whose pinion 10 * meshes directly with the pinion 14 * a of the seconds wheel 14 *.
  • the reference wheel 12 * integral with the pinion 12 * has the reference wheel of the rotation of the supports 2 *, 6 * around the axes A 1 , A 2 relative to the frame 1 *, it meshes with the reference wheel 11 * which is secured to the second support 6 * and no longer the frame as in the embodiment of the figure 1 .
  • the principle of deducing the angular displacements generated by the rotation of the supports 2 * and 6 * around the axes A 1 , A 2 is the same as in the previous embodiments.
  • the differential device with the inverters makes it possible to deduce the movements resulting from the rotation of the supports 2 *, 6 * of the transmission of the movement generated by the mainspring regardless of the number of pivot axes and the number of supports, as we have seen in the form of execution illustrated by the figure 2 .
  • the correction device must be located at the opposite end of the mobile secured to the axis of rotation between two supports.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
  • General Details Of Gearings (AREA)
  • Electric Clocks (AREA)
EP07405254A 2007-08-29 2007-08-29 Uhr Withdrawn EP2031465A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP07405254A EP2031465A1 (de) 2007-08-29 2007-08-29 Uhr
EP08783457.8A EP2181362B1 (de) 2007-08-29 2008-08-25 Uhr
CN200880104548.3A CN101939707B (zh) 2007-08-29 2008-08-25 计时器
JP2010522155A JP5389805B2 (ja) 2007-08-29 2008-08-25 時計
PCT/CH2008/000357 WO2009026735A2 (fr) 2007-08-29 2008-08-25 Piece d'horlogerie

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07405254A EP2031465A1 (de) 2007-08-29 2007-08-29 Uhr

Publications (1)

Publication Number Publication Date
EP2031465A1 true EP2031465A1 (de) 2009-03-04

Family

ID=39186953

Family Applications (2)

Application Number Title Priority Date Filing Date
EP07405254A Withdrawn EP2031465A1 (de) 2007-08-29 2007-08-29 Uhr
EP08783457.8A Active EP2181362B1 (de) 2007-08-29 2008-08-25 Uhr

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP08783457.8A Active EP2181362B1 (de) 2007-08-29 2008-08-25 Uhr

Country Status (4)

Country Link
EP (2) EP2031465A1 (de)
JP (1) JP5389805B2 (de)
CN (1) CN101939707B (de)
WO (1) WO2009026735A2 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2124111A1 (de) * 2008-04-30 2009-11-25 Cartier Création Studio S.A. Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr
EP2533109A1 (de) 2011-06-09 2012-12-12 Cartier Création Studio S.A. Mechanismus zur Vermeidung der schwerkraftbedingten Gangvariationen auf einer Reguliervorrichtung mit Spiralunruh, und mit dieser Perfektionierung ausgestattete Uhr
WO2013004782A1 (fr) 2011-07-07 2013-01-10 Gfpi S.A. Piece d'horlogerie

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH705836B1 (fr) * 2011-12-02 2016-01-15 Lvmh Swiss Mft Sa Pièce d'horlogerie.
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

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH189470A (de) * 1935-04-17 1937-02-28 Frantisek Ing Hejduk Veränderliches Übersetzungsgetriebe.
EP1615085A1 (de) * 2004-07-08 2006-01-11 Audemars Piguet (Renaud et Papi) SA Korrekturmechanismus von einem Teller einer Regulierungsvorrichtung für ein Uhruh-Spiralfeder

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6548771B1 (en) * 1999-08-12 2003-04-15 Seiko Instruments Inc. Multipole attitude detector switch with liquid contact
DE602005021748D1 (de) * 2005-03-30 2010-07-22 Montres Breguet Sa Uhr mit mindenstens zwei Reguliersystemen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH189470A (de) * 1935-04-17 1937-02-28 Frantisek Ing Hejduk Veränderliches Übersetzungsgetriebe.
EP1615085A1 (de) * 2004-07-08 2006-01-11 Audemars Piguet (Renaud et Papi) SA Korrekturmechanismus von einem Teller einer Regulierungsvorrichtung für ein Uhruh-Spiralfeder

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2124111A1 (de) * 2008-04-30 2009-11-25 Cartier Création Studio S.A. Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr
EP2533109A1 (de) 2011-06-09 2012-12-12 Cartier Création Studio S.A. Mechanismus zur Vermeidung der schwerkraftbedingten Gangvariationen auf einer Reguliervorrichtung mit Spiralunruh, und mit dieser Perfektionierung ausgestattete Uhr
WO2012168773A1 (fr) 2011-06-09 2012-12-13 Cartier Creation Studio S.A. Mecanisme evitant les variations de marche dues a la gravitation sur un dispositif reglant a balancier-spiral et piece d'horlogerie incorporant ce perfectionnement
CN103797426A (zh) * 2011-06-09 2014-05-14 卡迪亚创造工作室股份公司 防止由重力作用于摆轮游丝调节装置上而导致速率变化的机构以及结合该改进的钟表
US9134702B2 (en) 2011-06-09 2015-09-15 Cartier Creation Studio S.A. Mechanism preventing rate variations caused by gravity on a balance-spring regulating device and timepiece incorporating this improvement
CN103797426B (zh) * 2011-06-09 2016-10-05 卡地亚国际有限公司 防止由重力作用于摆轮游丝调节装置上而导致速率变化的机构以及结合该改进的钟表
WO2013004782A1 (fr) 2011-07-07 2013-01-10 Gfpi S.A. Piece d'horlogerie
CH705244A1 (fr) * 2011-07-07 2013-01-15 Gfpi S A Pièce d'horlogerie
US8956041B2 (en) 2011-07-07 2015-02-17 Gfpi S.A. Timepiece with tourbillon mechanism having a support

Also Published As

Publication number Publication date
WO2009026735A2 (fr) 2009-03-05
WO2009026735A3 (fr) 2009-05-28
CN101939707A (zh) 2011-01-05
WO2009026735A4 (fr) 2009-07-09
JP2010537205A (ja) 2010-12-02
JP5389805B2 (ja) 2014-01-15
EP2181362B1 (de) 2013-11-20
CN101939707B (zh) 2013-06-12
EP2181362A2 (de) 2010-05-05

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