EP2181362A2 - Piece d'horlogerie - Google Patents
Piece d'horlogerieInfo
- Publication number
- EP2181362A2 EP2181362A2 EP08783457A EP08783457A EP2181362A2 EP 2181362 A2 EP2181362 A2 EP 2181362A2 EP 08783457 A EP08783457 A EP 08783457A EP 08783457 A EP08783457 A EP 08783457A EP 2181362 A2 EP2181362 A2 EP 2181362A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- differential
- transmission
- coaxial
- supports
- wheel
- 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
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 62
- 230000003472 neutralizing effect Effects 0.000 claims abstract description 3
- 238000006073 displacement reaction Methods 0.000 claims description 16
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000010521 absorption reaction Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000006386 neutralization reaction Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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 parts, 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 displacements angular induced in the transmission train by the movements of said supports around their respective axes.
- a pitch correction mechanism of a sprung-balance adjusting device which is inspired by the double cardan attitude correction devices used in marine chronometers to keep it constantly in position. horizontal.
- 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 transmission gear train, a kinematic link between the two reference mobiles and a kinematic connection between the two transmission mobiles, the gear ratios being equal in all points between these two kinematic links, one of said mobiles of references being integral with the hinge axis of 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 of which the other input is in kinematic connection with the upstream part of the transmission gear train associated with one of said supports, one or several reversing mobiles ns one of said kinematic links to reverse the rotations relative to the two inputs of the differential, whose output is in kinematic connection with the downstream part 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. help of a single differential. Thanks to this feature, the invention is not limited to the sole correction of the attitude of the regulating device, even if this correction is of obvious interest, but offers other possibilities still unknown hitherto.
- 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.
- Figure 1 is a sectional view along the two axes of articulation of a schematic diagram of the first embodiment
- Figure 2 is a sectional view similar to Figure 1 of a second embodiment
- Figure 3 is a sectional view similar to the previous views of a variant of Figure 1
- Figure 4 is a sectional view similar to the previous views of a third embodiment.
- Figure 1 is a very schematic representation of a part of the finishing gear of a timepiece, the wheel seconds to the escape wheel. The large average or center wheel, the average wheel and the barrel, on the one hand and the escapement and the sprung balance, on the other hand have not been represented.
- the timepiece comprises a frame 1 on which a first support frame 2 is pivotally mounted about an axis Ai.
- a first shaft 3 centered on the axis A x 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 corresponding position to that occupied by the opening crossing the first face.
- This pivot 4 is engaged freely in an opening 5 of the frame 1, centered on the axis Ai.
- a second support frame 6 is mounted on the first support frame 2 around a pivot axis A 2 orthogonal to the axis Ai.
- a pivot 7 secured to 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 traversed by the axis Ai.
- the end of a tubular element 8 integral with the face opposite 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 freely in a centered opening on the axis A 2 and formed in the face of the first support frame 2 opposite to 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 Ai, 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 gear of the rotations of the supports 2, 6 relative to the frame. 1.
- the first gear train comprises a first transmission wheel 9 mounted freely around the solid shaft 3. 1 of frame 1 and coaxial with axis Ai.
- This first transmission wheel 9 corresponds to the second wheel of the finishing train and has a pinion 9a intended to mesh with the average wheel (not shown), mounted on the frame 1.
- This first transmission wheel 9 meshes with a second transmission wheel 10 freely mounted in the tubular element 8 centered on 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 integral with 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 shaft 10b of the second wheel of the first energy transmission gear of the exhaust spring motor 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 tubular element 8 centered on the second axis A 2 .
- 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 reference 19 meshes with the return 18 and the second meshes with the pinion 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 an inverter system and this, whatever the number of supports and axes. of articulation, as will be seen in the embodiment of FIG.
- 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 can advantageously carry an indicator needle, as illustrated in particular in Figure 1.
- the rotations generated by the joints between the supports 2, 6 are subjected to identical way by the two gear trains.
- the second reference gear train starting from a wheel 11 secured to 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 Ai, 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 in FIG. 1 it is the rotation of the second reference wheel 12 which is reversed, but it would also be possible to reverse the rotation of the second transmission wheel 10.
- the advantage of the proposed solution is that the energy absorbed by the friction due to the reversing gears is generated by the combined action of the counterweight and the gravity and not subtracted from the energy transmitted from the frame and that this absorption of energy dampens any oscillations of the frames around their respective axes. This absorption also prevents untimely rotation of the frames when the Al axis is substantially vertical. Adjustment of this absorption is therefore possible and desirable.
- this correction device is that the rotations about 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 algebraically. Indeed supposing that two supports rotate in opposite directions about parallel axes, the rotation relative to the frame will be their relative rotation.
- FIG. 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 brackets 6 and 21 being pivotally mounted about two axes combined, but being independent relative to each other.
- the axis Ain 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 about the axes on the transmission of a rotation through a gear transmission gear, distributed on the different supports articulated to each other, on which the invention is based.
- the first gear transmission gear comprises an additional wheel 22 coaxial with the pivot axis A 3 .
- 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 wheel of seconds. It meshes with the wheel 9 'coaxial with the pivot axis Ai, which is here secured to a pinion 9' 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 Have.
- 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 secured to a wheel 11' c which meshes with the wheel 12. All the rest of the mechanism is identical to that of Figure 1 to which we can refer.
- FIG. 3 is a variant of the embodiment of FIG. 1 in which the differential is off-center with respect to the axis A2.
- the sun wheel 13 is no longer coaxial with the pivot axis A 2 of the support frame 6 ', but with the axis of a deflection wheel 26 meshing with the pinion 10 a 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 embodiment illustrated in FIG. 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 Ai. and A 2 . Thanks to 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.
- the members having functions homologous to those of the embodiment of FIG. 1 have the same references accompanied by the sign *.
- supports 2 * and 6 * pivotally mounted about the axes A 1 , respectively A 2 .
- the support 2 * pivots around the tubular element 1a of the frame 1, coaxial with the axis Ai and a pivot 4 * is engaged freely in an opening 5 * of the frame 1 *, centered on the axis Ai.
- 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 Ai, A 2 , while the satellite 17 * meshes with the reference 18 * pivotally mounted on the tubular element l * a of the frame 1 *.
- This reference meshes with a 19 * reference which meshes with a 20 * reference 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 * interacts 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 Ai, 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 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 can be seen in the embodiment illustrated in FIG. 2.
- the differential correction device can be arranged either at the beginning or at the end of the kinematic chain of the second reference wheel, since this reference gear makes it possible to add algebraically the sum of the angular displacements of the supports 2 *, 6 * and that it introduces this value to an input of the correction device to differential whose other input receives the movement of the first transmission train to which is added the movement of the supports 2 *, 6 * that it is necessary to subtract to transmit to the output of the differential only the movement of the first gear first gear train.
- the correction device must be located at the opposite end of the mobile secured to the axis of rotation between two supports.
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Transmission Devices (AREA)
- Retarders (AREA)
- Electric Clocks (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP08783457.8A EP2181362B1 (fr) | 2007-08-29 | 2008-08-25 | Piece d'horlogerie |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07405254A EP2031465A1 (fr) | 2007-08-29 | 2007-08-29 | Pièce d'horlogerie |
EP08783457.8A EP2181362B1 (fr) | 2007-08-29 | 2008-08-25 | Piece d'horlogerie |
PCT/CH2008/000357 WO2009026735A2 (fr) | 2007-08-29 | 2008-08-25 | Piece d'horlogerie |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2181362A2 true EP2181362A2 (fr) | 2010-05-05 |
EP2181362B1 EP2181362B1 (fr) | 2013-11-20 |
Family
ID=39186953
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07405254A Withdrawn EP2031465A1 (fr) | 2007-08-29 | 2007-08-29 | Pièce d'horlogerie |
EP08783457.8A Active EP2181362B1 (fr) | 2007-08-29 | 2008-08-25 | Piece d'horlogerie |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07405254A Withdrawn EP2031465A1 (fr) | 2007-08-29 | 2007-08-29 | Pièce d'horlogerie |
Country Status (4)
Country | Link |
---|---|
EP (2) | EP2031465A1 (fr) |
JP (1) | JP5389805B2 (fr) |
CN (1) | CN101939707B (fr) |
WO (1) | WO2009026735A2 (fr) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2124111B1 (fr) | 2008-04-30 | 2010-11-17 | Cartier Création Studio S.A. | Mécanisme évitant les variations de marche dues à la gravitation sur un dispositif réglant à balancier-spiral et pièce d'horlogerie munie d'un tel mécanisme |
EP2533109B1 (fr) | 2011-06-09 | 2019-03-13 | Cartier International AG | Mécanisme évitant les variations de marche dues à la gravitation sur un dispositif réglant à balancier-spiral et pièce d'horlogerie incorporant ce perfectionnement |
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. |
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 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH189470A (de) * | 1935-04-17 | 1937-02-28 | Frantisek Ing Hejduk | Veränderliches Übersetzungsgetriebe. |
US6548771B1 (en) * | 1999-08-12 | 2003-04-15 | Seiko Instruments Inc. | Multipole attitude detector switch with liquid contact |
ATE406603T1 (de) * | 2004-07-08 | 2008-09-15 | Audemars Piguet Renaud Et Papi | Korrekturmechanismus von einem teller einer regulierungsvorrichtung für ein uhruh-spiralfeder |
EP1708048B1 (fr) * | 2005-03-30 | 2010-06-09 | Montres Breguet S.A. | Montre comportant au moins deux systèmes réglants |
-
2007
- 2007-08-29 EP EP07405254A patent/EP2031465A1/fr not_active Withdrawn
-
2008
- 2008-08-25 WO PCT/CH2008/000357 patent/WO2009026735A2/fr active Application Filing
- 2008-08-25 EP EP08783457.8A patent/EP2181362B1/fr active Active
- 2008-08-25 JP JP2010522155A patent/JP5389805B2/ja active Active
- 2008-08-25 CN CN200880104548.3A patent/CN101939707B/zh active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2009026735A3 * |
Also Published As
Publication number | Publication date |
---|---|
EP2031465A1 (fr) | 2009-03-04 |
WO2009026735A2 (fr) | 2009-03-05 |
JP2010537205A (ja) | 2010-12-02 |
JP5389805B2 (ja) | 2014-01-15 |
CN101939707B (zh) | 2013-06-12 |
WO2009026735A4 (fr) | 2009-07-09 |
EP2181362B1 (fr) | 2013-11-20 |
CN101939707A (zh) | 2011-01-05 |
WO2009026735A3 (fr) | 2009-05-28 |
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