EP2701013A1 - Uhrwerk mit erweiterter Gangreserve - Google Patents

Uhrwerk mit erweiterter Gangreserve Download PDF

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Publication number
EP2701013A1
EP2701013A1 EP12181455.2A EP12181455A EP2701013A1 EP 2701013 A1 EP2701013 A1 EP 2701013A1 EP 12181455 A EP12181455 A EP 12181455A EP 2701013 A1 EP2701013 A1 EP 2701013A1
Authority
EP
European Patent Office
Prior art keywords
barrel
torque
movement
watch
gear
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
EP12181455.2A
Other languages
English (en)
French (fr)
Other versions
EP2701013B1 (de
Inventor
Sylvain Cornibé
Eddy Valladon
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.)
Audemars Piguet Renaud et Papi SA
Original Assignee
Audemars Piguet Renaud et Papi 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 Audemars Piguet Renaud et Papi SA filed Critical Audemars Piguet Renaud et Papi SA
Priority to ES12181455T priority Critical patent/ES2744586T3/es
Priority to EP12181455.2A priority patent/EP2701013B1/de
Priority to US13/973,067 priority patent/US8956042B2/en
Priority to JP2013171910A priority patent/JP6180231B2/ja
Priority to CN201310371611.2A priority patent/CN103631126B/zh
Publication of EP2701013A1 publication Critical patent/EP2701013A1/de
Application granted granted Critical
Publication of EP2701013B1 publication Critical patent/EP2701013B1/de
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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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/16—Barrels; Arbors; Barrel axles
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/22—Compensation of changes in the motive power of the mainspring
    • 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
    • G04B9/00—Supervision of the state of winding, e.g. indicating the amount of winding

Definitions

  • the present invention relates to a watch movement with extended power reserve, for example mounted in a mechanical watch.
  • the invention aims to equip mechanical watches, for example wristwatches, chronographs and other watches, automatic or manual winding, preferably of high standing, a system that allows to double or even to further extend the duration of the power reserve.
  • the energy source for driving the wheel and the hands, including the date display is a spiral spring wound in a barrel.
  • European patent application no. EP 11188982.0 ( 2'455'820 ) proposes the use of a motor member comprising a barrel in which are mounted two superposed and coaxial springs.
  • the state of the art remains silent concerning an examination of the torque distribution in a watch movement, namely that we have not yet tried to find out where the different energy demands are in the movement.
  • the proprietor posed as an object the analysis of the couple, from the barrel to the needles.
  • the main object of the invention is a watch movement for a mechanical watch whose reserve is considerably extended, and a method for determining an increased power reserve.
  • the invention relates to a mechanical watch incorporating such a movement.
  • the invention further aims to allow the user of the watch to manually change the operating state between normal operation and operation with the extended reserve. It is also envisaged that the current state (normal reserve - extended reserve) is indicated by the watch. In addition, the extended reserve operating mode must not disturb the time base.
  • the present invention makes it possible to attain the objects targeted; the extended power reserve movement is defined in claim 1 while the method for providing such an increased reserve is the subject of independent claim 11.
  • the definition of mechanical watch is in the third independent claim 16.
  • the chronometric performances of a watch are improved when the oscillator stores a lot of energy: this makes it less sensitive to disturbances.
  • the licensee first undertook extensive research to determine the distribution of couples in a watch movement.
  • the various components of the gear train as well as the drive of the time and date display device have been scrutinized in detail to determine the locations of maximum energy consumption. It has been found that, apart from the date gear, the pendulum requires the most energy. This is conceived because the rocker must be accelerated from a stop position and against the force of a spiral spring, then it must be stopped (when the force applied is neutralized by the force of the spring), and then it returns to its position. initial position where it will be stopped again to operate the exhaust.
  • the decrease in the energy demand of a watch movement is obtained, according to the invention, by a decrease in the oscillation angle (amplitude) of the balance.
  • This reduction can be obtained, according to a particular embodiment of the invention, by changing the speed ratio at the center barrel gear. Increasing this ratio decreases the torque on the wheel of the exhaust, and the amplitude of the balance is lowered in favor of the power reserve.
  • the Fig. 1 is a diagram that shows the relationship between the torque in g ⁇ mm on the wheel of medium, provided by the barrel, and the running hours of the watch movement after a winding of the watch spring.
  • the ordinate of the diagram also shows the angle of oscillation of the balance in degrees.
  • the torque supplied is then 112 g ⁇ mm (CPL ini curve) and the amplitude of the balance is 240 ° (curve A ini); the watch stops after 90 hours of walking.
  • CPL ini curve CPL ini curve
  • GM medium wheel
  • the torque then falls to 75 g ⁇ mm and the amplitude of the pendulum to 205 ° ; the march already lasts 135 hours.
  • the torque needed to drive a perpetual calendar (QP) is 3.05 g ⁇ mm.
  • the available torque for the entire power reserve is greater than 10 g ⁇ mm.
  • Torque measurements were made using a Variocouple instrument from CSA Instruments S.A., Peseux, Switzerland.
  • the proposed mechanism carries the power reserve of a watch to a week or more, it would result in a delay of a few minutes at most.
  • the user would find his watch in working order, calendar indications up to date, and only have to make a correction of the hour of a few minutes, a much simpler procedure than updating a QP.
  • the Fig. 2A first shows the principle of the normal mode of a classic gear of a watch movement.
  • Ratchet 10 is distinguished with its shaft 19 which passes through the cylinder 12.
  • the output shaft 14 of the cylinder supports a satellite 17 of a planetary gear train 20 composed of a ring gear 11, a central gear (sun gear) 18 and several satellites 17 of which only one is shown.
  • the shaft of the central gear is fixed relative to the movement by the attachment 15, and the output 16 of the gear is constituted by the ring 11.
  • the low power mode is represented at the Fig. 2B .
  • the pieces are the same as those of the Fig. 2A , and their reference signs are increased by 100; for example, ratchet 10 at the Fig. 2A is the ratchet 110 at the Fig. 2B .
  • the ring 120 is blocked by the attachment 115, and the satellite 117 transmits its force directly to the central wheel 118 whose shaft forms the output 116.
  • the gear a reduction in the ratio between the barrel and the wheel of great average between 1.25 and 5 according to the number of teeth of the meshing wheels. This change of ratio has the effect of multiplying the output speed, thus a decrease in the torque transmitted to the balance.
  • FIG. fig.3 A second main mode for changing the torque provided by the watch spring is shown in FIG. fig.3 .
  • the barrel 30 carries two wheels, a relatively small wheel 32 on its upper face, and a relatively large wheel 34 on its lower surface, the planes of the two wheels being parallel.
  • the wheels 32 and 34 can mesh alternately in two center wheels 36 or 40, respectively, which are both fixed on a common shaft 38 and whose vertical spacing is a little larger than the vertical distance of the two gears. 32 and 34 of the barrel. This shaft 38 can be moved vertically according to the arrow 42.
  • the small wheel 32 In the normal mode, the small wheel 32 is engaged with the large center wheel 36.
  • the movable assembly 36, 38, 40 is raised according to the arrow 42, the large center wheel 36 comes out of engagement, and the small Center wheel 40 meshes with large barrel wheel 34.
  • the multiplication ratio 32/36 then becomes a 34/40 multiplication ratio which is higher and has the effect of longer duration of the power reserve. .
  • the Fig. 3 is only schematic. Any other relationship between the four wheels concerned will be possible.
  • the Fig. 4A and 4B show a third main embodiment for changing the torque provided by the watch spring.
  • the gears in play are reproduced quite schematically.
  • a barrel 52 has on its upper part a toothing 50 which is able to transmit a movement via the wheel 61 which is integral with an axis 62, the center mobile (not shown).
  • a planet gear consisting of a ring gear 54, satellites 56 (only one of which is shown) and a sun gear 58 is inserted between the cylinder 52 and the toothing 50.
  • the toothing 50 of the barrel and the sun gear 58 are integral, the ring 54 of the cylinder is secured to the cylinder 52, and the satellite 56 pivots on an axis 64 secured to the cylinder 52.
  • the satellite 56 can not rotate around its axis of rotation. Therefore, everything happens as if the elements 54, 56 and 58 were integral, and they all rotate at the same speed as the barrel 52.
  • the planetary gear is then completely transparent.
  • the toothing 50 of the barrel 52 thus rotates also at the same speed as that of the barrel.
  • the Fig. 4B shows a scheme of operation in low power mode and is based on the Fig. 4A .
  • the ring 54 is blocked which is symbolized by the stud 55.
  • the ring 54 of the barrel 52 is no longer secured to the barrel 52 but fixed (to a bridge or platinum).
  • the barrel unwinds, it forces the satellite 56 to roll on the ring of the barrel 54.
  • the satellite 56 will rotate the sun gear 58 at a higher rotational speed than the barrel 52, according to the size of the planetary gear.
  • the multiplier speed ratio of the sun gear will therefore increase the power reserve and reduce by the same torque transmitted to the center mobile.
  • the Fig. 5A and 5B illustrate a practical embodiment of the third main mode for changing the torque provided by the watch spring.
  • the gears in play are represented only schematically.
  • Fig. 5A shows the operation of the watch movement in normal mode. Certain elements, familiar to the person skilled in the art, are not represented, such as the cylinder 52 (see Fig. 4 ) and its teeth 50.
  • the ring of the cylinder 54 has a triangular toothing on its largest diameter. This toothing will work with the pawls 68.
  • the axes of rotation of the pawls 68 and satellites 56 are integral with the barrel.
  • the ring of the barrel 54 is pivotally connected relative to the barrel.
  • the center mobile not shown, performs a turn in one hour.
  • the pawls 68, the ring of the cylinder 54 and the satellites 56 are stationary relative to the cylinder 52.
  • the planetary gear becomes transparent, the ring 54 also rotates at the same angular speed as the cylinder 52.
  • the locking time of the ring 54 on the barrel via the pawls is very small: it corresponds to a relative displacement of the ring relative to the barrel by one third of the angular pitch of the toothing triangular.
  • Fig. 5B shows the operation in low power supply mode.
  • control finger 72 immobilizes the ring 54 of the barrel 52.
  • the barrel When the barrel is unwound, it forces the satellites 56 to roll on the ring 54 of the barrel. In this movement, the satellite 56 will rotate the sun gear 58 at a higher rotational speed than the barrel 52 (according to the sizing of the planetary gear).
  • the pawls 68 oscillate slightly on the triangular teeth of the ring 54 and have no function.
  • the Fig. 5A and 5B represent 3 satellites: only 1 or 2 are needed.
  • This embodiment is less cumbersome than the first embodiment.
  • the external triangular teeth of the barrel ring thus cooperate with two distinct elements: the control finger 72 to immobilize it, and the pawls 68 to make the ring 54 integral with the barrel 52.
  • Fig. 6A, 6AA, 6AB and 6B show a second practical embodiment of the third embodiment of the invention which is based on the Fig. 4A and 4B .
  • the gearing includes a barrel ring 54, a planet gear 56, a sun gear 58, a control finger 66 and a barrel 52.
  • a one-way gear 74 which is engaged with the sun gear 58.
  • the ring of the barrel 54 is pivotally connected relative to the barrel 52, as in the embodiment according to the Fig. 5A and 5B .
  • the axes of the satellite 56 and the unidirectional pinion 74 are integral with the cylinder 52.
  • the sun gear 58 can be considered as immobile to simplify the understanding of the mechanism.
  • Fig. 6AB shows that the sun gear 58 turns the other way with respect to the Fig. 6AA , and in this configuration, a rotation of the sun gear is possible because the unidirectional pinion 74 can be driven, and this rotation is transmitted via the satellite 56 to the ring 54 which then turns slower than the cylinder 52.
  • the Fig. 6B shows the operation of the watch movement in low power mode.
  • the control finger 66 immobilizes the barrel ring 54.
  • the barrel 52 forces the satellite 56 to roll on the ring of the barrel 54.
  • the satellite 56 will rotate the sun gear 58 at a speed of rotation greater than that of the barrel 52 (according to the sizing of the planetary gear).
  • the unidirectional pinion 74 rotates in a vacuum and has no function. He is trained but without effect.
  • FIG. 7 Another practical embodiment of switching between the normal mode and the low power mode according to the Fig. 4A and 4B is represented at the Fig. 7 .
  • a plate or bridge 82 is pivotably mounted a double switching tooth 80, secured to the pawl 15A, 115A.
  • the pawl is loaded by a leaf spring 88 which holds it in the chosen position.
  • the pawl includes an index 90, visible from the outside, which indicates the position of the chosen pawl, or normal walking (“NORMAL”) or walking with extended reserve (“EXTENDED").
  • NVMAL normal walking
  • EXTENDED walking with extended reserve
  • This position can be brought to the terminal stop conditions by a lever 86, accessible from outside the watch, guided in translation on the plate 82.
  • the finger 87 guided in rotation by the lever 86, cooperates with the plans 80A and 80B of the switching element 80 to effect the change of state.
  • the rotation of the finger 87 is limited by a frame 84 fixed to the plate 82
  • the invention provides a simple but effective system for substantially extending the running of a mechanical watch.
  • the invention can be applied in particular to simple mechanical watches but also to complicated watches, with calendar indications, chronograph, chronometers, etc.
  • This very thin, visible and recognizable system which can be integrated into any of the mentioned watch products, makes it possible to control the power reserve in short or long duration, and the watch can for example pass the weekends without visible degradation, the calendar not changing not during all this rest.
  • the user has the choice of the desired mode and is informed by the watch of the selected mode.
  • This change between normal mode and extended power reserve mode can be manual or automatic.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
EP12181455.2A 2012-08-23 2012-08-23 Uhrwerk mit erweiterter gangreserve Active EP2701013B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
ES12181455T ES2744586T3 (es) 2012-08-23 2012-08-23 Mecanismo de relojería con reserva de marcha extendida
EP12181455.2A EP2701013B1 (de) 2012-08-23 2012-08-23 Uhrwerk mit erweiterter gangreserve
US13/973,067 US8956042B2 (en) 2012-08-23 2013-08-22 Timepiece movement with power reserve for extended operation
JP2013171910A JP6180231B2 (ja) 2012-08-23 2013-08-22 拡張動作用パワーリザーブを有する時計用ムーブメント
CN201310371611.2A CN103631126B (zh) 2012-08-23 2013-08-23 具有用于延长运行的动力储备的计时器机芯

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12181455.2A EP2701013B1 (de) 2012-08-23 2012-08-23 Uhrwerk mit erweiterter gangreserve

Publications (2)

Publication Number Publication Date
EP2701013A1 true EP2701013A1 (de) 2014-02-26
EP2701013B1 EP2701013B1 (de) 2019-06-12

Family

ID=46724278

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12181455.2A Active EP2701013B1 (de) 2012-08-23 2012-08-23 Uhrwerk mit erweiterter gangreserve

Country Status (5)

Country Link
US (1) US8956042B2 (de)
EP (1) EP2701013B1 (de)
JP (1) JP6180231B2 (de)
CN (1) CN103631126B (de)
ES (1) ES2744586T3 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3182217A1 (de) * 2015-12-18 2017-06-21 Montres Breguet S.A. Mechanismus zum einstellen des kupplungsverhältnisses zwischen triebfedern einer uhr
CN106979284A (zh) * 2016-01-18 2017-07-25 张自武 一种擒纵机构变速器
WO2023242756A1 (fr) 2022-06-14 2023-12-21 Patek Philippe Sa Geneve Mouvement horloger à réserve de marche accrue

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2657167T3 (es) * 2015-06-11 2018-03-01 Société Anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Inversor de relojería y reloj con remontaje automático que comprende su aplicación
CN114690613B (zh) * 2020-12-31 2024-05-14 广东小天才科技有限公司 具有自发电功能的智能手表及其表头结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2783657A (en) * 1954-04-14 1957-03-05 Ingraham E Co Constant torque drive
US3177975A (en) * 1961-12-21 1965-04-13 Webcor Inc Linear control mechanism
EP1118898A1 (de) 2000-01-21 2001-07-25 Gianmarco Da Vià Halterung für Zusatzlinsen
CH693155A5 (de) 1998-11-04 2003-03-14 Andreas Strehler Anzeigemechanik einer Uhr.
EP1914604A1 (de) * 2006-10-19 2008-04-23 Girard-Perregaux S.A. Uhr mit Kraftübertragung mit konstantem Drehmoment zwischen der Kraftquelle und dem mechanischen Oszillator

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2302885C3 (de) * 1973-01-20 1975-06-12 Bifora-Uhren J. Bidlingmaier Gmbh, 7070 Schwaebisch Gmuend Automatikaufzug für die Zugfeder einer Kleinuhr
JP3496544B2 (ja) * 1998-04-17 2004-02-16 セイコーエプソン株式会社 ゼンマイ装置および時計
JP3582383B2 (ja) * 1998-11-17 2004-10-27 セイコーエプソン株式会社 ゼンマイトルク出力装置およびこれを用いた機械時計
EP1213626B1 (de) * 2000-12-07 2009-07-22 ETA SA Manufacture Horlogère Suisse Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr
CH704150A2 (fr) 2010-11-17 2012-05-31 Cartier Creation Studio Sa Organe moteur pour mouvement d'horlogerie.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2783657A (en) * 1954-04-14 1957-03-05 Ingraham E Co Constant torque drive
US3177975A (en) * 1961-12-21 1965-04-13 Webcor Inc Linear control mechanism
CH693155A5 (de) 1998-11-04 2003-03-14 Andreas Strehler Anzeigemechanik einer Uhr.
EP1118898A1 (de) 2000-01-21 2001-07-25 Gianmarco Da Vià Halterung für Zusatzlinsen
EP1914604A1 (de) * 2006-10-19 2008-04-23 Girard-Perregaux S.A. Uhr mit Kraftübertragung mit konstantem Drehmoment zwischen der Kraftquelle und dem mechanischen Oszillator

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3182217A1 (de) * 2015-12-18 2017-06-21 Montres Breguet S.A. Mechanismus zum einstellen des kupplungsverhältnisses zwischen triebfedern einer uhr
US10222744B2 (en) 2015-12-18 2019-03-05 Montres Breguet S.A. Mechanism for regulating the torque ratio between time-piece wheel sets
CN106979284A (zh) * 2016-01-18 2017-07-25 张自武 一种擒纵机构变速器
WO2023242756A1 (fr) 2022-06-14 2023-12-21 Patek Philippe Sa Geneve Mouvement horloger à réserve de marche accrue

Also Published As

Publication number Publication date
ES2744586T3 (es) 2020-02-25
US8956042B2 (en) 2015-02-17
US20140056113A1 (en) 2014-02-27
JP6180231B2 (ja) 2017-08-16
EP2701013B1 (de) 2019-06-12
CN103631126B (zh) 2017-05-31
CN103631126A (zh) 2014-03-12
JP2014041127A (ja) 2014-03-06

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