EP2210148A1 - Montre-bracelet mécanique à force de ressort constante - Google Patents

Montre-bracelet mécanique à force de ressort constante

Info

Publication number
EP2210148A1
EP2210148A1 EP08847321A EP08847321A EP2210148A1 EP 2210148 A1 EP2210148 A1 EP 2210148A1 EP 08847321 A EP08847321 A EP 08847321A EP 08847321 A EP08847321 A EP 08847321A EP 2210148 A1 EP2210148 A1 EP 2210148A1
Authority
EP
European Patent Office
Prior art keywords
barrel
differential
gear
elevator
wristwatch according
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Withdrawn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
EP08847321A
Other languages
German (de)
English (en)
Inventor
Patrick Kury
Stephan Kussmaul
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.)
Eterna AG Uhrenfabrik
Original Assignee
Eterna AG Uhrenfabrik
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 Eterna AG Uhrenfabrik filed Critical Eterna AG Uhrenfabrik
Publication of EP2210148A1 publication Critical patent/EP2210148A1/fr
Withdrawn legal-status Critical Current

Links

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
    • G04B1/22—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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/12—Driving mechanisms with mainspring with several mainsprings

Definitions

  • the invention relates to the field of mechanical watches, especially with automatic winding, in which a mainspring in a barrel with the help of the movements of a carrier can be pulled by a flywheel, wherein the mainspring has a constant spring force as possible.
  • Such watches are known. It is a so-called Stackfreed or a screw with radially increasing diameter or a so-called Maltese Cross used. These systems are complicated and have their mechanical disadvantages, in particular that they can not really guarantee the constant spring force.
  • the torque is also not at a not fully wound up clock, which is not worn, for example, not constant, but decreases with time. In this respect, this problem is not solved even with wristwatches with manual wind.
  • the present invention seeks to provide a clock of the type mentioned, in which over a long period of time, a substantially constant maximum torque is available.
  • the timepiece is also adjustable to provide minimal torque for improved accuracy of the gait. In other words, if it can be determined that the set mini- torque is no longer guaranteed, the clock stops.
  • Another goal is to extend the gear transit time with substantially constant torque.
  • the inventive mechanical wristwatch has a mainspring in a first barrel and a mechanical and / or automatic elevator. Furthermore, now a second barrel and a differential with three drive trains are provided. The fact that the strand connected to the elevator acts rectified on the first and the second barrel, both barrels are mounted torque neutral. In a standstill of the strand connected to the elevator, however, a drainage of the first barrel is compensated by an energy transfer via the differential from the second barrel. In particular, the advantageously stronger second barrel can then raise and / or support the first barrel.
  • FIG. 1 is a schematic diagram of the wesent ⁇ union components of such a clock according to a first embodiment
  • FIG. 3 is a schematic view of a device for Drehmo ⁇ mentbegrenzung with a central sun gear
  • Fig. 4 is a schematic partially sectioned view of the structure of the sun gear construction in interaction with the first barrel
  • Fig. 5 is a schematic view similar to Fig. 3 without representation of the sun gear.
  • FIG. 1 shows a basic schematic representation of the essential components of such a clock according to a first exemplary embodiment.
  • the reference numeral 10 designates in a general way the barrel of the mainspring, which is fixed in the interior according to the knowledge of the skilled in the first barrel 10.
  • the designated hereinafter as the first barrel spring 10 has the outside via a spring drum 12 with teeth as a drain wheel and the spring, not shown in the drawings, which is mounted inside the spring mounting 173 shown in FIG. 4 in the first barrel.
  • the spring may be designed as a 950 g * mm spring.
  • the gears 110 and 111 it is connected to an axle 121 on which a schematically illustrated bevel gear 131 is attached.
  • the axis 121 is in a Lock differential housing 130 of a differential 40 stored.
  • An axis 141 is arranged in alignment with respect to the axis 121 and is likewise mounted in the housing 130.
  • a bevel gear 132 is arranged in the housing 130, wel ⁇ Ches as the bevel gear 131 with a differential pinion 133 is engaged.
  • the differential bevel gear is mounted with its axis on the housing 130. In principle, it is also possible to provide at the opening indicated by 134 another bevel gear for engagement with the bevel gears 131 and 132.
  • the housing or differential carrier 130 is fixedly connected to a bevel gear 135, which via gear wheels 112 and 113 with a second barrel 20 is in operative engagement.
  • the unit consisting of bevel gears 131, 132, 133 and housing 130 may be referred to as differential 40 with bevel gears. It has a gear ratio of 1: 1 with respect to the component distribution.
  • a differential 40 is in principle a special planetary gear in which the sun gear and the ring gear are the same size.
  • the axle 141 is connected to the conventional known automatic elevator. It can also intervene there, the manual elevator. When this works, the axis 141 rotates and transmits the moment evenly on the two barrels 10 and 20. If the wearer of the self-winding watch does not move, then the axle 141 stands and locks. As a result, wheel 132 does not move and an outlet of bevel gear 131 results in an equal running of bevel gear 133, so that the housing 130 rotates in opposite directions and transmits its movement via the gear 135 to the second barrel 20 in such a way that the one located therein , Spring not shown in the drawings also relaxed.
  • the second barrel 20 has a higher torque and is designed for example to 1200 g * mm.
  • the illustrated differential 40 has a so-called state over ⁇ tion of -1.
  • the differential 40 may also be designed as a planetary gear with a stand ratio of unequal -1. This can be achieved by differently sized hollow and sun gears (corresponding to the Ke ⁇ gelchen 131 and 132), in which case, for example, the bevel gears 133/134 would then be inclined with its axis in the housing 30 to the small wheel 131/132.
  • gearboxes such as Stirnraddifferentiale used.
  • FIG. 2 shows a schematic diagram of essential components of such a watch with a differential 40 according to a second exemplary embodiment.
  • Identical functional components have the same or similar, painted reference numerals.
  • the differential carrier 130 in turn comprises the bevel gears 131 and 133, wherein the bevel gear 131 engages on the axis 121 in the ratchet wheel 11 of the first barrel 10 via a not visible in FIG. 2 gear.
  • the gear 135 'of the housing 130' of the differential is now engaged with the gear 151 of the automatic winding and preferably on the opposite side with a parallel axis with the first gear 152 of the manual wind, the elevator shaft has received the reference numeral 153.
  • the pawl 30, de ⁇ ren free end in the ratchet gear 136 'engages, wel ⁇ Ches with the housing 130' is firmly connected.
  • the pawl 30 is preferably secured with its base 31 on a bottom plate, not shown in FIG. 2 for clarity, on which also the barrels 10 and 20 are arranged.
  • the differential 40 transmits according to its configuration, the torque on both sides of the barrels 10 and 20.
  • the gear 133 rotates in Fig. 2 forward out of the image plane and rotates the bevel gears 131 and 132 'in accordance with the movement in accordance with To reach arrows on the barrels. Both barrels 10 and 20 are raised.
  • the pawl 30 only allows the differential housing 130 'to rotate in one direction. In particular, the housing 130 'stands still when the elevators are resting above the elements 151 and 153. The opposite rotation is prevented. During a course of the barrel 20, ie a rotation of the barrel 20 against the direction indicated by the arrow, the gear 114 rotates in the opposite direction to the direction indicated and the movement is transferred at standstill of the housing 130 'in the manner shown on the barrel 10. .A co-rotation of the housing 130 'is prevented by the pawl 30. This means that the first barrel 10 is now through the process of the second barrel 20 is raised.
  • the second barrel 20 is designed more (at ⁇ play, 1200 g * mm), when the first barrel 10 (in this example, 950 g * mm).
  • the direction shown by the arrow on the spring ⁇ houses 10 and 20 corresponds to the lift direction of the barrels 10 and 20th
  • the ratchet wheel 11 cooperates in a known manner with the other compo ⁇ nents of the barrel 10. In particular, it is connected to the square or locking pin 171 with the shaft 172.
  • the first barrel 10 is so far raised indirectly, the second barrel 20, however, directly.
  • the constant force can be maintained as long as the second barrel with an initial dimension of 1200g * mm remains above the said 1000g * mm. Furthermore, an extension of the operating life is achieved by the fact that, in the event of a theoretical drop in the energy gie of the first barrel 10 to 900g * mm at 1000g * ⁇ un the second barrel 20 by the compensation via the differential 40, the first barrel 10 actually at 950g * ⁇ un remains, so that also the term is extended.
  • the constant force which alone brings about an advantageous embodiment of the watch according to the invention, is not the only effect according to the invention.
  • a second advantage is that in a further embodiment, the disadvantages are avoided, which arise in a case provided with a sliding barrel.
  • the reference numeral 50 denotes a sun gear, which is connected via a column wheel or drive wheel 161 with the drain wheel 12 of the barrel 10. This will now be explained with a torque limiting device in connection with FIGS. 3 and 4.
  • Fig. 3 shows in a schematic view the torque limiting device with the central sun gear 50.
  • This is connected via a known sequence of reduction wheels 164 with a column wheel or drive wheel 161 which drives a rack 51 having a front abutment surface 163 which after appropriate movement in the direction of the arrow against a torque screw 52 pushes.
  • the torque screw 52 is fixed by means of an adjusting screw 53 to a base plate of the clock.
  • the torque screw 52 is advantageously an eccentric screw, so that by turning the same about the axis of the adjusting screw 53, the end position of the rack 51 is adjustable at which it st ⁇ sst with the boundary surface 163 against the torque screw 52.
  • Fig. 4 shows in a schematic partially sectioned manner the structure of the sun gear in Zusa ⁇ unenspiel with the first barrel 10. This construction is both exporting ⁇ approximately examples of Figs. 1 and 2 and for further in FIGS. not illustrated embodiments can be used.
  • the column wheel 161 has at its two ends in each case a gear: the engagement gear 166 for coupling with the impeller 12 of the first barrel 10 and the engagement wheel 167 for coupling with the sun gear 50th
  • the ratchet wheel 11 is rigidly connected to the shaft 172 via a square 171 acting as a locking pin.
  • the shaft 172 is passed through the barrel 10 and is there for spring mounting 173 in the first barrel 10.
  • At its opposite end it is mounted on a ball bearing 179, which is designed here as a double ball bearing.
  • the ball bearing 179 is in communication with the first barrel 10.
  • a rotation of the shaft 173 in one direction leads at standstill of the barrel 10, that is, the housing with the drain wheel 12, for mounting the spring therein.
  • a rotation of the barrel 10 in the same direction relaxes the spring.
  • the sun gear 50 rotates with rotating barrel 10 in the same direction.
  • the shaft 172 transmits its rotational movement via the small transmission gear 174, which is rotatably connected via the square 177 with the shaft 172, on the larger of the teeth of the planetary gear 165. This then rotates the sun gear 50 in the opposite direction.
  • a rotation of the ratchet wheel 11 for mounting the barrel 10 therefore leads to a rotation of the sun gear 50 in one direction.
  • one Winding the barrel 10 in the course of its expiration has a stationary sun gear 50 result.
  • the provision of the further toothed wheels 164 to the toothed rack 51 corresponds to a gear display.
  • the planetary gear 165 is provided with a further smaller toothing which engages the toothing assigned to this transmission gear 176 of the planetary ⁇ tenrades 165th
  • This transfer gear 176 then engages the first of the gears 164.
  • the transmission gear 176 may be mounted in particular with a Rubinlagerung 180 on the shaft 172, which is practical for reasons of space.
  • the averaging gear construction is known to the person skilled in the art. For the purposes of the present invention, however, it must provide the surface 163 which limits the movement of the rack 51 against the abutment surface 163 of the torque screw 52. It will subsequently be shown that this stop serves to limit the torque in its value upwards.
  • FIG. 5 shows a schematic view similar to FIG. 3 without representation of the sun gear 50, which is mounted concentrically to the central axis of the shaft 172 indicated by the square 177 and with the components shown in FIG. 5 via an external engagement in FIG the wheel 167 and via the bearing 178 of the planetary gear 165 is operatively connected.
  • a second torque screw is provided on the opposite side of the rack 51.
  • a stop surface is provided analogously, which is shown for clarity in FIG. 3 with the reference numeral 263 as a principle. This stop surface then limits the torque in its value down.
  • the function of the torque limit up is now as follows.
  • the ratchet wheel 11 is rotated by acting on the housing 130 elevator and pulls the spring inside the barrel 10. It also rotates the planetary gear 165 in the direction shown in Fig. 3, so that the sun gear 50 and the downstream gears 164 rotate according to the arrows.
  • the rack 151 is advanced against the torque screw 52.
  • a Drehmomentbegren- tion is provided at least upwards, which makes a maximum position for the mounting of the first barrel 10 adjustable by a torque limiter and in a further embodiment, the flow of the spring of the barrel 10 under a minimum voltage.
  • the mediating element, here a rack 51 can also be designed differently, for example by a toothed wheel, which has a radial pointing outward pointer, which can also push against also arranged radially to this gear maximum and / or minimum stops. Instead of the linear movement of the rod 51 then an angular movement of this pointer is provided.
  • the barrel 10 is a barrel with a spring which is fixedly attached to the inner edge of the spring housing and on the shaft 173 of the shaft 172 of the ratchet wheel 11.
  • the barrel 20 is a barrel 20 limited by a slip clutch or other known means in its elevator of the spring.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)

Abstract

Montre-bracelet mécanique présentant un ressort moteur dans un premier barillet (10) et un remontoir mécanique et/ou automatique (141, 151, 152). Il est prévu un deuxième barillet (20) et un différentiel (40) avec trois branches d'entraînement (121, 141, 135; 121, 114, 135'), la branche (141, 151, 152) reliée au remontoir agissant dans le même sens sur le premier et le deuxième barillet (10 et 20).
EP08847321A 2007-11-09 2008-10-22 Montre-bracelet mécanique à force de ressort constante Withdrawn EP2210148A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH17372007 2007-11-09
PCT/CH2008/000446 WO2009059441A1 (fr) 2007-11-09 2008-10-22 Montre-bracelet mécanique à force de ressort constante

Publications (1)

Publication Number Publication Date
EP2210148A1 true EP2210148A1 (fr) 2010-07-28

Family

ID=39628987

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08847321A Withdrawn EP2210148A1 (fr) 2007-11-09 2008-10-22 Montre-bracelet mécanique à force de ressort constante

Country Status (5)

Country Link
US (1) US8550701B2 (fr)
EP (1) EP2210148A1 (fr)
JP (1) JP5412436B2 (fr)
CN (1) CN101855601B (fr)
WO (1) WO2009059441A1 (fr)

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DE102012018570B4 (de) 2012-01-28 2015-03-12 Dirk Dornblüth Armbanduhr mit mechanischem Aufzug
WO2014021441A1 (fr) 2012-08-03 2014-02-06 Semiconductor Energy Laboratory Co., Ltd. Élément électroluminescent, dispositif électroluminescent, dispositif électronique et dispositif d'éclairage
EP3232274A1 (fr) * 2015-01-05 2017-10-18 Citizen Watch Co., Ltd. Mouvement pour pièce d'horlogerie mécanique
CH711790B1 (fr) * 2015-11-17 2021-03-31 Complitime Sa Mouvement d'horlogerie.
CH711916B1 (fr) * 2015-12-03 2020-02-28 Richemont Int Sa Système automatique de stockage d'énergie mécanique pour mouvement horloger.
CH711931A2 (fr) * 2015-12-18 2017-06-30 Montres Breguet Sa Mécanisme de réglage de rapport de couple entre des mobiles d'horlogerie.
KR102435641B1 (ko) * 2016-10-05 2022-08-23 밀워키 일렉트릭 툴 코포레이션 소형 리트랙션 시스템을 갖춘 줄자
EP3312681B1 (fr) * 2016-10-19 2020-01-29 Montres Breguet S.A. Mouvement horloger comportant un dispositif d'égalisation d'un couple moteur
EP3382468B1 (fr) * 2017-03-30 2020-01-15 The Swatch Group Research and Development Ltd Mouvement avec prolongateur de réserve de marche
CH713757B1 (fr) * 2017-05-05 2020-12-15 Gfpi Sa Mouvement d'horlogerie comprenant une pluralité de systèmes réglants.
CN106990647B (zh) * 2017-05-22 2023-01-06 华中科技大学 一种工业摄像机位姿调整装置
WO2021092512A1 (fr) * 2019-11-08 2021-05-14 Rambler Wheels, Llc Procédé et appareil pour heure d'été à réglage continu de l'heure
CN111501754A (zh) * 2020-04-16 2020-08-07 江苏长风海洋装备制造有限公司 一种钢管桩施工定位装置

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CH689470A5 (de) * 1996-05-09 1999-04-30 Fortis Uhren Ag Mechanisches Armbanduhrwerk mit einem Wecker und einem Chronographen.
ATE428958T1 (de) * 1999-08-04 2009-05-15 Piguet Frederic Sa Vorrichtung zur anzeige der gangreserve einer uhr
EP1115040B1 (fr) * 2000-01-06 2008-03-26 Chopard Manufacture SA Dispositif moteur pour mouvement d'horlogerie à grande réserve de marche
ATE470890T1 (de) * 2005-03-30 2010-06-15 Montres Breguet Sa Uhr mit mindenstens zwei reguliersystemen
ATE471538T1 (de) * 2005-10-10 2010-07-15 Montres Breguet Sa Uhrwerk mit konstantkraftvorrichtung

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Also Published As

Publication number Publication date
CN101855601A (zh) 2010-10-06
CN101855601B (zh) 2012-07-04
US8550701B2 (en) 2013-10-08
JP5412436B2 (ja) 2014-02-12
JP2011503555A (ja) 2011-01-27
US20100254229A1 (en) 2010-10-07
WO2009059441A1 (fr) 2009-05-14

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