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EP1213626B1 - Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr - Google Patents

Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr Download PDF

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Publication number
EP1213626B1
EP1213626B1 EP00204370A EP00204370A EP1213626B1 EP 1213626 B1 EP1213626 B1 EP 1213626B1 EP 00204370 A EP00204370 A EP 00204370A EP 00204370 A EP00204370 A EP 00204370A EP 1213626 B1 EP1213626 B1 EP 1213626B1
Authority
EP
European Patent Office
Prior art keywords
spring
central shaft
generator
oscillating weight
coupled
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.)
Expired - Lifetime
Application number
EP00204370A
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English (en)
French (fr)
Other versions
EP1213626A1 (de
Inventor
Jean-Philippe Rebeaud
Denis Burdet
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.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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 ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to DE60042597T priority Critical patent/DE60042597D1/de
Priority to EP00204370A priority patent/EP1213626B1/de
Priority to US09/987,997 priority patent/US6587401B2/en
Priority to JP2001371011A priority patent/JP4188589B2/ja
Priority to CNB011435313A priority patent/CN1239968C/zh
Publication of EP1213626A1 publication Critical patent/EP1213626A1/de
Priority to HK02109068A priority patent/HK1047322A1/xx
Application granted granted Critical
Publication of EP1213626B1 publication Critical patent/EP1213626B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04C—ELECTROMECHANICAL CLOCKS OR WATCHES
    • G04C10/00—Arrangements of electric power supplies in time pieces

Definitions

  • the present invention relates to an anti-shock transmission device for driving the rotor of an electric generator by an oscillating weight in a portable apparatus, comprising a central shaft and a toothed intermediate wheel, one of which is capable of being driven into rotation by movements of the oscillating mass and the other is coupled to the generator rotor by a kinematic connection, the central shaft and the intermediate wheel having a common rotational axis, and a spiral spring having one end inner coupled to the central shaft and an outer end coupled to the intermediate wheel.
  • the invention also relates to a wristwatch comprising an electric generator driven by an oscillating mass via such a transmission device.
  • Such a device can be used in particular in a small volume device carried by a user whose movements will cause the swinging of the oscillating mass, which is usually rotary.
  • This is for example, but not limited to, a wristwatch whose watch movement and / or other functional elements are powered by an energy accumulator charged by the electric generator. Since the oscillating mass generally rotates at a fairly low speed during normal operation and the generator rotor must rotate at a high speed to produce sufficient electrical voltage, it is necessary to use a multiplier transmission between these two members. In cases where the generator rotor has only one permanent rotating member on itself, the necessary transmission ratio is of the order of 100 and is usually achieved by means of a two-stage gear transmission.
  • the present invention aims to improve an anti-shock transmission device of this kind, avoiding the use of friction damping and creating a simple and inexpensive construction that avoids a rupture of the spring or its fasteners when the apparatus is shocked to a certain extent, for example (but not limited to) to the value of 5000 g prescribed by ISO 1413.
  • the invention relates to an anti-shock transmission device of the type indicated in the preamble, characterized in that the central shaft comprises a series of indentations distributed around its periphery and in that the inner end of the spring is arranged to engage in any one of said indentations by the elasticity of the spring and be able to disengage from the indentation when it is subjected to a sufficient force in at least one direction of rotation of the device.
  • each notch has an inclined flank and that the inner end of the spring has an inwardly projecting portion adapted to abut against said inclined flank to receive said force and slide on it as soon as said force exceeds a limit value.
  • a mechanism 1 with rotating oscillating weight 2 mounted on a plate 3 of the clockwork movement of the watch, rotates the rotor 4 of an electric micro-generator by means of an anti-shock transmission device 5 which multiplies the speed of rotation.
  • Mechanism 1 is constructed conventionally. Its central bearing support 6, fixed to the plate 3 by means of a screw 7 and a tubular nut 8, supports a toothed wheel 10 by a ball bearing 11.
  • the semicircular oscillating mass 2 is fixed to the toothed wheel 10 via a ring 12 and can rotate around the central axis 13 of the watch.
  • the rotor 4 of the generator comprises a permanent magnet 14 fixed on a shaft 15 provided with a pinion 16.
  • the pivots at the end of the shaft 15 are mounted by respective stones 17 and 18 in the plate 3 and in a bridge 19 which is set at stator 20 of the generator by means of feet 21.
  • the magnet 14 of the rotor rotates in a recess 22 of the stator.
  • the transmission device 5 carries a central shaft 24 provided with a pinion 25 and which meshes with the toothing 26 of the wheel 10, an intermediate wheel formed by a cylinder 27 provided with an external toothing 28 which meshes with the pinion 16 of the rotor 4, and a spiral spring 30 which rotatably connects the shaft 24 and the barrel 27.
  • the shaft 24 is rotatably mounted in the plate 3 and the bridge 19 by means of respective stones 31 and 32 for turn around an axis 33.
  • the barrel 27 will be described in more detail with reference to Figures 2 to 6 .
  • the figure 3 shows the shape of the spiral spring 30 in the state of rest, before it is mounted in the barrel 27. Its inner end has a bent portion 34 making an obtuse angle of about 135 ° with the adjacent portion of the first inner coil 36 of the spring. The bent portion 34 has a free end 37. The outer end 38 of the spring is welded to an anchor plate 39.
  • the spring 30 is formed of a section steel blade 0.04 x 0.5 mm and has at rest, between its two ends, 8.5 turns which are separated from each other by an interval. At rest, the inner turn 36 has a diameter of about 1.3 mm and the outer turn 40 has a diameter of about 3.4 mm.
  • spiral springs of this kind are generally manufactured in groups of three to obtain the desired interval between the turns at rest.
  • the springs are formed by winding the three corresponding blades around a mandrel provided with three clamps to hold the inner ends of the springs, then removing the internal tensions by a heat treatment. This process automatically creates the bent portion 34 at the end of each spring, i.e. obtaining this end shape requires no additional operation.
  • the barrel 27 comprises a plastic molded part comprising a cylindrical drum 41, a flat bottom 42 which pivots around a cylindrical surface 43 of the shaft 24, the toothing 28 on the periphery of the barrel 41, as well as three feet 44 for fixing a cover 45 which constitutes the upper face of the barrel and which pivots around a bearing 46 of the shaft 24.
  • the crown is removed in the Figures 5 to 6 to show the inside of the barrel.
  • the anchor plate 39 of the spring 30 is locked in a recess 47 of the drum 41.
  • the central shaft 24 has an enlarged portion 50 provided with a series of indentations 51 distributed around its periphery.
  • indentations 51 there are provided four indentations 51 having, in a plane perpendicular to the shaft 24, a substantially V-shaped asymmetrical profile whose longest branch forms an inclined flank 52 (FIG. figure 5 ), while its other side 53 extends approximately radially to an edge 54 of the notch.
  • the spring 30 can rest on arches 55 in an arc which are bordered by two flanges 56 ( figure 2 ) to guide the spring.
  • the diameter defined by the bearing surfaces 55 is slightly greater than that of the first turn 36 of the resting spring, so that the elasticity of the spring tends to engage its bent end 34 in any of the notches 51 and to tighten slightly the first turn 36 on the bearings 55 of the shaft.
  • the oscillating mass 2 When the watch is not subjected to movement, the oscillating mass 2 is stopped and the transmission device 5 transmits no torque to the rotor 4 of the generator, except possibly a low positioning torque of the magnet 14 relative to the stator 20. The device 5 is then in the equilibrium position shown in FIG. figure 4 .
  • the oscillating mass 2 starts rotating in any direction and rotates the shaft 24 via the toothing 26 and the pinion 25.
  • the spring 30 is then energized and transmits a torque cylinder 27, which also starts to rotate and drives in rapid rotation the rotor 4 via the toothing 28 and pinion 16.
  • the device reaches the position represented in FIG. figure 7 , where the inclined flank 52 exerts a force F, approximately perpendicular to the sidewall 52, on the end 37 of the spring. If the force F exceeds a certain limit capable of pushing the end 37 towards the outside, this latter slides on the inclined sidewall 52 towards the outside and escapes from the notch from the position of the figure 8 , so that the spring and the barrel rotate less quickly than the tree.
  • the end 37 of the spring thanks to the elasticity thereof, will tend to engage automatically in one of the indentations 51 and remain engaged to re-transmit torque to the spring when dynamic conditions allow.
  • the figure 6 represents a situation where the torque applied by the shaft 24 to the spring in the direction B has a value so high that all the turns are pressed against the shaft, except the end portion of the outer coil.
  • the absolute value of this couple is substantially the same as in the case illustrated by the figure 5 , but the resulting force between the outer end 38 of the spring and the anchor plate 39 is only a fraction of the force to be transmitted for the same torque at the bearings 55 of the shaft, because it acts with a much greater lever.
  • a break in the weld between the elements 38 and 39 is not to be feared for such a value of the torque to be transmitted.
  • one absolutely wanted to guard against the risk of rupture of the external anchorage of the spring one could also use a sliding flange system of the type well known for the barrels causing the movements of mechanical watches.
  • the scope of the present invention is not limited to watches and can extend especially to all portable devices equipped with an electric generator, for example mobile phones, measuring devices or medical devices.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Electric Clocks (AREA)

Claims (11)

  1. Stoßsichere Übertragungsvorrichtung für den Antrieb des Rotors (4) eines elektrischen Generators durch eine oszillierende Masse (2) in einem tragbaren Gerät, wobei die stoßsichere Übertragungsvorrichtung umfasst:
    eine Zentralwelle (24) und ein Zwischenzahnrad (28), wovon eine(s) durch die Bewegungen der oszillierenden Masse rotatorisch angetrieben werden kann und das (die) andere dazu vorgesehen ist, mit dem Rotor des Generators durch eine kinematische Verbindung gekoppelt zu werden, wobei die Zentralwelle (24) und das Zwischenrad (28) eine gemeinsame Drehachse (33) besitzen, und
    eine Feder (30) in Spiralform, die ein mit der Zentralwelle (24) gekoppeltes inneres Ende und ein mit dem Zwischenrad (28) gekoppeltes äußeres Ende besitzt,
    dadurch gekennzeichnet, dass die Zentralwelle (24) eine Reihe von Aussparungen (51) aufweist, die längs ihres Umfangs verteilt sind, und dass das innere Ende (37) der Feder dazu ausgelegt ist, mit irgendeiner der Aussparungen (51) durch die Elastizität der Feder in Eingriff zu gelangen und mit der Aussparung außer Eingriff gelangen kann, wenn sie einer ausreichenden Kraft in wenigstens einem Drehsinn (A) der Vorrichtung unterliegt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass jede Aussparung (51) eine schräge Flanke (52) aufweist und dass das innere Ende der Feder einen nach innen vorstehenden Teil (34) aufweist, der an der schrägen Flanke anschlagen kann, um die Kraft aufzunehmen und um an dieser zu gleiten, wenn die Kraft einen Grenzwert übersteigt.
  3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der vorstehende Teil der Feder durch einen gebogenen Teil (34) gebildet ist, der ein freies Ende (37) besitzt, das an der schrägen Flanke anschlagen kann.
  4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der gebogene Teil (34) mit dem angrenzenden Teil der Feder einen stumpfen Winkel (35) bildet, wobei die Innenfläche des Winkels so beschaffen ist, dass sie sich an einem Rand (54) der Aussparung abstützt.
  5. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass jede Aussparung (51) in einer zur Welle senkrechten Ebene ein asymmetrisches Profil im Wesentlichen in Form eines V hat, wovon der längste Schenkel die schräge Flanke (52) bildet.
  6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Zentralwelle mit einem Ritzel (25) versehen ist, das dazu bestimmt ist, durch Zahneingriff mit der oszillierenden Masse gekoppelt zu werden, und dass das Zwischenrad (28) dazu bestimmt ist, durch Zahneingriff mit dem Rotor des Generators gekoppelt zu werden.
  7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, dass die Feder (30) sich in einem Federgehäuse (27) befindet, das eine Trommel (41) aufweist, die mit einem Boden und mit einem Deckel versehen ist, wobei das äußere Ende (38) der Feder in der Trommel verankert ist, und dass das Zwischenrad durch eine Außenzahnung (28) an der Trommel gebildet ist.
  8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass die Zentralwelle (24) in dem Federgehäuse einen erweiterten Teil (50) aufweist, in dem die Aussparungen (51) ausgebildet sind, und zwischen den Aussparungen kreisbogenförmige Bereiche (55) für die Abstützung der Feder aufweist.
  9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass eine erste Innenwindung (36) der Feder im Ruhezustand, in dem die Feder nicht an der Zentralwelle montiert ist, einen kleineren Durchmesser als der durch die genannten Bereiche (55) definierte Durchmesser aufweist.
  10. Vorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Zentralwelle durch die oszillierende Masse in die zwei Richtungen (A und B) angetrieben werden kann.
  11. Armbanduhr, die einen elektrischen Generator umfasst, der durch eine oszillierende Masse über eine Übertragungsvorrichtung (5) nach einem der Ansprüche 1 bis 10 angetrieben werden kann.
EP00204370A 2000-12-07 2000-12-07 Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr Expired - Lifetime EP1213626B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE60042597T DE60042597D1 (de) 2000-12-07 2000-12-07 Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr
EP00204370A EP1213626B1 (de) 2000-12-07 2000-12-07 Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr
US09/987,997 US6587401B2 (en) 2000-12-07 2001-11-16 Anti-shock transmission device for driving a generator by an oscillating weight in particular in a watch
JP2001371011A JP4188589B2 (ja) 2000-12-07 2001-12-05 特にウォッチにおいて振動重錘により発電器を駆動するためのアンチショック伝達装置
CNB011435313A CN1239968C (zh) 2000-12-07 2001-12-06 适用于手表的用于摆动锤驱动发电机的防震传动机构
HK02109068A HK1047322A1 (en) 2000-12-07 2002-12-13 Anti-shock transmission device for driving a generator by an oscillating weight in particular in a watch

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00204370A EP1213626B1 (de) 2000-12-07 2000-12-07 Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr

Publications (2)

Publication Number Publication Date
EP1213626A1 EP1213626A1 (de) 2002-06-12
EP1213626B1 true EP1213626B1 (de) 2009-07-22

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ID=8172391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00204370A Expired - Lifetime EP1213626B1 (de) 2000-12-07 2000-12-07 Stossfeste Übertragungsmittel zum Antrieb eines Generators durch eine Schwungmasse, insbesondere in einer Uhr

Country Status (6)

Country Link
US (1) US6587401B2 (de)
EP (1) EP1213626B1 (de)
JP (1) JP4188589B2 (de)
CN (1) CN1239968C (de)
DE (1) DE60042597D1 (de)
HK (1) HK1047322A1 (de)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102011106785B4 (de) * 2011-07-06 2015-07-23 JuB-Creative Product GmbH Kinetischer Wandler

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US9298162B2 (en) * 2010-10-01 2016-03-29 Rolex Sa Timepiece barrel with thin disks
ES2744586T3 (es) * 2012-08-23 2020-02-25 Audemars Piguet Renaud Et Papi Sa Mecanismo de relojería con reserva de marcha extendida
EP2765462B1 (de) * 2013-02-12 2018-04-04 ETA SA Manufacture Horlogère Suisse Stoßfestes Minutenrad
CN104133362B (zh) * 2013-05-01 2021-05-18 劳力士有限公司 钟表振荡器的摆锤的减震体
CN106586945B (zh) * 2017-01-07 2018-02-09 杭州电子科技大学 低驱动电压的微型冲击锤
CN107957670B (zh) * 2017-10-13 2020-03-24 烟台职业学院 一种大型机械表的智能上条机构
NL2021361B1 (en) * 2018-07-20 2020-01-29 Kinetron Bv Electric low-power supply system for devices and device comprising such a low-power supply system

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NL85867C (de) 1948-12-31
DE832579C (de) * 1949-07-25 1952-02-25 Junghans Geb Ag Federnde Lagerung fuer Wellenzapfen in feinmechanischen Getrieben
US2721627A (en) * 1952-02-01 1955-10-25 Eastman Kodak Co Shock-absorber for spring motors
FR2268293B3 (de) * 1974-04-18 1977-02-18 Valroger Pierre
NL9001976A (nl) * 1990-09-07 1992-04-01 Kinetron Bv Generator.
CH686474B5 (fr) * 1994-05-04 1996-10-15 Ebauchesfabrik Eta Ag Dispositif de couplage entre une source d'énergie mécanique et une génératrice électrique dans une pièce d'horlogerie.
DE69606516T2 (de) * 1995-09-13 2000-07-06 Citizen Watch Co., Ltd. Kleiner elektronischer apparat mit generator
JP3497708B2 (ja) 1997-10-09 2004-02-16 株式会社東芝 半導体集積回路
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011106785B4 (de) * 2011-07-06 2015-07-23 JuB-Creative Product GmbH Kinetischer Wandler

Also Published As

Publication number Publication date
JP2002250781A (ja) 2002-09-06
DE60042597D1 (de) 2009-09-03
JP4188589B2 (ja) 2008-11-26
CN1239968C (zh) 2006-02-01
US20020071348A1 (en) 2002-06-13
US6587401B2 (en) 2003-07-01
CN1357804A (zh) 2002-07-10
EP1213626A1 (de) 2002-06-12
HK1047322A1 (en) 2003-02-14

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