JP2009198502A - Automatic winding mechanism for timepiece - Google Patents

Automatic winding mechanism for timepiece Download PDF

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Publication number
JP2009198502A
JP2009198502A JP2009036373A JP2009036373A JP2009198502A JP 2009198502 A JP2009198502 A JP 2009198502A JP 2009036373 A JP2009036373 A JP 2009036373A JP 2009036373 A JP2009036373 A JP 2009036373A JP 2009198502 A JP2009198502 A JP 2009198502A
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Japan
Prior art keywords
winding mechanism
mechanism according
vibrating weight
weight ring
supported
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JP2009036373A
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Japanese (ja)
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JP5414301B2 (en
Inventor
Joachim Mutrux
ヨアヒム・ムトルクス
Philippe Roehrich
フィリップ・ルーリク
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Bucherer Montres SA
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Bucherer Montres SA
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    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/10—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited
    • G04B5/12—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited acting in one direction only
    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/10—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited
    • G04B5/14—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited acting in both directions
    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/16—Construction of the weights
    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/18—Supports, suspensions or guide arrangements, for oscillating weights
    • G04B5/184—Guide arrangement of the moving weight in a circular course

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic winding mechanism for a timepiece which is protected from impacts, more surely than in conventional art. <P>SOLUTION: This winding mechanism has an oscillation weight ring 9, and the oscillation weight ring is supported rotatably on many rollers 10 in a timepiece mechanism. The geometrical axis of the oscillation weight ring 9 substantially matches with the geometric axis of the timepiece mechanism. The rotation motion of the oscillation weight ring 9 can be transmitted to the timepiece mechanism via teeth 8 of the oscillation weight ring 9. Each roller 10 is supported by an attenuating mechanism 22 for attenuating the radial movement of the oscillation weight ring 9 during impact. Each roller 10 is supported by a support plate 12 which is rockable by a ball bearing 33. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

本発明は、振動重錘リングを備え、この振動重錘リングの幾何学的軸線が時計仕掛けの幾何学的軸線とほぼ一致するように、振動重錘リングが時計仕掛け内で多数のローラに回転自在に支承され、振動重錘リングの回転運動が例えば振動重錘リングの歯を介して時計仕掛けに伝達可能である、時計用の自動巻上げ機構に関する。   The present invention includes a vibrating weight ring, and the vibrating weight ring rotates to a number of rollers within the clockwork so that the geometric axis of the vibrating weight ring substantially matches the geometric axis of the clockwork. The present invention relates to an automatic winding mechanism for a watch that is freely supported and capable of transmitting the rotational motion of a vibrating weight ring to a clockwork via, for example, teeth of the vibrating weight ring.

この種の巻上げ機構は従来技術において、特許文献１によって知られている。この巻上げ機構は腕時計の時計仕掛けの自動巻上げを可能にする。この巻上げ機構の場合、振動重錘リングが環状室内で３個のローラに回転自在に懸垂されている。振動重錘リングの回転運動は、ばねを緊張させて時計仕掛けを巻上げるように、一方向伝動部材（Ｇｌｅｉｃｈｒｉｃｈｔｅｒ）を備えた伝動装置を介して時計仕掛けに伝達される。振動重錘リングができるだけ小さな摩擦で回転できるようにするために、上記のローラをできるだけ摩擦を生じないように支承すべきである。このような巻上げ機構の場合、振動重錘リングの質量が比較的に大きいので、衝撃時に、ローラ、特にローラの軸受が損傷し得るという難点がある。   This type of winding mechanism is known from US Pat. This winding mechanism enables automatic winding of the watch clockwork. In the case of this winding mechanism, the vibrating weight ring is suspended in a freely rotating manner by three rollers in the annular chamber. The rotational movement of the vibrating weight ring is transmitted to the clockwork via a transmission device with a one-way transmission member (Gleichrichter) so as to tension the spring and wind up the clockwork. In order to allow the vibrating weight ring to rotate with as little friction as possible, the above roller should be supported with as little friction as possible. In the case of such a winding mechanism, since the mass of the vibrating weight ring is relatively large, there is a problem that the roller, particularly the roller bearing, can be damaged at the time of impact.

英国特許第７０５９３０号明細書British patent No. 705930

本発明の根底をなす課題は、上記難点を回避する上記種類の巻上げ機構を提供することである。それによって、巻上げ機構は強い衝撃を受けたときにも、衝撃に対して従来よりもはるかに確実に保護されるようにすべきである。それにもかかわらず、巻上げ機構は機能を確実に発揮するように製作できるようにすべきである。   The problem underlying the present invention is to provide a winding mechanism of the above kind that avoids the above difficulties. Thereby, the hoisting mechanism should be much more reliably protected against impacts when subjected to strong impacts than before. Nevertheless, the hoisting mechanism should be able to be manufactured to function reliably.

課題は請求項１に従い、ローラがそれぞれ、衝撃時に振動重錘リングの半径方向の移動を減衰する減衰機構に配置されていることによって解決される。本発明に係る巻上げ機構の場合、ローラの軸受は固定されていないで、それぞれローラに作用する力を減衰する減衰機構上に配置されている。従って、ローラのために、比較的に高価な軸受、特にボールベアリングを使用することができる。この軸受に作用する力が減衰されるので、この軸受は比較的に長い寿命を有する。例えば、比較的に摩擦が小さく、潤滑不要である、セラミックスまたは類似の材料からなるボールベアリングが適している。ボールベアリングは特にセラミックスによって作られている。   The problem is solved according to claim 1 by the fact that the rollers are each arranged in a damping mechanism that attenuates the radial movement of the vibrating weight ring in the event of an impact. In the case of the winding mechanism according to the present invention, the roller bearings are not fixed, but are arranged on damping mechanisms that attenuate the forces acting on the rollers. Thus, relatively expensive bearings, in particular ball bearings, can be used for the rollers. Since the forces acting on the bearing are damped, the bearing has a relatively long life. For example, ball bearings made of ceramics or similar materials that are relatively low in friction and do not require lubrication are suitable. Ball bearings are especially made of ceramics.

本発明の他の実施形では、ローラがそれぞればね要素の力に逆らってほぼ半径方向に移動可能である。このようなばね要素は、ローラのきわめて適切な減衰を可能にし、比較的に簡単に製作および組み立て可能である。   In another embodiment of the invention, the rollers are each movable in a substantially radial direction against the force of the spring element. Such a spring element allows a very suitable damping of the roller and is relatively easy to manufacture and assemble.

本発明の他の実施形では、ローラがそれぞれ揺動可能に支承されている。これは、ばね要素による、きわめて簡単で確実な減衰を可能にする。この場合特に、減衰機構がそれぞれ支承板を備え、この支承板上にそれぞれ上記ローラが支承されている。この支承板は本発明の他の実施形に従い、それぞれ地板の切欠き内に支承され、ストッパによって位置決めされている。このストッパは好ましくは偏心ねじによって調節可能である。切欠きはそれぞれ、地板のエッジに設けられている。この地板の上には環状室が設けられ、この環状室内には振動重錘リングが比較的に小さな半径方向および軸方向遊びでもって支承されている。   In another embodiment of the invention, the rollers are each supported in a swingable manner. This allows a very simple and reliable damping by the spring element. In this case, in particular, each damping mechanism is provided with a support plate, and the rollers are supported on the support plate. The bearing plates are each supported in a notch in the main plate and positioned by a stopper according to another embodiment of the invention. This stopper is preferably adjustable by an eccentric screw. Each notch is provided at the edge of the main plate. An annular chamber is provided on the main plate, and a vibrating weight ring is supported in the annular chamber with relatively small radial and axial play.

振動重錘リングは基本的には、支承板内に設けられたローラによって案内される。   The vibrating weight ring is basically guided by a roller provided in the support plate.

本発明の他の実施形では、振動重錘リングの軸方向の運動が一方向においてブリッジに配置された多数の当接要素によって制限され、他の方向において地板によって制限されている。この当接要素は本発明の他の実施形ではねじである。このねじを適当に位置決めすることにより、軸方向の遊びを軸方向に正確に調節することができる。このねじは特に、ストッパを形成する周方向のエッジを備えた頭付きねじである。   In another embodiment of the invention, the axial movement of the vibrating weight ring is limited by a number of abutment elements arranged on the bridge in one direction and limited by the ground plane in the other direction. This abutment element is a screw in another embodiment of the invention. By appropriately positioning the screw, the axial play can be accurately adjusted in the axial direction. This screw is in particular a headed screw with a circumferential edge forming a stopper.

衝撃の際の振動重錘リングの半径方向の移動は好ましくは、ブリッジの外側エッジに設けたストッパによって制限される。上記の減衰機構に基づいて、このようなストッパは適切に減衰される。   The radial movement of the vibrating weight ring upon impact is preferably limited by a stopper provided on the outer edge of the bridge. Based on the damping mechanism described above, such a stopper is appropriately damped.

他の特徴は、従属請求項、次の記載および図面から明らかである。   Other features will be apparent from the dependent claims, the following description and the drawings.

次に、図に基づいて本発明の実施の形態を詳しく説明する。   Next, embodiments of the present invention will be described in detail with reference to the drawings.

本発明に係る巻上げ機構の斜視図である。It is a perspective view of the winding mechanism which concerns on this invention. 本発明に係る巻上げ機構の底面図である。It is a bottom view of the winding mechanism which concerns on this invention. 本発明に係る巻上げ機構の斜視図であり、この場合振動重錘リングが図示上の理由から地板から持ち上げられている。It is a perspective view of the winding mechanism which concerns on this invention, In this case, the vibration weight ring is lifted from the ground plane for the reason on illustration. 図５のＩＶ−ＩＶ線に沿った断面図である。It is sectional drawing along the IV-IV line of FIG. 本発明に係る巻上げ機構を備えた時計仕掛けの平面図である。It is a top view of the clockwork provided with the winding mechanism which concerns on this invention.

巻上げ機構１は、腕時計の図示していないケースに組み込むためのものであり、振動重錘リング９を備えている。この振動重錘リングは図３に示すごとく、時計仕掛けの地板２上に配置されている。振動重錘リング９は、例えば焼入れされた鋼から作られた平らなリング状振動重錘支持体３を備えている。振動重錘支持体３の上面５には、部分円状、特に半円形の振動重錘４が固定されている。この振動重錘は比較的に大きな比重を有する材料、特に金属から作られている。振動重錘支持体３は図２に示すごとくその内面に、周方向に延在する比較的に小さな歯８を備えている。この歯は地板２に支承されたピニオン２０にかみ合っている。振動重錘リング９の回転時に、ピニオン２０が回転させられ、そして図示していない伝動装置を介して巻上げばねを緊張させる。ピニオン２０は好ましくは図示していない衝撃吸収要素、例えばそれ自体公知のＩＮＣＡＢＬＯＣ耐震機構を介して支承されている。それによって、半径方向の衝撃を受けたときに、ローラ１０と支承部３３はそれに振動重錘が押し付けられても損傷しない。伝動装置は好ましくは、振動重錘リング９が両方向に作用するように形成されている。伝達は例えばそれ自体公知の一方向作用または交互作用のクラッチシステムを介して行われる。振動重錘支持体３は内側エッジ７に対して平行な外側エッジ６を有する。示唆的に示した巻上げ部材３１は公知のごとく、手による巻上げを可能にする。   The winding mechanism 1 is for incorporation into a case (not shown) of a wristwatch, and includes a vibration weight ring 9. As shown in FIG. 3, the vibration weight ring is disposed on a clockwork main plate 2. The vibrating weight ring 9 includes a flat ring-shaped vibrating weight support 3 made of, for example, hardened steel. On the upper surface 5 of the vibrating weight support 3, a partially circular, particularly semicircular vibrating weight 4 is fixed. The vibrating weight is made of a material having a relatively large specific gravity, particularly a metal. As shown in FIG. 2, the vibrating weight support 3 has relatively small teeth 8 extending in the circumferential direction on the inner surface thereof. This tooth meshes with a pinion 20 supported on the main plate 2. When the vibrating weight ring 9 is rotated, the pinion 20 is rotated and the winding spring is tensioned via a transmission device (not shown). The pinion 20 is preferably supported via a shock absorbing element, not shown, for example an INCABLOC seismic mechanism known per se. Thereby, when subjected to a shock in the radial direction, the roller 10 and the support portion 33 are not damaged even if the vibration weight is pressed against the roller 10 and the support portion 33. The transmission is preferably formed such that the vibrating weight ring 9 acts in both directions. The transmission takes place, for example, via a known one-way or interactive clutch system. The vibrating weight support 3 has an outer edge 6 parallel to the inner edge 7. As is known, the hoisting member 31 shown suggestively enables the hoisting by hand.

振動重錘リング９は図５に示すごとく、ブリッジ３２の周囲に、比較的に狭い幅で周方向に配置されている。それによって、時計仕掛けが振動重錘支持体３によって狭い範囲しか覆われないので、時計仕掛けは図示していない窓、例えばケースの底に設けた窓から見える。   As shown in FIG. 5, the vibration weight ring 9 is arranged around the bridge 32 in the circumferential direction with a relatively narrow width. Thereby, since the clockwork is covered only in a narrow range by the vibration weight support 3, the clockwork can be seen from a window (not shown), for example, a window provided at the bottom of the case.

振動重錘９は内側エッジ７のところで３個のローラ１０に支承されている。このローラは振動重錘９の幾何学的な軸線に対して等しい間隔をおいて支承されている。ローラ１０はそれぞれ、周方向の溝１０ａを有している。この溝には振動重錘支持体３の上記内側エッジ７が係合し、それによって振動重錘支持体はこの高さ位置で案内されている。ローラ１０はそれぞれ下端においてボールベアリング３３によって減衰機構２２の支承板１２に回転可能に支承されている。ボールベアリング３３は支承板１２の穴１１に挿入されている。ボールベアリング３３は例えばセラミックス製のボールを備えている。ローラ１０は例えばＤＬＣ（ダイヤモンド・ライク・カーボン）からなり、振動重錘リング９は焼入れされた鋼からなっている。基本的には、ボールベアリング３３の代わりに、摩擦の小さな他の軸受を使用することができる。   The vibrating weight 9 is supported by three rollers 10 at the inner edge 7. This roller is supported at equal intervals with respect to the geometric axis of the vibrating weight 9. Each of the rollers 10 has a circumferential groove 10a. The groove is engaged with the inner edge 7 of the vibrating weight support 3 so that the vibrating weight support is guided at this height position. Each of the rollers 10 is rotatably supported on the support plate 12 of the damping mechanism 22 by a ball bearing 33 at the lower end. The ball bearing 33 is inserted into the hole 11 of the support plate 12. The ball bearing 33 includes, for example, ceramic balls. The roller 10 is made of, for example, DLC (Diamond Like Carbon), and the vibration weight ring 9 is made of hardened steel. Basically, instead of the ball bearing 33, another bearing having a small friction can be used.

減衰機構２２はそれぞれ、地板２の切欠き１５内に配置され、固定ねじ３４によって地板に揺動可能に支承されている。固定ねじ３４はそれぞれ、ローラ１０に対して間隔をおいて配置された穴１３を通過し、地板２のねじ穴３５にねじ込まれている。固定ねじ３４は、支承板１２がそれぞれ切欠き１５内で制限されて揺動できるように形成されている。同様に、ローラ１０に対して間隔をおいて、支承板１２はそれぞれ突起１４を備えている。この突起には、特に図２から明らかなように、ばね要素１６のばねアーム１７が作用する。ばね要素１６はそれぞれ固定ねじ１８によって地板２に固定連結されている。固定ねじ３４と突起１４の間隔は、ローラ１０と突起の間隔よりも大きい。ばね要素１６は支承板１２を静止位置に保持する。この静止位置は切欠き１５内でストッパ３６（図３）によって定めることが可能である。このストッパの少なくとも１個は偏心ねじ３６ａによって形成される。この偏心ねじによって、振動重錘リング９の半径方向遊びを調節することができる。支承板１２はそれぞれ、上記静止位置から、ばね要素１６の戻し力に逆らって、対応するローラ１０がほぼ半径方向内側に移動するように揺動可能である。衝撃の結果半径方向の力が振動重錘リング９に作用すると、この半径方向の力は少なくとも１個のローラ１０に作用する。このローラはばね要素１６の戻し力に逆らって動く。従って、この半径方向運動が減衰機構２２によって減衰させられる。振動重錘リング９または振動重錘支持体３が図４に示したブリッジ３２の外周面３０に当接することにより、この半径方向運動は制限される。   Each of the damping mechanisms 22 is disposed in the notch 15 of the ground plane 2 and is supported on the ground plane by a fixing screw 34 so as to be swingable. Each fixing screw 34 passes through a hole 13 arranged at a distance from the roller 10 and is screwed into a screw hole 35 in the main plate 2. The fixing screw 34 is formed so that the support plate 12 can swing while being limited in the notch 15. Similarly, the support plate 12 is provided with a protrusion 14 at a distance from the roller 10. A spring arm 17 of the spring element 16 acts on this protrusion, as is apparent from FIG. Each spring element 16 is fixedly connected to the main plate 2 by a fixing screw 18. The distance between the fixing screw 34 and the protrusion 14 is larger than the distance between the roller 10 and the protrusion. The spring element 16 holds the bearing plate 12 in a stationary position. This rest position can be determined in the notch 15 by a stopper 36 (FIG. 3). At least one of the stoppers is formed by an eccentric screw 36a. With this eccentric screw, the radial play of the vibrating weight ring 9 can be adjusted. Each of the support plates 12 is swingable from the stationary position so that the corresponding roller 10 moves substantially radially inward against the return force of the spring element 16. When a radial force acts on the vibrating weight ring 9 as a result of the impact, this radial force acts on at least one roller 10. This roller moves against the return force of the spring element 16. Therefore, this radial motion is damped by the damping mechanism 22. This radial motion is limited by the vibrating weight ring 9 or the vibrating weight support 3 coming into contact with the outer peripheral surface 30 of the bridge 32 shown in FIG.

衝撃の場合さらに、軸方向の力が振動重錘リング９に作用する。これにより、振動重錘リングは軸方向に運動する。この運動は一方向において、図４に示した地板の表面２３によって制限される。他の方向では、軸方向の運動は３個のねじ２６によって制限される。このねじはそれぞれ、図４に示すように、ブリッジ３２のねじ穴２８にねじ込まれている。ねじ２６は図５に示すごとく、等間隔をおいてそれぞれブリッジ３２のエッジ領域に配置され、その際それぞれ頭２７が振動重錘リング９のエッジ２５を覆っている。静止状態では、エッジ２５がそれぞれ、図４に示すように、振動重錘リング９の上面２４から離して配置されている。振動重錘支持体３の下面と表面２３も互いに離れている。それによって、静止位置では、振動重錘支持体３はローラ１０にのみ接触している。従って、振動重錘リング９はその幾何学的軸線を中心としてその周方向に比較的に小さな摩擦で回転することができる。   Further, in the case of an impact, an axial force acts on the vibrating weight ring 9. Thereby, the vibrating weight ring moves in the axial direction. This movement is limited in one direction by the surface 23 of the main plate shown in FIG. In the other direction, the axial movement is limited by three screws 26. Each of these screws is screwed into the screw hole 28 of the bridge 32 as shown in FIG. As shown in FIG. 5, the screws 26 are arranged at equal intervals in the edge region of the bridge 32, and the heads 27 cover the edges 25 of the vibrating weight ring 9. In the stationary state, the edges 25 are arranged away from the upper surface 24 of the vibrating weight ring 9 as shown in FIG. The lower surface and the surface 23 of the vibration weight support 3 are also separated from each other. Thereby, the vibration weight support 3 is in contact with only the roller 10 in the stationary position. Accordingly, the vibrating weight ring 9 can rotate with relatively little friction in the circumferential direction around the geometric axis.

１ 巻上げ機構
２ 地板
３ 振動重錘支持体
４ 振動重錘
５ 上面
６ 外側エッジ
７ 内側エッジ
８ 歯
９ 振動重錘リング
１０ ローラ
１０ａ 溝
１１ 穴
１２ 支承板
１３ 穴
１４ 突起
１５ 切欠き
１６ ばね要素
１７ ばねアーム
１８ 固定ねじ
１９ 切欠き
２０ ピニオン
２２ 減衰機構
２３ 表面
２４ 上面
２５ エッジ
２６ ねじ
２７ 頭
２８ ねじ穴
２９ ブリッジ
３０ 外周面
３１ 巻上げ部材
３２ ブリッジ
３３ 軸受
３４ 固定ねじ
３５ ねじ穴
３６ ストッパ
３６ａ 偏心ねじ DESCRIPTION OF SYMBOLS 1 Winding mechanism 2 Ground plate 3 Vibration weight support body 4 Vibration weight 5 Upper surface 6 Outer edge 7 Inner edge 8 Tooth 9 Vibration weight ring 10 Roller 10a Groove 11 Hole 12 Bearing plate 13 Hole 14 Protrusion 15 Notch 16 Spring element 17 Spring arm 18 Fixing screw 19 Notch 20 Pinion 22 Damping mechanism 23 Surface 24 Upper surface 25 Edge 26 Screw 27 Head 28 Screw hole 29 Bridge 30 Outer peripheral surface 31 Lifting member 32 Bridge 33 Bearing 34 Fixing screw 35 Screw hole 36 Stopper 36a Eccentric screw

Claims (16)

振動重錘リング（９）を備え、この振動重錘リングの幾何学的軸線が時計仕掛けの幾何学的軸線とほぼ一致するように、振動重錘リングが時計仕掛け内で多数のローラ（１０）に回転自在に支承され、振動重錘リング（９）の回転運動が例えば振動重錘リング（９）の歯（８）を介して時計仕掛けに伝達可能である、時計用の自動巻上げ機構において、
ローラ（１０）がそれぞれ、衝撃時に振動重錘リング（９）の半径方向の移動を減衰する減衰機構（２２）に支承されていることを特徴とする巻上げ機構。 The vibrating weight ring (9) is provided with a number of rollers (10) in the clockwork so that the geometric axis of the vibrating weight ring substantially coincides with the geometrical axis of the clockwork. In the automatic winding mechanism for a watch, the rotary motion of the vibrating weight ring (9) can be transmitted to the clockwork via the teeth (8) of the vibrating weight ring (9), for example.
A winding mechanism characterized in that each roller (10) is supported by a damping mechanism (22) for damping the radial movement of the vibrating weight ring (9) upon impact. 減衰機構（２２）がそれぞればね要素（１６）を備えていることを特徴とする請求項１に記載の巻上げ機構。   Winding mechanism according to claim 1, characterized in that each damping mechanism (22) comprises a spring element (16). ばね要素（１６）がそれぞればねアーム（１７）を備えていることを特徴とする請求項２に記載の巻上げ機構。   3. Winding mechanism according to claim 2, characterized in that each spring element (16) comprises a spring arm (17). ローラ（１０）がそれぞれボールベアリング（３３）に支承されていることを特徴とする請求項１〜３のいずれか一項に記載の巻上げ機構。   The winding mechanism according to any one of claims 1 to 3, wherein each of the rollers (10) is supported by a ball bearing (33). ボールベアリング（３３）がセラミック軸受であるかまたは摩擦の小さなコーティングを備えていることを特徴とする請求項４に記載の巻上げ機構。   5. Winding mechanism according to claim 4, characterized in that the ball bearing (33) is a ceramic bearing or is provided with a low friction coating. 減衰機構（２２）がそれぞれ支承板（１２）を備え、前記各ローラがこの支承板に回転可能に支承されていることを特徴とする請求項１〜５のいずれか一項に記載の巻上げ機構。   The winding mechanism according to any one of claims 1 to 5, wherein each of the damping mechanisms (22) includes a support plate (12), and each of the rollers is rotatably supported by the support plate. . 支承板（１２）がそれぞれ切欠き（１５）内に支承されていることを特徴とする請求項６に記載の巻上げ機構。   7. Winding mechanism according to claim 6, characterized in that the support plates (12) are each supported in a notch (15). 支承板（１２）がそれぞれ地板（２）に揺動可能に支承されていることを特徴とする請求項６または７に記載の巻上げ機構。   The winding mechanism according to claim 6 or 7, characterized in that each of the support plates (12) is swingably supported by the main plate (2). 支承板（１２）がそれぞれ、揺動軸線から離れたところに突起（１４）を備え、支承板（１２）をストッパ（３６）に押し付けるばね要素（１６）が前記突起に作用していることを特徴とする請求項８に記載の巻上げ機構。   Each of the support plates (12) is provided with a protrusion (14) at a position away from the swing axis, and a spring element (16) that presses the support plate (12) against the stopper (36) acts on the protrusion. The winding mechanism according to claim 8, wherein 少なくとも１個のストッパ（３６）が偏心ねじ（３６ａ）によって形成されていることを特徴とする請求項９に記載の巻上げ機構。   10. Winding mechanism according to claim 9, characterized in that at least one stopper (36) is formed by an eccentric screw (36a). 衝撃の結果としての振動重錘リング（９）の軸方向運動が、一方向において多数の当接要素（２６）によって制限され、他の方向において地板（２）によって制限されていることを特徴とする請求項１〜１０のいずれか一項に記載の巻上げ機構。   The axial movement of the vibrating weight ring (9) as a result of the impact is limited by a number of abutment elements (26) in one direction and by the ground plane (2) in the other direction. The winding mechanism according to any one of claims 1 to 10. 当接要素（２６）がそれぞれブリッジ（３２）に固定されたねじであることを特徴とする請求項１１に記載の巻上げ機構。   12. Winding mechanism according to claim 11, characterized in that the abutment elements (26) are screws each fixed to the bridge (32). 等間隔に配置した３個の当接要素（２６）が設けられていることを特徴とする請求項１１または１２に記載の巻上げ機構。   13. Winding mechanism according to claim 11 or 12, characterized in that three abutment elements (26) arranged at equal intervals are provided. 振動重錘リング（９）の半径方向移動が、１個または複数のブリッジ（３２）の周面（３０）によってあるいは他の要素によって制限されていることを特徴とする請求項１〜１３のいずれか一項に記載の巻上げ機構。   14. The radial movement of the vibrating weight ring (9) is limited by the peripheral surface (30) of one or more bridges (32) or by other elements. A winding mechanism according to claim 1. 振動重錘リング（９）が平らなリングとして形成された振動重錘支持体（３）を備え、この振動重錘支持体が内側エッジ（７）に、周方向に延在する歯（８）を備えていることを特徴とする請求項１〜１４のいずれか一項に記載の巻上げ機構。   The vibrating weight ring (9) includes a vibrating weight support (3) formed as a flat ring, and the vibrating weight support is provided on the inner edge (7) with teeth extending in the circumferential direction (8). The winding mechanism according to any one of claims 1 to 14, wherein the winding mechanism is provided. 振動重錘支持体（３）の上面に円形の振動重錘（４）が固定されていることを特徴とする請求項１５に記載の巻上げ機構。   The winding mechanism according to claim 15, characterized in that a circular vibrating weight (4) is fixed to the upper surface of the vibrating weight support (3).
JP2009036373A 2008-02-22 2009-02-19 Automatic winding mechanism for watches Active JP5414301B2 (en)

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JP7381745B2 (en) 2019-12-18 2023-11-15 ザ・スウォッチ・グループ・リサーチ・アンド・ディベロップメント・リミテッド Oscillating winding weight with decorative elements for automatic timepiece movements

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