JP5975808B2 - Switch operating mechanism - Google Patents
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- JP5975808B2 JP5975808B2 JP2012199050A JP2012199050A JP5975808B2 JP 5975808 B2 JP5975808 B2 JP 5975808B2 JP 2012199050 A JP2012199050 A JP 2012199050A JP 2012199050 A JP2012199050 A JP 2012199050A JP 5975808 B2 JP5975808 B2 JP 5975808B2
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- 210000000078 claw Anatomy 0.000 claims description 79
- 230000005540 biological transmission Effects 0.000 claims description 16
- 238000004146 energy storage Methods 0.000 claims description 6
- 230000001360 synchronised effect Effects 0.000 description 18
- 238000010586 diagram Methods 0.000 description 11
- 239000011295 pitch Substances 0.000 description 8
- 238000000034 method Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 238000009825 accumulation Methods 0.000 description 3
- 206010044048 Tooth missing Diseases 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 208000004188 Tooth Wear Diseases 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
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- Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
Description
この発明は、例えば電力系統の保護や開閉を行うための開閉器の操作機構に関し、特に操作機構における大歯車と小歯車との噛み合い構造に関するものである。 The present invention relates to an operation mechanism of a switch for protecting or switching an electric power system, for example, and more particularly to a meshing structure of a large gear and a small gear in the operation mechanism.
従来、開閉器の操作機構において、カムと同心に固定して設けられていると共に一部に欠歯部が形成されその欠歯部に溝部が設けられている大歯車と、この大歯車と噛み合いかつ駆動源により回転駆動される小歯車と、大歯車の欠歯部に形成された溝部に一方側を揺動自在に支持して、少なくとも２個の第１歯、第２歯を有する１個の同期爪と、この同期爪の他方側を押圧するばねとを備えている。 Conventionally, in a switch operating mechanism, a large gear that is fixedly provided concentrically with a cam and has a partially-toothed portion and a groove portion in the partially-toothed portion is engaged with the large gear. One having at least two first teeth and second teeth with a small gear rotatably driven by a driving source and a groove formed in a toothless portion of the large gear so that one side can swing freely. And a spring that presses the other side of the synchronization claw.
同期爪は、投入ばねの蓄勢完了直後に小歯車と同期爪の他方側に位置する第１歯と噛み合う位置にあり、同期爪の一方側に位置する第２歯が閉路動作開始後に噛み合うように形成されて、小歯車が大歯車と円滑に再噛み合い可能に構成されているものがある。なお、同期爪の第１歯と第２歯との間は、１歯分が欠落した状態となっている。 The synchronization pawl is in a position where it meshes with the first gear located on the other side of the small gear and the synchronization pawl immediately after the completion of the energization of the closing spring, and the second tooth located on one side of the synchronization pawl is meshed after the closing operation is started. In some cases, the small gear is configured to be able to smoothly re-engage with the large gear. In addition, between the 1st tooth | gear and 2nd tooth | gear of a synchronous nail | claw, it is in the state which lost one tooth part.
上述した従来の開閉器の操作機構は、１個の同期爪に設けられた第１歯と第２歯との間は、１歯分が欠落した状態で欠歯となっており、閉路動作開始後、小歯車と同期爪の欠歯の１ピッチ分だけ大歯車が加速回転して、同期爪の第２歯で衝突し係合するため、衝撃力が発生する。このときの衝撃力は大歯車の回転速度と大歯車に連結された投入ばねロッドおよび投入ばね、カム、カム軸等を含んだ回転慣性の積、所謂角運動量で静止した小歯車と衝突する。その結果、生ずる力であり、大歯車の回転速度に比例して衝撃力が大きくなる。衝撃力が大きくなると、同期爪の第２歯の歯面と小歯車の面圧が高くなり、蓄勢動作回数が多い場合は第２歯の磨耗が多くなるという問題があった。 The operation mechanism of the conventional switch described above has a missing tooth with one tooth missing between the first tooth and the second tooth provided on one synchronous claw, and the closing operation starts. Thereafter, the large gear is accelerated and rotated by one pitch of the small gear and the missing tooth of the synchronous claw, and collides with and engaged with the second tooth of the synchronous claw, so that an impact force is generated. The impact force at this time collides with a small gear stationary at a so-called angular momentum, which is the product of rotational inertia including the rotational speed of the large gear and the closing spring rod and closing spring connected to the large gear, the closing spring, the cam, and the camshaft. As a result, this is a generated force, and the impact force increases in proportion to the rotational speed of the large gear. When the impact force is increased, the tooth pressure of the second tooth of the synchronous claw and the surface pressure of the small gear are increased, and there is a problem that the second tooth is worn when the number of energy accumulation operations is large.
この発明は、上記のような課題を解決するためになされたものであり、衝撃力が少なく歯の磨耗が少ない多回数の蓄勢動作に耐え得る開閉器の操作機構を提供することを目的とするものである。 The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a switch operating mechanism that can withstand a large number of energy storage operations with low impact force and low tooth wear. To do.
この発明に係わる開閉器の操作機構は、電路を開閉する開閉器を駆動する駆動レバーと、前記駆動レバーを操作する操作手段とを備え、前記操作手段は、回転エネルギーを発生する電動機と、前記電動機の回転エネルギーが伝達される第１の伝達機構と、前記第１の伝達機構と係合され一部に欠歯部が形成された第２の伝達機構と、前記第２の伝達機構に連結された蓄勢機構と、前記第２の伝達機構の欠歯部が形成された切り欠き部と、前記切り欠き部に一方側を揺動自在に支持して配設され、少なくとも２個の第１歯、第２歯を有し、前記第１歯と前記第２歯間の一ピッチ分は欠歯に構成された第１の同期爪と、前記切り欠き部に前記第１の同期爪と並列に配置されるとともに一方側を揺動自在に支持して配設され、前記第１の同期爪の前記第１歯と前記第２歯との間の欠歯位置に第３歯を有する第２の同期爪とから構成されたものである。 A switch operating mechanism according to the present invention includes a drive lever that drives a switch that opens and closes an electric circuit, and an operation unit that operates the drive lever, wherein the operation unit includes a motor that generates rotational energy, Connected to the first transmission mechanism for transmitting the rotational energy of the electric motor, the second transmission mechanism that is engaged with the first transmission mechanism and partially formed with a missing tooth portion, and the second transmission mechanism And a notch portion in which a toothless portion of the second transmission mechanism is formed, and one side of the notch portion is swingably supported by the notch portion. A first synchronous claw having one tooth and a second tooth, the pitch between the first tooth and the second tooth being configured as a missing tooth; and the first synchronous claw at the notch Arranged in parallel and supported by one side so as to be swingable, in front of the first synchronizing claw Those made up of a second synchronization pawl having a third tooth missing tooth position between the second teeth and the first teeth.
この発明に係わる開閉器の操作機構によれば、安価で多回数の開閉回数に耐え得る開閉器の操作機構を得ることができる。 According to the switch operating mechanism according to the present invention, it is possible to obtain a switch operating mechanism that is inexpensive and can withstand a large number of switching operations.
実施の形態１．
以下、この発明の実施の形態１を図１ないし図９に基づいて説明するが、各図において、同一、または相当部材、部位については同一符号を付して説明する。図１はこの発明の実施の形態１に係わる開閉器の操作機構における閉路状態を示す構成図である。図２はこの発明の実施の形態１に係わる開閉器の操作機構における開路状態を示す構成図である。図３はこの発明の実施の形態１に係わる開閉器の操作機構を示す構成図である。図４はこの発明の実施の形態１に係わる開閉器の操作機構における図３の左側面図である。図５はこの発明の実施の形態１に係わる開閉器の操作機構における図３の右側面図である。図６はこの発明の実施の形態１に係わる開閉器の操作機構における図３のＡ−Ａ線の他方側断面図である。図７はこの発明の実施の形態１に係わる開閉器の操作機構における大歯車と小歯車と第１同期爪および第２同期爪を示す斜視図である。図８はこの発明の実施の形態１に係わる開閉器の操作機構における大歯車と小歯車と第１同期爪および第２同期爪を示す正面図である。図９はこの発明の実施の形態１に係わる開閉器の操作機構における大歯車と第１同期爪および第２同期爪を示す大歯車の欠歯部外周側より見た図である。
Embodiment 1 FIG.
Hereinafter, Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 9. In each figure, the same or equivalent members and parts will be described with the same reference numerals. 1 is a configuration diagram showing a closed state in an operating mechanism of a switch according to Embodiment 1 of the present invention. FIG. 2 is a configuration diagram showing an open circuit state in the switch operating mechanism according to the first embodiment of the present invention. FIG. 3 is a block diagram showing the operating mechanism of the switch according to Embodiment 1 of the present invention. 4 is a left side view of FIG. 3 in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 5 is a right side view of FIG. 3 in the operating mechanism of the switch according to Embodiment 1 of the present invention. 6 is a cross-sectional side view taken along line AA of FIG. 3 in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 7 is a perspective view showing a large gear, a small gear, a first synchronization claw, and a second synchronization claw in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 8 is a front view showing a large gear, a small gear, a first synchronization claw, and a second synchronization claw in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 9 is a view as seen from the outer peripheral side of the toothless portion of the large gear showing the large gear, the first synchronizing pawl, and the second synchronizing pawl in the switch operating mechanism according to Embodiment 1 of the present invention.
これら各図において、１は真空バルブ、２は真空バルブ１内に配置され、固定通電軸３に固着された固定側電極であり、固定通電軸３を通して上部側ジャンクション４と電気的に接続される。５は真空バルブ１内に配置され、固定側電極２と相対して対向し可動通電軸６に固着された可動側電極であり、可動通電軸６を通して下部側ジャンクション７と電気的に接続される。８は絶縁された操作ロッドであり、この操作ロッド８の一方側、すなわち、上端側が可動通電軸６の真空バルブ１外に延在する下端部に取り付けられ、この操作ロッド８の他方側、すなわち、下端側が基台フレーム９内に挿通されて基台フレーム９内に位置している。 In each of these drawings, 1 is a vacuum valve, 2 is a fixed side electrode disposed in the vacuum valve 1 and fixed to the fixed energizing shaft 3, and is electrically connected to the upper junction 4 through the fixed energizing shaft 3. . Reference numeral 5 denotes a movable side electrode which is disposed in the vacuum valve 1 and is opposed to the fixed side electrode 2 and fixed to the movable energizing shaft 6, and is electrically connected to the lower junction 7 through the movable energizing shaft 6. . Reference numeral 8 denotes an insulated operating rod, and one side, that is, the upper end side of the operating rod 8 is attached to a lower end portion extending outside the vacuum valve 1 of the movable energizing shaft 6, and the other side of the operating rod 8, that is, The lower end side is inserted into the base frame 9 and positioned in the base frame 9.
１０は軸心を真空バルブ１の固定側電極２と可動側電極５間の開閉方向、すなわち、操作ロッド８の軸心と直交するように配設された支軸であり、基台フレーム９内に軸支されている。１１は支軸１０に固着された駆動レバーであり、この駆動レバー１１の一方側１１ａが後述する操作機構部１００である出力リンク１１０の一方側１１０ａに連結ピン１２により連結され、駆動レバー１１を介して支軸１０を回動させる。
また、駆動レバー１１の他方側１１ｂは操作ロッド８の下端側である他方側に回動自在に連結ピン１３により連結されている。操作機構部１００の動作により、駆動レバー１１を介して支軸１０を回動させることによって操作ロッド８が上下方向に作動され、真空バルブ１の固定側電極２と可動側電極５間の開極動作および閉極動作が行われる。
Reference numeral 10 denotes a support shaft whose axis is arranged so as to be orthogonal to the opening / closing direction between the fixed electrode 2 and the movable electrode 5 of the vacuum valve 1, that is, the axis of the operation rod 8. Is pivotally supported. Reference numeral 11 denotes a drive lever fixed to the support shaft 10, and one side 11a of the drive lever 11 is connected to one side 110a of an output link 110 which is an operation mechanism unit 100 described later by a connection pin 12, and the drive lever 11 is The support shaft 10 is rotated through.
The other side 11b of the drive lever 11 is connected to the other side, which is the lower end side of the operating rod 8, by a connecting pin 13 so as to be freely rotatable. By the operation of the operation mechanism unit 100, the operation rod 8 is operated in the vertical direction by rotating the support shaft 10 via the drive lever 11, and the opening between the fixed side electrode 2 and the movable side electrode 5 of the vacuum valve 1 is opened. Operation and closing operation are performed.
操作機構部１００は、電動機１０１と、電動機１０１の出力歯車１０２により中歯車１０３に係合されて駆動される蓄勢軸１０４と、蓄勢軸１０４に中歯車１０３と同心状に設けられた中歯車１０３とともに第１の伝達機構を構成する小歯車１０５と、小歯車１０５に係合されてカム軸１０６と同心状に設けられ、一部に欠歯部１０７ａが形成された第２の伝達機構を構成する大歯車１０７と、大歯車１０７とカム軸１０６を介して一体的に構成され、大歯車１０７と連動して回動する投入カム１０８と、一方側が投入カム１０８と係合され、主軸１０９を支点として回動可能に構成され、他方側が出力リンク１１０の他方側１１０ｂと連結ピン１１１により連結される出力レバー１１２と、一方側１１３ａが連結ピン１１４を介して大歯車１０７に枢着され、他方側１１３ｂが投入ばね座１１５を介して投入ばね１１６が装着され、大歯車１０７の回動により投入ばね１１６を蓄勢および放勢する投入ばねロッド１１３とから構成されている。投入ばねロッド１１３と投入ばね１１６などにより蓄勢機構が構成される。 The operation mechanism unit 100 includes an electric motor 101, an accumulator shaft 104 that is driven by being engaged with an intermediate gear 103 by an output gear 102 of the electric motor 101, and an intermediate shaft provided concentrically with the intermediate gear 103 on the accumulator shaft 104. A small gear 105 that constitutes a first transmission mechanism together with the gear 103, and a second transmission mechanism that is engaged with the small gear 105 and provided concentrically with the cam shaft 106, and in which part of the toothless portion 107a is formed. A large gear 107, a large gear 107 and a camshaft 106, which are integrated with each other, and a closing cam 108 that rotates in conjunction with the large gear 107, and one side is engaged with the closing cam 108, and the main shaft 109 is configured to be rotatable about a fulcrum, the other side is connected to the other side 110b of the output link 110 by the connecting pin 111, and the one side 113a is connected to the large pin through the connecting pin 114. The closing spring 116 is mounted on the other side 113b via the closing spring seat 115, and is composed of a closing spring rod 113 that stores and releases the closing spring 116 by rotation of the large gear 107. Yes. An energizing mechanism is constituted by the closing spring rod 113 and the closing spring 116.
１１７はフレーム、１１８は一方側１１８ａが連結ピン１１９を介して出力レバー１１２に枢着され、他方側１１８ｂが開放ばね座１２０を介して開放ばね１２１が装着された開放ばねロッド、１２２はリミットスイッチ、１２３は投入コイル、１２４は投入ラッチ、１２５は投入ラッチ１２４と係合する投入ラッチピン、１２６は投入トリガー、１２７は引き外しラッチ、１２８は引き外しラッチピン、１２９は引き外しトリガーである。 117 is a frame, 118 is one side 118a pivotally connected to the output lever 112 via a connecting pin 119, and the other side 118b is an open spring rod to which an open spring 121 is attached via an open spring seat 120, 122 is a limit switch , 123 is a closing coil, 124 is a closing latch, 125 is a closing latch pin that engages with the closing latch 124, 126 is a closing trigger, 127 is a releasing latch, 128 is a releasing latch pin, and 129 is a releasing trigger.
１３０は大歯車１０７の欠歯部１０７ａに形成された切り欠き部であり、例えば、図９に示すように、大歯車１０７の欠歯部１０７ａの板厚方向中央部に凹形状溝部として構成された場合を示している。
１３１は大歯車１０７の欠歯部１０７ａに形成された凹形状溝部である切り欠き部１３０に一方側を揺動自在に支持して配設され、少なくとも２個の第１歯１３１ａ、第２歯１３１ｂを有する第１の同期爪であり、第１歯１３１ａと第２歯１３１ｂ間の一ピッチ分は欠歯となっている。
１３２は大歯車１０７の欠歯部１０７ａに形成された凹形状溝部である切り欠き部１３０に第１の同期爪１３１と並列に配置されるとともに一方側を揺動自在に支持して配設され、第１の同期爪１３１の第１歯１３１ａと第２歯１３１ｂとの間の欠歯位置に第３歯１３２ａを有する第２の同期爪である。
Reference numeral 130 denotes a notch formed in the missing tooth portion 107a of the large gear 107, and is configured as a concave groove portion at the center in the thickness direction of the missing tooth portion 107a of the large gear 107, for example, as shown in FIG. Shows the case.
Reference numeral 131 denotes a notch portion 130 which is a concave groove portion formed in the missing tooth portion 107a of the large gear 107, and is supported by one side so as to be swingable. At least two first teeth 131a and second teeth are arranged. It is the 1st synchronous claw which has 131b, and one pitch part between the 1st tooth 131a and the 2nd tooth 131b is a missing tooth.
132 is disposed in parallel with the first synchronization pawl 131 and supported on one side so as to be swingable in a notch 130 which is a concave groove formed in the toothless portion 107 a of the large gear 107. The second synchronous claw having the third tooth 132a at the missing tooth position between the first tooth 131a and the second tooth 131b of the first synchronous claw 131.
第１の同期爪１３１と第２の同期爪１３２とは同期軸１３３を支点として揺動自在に回転できるように支持されており、第１の同期爪１３１および第２の同期爪１３２の歯形が大歯車７の歯形とピッチ円が同じとなるような位置に大歯車７に軸着されたピン１３４によって位置規制されている。
１３５は第１の同期爪１３１の他方側を押圧する第１復帰ばねであり、１３６は第２の同期爪１３２の他方側を押圧する第２復帰ばねであり、小歯車１０５と噛み合わない場合、第１の同期爪１３１および第２の同期爪１３２をピン１３４に押圧している。
The first synchronization claw 131 and the second synchronization claw 132 are supported so as to be able to swing freely around the synchronization shaft 133, and the tooth shapes of the first synchronization claw 131 and the second synchronization claw 132 are the same. The position of the large gear 7 is restricted by a pin 134 attached to the large gear 7 at a position where the tooth profile and the pitch circle are the same.
135 is a first return spring that presses the other side of the first synchronization pawl 131, 136 is a second return spring that presses the other side of the second synchronization pawl 132, and does not mesh with the small gear 105, The first synchronization claw 131 and the second synchronization claw 132 are pressed against the pin 134.
次に、このように構成された機構の動作について説明する。駆動レバー１１は開放ばね１２１によって反時計方向に回転力を与えている主軸１０９に固定された出力レバー１１２に連結されており、引き外しラッチ１２７と引き外しラッチピン１２８との係合によって投入位置を維持している。引き外しトリガー１２９によって引き外しラッチ１２７が反時計方向に回転すると出力リンク１１０が上方に移動し、出力リンク１１０の上方への移動により駆動レバー１１が支軸１０を支点として時計方向に回転する。駆動レバー１１が支軸１０を支点として時計方向に回転すると操作ロッド８が下方側に移動し、操作ロッド８に連結された可動通電軸６も下方側に移動して可動側電極５が開路される。 Next, the operation of the mechanism configured as described above will be described. The drive lever 11 is connected to an output lever 112 fixed to the main shaft 109 which provides a counterclockwise rotational force by an opening spring 121, and the engagement position is set by engagement of the release latch 127 and the release latch pin 128. Is maintained. When the trip latch 127 rotates counterclockwise by the trip trigger 129, the output link 110 moves upward, and the drive lever 11 rotates clockwise about the support shaft 10 by the upward movement of the output link 110. When the drive lever 11 rotates clockwise with the support shaft 10 as a fulcrum, the operating rod 8 moves downward, the movable energizing shaft 6 connected to the operating rod 8 also moves downward, and the movable electrode 5 is opened. The
カム軸１０６に固定され、カム軸１０６とともに回転するようになっている大歯車１０７の中心とその側面に設けられた連結ピン１１４の間をクランク、投入ばね１１６が反時計方向、大歯車１０７の側面に設けられた連結ピン１１４と投入ばねロッド１１３を連結棒として、てこクランク機構（以下、単に機構と呼ぶ）を形成している。 A crank is inserted between the center of the large gear 107 fixed to the cam shaft 106 and is rotated together with the cam shaft 106 and a connecting pin 114 provided on the side surface thereof. A lever crank mechanism (hereinafter simply referred to as a mechanism) is formed by using a connecting pin 114 and a closing spring rod 113 provided on the side surface as a connecting rod.
大歯車１０７は投入ラッチ１２４によって機構の思案点からわずかに時計方向にずれた投入待機位置で静止している。投入ラッチ１２４が反時計方向に回転すると、投入ばね１１６に蓄勢している機械エネルギーによって、大歯車１０７は反時計方向に回転する。
大歯車１０７とともにカム軸１０６に固定している投入カム１０８が回転して開放位置にある駆動レバー１１を開放ばね１２１の回転力に抗して投入位置に復帰させる。すなわち、出力リンク１１０が下方に移動し、出力リンク１１０の下方への移動により駆動レバー１１が支軸１０を支点として反時計方向に回転する。駆動レバー１１が支軸１０を支点として反時計方向に回転すると操作ロッド８が上方側に移動し、操作ロッド８に連結された可動通電軸６も上方側に移動して可動側電極５が閉路される。
大歯車１０７と噛み合っている小歯車１０５が反時計方向に回転すると、投入ばね１１６の回転力に抗して大歯車１０７を時計方向に回転させ、図１に示す状態に復帰する。以上に述べた各要素がフレーム１１７に組み込まれ操作機構部を形成している。
The large gear 107 is stopped at the closing standby position slightly shifted clockwise from the thought point of the mechanism by the closing latch 124. When the closing latch 124 rotates counterclockwise, the large gear 107 rotates counterclockwise by the mechanical energy stored in the closing spring 116.
The closing cam 108 fixed to the cam shaft 106 together with the large gear 107 rotates to return the driving lever 11 in the open position to the closing position against the rotational force of the opening spring 121. That is, the output link 110 moves downward, and the drive lever 11 rotates counterclockwise about the support shaft 10 by the downward movement of the output link 110. When the drive lever 11 rotates counterclockwise with the support shaft 10 as a fulcrum, the operating rod 8 moves upward, the movable energizing shaft 6 connected to the operating rod 8 also moves upward, and the movable electrode 5 is closed. Is done.
When the small gear 105 meshed with the large gear 107 rotates counterclockwise, the large gear 107 rotates clockwise against the rotational force of the closing spring 116, and returns to the state shown in FIG. Each element described above is incorporated in the frame 117 to form an operation mechanism section.
次に、大歯車１０７と小歯車１０５との噛み合い部の動作について説明する。大歯車１０７の小歯車１０５と対向する部分は図７および図８に示すように所定数の歯が取り除かれた欠歯部１０７ａが形成され、さらにその欠歯部１０７ａに例えば板厚方向中央部に凹形状溝部として切り欠き部１３０を設けている。
この大歯車１０７の欠歯部１０７ａに形成した切り欠き部１３０内部には、大歯車１０７の歯形と同形の少なくとも２個の第１歯１３１ａ、第２歯１３１ｂを有する第１の同期爪１３１が配設され、第１の同期爪１３１の第１歯１３１ａと第２歯１３１ｂ間の一ピッチ分の１個は欠歯となっている。
Next, the operation of the meshing portion between the large gear 107 and the small gear 105 will be described. As shown in FIGS. 7 and 8, a portion of the large gear 107 facing the small gear 105 is formed with a missing tooth portion 107a from which a predetermined number of teeth are removed, and the missing tooth portion 107a is, for example, a central portion in the thickness direction. A notch 130 is provided as a concave groove.
A first synchronous claw 131 having at least two first teeth 131a and second teeth 131b having the same shape as the tooth shape of the large gear 107 is provided in the notch portion 130 formed in the toothless portion 107a of the large gear 107. One of the pitches between the first teeth 131a and the second teeth 131b of the first synchronization pawl 131 is missing.
また、大歯車１０７の欠歯部１０７ａに形成した切り欠き部１３０内部には、第１の同期爪１３１と並列に第１の同期爪１３１の第１歯１３１ａと第２歯１３１ｂとの間の欠歯位置に第３歯１３２ａを有する第２の同期爪１３２が配設され、第１の同期爪１３１、第２の同期爪１３２は揺動可能なように大歯車１０７に回転自在に配設された同期軸１３３に取り付けられている。
また、第１の同期爪１３１および第２の同期爪１３２には復帰可能となるようそれぞれ第１復帰ばね１３５および第２復帰ばね１３６が配設され、第１復帰ばね１３５および第２復帰ばね１３６の一方側は大歯車１０７の切り欠き部１３０の底部側に当接触し、第１復帰ばね１３５及び第２復帰ばね１３６の他方側は第１の同期爪１３１および第２の同期爪１３２のそれぞれ他方側に当接触し、第１復帰ばね１３５及び第２復帰ばね１３６は大歯車１０７の半径方向に同期軸１３３を中心に回転するが第１の同期爪１３１および第２の同期爪１３２の歯形が大歯車１０７の歯形とピッチ円が同じとなるような位置に大歯車１０７に軸着されたピン１３４によって位置規制されている。
Further, in the notch portion 130 formed in the missing tooth portion 107a of the large gear 107, the first synchronizing claw 131 is disposed in parallel with the first synchronizing claw 131 between the first tooth 131a and the second tooth 131b. A second synchronization claw 132 having third teeth 132a is disposed at the missing tooth position, and the first synchronization claw 131 and the second synchronization claw 132 are rotatably disposed on the large gear 107 so as to be swingable. Attached to the synchronized shaft 133.
In addition, a first return spring 135 and a second return spring 136 are disposed on the first synchronization pawl 131 and the second synchronization pawl 132 so as to be able to return, respectively, and the first return spring 135 and the second return spring 136 are provided. Of the first return spring 135 and the second return spring 136 are respectively in contact with the first synchronization pawl 131 and the second synchronization pawl 132, respectively. The first return spring 135 and the second return spring 136 are brought into contact with the other side and rotate around the synchronization shaft 133 in the radial direction of the large gear 107, but the tooth shapes of the first synchronization pawl 131 and the second synchronization pawl 132. However, the position of the large gear 107 is regulated by a pin 134 attached to the large gear 107 at a position where the tooth profile of the large gear 107 is the same as the pitch circle.
このため、小歯車１０５が反時計方向に回転して第１の同期爪１３１の同期軸１３３から離れた側の第１歯１３１ａも噛み合い歯面を押圧すると、接触する歯面の圧力角の関係から第１の同期爪１３１は反時計方向の回転モーメントが作用することになり、同期軸１３３を中心にして時計方向に回転して小歯車１０５との噛み合いが外れ大歯車１０７を回転させることはない。 For this reason, when the small gear 105 rotates counterclockwise and the first teeth 131a on the side away from the synchronization shaft 133 of the first synchronization pawl 131 also mesh and press the tooth surface, the relationship between the pressure angles of the contact tooth surfaces Therefore, the counterclockwise rotational moment acts on the first synchronizing claw 131, and the clockwise rotation about the synchronizing shaft 133 disengages from the small gear 105 to rotate the large gear 107. Absent.
一方、大歯車１０７が反時計方向に回転すると、第１の同期爪１３１の同期軸１３３から離れた側の第１歯１３１ａが小歯車１０５と噛み合って、この第１歯１３１ａに作用する押圧力が第１の同期爪１３１を反時計方向に回転させる回転モーメントとして作用するが、第２の同期爪１３２は大歯車１０７の半径方向にはピン１３４で拘束され、同期軸１３３を中心に回動できないため、第２の同期爪１３２の姿勢は図示の状態のまま変わらず、小歯車１０５は回転する。 On the other hand, when the large gear 107 rotates counterclockwise, the first teeth 131a on the side of the first synchronization pawl 131 away from the synchronization shaft 133 mesh with the small gear 105, and the pressing force acting on the first teeth 131a. Acts as a rotational moment for rotating the first synchronizing claw 131 counterclockwise, but the second synchronizing claw 132 is constrained by a pin 134 in the radial direction of the large gear 107 and rotates around the synchronizing shaft 133. Since this is not possible, the posture of the second synchronization pawl 132 remains the same as shown, and the small gear 105 rotates.
次に蓄勢操作について図１０および図１１に基づいて説明する。大歯車１０７の反時計方向の回転が進み、投入ばねロッド１１３が思案点を越えた位置で、リミットスイッチ１２２で電動機１０１の電源を停止すると電動機１０１の出力歯車１０２の回転力は惰性により回転後に無くなるが、投入ばね１１６の力により投入ばねロッド１１３を介し、大歯車１０７を反時計に回転する力が作用しているため、図１０に示すように、大歯車１０７は反時計方向に回転するが、小歯車１０５は時計方向に回転して大歯車１０７との噛み合い外れ、小歯車１０５の歯先により第１の同期爪１３１の第１歯１３１ａが押されて第１復帰ばね１３５のばね力に抗して第１の同期爪１３１は同期軸１３３を支点として反時計方向に回転する。さらに、大歯車１０７が反時計方向に回転すると、図１１に示すように、小歯車１０５が惰性により時計方向に回転し、第１の同期爪１３１の第１歯１３１ａが第１復帰ばね１３５のばね力により復帰して小歯車１０５の歯間に噛み合うとともに大歯車１０７に回転自在に軸着した投入ラッチピン１２５と投入ラッチ１２４とが係合し、投入ばね１１６の蓄勢が完了する。 Next, the energy storage operation will be described with reference to FIGS. When the rotation of the large gear 107 advances in the counterclockwise direction and the power supply of the electric motor 101 is stopped by the limit switch 122 at the position where the closing spring rod 113 exceeds the thought point, the rotational force of the output gear 102 of the electric motor 101 is rotated after inertia. Although no force is generated, a force that rotates the large gear 107 counterclockwise is exerted via the closing spring rod 113 due to the force of the closing spring 116, so that the large gear 107 rotates counterclockwise as shown in FIG. However, the small gear 105 rotates clockwise to disengage from the large gear 107, and the first tooth 131 a of the first synchronization pawl 131 is pushed by the tooth tip of the small gear 105, and the spring force of the first return spring 135 is pushed. In contrast, the first synchronization pawl 131 rotates counterclockwise about the synchronization shaft 133 as a fulcrum. Further, when the large gear 107 rotates counterclockwise, the small gear 105 rotates clockwise due to inertia as shown in FIG. 11, and the first teeth 131 a of the first synchronization pawl 131 are moved by the first return spring 135. The closing latch pin 125 and the closing latch 124 which are returned by the spring force and meshed between the teeth of the small gear 105 and rotatably mounted on the large gear 107 are engaged with each other, and the energy storage of the closing spring 116 is completed.
次に投入操作について図１２および図１３に基づいて説明する。投入トリガー１２６を駆動する投入コイル１２３に電気的指令が入ると、投入コイル１２３が励磁され投入トリガー１２６が反時計方向に回転し、投入ラッチ１２４と投入ラッチピン１２５との係合が外れ、上述したように投入ばね１１６の力により大歯車１０７は反時計方向に回転する。図１２に示すように、小歯車１０５は回転していない状態であり、第２の同期爪１３２の第３歯１３２ａと噛み合った後、大歯車１０７はさらに反時計方向に回転し、図示はしないが小歯車１０５の歯先により第２の同期爪１３２の第３歯１３２ａが押されて第２復帰ばね１３６のばね力に抗して第２の同期爪１３２は同期軸１３３を支点として反時計方向に回転する。さらに、大歯車１０７が反時計方向に回転すると、図示はしないが小歯車１０５は第１の同期爪１３１の第２歯１３１ｂと噛み合う。このとき、第２の同期爪１３２の第３歯１３２ａが第２復帰ばね１３６のばね力により復帰する。
そして、大歯車１０７がさらに反時計方向に回転すると、図１３に示すように、小歯車１０５は第１の同期爪１３１の第２歯１３１ｂとの噛み合いが外れ、その後、大歯車１０７の歯と順次噛み合い、大歯車１０７と小歯車１０５との噛み合いが回復するとともに小歯車１０５も時計方向に回転し蓄勢が開始されていく。
Next, the input operation will be described with reference to FIGS. When an electrical command is input to the making coil 123 that drives the making trigger 126, the making coil 123 is excited, the making trigger 126 rotates counterclockwise, and the making latch 124 and the making latch pin 125 are disengaged. Thus, the large gear 107 rotates counterclockwise by the force of the closing spring 116. As shown in FIG. 12, the small gear 105 is not rotating, and after meshing with the third tooth 132a of the second synchronization pawl 132, the large gear 107 further rotates counterclockwise, not shown. However, the third tooth 132a of the second synchronizing claw 132 is pushed by the tooth tip of the small gear 105 and the second synchronizing claw 132 counterclockwise with the synchronizing shaft 133 as a fulcrum against the spring force of the second return spring 136. Rotate in the direction. Further, when the large gear 107 rotates counterclockwise, the small gear 105 meshes with the second teeth 131b of the first synchronization pawl 131 (not shown). At this time, the third teeth 132 a of the second synchronization pawl 132 are restored by the spring force of the second return spring 136.
When the large gear 107 further rotates counterclockwise, the small gear 105 is disengaged from the second teeth 131b of the first synchronization pawl 131 as shown in FIG. The meshing of the large gear 107 and the small gear 105 is restored, and the small gear 105 is also rotated in the clockwise direction to start storing energy.
先端に小歯車１０５を軸着した蓄勢軸１０４には時計方向には噛み合うが反時計方向には噛み合わない一方向クラッチ（図示せず）を内蔵した中歯車１０３が配設されている。そのため、大歯車１０７と小歯車１０５を軸着した蓄勢軸１０４は回転するが、中歯車１０３以下の歯車列の負荷が伝達されなくなっている。そのため中歯車１０３以下の歯車列の回転慣性が負荷とならないため、投入ばね１１６の位置エネルギーが投入動作の運動エネルギーに有効に変換され、所定の投入速度を得ることが出来る。 An accumulator shaft 104 having a small gear 105 attached to the tip is provided with a middle gear 103 incorporating a one-way clutch (not shown) that meshes clockwise but does not mesh counterclockwise. For this reason, the accumulator shaft 104 with the large gear 107 and the small gear 105 attached thereto rotates, but the load of the gear train below the intermediate gear 103 is not transmitted. Therefore, since the rotational inertia of the gear train below the middle gear 103 is not a load, the potential energy of the closing spring 116 is effectively converted into the kinetic energy of the closing operation, and a predetermined closing speed can be obtained.
次に蓄勢動作について説明する。電動機１０１の出力歯車１０２を軸着した軸は時計方向には回転を拘束し、反時計方向には回転自由に回転するように電動機１０１のフレームに固定した一方向クラッチ（図示せず）を設けている。 Next, the accumulating operation will be described. A one-way clutch (not shown) fixed to the frame of the motor 101 is provided so that the shaft on which the output gear 102 of the motor 101 is attached is constrained to rotate clockwise and can rotate freely counterclockwise. ing.
中歯車１０３は電動機１０１の出力歯車１０２と噛み合っている。電動機１０１に電気エネルギーが注入されると、電動機１０１の出力歯車１０２は反時計方向に回転する。出力歯車１０２と噛み合っている中歯車１０３は時計方向に回転するが、中歯車１０３に内蔵された一方向クラッチ（図示せず）が時計方向に回転時には蓄勢軸１０４と噛み合い、蓄勢軸１０４も時計方向に回転する。
中歯車１０３には投入ばね１１６の負荷が作用しているため反時計方向の回転トルクが作用して、電動機１０１の出力歯車１０２の時計方向の回転トルクが作用するが一方向クラッチで回転を拘束しているため、出力歯車１０２は時計方向には回転しない。
The intermediate gear 103 meshes with the output gear 102 of the electric motor 101. When electric energy is injected into the motor 101, the output gear 102 of the motor 101 rotates counterclockwise. The intermediate gear 103 engaged with the output gear 102 rotates in the clockwise direction. However, when a one-way clutch (not shown) built in the intermediate gear 103 rotates in the clockwise direction, the intermediate gear 103 is engaged with the accumulator shaft 104, and the accumulator shaft 104. Also rotate clockwise.
Since the load of the closing spring 116 is acting on the intermediate gear 103, counterclockwise rotational torque acts, and the clockwise rotational torque of the output gear 102 of the motor 101 acts, but the rotation is restricted by a one-way clutch. Therefore, the output gear 102 does not rotate clockwise.
電動機１０１の出力歯車１０２の反時計方向の回転で、中歯車１０３は時計方向に回転し、中歯車１０３には時計方向に蓄勢軸１０４と噛み合う一方向クラッチが内蔵されているため、蓄勢軸１０４及び蓄勢軸１０４に軸着された小歯車１０５も時計方向に回転する。
小歯車１０５の時計方向の回転により大歯車１０７は反時計方向に回転し、大歯車１０７に回転自在に取り付けられた投入ばねロッド１１３は上方向に移動し、投入ばねロッド１１３の他端には投入ばね座１１５により投入ばね１１６取り付けられている。投入ばね１１６の投入ばね座１１５の反対の端部はフレーム１１７に当接している。投入ばねロッド１１３の上方向の移動により、投入ばね座１１５も上方向に移動する。
その結果、投入ばね１１６は圧縮される。大歯車１０７の反時計方向の回転が進み蓄勢動作をし、投入ラッチピン１２５と投入ラッチ１２４とが係合し、投入ばね１１６の蓄勢を維持するという動作を繰り返す構造となっている。
Due to the counterclockwise rotation of the output gear 102 of the electric motor 101, the intermediate gear 103 rotates clockwise, and the intermediate gear 103 has a built-in one-way clutch that meshes with the energy storage shaft 104 in the clockwise direction. The small gear 105 attached to the shaft 104 and the accumulator shaft 104 also rotates in the clockwise direction.
Due to the clockwise rotation of the small gear 105, the large gear 107 rotates counterclockwise, and the closing spring rod 113 rotatably attached to the large gear 107 moves upward. A closing spring 116 is attached by a closing spring seat 115. The opposite end of the closing spring 115 of the closing spring 116 is in contact with the frame 117. Due to the upward movement of the closing spring rod 113, the closing spring seat 115 also moves upward.
As a result, the closing spring 116 is compressed. The structure is such that the counterclockwise rotation of the large gear 107 proceeds to perform an accumulating operation, the closing latch pin 125 and the closing latch 124 are engaged, and the operation of maintaining the storing force of the closing spring 116 is repeated.
以上のようにこの発明によれば、投入時に大歯車１０７の回転により、大歯車１０７の欠歯部１０７ａに設けられた切り欠き部１３０に配設された第２の同期爪１３２の第３歯１３２ａと小歯車１０５の衝突は大歯車１０７の歯の一ピッチ分回転での衝突となるため、歯と歯の衝突は速度が遅いため衝撃力が小さくなるため、開閉回数が多い開閉器においては、歯車の磨耗が少なく信頼性の高い、開数寿命の多い開閉装置の提供が可能となる。 As described above, according to the present invention, the third tooth of the second synchronizing pawl 132 disposed in the notch portion 130 provided in the missing tooth portion 107a of the large gear 107 due to the rotation of the large gear 107 when being turned on. Since the collision between the gear 132a and the small gear 105 is a collision by rotating the tooth of the large gear 107 by one pitch, the impact between the teeth and the teeth is low and the impact force is small. Thus, it is possible to provide a switchgear with a high reliability and a low number of gears, with little wear on the gears.
実施の形態２．
この発明の実施の形態２を図１４に基づいて説明する。上述した実施の形態１においては、大歯車１０７の欠歯部１０７ａに形成した切り欠き部１３０は大歯車１０７の板厚方向中央部に凹形状溝部として構成され、この凹形状溝部として構成された切り欠き部１３０内に第１の同期爪１３１と第２の同期爪１３２が並列に配設された場合を示しているが、この実施の形態２においては、大歯車１０７の欠歯部１０７ａの両面にそれぞれ切り欠き部２３０、切り欠き部２３１を形成し、切り欠き部２３０に第１の同期爪１３１を配設し、切り欠き部２３１に第２の同期爪１３２を並列に配設したものであり、上述した実施の形態１と同様の効果を奏する。また、上述した実施の形態１の切り欠き部１３０よりもこの実施の形態２の切り欠き部２３０、切り欠き部２３１の方が容易に形成することができる。
Embodiment 2. FIG.
A second embodiment of the present invention will be described with reference to FIG. In the first embodiment described above, the notch 130 formed in the toothless portion 107a of the large gear 107 is configured as a concave groove at the central portion in the plate thickness direction of the large gear 107, and is configured as the concave groove. Although the case where the first synchronization claw 131 and the second synchronization claw 132 are arranged in parallel in the notch portion 130 is shown, in the second embodiment, the missing tooth portion 107a of the large gear 107 is shown. A notch portion 230 and a notch portion 231 are formed on both surfaces, a first synchronization claw 131 is provided in the notch portion 230, and a second synchronization claw 132 is provided in parallel in the notch portion 231. Thus, the same effects as those of the first embodiment described above can be obtained. Further, the notch portion 230 and the notch portion 231 of the second embodiment can be formed more easily than the notch portion 130 of the first embodiment described above.
実施の形態３．
この発明の実施の形態３を図１５に基づいて説明する。上述した実施の形態１においては、大歯車１０７の欠歯部１０７ａに形成した切り欠き部１３０は大歯車１０７の板厚方向中央部に凹形状溝部として構成され、この凹形状溝部として構成された切り欠き部１３０内に第１の同期爪１３１と第２の同期爪１３２が並列に配設された場合を示しているが、この実施の形態３においては、大歯車１０７の欠歯部１０７ａの片側面に切り欠き部２３２を形成し、その切り欠き部２３２に第１の同期爪１３１と第２の同期爪１３２を並列に配設したものであり、上述した実施の形態１と同様の効果を奏する。また、上述した実施の形態１の切り欠き部１３０よりもこの実施の形態３の切り欠き部２３２の方が容易に形成することができる。
Embodiment 3 FIG.
A third embodiment of the present invention will be described with reference to FIG. In the first embodiment described above, the notch 130 formed in the toothless portion 107a of the large gear 107 is configured as a concave groove at the central portion in the plate thickness direction of the large gear 107, and is configured as the concave groove. Although the case where the first synchronization claw 131 and the second synchronization claw 132 are arranged in parallel in the notch portion 130 is shown, in the third embodiment, the missing tooth portion 107a of the large gear 107 is shown. The notch part 232 is formed on one side surface, and the first synchronizing claw 131 and the second synchronizing claw 132 are arranged in parallel in the notch part 232, and the same effect as in the first embodiment described above. Play. Further, the cutout portion 232 of the third embodiment can be formed more easily than the cutout portion 130 of the first embodiment described above.
実施の形態４．
この発明の実施の形態４を図１６に基づいて説明する。図において、大歯車１０７には上述した実施の形態１と同様な切り欠き部１３０（図示せず）を有し、この切り欠き部１３０には大歯車１０７の歯形と同形の少なくとも２個の第１歯１３１ａ、第２歯１３１ｂを有する第１の同期爪１３１（図示せず）が配設され、第１の同期爪１３１（図示せず）の第１歯１３１ａと第２歯１３１ｂ間の一ピッチ分の1個は欠歯となっている。
Embodiment 4 FIG.
Embodiment 4 of the present invention will be described with reference to FIG. In the figure, the large gear 107 has a notch 130 (not shown) similar to that of the first embodiment described above, and the notch 130 has at least two second gears having the same shape as the tooth profile of the large gear 107. A first synchronizing claw 131 (not shown) having one tooth 131a and a second tooth 131b is disposed, and one between the first tooth 131a and the second tooth 131b of the first synchronizing claw 131 (not shown). One pitch is missing.
また、大歯車１０７の欠歯部１０７ａに形成した切り欠き部１３０内部には、第１の同期爪１３１と並列に第１の同期爪１３１の第１歯１３１ａと第２歯１３１ｂとの間の欠歯位置に第３歯１３２ａを有する第２の同期爪１３２（図示せず）が配設され、第１の同期爪１３１及び第２の同期爪１３２は揺動可能なように大歯車１０７に回転自在に配設された同期軸１３３（図示せず）に取り付けられ、また、第１の同期爪１３１および第２の同期爪１３２には復帰可能なるようそれぞれ第１復帰ばね１３５および第２復帰ばね１３６が設けられ、第１復帰ばね１３５および第２復帰ばね１３６の他端は大歯車１０７の切り欠き部１３０に底部側に固定されている。 Further, in the notch portion 130 formed in the missing tooth portion 107a of the large gear 107, the first synchronizing claw 131 is disposed in parallel with the first synchronizing claw 131 between the first tooth 131a and the second tooth 131b. A second synchronization claw 132 (not shown) having third teeth 132a is disposed at the missing tooth position, and the first synchronization claw 131 and the second synchronization claw 132 are arranged on the large gear 107 so as to be swingable. A first return spring 135 and a second return spring are attached to a synchronous shaft 133 (not shown) that is rotatably arranged, and can be returned to the first synchronous claw 131 and the second synchronous claw 132, respectively. A spring 136 is provided, and the other ends of the first return spring 135 and the second return spring 136 are fixed to the notch portion 130 of the large gear 107 on the bottom side.
さらに、第１復帰ばね１３５および第２復帰ばね１３６は第１の同期爪１３１および第２の同期爪１３２は大歯車１０７の半径方向に同期軸１３３を中心に回転するが第１の同期爪１３１および第２の同期爪１３２の歯形が大歯車１０７の歯形とピッチ円が同じとなるような位置に大歯車１０７に軸着されたピン１３４で位置規制している。大歯車１０７と噛み合う小歯車１０５を軸着した蓄勢軸１０４は操作機構フレーム１３７の片方に配設された軸受箱１３８に軸受に対し、回転自在に軸支されている。 Further, the first return spring 135 and the second return spring 136 have the first synchronization claw 131 and the second synchronization claw 132 rotate around the synchronization shaft 133 in the radial direction of the large gear 107, but the first synchronization claw 131. And the position of the second synchronous claw 132 is regulated by a pin 134 that is pivotally attached to the large gear 107 so that the tooth profile of the large gear 107 is the same as that of the large gear 107. The accumulator shaft 104 with the small gear 105 meshing with the large gear 107 is pivotally supported by a bearing box 138 disposed on one side of the operation mechanism frame 137 so as to be rotatable with respect to the bearing.
他方の操作機構フレーム１３７には蓄勢軸１０４の軸周りに回転拘束をした軸受箱１３９内に、蓄勢軸１０４が時計方向には回転自由に回転するが、反時計方向には回転を拘束する一方向クラッチ１４０が圧入されており、上記一方向クラッチ１４０の両側には軸受１４１が圧入され、一方向クラッチ１４０のクラッチ機能を安定化している。 In the other operation mechanism frame 137, the accumulator shaft 104 rotates freely in the clockwise direction in the bearing box 139 constrained to rotate around the accumulator shaft 104, but constrains the rotation in the counterclockwise direction. The one-way clutch 140 is press-fitted, and bearings 141 are press-fitted on both sides of the one-way clutch 140 to stabilize the clutch function of the one-way clutch 140.
先端に小歯車１０５を軸着した蓄勢軸１０４には時計方向には噛み合うが反時計方向には噛み合わない一方向クラッチ１４２を内蔵した中歯車１０３が配設されている。そのため、大歯車１０７と小歯車１０５を軸着した蓄勢軸１０４は回転するが、中歯車１０３以下の歯車列の負荷が伝達されなくなっている。なお、蓄勢軸１０４には、電動機１０１の出力歯車１０２と噛み合っている。電動機１０１の出力歯車１０２には上述した実施の形態１と異なり、一方向クラッチが内蔵されていない。 An accumulator shaft 104 having a small gear 105 mounted at the tip is provided with an intermediate gear 103 having a built-in one-way clutch 142 that meshes clockwise but does not mesh counterclockwise. For this reason, the accumulator shaft 104 with the large gear 107 and the small gear 105 attached thereto rotates, but the load of the gear train below the intermediate gear 103 is not transmitted. The accumulator shaft 104 meshes with the output gear 102 of the electric motor 101. Unlike the above-described first embodiment, the output gear 102 of the electric motor 101 does not include a one-way clutch.
次に動作について説明する。電動機１０１に電気エネルギーが注入されると、電動機１０１の出力歯車１０２は反時計方向に回転する。
上記出力歯車１０２と噛み合っている中歯車１０３は時計方向に回転するが、中歯車１０３には投入ばね１１６の負荷が作用しているため反時計方向の回転トルクが作用して、電動機１０１の出力歯車１０２には時計方向の回転トルクが作用するが一方向クラッチで回転で拘束しているため、出力歯車１０２は時計方向には回転しない。電動機１０１の出力歯車１０２の反時計方向の回転で、中歯車１０３は時計方向に回転し、中歯車１０３には時計方向に蓄勢軸１０４と噛み合う一方向クラッチ１４２が内蔵されているため、蓄勢軸１０４及び蓄勢軸１０４に軸着された小歯車１０５も時計方向に回転する。
Next, the operation will be described. When electric energy is injected into the motor 101, the output gear 102 of the motor 101 rotates counterclockwise.
The intermediate gear 103 engaged with the output gear 102 rotates in the clockwise direction. However, since the load of the closing spring 116 is applied to the intermediate gear 103, the counterclockwise rotational torque is applied to the output of the electric motor 101. Although the clockwise torque acts on the gear 102, the output gear 102 does not rotate in the clockwise direction because it is constrained by the rotation by the one-way clutch. As the output gear 102 of the electric motor 101 rotates counterclockwise, the intermediate gear 103 rotates clockwise, and the intermediate gear 103 has a built-in one-way clutch 142 that meshes with the accumulator shaft 104 in the clockwise direction. The small gear 105 attached to the force shaft 104 and the energy storage shaft 104 also rotates in the clockwise direction.
小歯車１０５の時計方向の回転により大歯車１０７は反時計方向に回転し、大歯車１０７に回転自在に取り付けられた投入ばねロッド１１３は上方向に移動し、投入ばね１１６を蓄勢する操作は上述した実施形態１と同様であり、以下図示を省略する。投入コイル１２３に外部より電気エネルギーを与えると、投入コイル１２３が励磁され、投入ラッチ１２４が反時計方向に回転し、投入ラッチ１２４も反時計方向に回転して投入ラッチピン１２５との係合が外れ、投入ラッチピン１２５を回転自在に軸着した大歯車１０７は反時計方向に回転し始める。
その時、小歯車１０５は時計方向には自由に回転できるため、第２の同期爪１３２の歯と噛み合い、その後、第１の同期爪１３１の同期軸１３３に近い歯と噛み合い、更に大歯車１０７が反時計方向に回転する。大歯車１０７の歯と噛み合い、大歯車１０７と小歯車１０５とは投入ばね１１６によって回転する。
The rotation of the small gear 105 in the clockwise direction causes the large gear 107 to rotate in the counterclockwise direction, and the closing spring rod 113 that is rotatably attached to the large gear 107 moves upward to store the closing spring 116. It is the same as that of Embodiment 1 mentioned above, and abbreviate | omits illustration below. When electrical energy is applied to the making coil 123 from the outside, the making coil 123 is excited, the making latch 124 rotates counterclockwise, and the making latch 124 also rotates counterclockwise to disengage from the making latch pin 125. The large gear 107 on which the closing latch pin 125 is rotatably mounted starts to rotate counterclockwise.
At this time, since the small gear 105 can freely rotate in the clockwise direction, the small gear 105 meshes with the teeth of the second synchronizing claw 132, and then meshes with the teeth near the synchronizing shaft 133 of the first synchronizing claw 131. Rotates counterclockwise. The large gear 107 meshes with the teeth of the large gear 107, and the large gear 107 and the small gear 105 are rotated by the closing spring 116.
カム軸１０６に固着された投入カム１０８はともに回転するようになっている。投入カム１０８は開放位置にある駆動レバー１１を開放ばね１２１の回転力に抗して投入位置に復帰させ、可動側電極５を閉極する。大歯車１０７は反時計方向に回転した後、下部思案点を越えさらに反時計方向に回転後、投入ばね１１６による回転力は大歯車１０７を時計方向に回転しようと働くが、大歯車１０７と噛み合っている小歯車１０５を軸着している蓄勢軸１０４は軸受箱１３９内に一方向クラッチで時計方向には回転拘束されるため、大歯車１０７の時計方向の回転を拘束し、投入が完了する。投入が完了した後の開放動作は上述した実施の形態１と同様であり説明を省略する。 The input cam 108 fixed to the cam shaft 106 rotates together. The closing cam 108 returns the driving lever 11 in the open position to the closing position against the rotational force of the opening spring 121 and closes the movable electrode 5. After the large gear 107 has rotated counterclockwise, after passing further below the lower point and further rotating counterclockwise, the rotational force of the closing spring 116 works to rotate the large gear 107 clockwise, but meshes with the large gear 107. The accumulator shaft 104, which is attached to the small gear 105, is constrained to rotate clockwise by a one-way clutch in the bearing housing 139. Therefore, the clockwise rotation of the large gear 107 is constrained and the insertion is completed. To do. The opening operation after the completion of the insertion is the same as that of the first embodiment described above, and a description thereof will be omitted.
なお、この発明は、その発明の範囲内において、各実施の形態を自由に組み合わせたり、各実施の形態を適宜、変形、省略することが可能である。 It should be noted that within the scope of the present invention, the embodiments can be freely combined, or the embodiments can be appropriately modified or omitted.
この発明は、開閉器の操作機構の初期位置からピニオンギアがリングギアに当接付近までの間では電磁スイッチの電磁力を低減できるとともに、当接以降は電磁力を向上させることができる開閉器の操作機構の実現に好適である。 The present invention can reduce the electromagnetic force of the electromagnetic switch from the initial position of the operating mechanism of the switch to the vicinity of the contact of the pinion gear with the ring gear, and can improve the electromagnetic force after the contact It is suitable for realizing the operation mechanism.
５ 可動側電極 １１ 駆動レバー
１０１ 電動機 １０２ 出力歯車
１０３ 中歯車 １０５ 小歯車
１０７ 大歯車 １０７ａ 欠歯部
１１３ 投入ばねロッド １１６ 投入ばね
１３０ 切り欠き部 １３１ 第１の同期爪
１３１ａ 第１歯 １３１ｂ 第２歯
１３２ 第２の同期爪 １３２ａ 第３歯
DESCRIPTION OF SYMBOLS 5 Movable electrode 11 Drive lever 101 Electric motor 102 Output gear 103 Medium gear 105 Small gear 107 Small gear 107 Large gear 107a Notch part 113 Closing spring rod 116 Closing spring 130 Notch part 131 1st synchronous claw 131a 1st tooth 131b 2nd tooth 132 Second synchronous claw 132a Third tooth
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