JPH0253895B2 - - Google Patents
Info
- Publication number
- JPH0253895B2 JPH0253895B2 JP59276779A JP27677984A JPH0253895B2 JP H0253895 B2 JPH0253895 B2 JP H0253895B2 JP 59276779 A JP59276779 A JP 59276779A JP 27677984 A JP27677984 A JP 27677984A JP H0253895 B2 JPH0253895 B2 JP H0253895B2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- liquid
- pressure liquid
- differential piston
- valve
- 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
Links
- 239000007788 liquid Substances 0.000 claims description 61
- 230000007246 mechanism Effects 0.000 claims description 7
- 230000004044 response Effects 0.000 claims description 3
- 238000005086 pumping Methods 0.000 description 29
- 230000002265 prevention Effects 0.000 description 23
- 238000010586 diagram Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 3
- 230000005284 excitation Effects 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000005856 abnormality Effects 0.000 description 2
- 230000003321 amplification Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Landscapes
- Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は電力用開閉器等に用いられ、開閉器
の遮断及び投入操作を行なう液圧操作装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic operating device that is used in a power switch or the like and performs the shutoff and closing operations of the switch.
送電系統の大容量化、高電圧化に伴つて、開閉
器、特に電力用遮断器の性能向上についての要求
が強くなつている。消弧絶縁媒体としてSF6ガス
を用いるガス絶縁遮断器の適用は言うに及ばず、
開閉速度の高速化や、開閉時間のばらつきを少な
くするなどの系統の安定化に寄与する性能の向上
が望まれている。同時に、操作時の騒音を低く押
え、また機器の保守性を向上させるなど、使用時
の問題点の改善も要求されつつある。
BACKGROUND OF THE INVENTION As power transmission systems become larger in capacity and voltage, there is a growing demand for improved performance of switches, especially power circuit breakers. Not to mention the application of gas insulation circuit breakers using SF6 gas as the arc-extinguishing insulating medium.
There is a desire for improved performance that contributes to system stability, such as faster opening/closing speeds and less variation in opening/closing times. At the same time, there is a growing demand for improvements in problems encountered during use, such as keeping operating noise low and improving equipment maintainability.
従来、駆動源としては空気圧が一般的に用いら
れていた。しかし、系統の大容量化、高電圧化に
伴う機器の大形化のために、空気圧式操作装置は
大形化し操作時の給排気に伴う騒音が高くなると
ともに空気圧を発生するコンプレツサの保守費用
が増大する等の欠点があり、その結果、油圧等の
液体圧を用いる操作方式に切り換えられつつあ
る。 Conventionally, air pressure has generally been used as a driving source. However, due to the increase in the size of equipment due to larger capacity and higher voltage systems, pneumatic operating devices have become larger and the noise associated with air supply and exhaust during operation has increased, as well as maintenance costs for the compressor that generates air pressure. However, there are disadvantages such as increased pressure, and as a result, there is a trend toward switching to an operation method that uses liquid pressure such as hydraulic pressure.
液圧式操作装置、中でも油圧操作装置は油の非
圧縮性の故に空気圧に比べて高圧化し易く、その
結果、操作時の騒音が少なく、また装置が縮少化
されるとともに高速操作時においても応答性が良
い等の数多くの利点がある。 Due to the incompressibility of oil, hydraulic operating devices, especially hydraulic operating devices, are easier to raise to higher pressure than air pressure.As a result, they produce less noise during operation, are smaller in size, and are more responsive even during high-speed operation. It has many advantages such as good performance.
一方、液圧操作方式においては、組立初期に液
中に空気が混入したり、液体の圧縮過程において
混入した空気が液中へ溶解したりすれば、これら
の空気のために遮断器の応答が遅れ、開閉時間が
ばらつくなどの問題点を有している。 On the other hand, in the hydraulic operation method, if air gets mixed into the liquid at the initial stage of assembly, or if air mixed in during the liquid compression process dissolves into the liquid, the response of the circuit breaker will be affected by this air. It has problems such as delays and variations in opening and closing times.
このため、従来の装置においては組立後に長時
間に亘り多数回のならし操作を繰り返して装置内
部の空気を排出する作業が必要であつた。特に変
電所等に据え付けられた後に部品交換のための解
体再組立を行なう場合、このような多数回のなら
し操作は開閉設備の復旧時間を長びかせる原因と
なり、変電所の運営上問題となることもある。 For this reason, in the conventional device, after assembly, it was necessary to repeat the break-in operation many times over a long period of time to exhaust the air inside the device. Particularly when disassembling and reassembling parts to replace parts after installation at a substation, such repeated break-in operations can prolong the recovery time of the switchgear equipment, causing problems in the operation of the substation. It may happen.
このような問題点を解決するために、従来シリ
ンダに作用する高圧液体を選択的に切り換える主
弁の制御回路及び差動ピストンの大受圧面に作用
する液体圧力を、操作指令の与えられた瞬時を除
いて常時高圧に保つような液圧式操作装置が提案
されている。また、これとは別に特に遮断器の操
作装置にはいわゆる「ポンピング防止機能」が要
求される。例えば手動操作等により遮断器に投入
指令を与えている最中に電力系統の異常等を除去
するための遮断指令が入つた場合、同時励磁防止
機能（通常は電気回路で構成する。）が働いて投
入動作を完了した後に遮断動作を行なう。この
時、遮断動作完了時になお投入指令が継続してい
ると、遮断器は再度投入動作を行なうことになり
電力系統の異常を継続させる可能性がある。この
ような現象をポンピング動作と呼びこれを防ぐた
めに通常は電磁継電器等を用いてポンピング防止
機能を構成することが多い。 In order to solve these problems, conventional control circuits for the main valve that selectively switches the high-pressure liquid acting on the cylinder and the liquid pressure acting on the high pressure receiving surface of the differential piston are controlled at the instant when an operation command is given. A hydraulic operating device has been proposed that maintains high pressure at all times except for. Additionally, in addition to this, a so-called "pumping prevention function" is particularly required for circuit breaker operating devices. For example, if a shutdown command is received to remove an abnormality in the power system while a closing command is being given to the circuit breaker by manual operation, etc., the simultaneous excitation prevention function (usually configured with an electric circuit) is activated. After the closing operation is completed, the shutting operation is performed. At this time, if the closing command continues after the closing operation is completed, the circuit breaker will perform the closing operation again, which may cause the abnormality in the power system to continue. This phenomenon is called a pumping operation, and to prevent this, an electromagnetic relay or the like is usually used to provide a pumping prevention function.
第４図はこのような従来の液圧式操作装置の断
面図を示している。図において、１は開閉器の接
触子で、ロツド２を介して液圧式操作装置の駆動
部に連結され、投入・遮断動作を行なう。液圧式
操作装置６は接触子１を駆動する差動ピストン３
とシリンダ５及びダツシユポツトリング４ａ，４
ｂよりなる。この操作装置６は主弁７により操作
されるが、その際、増巾弁８を介して高圧液体の
供給をうける。なお、高圧液体は図示されていな
いポンプにより常に所定圧力に維持されるアキユ
ムレータ９から供給される。 FIG. 4 shows a sectional view of such a conventional hydraulic operating device. In the figure, reference numeral 1 denotes a contactor of a switch, which is connected via a rod 2 to a drive section of a hydraulic operating device, and performs closing/closing operations. The hydraulic operating device 6 includes a differential piston 3 that drives the contactor 1.
and cylinder 5 and needle pot rings 4a, 4
Consists of b. This operating device 6 is operated by a main valve 7 and is supplied with high-pressure liquid via a widening valve 8 . Note that the high-pressure liquid is supplied from an accumulator 9 that is always maintained at a predetermined pressure by a pump (not shown).
高圧液体はアキユムレータ９から管路１０を介
してシリンダ５の内部の小ピストン面側の室５ａ
に供給され、更に管路１１を介して主弁７に供給
される。 The high-pressure liquid is passed from the accumulator 9 through the conduit 10 to the chamber 5a on the small piston surface side inside the cylinder 5.
It is further supplied to the main valve 7 via the conduit 11.
主弁７は相対向して配設される排出弁１４及び
ばね１４ａと供給弁１３及びばね１３ａにより構
成される。排出弁１４のパイロツト室１５は管路
１６を経由して増巾弁８から導かれる高圧液体の
作用を受ける。その結果、供給弁１３及び排出弁
１４は一体となつて動作し主弁７を切り換える。
すなわち、排出弁１４のパイロツト室１５に高圧
液体が作用しないとき、差動ピストン３の大ピス
トン面側の室５ｂは、管路１７を介して低圧タン
ク１８に連通される。 The main valve 7 is composed of a discharge valve 14 and a spring 14a, and a supply valve 13 and a spring 13a, which are arranged to face each other. The pilot chamber 15 of the discharge valve 14 is acted upon by high-pressure liquid which is led from the amplification valve 8 via a line 16. As a result, the supply valve 13 and the discharge valve 14 operate in unison to switch the main valve 7.
That is, when high pressure liquid does not act on the pilot chamber 15 of the discharge valve 14, the chamber 5b on the large piston surface side of the differential piston 3 is communicated with the low pressure tank 18 via the conduit 17.
一方、排油弁１４のパイロツト室１５が高圧液
体の作用を受ける時、差動ピストン３の大ピスト
ン面側の室５ｂは、管路１１を介してアキユムレ
ータ９に連通される。管路１２から分岐した管路
５１はアキユムレータ９からの高圧液体を増巾弁
８の補助供給弁２０の側に供給する。また、管路
５２はアキユムレータからの高圧液体を絞り５
４、管路５６を介して投入弁３８の一端に導くと
ともに絞り５３及び管路５５を介してパイロツト
室２１へも導く。遮断弁２８の一端は管路５７及
び管路５５を介してパイロツト室２１へ連通し、
他の一端は管路５８を介して低圧タンク１８へ連
通している。増巾弁８は相対向して配設される補
助排出弁１９及びばね１９ａ、補助供給弁２０及
びばね２０ａから構成され補助排出弁１９のパイ
ロツト室２１に高圧液体の作用を受ける。その結
果、補助排出弁１９及び補助供給弁２０は一体と
なつて動作し、増巾弁８を切り換える。すなわ
ち、パイロツト室２１に高圧液体が作用すると
き、管路１６は管路５１を介してアキユムレータ
９に連通する。一方、高圧液体が作用しない時、
管路１６は管路２２を介して低圧タンク１８に連
通する。 On the other hand, when the pilot chamber 15 of the oil drain valve 14 is subjected to the action of high pressure liquid, the chamber 5b on the large piston surface side of the differential piston 3 is communicated with the accumulator 9 via the pipe line 11. A pipe line 51 branched from the pipe line 12 supplies high-pressure liquid from the accumulator 9 to the auxiliary supply valve 20 side of the widening valve 8 . In addition, the pipe line 52 is used to throttle the high pressure liquid from the accumulator.
4. It is led to one end of the input valve 38 via the pipe 56 and also to the pilot chamber 21 via the throttle 53 and the pipe 55. One end of the shutoff valve 28 communicates with the pilot chamber 21 via a conduit 57 and a conduit 55;
The other end communicates with the low pressure tank 18 via a conduit 58. The width increasing valve 8 is composed of an auxiliary discharge valve 19 and a spring 19a, and an auxiliary supply valve 20 and a spring 20a, which are arranged opposite to each other, and a pilot chamber 21 of the auxiliary discharge valve 19 is subjected to the action of high pressure liquid. As a result, the auxiliary discharge valve 19 and the auxiliary supply valve 20 operate in unison to switch the width increase valve 8. That is, when high pressure liquid acts on the pilot chamber 21, the conduit 16 communicates with the accumulator 9 via the conduit 51. On the other hand, when high pressure liquid does not act,
Line 16 communicates with low pressure tank 18 via line 22 .
投入弁３８及び遮断弁２８は、それぞれ球形弁
２９，３０と復帰ばね３１，３２で構成され、操
作棒３３，３４を介して指令に応じて直線的に動
作する電磁装置３５，３６により操作される。 The closing valve 38 and the shutoff valve 28 are each composed of spherical valves 29, 30 and return springs 31, 32, and are operated by electromagnetic devices 35, 36 that operate linearly in response to commands via operating rods 33, 34. Ru.
各電磁装置３５，３６は可動鉄心３５ａ，３６
ａ及び固定コイル３５ｂ，３６ｂからなる。 Each electromagnetic device 35, 36 has a movable iron core 35a, 36
a and fixed coils 35b and 36b.
投入弁３８の一端に連通した管路５６は管路５
９を介して投入制御装置６１に連通しており、投
入弁３８の他端は管路６０を介して低圧タンク１
８へ連通している。 A pipe line 56 communicating with one end of the input valve 38 is a pipe line 5.
The other end of the injection valve 38 is connected to the low pressure tank 1 via a pipe line 60.
It connects to 8.
投入制御装置６１は高圧液体の作用を受けて駆
動される小ピストン６２を有しており、この小ピ
ストン６２がシリンダ５に固定された軸６４の回
りに回動するラツチ６３を背後から押圧すること
によつて、差動ピストン３に固定された突出ピン
５０とラツチ６３の係合状態を保持する。なお、
差動ピストン３に軸方向（上方向）の推力が付与
された状態で小ピストン６２の押圧力を除去すれ
ば、差動ピストン３の推力によつてラツチ６３と
突出ピン５０の係合が自然に解除されるようラツ
チ６３の形状が定められている。 The input control device 61 has a small piston 62 that is driven by the action of high-pressure liquid, and this small piston 62 presses from behind a latch 63 that rotates around a shaft 64 fixed to the cylinder 5. As a result, the engagement between the protruding pin 50 fixed to the differential piston 3 and the latch 63 is maintained. In addition,
If the pressing force of the small piston 62 is removed with an axial (upward) thrust being applied to the differential piston 3, the latch 63 and the protruding pin 50 will naturally engage with each other due to the thrust of the differential piston 3. The shape of the latch 63 is determined so that the latch 63 is released at a certain time.
次に上記のように構成された従来の装置の遮断
時の動作について第６図に示したタイムチヤート
を併せ用いて説明する。図において、ａは遮断電
磁装置３６の励磁信号の入、切を、ｂは補助排出
弁１９のパイロツト室２１の液体圧力を、ｃは一
体となつて動作する補助排出弁１９及び補助供給
弁２０の位置を、ｄは排出弁１４のパイロツト室
１５の液体圧力を、ｅは一体となつて動作する供
給弁１３及び排出弁１４の位置を、ｆは差動ピス
トン３の大ピストン面側の室５ｂ内部の液体圧力
を、ｇは差動ピストン３の動きを、またｈはラツ
チ６３の動きを表わすタイムチヤートである。 Next, the operation of the conventional device configured as described above at the time of shutoff will be explained with reference to the time chart shown in FIG. In the figure, a indicates the ON/OFF state of the excitation signal for the cut-off electromagnetic device 36, b indicates the liquid pressure in the pilot chamber 21 of the auxiliary discharge valve 19, and c indicates the auxiliary discharge valve 19 and the auxiliary supply valve 20 that operate together. , d is the liquid pressure in the pilot chamber 15 of the discharge valve 14, e is the position of the supply valve 13 and discharge valve 14 that operate together, and f is the chamber on the large piston surface side of the differential piston 3. 5b is the internal liquid pressure, g is the movement of the differential piston 3, and h is a time chart showing the movement of the latch 63.
投入状態を示す第５図において、接触子１を開
くために電磁装置３６に投入指令が入力されると
第６図ａのa1点で可動鉄心３６ａが駆動され、操
作棒３４を介して遮断弁２８に作用し、球形弁３
０が開かれる。その結果、増巾弁８の補助排出弁
１９のパイロツト室２１は、管路５７及び５８を
経て低圧タンク１８に連通し、第６図ｂのb1点に
示すように高圧液体が排出される。 In FIG. 5 showing the closing state, when a closing command is input to the electromagnetic device 36 to open the contact 1, the movable core 36a is driven at point a in FIG. Acting on valve 28, spherical valve 3
0 is opened. As a result, the pilot chamber 21 of the auxiliary discharge valve 19 of the widening valve 8 communicates with the low-pressure tank 18 via lines 57 and 58, and the high-pressure liquid is discharged as shown at point b 1 in FIG. 6b. .
これにより、第６図ｃに示すc1点で増巾弁８の
補助排出弁１９が開口し、補助供給弁２０は閉止
する。この為、主弁７の排出弁１４のパイロツト
室１５は、第６図ｄに示すd1点で管路１６、管路
２２を通して低圧タンク１８に連通し、パイロツ
ト室１５の高圧液体は排出される。 As a result, the auxiliary discharge valve 19 of the width increasing valve 8 opens and the auxiliary supply valve 20 closes at point c shown in FIG. 6c. Therefore, the pilot chamber 15 of the discharge valve 14 of the main valve 7 is communicated with the low pressure tank 18 through the pipe line 16 and the pipe line 22 at one point d shown in FIG. 6d, and the high pressure liquid in the pilot chamber 15 is discharged. Ru.
主弁７の排出弁１４は、そのパイロツト室１５
の高圧液体が排出されると、低圧タンク１８に連
通する管路１７を開口するとともに、第６図ｅに
示すe1点で対向して配設される供給弁１３を閉止
する。これにより、差動ピストン３の大面積側の
室５ｂの高圧液体は第６図ｆのf1点で管路１７を
通して排出される。その結果、図中、下方向の推
力が発生し、差動ピストン３は第６図ｇのg1点か
ら遮断方向に駆動を開始する。 The discharge valve 14 of the main valve 7 is connected to its pilot chamber 15.
When the high-pressure liquid is discharged, the pipe line 17 communicating with the low-pressure tank 18 is opened, and the supply valves 13 disposed opposite to each other at point e shown in FIG. 6e are closed. As a result, the high pressure liquid in the large area side chamber 5b of the differential piston 3 is discharged through the conduit 17 at point f1 in FIG. 6f. As a result, a downward thrust is generated in the figure, and the differential piston 3 starts driving in the blocking direction from point g1 in Figure 6g.
このとき、投入制御装置６１には管路５９及び
絞り５４を介してアキユムレータ９から高圧液が
供給されているため、ラツチ６３は小ピストン６
２によつて常に背後から押圧されており、差動ピ
ストン２６が遮断方向に駆動を完了する。（第６
図ｇのg1点→g2点）突出ピン５０がラツチ６３を
よぎると（第６図ｇのg2点）小ピストン６２に押
圧されたラツチ６３は軸６４の回りに回動を開始
し（第６図ｈのh1点）突出ピン５０と係合する
（第６図ｈのh2点）。 At this time, since the high pressure liquid is supplied to the injection control device 61 from the accumulator 9 via the pipe line 59 and the throttle 54, the latch 63 is connected to the small piston 6.
2, the differential piston 26 completes its drive in the blocking direction. (6th
(Point g 1 → Point g 2 in Figure g) When the protruding pin 50 crosses the latch 63 (Point g 2 in Figure 6 g), the latch 63 pressed by the small piston 62 starts rotating around the shaft 64. ( 1 point h in FIG. 6 h) engages with the protruding pin 50 ( 2 points h in FIG. 6 h).
一方、第６図ａのa2点で電磁装置３６への指令
が解除されると、球形弁３０が液圧力によつて上
昇復帰して遮断弁２８は閉止される。その結果、
第６図ｂのb2点から絞り５３、管路５５を介して
パイロツト室２１へ高圧液が徐々に供給され、こ
のパイロツト室２１の圧力が予め設定されたある
一定値に達すると、閉止状態にある補助供給弁２
０に加わる背圧力が補助排出弁１９に加わる背圧
力に打ち勝つて、補助排出弁１９及び補助供給弁
２０は一体となつて移動する（第６図ｃのc2点）。
増巾弁８の補助排出弁１９は低圧タンク１８に連
通する管路２２を閉止するとともに、それに対向
する補助供給弁２０を開口せしめる。これによ
り、高圧液体は管路１２、管路５１及び管路１６
を通して排出弁１４のパイロツト室１５に達し
（第６図ｄのd2点）、再び主弁７を切り換える。 On the other hand, when the command to the electromagnetic device 36 is released at point a2 in FIG. the result,
High-pressure liquid is gradually supplied to the pilot chamber 21 from point b in FIG. Auxiliary supply valve 2 located in
The back pressure applied to the auxiliary discharge valve 19 overcomes the back pressure applied to the auxiliary discharge valve 19, and the auxiliary discharge valve 19 and the auxiliary supply valve 20 move together (point c 2 in FIG. 6c).
The auxiliary discharge valve 19 of the widening valve 8 closes the conduit 22 communicating with the low pressure tank 18, and opens the auxiliary supply valve 20 opposite thereto. As a result, the high-pressure liquid flows through the pipes 12, 51, and 16.
It reaches the pilot chamber 15 of the discharge valve 14 (point d 2 in Fig. 6d), and switches the main valve 7 again.
排出弁１４はそのパイロツト室１５に高圧液体
の作用を受けると、低圧タンク１８に連通する管
路１７を閉止するとともに、対向して配設される
供給弁１３を開口させる（第６図ｅのe2点）。そ
の結果、差動ピストン３の大面積側の室５ｂに
は、供給弁１３及び管路１１を通じて高圧液体が
達し、差動ピストン３の受圧面積差のために、図
中、上方向の推力が発生するが（第６図ｆのf2
点）、既にラツチ６３と突出ピン５０が係合を完
了（第６図ｈのh2点）している。また、小ピスト
ン６２には絞り５４及び管路５９を介して供給さ
れる高圧液による背力が加えられているので、差
動ピストン３に加わる上方向推力はラツチ６３に
よつて保持され遮断が完了して、第５図の状態を
保つ。 When the pilot chamber 15 of the discharge valve 14 is subjected to the action of high pressure liquid, the discharge valve 14 closes the pipe 17 communicating with the low pressure tank 18 and opens the supply valve 13 disposed opposite to it (as shown in FIG. 6e). e 2 points). As a result, the high-pressure liquid reaches the large-area side chamber 5b of the differential piston 3 through the supply valve 13 and the pipe line 11, and due to the difference in the pressure-receiving area of the differential piston 3, an upward thrust in the figure is generated. (f 2 in Fig. 6 f)
point), the latch 63 and the protruding pin 50 have already completed engagement (point h2 in FIG. 6h). Furthermore, since a back force is applied to the small piston 62 by the high pressure fluid supplied via the throttle 54 and the conduit 59, the upward thrust applied to the differential piston 3 is held by the latch 63 and is not shut off. Once completed, maintain the state shown in Figure 5.
次に、投入動作について説明する。第５図にお
いて、接触子１を投入するために電磁装置３５に
投入指令が入力されると、可動鉄心３５ａが駆動
され、操作棒３３を介して投入弁３８に作用し、
球形弁２９が開かれる。これによつて、管路５６
及び５９は低圧タンク１８に連通して高圧液体が
排出される。その結果、投入制御装置６１の小ピ
ストン６２を背後より押圧する力は除去される
が、既に述べたように、小ピストン６２の押圧力
を除去すれば、差動ピストン３の推力によつてラ
ツチ６３と突出ピン５０の係合が自然に解除され
るようラツチ６３の形状が定められているので、
差動ピストン３は上方向へ移動を開始して最終的
に投入を完了する。 Next, the charging operation will be explained. In FIG. 5, when a closing command is input to the electromagnetic device 35 to close the contact 1, the movable core 35a is driven and acts on the closing valve 38 via the operating rod 33.
Spherical valve 29 is opened. As a result, the conduit 56
and 59 communicate with the low-pressure tank 18 to discharge high-pressure liquid. As a result, the force pushing the small piston 62 of the closing control device 61 from behind is removed, but as already mentioned, if the pushing force of the small piston 62 is removed, the latch will be latched by the thrust of the differential piston 3. Since the shape of the latch 63 is determined so that the engagement between the latch 63 and the protruding pin 50 is naturally released,
The differential piston 3 starts moving upward and finally completes the injection.
一方、管路５２及び絞り５４を介してアキユム
レータ９の高圧液は徐々に管路５９に再び供給さ
れ、差動ピストン３が動作を完了した時点におい
ては管路５９が次の遮断動作に備え高圧液で満た
された第５図の状態になる。 On the other hand, the high-pressure liquid in the accumulator 9 is gradually supplied again to the pipe line 59 via the pipe line 52 and the throttle 54, and when the differential piston 3 completes its operation, the pipe line 59 is at high pressure in preparation for the next shutoff operation. It will be in the state shown in Figure 5, filled with liquid.
次に第７図を用いてポンピング防止機能につい
て説明する。図の回路において、端子Ｔ及びＣに
は各々遮断及び投入指令が入力され遮断コイル
TT及び投入コイルCCを各々励磁して遮断器を動
作させる。接点Aa及びAbは遮断器に連動して作
動する補助接点で、遮断器の遮断状態においては
Aaは開放し、Abは閉止する。また、投入状態に
おいてはAaは閉止し、Abは開放する。Ｙはポン
ピング防止用電磁継電器のコイルで、Ｙが励磁さ
れると、Yaは閉止し、Ybは開放する。 Next, the pumping prevention function will be explained using FIG. 7. In the circuit shown in the figure, the cutoff and make-on commands are input to terminals T and C, respectively, and the cutoff coil
TT and closing coil CC are each excited to operate the circuit breaker. Contacts Aa and Ab are auxiliary contacts that operate in conjunction with the circuit breaker, and when the circuit breaker is in the disconnected state,
Aa is open and Ab is closed. Furthermore, in the closed state, Aa is closed and Ab is open. Y is a coil of an electromagnetic relay for preventing pumping, and when Y is excited, Ya is closed and Yb is opened.
次に作用について説明する。例えば、遮断状態
において、投入指令が端子Ｃに入力されると、接
点Yb，Abを通じて投入コイルCCが励磁されて
遮断器は投入される。投入が完了すると、接点
Aaは閉止し、接点Abは開放し、投入コイルの励
磁は解かれる。このとき、投入指令が継続してい
ると、閉止した接点Aaを経由してコイルＹに電
流が流れて接点Yaが閉止し、自己保持されると
ともにYbが開放する。このような状態において、
遮断指令が端子Ｔに入力されると、接点Aaを通
じて遮断コイルTTが励磁されて遮断器が遮断
し、接点Aaが再び開放してAbが閉止する。この
状態においてもなお投入指令が継続している場
合、Yb接点が投入コイルCCに直列に挿入されて
いなければ遮断器は再投入してポンピング動作を
生じるが、自己保持されたコイルＹの接点Ybが
挿入されているために第７図の回路においてはポ
ンピング動作を生じることはない。 Next, the effect will be explained. For example, in the cut-off state, when a closing command is input to terminal C, closing coil CC is excited through contacts Yb and Ab, and the circuit breaker is closed. When the input is completed, the contact
Aa is closed, contact Ab is opened, and the excitation of the closing coil is released. At this time, if the closing command continues, current flows through the coil Y via the closed contact Aa, causing the contact Ya to close, self-holding, and Yb to open. In such a situation,
When a cutoff command is input to terminal T, cutoff coil TT is energized through contact Aa, the circuit breaker is cut off, contact Aa is opened again, and Ab is closed. If the closing command continues even in this state, if the Yb contact is not inserted in series with the closing coil CC, the circuit breaker will close again and a pumping operation will occur, but the self-holding coil Y contact Yb 7, no pumping operation occurs in the circuit shown in FIG.
従来の液圧式操作装置は以上のように構成され
ているので、ポンピング防止の機能を電磁継電器
を用いて構成することが多く、そのため制御回路
が複雑となつて遮断時の振動による誤動作等を生
じ易く、また電磁継電器の台数が増加するために
高価で大形化するという欠点があつた。
Since conventional hydraulic operating devices are configured as described above, the pumping prevention function is often configured using electromagnetic relays, which makes the control circuit complicated and causes malfunctions due to vibration when shutting off. However, since the number of electromagnetic relays increases, it becomes expensive and large in size.
この発明に係る液圧式操作装置は、第１の操作
信号でトリガ機構を作動して保持装置の保持を解
除して差動ピストンを前進させ、第２の操作信号
で液体切換弁を作動して大ピストン面側の高圧液
体を除去して小ピストン面側の高圧液体で差動ピ
ストンを後退させて差動ピストンを保持装置で保
持し、第２の操作信号が解除されると常時高圧を
維持する蓄圧装置から絞りを介して高圧液体が作
用して液体切換弁を復帰させ、液体切換弁の復帰
によつて大ピストン面側に高圧液体が供給され、
大ピストン面側に高圧液体が供給された状態で待
機させるようにしたものである。
The hydraulic operating device according to the present invention operates the trigger mechanism with the first operating signal to release the holding device and advance the differential piston, and operates the liquid switching valve with the second operating signal. The high-pressure liquid on the large piston surface side is removed and the differential piston is moved back with the high-pressure liquid on the small piston surface side, and the differential piston is held by the holding device, and when the second operation signal is released, the high pressure is maintained at all times. High-pressure liquid acts through the throttle from the pressure accumulator to return the liquid switching valve, and due to the return of the liquid switching valve, high-pressure liquid is supplied to the large piston surface side,
It is designed to stand by with high-pressure liquid supplied to the large piston surface side.
この発明においては、小ピストン面側を高圧液
体で常時加圧し、大ピストン面側は差動ピストン
を保持装置で保持した状態にして高圧液体で加圧
しておくことによつて、保持装置をトリガ機構で
作動させて差動ピストンを前進位置に移動させる
ことができる。
In this invention, the holding device is triggered by constantly pressurizing the small piston side with high-pressure liquid, and by pressurizing the large piston side with high-pressure liquid while holding the differential piston with the holding device. A mechanism can be actuated to move the differential piston to a forward position.
以下、この発明の一実施例を図について説明す
る。第１図〜第３図において、３５は電磁装置
で、取付台８０に固定された固定コイル３５ｂと
可動鉄心３５ａから成る。可動鉄心３５ａの一端
にはピン８２で回動自由に取付けられたポンピン
グ防止レバー８１が設けられている。ばね８３に
よつて押圧されたポンピング防止レバー８１の側
部には切欠き８１ａがあつて、ピン８５の回りに
回動自由なトリガー８４の一端８４ｃが係合して
いる。トリガー８４はばね８６によつて押圧され
ている。なお、トリガー８４には突出部８４ｂが
設けられている。８７はトリガー８４の停止位置
を定めるためのストツパーである。８９はポンピ
ング防止レバー８１に対向する位置に設けられた
ポンピング防止ピンで、ばね９０によつて背後か
ら押圧されている。トリガー８４のポンピング防
止レバー８１に相対する一端８４ａは遮断器の遮
断状態においてラツチ６３を背後から支持し突出
ピン５０とラツチ６３の係合を機械的に保持して
いる。ラツチ６３はばね８８によつて背後から押
圧されており、そのばね力はトリガ８４とラツチ
６３の係合を除去すれば差動ピストン３の推力に
よつてラツチ６３と突出ピン５０の係合が自然に
解除されるような大きさである。
An embodiment of the present invention will be described below with reference to the drawings. In FIGS. 1 to 3, numeral 35 is an electromagnetic device consisting of a fixed coil 35b fixed to a mounting base 80 and a movable iron core 35a. A pumping prevention lever 81 is rotatably attached to one end of the movable core 35a with a pin 82. A notch 81a is provided on the side of the anti-pumping lever 81 pressed by the spring 83, and one end 84c of a trigger 84, which is freely rotatable around a pin 85, is engaged with the notch 81a. Trigger 84 is pressed by a spring 86. Note that the trigger 84 is provided with a protrusion 84b. 87 is a stopper for determining the stop position of the trigger 84. A pumping prevention pin 89 is provided at a position opposite to the pumping prevention lever 81, and is pressed from behind by a spring 90. One end 84a of the trigger 84 facing the anti-pumping lever 81 supports the latch 63 from behind and mechanically maintains the engagement between the protruding pin 50 and the latch 63 when the circuit breaker is closed. The latch 63 is pressed from behind by a spring 88, and when the trigger 84 and the latch 63 are disengaged, the thrust of the differential piston 3 causes the latch 63 to engage with the protruding pin 50. It is large enough to be released naturally.
次に上記のように構成されたこの発明による装
置の投入時の動作について説明する。 Next, a description will be given of the operation of the apparatus according to the present invention configured as described above when it is turned on.
遮断状態を示す第２図において、接触子１を投
入するために電磁装置３５に投入指令が入力され
ると、可動鉄心３５ａが駆動されてポンピング防
止レバー８１が下方に移動する。このため、トリ
ガー８４の一端８４ｃは時計方向に回動を開始
し、トリガー８４の端部８４ａとラツチ６３の係
合が解除され、差動ピストン３に与えられた推力
によつてラツチ６３と突出ピン５０の係合が解除
されて、差動ピストン３が上方に移動し、遮断器
が投入される。このとき、トリガー８４の回動に
よつて突出部８４ｂはポンピング防止レバー８１
を回動させ、投入指令が解除された時点におい
て、トリガー８４及びポンピング防止レバー８１
は第１図ａ，ｂの状態になつて投入動作が完了す
る。 In FIG. 2 showing the cut-off state, when a closing command is input to the electromagnetic device 35 to close the contactor 1, the movable iron core 35a is driven and the pumping prevention lever 81 is moved downward. Therefore, one end 84c of the trigger 84 starts rotating clockwise, and the engagement between the end 84a of the trigger 84 and the latch 63 is released, and the thrust applied to the differential piston 3 causes the latch 63 to protrude. The pin 50 is disengaged, the differential piston 3 moves upward, and the circuit breaker is closed. At this time, the rotation of the trigger 84 causes the protrusion 84b to move against the pumping prevention lever 81.
When the closing command is released, the trigger 84 and the pumping prevention lever 81 are rotated.
The closing operation is completed when the state becomes as shown in FIG. 1a and b.
次に、遮断時の動作について説明する。投入状
態を示す第１図ａ，ｂにおいて、接触子１を遮断
するために電磁装置３６に遮断指令が入力される
と、可動鉄心３６ａが駆動され、操作棒３４を介
して遮断弁２８に作用して球形弁３０が開かれ
る。以下、従来装置と同様に増巾弁８及び主弁７
が切り換わり、差動ピストン３の大ピストン面側
の室５ｂの高圧液体が排出されて差動ピストン３
が下降し、突出ピン５０がばね８８で押圧された
ラツチ６３をよぎると、ラツチ６３と突出ピン５
０が係合し、さらに、ばね８６で押圧されたトリ
ガー８４の端部８４ａとラツチ６３が係合する。
この後、従来装置と同様に増巾弁８及び主弁７が
復帰して、大ピストン面側の室５ｂには高圧液体
が供給され第２図ａ，ｂの状態となつて遮断が完
了する。 Next, the operation when shutting off will be explained. In FIGS. 1a and 1b showing the closed state, when a cutoff command is input to the electromagnetic device 36 to cut off the contact 1, the movable core 36a is driven and acts on the cutoff valve 28 via the operating rod 34. The spherical valve 30 is then opened. Hereinafter, the width increasing valve 8 and the main valve 7 are similar to the conventional device.
is switched, the high-pressure liquid in the chamber 5b on the large piston surface side of the differential piston 3 is discharged, and the differential piston 3
is lowered, and when the protruding pin 50 crosses the latch 63 pressed by the spring 88, the latch 63 and the protruding pin 5
0 is engaged, and furthermore, the end 84a of the trigger 84 pressed by the spring 86 and the latch 63 are engaged.
After this, the width increasing valve 8 and the main valve 7 return to their original positions in the same way as in the conventional device, and high pressure liquid is supplied to the chamber 5b on the large piston surface side, resulting in the states shown in Fig. 2 a and b, and the shutoff is completed. .
次に、ポンピング防止機能について説明する。
第１図ａ，ｂの投入状態において、投入完了後も
継続して投入指令が与えられると、第３図ａに示
すようにポンピング防止レバー８１はポンピング
防止ピン８９と係合状態となつてポンピング防止
レバー８１の復帰が阻止される。この状態におい
て、遮断指令が与えられ、差動ピストン３が下降
して突出ピン５０とラツチ６３が係合すると、ト
リガー８４は復帰し、突出ピン５０とラツチ６３
の係合を保持する。しかし、ポンピング防止レバ
ー８１がポンピング防止ピン８９に復帰を阻止さ
れているために、一旦投入指令を解除して、ポン
ピング防止レバー８１の切欠き８１ａとトリガー
８４の端部８４ｃを第２図ａ，ｂのように係合さ
せなければ、再度遮断器が投入することはなく、
ポンピング防止の機能が達成される。 Next, the pumping prevention function will be explained.
In the closing state shown in FIGS. 1a and 1b, if a closing command is continuously given even after closing is completed, the pumping prevention lever 81 engages with the pumping prevention pin 89 as shown in FIG. 3a, and the pumping is stopped. The prevention lever 81 is prevented from returning. In this state, when a cutoff command is given and the differential piston 3 descends to engage the protruding pin 50 and latch 63, the trigger 84 returns and the protruding pin 50 and latch 63 are engaged.
hold the engagement. However, since the pumping prevention lever 81 is prevented from returning by the pumping prevention pin 89, the closing command is temporarily released and the notch 81a of the pumping prevention lever 81 and the end 84c of the trigger 84 are connected as shown in FIG. If the circuit breaker is not engaged as shown in b, the circuit breaker will not close again.
The function of anti-pumping is achieved.
なお、このようなポンピング防止装置の構成そ
のものは、例えば実公昭56−46292等に示される
ように公知のものである。 The structure of such a pumping prevention device itself is known, for example, as shown in Japanese Utility Model Publication No. 56-46292.
なお、本発明の一実施例の説明において「遮
断」または「投入」とあるところを各々「投入」
または「遮断」に読み換えても本発明の効果は同
様である。 In addition, in the description of an embodiment of the present invention, "blocking" or "turning on" is replaced with "turning on" respectively.
Alternatively, the effect of the present invention is the same even if it is read as "blocking".
また、本実施例においては、差動ピストンの大
面積側へ高圧液体を供給・排出するために主弁及
び増巾弁の両者を併用する場合について説明して
いるが、この増巾弁で直接差動ピストンの大面積
側へ高圧液体を供給・排出することも可能であ
り、この場合も本発明が同様の効果を奏すること
は明らかである。 In addition, in this embodiment, a case is explained in which both the main valve and the widening valve are used together to supply and discharge high pressure liquid to the large area side of the differential piston. It is also possible to supply and discharge high-pressure liquid to the larger-area side of the differential piston, and it is clear that the present invention provides similar effects in this case as well.
本発明の装置は上記のように、差動ピストンに
作用する推力の保持装置の操作信号の増巾を、従
来の液体切換弁に換えて、トリガーを用いた機械
的な増巾機構で構成するようにしたので、ポンピ
ング防止の機能を、従来の電磁継電器を用いる方
法に比べて、極めて簡素な機構で構成することが
可能となる。
As described above, the device of the present invention uses a mechanical amplification mechanism using a trigger to amplify the operating signal of the thrust holding device that acts on the differential piston, instead of the conventional liquid switching valve. As a result, the pumping prevention function can be configured with an extremely simple mechanism compared to a conventional method using an electromagnetic relay.
その結果、信頼性が向上するとともに、極めて
安価なポンピング防止機能を有する液圧式操作装
置を得ることができる。 As a result, it is possible to obtain a hydraulic operating device having improved reliability and an extremely inexpensive pumping prevention function.
第１図は本発明の一実施例を示す構成図で、ａ
は全体構成図、ｂはａの要部を示す構成図、第２
図は第１図の動作を説明する説明図で、ａは全体
図、ｂはａの要部の説明図、第３図ａ，ｂは第１
図のポンピング防止機構の動作を説明する説明図
で、第４図は従来の液圧式操作装置の構成図、第
５図は第４図の動作を説明する説明図、第６図は
第４図の動作を説明するタイミングチヤート、第
７図は第４図のポンピング防止機構の制御を示す
回路図である。
図において、７は主弁、８は増巾弁である。な
お、各図中、同一符号は同一又は相当部分を示
す。
FIG. 1 is a configuration diagram showing one embodiment of the present invention, a
is an overall configuration diagram, b is a configuration diagram showing the main parts of a, 2nd
The figures are explanatory views for explaining the operation of Fig. 1, where a is an overall view, b is an explanatory view of the main part of a, and Figs. 3 a and b are illustrations of the first
FIG. 4 is a configuration diagram of a conventional hydraulic operating device, FIG. 5 is an explanatory diagram explaining the operation of FIG. 4, and FIG. 6 is a diagram explaining the operation of the pumping prevention mechanism shown in FIG. FIG. 7 is a timing chart illustrating the operation of FIG. 4, and FIG. 7 is a circuit diagram showing control of the pumping prevention mechanism shown in FIG. In the figure, 7 is a main valve, and 8 is a width increasing valve. In each figure, the same reference numerals indicate the same or equivalent parts.
Claims (1)
体を作用させ、大ピストン面側には液体圧を制御
する液体切換弁を介して高圧液体を作用させて上
記両ピストン面に作用する力の差によつて上記差
ピストンを前進位置に駆動し、上記差動ピストン
が後退位置において停止するときは上記差動ピス
トンを保持装置で後退位置に保持して上記両ピス
トン面に高圧液体を同時に作用させ、上記保持装
置の保持力を除去することによつて上記両ピスト
ン面に作用する力の差で上記差動ピストンを前進
位置に前進させ、上記大ピストン面側の高圧液体
を除去することによつて上記差動ピストンを後退
位置に後退させる液圧式操作装置において、第１
の操作信号でトリガ機構を作動して上記保持装置
の保持を解除して上記差動ピストンを前進させ、
第２の操作信号で上記液体切換弁を作動して上記
大ピストン面側の高圧液体を除去して上記差動ピ
ストンを後退させて上記差動ピストンを上記保持
装置で保持し、上記第２の操作信号が解除される
と常時高圧を維持する蓄圧装置から絞りを介して
高圧液体が作用して上記液体切換弁を復帰させ、
上記液体切換弁の復帰によつて上記大ピストン面
側に高圧液体が供給され、上記大ピストン面側に
高圧液体が供給された状態で待機させるように構
成した液圧操作装置。1 High-pressure liquid is always applied to the small piston surface side of the differential piston, and high-pressure liquid is applied to the large piston surface side via a liquid switching valve that controls the liquid pressure, thereby creating a difference in the force acting on both piston surfaces. to drive the differential piston to the forward position, and when the differential piston stops at the backward position, the differential piston is held in the backward position by a holding device and high pressure liquid is applied simultaneously to both piston surfaces. By removing the holding force of the holding device, the differential piston is advanced to the forward position by the difference in force acting on both piston surfaces, and the high pressure liquid on the large piston surface side is removed. In the hydraulic operating device for retracting the differential piston to a retracted position, the first
actuating a trigger mechanism in response to an operation signal to release the holding device and move the differential piston forward;
The liquid switching valve is actuated by a second operation signal to remove the high pressure liquid on the large piston surface side, the differential piston is moved backward, the differential piston is held by the holding device, and the second When the operation signal is released, high pressure liquid acts through the throttle from the pressure accumulator that maintains high pressure at all times, returning the liquid switching valve,
The hydraulic operating device is configured to supply high pressure liquid to the large piston surface side when the liquid switching valve returns, and to wait in a state where the high pressure liquid is supplied to the large piston surface side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27677984A JPS61158635A (en) | 1984-12-28 | 1984-12-28 | Hydraulic type operator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27677984A JPS61158635A (en) | 1984-12-28 | 1984-12-28 | Hydraulic type operator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61158635A JPS61158635A (en) | 1986-07-18 |
| JPH0253895B2 true JPH0253895B2 (en) | 1990-11-20 |
Family
ID=17574240
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27677984A Granted JPS61158635A (en) | 1984-12-28 | 1984-12-28 | Hydraulic type operator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61158635A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0475691U (en) * | 1990-11-16 | 1992-07-02 |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4785712A (en) * | 1986-05-27 | 1988-11-22 | Mitsubishi Denki Kabushiki Kaisha | Hydraulic operating apparatus for electric circuit breaker |
| US5986909A (en) * | 1998-05-21 | 1999-11-16 | Robicon Corporation | Multiphase power supply with plural series connected cells and failed cell bypass |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6137163Y2 (en) * | 1979-03-16 | 1986-10-28 |
-
1984
- 1984-12-28 JP JP27677984A patent/JPS61158635A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0475691U (en) * | 1990-11-16 | 1992-07-02 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61158635A (en) | 1986-07-18 |
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