JPH0213408B2 - - Google Patents
Info
- Publication number
- JPH0213408B2 JPH0213408B2 JP27590984A JP27590984A JPH0213408B2 JP H0213408 B2 JPH0213408 B2 JP H0213408B2 JP 27590984 A JP27590984 A JP 27590984A JP 27590984 A JP27590984 A JP 27590984A JP H0213408 B2 JPH0213408 B2 JP H0213408B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- liquid
- differential piston
- 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
Links
- 239000007788 liquid Substances 0.000 claims description 86
- 230000000903 blocking effect Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000007257 malfunction Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000007789 sealing Methods 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 used in a power switch to perform 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
は強い。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。
As the capacity and voltage of power transmission systems increases, there is a strong demand for improved performance of switches, especially power circuit breakers. In addition to the application of gas-insulated circuit breakers that use SF6 gas as the arc-extinguishing insulating medium, improvements in performance that contribute to system stability, such as faster opening/closing speed and less variation in opening/closing times, are desired. ing. 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替えられつつあ
る。 Conventionally, air pressure has generally been used as a driving source. However, as systems become larger in capacity and equipment becomes larger due to higher voltages, pneumatic operating devices become larger and the noise associated with air supply and exhaust during operation increases, as well as maintenance of the compressor that generates air pressure. There are disadvantages such as increased cost, and as a result, an operation method using hydraulic pressure or the like is being switched to.
液圧式操作装置、中でも油圧操作置は油の非圧
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 increase the pressure to higher 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 during the initial assembly stage, or if air gets mixed into the liquid during the liquid compression process and dissolves into the liquid, the response of the circuit breaker will be delayed due to this air. , there are problems such as 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となり、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 conventional equipment, after assembly, it is necessary to repeat the break-in operation many times over a long period of time to exhaust the air inside the equipment. When performing disassembly and reassembly, such a large number of break-in operations may prolong the recovery time of the switchgear equipment and may pose problems in the operation of the substation.
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考案さ
れている。 In order to solve these problems, conventional control circuits for the main valve that selectively switch the high-pressure liquid acting on the cylinder and the liquid pressure acting on the large pressure receiving surface of the differential piston are controlled at the instant when an operation command is given. Hydraulic operating devices have been devised that maintain high pressure at all times except for.
第６図はこのような従来の液圧式操作装置の構
成図を示している。図において、１は開閉器の接
触子で、ロツド２を介して駆動装置に連結され、
投入・遮断動作を行なう。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，４ｂとで駆動装置６が構成されてい
る。駆動装置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。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。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
て主弁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。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の側に供給する管路である。また、管
路５２はアキユムレータからの高圧液体を、絞り
５４、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５
７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２
０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。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。各電磁装置は可動鉄心３５ａ，３６ａ及び固
定コイル３５ｂ，３６ｂからなる。投入弁３８の
一端に連通した管路５６は管路５９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１８へ連通してい
る。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６
３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。 FIG. 6 shows a configuration diagram of such a conventional hydraulic operating device. In the figure, 1 is a contactor of a switch, which is connected to a drive device via a rod 2.
Performs closing/cutting operations. A drive device 6 is composed of a differential piston 3 for driving the contactor 1, a cylinder 5, and dart pot rings 4a and 4b. The drive 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 always maintained at a predetermined pressure by a pump (not shown) in an accumulator 9.
Supplied from. The high-pressure liquid is supplied from the accumulator 9 via a conduit 10 to a chamber 5a inside the cylinder 5 on the small piston surface side, and further supplied to the main valve 7 via a conduit 11. 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. the result,
The supply valve 13 and the discharge valve 14 operate together 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 a low pressure tank 18 via a conduit 17. 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 branch 51 from the pipe 12 is a pipe that supplies high-pressure liquid from the accumulator 9 to the auxiliary supply valve 20 side of the widening valve 8 . Further, the pipe 52 guides the high-pressure liquid from the accumulator to one end of the input valve 38 via the throttle 54 and 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 is connected to the pipe line 5
7 and the pilot chamber 21 via a pipe 55, and the other end is connected to the low pressure tank 18 via a pipe 58.
It is connected to. The width increasing valve 8 includes an auxiliary discharge valve 19, a spring 19a, and an auxiliary supply valve 2, which are arranged to face each other.
The pilot chamber 21 of the auxiliary discharge valve 19 receives 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 . 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. Each electromagnetic device consists of a movable core 35a, 36a and a fixed coil 35b, 36b. A pipe line 56 communicating with one end of the injection valve 38 communicates with a injection control device 61 via a pipe line 59, and the other end of the injection valve 38 communicates with the low pressure tank 18 via a pipe line 60. 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. Note that if the pressing force of the small piston 62 is removed while the differential piston 3 is being applied with an axial (upward) thrust, the thrust of the differential piston 3 will cause the latch 6 to open.
The shape of the latch 63 is determined so that the engagement between the latch 3 and the protruding pin 50 is naturally released.
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７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６図において、接触子１を開
くために第７図ａのa1点で電磁装置３６に投入指
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、球形弁
３０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に連通して第７図ｂのb1点
で示すように高圧液体が排出される。これによ
り、増巾弁８の補助排出弁１９は開口し、補助供
給弁２０は第７図ｃのc1点で示すように閉止す
る。この為、主弁７の排出弁１４のパイロツト室
１５は、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内の高圧液体は
第７図ｄのd1点で示すように排出される。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、対向して配設される
供給弁１３を第７図ｅのe1点で示すように閉止す
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、管路１７を通して第７図ｆの
f1点で示すように排出される。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７図
ｇのg1点からg2点の遮断方向に駆動を開始する。
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６２
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し、突出ピン５
０がラツチ６３をよぎる（第７図ｇのg2点）と、
小ピストン６２に押圧されたラツチ６３は、軸６
４の回りに回動を開始（第７図ｈのh1点）し、突
出ピン５０と係合する（第７図ｈのh2点）。一方、
第７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、絞り５
３、管路５５を介してパイロツト室２１へ高圧液
が除々に供給（第７図ｂのb2点から）される。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（第７図ｃのc2点）す
る。そして、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を通して第７図ｄのd2点に示すよう
に排出弁１４のパイロツト室１５に達し、再び主
弁７を切り換える。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（第７図ｅの
e2点）させる。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（第７図ｆの
f2点）するが、既にラツチ６３と突出ピン５０が
係合を完了（第７図ｈのh2点）しており、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８図の状
態を保つ。 In FIG. 6 showing the closing state, when a closing command is input to the electromagnetic device 36 at point a in FIG. 7a to open the contact 1, the movable iron core 36a is driven.
Acting on the shutoff valve 28 via the operating rod 34, the spherical valve 30 is opened. As a result, the pilot chamber 21 of the auxiliary discharge valve 19 of the widening valve 8 is connected to the pipes 57 and 58.
The high pressure liquid is communicated with the low pressure tank 18 through the tank 18, and the high pressure liquid is discharged as shown at point b1 in FIG. 7b. As a result, the auxiliary discharge valve 19 of the width increasing valve 8 opens, and the auxiliary supply valve 20 closes as shown at point c1 in FIG. 7c. For this reason, 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 16 and the pipe 22, and the high pressure liquid in the pilot chamber 15 is drained as shown by point d1 in FIG. 7d. is discharged. Main valve 7
When the high-pressure liquid in the pilot chamber 15 is discharged, the discharge valve 14 opens the pipe line 17 communicating with the low-pressure tank 18, and also opens the supply valve 13 disposed opposite to it in e of FIG. Close as indicated by one point. As a result, the high pressure liquid in the chamber 5b on the large area side of the differential piston 3 passes through the pipe line 17 as shown in FIG. 7f.
f is discharged as shown by one point. As a result, in the figure,
A downward thrust is generated, and the differential piston 3 starts driving in the blocking direction from point g1 to point g2 in FIG. 7g.
At this time, since 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 62.
The differential piston 26 completes its drive in the blocking direction, and the protruding pin 5
When 0 crosses the latch 63 (g 2 point in Figure 7 g),
The latch 63 pressed by the small piston 62
4 ( 1 point h in FIG. 7 h) and engages with the protruding pin 50 ( 2 points h in FIG. 7 h). on the other hand,
When the command to the electromagnetic device 36 is released at point a 2 in FIG. As a result, aperture 5
3. High-pressure liquid is gradually supplied to the pilot chamber 21 via the pipe 55 (from point b 2 in FIG. 7b). When the pressure in the pilot chamber 21 reaches a certain preset value, the auxiliary supply valve 2 is closed.
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. 7c). The auxiliary discharge valve 19 of the width increaser valve 8 closes the pipe line 22 communicating with the low pressure tank 18, and opens the auxiliary supply valve 20 opposite thereto. As a result, the high pressure liquid is transferred to the pipe line 12 and the pipe line 51.
It then passes through the conduit 16 to the pilot chamber 15 of the discharge valve 14 as shown at point d2 in FIG. 7d, and switches the main valve 7 again. When the discharge valve 14 receives the action of high-pressure liquid in its pilot chamber 15, it closes the pipe line 17 communicating with the low-pressure tank 18 and opens the supply valve 13 disposed opposite to it (as shown in FIG. 7e).
e 2 points) As a result, 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 a thrust upward in the figure is generated due to the difference in the pressure-receiving area of the differential piston 3 ( Figure 7 f
f 2 points), but the latch 63 and the protruding pin 50 have already completed engagement (h 2 points in Fig. 7 h), and the small piston 62 is supplied via the throttle 54 and the conduit 59. Since a back force is applied by the high-pressure liquid, the upward thrust applied to the differential piston 3 is held by the latch 63, and the shutoff is completed and the state shown in FIG. 8 is maintained.
次に投入動作について説明する。第８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、高圧液体が排
出される。その結果、保持装置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。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６図の状態になる。 Next, the closing operation will be explained. In FIG. 8, 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, causing the spherical valve 29 to open. It will be done. Thereby, the lines 56 and 59 communicate with the low pressure tank 18, and the high pressure liquid is discharged. As a result, the force that presses the small piston 62 of the holding device 61 from behind is removed, but as mentioned above, if the pressing force of the small piston 62 is removed, the latch 63 is moved by the thrust of the differential piston 3. Since the shape of the latch 63 is determined so that the engagement of the protruding pin 50 is naturally released, the differential piston 3 begins to move upward and finally completes the closing. 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 ready for the next shutoff operation. The state shown in Fig. 6 is filled with high-pressure liquid.
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、インパルス状の動作指令が遮断電磁
装置３６に与えられると、球形弁３０が瞬時開く
ためパイロツト室２１の圧力も瞬時下がり、増巾
弁８は一旦状態を反転する。しかし、動作指令が
極めて短時間のために球形弁３０は即座に復帰す
る。その結果、絞り５３から高圧液体がパイロツ
ト室２１に再度供給され、増巾弁８は動作指令が
与えられる直前の状態に戻つてしまう。このた
め、主弁７も動作指令に対応して状態を一旦反転
した後、再度状態を復帰させるので、結局差動ピ
ストン３は遮断方向へ動作を開始するが、動作を
完了する以前に再び投入方向（上方向）へ戻つて
しまうという不具合が生じていた。
Since the conventional hydraulic operating device is configured as described above, when an impulse-like operation command is given to the shut-off electromagnetic device 36, the spherical valve 30 instantly opens, and the pressure in the pilot chamber 21 also drops instantly, causing an increase in width. Valve 8 once reverses its state. However, since the operation command is extremely short, the spherical valve 30 returns immediately. As a result, high-pressure liquid is supplied from the throttle 53 to the pilot chamber 21 again, and the width increasing valve 8 returns to the state immediately before the operation command was given. For this reason, the main valve 7 also reverses its state once in response to the operation command, and then returns to its state again, so that the differential piston 3 eventually starts operating in the blocking direction, but it closes again before completing its operation. There was a problem where the screen would return to the upper direction.
この発明に係る減圧式操作装置は、遮断動作完
了時に液体切換弁を復帰させるための高圧液体を
差動ピストンに連動して開放、閉止を行なう部位
を介して供給するように構成したものである。
The pressure reduction type operating device according to the present invention is configured to supply high-pressure liquid for returning the liquid switching valve when the shutoff operation is completed through a part that opens and closes in conjunction with a differential piston. .
その結果、液体切換弁には差動ピストンの動作
完了を検出した後に高圧液体が供給されることに
なり、インパルス状の動作指令が遮断電磁装置に
与えられても液圧式操作装置は正常に動作する。
As a result, high-pressure liquid is supplied to the liquid switching valve after detecting the completion of the differential piston operation, and the hydraulic operating device operates normally even if an impulse-like operation command is given to the shutoff electromagnetic device. do.
以下、この発明の一実施例を図について説明す
る。
An embodiment of the present invention will be described below with reference to the drawings.
第１図において、７４はダツシユポツトリング
でシリンダ５の内面に沿つて上下にわずかに摺動
可能に構成されている。そして、ダツシユポツト
リング７４がピストン３に押圧された状態におい
て、ダツシユポツトリング７４の周囲に設けられ
た環状溝部７３がシリンダ５に設けられた管路７
６と７７を連通させるとともに、大ピストン面側
の室５ｂからほぼ油密を保ちつつ隔てられる。ま
た、ダツシユポツトリング７４がピストン３によ
つて押圧されず、かつ大ピストン面側の室５ｂよ
り管路７６及び７７の内部の圧力が高いときはダ
ツシユポツトリング７４は上方へ押し上げられて
大ピストン面側の室５ｂと管路７６及び７７は連
通する。管路７６はアキユムレータ９から低圧タ
ンク１８への高圧液体の放出量を抑制するための
絞り７５を介して常時高圧を保つ管路１１へ、ま
た管路７７は絞り７２、管路７１を介してパイロ
ツト室２１へ連通している。 In FIG. 1, reference numeral 74 denotes a dart pot ring which is configured to be slightly slidable up and down along the inner surface of the cylinder 5. When the dart pot ring 74 is pressed by the piston 3, the annular groove 73 provided around the dart pot ring 74 is connected to the pipe line 7 provided in the cylinder 5.
6 and 77 are communicated with each other, and are separated from the chamber 5b on the large piston surface side while maintaining almost oil tightness. Further, when the dart pot ring 74 is not pressed by the piston 3 and the pressure inside the pipes 76 and 77 is higher than the pressure inside the chamber 5b on the large piston surface side, the dart pot ring 74 is pushed upward. The chamber 5b on the large piston surface side communicates with the conduits 76 and 77. The pipe line 76 is connected to the pipe line 11 which maintains high pressure at all times via a throttle 75 for suppressing the amount of high-pressure liquid discharged from the accumulator 9 to the low-pressure tank 18, and the pipe line 77 is connected to the pipe line 11 through the throttle 72 and the pipe line 71. It communicates with the pilot room 21.
次に上記のように構成されたこの発明による装
置の遮断時の動作について第２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、ｈ
はラツチ６３の動きを、またｉは環状溝部７３の
内部の液体圧力を表わすタイムチヤートである。 Next, the operation of the device according to the present invention constructed as described above at the time of shutoff will be explained with reference to the time chart shown in FIG. In the figure, a
is the ON/OFF state of the excitation signal for the cut-off electromagnetic device 36, b is the liquid pressure in the pilot chamber 21 of the auxiliary discharge valve 19, and c is the position of the auxiliary discharge valve 19 and the auxiliary supply valve 20, which 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
is the liquid pressure inside the chamber 5b on the large piston surface side of the differential piston 3, g is the movement of the differential piston 3, h is
is a time chart representing the movement of the latch 63, and i represents the liquid pressure inside the annular groove 73.
投入状態を示す第１図において、接触子１を開
くために第２図ａのa1点で電磁装置３６に投入指
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、球形弁
３０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に連通して第２図ｂのb1点
で高圧液体が排出される。これにより、増巾弁８
の補助排出弁１９は開口し、補助供給弁２０は第
２図ｃのc1点で閉止する。この為、主弁７の排出
弁１４のパイロツト室１５は、管路１６、管路２
２を通して低圧タンク１８に連通して、パイロツ
ト室１５内の高圧液体が第２図ｄのd1点で排出さ
れる。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、対向し
て配設される供給弁１３を第２図ｅのe1点で閉止
する。これにより、差動ピストン３の大面積側の
室５ｂの高圧液体は管路１７を通して第２図ｆの
f1点で排出される。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２図ｇのg1点か
ら遮断方向に駆動を開始する。差動ピストン３の
大面積側の室５ｂの圧力が低下すると、管路７６
及び７７の高圧液体はダツシユポツトリング７４
を押し上げながら排出され、また絞り７５から
徐々に供給される高圧液体も第２図ｉのi1点で示
すように同時に排出される。従つて、第６図ａに
示すようなインパルス状の動作指令が与えられた
場合でも、増巾弁８及び主弁７が一旦状態を反転
してしまえば、上述のように管路７７の内部の高
圧液体が排出されてしまうので、動作指令信号の
消滅後（第２図ａのa3点以後）遮断弁２８が閉止
されても差動ピストン３が動作を完了するまでは
増巾弁８及び主弁７の状態が反転復帰することは
ない。このとき、保持装置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し、突出ピン
５０がラツチ６３をよぎる（第２図ｇのg2点）
と、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（第２図ｈのh1点から）
し、突出ピン５０と係合（第７図ｈのh2点）す
る。遮断が完了したこの状態においては、ダツシ
ユポツトリング７４の下面とシリンダ５が密着し
ており、その結果、アキユムレータ９からの高圧
液体は絞り７５を介して環状溝７３及び管路７
６，７７へ供給（第２図ｉのi2点から）され、さ
らに絞り７２及び管路７１を介してパイロツト室
２１へ高圧液が徐々に供給（第２図ｂのb2点か
ら）される。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２０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１
９及び補助供給弁２０は一体となつて移動（第２
図ｃのc2点）する。そして、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１
２、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、再び主弁７を切り換え
る。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を第２図ｅのe2点で開口させる。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、上方向の推力が第２図ｆのf2点で発生する
が、既にラツチ６３と突出ピン５０が係合を完了
（第２図ｈのh2点）しており、また小ピストン６
２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、第３図の状態を保つ。 In FIG. 1 showing the closing state, when a closing command is input to the electromagnetic device 36 at point a in FIG. 2 to open the contact 1, the movable iron core 36a is driven,
Acting on the shutoff valve 28 via the operating rod 34, the spherical valve 30 is opened. As a result, the pilot chamber 21 of the auxiliary discharge valve 19 of the widening valve 8 is connected to the pipes 57 and 58.
It communicates with the low pressure tank 18 through the tank 18, and the high pressure liquid is discharged at point b in FIG. 2b. As a result, the width increasing valve 8
The auxiliary discharge valve 19 opens, and the auxiliary supply valve 20 closes at point c in FIG. 2c . For this reason, the pilot chamber 15 of the discharge valve 14 of the main valve 7 is connected to the pipe line 16 and the pipe line 2.
2 to the low pressure tank 18, the high pressure liquid in the pilot chamber 15 is discharged at point d1 in FIG. 2d. When the high pressure liquid in the pilot chamber 15 is discharged, the discharge valve 14 of the main valve 7 discharges the low pressure liquid into the low pressure tank 18.
The pipe line 17 communicating with is opened, and the supply valve 13 disposed opposite thereto is closed at point e in FIG. 2e . As a result, the high pressure liquid in the chamber 5b on the large area side of the differential piston 3 passes through the pipe line 17 as shown in FIG. 2f.
f It is discharged at one point. 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 2g. When the pressure in the large area side chamber 5b of the differential piston 3 decreases, the pipe line 76
and 77 high pressure liquid is in the dart pot ring 74
The high-pressure liquid is discharged while pushing up, and the high-pressure liquid gradually supplied from the throttle 75 is also discharged at the same time, as shown at point i in FIG. 2i . Therefore, even if an impulse-like operation command as shown in FIG. Therefore, even if the shutoff valve 28 is closed after the operation command signal disappears (after point a 3 in FIG. And the state of the main valve 7 will not reverse and return. At this time, since high pressure liquid is supplied to the holding 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, and the protruding pin 50 crosses the latch 63 (point g 2 in Figure 2 g).
, the latch 63 pressed by the small piston 62 starts rotating around the shaft 64 (from point h1 in Fig. 2h)
and engages with the protruding pin 50 ( 2 points h in Fig. 7 h). In this state where the shutoff is completed, the lower surface of the dart pot ring 74 and the cylinder 5 are in close contact with each other, and as a result, the high pressure liquid from the accumulator 9 flows through the annular groove 73 and the pipe line 7 through the throttle 75.
6, 77 (from 2 points i in Figure 2 i), and then gradually supplied to the pilot chamber 21 via the throttle 72 and pipe 71 (from 2 points b in Figure 2 b). Ru. When the pressure in the pilot chamber 21 reaches a certain preset value, the back pressure applied to the auxiliary supply valve 20 in the closed state overcomes the back pressure applied to the auxiliary discharge valve 19, and the auxiliary discharge valve 1
9 and the auxiliary supply valve 20 move together (second
Figure c c 2 points). The auxiliary discharge valve 19 of the widening valve 8 closes the pipe 22 communicating with the low pressure tank 18, and the auxiliary supply valve 20 opposite thereto closes the pipe 22 communicating with the low pressure tank 18.
Open it. This allows the high-pressure liquid to flow through pipe 1.
2. It reaches the pilot chamber 15 of the discharge valve 14 through the pipe 51 and the pipe 16, and switches the main valve 7 again. When the discharge valve 14 receives the action of high-pressure liquid in its pilot chamber 15, it closes the pipe line 17 communicating with the low-pressure tank 18, and also closes the supply valve 13 disposed opposite to it at point e in Figure 2 e. Open it with . As a result, the high pressure liquid reaches the chamber 5b on the large area side 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, the upward thrust in the figure is This occurs at point f 2 in Figure 2 f, but the latch 63 and the protruding pin 50 have already completed engagement (point h 2 in Figure 2 h), and the small piston 6
Since a back force is applied to the differential piston 2 by the high pressure fluid supplied through the throttle 54 and the conduit 59, the upward thrust applied to the differential piston 3 is held by the latch 63, and the shutoff is completed. Maintain the state shown in Figure 3.
なお、投入動作については従来のものと同様で
あるので説明を省略する。 Note that the closing operation is the same as the conventional one, so a description thereof will be omitted.
次に本発明の他の実施例について説明する。第
４図は本発明の他の実施例の要部を示す断面図で
ある。図において、１０２はピストン５とダツシ
ユポツトリング７４の間の摺動用のすき間１０１
を液密にシールするためのパツキンである。遮断
動作の最終過程において、差動ピストン３がダツ
シユポツトリング７４に嵌合し始めると、差動ピ
ストン３とダツシユポツトリング７４で囲まれる
空間１０３の圧力が上昇し、この液圧力によつて
制動力が発生する。このとき、パツキン１０２は
無ければ高圧液はすき間１０１を介して管路７７
へ侵入する。このため、ダツシユポツトリング７
４による制動力が極めて大きく設定されている場
合には、空間１０３の液圧力が極めて高いので、
すき間１０１を介して管路７７へ侵入した高圧液
のために管路７７内の液圧力が変動する。その結
果、絞り７２を介してパイロツト室２１の圧力が
変動して、補助排出弁１９が当初設定した時期よ
りも早く動作するような誤動作の可能性もある。 Next, other embodiments of the present invention will be described. FIG. 4 is a sectional view showing the main parts of another embodiment of the present invention. In the figure, 102 is a sliding gap 101 between the piston 5 and the dart pot ring 74.
This is a gasket for liquid-tight sealing. In the final process of the shutoff operation, when the differential piston 3 begins to fit into the dart pot ring 74, the pressure in the space 103 surrounded by the differential piston 3 and the dart pot ring 74 increases, and this fluid pressure causes Braking force is generated. At this time, if there is no packing 102, the high pressure liquid will pass through the gap 101 to the pipe 77.
to invade. For this reason, the needle pot ring 7
When the braking force by 4 is set to be extremely large, the hydraulic pressure in the space 103 is extremely high, so
Due to the high pressure liquid that has entered the pipe line 77 through the gap 101, the liquid pressure within the pipe line 77 fluctuates. As a result, the pressure in the pilot chamber 21 fluctuates through the throttle 72, and there is a possibility that the auxiliary discharge valve 19 malfunctions earlier than the originally set timing.
このような場合には図に示すようにピストン５
とダツシユポツトリング７４の間にパツキン１０
２を設けて高圧液の侵入を防止する構造とするこ
とによつて誤動作の恐れは無くなる。 In such a case, as shown in the figure, the piston 5
Patsukin 10 between and Datsushi Pottring 74
2 to prevent the intrusion of high pressure liquid eliminates the possibility of malfunction.
次に第４図の説明で述べたものと同様の目的を
持つて成された他の実施例を説明する。 Next, another embodiment having the same purpose as that described in the explanation of FIG. 4 will be described.
第５図において、７７ａは絞り７５と絞り７２
の間をつなぐ管路で、絞り７５を介してアキユム
レータ９からの高圧液が常に供給されている。管
路７７ａの中間部は分岐して管路１１０を構成し
ている。管路１１０の管路７７ａと対向する側の
一端は、開口部１１０ａを有しており、ダツシユ
ポツトリング７４ｂが差動ピストン３に押圧され
て下降状態にあるときは、開口部１１０ａが閉止
される。また、ダツシユポツトリング７４ｂが差
動ピストン３に押圧されない状態にあるときに、
管路７７ａ及び１１０の内部が高圧状態になる
と、液圧力によつてダツシユポツトリング７４ｂ
が上方へ押し上げられる。その結果、管路１１０
の開口部１１０ａが開放される。従つて、遮断動
作の途中過程においては、管路７７ａ内の高圧液
は開口部１１０ａから放出されており、管路７１
及びパイロツト室２１に高圧液が供給されること
はない。一方、遮断動作の最終状態においては、
開口部１１０ａはダツシユポツトリング７４ｂに
よつて閉止されるので、絞り７５から供給される
管路７７ａ内の高圧液は保持されて、管路７１及
びパイロツト室２１に高圧液が供給される。この
とき、差動ピストン３とダツシユポツトリング７
４ｂの間の室１０３の高圧液はすき間１０１に侵
入するが、開口部１１０ａがダツシユポツトリン
グ７４ｂに閉止されているため、管路７７ａの内
部にまでは侵入することがない。 In FIG. 5, 77a is the aperture 75 and the aperture 72.
The high-pressure liquid from the accumulator 9 is constantly supplied through the conduit 75 between the two. The intermediate portion of the pipe line 77a branches to form a pipe line 110. One end of the conduit 110 facing the conduit 77a has an opening 110a, and when the dart pot ring 74b is pressed by the differential piston 3 and is in the downward state, the opening 110a is closed. be done. Furthermore, when the dart pot ring 74b is not pressed by the differential piston 3,
When the insides of the pipes 77a and 110 reach a high pressure state, the needle pot ring 74b is
is pushed upward. As a result, conduit 110
The opening 110a of is opened. Therefore, during the course of the shutoff operation, the high pressure liquid in the pipe line 77a is released from the opening 110a, and the high pressure liquid in the pipe line 71a is released from the opening 110a.
Also, high pressure liquid is not supplied to the pilot chamber 21. On the other hand, in the final state of the shutoff operation,
Since the opening 110a is closed by the dart pot ring 74b, the high pressure liquid in the pipe line 77a supplied from the throttle 75 is held, and the high pressure liquid is supplied to the pipe line 71 and the pilot chamber 21. At this time, the differential piston 3 and the dart pot ring 7
The high-pressure liquid in the chamber 103 between the chambers 4b and 4b enters the gap 101, but because the opening 110a is closed by the dash pot ring 74b, the high-pressure liquid does not enter the inside of the conduit 77a.
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 will produce similar effects in this case as well.
以上のようにこの発明によれば、遮断動作が完
了した後に液体切換弁に高圧液体が供給されるよ
う回路が構成されているので、インパルス状の動
作指令が遮断電磁装置に与えられても、液圧式操
作装置が正常に動作するという利点がある。
As described above, according to the present invention, the circuit is configured so that high-pressure liquid is supplied to the liquid switching valve after the shutoff operation is completed, so even if an impulse-like operation command is given to the shutoff electromagnetic device, There is an advantage that the hydraulic operating device operates normally.
第１図はこの発明の一実施例を示す液圧式操作
装置の構成図、第２図は第１図の動作を説明する
タイムチヤート、第３図は第１図の動作を説明す
る説明図、第４図及び第５図はそれぞれこの発明
の他の実施例を示す要部の断面図、第６図は従来
の液圧式操作装置の構成図、第７図は第６図の動
作を説明するタイムチヤート、第８図は第６図の
動作を説明する説明図である。
図において、３は差動ピストン、５はシリン
ダ、６は駆動装置、８は増巾弁、９はアキユムレ
ータ（蓄圧装置）、６１は保持装置である。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 of a hydraulic operating device showing an embodiment of the present invention, FIG. 2 is a time chart explaining the operation of FIG. 1, and FIG. 3 is an explanatory diagram explaining the operation of FIG. 1. 4 and 5 are sectional views of main parts showing other embodiments of the present invention, FIG. 6 is a configuration diagram of a conventional hydraulic operating device, and FIG. 7 explains the operation of FIG. 6. The time chart, FIG. 8, is an explanatory diagram illustrating the operation of FIG. 6. In the figure, 3 is a differential piston, 5 is a cylinder, 6 is a drive device, 8 is a widening valve, 9 is an accumulator (pressure accumulation device), and 61 is a holding device. In addition,
In each figure, the same reference numerals indicate the same or corresponding parts.
Claims (1)
小ピストン面側（ロツド側）には常時高圧液体を
作用させ、大ピストン面側（ヘツド側）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
させて上記差動ピストンを駆動し、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両ピ
ストン面に高圧液体が同時に作用するように構成
し、上記両ピストン面に作用する力の差によつて
生じる推力を上記差動ピストンまたはその延長部
に作用するよう構成した保持装置で保持すること
によつて上記差動ピストンの位置を保持し、保持
装置の保持力の除去によつて上記差動ピストンを
前進させ、また大ピストン面側（ヘツド側）の高
圧液体を除去することによつて上記差動ピストン
を後退させて上記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と、液体切換弁を操作
するための人力信号の増巾をいずれも液体圧力を
用いて行なうものにおいて、液体切換弁の復帰の
ための高圧液体は常時高圧を維持する蓄圧装置と
液体切換弁の間にあつて、上記差動ピストンに連
動して開放、閉止を行なう放圧機能部を介して供
給されることを特徴とする液圧式操作装置。 ２ 放圧機能部は差動ピストンに同心状態で係合
し、かつシリンダの内面に沿つて摺動可能な環状
部材で構成されていることを特徴とする特許請求
の範囲第１項記載の液圧式操作装置。 ３ 放圧機能部と蓄圧装置の間に絞り要素を設け
たことを特徴とする特許請求の範囲第１項又は第
２項記載の液圧式操作装置。[Claims] 1. A differential piston is used as a drive device, and high-pressure liquid is always applied to the small piston surface side (rod side), and liquid pressure is controlled on the large piston surface side (head side). The differential piston is driven by applying a high-pressure liquid through a liquid switching valve, and when the differential piston stops at a retreated position, the high-pressure liquid is applied to both piston surfaces at the same time. The position of the differential piston is held by holding the thrust generated by the difference in forces acting on the piston surface with a holding device configured to act on the differential piston or its extension, and the holding device maintains the position of the differential piston. Thrust acting on the differential piston by moving the differential piston forward by removing the holding force and retracting the differential piston by removing the high pressure liquid on the large piston surface side (head side). In a device that uses liquid pressure to both increase the amplitude of the operation signal for the holding device and the amplitude of the human power signal for operating the liquid switching valve, the high-pressure liquid for returning the liquid switching valve must be kept at high pressure at all times. A hydraulic operating device, characterized in that the pressure is supplied through a pressure release function section that is located between a pressure accumulator to be maintained and a liquid switching valve and opens and closes in conjunction with the differential piston. 2. The liquid according to claim 1, wherein the pressure relief function part is constituted by an annular member that concentrically engages with the differential piston and is slidable along the inner surface of the cylinder. Pressure operating device. 3. The hydraulic operating device according to claim 1 or 2, characterized in that a throttle element is provided between the pressure relief function section and the pressure accumulator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27590984A JPS61156613A (en) | 1984-12-27 | 1984-12-27 | Hydraulic type operator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27590984A JPS61156613A (en) | 1984-12-27 | 1984-12-27 | Hydraulic type operator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61156613A JPS61156613A (en) | 1986-07-16 |
| JPH0213408B2 true JPH0213408B2 (en) | 1990-04-04 |
Family
ID=17562117
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27590984A Granted JPS61156613A (en) | 1984-12-27 | 1984-12-27 | Hydraulic type operator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61156613A (en) |
Families Citing this family (3)
| 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 |
| JP3317534B2 (en) * | 1992-12-25 | 2002-08-26 | 株式会社東芝 | Hydraulic operation device for power switch |
| JP4724234B2 (en) * | 2009-04-13 | 2011-07-13 | 株式会社東芝 | Hydraulic operation device |
-
1984
- 1984-12-27 JP JP27590984A patent/JPS61156613A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61156613A (en) | 1986-07-16 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |