JPS621108B2 - - Google Patents
Info
- Publication number
- JPS621108B2 JPS621108B2 JP54159166A JP15916679A JPS621108B2 JP S621108 B2 JPS621108 B2 JP S621108B2 JP 54159166 A JP54159166 A JP 54159166A JP 15916679 A JP15916679 A JP 15916679A JP S621108 B2 JPS621108 B2 JP S621108B2
- Authority
- JP
- Japan
- Prior art keywords
- servo motor
- valve
- throttle
- closing speed
- switching
- 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
- 238000000034 method Methods 0.000 claims description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 43
- 239000003921 oil Substances 0.000 description 35
- 230000002159 abnormal effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 238000001514 detection method Methods 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Landscapes
- Control Of Water Turbines (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は水力機械の保護装置に係り、特に水車
およびポンプ水車のガイドベーンを開閉駆動する
サーボモータの閉鎖過程に異常が生じた場合に対
処しうる水力機械の保護装置に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a protection device for hydraulic machinery, and in particular, it is used to cope with the case where an abnormality occurs in the closing process of a servo motor that drives the guide vanes of a water turbine and a pump water turbine. This invention relates to a protective device for hydraulic machinery that can be used.
一般に、フランシス水車およびポンプ水車は運
転中に負荷遮断を行つたり、または何らかの不足
の原因により非常停止を行う必要がある。
Generally, Francis turbines and pump turbines require load shedding during operation or emergency shutdown due to some shortage.
従来、水圧鉄管内の水圧上昇を極力低く抑える
ために、ガイドベーンを開閉駆動するサーボモー
タの閉鎖速度として、第１図に示すような全スト
ロークの途中に急閉鎖速度と緩閉鎖速度の異なつ
た２つの閉鎖速度を有する、いわゆる急緩２段閉
鎖速度方式が採用されてきた。即ち、第３図に示
す従来技術においてポンプ水車が水車側の負荷遮
断をする場合を例にとつてこの急緩２段閉鎖速度
方式を説明すると、図示にないポンプ水車急停止
用電磁弁の動作により、ポンプ水車急停止用の電
磁弁の圧油２０が排油され、ポンプ水車急停止弁
１８が排油側に切換わり、主配圧弁１０のプラン
ジヤー１１が下動し、サーボモータ５が主配圧弁
１０のプランジヤーストロークによつて定まる閉
鎖速度、すなわち第１図の中の急閉鎖速度線１Ａ
に沿つてまず急閉鎖する。サーボモータ５がある
所定の開度まで閉鎖すると、水車側切換弁１２が
カム１３によつて切換えられ、水車側絞り弁１６
のピストン２５を絞り位置に操作する。この絞り
弁１６の動作によつて、サーボモータ５は第１図
中の緩閉鎖速度線２Ａに沿てて緩閉鎖する。この
ようにして、サーボモータの急緩２段閉鎖速度方
式が達成される（尚第１図のグラフにおいて、縦
軸はサーボストロークＤを、横軸は閉鎖時間Ｔを
示す）。この動作はポンプ側についてもまつたく
同様である。しかし、このような従来方式におい
て、切換弁１２，１４または絞り弁１６，１７に
故障を生じた場合、サーボモータ動作特性は、第
１図において点線３Ａで示すようになりガイドベ
ーンは急閉鎖される。この場合、水圧鉄管内の水
圧は異常に上昇し、場合によつては水圧鉄管破裂
というような大事故の原因となつていた。 Conventionally, in order to keep the rise in water pressure inside the penstock as low as possible, the closing speed of the servo motor that drives the guide vane to open and close has been changed to a sudden closing speed and a slow closing speed during the entire stroke as shown in Figure 1. A so-called quick-slow two-stage closing speed system with two closing speeds has been adopted. That is, to explain this two-step closing speed system using the case where the pump-turbine cuts off the load on the water-turbine side in the prior art shown in FIG. As a result, the pressure oil 20 of the electromagnetic valve for sudden stop of the pump-turbine is drained, the sudden stop valve 18 of the pump-turbine is switched to the oil drain side, the plunger 11 of the main pressure distribution valve 10 is moved downward, and the servo motor 5 is The closing speed determined by the plunger stroke of the pressure regulating valve 10, that is, the sudden closing speed line 1A in FIG.
First, there will be a sudden closure. When the servo motor 5 is closed to a certain predetermined opening degree, the water turbine side switching valve 12 is switched by the cam 13, and the water turbine side throttle valve 16 is switched by the cam 13.
The piston 25 of is operated to the throttle position. Due to this operation of the throttle valve 16, the servo motor 5 is slowly closed along the slow closing speed line 2A in FIG. In this way, a two-stage closing speed system of the servo motor is achieved (in the graph of FIG. 1, the vertical axis shows the servo stroke D and the horizontal axis shows the closing time T). This operation is exactly the same on the pump side. However, in such a conventional system, if a failure occurs in the switching valves 12, 14 or the throttle valves 16, 17, the servo motor operating characteristics will become as shown by dotted line 3A in Figure 1, and the guide vane will be suddenly closed. Ru. In this case, the water pressure inside the penstock would rise abnormally, which could lead to a major accident such as a rupture of the penstock.
このような大事故を防止するため、近年、サー
ボモータの急緩閉鎖速度切換用切換装置に第２の
切換装置を追加して二重化し、水圧鉄管又はうず
巻きケーシング内の異常水圧上昇を検出してこの
第２の切換装置を作動させ以て水圧鉄管の異常圧
力上昇を防止しようという提案がなされている
（特開昭53−105642号）。 In order to prevent such major accidents, in recent years, a second switching device has been added to the switching device for switching the servo motor's rapid and slow closing speed to make it redundant, and the system is designed to detect abnormal increases in water pressure inside the penstock or spiral casing. A proposal has been made to prevent an abnormal pressure rise in the penstock by operating this second switching device (Japanese Patent Application Laid-open No. 105642/1983).
しかしながらこの提案では、水圧鉄管内の異常
水圧上昇を検出してから第２の切換装置の作動指
令信号を出すため、指令信号として遅すぎ、従つ
て、水圧鉄管内の異常水圧上昇は、かなり大きく
なる。また、主機の色々な運転状態、各種遮断条
件などによつて正常時の水圧上昇値はそれぞれ異
るので、異常指令信号として検出するための水圧
設定値は、通常遮断に対してかなり高いところに
セツトしておかなければならないなど大きな欠点
を有している。
However, in this proposal, the command signal for operating the second switching device is issued after detecting the abnormal water pressure rise in the penstock, which is too slow as a command signal, and therefore the abnormal water pressure rise in the penstock is quite large. Become. In addition, the water pressure rise value during normal operation varies depending on the various operating conditions of the main engine, various shutoff conditions, etc., so the water pressure setting value to be detected as an abnormal command signal must be set at a considerably higher level than normal shutoff. It has major drawbacks, such as the need to set it in advance.
本発明の目的は、上記した如き従来技術の欠点
をなくし、サーボモータの急緩閉鎖速度切換用切
換装置が故障した場合であつても、水圧鉄管内の
水圧上昇は正常遮断時の水圧上昇とほぼ同程度で
すむように又は高くなるとしても極くわずか高く
なる程度ですむように、サーボモータを全ストロ
ークの途中で緩閉鎖に移行させることができるよ
うにした水力機械の保護装置を提供することにあ
る。 An object of the present invention is to eliminate the drawbacks of the prior art as described above, and even if the switching device for switching the servo motor's rapid/relaxed closing speed fails, the increase in water pressure in the penstock will be the same as the increase in water pressure during normal shutoff. To provide a protection device for a hydraulic machine capable of shifting a servo motor to a gentle closing in the middle of a full stroke so that the increase is almost the same or only slightly higher.
上記問題点を解決するための本発明は、水力機
械のガイドベーンを開閉操作するサーボモータ
と、水力機械の回転速度の変化に応動して上記サ
ーボモータに圧油を給排する主配圧弁と、ガイド
ベーン閉鎖時におけるサーボモータの圧油の給排
管路の流路を段階的に絞り、所定の急閉鎖速度お
よびこれに引きつづいて所定の緩閉鎖速度でサー
ボモータを段階的に閉じることの出来る第１の絞
り装置と、サーボモータの全ストロークの途中に
設定された閉鎖速度切換点でサーボモータに緩閉
鎖速度を与えるように前記第１の絞り弁を切換え
る第１の切換装置とを備えた水力機械の保護装置
において、
正常運転者は前記給排管路を全開する位置にあ
る第２の絞り装置と、
前記第１の絞り装置の故障を前記サーボモータ
の動作位置と前記第１の絞り装置のピストンの動
きとを直接的に検出して前記第２の絞り装置を前
記給排管路の流路絞り位置に切換えてサーボモー
タに前記所定の緩閉鎖速度を与えるように作用す
る第２の切換装置とを有することを特徴とするも
のである。
To solve the above problems, the present invention includes a servo motor that opens and closes a guide vane of a hydraulic machine, and a main pressure distribution valve that supplies and discharges pressure oil to the servo motor in response to changes in the rotational speed of the hydraulic machine. , step-by-step narrowing of the flow path of the pressure oil supply and discharge pipeline of the servo motor when the guide vane is closed, and step-by-step closing of the servo motor at a predetermined rapid closing speed and subsequently at a predetermined slow closing speed; and a first switching device that switches the first throttle valve so as to give a gentle closing speed to the servo motor at a closing speed switching point set in the middle of the full stroke of the servo motor. In the protection device for hydraulic machinery, a normal operator detects a failure of the second throttling device located at the position where the supply/discharge pipe is fully opened, and the first throttling device at the operating position of the servo motor and the first throttling device. The movement of the piston of the throttle device is directly detected and the second throttle device is switched to a flow passage throttle position of the supply/discharge pipe, thereby acting to give the servo motor the predetermined slow closing speed. The present invention is characterized in that it has a second switching device.
以上の本発明によれば、第２の切換装置は、前
記第１の絞り装置の故障を前記サーボモータの動
作位置と前記第１の絞り装置のピストンの動きと
を直接的に検出して前記第２の絞り装置を前記給
排管路の流路絞り位置に切換えてサーボモータに
前記所定の緩閉鎖速度を与えるように作用するも
のであるから、先に示した公知文献のごとく故障
により、水圧鉄管内の水圧が異常上昇してから絞
り位置を切換えるのではなく、故障発生源の事象
に基づいて切換えることができ、したがつて水圧
鉄管内の異常水圧上昇に達する前に先行的に当該
水圧の異常上昇を抑制することが可能となる。こ
のことにより、本発明の目的を達成することがで
きる。
According to the present invention, the second switching device detects a failure of the first throttle device by directly detecting the operating position of the servo motor and the movement of the piston of the first throttle device. Since the second throttling device is operated to switch the flow path throttling position of the supply/discharge pipe to give the servo motor the predetermined slow closing speed, a malfunction may occur as in the previously mentioned prior art document. Rather than switching the throttling position after the water pressure in the penstock has abnormally increased, it is possible to switch the throttling position based on the event at the source of the failure. It becomes possible to suppress abnormal increases in water pressure. This makes it possible to achieve the object of the present invention.
以下本発明の各実施例を第４図ないし第８図に
基づいて詳細に説明する。図中、第３図の従来装
置と共通する部分は同一の符号で示してある。
Each embodiment of the present invention will be described in detail below with reference to FIGS. 4 to 8. In the figure, parts common to the conventional device of FIG. 3 are designated by the same reference numerals.
第１実施例
第４図に示す一実施例においては、ガイドベー
ンを開閉駆動するサーボモータ５が給油管路６，
７を介して主配圧弁１０に接続されている。主配
圧弁１０は調速機からの信号に応答して切換制御
されるようになされており、図中、８および９は
排油管路を、また１１はプランジヤーを示す。水
車側の第１切換弁２７およびポンプ側の第１切換
弁３１は夫々カム２８，３２によつて検知された
サーボモータ５の閉鎖速度切換点で通油側に切換
わつて水車側およびポンプ側の第１の絞り弁３
５，３６を夫々絞り側に操作するようになされて
いる。さらに本例では水車側の第２の切換弁２９
およびポンプ側の第２の切換弁３３が設けられて
おり、カム３０，３４によつて検知されたサーボ
モータ５の閉鎖速度切換点で通油側に切換わつて
絞り弁切換弁４１，４２に夫々圧油を通油するよ
うになされている。これら水車側およびポンプ側
の各絞り弁切換弁４１，４２は第１の絞り弁ピス
トン３７，３８の開位置で通油側に切換わり、前
記第２の切換弁２９，３３からの圧油を第２の絞
り弁３９，４０に対して夫々作用するようになさ
れている。その他図中、１８はポンプ水車急停止
弁を、２０はポンプ水車急停止用の電磁弁（図示
せず）からの圧油を、２１，２２は各部への圧油
を夫々示し、また２３，２４は調速機連動機構を
示す。First Embodiment In one embodiment shown in FIG.
It is connected to the main pressure distribution valve 10 via 7. The main pressure distribution valve 10 is controlled to switch in response to a signal from a speed governor, and in the figure, 8 and 9 indicate oil drain pipes, and 11 indicates a plunger. The first switching valve 27 on the water turbine side and the first switching valve 31 on the pump side are switched to the oil passing side at the closing speed switching point of the servo motor 5 detected by the cams 28 and 32, respectively, and the first switching valve 27 on the water turbine side and the first switching valve 31 on the pump side switch to the oil passing side. the first throttle valve 3 of
5 and 36 are respectively operated to the aperture side. Furthermore, in this example, the second switching valve 29 on the water turbine side
A second switching valve 33 on the pump side is provided, and switches to the oil passing side at the closing speed switching point of the servo motor 5 detected by the cams 30 and 34, and switches to the throttle valve switching valve 41 and 42. Each of them is designed to allow pressure oil to pass through them. These throttle valve switching valves 41 and 42 on the water turbine side and the pump side are switched to the oil passing side when the first throttle valve pistons 37 and 38 are in the open position, and the pressure oil from the second switching valves 29 and 33 is switched to the oil passing side. It is adapted to act on the second throttle valves 39 and 40, respectively. In addition, in the figure, 18 indicates a pump-turbine sudden stop valve, 20 indicates pressure oil from a solenoid valve (not shown) for sudden pump-turbine stop, 21 and 22 indicate pressure oil to each part, and 23, 24 indicates a speed governor interlocking mechanism.
次に第４図の装置の負荷遮断時の動作を水車側
について説明する。ポンプ水車急停止用の電磁弁
（図示せず）が作動すると、その圧油２０が排油
されてポンプ水車急停止弁１８が排油側に切換わ
り、主配圧弁１０のプランジヤー１１が調速機か
らの信号とは無関係に圧油２２によつて図中下方
に移動する。このプランジヤーストーロークに対
応した閉鎖速度でサーボモータ５が図中矢印Ｐ方
向に移動し、第２図中曲線１Ｂで示すようにガイ
ドベーンの急速閉鎖が行われる。 Next, the operation of the apparatus shown in FIG. 4 at the time of load interruption will be explained on the water turbine side. When the solenoid valve (not shown) for sudden stop of the pump-turbine is activated, the pressure oil 20 is drained, the sudden stop valve 18 for the pump-turbine is switched to the oil drain side, and the plunger 11 of the main pressure distribution valve 10 is activated. It moves downward in the figure by pressure oil 22 regardless of the signal from the machine. The servo motor 5 moves in the direction of the arrow P in the figure at a closing speed corresponding to this plunger stroke, and the guide vane is rapidly closed as shown by the curve 1B in FIG. 2.
サーボモータ５がガイドベーンのある程度の開
度まで閉鎖動作すると、水車側の第１の切換弁２
７がカム２８の位置検知点で切換えられ、水車側
の第１の絞り弁３５のピストン３７を操作する動
作によつてサーボモータ５の閉鎖速度が低下され
る。したがつて、ガイドベーン閉鎖は第２図中曲
線２Ｂに沿う緩閉鎖速度で行われ、これによつて
正常の遮断時にはサーボモータの急緩２段閉鎖速
度方式による閉鎖が達成される。 When the servo motor 5 closes the guide vane to a certain degree, the first switching valve 2 on the water turbine side closes the guide vane.
7 is switched at the position detection point of the cam 28, and the closing speed of the servo motor 5 is reduced by the operation of operating the piston 37 of the first throttle valve 35 on the water turbine side. Therefore, the guide vane is closed at a slow closing speed along the curve 2B in FIG. 2, so that during normal shut-off, the servo motor achieves closing using the rapid-slow two-stage closing speed method.
ここで本実施例においては、水車側の第２の切
換弁２９が第１の切換弁２７と同一のまたは僅か
に閉鎖側寄りの切換弁動作開度位置でカム３０に
よつて通油側に切換えられるようになされてい
る。また第２の絞り弁切換弁４１はカム４３によ
つて第１の絞り弁ピストン３７が開位置にあると
きは通油側位置をとり、一方第１の絞り弁３５が
正常であつてピストン３７が絞り位置に動作する
と排油位置に切換わり、正常時には第２の絞り弁
３９が常に全開位置を保つようになされている。 In this embodiment, the second switching valve 29 on the water turbine side is switched to the oil passing side by the cam 30 at the same switching valve operating opening position as the first switching valve 27 or slightly closer to the closing side. It is designed to be switchable. Further, the second throttle valve switching valve 41 is controlled by the cam 43 to assume the oil passing side position when the first throttle valve piston 37 is in the open position, while on the other hand, when the first throttle valve 35 is normal and the piston 37 When the throttle valve 39 moves to the throttle position, it switches to the oil draining position, and the second throttle valve 39 always maintains the fully open position during normal operation.
したがつて、万一水車側の第１の切換弁２７、
第１の絞り弁３５に故障が生じて、第１の絞り弁
ピストン３７が動作しない場合には、前記第２の
絞り弁３９が第１の絞り弁の場合と同一またはこ
れよりも僅かに閉鎖側に設定されたサーボモータ
のある所定の開度の位置で自動時に作動され、サ
ーボモータ５による閉鎖を第２図中曲線２Ｂとほ
とんど等しい曲線３Ｂに沿つて行い、目的とする
急緩２段の閉鎖が支障なく達成される。 Therefore, in the unlikely event that the first switching valve 27 on the water turbine side
If a failure occurs in the first throttle valve 35 and the first throttle valve piston 37 does not operate, the second throttle valve 39 is closed the same as or slightly more than the first throttle valve. The servo motor 5 is automatically operated at a predetermined opening position, and the servo motor 5 closes along the curve 3B, which is almost the same as the curve 2B in FIG. closure is achieved without any hindrance.
このように本実施例においては、主配圧弁１０
からの供油によりガイドベーンを開閉駆動するサ
ーボモータ５と、サーボモータ５の排油側管路を
段階的に絞る第１の絞り弁３５と、サーボモータ
５の所定開度の検知点で第１の絞り弁３５の絞り
段階を切換える第１の切換弁２７とを含むガイド
ベーン急緩閉鎖機構に対して、前記サーボモータ
５の排油管路に設けられ常時は全開位置にある第
２の絞り弁３９と、サーボストロークに関して第
１の切換弁２７より僅かに閉方向の開度で通油状
態に切換わる第２の切換弁２９と第１の絞り弁ピ
ストン３７の位置に応じてこの通油路を開放する
絞り弁切換弁４１とを設けてあるので、第１の絞
り弁の故障時にもサーボモータのほぼ所定開度で
第２の絞り弁が作動してサーボ閉鎖速度を緩速に
切換えることができ、負荷遮断時における鉄管内
の水圧の異常な上昇を遅れなく防止することがで
きる。 In this way, in this embodiment, the main pressure distribution valve 10
a servo motor 5 that drives the guide vane to open and close using oil supplied from the servo motor 5; a first throttle valve 35 that throttles the oil drain side pipe of the servo motor 5 in stages; A second throttle which is provided in the oil drain pipe of the servo motor 5 and which is normally in a fully open position is provided in the guide vane rapid closing mechanism including a first switching valve 27 that switches the throttle stage of the first throttle valve 35. This oil flow is performed according to the positions of the valve 39, the second switching valve 29, which switches to the oil flow state at an opening slightly closer to the closing direction than the first switching valve 27 in terms of the servo stroke, and the first throttle valve piston 37. Since the throttle valve switching valve 41 is provided to open the passage, even if the first throttle valve fails, the second throttle valve operates at approximately the predetermined opening of the servo motor and switches the servo closing speed to a slow speed. This makes it possible to promptly prevent an abnormal increase in water pressure within the iron pipe during load shedding.
尚ここでは水車側の場合について説明したが、
ポンプ側の動作についても全く同様である。 Here, we have explained the case on the water turbine side.
The same applies to the operation on the pump side.
第２の実施例
前記第４の実施例ではサーボモータの確実な急
緩２段閉鎖をサーボ排油管路の絞りによつて行つ
ているが、本発明はこれをサーボ給油管路の絞り
によつても達成することができ、以下かかる実施
例を第５図について説明する。Second Embodiment In the fourth embodiment, the reliable two-stage closing of the servo motor is performed by restricting the servo oil drain pipe, but the present invention achieves this by restricting the servo oil supply pipe. Such an embodiment will be described below with reference to FIG. 5.
第５図の実施例においては、第４図示の第２の
絞り弁３９，４０に代えて主配圧弁プランジヤー
のストロークを調節するためのプランジヤースト
ローク調整弁を設けてサーボモータ給油管路を絞
るようになされている。その他の点の構成は基本
的には第４図の実施例と同様であり、対応する部
分は同一の符号で示してある。 In the embodiment shown in FIG. 5, a plunger stroke adjustment valve for adjusting the stroke of the main pressure distribution valve plunger is provided in place of the second throttle valves 39 and 40 shown in FIG. 4 to throttle the servo motor oil supply pipe. It is done like this. The configuration in other respects is basically the same as the embodiment shown in FIG. 4, and corresponding parts are designated by the same reference numerals.
図示の実施例において遮断時の動作を、たとえ
ば水車側について説明すると、サーボモータ５に
よるベーン閉鎖時に、万一第１の絞り弁３５等が
故障してピストン３７が不動作であると第２の切
換弁２９からの圧油がカム４３の動作で切換弁４
１からプランジヤーストローク調整弁４５に送ら
れ、ピストン４６を作動させて主配圧弁プランジ
ヤー１１のストロークを制御する。これによつて
サーボモータ５の給油管路が絞られ、以降サーボ
モータは緩速閉鎖するので所定の急緩２段閉鎖速
度が得られる。 To explain the operation at the time of shutoff in the illustrated embodiment, for example on the water turbine side, when the vane is closed by the servo motor 5, if the first throttle valve 35 or the like fails and the piston 37 is inoperable, the second throttle valve Pressure oil from the switching valve 29 is transferred to the switching valve 4 by the operation of the cam 43.
1 to the plunger stroke adjustment valve 45, which operates the piston 46 to control the stroke of the main pressure distribution valve plunger 11. As a result, the oil supply pipe of the servo motor 5 is throttled, and since the servo motor is thereafter slowly closed, a predetermined rapid and slow two-stage closing speed can be obtained.
第３の実施例
また本発明においては前記第２切換装置の切換
えの際のサーボモータの所定開度における切換位
置の検知および第１の絞り弁ピストンの不作動検
知を電気的手段によつても行うことができ、かか
る実施例を夫々第６図および第７図について説明
する。Third Embodiment Furthermore, in the present invention, when the second switching device is switched, the detection of the switching position at a predetermined opening of the servo motor and the detection of the non-operation of the first throttle valve piston can be performed by electrical means. Such embodiments are described with respect to FIGS. 6 and 7, respectively.
第６図は前記電気的検知方式を第４図に相当す
るサーボ排油管路中の第２の絞り弁の絞り動作制
御に適用した例を示し、図中、油圧回路および機
械的装置の構成および動作は基本的には第４図に
示すものと同様である。 FIG. 6 shows an example in which the electrical detection method is applied to the throttle operation control of the second throttle valve in the servo oil drain pipe corresponding to FIG. The operation is basically the same as that shown in FIG.
第６図の実施例においては、水車側の第２の絞
り弁３９の絞り動作を制御するために水車側の絞
り操作用の電磁弁５１が設けられており、第８図
に示すようにこの電磁弁５１のソレノイド６０の
励磁回路中にはガイドベーン開度位置開閉器５６
および水車側の第１の絞り弁位置開閉器５８が
夫々直列に接続されている。ここでガイドベーン
開度位置開閉器５６はガイドベーン位置開閉器１
９中の一つの接点であつて水車側の第１の切換弁
２７の切換動作の開度位置と同一のまたは僅かに
閉側寄りの開度位置で閉路するようになされてい
る。また第１の絞り弁位置開閉器５８は水車側の
第１の絞り弁のカム４３と連動する位置開閉器４
９中の一つの接点であつて、水車側の第１の絞り
弁ピストン３７の開位置では閉路し、ピストン３
７の正常絞り動作位置では開路するようになされ
ている。尚、以上の水車側についての構成はポン
プ側についても全く同様であつて、電磁弁５２、
ガイドベーン開度位置開閉器５７、第１の絞り弁
位置開閉器５９、位置開閉器５０等が夫々対応し
てポンプ側に設けられている。その他図中、５４
は急停止用の補助継電器開閉器をまた５５は水車
−ポンプ運転モード切換用の開閉器を示す。 In the embodiment shown in FIG. 6, a solenoid valve 51 for throttle operation on the water turbine side is provided to control the throttle operation of the second throttle valve 39 on the water turbine side, and as shown in FIG. A guide vane opening position switch 56 is provided in the excitation circuit of the solenoid 60 of the solenoid valve 51.
and a first throttle valve position switch 58 on the water turbine side are connected in series. Here, the guide vane position switch 56 is the guide vane position switch 1.
9, and is configured to close at an opening position that is the same as, or slightly closer to, the opening position of the switching operation of the first switching valve 27 on the water turbine side. Further, the first throttle valve position switch 58 is a position switch 4 that is interlocked with the cam 43 of the first throttle valve on the water turbine side.
9, the circuit is closed when the first throttle valve piston 37 on the water turbine side is in the open position, and the piston 3
At the normal throttle operation position 7, the circuit is opened. Incidentally, the above configuration on the water turbine side is exactly the same on the pump side, and the solenoid valve 52,
A guide vane opening position switch 57, a first throttle valve position switch 59, a position switch 50, etc. are respectively provided on the pump side. Others in the figure, 54
55 indicates an auxiliary relay switch for sudden stop, and 55 indicates a switch for switching between water turbine and pump operation modes.
したがつて、たとえば水車側の負荷遮断時に、
水車側の第１の絞り弁３５等が正常であれば位置
開閉器４９の接点５８が閉路せず、電磁弁５１の
ソレノイド６０が消磁状態にあるので第２の絞り
弁３９は動作しない。ここで万一第１の絞り弁３
５等が故障してピストン３７が作動しないと前記
接点５８がソレノイド６０の励磁回路を閉成して
電磁弁５１を通油状態に切換え圧油５３を供給
し、第２の絞り弁３９を絞り位置に作動させ、こ
れによつて急緩２段速度閉鎖を支障なく達成す
る。この動作はポンプ側についても全く同様であ
る。 Therefore, for example, when the load is cut off on the water turbine side,
If the first throttle valve 35 on the water turbine side is normal, the contact 58 of the position switch 49 will not close, and the solenoid 60 of the electromagnetic valve 51 will be in a demagnetized state, so the second throttle valve 39 will not operate. Here, in case the first throttle valve 3
5 or the like fails and the piston 37 does not operate, the contact 58 closes the excitation circuit of the solenoid 60, switches the solenoid valve 51 to the oil-through state, supplies the pressure oil 53, and throttles the second throttle valve 39. position, thereby achieving rapid and slow two-speed closure without difficulty. This operation is exactly the same on the pump side.
第４の実施例
前記第６図の電気的切換制御方式は主配圧弁の
プランジヤーストローク調節によりサーボ給油管
路の絞りを制御する第５図に相当する装置にも適
用することができる。第７図はこのような場合に
おける本発明の別の実施例を示す。この実施例で
は急速停止の際の二重絞り装置として第４図の排
油管路中の第２の絞り弁に代えて第５図の給油管
路を調節する主配圧弁のプランジヤーストローク
調節弁が用いられており、このプランジヤースト
ローク調節弁を前記第６図の各電磁弁の電気的な
開閉動作によつて制御するようになされている。
したがつて本実施例においても、水車およびポン
プの急速停止における急緩２段速度閉鎖方式を確
実に達成することができる。Fourth Embodiment The electrical switching control system shown in FIG. 6 can also be applied to the device shown in FIG. 5, which controls the throttle of the servo oil supply pipe by adjusting the plunger stroke of the main pressure distribution valve. FIG. 7 shows another embodiment of the invention for such a case. In this embodiment, the plunger stroke control valve of the main pressure distribution valve that regulates the oil supply pipe shown in Fig. 5 replaces the second throttle valve in the oil drain pipe shown in Fig. 4 as a double throttling device in the case of a rapid stop. is used, and this plunger stroke control valve is controlled by the electrical opening and closing operations of the electromagnetic valves shown in FIG. 6.
Therefore, in this embodiment as well, it is possible to reliably achieve the two-stage rapid-relaxation speed closing system in the rapid stop of the water turbine and pump.
以上本発明をポンプ水車の実施例について説明
したが、本発明はその他一般の回転水力機械の急
停止の際の保護装置に広く適用することができ
る。 Although the present invention has been described above with reference to an embodiment of a pump-turbine, the present invention can be widely applied to other general rotary hydraulic machines that protect against sudden stops.
叙上のように本発明によれば、水力機械の急停
止の際のガイドベーンの急緩２段速度閉鎖方式を
確実に達成することができ、閉鎖制御装置の故障
の際の水圧鉄管内の異常昇圧による事故を適確に
防止することができる。
As described above, according to the present invention, it is possible to reliably achieve a two-stage speed closing system of guide vanes that rapidly loosens and slows down when a hydraulic machine suddenly stops, and to prevent damage to the penstock in the event of a failure of the closure control device. Accidents caused by abnormal pressure increase can be accurately prevented.
第１図および第２図はサーボモータの動作特性
線図を示し、第１図は従来技術による線図を第２
図は本発明による線図を示す。第３図は従来技術
におけるサーボモータの急緩閉鎖速度切換用切換
装置を含む線図的説明図を示す。第４図、第５
図、第６図および第７図は本発明の水力機械の保
護装置を説明する４つの具体例の線図的説明図を
示し、第８図は第６図および第７図に示す具体例
の電気回路図を示す。
５……サーボモータ、６，７……給油管路、
８，９……排油管路、１０……主配圧弁、２７，
２９……水車側の第１、第２切換弁、３１，３３
……ポンプ側の第１、第２切換弁、３５，３９…
…水車側の第１、第２絞り弁、３６，４０……ポ
ンプ側の第１、第２絞り弁、４１，４２……絞り
弁切換弁（水車・ポンプ側）、４５，４７……主
配圧弁プランジヤーストローク調整弁（水車・ポ
ンプ側）、５１，５２……第２絞り弁用電磁弁
（水車・ポンプ側）。
Figures 1 and 2 show operating characteristic diagrams of the servo motor, and Figure 1 shows the diagram according to the prior art.
The figure shows a diagram according to the invention. FIG. 3 shows a diagrammatic explanatory diagram including a switching device for switching between quick and slow closing speeds of a servo motor in the prior art. Figures 4 and 5
6 and 7 show diagrammatic illustrations of four specific examples of the protection device for hydraulic machinery of the present invention, and FIG. 8 shows the specific examples shown in FIGS. 6 and 7. Shows an electrical circuit diagram. 5... Servo motor, 6, 7... Oil supply pipe,
8, 9...Drainage pipe line, 10...Main pressure distribution valve, 27,
29...First and second switching valves on the water turbine side, 31, 33
...First and second switching valves on the pump side, 35, 39...
...first and second throttle valves on the water turbine side, 36, 40...first and second throttle valves on the pump side, 41, 42...throttle valve switching valve (water turbine/pump side), 45, 47...main Pressure distribution valve plunger stroke adjustment valve (water turbine/pump side), 51, 52... Solenoid valve for second throttle valve (water turbine/pump side).
Claims (1)
ボモータと、水力機械の回転速度の変化に応動し
て上記サーボモータに圧油を給排する主配圧弁
と、ガイドベーン閉鎖時におけるサーボモータの
圧油の給排管路の流路を段階的に絞り、所定の急
閉鎖速度およびこれに引きつづいて所定の緩閉鎖
速度でサーボモータを段階的に閉じることの出来
る第１の絞り装置と、サーボモータの全ストロー
クの途中に設定された閉鎖速度切換点でサーボモ
ータに緩閉鎖速度を与えるように前記第１の絞り
弁を切換える第１の切換装置とを備えた水力機械
の保護装置において、 正常運転時は前記給排管路を全開する位置にあ
る第２の絞り装置と、 前記第１の絞り装置の故障を前記サーボモータ
の動作位置と前記第１の絞り装置のピストンの動
きとを直接的に検出して前記第２の絞り装置を前
記給排管路の流路絞り位置に切換えてサーボモー
タに前記所定の緩閉鎖速度を与えるように作用す
る第２の切換装置とを有することを特徴とする前
記水力機械の保護装置。[Claims] 1. A servo motor that opens and closes a guide vane of a hydraulic machine, a main pressure distribution valve that supplies and discharges pressure oil to the servo motor in response to changes in the rotational speed of the hydraulic machine, and when the guide vane is closed. A first method that can step-by-step narrow the flow path of the pressure oil supply and discharge pipe of the servo motor and close the servo motor step-by-step at a predetermined rapid closing speed and subsequently at a predetermined slow closing speed. A hydraulic machine comprising a throttle device and a first switching device that switches the first throttle valve to provide a slow closing speed to the servo motor at a closing speed switching point set in the middle of a full stroke of the servo motor. In the protection device, a second throttle device is located at a position where the supply/discharge pipe is fully opened during normal operation, and a failure of the first throttle device is detected by adjusting the operating position of the servo motor and the piston of the first throttle device. and a second switching device that directly detects the movement of the valve and switches the second throttle device to a flow path throttle position of the supply/discharge pipe to give the servo motor the predetermined slow closing speed. The protection device for the hydraulic machine, characterized in that it has the following.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15916679A JPS5683575A (en) | 1979-12-10 | 1979-12-10 | Protective system for hydraulic machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15916679A JPS5683575A (en) | 1979-12-10 | 1979-12-10 | Protective system for hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5683575A JPS5683575A (en) | 1981-07-08 |
| JPS621108B2 true JPS621108B2 (en) | 1987-01-12 |
Family
ID=15687709
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15916679A Granted JPS5683575A (en) | 1979-12-10 | 1979-12-10 | Protective system for hydraulic machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5683575A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60240880A (en) * | 1984-05-14 | 1985-11-29 | Hitachi Ltd | Control of movable vane turbine |
| JP2787694B2 (en) * | 1989-01-19 | 1998-08-20 | カシオ計算機株式会社 | Panning control device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS53105642A (en) * | 1977-02-26 | 1978-09-13 | Toshiba Corp | Safeguard for hydraulic machinery |
-
1979
- 1979-12-10 JP JP15916679A patent/JPS5683575A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS53105642A (en) * | 1977-02-26 | 1978-09-13 | Toshiba Corp | Safeguard for hydraulic machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5683575A (en) | 1981-07-08 |
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