JPS62210204A - High speed valve controller for turbine - Google Patents
High speed valve controller for turbineInfo
- Publication number
- JPS62210204A JPS62210204A JP5083186A JP5083186A JPS62210204A JP S62210204 A JPS62210204 A JP S62210204A JP 5083186 A JP5083186 A JP 5083186A JP 5083186 A JP5083186 A JP 5083186A JP S62210204 A JPS62210204 A JP S62210204A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- generator
- output
- intercept
- valves
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 8
- 238000010248 power generation Methods 0.000 claims 1
- 238000011084 recovery Methods 0.000 abstract description 2
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 230000002123 temporal effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000001514 detection method Methods 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 239000010902 straw Substances 0.000 description 1
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、蒸気タービンの出力を高速に制御するター
ビン高速バルブ制御装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a turbine high-speed valve control device that controls the output of a steam turbine at high speed.
従来この種の装置としては第4図に示すものがあつt。 A conventional device of this type is shown in FIG. 4.
図において1は高圧タービン、2はその高圧タービン1
を通過し之蒸気を再加熱するための再熱器、3Aは低圧
第一段タービ/、3Bは低圧第二段タービン、4はター
ビンの回転エネルギーを電気エネルギーに変換するtめ
の発電機、5は上述のタービ/と発電機4を一体に軸結
合した回転軸、6は高圧タービン1に供給される蒸気流
量を調節するための加減弁%7Aは低圧藁一段タービ/
3Aに供給される再熱器2からの再熱蒸気の流量を調節
する几めのインターセプ)17Bは低圧第二段タービン
3Bに供給される再熱器2からの再熱蒸気の流量を調節
するためのインタセプト弁、8は発電機4の出力が接続
される送電系統に発生した事故を検知してインタセプト
弁7Aおよび7Bの開度を速やかに制御する九めのター
ビン高速パルプ制御回路である。In the figure, 1 is a high-pressure turbine, 2 is the high-pressure turbine 1
3A is a low-pressure first-stage turbine, 3B is a low-pressure second-stage turbine, 4 is a t-th generator that converts the rotational energy of the turbine into electrical energy, Reference numeral 5 denotes a rotary shaft to which the above-mentioned turbine/generator 4 is integrally connected, and 6 is a control valve for adjusting the flow rate of steam supplied to the high-pressure turbine 1. 7A is a low-pressure straw one-stage turbine/
17B adjusts the flow rate of reheated steam from the reheater 2 supplied to the low-pressure second stage turbine 3B. The intercept valve 8 is a ninth turbine high-speed pulp control circuit that detects an accident occurring in the power transmission system to which the output of the generator 4 is connected and promptly controls the opening of the intercept valves 7A and 7B.
次に第4図に示した従来装置の動作について説明する。Next, the operation of the conventional device shown in FIG. 4 will be explained.
発′電機4の発電出力を他の系統に接続する図示しない
被接続送電線に事故が発生すると、その事故を検知して
タービン高速パルプ制御回路8が動作し、インターセプ
ト弁7Aおよび7Bに開閉指令を出力する。この結果、
インターセプト弁7Aおよび7Bの開度は第5図の如く
変化する。When an accident occurs in a connected transmission line (not shown) that connects the generated output of the generator 4 to other systems, the accident is detected and the turbine high-speed pulp control circuit 8 is activated, commanding the intercept valves 7A and 7B to open and close. Output. As a result,
The opening degrees of intercept valves 7A and 7B change as shown in FIG.
図においてtlは事故検出遅れなどを含む開成不動時間
、t2は全閉時間、t、は弁を開き始めるまでに要する
開放不動時間、tllは全開時間である。ここで前記夫
々の時間11,12,1.はタービン高速パルプ制御装
置の応答特性を考慮したうえで可能な限り短い時間に設
定される。このようにして一旦、全閉されたインターセ
プト弁7は、あらかじめ決められた時間t4で開放され
て、全開位置に戻る。In the figure, tl is the opening/immobility time including accident detection delay, t2 is the fully closing time, t is the opening/immobility time required until the valve starts to open, and tll is the full opening time. Here, the respective times 11, 12, 1. is set to the shortest possible time in consideration of the response characteristics of the turbine high-speed pulp control device. The intercept valve 7, which is once fully closed in this manner, is opened at a predetermined time t4 and returns to the fully open position.
第6図はタービン高速パルプ制御時のタービン出力の経
時的変化(曲線T)1発電機4の出力の経時的変化(曲
、WG)および再熱器2内部の蒸気圧力の経時的変化(
曲線V)を示した図である。Figure 6 shows the temporal change in turbine output (curve T) during turbine high-speed pulp control, the temporal change in the output of the generator 4 (curve, WG), and the temporal change in the steam pressure inside the reheater 2 (curve T).
It is a figure showing curve V).
すなわちインターセプト弁7Aおよび7Bを急閉するこ
とによフ低圧タービン3Aおよび3Bに供給される再熱
器2の蒸気流量が急激に減少するためタービン出力つf
り高圧タービン1の出力と低圧タービンγAおよび7B
の出力を加えた値は曲線Tで示したように急激に減少す
ると同時に、曲線Vで示し念ように再熱器2の内部の蒸
気圧力が急激に上昇する。これと同時に、発電機4の出
力もタービン出力の変化に追従する形で曲ilTで示し
たタービン出力を中心にして曲線Gで示したように大き
く撮動する。That is, by rapidly closing the intercept valves 7A and 7B, the flow rate of steam from the reheater 2 supplied to the low-pressure turbines 3A and 3B decreases rapidly, so that the turbine output and f
The output of high pressure turbine 1 and low pressure turbines γA and 7B
As shown by curve T, the sum of the outputs of 1 and 2 rapidly decreases, and at the same time, as shown by curve V, the steam pressure inside the reheater 2 rapidly increases. At the same time, the output of the generator 4 is also greatly captured as shown by curve G, centering on the turbine output shown by curve ilT, in a manner that follows the change in turbine output.
従来のタービン高速パルプ制御装置は以上のように構成
されているので、送電線事故等が原因でタービン高速パ
ルプ制御回路8が作動し、インターセプト弁7Aおよび
7Bが急閉すると再熱器2内部の蒸気圧力の上昇が大変
大きくなって安全弁が動作し几り、再熱器2そのものの
耐圧補強をすることが必要となる。また、再熱器2内部
の蒸気圧力の上昇を抑えようとしてインターセプト弁7
Aおよび7Bの全開時間を早くしすぎると、その開放制
御の途中において発電機4の同期が保てなくなって脱調
する問題点があり、更に1発電機4の出力の変化が大き
くて非常に大きな動揺を電力系統に与えるなどの問題点
があった。Since the conventional turbine high-speed pulp control device is configured as described above, when the turbine high-speed pulp control circuit 8 is activated due to a power transmission line accident, etc., and the intercept valves 7A and 7B are suddenly closed, the inside of the reheater 2 is The rise in steam pressure becomes so great that the safety valve operates and the reheater 2 itself needs to be reinforced with pressure resistance. In addition, in an attempt to suppress the rise in steam pressure inside the reheater 2, the intercept valve 7
If the full opening time of A and 7B is made too early, there is a problem that the synchronization of the generator 4 cannot be maintained in the middle of the opening control, resulting in a loss of synchronization.Furthermore, the change in the output of the first generator 4 is large, resulting in a very There were problems such as large disturbances being caused to the power system.
この発明は上記のような問題点を解消する念めになされ
たもので、再熱器内の蒸気圧力の上昇を抑制し、インタ
ーセプト弁開放過程における発電機の税調を防止できる
とともに1発電機の出力の変化を小さくして電力系統の
動揺を小さくできるタービン高速パルプ制御装置を得る
ことを目的とする。This invention was made with the aim of solving the above-mentioned problems, and it is possible to suppress the rise in steam pressure in the reheater, prevent tax adjustment of the generator during the process of opening the intercept valve, and reduce the burden on one generator. The object of the present invention is to obtain a turbine high-speed pulp control device that can reduce fluctuations in a power system by reducing changes in output.
この発明に係るタービン高速パルプ制御装置は、複数個
あるインターセプト弁を複数のグループに別け、各グル
ープ別にインターセプト弁を開閉制御する夫々のタービ
ン高速パルプ制御回路を備えるようにしたものである。The turbine high-speed pulp control device according to the present invention divides a plurality of intercept valves into a plurality of groups, and includes a turbine high-speed pulp control circuit for controlling opening and closing of the intercept valves for each group.
この発明におけるタービン高速パルプ制御装置は、各タ
ービン高速パルプ制御回路によりインターセプト弁のグ
ループ別にインターセプト弁を閉じ始める時間、開は始
める時間および開ける速度に差を設けることにより再熱
蒸気のエネルギーを利用して回転する低圧タービンの出
力を調節する。The turbine high-speed pulp control device according to the present invention utilizes the energy of reheated steam by setting differences in the time at which intercept valves begin to close, the time at which they begin to open, and the opening speed for each group of intercept valves by each turbine high-speed pulp control circuit. to adjust the output of the rotating low-pressure turbine.
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.
図中、第4図と同一の部分は同一の符号をもって図示し
た第1図において、8Aは発電機4が接続される送電系
統に発生した事故を検知して低圧タービン3Aに再熱蒸
気を供給するインターセプト弁7Aの開度を速やかに制
御するtめの第1のタービン高速パルプ制御回路、8B
は発電機4が接続される送電系統に発生し几事故を検知
して低圧タービy3Bに再熱蒸気を供給するインターセ
プト弁7Bの開度を速やかに制御する念めの第2のター
ビン高速パルプ制御回路である。In FIG. 1, the same parts as in FIG. 4 have the same symbols. In FIG. 1, 8A detects an accident that has occurred in the power transmission system to which the generator 4 is connected and supplies reheated steam to the low-pressure turbine 3A. t-th first turbine high-speed pulp control circuit 8B that promptly controls the opening degree of the intercept valve 7A;
is a second turbine high-speed pulp control that detects a failure that occurs in the power transmission system to which the generator 4 is connected and promptly controls the opening degree of the intercept valve 7B that supplies reheated steam to the low-pressure turbine Y3B. It is a circuit.
次に動作について説明する。発電機4が接続されている
図示しない送電系統に事故が発生すると、その事故を検
知して第1および第2のタービ/高速パルプ制御回路8
A、8Bが動作し、インターセプト弁7A、7Bに開閉
指令を各々出力する。Next, the operation will be explained. When an accident occurs in the power transmission system (not shown) to which the generator 4 is connected, the accident is detected and the first and second turbine/high-speed pulp control circuits 8
A and 8B operate and output opening/closing commands to intercept valves 7A and 7B, respectively.
この結果、インターセプト弁7Aの開度は第2図(a)
の如く変化する。同図においてtIAは事故検出遅れな
どを含む閉成不動時間、t2Aは全閉時間。As a result, the opening degree of the intercept valve 7A is as shown in Fig. 2(a).
It changes like this. In the figure, tIA is the closing immobility time including the delay in detecting an accident, and t2A is the fully closing time.
t、Aは弁を開き始めるまでに要する開放不動時間、t
4Aは全開時間である。ここ前記夫々の時間tIA。t, A is the opening immobility time required until the valve starts to open, t
4A is the full opening time. Here the respective times tIA.
t2A+tLAはタービン高速パルプ制御装置の応答特
性を考慮したうえで可能な限り短い時間に設定さnる。t2A+tLA is set to the shortest possible time in consideration of the response characteristics of the turbine high speed pulp control device.
このようにして一旦、全閉されたインターセプト弁7A
は、あらかじめ決められた時間t、Aで開放さ几て、全
開位置に戻る。In this way, the intercept valve 7A is once fully closed.
is opened at a predetermined time t, A, and returns to the fully open position.
cnと同時に、インターセプト弁7Bの開度は第2図(
b)の実線の如く変化する。同図においてtlBは事故
検出遅れなどを含む閉成不動時間、 t2Bは全閉時間
、 t、Bは弁を開き始めるまでに要する開放不動時
間、 t、Bは全開時間である。ここで前記夫々の時
間t2B、t、Bはタービン高速パルプ制御装置の応答
特性を考慮したうえで可能な限シ短い時間に設定さ几る
7、このようにして一旦、全閉されたインターセプト弁
7Bは、あらかじめ決めら几た時間tuBで開放されて
、全開位置に戻る。At the same time as cn, the opening degree of intercept valve 7B is changed as shown in Fig. 2 (
It changes as shown by the solid line in b). In the figure, tlB is the closing immobility time including accident detection delay, t2B is the fully closing time, t and B are the opening immobility time required until the valve starts to open, and t and B are the full opening time. Here, each of the above-mentioned times t2B, t, and B are set to the shortest possible time in consideration of the response characteristics of the turbine high-speed pulp control device.7 In this way, once the intercept valve is fully closed, 7B is released at a predetermined time tuB and returns to the fully open position.
なお1図中、閉路開始時間となる時間txBは同じく時
間t1Aよりある一定時間遅れた時間に、全開時間t1
1Bは全開時間tlIAより長い時間に設定されている
。第2図缶)における一点鎖線は第2図(a)のインタ
ーセプト弁7Aの開度曲線を比較上示し念ものである。In addition, in Figure 1, time txB, which is the closing start time, is a certain period of time later than time t1A, and full-open time t1
1B is set to be longer than the full open time tlIA. The one-dot chain line in FIG. 2(a) is a comparative illustration of the opening degree curve of the intercept valve 7A in FIG. 2(a).
第3図(a)および同図ら)はこの発明によるタービン
高速パルプ制御時のタービン出力の経時的変化(曲線T
)、発電機4の出力の経時的変化(曲線G)および再熱
器2の内部の蒸気圧力の経時的変化(曲線V)を示した
図である。すなわち、インターセプト弁7Aを急閉する
ことにより低圧g 一段タービン3Aに供給される蒸気
流量が急激に減少する之めタービン出力つまり高圧ター
ビン1の出力と、低圧第一段タービン3Aの出力と、低
圧第二段タービン3Bの出力を合計した値は曲線Tで示
し九ように若干急激に減少する。いったん全閉されたイ
ンターセプト弁7Aを開き始めてから。Figures 3(a) and 3(a) and 3(a) and 3(a) and 4(a) and 3(a) and 3(a) and 4(a) and 3(a) and 4(b), respectively) show the temporal change in turbine output (curve T) during turbine high-speed pulp control according to the present invention.
) is a diagram showing a temporal change in the output of the generator 4 (curve G) and a temporal change in the steam pressure inside the reheater 2 (curve V). That is, by quickly closing the intercept valve 7A, the low pressure g, the steam flow rate supplied to the first stage turbine 3A is rapidly reduced, and the turbine output, that is, the output of the high pressure turbine 1, the output of the low pressure first stage turbine 3A, and the low pressure The total output of the second stage turbine 3B is shown by curve T and decreases somewhat rapidly as shown in FIG. After starting to open intercept valve 7A, which was once fully closed.
続いてインターセプト弁7Bを急閉後、比較的ゆっくり
し九時間t4Bで全開に戻す。第2図缶)の両曲線の比
較で明白なように、インターセプト弁7Aと同7Bとが
全閉になる時間をずらし九ので曲線Tで示したこの発明
におけるタービン出力の減少幅は従来技術のそれに比較
して充分に小さい。曲線Vで示したように再熱器2の内
部の蒸気圧力は。Subsequently, the intercept valve 7B is quickly closed, and then returned to the fully open position relatively slowly at 9 hours t4B. As is clear from the comparison of both curves in Fig. 2 (Fig. 2), since the times at which the intercept valves 7A and 7B are fully closed are shifted, the amount of decrease in turbine output in this invention shown by curve T is less than that in the prior art. It's quite small in comparison. As shown by curve V, the steam pressure inside the reheater 2 is:
その出口管路の閉路する時間をずらしたので余り急激に
上昇せず、しかもその上昇量も小さい。この時1発電機
4の出力も曲線Tで示したタービン出力の変化に追従す
る形で、タービン出力を中心にして曲線Gで示したよう
に従来装置より比較的に振幅を小さくして振動する。Since the closing time of the outlet pipe is shifted, the rise does not occur too rapidly, and the amount of rise is also small. At this time, the output of the first generator 4 also follows the change in the turbine output shown by the curve T, and vibrates with a relatively smaller amplitude than the conventional device as shown by the curve G around the turbine output. .
なお、上記実施例では複数個あるインターセプト弁を2
つのグループに分けて2つのタービン高速パルプ制御回
路からの出力信号により制御し念ものを示したが、3つ
以上のインターセプト弁を3つ以上のグループに分けて
3つ以上のタービン高速パルプ制御回路からの出力信号
により再熱器の出口管路の閉路する時間を互いにずらせ
るように制御してもよい。In addition, in the above embodiment, there are two or more intercept valves.
In this example, three or more intercept valves are divided into three or more groups and controlled by output signals from two turbine high-speed pulp control circuits. The closing times of the outlet pipes of the reheater may be controlled to be staggered from each other by output signals from the reheater.
以上のように、この発明によれば複数個あるインターセ
プト弁を複数のグループに分け、各々の開閉時間をずら
して開閉制御するように構成し念ので、再熱器内部の蒸
気圧力の上昇を抑えて安全弁が作動するのを防止し、再
熱器などの耐圧設計を必要以上に高めることもなくなり
1発電機の出力変動を小さくして過大な動揺を電力系統
に与えることを防止でき、タービン出力の回復途中にお
いて発電機の同期が保てなくなって同調することを防止
できるものが得られる効果がある。As described above, according to the present invention, a plurality of intercept valves are divided into a plurality of groups, and the opening and closing times of each are staggered to control the opening and closing, thereby suppressing the rise in steam pressure inside the reheater. This prevents the safety valve from operating, and eliminates the need to unnecessarily increase the pressure-resistant design of reheaters, etc.1.It reduces the output fluctuations of the generator and prevents excessive oscillations from being applied to the power system, reducing the turbine output. This has the effect of preventing the generator from losing synchronization and synchronizing during recovery.
第1図はこの発明の一実施例によるタービン高速パルプ
制御装置を示すブロック構成図、@2図(a)および同
図(b)はこの発明の一実施例におけるインターセプト
弁の開閉動作を示す特性図、第3図(a)および同図缶
ンはこの発明の一実施例により制御されたときのタービ
ン出力、発電機出力および再熱器の蒸気圧力の経時的変
化を各々示す特性図、第4図は従来のタービン高速パル
プ制御装置を示すブロック構成図、第5図は従来の装置
lKおけるインターセプト弁の動作を示す特性図、第6
図(a)および同図ら)は従来の装置により制御された
ときのタービン出力2見電機出力および再熱器の蒸気圧
力の経時的変化を各々示す特性図である。
図において、1は高圧タービン、2は再熱器、3A、3
Bは低圧タービン、4は発電機、7A。
7Bはインターセプト弁、8A、8Bはタービン高速バ
ルブ制御回路。
なお1図中、同一符号は同一、又は相当部分を示す。Figure 1 is a block configuration diagram showing a turbine high-speed pulp control device according to an embodiment of the present invention, and Figures 2 (a) and 2 (b) are characteristics showing the opening/closing operation of an intercept valve in an embodiment of the present invention. 3(a) and 3(a) are characteristic diagrams showing the temporal changes in turbine output, generator output, and reheater steam pressure when controlled by an embodiment of the present invention, respectively. Fig. 4 is a block configuration diagram showing a conventional turbine high-speed pulp control device, Fig. 5 is a characteristic diagram showing the operation of the intercept valve in the conventional device IK, and Fig. 6
Figures (a) and 3(a) are characteristic diagrams showing temporal changes in turbine output, electrical output, and reheater steam pressure, respectively, when controlled by a conventional device. In the figure, 1 is a high-pressure turbine, 2 is a reheater, 3A, 3
B is a low pressure turbine, 4 is a generator, 7A. 7B is an intercept valve, and 8A and 8B are turbine high-speed valve control circuits. In addition, in FIG. 1, the same reference numerals indicate the same or equivalent parts.
Claims (1)
発生を検知してインターセプト弁を全閉し、然る後に全
開に制御するタービン高速バルブ制御装置において、複
数個ある前記インターセプト弁を複数のグループに分け
、前記各々のグループに相互に異なつた閉路開始時間お
よび全開時間を与える各開閉制御信号を各々出力する各
タービン高速バルブ制御回路を備えたことを特徴とする
タービン高速バルブ制御装置。In a turbine high-speed valve control device that detects the occurrence of an accident in a power transmission line connected to the power generation output of a steam turbine generator, fully closes an intercept valve, and then controls the intercept valve to fully open, the plurality of intercept valves are connected to a plurality of groups. A turbine high-speed valve control device comprising: a turbine high-speed valve control circuit which outputs respective opening/closing control signals for giving mutually different closing start times and full-open times to the respective groups.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5083186A JPH0676765B2 (en) | 1986-03-07 | 1986-03-07 | Turbin high speed valve controller |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5083186A JPH0676765B2 (en) | 1986-03-07 | 1986-03-07 | Turbin high speed valve controller |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS62210204A true JPS62210204A (en) | 1987-09-16 |
JPH0676765B2 JPH0676765B2 (en) | 1994-09-28 |
Family
ID=12869703
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP5083186A Expired - Lifetime JPH0676765B2 (en) | 1986-03-07 | 1986-03-07 | Turbin high speed valve controller |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0676765B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019163438A1 (en) | 2018-02-21 | 2019-08-29 | 株式会社東芝 | Control device for steam governing valve of power generation plant, and method for controlling steam governing valve of power generation plant |
-
1986
- 1986-03-07 JP JP5083186A patent/JPH0676765B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019163438A1 (en) | 2018-02-21 | 2019-08-29 | 株式会社東芝 | Control device for steam governing valve of power generation plant, and method for controlling steam governing valve of power generation plant |
Also Published As
Publication number | Publication date |
---|---|
JPH0676765B2 (en) | 1994-09-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0236959B1 (en) | Method for starting thermal power plant | |
US4819435A (en) | Method for reducing valve loops for improving stream turbine efficiency | |
JPS62210204A (en) | High speed valve controller for turbine | |
US5191764A (en) | Governor valve positioning to overcome partial-arc admission limits | |
Patel, TS Bhatti, DP Kothari | Improvement of power system transient stability using fast valving: A review | |
US3511051A (en) | Speed governing systems for steam turbines | |
JPS62210203A (en) | High sped valve controller for turbine | |
CN215633162U (en) | Frequency modulation control system for intermediate reheating unit of thermal generator set | |
JP3026049B2 (en) | Turbine control device | |
JPS6242126B2 (en) | ||
JPH0467001B2 (en) | ||
JPS6242124B2 (en) | ||
JPS60156908A (en) | Turbine high-speed valve controller | |
JP2620124B2 (en) | Bleed turbine control method and apparatus | |
JPH0577841B2 (en) | ||
JPS58211505A (en) | High speed valve control system | |
JPH06146806A (en) | Opening controller for electro-hydraulic control valve | |
CA1163814A (en) | Method of varying turbine output of a supercritical- pressure steam generator-turbine installation | |
JPS60198310A (en) | Controller for turbine | |
JP2523493B2 (en) | Turbin bypass system | |
JPS60138209A (en) | Bearing feed oil temperature control device | |
JPS6212361B2 (en) | ||
JPS6039843B2 (en) | steam turbine control device | |
JPS6291605A (en) | Steam turbine control device | |
JPH0128202B2 (en) |