JPH0536601B2 - - Google Patents
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- Publication number
- JPH0536601B2 JPH0536601B2 JP59183643A JP18364384A JPH0536601B2 JP H0536601 B2 JPH0536601 B2 JP H0536601B2 JP 59183643 A JP59183643 A JP 59183643A JP 18364384 A JP18364384 A JP 18364384A JP H0536601 B2 JPH0536601 B2 JP H0536601B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- cam
- control
- opening method
- controlled
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、蒸気タービンの加減弁制御装置に係
り、特に起動時の熱応力を低減し、起動時間を短
縮するとともに、通常運転時には高率運転が可能
な加減弁制御装置に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a control valve control device for a steam turbine, and in particular reduces thermal stress at startup, shortens startup time, and maintains high efficiency during normal operation. The present invention relates to a control valve control device that can be operated.
第１図は蒸気タービンの蒸気入口部の概念を示
し、第２図はノズルと動翼と静翼の回りの一部分
を拡大して示す。
FIG. 1 shows the concept of the steam inlet of a steam turbine, and FIG. 2 shows an enlarged view of a portion around the nozzle, rotor blades, and stationary blades.
これらの図において、蒸気は加減弁１ａ〜１ｄ
により流量を制御されながら、ノズルボツクス２
に入り、ノズル３で膨張し、動翼４に衝突するこ
とにより仕事をする。なお、第２図中、５は静翼
である。 In these figures, steam flows through control valves 1a to 1d.
while the flow rate is controlled by the nozzle box 2.
It enters the air, expands in the nozzle 3, and does work by colliding with the moving blade 4. In addition, in FIG. 2, 5 is a stationary blade.
第３図は、従来の加減弁制御装置を示す。 FIG. 3 shows a conventional control valve control device.
加減弁１を作動させたい時、すなわち蒸気ター
ビンの負荷を変化させたい時は、要求負荷に見合
つた制御油をリレー弁６に送り、ラツク７を押し
上げ、ピニオン８を回す。これにより、カム軸９
が回転し、カム１０を回す。カム１０が回転する
と、カムフオロア１１を介してレバー１２を動か
し、パイロツト弁１３を引き上げる。これに伴
い、圧油がサーボモータ１４に供給され、加減弁
１が開き、蒸気量が増加する。 When it is desired to operate the control valve 1, that is, when it is desired to change the load on the steam turbine, control oil corresponding to the required load is sent to the relay valve 6, the rack 7 is pushed up, and the pinion 8 is turned. As a result, the camshaft 9
rotates, turning the cam 10. When the cam 10 rotates, it moves the lever 12 via the cam follower 11 and pulls up the pilot valve 13. Along with this, pressure oil is supplied to the servo motor 14, the control valve 1 opens, and the amount of steam increases.
第４図Ａ，Ｂは４個の加減弁を持つた蒸気ター
ビンの加減弁開方式の例を示す。 FIGS. 4A and 4B show an example of a control valve opening method for a steam turbine having four control valves.
その第４図Ａは、加減弁を順番に開く方式で順
次開方式と呼ばれている。 The method shown in FIG. 4A is a method in which the control valves are opened in sequence, and is called a sequential opening method.
第４図Ｂは、第１、第２の加減弁を同時に開く
方式で、１、２弁同時開方式と呼ばれている。 FIG. 4B shows a method in which the first and second control valves are opened simultaneously, which is called a 1- and 2-valve simultaneous opening method.
第５図は、加減弁の開方式の相違による第１段
後の蒸気温度変化を示す図であつて、順次開方式
の場合はＡで、１、２弁同時開方式の場合はＢで
示している。 FIG. 5 is a diagram showing the change in steam temperature after the first stage due to differences in the opening method of the control valves, with A in the case of the sequential opening method and B in the case of the simultaneous opening method of 1 and 2 valves. ing.
負荷が０〜100％に変化する時、第１段後の蒸
気温度の変化は順次開方式Ａの場合にはT1、１、
２弁同時開方式の場合はT2となる。したがつて、
順次開方式の方が温度変化幅が大きい。このこと
は、熱応力が大きく発生することを意味し、起動
時間を１、２弁同時開方式よりゆつくりさせる必
要があることを示している。 When the load changes from 0 to 100%, the change in steam temperature after the first stage is T 1 , 1,
In the case of a two-valve simultaneous opening method, it is T 2 . Therefore,
The sequential opening method has a larger range of temperature changes. This means that a large amount of thermal stress is generated, and it is necessary to make the start-up time slower than the one- and two-valve simultaneous opening system.
第６図は、加減弁開方式の相違によるタービン
効率の変化を示す図であつて、この図において
も、順次開方式の場合はＡで、１、２弁同時開方
式の場合はＢで示している。１、２弁同時開方式
は、順次開方式に比べて、低負荷領域で効率が低
下する。 FIG. 6 is a diagram showing changes in turbine efficiency due to differences in control valve opening methods. In this figure as well, the sequential opening method is indicated by A, and the simultaneous opening method of 1 and 2 valves is indicated by B. ing. The simultaneous opening method of one and two valves is less efficient in the low load region than the sequential opening method.
以上に述べたごとく、順次開方式は高い効率が
得られるものの、熱応力が高くなる。逆に、１、
２弁同時開方式は低負荷領域での効率は低下する
ものの、熱応力が低いので、急速起動に効果のあ
る方式となつている。蒸気タービンの設計、製作
に当たつて、どちらを選ぶかは運用目的により決
定されている。方式が決定されると、それに従
い、カム形状が決まる。旧来技術では、一度カム
形状が決定されると、別の方式により運転しよう
とすればカムを交換しなければならない。そのた
めには、プラントの停止を必要とする。 As described above, although the sequential opening method provides high efficiency, it also causes high thermal stress. On the contrary, 1,
Although the two-valve simultaneous opening method has lower efficiency in low load regions, it is effective for rapid startup because thermal stress is low. When designing and manufacturing a steam turbine, the choice is determined by the operational purpose. Once the method is determined, the cam shape is determined accordingly. In conventional technology, once the cam shape is determined, the cam must be replaced if a different method of operation is desired. This requires the plant to be shut down.
前記の如き旧来技術の問題点を改善するため、
負荷に応動して回動するカム軸に絞り調速用カム
とノズル調速用カムとを組として設け、加減弁の
開方式をノズル調速用開方式と絞り方式用開方式
とに切り換え可能な加減弁制御装置が知られてい
る（特開昭49−63805号公報参照）。 In order to improve the problems of the old technology as mentioned above,
A cam for controlling the throttle speed and a cam for controlling the nozzle speed are installed as a set on the camshaft that rotates in response to the load, and the opening method of the adjustment valve can be switched between the opening method for nozzle speed regulation and the opening method for the throttle method. A control valve control device is known (see Japanese Patent Application Laid-Open No. 49-63805).
前記特開昭49−63805号公報に示す従来技術は、
タービンの起動過程には絞り調速方式で運転し、
通常運転時にはノズル調速方式で運転することが
できるが、構造が複雑で部品点数が多く、コスト
高になるという問題がある。
The prior art disclosed in Japanese Patent Application Laid-Open No. 49-63805 is as follows:
During the startup process of the turbine, the throttle control system is used.
During normal operation, it is possible to operate using the nozzle speed control method, but there are problems in that the structure is complex, the number of parts is large, and the cost is high.
本発明は、前記の従来技術の問題点を改善し、
比較的簡単な構成であり乍ら起動時には１、２弁
同時開方式とし、通常運転に入つた時は順次開方
式に切り換えることができる加減弁制御装置を提
供することを目的とする。 The present invention improves the problems of the prior art described above,
It is an object of the present invention to provide a control valve control device which has a relatively simple configuration and can simultaneously open one and two valves at startup and switch to a sequential opening system when normal operation begins.
〔課題を解決するための手段〕
本発明は、前記の如き目的を達成するため、負
荷に応じて回動するカム軸に、少なくとも１、２
弁同時開方式用のカムと、順次開方式用のカムと
を設け、その１、２弁同時開方式用のカムと順次
開方式用のカムとをそれぞれ各別のカムオロアお
よびレバーを介してそれぞれ各別のパイロツト弁
に連係させ、かつ、該パイロツト弁と加減弁制御
用サーボモータとの間にソレノイドにより切換え
られる切換弁を配設し、該切換弁により、蒸気タ
ービンの起動時には前記１、２弁同時開方式用の
カムと連係するパイロツト弁により加減弁を制御
し、通常運転時には前記順次開方式用のカムと連
係するパイロツト弁により加減弁を制御すべくな
したことを特徴とする。[Means for Solving the Problems] In order to achieve the above objects, the present invention provides at least one or two camshafts that rotate according to the load.
A cam for the simultaneous valve opening method and a cam for the sequential opening method are provided, and the cam for the 1st and 2nd valve simultaneous opening method and the cam for the sequential opening method are respectively connected via separate cam followers and levers. A switching valve connected to each separate pilot valve and switched by a solenoid is provided between the pilot valve and a servo motor for controlling the control valve. The control valve is characterized in that the control valve is controlled by a pilot valve linked to a cam for the simultaneous valve opening system, and during normal operation, the control valve is controlled by a pilot valve linked to the cam for the sequential opening system.
本発明の加減弁制御装置は、前記の構成よりな
るから、必要最低限の簡単な構成でありながら、
１、２弁同時開方式と順次開方式とを選択して加
減弁を制御することができる。すなわち、切換弁
のソレノイドを付勢してないときには、順次開方
式用のカムによつて働くパイロツト弁によつて制
御される圧油は切換弁によつて遮断され、サーボ
モータへの圧油は１、２弁同時開方式用のカムに
よつて動くパイロツト弁によつて制御されるの
で、１、２弁同時開方式によつて加減弁を制御す
る。また、切換弁のソレノイドを付勢すると、
１、２弁同時開方式用のカムによつて動くパイロ
ツト弁により制御される圧油は切換弁により遮断
され、サーボモータへの圧油は順次開方式用のカ
ムによつて動くパイロツト弁によつて制御される
ので、順次開方式によつて加減弁を制御する。し
かも、この機能は、各々のパイロツト弁と１つの
切換弁とによつて達成される。
Since the control valve control device of the present invention has the above-mentioned configuration, it has the minimum necessary simple configuration, and yet
The control valves can be controlled by selecting between the one- and two-valve simultaneous opening method and the sequential opening method. That is, when the solenoid of the switching valve is not energized, the pressure oil controlled by the pilot valve operated by the sequential opening cam is shut off by the switching valve, and the pressure oil to the servo motor is Since it is controlled by a pilot valve moved by a cam for the 1- and 2-valve simultaneous opening system, the adjustment valve is controlled by the 1- and 2-valve simultaneous opening system. Also, when the solenoid of the switching valve is energized,
Pressure oil controlled by a pilot valve operated by a cam for the 1- and 2-valve simultaneous opening system is shut off by a switching valve, and pressure oil to the servo motor is controlled by a pilot valve operated by a cam for the sequential opening system. Since the control valve is controlled by the valve, the control valve is controlled by a sequential opening method. Moreover, this function is accomplished by each pilot valve and one switching valve.
以下、本発明の実施例を図面により説明する。 Embodiments of the present invention will be described below with reference to the drawings.
第７図および第８図は、本発明の実施例を示す
もので、制御油により作動するリレー弁６と、こ
のリレー弁６に挿入されたピストンロツドに連結
されたラツクと、カム軸９に取り付けられかつラ
ツク７にかみ合わされたピニオン８と、前記カム
軸９に設けられた１、２弁同時開方式用のカム１
０ａおよび順次開方式用のカム１０ｂと、各カム
１０ａ，１０に格別に係合されたカムフオロア１
１ａ，１１ｂと、各カムフオロア１１ａ，１１ｂ
に格別に連結されたレバー１２ａ，１２ｂと、各
レバー１２ａ，１２ｂに連係されたパイロツト弁
１３ａ，１３ｂと、加減弁１のサーボモータ１４
と、ソレノイド１６を有する切換弁１５とを備え
ている。 7 and 8 show an embodiment of the present invention, which shows a relay valve 6 operated by control oil, a rack connected to a piston rod inserted into the relay valve 6, and a rack attached to a camshaft 9. a pinion 8 which is connected to the rack 7, and a cam 1 provided on the camshaft 9 for simultaneous opening of one and two valves.
0a and a cam 10b for the sequential opening system, and a cam follower 1 that is specially engaged with each cam 10a, 10.
1a, 11b and each cam follower 11a, 11b
levers 12a, 12b that are specifically connected to the levers 12a, 12b, pilot valves 13a, 13b that are connected to each lever 12a, 12b, and a servo motor 14 of the control valve 1.
and a switching valve 15 having a solenoid 16.
前記切換弁１５は、ソレノイド１６を付勢して
ないときには、第７図に示すように、サーボモー
タ１４への圧油はパイロツト弁１３ａによつて制
御されると共に、パイロツト弁１３ｂにより制御
される圧油は遮断され、ソレノイド１６を付勢す
ると、第８図に示すように、サーボモータへの圧
油はパイロツト弁１３ｂによつて制御されると共
に、パイロツト弁１３ａによつて制御される圧油
は遮断されるようになつており、蒸気タービンの
起動時には１、２弁同時開方式用のカム１０ａに
よる制御に、通常運転時には順次開方式用のカム
１０ｂによる制御に切り換えるように構成されて
いる。 When the switching valve 15 does not energize the solenoid 16, as shown in FIG. 7, the pressure oil to the servo motor 14 is controlled by the pilot valve 13a and the pilot valve 13b. When the pressure oil is shut off and the solenoid 16 is energized, as shown in FIG. 8, the pressure oil to the servo motor is controlled by the pilot valve 13b, and the pressure oil controlled by the pilot valve 13a is is shut off, and is configured to switch to control by the cam 10a for the one- and two-valve simultaneous opening system when starting the steam turbine, and to switch to control by the cam 10b for the sequential opening system during normal operation. .
前記実施例の加減弁制御装置は、次のように操
作され作用する。 The control valve control device of the above embodiment is operated and operated as follows.
すなわち、リレー弁６に制御油が供給されるに
伴い、ラツク７およびピニオン８を介してカム軸
９が回転操作され、カム１０ａ，１０ｂが回動
し、カムフオロア１１ａ，１１ｂを通じてレバー
１２ａ，１２ｂが作動し、パイロツト弁１３ａ，
１３ｂを動かす。パイロツト弁１３ａ，１３ｂで
制御された圧油は、ソレノイド１６により切り換
えられる切換弁１５を通つてサーボモータ１４に
供給され、加減弁１を開閉する。 That is, as control oil is supplied to the relay valve 6, the camshaft 9 is rotated through the rack 7 and pinion 8, the cams 10a and 10b are rotated, and the levers 12a and 12b are rotated through the cam followers 11a and 11b. operates, and the pilot valve 13a,
Move 13b. Pressure oil controlled by the pilot valves 13a and 13b is supplied to the servo motor 14 through a switching valve 15 switched by a solenoid 16 to open and close the control valve 1.
蒸気タービンの起動時には、切換弁１５はソレ
ノイド１６が付勢されずに第７図の状態になつて
いる。この状態では、サーボモータ１４への圧油
はパイロツト弁１３ａにより制御される。従つ
て、１、２弁同時開方式用のカム１０ａの動きに
よつて制御されることになり、この制御の場合、
第５図から分かるように、急速起動が行われ、第
１段後蒸気温度はT2と低いので、熱応力を低く
抑えることができる。一方、順次開方式用のカム
１０ｂによつて動くパイロツト弁１３ｂにより制
御される圧油は切換弁１５により遮断されるの
で、カム１０ｂの動きはサーボモータ１４には伝
わらない。 When the steam turbine is started, the switching valve 15 is in the state shown in FIG. 7 with the solenoid 16 not energized. In this state, the pressure oil to the servo motor 14 is controlled by the pilot valve 13a. Therefore, it is controlled by the movement of the cam 10a for the one- and two-valve simultaneous opening system, and in this case,
As can be seen from FIG. 5, rapid startup is performed and the steam temperature after the first stage is as low as T 2 , so thermal stress can be kept low. On the other hand, since the pressure oil controlled by the pilot valve 13b moved by the sequential opening cam 10b is shut off by the switching valve 15, the movement of the cam 10b is not transmitted to the servo motor 14.
蒸気タービンが通常運転に入つた時は、ソレノ
イド１６を付勢して切換弁１５は第８図の状態に
切り換えられる。この状態では、サーボモータ１
４への圧油はパイロツト弁１３ｂにより制御され
る。したがつて、サーボモータ１４は順次開方式
用のカム１０ｂの動きによつて制御されることに
なり、この制御の場合には第６図から分かるよう
に、蒸気タービンを高効率で運転することができ
る。なお、この状態では１、２弁同時開方式用の
カム１０ａによつて動くパイロツト弁１３ａによ
り制御される圧油は切換弁１５により遮断され、
カム１０ａの動きはサーボモータ１４には伝わら
ない。 When the steam turbine enters normal operation, the solenoid 16 is energized and the switching valve 15 is switched to the state shown in FIG. In this state, servo motor 1
4 is controlled by a pilot valve 13b. Therefore, the servo motor 14 is controlled by the movement of the cam 10b for the sequential opening method, and in this case, as can be seen from FIG. 6, the steam turbine can be operated with high efficiency. I can do it. In this state, the pressure oil controlled by the pilot valve 13a moved by the cam 10a for the 1- and 2-valve simultaneous opening system is shut off by the switching valve 15.
The movement of the cam 10a is not transmitted to the servo motor 14.
以上述べたように、本発明によれば、必要最低
限の簡単な構成でありながら、蒸気タービンの起
動時には１、２弁同時開方式によつて制御するこ
とにより熱応力を低く抑え、通常運転時には順次
開方式によつて制御することによつて蒸気タービ
ンを高効率で運転することができる。
As described above, according to the present invention, although the configuration is simple and minimal, thermal stress is kept low by controlling the steam turbine by opening one and two valves at the same time when starting the steam turbine, resulting in normal operation. Steam turbines can sometimes be operated with high efficiency by controlling them in a sequential opening manner.
第１図は蒸気タービンの蒸気入口部の概念図、
第２図は同ノズルと動翼と静翼の回りの一部分の
拡大断面図、第３図は従来の加減弁制御装置を示
す図、第４図Ａは順次開方式の負荷と加減弁開度
の関係を示す図、第４図Ｂは１、２弁同時開方式
の負荷と加減弁開度の関係を示す図、第５図は
１、２弁同時開方式と順次開方式について負荷と
第１段後蒸気温度の関係を示す図、第６図は１、
２弁同時開方式と順次開方式について負荷とター
ビン効率変化との関係を示す図である。第７図は
本発明の実施例を示す図であつて１、２弁同時開
方式による制御の状態を示す図、第８図は同じく
順次開方式による制御に切り換えた状態を示す図
である。
１，１ａ〜１ｄ……加減弁、６……リレー弁、
７……ラツク、８……ピニオン、９……カム軸、
１０ａ……１、２弁同時開方式用のカム、１０ｂ
……順次開方式用のカム、１１，１１ａ，１１ｂ
……カムフオロア、１２，１２ａ，１２ｂ……レ
バー、１３，１３ａ，１３ｂ……パイロツト弁、
１４……サーボモータ、１５……切換弁、１６…
…切換弁のソレノイド。
Figure 1 is a conceptual diagram of the steam inlet of a steam turbine.
Figure 2 is an enlarged cross-sectional view of a part of the nozzle, rotor blades, and stator vanes, Figure 3 is a diagram showing a conventional control valve control device, and Figure 4A is the load and control valve opening of the sequential opening method. Figure 4B is a diagram showing the relationship between the load and the adjustment valve opening for the 1 and 2 valve simultaneous opening system, and Figure 5 is a diagram showing the relationship between the load and the adjustment valve opening for the 1 and 2 valve simultaneous opening system and the sequential opening system. A diagram showing the relationship between the steam temperature after the first stage, Figure 6 is 1,
FIG. 3 is a diagram showing the relationship between load and turbine efficiency change for the two-valve simultaneous opening method and the sequential opening method. FIG. 7 is a diagram showing an embodiment of the present invention, and is a diagram showing a control state using the one- and two-valve simultaneous opening method, and FIG. 8 is a diagram showing a state in which the control is also switched to the sequential opening method. 1, 1a to 1d...Adjustment valve, 6...Relay valve,
7...Rack, 8...Pinion, 9...Camshaft,
10a...Cam for simultaneous opening of 1 and 2 valves, 10b
...Cam for sequential opening method, 11, 11a, 11b
...Cam follower, 12, 12a, 12b...Lever, 13, 13a, 13b...Pilot valve,
14...Servo motor, 15...Switching valve, 16...
...Solenoid of switching valve.
Claims (1)
１、２弁同時開方式用のカムと、順次開方式用の
カムとを設け、その１、２弁同時開方式用のカム
と順次開方式用のカムとをそれぞれ各別のカムフ
オロアおよびレバーを介してそれぞれ各別のパイ
ロツト弁に連係させ、かつ、該各パイロツト弁と
加減弁制御用サーボモータとの間にソレノイドに
より切換えられる切換弁を配設し、該切換弁によ
り、蒸気タービンの起動時には前記１、２弁同時
開方式用のカムと連係するパイロツト弁により加
減弁を制御し、通常運転時には前記順次開方式用
のカムと連係するパイロツト弁により加減弁を制
御すべくなしたことを特徴とする加減弁制御装
置。1 A camshaft that rotates according to the load is provided with at least a cam for the 1- and 2-valve simultaneous opening method and a cam for the sequential opening method, and the cam for the 1- and 2-valve simultaneous opening method and the sequential opening method. The control cams are connected to respective pilot valves via separate cam followers and levers, and a switching valve that is switched by a solenoid is arranged between each pilot valve and a servo motor for controlling the control valve. When the steam turbine is started, the control valve is controlled by a pilot valve that is linked to the cam for the one- and two-valve simultaneous opening system, and during normal operation, the pilot valve is linked to the cam for the sequential opening system. A regulating valve control device characterized in that the regulating valve is controlled by a valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18364384A JPS6161903A (en) | 1984-09-04 | 1984-09-04 | Control valve control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18364384A JPS6161903A (en) | 1984-09-04 | 1984-09-04 | Control valve control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6161903A JPS6161903A (en) | 1986-03-29 |
| JPH0536601B2 true JPH0536601B2 (en) | 1993-05-31 |
Family
ID=16139376
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18364384A Granted JPS6161903A (en) | 1984-09-04 | 1984-09-04 | Control valve control device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6161903A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014155579A1 (en) * | 2013-03-27 | 2014-10-02 | 三菱重工コンプレッサ株式会社 | Multi-valve-type steam valve and steam turbine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4963805A (en) * | 1972-10-23 | 1974-06-20 |
-
1984
- 1984-09-04 JP JP18364384A patent/JPS6161903A/en active Granted
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014155579A1 (en) * | 2013-03-27 | 2014-10-02 | 三菱重工コンプレッサ株式会社 | Multi-valve-type steam valve and steam turbine |
| CN105074135A (en) * | 2013-03-27 | 2015-11-18 | 三菱重工压缩机有限公司 | Multi-valve-type steam valve and steam turbine |
| US10227898B2 (en) | 2013-03-27 | 2019-03-12 | Mitsubishi Heavy Industries Compressor Corporation | Multi-valve steam valve and steam turbine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6161903A (en) | 1986-03-29 |
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