JPS6239651B2 - - Google Patents
Info
- Publication number
- JPS6239651B2 JPS6239651B2 JP57013210A JP1321082A JPS6239651B2 JP S6239651 B2 JPS6239651 B2 JP S6239651B2 JP 57013210 A JP57013210 A JP 57013210A JP 1321082 A JP1321082 A JP 1321082A JP S6239651 B2 JPS6239651 B2 JP S6239651B2
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- combustion gas
- boiler
- thermal power
- power plant
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/08—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with working fluid of one cycle heating the fluid in another cycle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
【発明の詳細な説明】
本発明は、ボイラの生蒸気側に主発電機を駆動
するための蒸気タービンが、ボイラの燃焼ガス側
に燃焼ガスタービンがそれぞれ後置接続され、前
記ボイラに駆動機を備えた燃焼空気用の圧縮機が
接続される火力発電所に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention provides a steam turbine for driving a main generator on the live steam side of a boiler, and a combustion gas turbine on the combustion gas side of the boiler. The present invention relates to a thermal power plant to which a combustion air compressor equipped with a combustion air compressor is connected.
かかる火力発電所は雑誌“Brown Boveri
Mitteiluugen”1975年７月／８月号の第310頁の
第２図で知られている。この公知の火力発電所の
燃焼ガスタービンは燃焼空気用の圧縮機の駆動機
であり、その駆動軸に燃焼ガスタービンの駆動軸
が連結されている。燃焼空気用の圧縮機の駆動軸
には更に電動機の従動軸が連結され、この電動機
によつて前記圧縮機は火力発電所の起動過程にお
いて駆動される。 Such a thermal power plant was published in the magazine “Brown Boveri
Mitteiluugen" July/August 1975 issue, page 310, figure 2. The combustion gas turbine of this known thermal power plant is the drive machine for the compressor for the combustion air, and The drive shaft of the combustion gas turbine is connected to the combustion air compressor.A driven shaft of an electric motor is further connected to the drive shaft of the combustion air compressor, and the compressor is driven by the electric motor during the startup process of the thermal power plant. be done.
この周知の火力発電所は過給ボイラを有してい
る。この火力発電所の燃焼ガスタービンには調整
フラツパ弁付きの燃焼ガスバイパス配管が並列接
続されている。火力発電所が制御機能を維持する
ために、主発電機が定格負荷の場合、常に一部の
燃焼ガス流がバイパス配管を介して燃焼ガスター
ビンを迂回して煙突に導かれねばならない。この
場合圧縮機はボイラに定格負荷のために必要な量
の燃焼空気を正確に供給する。 This known thermal power plant has a supercharged boiler. A combustion gas bypass pipe with a regulating flapper valve is connected in parallel to the combustion gas turbine of this thermal power plant. In order for the thermal power plant to maintain its control function, whenever the main generator is at rated load, a portion of the combustion gas flow must be directed via the bypass pipe around the combustion gas turbine and into the chimney. In this case, the compressor supplies the boiler with exactly the amount of combustion air required for the rated load.
主発電機の需要出力（目標出力）を高める場
合、燃焼ガスバイパス配管にある調整フラツパ弁
の開度が減少され、それによつて燃焼ガスタービ
ンおよび圧縮機の回転数が高められ、相応して多
量の燃焼空気がボイラに供給される。逆に主発電
機の負荷が低下した場合、燃焼ガスバイパス配管
にある調整フラツパ弁の開度が増大され、それに
よつて燃焼ガスタービンおよび圧縮機の回転数が
減少される。 When increasing the demand output (target output) of the main generator, the opening of the regulating flapper valve in the combustion gas bypass line is reduced, thereby increasing the rotational speed of the combustion gas turbine and the compressor and increasing the amount of of combustion air is supplied to the boiler. Conversely, when the load on the main generator decreases, the opening degree of the regulating flapper valve in the combustion gas bypass line is increased, thereby reducing the rotational speed of the combustion gas turbine and the compressor.
特に定格運転の場合に燃焼ガスバイパス配管を
通して常に使用されずに流出する一部の燃焼ガス
流のために、公知の火力発電所の総合効率は劣化
している。 The overall efficiency of known thermal power plants is degraded due to a part of the combustion gas flow that is always left unused through the combustion gas bypass line, especially in the case of rated operation.
本発明の目的は、良好な制御機能と改良された
総合効率とを示す冒頭に述べた形式の火力発電所
を提供することにある。 The object of the invention is to provide a thermal power plant of the type mentioned at the outset which exhibits good control capabilities and improved overall efficiency.
この目的は本発明によれば、燃焼ガスタービン
が圧縮機から分離された補助発電機の駆動機とし
て構成されることによつて達成される。 This object is achieved according to the invention in that the combustion gas turbine is configured as a drive for an auxiliary generator that is separate from the compressor.
本発明によれば補助発電機および燃焼空気用の
圧縮機に対する個々の駆動機がそれぞれ異なつた
回転数をもつことができるので、圧縮機駆動機お
よび圧縮機は任意の回転数を有することができ、
それによつて主発電機の目標出力に相応した量の
燃焼空気を常に正確にボイラに供給することが可
能となる。 According to the invention, the individual drives for the auxiliary generator and the combustion air compressor can each have different rotational speeds, so that the compressor drive and the compressor can have any rotational speed. ,
This makes it possible to always accurately supply the boiler with an amount of combustion air corresponding to the target output of the main generator.
同時にこのボイラは、それから出る燃焼ガス
が、従来のように燃焼ガスタービンが圧縮機の駆
動機として構成される場合に許されるよりも極め
て高い温度を示すように設計することができる。
高められた燃焼ガス温度のために、電気系統に電
力を供給する補助発電機を燃焼ガスタービンで駆
動すること、およびそれによつて火力発電所の総
合効率を改善することができる。 At the same time, this boiler can be designed in such a way that the combustion gases leaving it exhibit a much higher temperature than would be permitted if a combustion gas turbine was conventionally configured as a drive for the compressor.
Due to the increased combustion gas temperature, it is possible to drive an auxiliary generator powering the electrical system with the combustion gas turbine and thereby improve the overall efficiency of the thermal power plant.
燃焼空気用の圧縮機が燃焼ガスタービンと連結
されず、この燃焼ガスタービンから独立した特別
な圧縮機駆動機で駆動され、この圧縮機駆動機の
回転数が主発電機の出力目標値の変動に遅れを生
ずることなくあるいはごく僅かな遅れをもつて適
合できるので、火力発電所の良好な制御機能もこ
れにより保証される。 The compressor for combustion air is not connected to the combustion gas turbine, but is driven by a special compressor drive machine independent from the combustion gas turbine, and the rotation speed of this compressor drive machine changes the output target value of the main generator. A good control function of the thermal power plant is thereby also ensured, since the system can be adapted without or with very little delay.
主発電機に調整器を接続し、これに接続された
調整機構が圧縮機駆動機の回転数を主発電機の出
力目標値と出力実際値との差によつて形成される
制御偏差に応じて調整するようにすると有利であ
る。 A regulator is connected to the main generator, and a regulating mechanism connected to the regulator adjusts the rotation speed of the compressor drive machine according to the control deviation formed by the difference between the target output value and the actual output value of the main generator. It is advantageous to make adjustments based on
以下図面に示す２つの実施例に基づいて本発明
を詳細に説明する。 The present invention will be described in detail below based on two embodiments shown in the drawings.
第１図における火力発電所は、貫流ボイラ３と
この貫流ボイラ３から出ている生蒸気配管１８に
接続されている蒸気タービン８とを有している。
貫流ボイラ３としては、たとえば石灰石あるいは
白雲石のような吸収剤を含んでいる微粉炭の流動
床が燃焼されるようないわゆる過給ボイラが使用
される。この微分炭の供給配管は図示されていな
い。 The thermal power plant in FIG. 1 has a once-through boiler 3 and a steam turbine 8 connected to a live steam pipe 18 coming out of the once-through boiler 3.
As once-through boiler 3, a so-called supercharged boiler is used, in which a fluidized bed of pulverized coal containing an absorbent such as limestone or dolomite is burned. This differential coal supply piping is not shown.
ボイラ３への燃焼空気の供給は燃焼空気のため
の圧縮機１によつて行なわれ、この圧縮機１はボ
イラ３の燃焼空気供給配管１９に接続されてい
る。 The supply of combustion air to the boiler 3 takes place by means of a combustion air compressor 1, which is connected to a combustion air supply line 19 of the boiler 3.
蒸気タービン８には復水ポンプ１１をもつた復
水器１０が後置接続され、この復水ポンプ１１は
低圧給水加熱器１３を介して給水タンク１４に復
水を圧送する。給水タンク１４は同時に脱気器と
して作用する。給水タンク１４には給水ポンプ１
５を介して給水加熱器１６が後置接続される。給
水加熱器１６はボイラ３の給水供給配管２０に通
じている。 A condenser 10 with a condensate pump 11 is connected downstream of the steam turbine 8 , and the condensate pump 11 pumps condensate via a low-pressure feedwater heater 13 to a feedwater tank 14 . The water tank 14 also acts as a deaerator. The water supply tank 14 has a water supply pump 1
A feed water heater 16 is connected downstream via 5. The feedwater heater 16 communicates with the feedwater supply pipe 20 of the boiler 3 .
ボイラ３の燃焼ガス配管２１には集塵機４があ
り、これには燃焼ガスタービン５が後置接続され
ている。燃焼ガスタービン５は圧縮機１から分離
された補助発電機６の駆動機であり、これは補助
発電機６に連結され、この補助発電機６と共に一
つのターボ設備を形成している。 A dust collector 4 is located in the combustion gas pipe 21 of the boiler 3, to which a combustion gas turbine 5 is connected downstream. The combustion gas turbine 5 is the drive of an auxiliary generator 6 which is separated from the compressor 1 and is connected to the auxiliary generator 6, with which it forms a turbo installation.
圧縮機１の駆動機としては補助蒸気タービン２
が設けられており、この補助蒸気タービン２はボ
イラ３から蒸気タービン８に行く生蒸気配管１８
と配管２２を介して接続されている。この補助蒸
気タービン２の排気側には復水器７が接続されて
おり、この復水器７に後置接続された復水ポンプ
１２は前述の復水ポンプ１１と同時に低圧給水加
熱器１３の復水入口側に接続される。 The auxiliary steam turbine 2 serves as the drive machine for the compressor 1.
The auxiliary steam turbine 2 is connected to a live steam pipe 18 going from the boiler 3 to the steam turbine 8.
and is connected via piping 22. A condenser 7 is connected to the exhaust side of the auxiliary steam turbine 2, and a condensate pump 12 connected downstream of the condenser 7 operates simultaneously with the aforementioned condensate pump 11. Connected to the condensate inlet side.
圧縮機１の駆動機となつている補助蒸気タービ
ン２への生蒸気配管２２には、調整器２５に接続
された調整機構１７が接続されている。調整機構
１７はこの実施例の場合は弁である。調整器２５
には主発電機９の出力実際値の検出器２６が接続
されている。主発電機９は蒸気タービン８に連結
され、それによつて駆動される。更に調整器２５
には主発電機９の出力目標値ＰSの発信器２７が
接続されている。 An adjustment mechanism 17 connected to a regulator 25 is connected to a live steam piping 22 to an auxiliary steam turbine 2 serving as a drive machine for the compressor 1 . The regulating mechanism 17 is a valve in this embodiment. Adjuster 25
A detector 26 for the actual output value of the main generator 9 is connected to. The main generator 9 is connected to and driven by the steam turbine 8. Furthermore, the regulator 25
A transmitter 27 for output target value P S of the main generator 9 is connected to.
主発電機９の出力実際値Ｐが出力目標値ＰSか
らずれると、出力実際値Ｐが出力目標値ＰSより
小さい場合には、調整器２５が弁から成る調整機
構１７のサーボモータ（図示せず）に開放パルス
を与え、出力実際値Ｐが出力目標値ＰSより大き
い場合には閉鎖パルスを与える。これに相応して
燃焼空気用の圧縮機１の回転数およびそれに伴な
つてボイラ３に供給される燃焼空気量も増加ある
いは減少される。これに同期して微粉炭の供給な
いし給水タンク１４からボイラ３への給水も増加
あるいは減少されるので、制御偏差ＰS―Ｐは最
終的に再び零になる。種々の調整過程中に変動す
る圧縮機１の回転数は従つて燃焼ガスタービン５
によつてではなく、燃焼ガスタービン５から分離
されて圧縮機１の駆動機となつている補助蒸気タ
ービン２だけによつて発生される。 When the actual output value P of the main generator 9 deviates from the output target value P S , if the actual output value P is smaller than the output target value P S , the regulator 25 is operated by the servo motor of the adjustment mechanism 17 consisting of a valve (Fig. (not shown) gives an opening pulse, and gives a closing pulse if the actual output value P is greater than the output target value P S . Correspondingly, the rotational speed of the combustion air compressor 1 and the amount of combustion air supplied to the boiler 3 are increased or decreased accordingly. In synchronization with this, the supply of pulverized coal or the supply of water from the water supply tank 14 to the boiler 3 is also increased or decreased, so that the control deviation P S -P eventually becomes zero again. The rotating speed of the compressor 1, which varies during the various adjustment processes, therefore affects the combustion gas turbine 5.
It is not generated by the combustion gas turbine 5, but only by the auxiliary steam turbine 2, which is separate from the combustion gas turbine 5 and serves as the drive for the compressor 1.
燃焼ガスタービン５が圧縮機１に連結されてお
らず、従つてその回転数を圧縮機１の必要出力に
合わせる必要がないので、ボイラ３は、燃焼ガス
配管２１を通つてボイラ３から出る燃焼ガスが最
適な高温を有し、それによつて火力発電所全体の
効率が改善されるように設計することができる。 Since the combustion gas turbine 5 is not connected to the compressor 1 and therefore does not need to adjust its rotational speed to the required output of the compressor 1, the boiler 3 is connected to the combustion gas leaving the boiler 3 through the combustion gas pipe 21. It can be designed such that the gas has an optimal high temperature, thereby improving the overall efficiency of the thermal power plant.
燃焼空気用の圧縮機１およびこの圧縮機１の駆
動機である補助蒸気タービン２の軸には継手２３
を介して電動機２４も連結できる。電動機２４は
火力発電所の起動過程において圧縮機１を駆動す
る働きをする。更に補助蒸気タービン２に対する
生蒸気は直接ボイラ３から出さず、蒸気タービン
８の種々の圧力段の一つから抽気することもでき
る。 A joint 23 is attached to the shaft of the compressor 1 for combustion air and the auxiliary steam turbine 2 that is the drive machine for this compressor 1.
An electric motor 24 can also be connected via. The electric motor 24 serves to drive the compressor 1 during the startup process of the thermal power plant. Furthermore, the live steam for the auxiliary steam turbine 2 may not be taken directly from the boiler 3, but may be extracted from one of the various pressure stages of the steam turbine 8.
圧縮機１の駆動機２は、給電回路に調整器２５
の調整機構として用いられる可変抵抗が直列接続
されている電動機だけで構成することもできる。 The drive machine 2 of the compressor 1 has a regulator 25 in its power supply circuit.
It is also possible to use only an electric motor connected in series with a variable resistor used as an adjustment mechanism.
第１図と同一部分には同一符号が付されている
第２図における火力発電所は、第１図における火
力発電所とは圧縮機の駆動機がボイラ３に後置接
続された補助ガスタービン２から構成されている
点だけが異なつている。すなわちこのガスタービ
ンは燃焼ガス配管２１に調整フラツパ弁から成る
調整機構１７を介して接続される。調整機構１７
は調整器２５に付属され、主発電機９の出力目標
値が高くなつた場合には相応して開かれ、小さく
なつた場合には相応して閉鎖される。更に補助発
電機６と連結された燃焼ガスタービン５にも調整
フラツパ弁２８が前置接続される。調整フラツパ
弁２８は火力発電所の起動の際には閉鎖され、そ
れによつて燃焼ガスタービン５を燃焼ガス配管２
１から分離する。 The thermal power plant in FIG. 2, in which the same parts as in FIG. 1 are given the same reference numerals, is different from the thermal power plant in FIG. The only difference is that it is composed of two parts. That is, this gas turbine is connected to the combustion gas pipe 21 via an adjustment mechanism 17 consisting of an adjustment flapper valve. Adjustment mechanism 17
is assigned to the regulator 25 and is correspondingly opened if the desired output value of the main generator 9 becomes high, and correspondingly closed if it becomes low. Furthermore, a regulating flap valve 28 is also connected upstream of the combustion gas turbine 5 which is connected to the auxiliary generator 6 . The regulating flapper valve 28 is closed during start-up of the thermal power plant, thereby connecting the combustion gas turbine 5 to the combustion gas pipe 2.
Separate from 1.
圧縮機駆動機２として構成された補助ガスター
ビンは比較的速やかに起動できるという利点を有
する。 The auxiliary gas turbine configured as compressor drive 2 has the advantage that it can be started up relatively quickly.
第１図および第２図はそれぞれ本発明に基づく
火力発電所の異なつた実施例の概略系統図であ
る。
１……圧縮機、２……圧縮機駆動機、３……ボ
イラ、５……燃焼ガスタービン、６……補助発電
機、９……主発電機、１７……調整機構、２５…
…調整器。
1 and 2 are schematic diagrams of different embodiments of a thermal power plant according to the present invention, respectively. DESCRIPTION OF SYMBOLS 1... Compressor, 2... Compressor drive machine, 3... Boiler, 5... Combustion gas turbine, 6... Auxiliary generator, 9... Main generator, 17... Adjustment mechanism, 25...
...Regulator.
Claims (1)
の蒸気タービンが、燃焼ガス側に燃焼ガスタービ
ンがそれぞれ後置接続され、前記ボイラに駆動機
を備えた燃焼空気用の圧縮機が接続されている火
力発電所において、前記燃焼ガスタービンが圧縮
機から分離された補助発電機の駆動機として構成
されることを特徴とする火力発電所。 ２ 特許請求の範囲第１項記載の火力発電所にお
いて、圧縮機駆動機がボイラの生蒸気側に接続さ
れている補助蒸気タービンとして構成されること
を特徴とする火力発電所。 ３ 特許請求の範囲第１項記載の火力発電所にお
いて、圧縮機駆動機が電動機として構成されるこ
とを特徴とする火力発電所。 ４ 特許請求の範囲第１項記載の火力発電所にお
いて、圧縮機駆動機がボイラの燃焼ガス側に接続
された補助ガスタービンとして構成されることを
特徴とする火力発電所。[Claims] 1. A steam turbine for driving a main generator on the live steam side of a boiler, a combustion gas turbine on the combustion gas side, and a combustion air generator equipped with a drive machine in the boiler. A thermal power plant to which a compressor is connected, wherein the combustion gas turbine is configured as a driver for an auxiliary generator separated from the compressor. 2. The thermal power plant according to claim 1, wherein the compressor drive machine is configured as an auxiliary steam turbine connected to the live steam side of the boiler. 3. The thermal power plant according to claim 1, wherein the compressor drive machine is configured as an electric motor. 4. The thermal power plant according to claim 1, wherein the compressor drive machine is configured as an auxiliary gas turbine connected to the combustion gas side of the boiler.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19813103431 DE3103431A1 (en) | 1981-02-02 | 1981-02-02 | "STEAM POWER PLANT" |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57146008A JPS57146008A (en) | 1982-09-09 |
| JPS6239651B2 true JPS6239651B2 (en) | 1987-08-24 |
Family
ID=6123836
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57013210A Granted JPS57146008A (en) | 1981-02-02 | 1982-01-29 | Thermoelectric power plant |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0057260A3 (en) |
| JP (1) | JPS57146008A (en) |
| DE (1) | DE3103431A1 (en) |
| ZA (1) | ZA82624B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19506727A1 (en) * | 1995-02-27 | 1996-08-29 | Abb Management Ag | Process for operating a power plant |
| DE102008019906A1 (en) | 2007-10-14 | 2009-04-16 | Ingelheim, Peter, Graf Von | Thermal power plant for generating steam, is provided with two consecutive steam cycles, where liquid with specific condensation capacity at particular temperature and vapor pressure at that temperature is evaporated |
| DE102010051956A1 (en) * | 2010-11-19 | 2012-05-24 | Siemens Aktiengesellschaft | Quick-closing flap |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR955203A (en) * | 1950-01-11 | |||
| FR936998A (en) * | 1948-08-13 | |||
| FR954930A (en) * | 1950-01-06 | |||
| FR775449A (en) * | 1933-07-13 | 1934-12-28 | Brown | Steam generator with combustion chamber under pressure |
| CH176432A (en) * | 1934-05-04 | 1935-04-15 | Bbc Brown Boveri & Cie | Steam system that has a steam generator with high heating gas speeds, at least one fan for the combustion air of the steam generator and several steam consumers. |
| FR1280039A (en) * | 1960-11-16 | 1961-12-29 | Babcock & Wilcox France | Improvements to combined cycle steam and gas energy production facilities |
| US3417737A (en) * | 1966-09-20 | 1968-12-24 | Foxboro Co | Once-through boiler control system |
-
1981
- 1981-02-02 DE DE19813103431 patent/DE3103431A1/en not_active Withdrawn
- 1981-10-21 EP EP81108656A patent/EP0057260A3/en not_active Withdrawn
-
1982
- 1982-01-29 JP JP57013210A patent/JPS57146008A/en active Granted
- 1982-02-01 ZA ZA82624A patent/ZA82624B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| EP0057260A2 (en) | 1982-08-11 |
| ZA82624B (en) | 1982-12-29 |
| EP0057260A3 (en) | 1982-08-18 |
| DE3103431A1 (en) | 1982-09-02 |
| JPS57146008A (en) | 1982-09-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5203159A (en) | Pressurized fluidized bed combustion combined cycle power plant and method of operating the same | |
| US2219994A (en) | Gas turbine plant and regulating system therefor | |
| US4081956A (en) | Combined gas turbine and steam turbine power plant | |
| CA1208921A (en) | Combined plant having steam turbine and gas turbine connected by single shaft | |
| CA2309058C (en) | Method for closed-loop output control of a steam power plant, and a steam power plant | |
| EP0034614A1 (en) | Control system for cheng dual-fluid cycle engine system. | |
| CS257271B2 (en) | Medium pressure or high pressure body of turbine | |
| US4854121A (en) | Combined cycle power plant capable of controlling water level in boiler drum of power plant | |
| JPS61152914A (en) | Starting of thermal power plant | |
| EP0172224A1 (en) | GAS TURBINE WITH FREE WORK TURBINE AND STEAM INJECTION. | |
| EP0902168A2 (en) | Method and arrangement for a combi power plant | |
| JPS6239651B2 (en) | ||
| JP3857350B2 (en) | Control device for combined cycle power plant | |
| US4133567A (en) | Combined cycle electric power generating system with improvement | |
| JPS61108814A (en) | Gas-steam turbine composite facility | |
| WO2020241543A1 (en) | Gas turbine, method for controlling same, and combined cycle plant | |
| JPH05340205A (en) | Control device for combined cycle power plant | |
| JPH0486359A (en) | Output control unit of co-generation plant | |
| US4175382A (en) | Steam power plant with pressure-fired boiler | |
| JPS59134331A (en) | Method of and device for controlling slide pressure operation of pressurized coal gasification type power plant | |
| JPS58107805A (en) | Control of turbine for combined cycle power generation | |
| JP2554099B2 (en) | Control device for combined cycle power plant | |
| JPS6246681B2 (en) | ||
| JPS5845566B2 (en) | combined cycle power plant | |
| SU979673A1 (en) | Method of controlling ship combination gas steam turbine plant |