JP3431435B2 - Combined power plant and closed air-cooled gas turbine system - Google Patents
Combined power plant and closed air-cooled gas turbine systemInfo
- Publication number
- JP3431435B2 JP3431435B2 JP00036797A JP36797A JP3431435B2 JP 3431435 B2 JP3431435 B2 JP 3431435B2 JP 00036797 A JP00036797 A JP 00036797A JP 36797 A JP36797 A JP 36797A JP 3431435 B2 JP3431435 B2 JP 3431435B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- steam
- air
- cooling
- gas turbine
- 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
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
- F01K23/10—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 exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/106—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 exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
Description
【０００１】[0001]
【発明の属する技術分野】本発明はコンバインド発電プ
ラントおよびクローズド空気冷却ガスタービンシステム
に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combined power generation plant and a closed air cooling gas turbine system.
【０００２】[0002]
【従来の技術】圧縮機から吐出された空気をブースト圧
縮機で昇圧し、この昇圧された空気でガスタービン高温
部を冷却し、冷却後の空気をタービンガスパス中に放出
することなく燃焼用空気として回収する空気冷却ガスタ
ービンの構成については、例えば特開昭５４−８２５１
８号公報に記載されている。2. Description of the Related Art The air discharged from a compressor is boosted by a boost compressor, the hot air of the gas turbine is cooled by this boosted air, and the cooled air is used for combustion without being discharged into a turbine gas path. Regarding the structure of the air-cooled gas turbine for collecting as air, for example, Japanese Patent Laid-Open No. 54-8251
No. 8 publication.
【０００３】また、圧縮機吐出空気をプリクーラで冷却
し、冷却した空気をブースト圧縮機で昇圧し、昇圧した
空気でガスタービン高温部を冷却し、冷却後の空気をタ
ービンガスパス中に放出することなく燃焼用空気として
回収するガスタービン構成については、例えば文献（th
e ASME Joint International Power Generation Confer
ence 94-JPGC-GT-8）に記載されている。Further, the air discharged from the compressor is cooled by a precooler, the cooled air is boosted by a boost compressor, the high temperature portion of the gas turbine is cooled by the boosted air, and the cooled air is discharged into a turbine gas path. For example, refer to the document (th.
e ASME Joint International Power Generation Confer
ence 94-JPGC-GT-8).
【０００４】[0004]
【発明が解決しようとする課題】このように形成されて
いるクローズド空気冷却ガスタービンシステムである
と、ガスタービン高温部を冷却した後の空気がタービン
ガスパス中に放出されないため、冷却空気のガスパス混
合によるガス温度の低下およびその混合損失がなく、さ
らに遠心力によるポンピング動力を回収することができ
るのでプラント効率の大幅な向上が予想される。In the closed air cooling gas turbine system formed as described above, since the air after cooling the high temperature part of the gas turbine is not discharged into the turbine gas path, the gas path of the cooling air is cooled. There is no reduction in gas temperature due to mixing and its mixing loss, and pumping power due to centrifugal force can be recovered, so that a significant improvement in plant efficiency is expected.
【０００５】しかし、冷却後の空気を燃焼用空気として
回収するクローズド空気冷却ガスタービンでは、高温部
冷却による冷却空気の圧力損失分だけ予め冷却空気の圧
力を昇圧するブースト圧縮機が必要である。よって、ブ
ースト圧縮機動力分はプラント効率の低下要因になるき
らいがある。However, in a closed air cooling gas turbine for recovering the cooled air as combustion air, a boost compressor is required to preliminarily increase the pressure of the cooling air by the pressure loss of the cooling air due to the high temperature part cooling. Therefore, the power of the boost compressor tends to be a factor of reducing the plant efficiency.
【０００６】また、次期高温ガスタービンでは燃焼器出
口温度１５００℃、圧縮機圧力比２５程度になるため、
圧縮機吐出空気温度も５００℃程度まで上昇する。５０
０℃の圧縮機吐出空気をブースト圧縮機で昇圧するとさ
らに冷却空気温度が上昇するため高温部を冷却すること
は不可能となる恐れがある。ゆえに圧縮機吐出からの冷
却空気をプリクーラで減温し、高温部の冷却を可能とす
ることが不可欠である。Further, in the next high temperature gas turbine, since the combustor outlet temperature is 1500 ° C. and the compressor pressure ratio is about 25,
The compressor discharge air temperature also rises to about 500 ° C. Fifty
When the air discharged from the compressor at 0 ° C. is boosted by the boost compressor, the temperature of the cooling air further rises, and it may be impossible to cool the high temperature portion. Therefore, it is essential to cool the high temperature part by cooling the cooling air from the compressor discharge with a precooler.
【０００７】このようにクローズド空気冷却ガスタービ
ンでは、補機としてプリクーラとブースト圧縮機が必要
でプリクーラの排熱とブースト圧縮機の動力分はプラン
ト効率の低下要因となる。As described above, in the closed air cooling gas turbine, the precooler and the boost compressor are required as auxiliary equipments, and the exhaust heat of the precooler and the power component of the boost compressor are factors that reduce the plant efficiency.
【０００８】この効率低下を最小限にとどめるには、プ
ラント効率向上の点で、前記プリクーラ排熱をコンバイ
ンドサイクルとしていかに有効利用するかが課題とな
る。プリクーラの排熱回収効果を大きくするには高温の
冷媒をプリクーラに供給し、その排熱をできるだけ温度
の高い箇所に回収することが望ましい。しかし、高温の
冷媒では冷却空気温度を必要なだけ下げることができず
高温部を十分に冷却できない可能性がある。前記従来の
技術ではこれらの課題を解決するプリクーラの熱交換器
の構成およびプリクーラ排熱の回収サイクルについては
言及していない。In order to minimize this efficiency decrease, how to effectively use the precooler exhaust heat as a combined cycle becomes a problem from the viewpoint of improving plant efficiency. In order to enhance the exhaust heat recovery effect of the precooler, it is desirable to supply a high-temperature refrigerant to the precooler and recover the exhaust heat to a location with a temperature as high as possible. However, there is a possibility that the temperature of the cooling air cannot be lowered as much as necessary with the high temperature refrigerant and the high temperature portion cannot be cooled sufficiently. The above-mentioned conventional technology does not mention the configuration of the heat exchanger of the precooler and the recovery cycle of the precooler exhaust heat which solve these problems.
【０００９】また、クローズド空気冷却ガスタービンの
起動から定格運転、停止と様々な運転状態で、ガスター
ビン高温部の冷却に必要な冷却空気量は変動するので、
それに合わせて冷却空気流量を制御する必要がある。さ
らに、様々な運転状態でプリクーラ出口冷却空気温度を
設定値に維持するために、プリクーラに供給される冷媒
量を制御する必要がある。プリクーラで使用され温度上
昇した冷媒を回収するとき、冷媒の温度と回収先の温度
との差が大きいと熱応力の発生原因となるので温度差が
許容値内におさまるように制御する必要もある。Further, the amount of cooling air required for cooling the high temperature part of the gas turbine varies depending on various operating states of the closed air cooling gas turbine, from start to rated operation and stop.
It is necessary to control the cooling air flow rate accordingly. Further, in order to maintain the precooler outlet cooling air temperature at the set value in various operating conditions, it is necessary to control the amount of refrigerant supplied to the precooler. When recovering the refrigerant whose temperature has risen due to use in the pre-cooler, if the difference between the temperature of the refrigerant and the temperature of the recovery destination is large, thermal stress will occur.Therefore, it is necessary to control the temperature difference to be within the allowable value. .
【００１０】また、このクローズド冷却方式ではガスタ
ービン高温部の寿命によりクラックが発生し、そこから
冷却空気がリークする可能性がある。このリークが大量
になるとリーク箇所以降の高温部を十分に冷却できなく
なり回収空気の温度も高温になる。リークにより燃焼器
への回収空気量が減少するとタービン第１段静翼を通過
する作動ガス量が減少して第１段静翼入口圧力が低下す
る。第１段静翼入口圧力が低下するとガスタービン出力
が低下する。このとき負荷一定制御状態で運転されてい
ると出力低下を防ぐために燃料が増量されることにな
る。しかし、リークにより燃焼器流入空気量が減少して
いるので燃焼温度が上昇することになる。燃焼温度の上
昇は従来排ガス温度の上昇で検知しているが、クローズ
ド冷却方式でリークが生じた場合は排ガス温度が上昇せ
ず、排ガス温度では検知できない可能性がある。Further, in this closed cooling system, cracks may occur due to the life of the high temperature part of the gas turbine, and cooling air may leak from the cracks. If this leak becomes large, the high temperature part after the leak part cannot be cooled sufficiently and the temperature of the collected air also becomes high. When the amount of recovered air to the combustor decreases due to the leak, the amount of working gas passing through the turbine first stage vanes decreases, and the first stage vane inlet pressure decreases. When the pressure at the inlet of the first stage vane decreases, the gas turbine output decreases. At this time, if the engine is operated in the constant load control state, the amount of fuel will be increased in order to prevent the output from decreasing. However, the amount of air flowing into the combustor decreases due to the leak, and therefore the combustion temperature rises. Conventionally, the rise in combustion temperature is detected by the rise in exhaust gas temperature. However, if a leak occurs in the closed cooling system, the exhaust gas temperature does not rise and may not be detected by the exhaust gas temperature.
【００１１】本発明はこれに鑑みなされたもので、その
目的とするところは、前述したプリクーラの排熱をプラ
ントに有効に回収し、高効率化を図ることにある。さら
にクローズド空気冷却ガスタービンの様々な運転モード
において適正な運転状態を保ち信頼性の向上を図ること
ができるこの種のコンバインド発電プラントおよびクロ
ーズド空気冷却ガスタービンシステムを提供するにあ
る。The present invention has been made in view of the above circumstances, and an object of the present invention is to effectively recover the exhaust heat of the precooler described above to the plant to achieve high efficiency. Another object of the present invention is to provide a combined power generation plant of this type and a closed air cooling gas turbine system capable of maintaining an appropriate operating state in various operating modes of the closed air cooling gas turbine and improving reliability.
【００１２】[0012]
【課題を解決するための手段】すなわち本発明は、ガス
タービン高温部を冷却する冷却媒体として、圧縮機吐出
空気をプリクーラで冷却しブースト圧縮機にて昇圧した
空気を用い、冷却後の空気を燃焼空気として燃焼器に回
収するクローズド空気冷却ガスタービンと、このガスタ
ービンの排ガスにより蒸気を発生する排熱回収ボイラ
と、この排熱回収ボイラで発生した蒸気を動力に変換す
る蒸気タービンとを備えたコンバインド発電プラントに
おいて、前記空気冷却ガスタービンのプリクーラとし
て、それぞれ冷却媒体の温度が異なる複数の熱交換器を
備、プリクーラ上流側熱交換器には温度の高い冷媒が供
給され、かつ温度の高い箇所に回収されるように形成し
所期の目的を達成するようにしたものである。That is, the present invention uses, as a cooling medium for cooling a high temperature part of a gas turbine, air discharged from a compressor by a precooler and boosted by a boost compressor. It is equipped with a closed air cooling gas turbine that collects combustion air in the combustor, an exhaust heat recovery boiler that generates steam from the exhaust gas of this gas turbine, and a steam turbine that converts the steam generated in this exhaust heat recovery boiler into power. In the combined power generation plant, as a precooler of the air-cooled gas turbine, a plurality of heat exchangers each having a different cooling medium temperature are provided, and the precooler upstream heat exchanger is supplied with a high-temperature refrigerant and has a high temperature. It is formed so that it can be collected in a certain place to achieve the intended purpose.
【００１３】また、前記空気冷却ガスタービンのプリク
ーラに複数の熱交換器を備えるとともに、前記プリクー
ラの冷却媒体として前記排熱回収ボイラからの蒸気と給
水の両方を用い、冷却後の温度上昇した蒸気、給水を再
び前記排熱回収ボイラに供給するようにしたものであ
る。また、前記空気冷却ガスタービンのプリクーラに複
数の熱交換器を備えるとともに、前記プリクーラの冷却
媒体として前記高圧蒸気タービン出口の蒸気と前記排熱
回収ボイラの中圧節炭器出口給水を昇圧した高圧給水の
両方を用い、プリクーラ冷却後の温度上昇した前記蒸
気、給水をそれぞれ前記再熱器出口と高圧蒸発器入口に
供給するようにしたものである。Further, the precooler of the air cooling gas turbine is provided with a plurality of heat exchangers, and both the steam from the exhaust heat recovery boiler and the feed water are used as the cooling medium of the precooler, and the steam whose temperature has risen after cooling is used. The feed water is supplied again to the exhaust heat recovery boiler. In addition, the precooler of the air-cooled gas turbine is provided with a plurality of heat exchangers, and the high-pressure steam of the high-pressure steam turbine outlet as the cooling medium of the precooler and the intermediate-pressure economizer outlet feedwater of the exhaust heat recovery boiler are pressurized. Both of the feed water are used to supply the steam and feed water whose temperature has risen after precooler cooling to the reheater outlet and the high pressure evaporator inlet, respectively.
【００１４】また、ガスタービン高温部を冷却する冷却
媒体として、圧縮機吐出空気をプリクーラで冷却しブー
スト圧縮機にて昇圧した空気を用い、冷却後の空気を燃
焼空気として燃焼器に回収するクローズド空気冷却ガス
タービンと、このガスタービンの排ガスにより高圧、中
圧、低圧の三種類の圧力の蒸気を発生するために節炭
器、蒸発器、過熱器を高圧、中圧、低圧蒸気に対してそ
れぞれ備え、前記高圧蒸気により駆動した高圧蒸気ター
ビン出口の蒸気を再熱する再熱器を備えた排熱回収ボイ
ラと、前記排熱回収ボイラからの蒸気を動力に変換する
蒸気タービンとを有するコンバインド発電プラントにお
いて、前記空気冷却ガスタービンのプリクーラに複数の
熱交換器を備えるとともに、このプリクーラの冷却媒体
として高圧蒸発器出口の蒸気と前記排熱回収ボイラの中
圧節炭器出口給水を昇圧した高圧給水の両方を用い、プ
リクーラ冷却後の温度上昇した前記蒸気、給水をそれぞ
れ前記高圧過熱器出口と高圧蒸発器入口に供給するよう
にしたものである。Further, as a cooling medium for cooling the high temperature part of the gas turbine, the air discharged from the compressor is cooled by a precooler and the pressure is increased by a boost compressor, and the cooled air is recovered as combustion air in a combustor. An air cooling gas turbine and a gas saver, an evaporator, and a superheater are used to generate high-pressure, medium-pressure, and low-pressure steam from the exhaust gas of the gas turbine for high-pressure, medium-pressure, and low-pressure steam. A combined exhaust heat recovery boiler equipped with a reheater that reheats the steam at the outlet of the high pressure steam turbine driven by the high pressure steam, and a steam turbine that converts the steam from the exhaust heat recovery boiler into power. In a power plant, the precooler of the air-cooled gas turbine is equipped with a plurality of heat exchangers, and a high-pressure evaporator is used as a cooling medium for the precooler. Of both the steam and the exhaust heat recovery boiler medium pressure economizer outlet feed water is used to pressurize the high pressure feed water, the temperature rises after precooler cooling, feed water to the high pressure superheater outlet and high pressure evaporator inlet, respectively. It is something that is supplied.
【００１５】また、前記空気冷却ガスタービンのプリク
ーラに複数の熱交換器を備えるとともに、前記プリクー
ラの冷却媒体として前記高圧蒸気タービン出口の蒸気と
前記排熱回収ボイラの低圧節炭器出口給水を昇圧した中
圧給水の両方を用い、プリクーラ冷却後の温度上昇した
前記蒸気、給水を、それぞれ前記再熱器出口と中圧節炭
器出口に供給するようにしたものである。Further, the precooler of the air-cooled gas turbine is provided with a plurality of heat exchangers, and the steam of the outlet of the high-pressure steam turbine and the feed water of the low-pressure economizer outlet of the exhaust heat recovery boiler are pressurized as a cooling medium of the precooler. Both of the above-mentioned medium pressure feed water are used to supply the steam and feed water whose temperature has risen after precooler cooling to the reheater outlet and the medium pressure economizer outlet, respectively.
【００１６】また、前記排熱回収ボイラから前記プリク
ーラへの供給系または前記プリクーラから前記排熱回収
ボイラへの回収系上にプリクーラへの供給流量を調整す
る装置を設け、前記回収配管と排熱回収ボイラ配管との
合流点で温度差が許容値以下となるように前記プリクー
ラ供給流量調整装置によりプリクーラへの供給流量を調
整するようにしたものである。Further, a device for adjusting the supply flow rate to the precooler is provided on the supply system from the exhaust heat recovery boiler to the precooler or the recovery system from the precooler to the exhaust heat recovery boiler, and the recovery pipe and the exhaust heat are provided. The supply flow rate to the precooler is adjusted by the precooler supply flow rate adjusting device so that the temperature difference at the confluence with the recovery boiler pipe is equal to or less than the allowable value.
【００１７】また、前記ガスタービンのプリクーラから
前記排熱回収ボイラへの回収配管上に蒸気若しくは水を
混入して排熱回収ボイラへの回収温度を調整する装置を
設け、前記回収配管と排熱回収ボイラ配管との合流点で
温度差が許容値以下となるように前記回収温度調整装置
により蒸気若しくは水の混入量を変化させるようにした
ものである。Further, a device for adjusting the recovery temperature of the exhaust heat recovery boiler by mixing steam or water is provided on the recovery pipe from the precooler of the gas turbine to the exhaust heat recovery boiler, and the recovery pipe and the exhaust heat are provided. The amount of steam or water mixed is changed by the recovery temperature adjusting device so that the temperature difference at the confluence with the recovery boiler pipe becomes equal to or less than the allowable value.
【００１８】また、ガスタービン高温部を冷却する冷却
媒体として、圧縮機吐出空気をプリクーラで冷却しブー
スト圧縮機にて昇圧した空気を用いるとともに、冷却後
の空気を燃焼空気として燃焼器に回収するクローズド空
気冷却ガスタービンシステムにおいて、前記プリクーラ
の排熱を前記ガスタービンの燃料の温度上昇に用いるよ
うにしたものである。また、前記プリクーラの熱交換器
として蒸発器を備えるようにしたものである。また、前
記ブースト圧縮機の駆動装置を電気モータとし、前記ガ
スタービンの排気ガス温度またはガスタービン回転数に
応じてブースト圧縮機の回転数を変化させ、前記ガスタ
ービン高温部へ供給する冷却空気量を調整するようにし
たものである。Further, as the cooling medium for cooling the high temperature part of the gas turbine, the air discharged from the compressor by the precooler and the pressure boosted by the boost compressor is used, and the cooled air is recovered as the combustion air in the combustor. In the closed air cooling gas turbine system, the exhaust heat of the precooler is used to raise the temperature of the fuel of the gas turbine. Also, an evaporator is provided as a heat exchanger of the precooler. Further, an electric motor is used as a drive device of the boost compressor, the rotation speed of the boost compressor is changed according to the exhaust gas temperature of the gas turbine or the gas turbine rotation speed, and an amount of cooling air supplied to the high temperature part of the gas turbine. Is adjusted.
【００１９】また、前記ブースト圧縮機の駆動源をガス
タービン回転軸とするようにしたものである。また、前
記冷却媒体の流通系に、冷却空気のリーク状態を検出す
る検出手段を設けるとともに、そのリーク状態の検出に
燃料流量の変動量または回収空気圧力の変動量を用いる
ようにしたものである。Further, the drive source of the boost compressor is a gas turbine rotating shaft. Further, the flow system of the cooling medium is provided with a detecting means for detecting the leak state of the cooling air, and the variation amount of the fuel flow rate or the variation amount of the recovered air pressure is used for detecting the leak state. .
【００２０】すなわちこのように形成されたプラントで
あると、プリクーラの熱交換器が複数設けられ、プリク
ーラ上流側熱交換器には温度の高い冷媒が供給され、温
度の高い箇所に回収されることにより高効率化が図られ
ると同時に、十分に冷却空気温度が下らない分は下流側
の熱交換器に低温の冷媒を供給することによりガスター
ビン高温部の冷却効果を高めることができ、また、ガス
タービン高温部の冷却に必要な冷却空気量の調節につい
ては、ブースト圧縮機の駆動装置を電気モータとし、前
記ガスタービンの排気ガス温度またはガスタービン回転
数に応じてブースト圧縮機の回転数を変化させ、ガスタ
ービン高温部へ供給する空気量を調整することにより達
成できる。また、ガスタービンの排気ガス温度またはガ
スタービン回転数に応じて冷却空気供給配管上に設けた
空気流量調節装置で調整され、前記ガスタービン高温部
へ供給する空気量が制御され、ガスタービン高温部の冷
却効果を高めることができる。That is, in the plant formed as described above, a plurality of heat exchangers of the precooler are provided, the high temperature refrigerant is supplied to the precooler upstream heat exchanger, and the precooler heat exchanger is recovered at a high temperature location. As a result, the cooling efficiency of the gas turbine high temperature part can be enhanced by supplying a low-temperature refrigerant to the heat exchanger on the downstream side as much as the cooling air temperature does not fall sufficiently. For adjusting the amount of cooling air required for cooling the high temperature part of the turbine, an electric motor is used as the drive device of the boost compressor, and the rotation speed of the boost compressor is changed according to the exhaust gas temperature of the gas turbine or the gas turbine rotation speed. Then, it can be achieved by adjusting the amount of air supplied to the high temperature part of the gas turbine. Further, according to the exhaust gas temperature of the gas turbine or the gas turbine rotation speed, it is adjusted by an air flow rate adjusting device provided on the cooling air supply pipe, the amount of air supplied to the gas turbine high temperature part is controlled, and the gas turbine high temperature part is controlled. The cooling effect of can be enhanced.
【００２１】様々な運転状態でプリクーラ出口冷却空気
温度を設定値に維持することについては、排熱回収ボイ
ラからプリクーラへの冷媒供給配管またはプリクーラか
ら排熱回収ボイラへの冷媒回収配管上にプリクーラへの
冷媒流量を調整する装置を設け、プリクーラ出口空気温
度を計測しその温度が設定値となるようにプリクーラ冷
媒流量調整装置によりプリクーラへの冷媒供給流量を調
整することにより達成できる。For maintaining the precooler outlet cooling air temperature at the set value in various operating conditions, the refrigerant supply pipe from the exhaust heat recovery boiler to the precooler or the refrigerant recovery pipe from the precooler to the exhaust heat recovery boiler is connected to the precooler. Is provided, the precooler outlet air temperature is measured, and the precooler refrigerant flow rate adjusting device adjusts the refrigerant supply flow rate to the precooler so that the temperature becomes a set value.
【００２２】またプリクーラで使用され温度上昇した冷
媒を回収するとき、冷媒の温度と回収先の温度との差が
大きいと熱応力の発生原因となることについては、排熱
回収ボイラからプリクーラへの供給配管またはプリクー
ラから排熱回収ボイラへの回収配管上にプリクーラへの
供給冷媒流量を調整する装置を設け、回収配管と排熱回
収ボイラ配管との合流点で温度差が許容値以下となるよ
うにプリクーラ供給流量調整装置によりプリクーラへの
冷媒流量を調整することにより達成できる。Further, when recovering the refrigerant whose temperature has been raised and used in the precooler, if the difference between the temperature of the refrigerant and the temperature of the recovery destination is large, thermal stress will be generated. Therefore, from the exhaust heat recovery boiler to the precooler, A device for adjusting the flow rate of the refrigerant supplied to the precooler is installed on the recovery pipe from the supply pipe or the precooler to the exhaust heat recovery boiler so that the temperature difference at the confluence of the recovery pipe and the exhaust heat recovery boiler pipe will be below the allowable value. It can be achieved by adjusting the refrigerant flow rate to the precooler by the precooler supply flow rate adjusting device.
【００２３】また、プリクーラから排熱回収ボイラへの
回収配管上に蒸気若しくは水を混入して排熱回収ボイラ
への回収温度を調整する装置を設け、回収配管と排熱回
収ボイラ配管との合流点で温度差が許容値以下となるよ
うに回収温度調整装置により蒸気若しくは水の混入量を
変化させることによっても達成できる。冷却空気のリー
クを検知することについては、燃料流量の変動または回
収空気圧力を監視することによって達成できる。Further, a device for adjusting the recovery temperature to the exhaust heat recovery boiler by mixing steam or water is provided on the recovery pipe from the precooler to the exhaust heat recovery boiler, and the recovery pipe and the exhaust heat recovery boiler pipe are joined. This can also be achieved by changing the mixing amount of steam or water by the recovery temperature adjusting device so that the temperature difference becomes less than the allowable value at the point. Detecting cooling air leaks can be accomplished by monitoring fuel flow fluctuations or recovered air pressure.
【００２４】[0024]
【発明の実施の形態】以下図示した実施例に基づいて本
発明を詳細に説明する。図１にはそのクローズド空気冷
却ガスタービンシステムが系統図で示されている。ガス
タービン装置は、主として圧縮機１、燃焼器２、タービ
ン３から構成され、蒸気タービン装置は高圧蒸気タービ
ン４、再熱蒸気タービン５、低圧蒸気タービン６で構成
されている。この場合、ガスタービン装置と蒸気タービ
ン装置および発電機７は同軸上に設置されている。BEST MODE FOR CARRYING OUT THE INVENTION The present invention will be described in detail based on the embodiments shown in the drawings. FIG. 1 is a system diagram showing the closed air cooling gas turbine system. The gas turbine device is mainly composed of a compressor 1, a combustor 2 and a turbine 3, and the steam turbine device is composed of a high pressure steam turbine 4, a reheat steam turbine 5 and a low pressure steam turbine 6. In this case, the gas turbine device, the steam turbine device, and the generator 7 are installed coaxially.
【００２５】タービン３からの排出ガスは、経路８を介
して排熱回収ボイラ９に供給される。排熱回収ボイラ９
には、低圧節炭器１０、低圧ドラム１１、低圧蒸発器１
２、中圧節炭器１３、中圧ドラム１４、中圧蒸発器１
５、低圧過熱器１６、高圧節炭器１７、中圧過熱器１
８、高圧ドラム１９、高圧蒸発器２０、高圧１次過熱器
２１、１次再熱器２２、２次再熱器２３、高圧２次過熱
器２４、給水ポンプ２５、中圧ポンプ２６、高圧ポンプ
２７、再循環ポンプ２８、プリクーラ給水ポンプ２９が
設置されている。The exhaust gas from the turbine 3 is supplied to the exhaust heat recovery boiler 9 via the path 8. Exhaust heat recovery boiler 9
Includes a low pressure economizer 10, a low pressure drum 11, and a low pressure evaporator 1.
2, medium pressure economizer 13, medium pressure drum 14, medium pressure evaporator 1
5, low pressure superheater 16, high pressure economizer 17, medium pressure superheater 1
8, high pressure drum 19, high pressure evaporator 20, high pressure primary superheater 21, primary reheater 22, secondary reheater 23, high pressure secondary superheater 24, water supply pump 25, medium pressure pump 26, high pressure pump 27, a recirculation pump 28, and a precooler water supply pump 29 are installed.
【００２６】蒸気タービン系は、高圧蒸気タービン４、
再熱蒸気タービン５、低圧タービン６、復水器３０で構
成され、クローズド空気冷却系統はプリクーラ３１、ブ
ースト圧縮機３２、ガスタービン高温部３３で構成され
ている。The steam turbine system includes a high pressure steam turbine 4,
It is composed of the reheat steam turbine 5, the low-pressure turbine 6, and the condenser 30, and the closed air cooling system is composed of a precooler 31, a boost compressor 32, and a gas turbine high temperature section 33.
【００２７】圧縮機入口空気４１は圧縮機１で昇圧され
燃焼器２に供給される。また圧縮機吐出空気の一部はプ
リクーラ３１で減温される。プリクーラ３１で減温され
た空気はブースト圧縮機３２で昇圧されガスタービン高
温部３３の冷却に用いられる。ガスタービン高温部３３
を冷却した空気はタービンガスパス中に放出されること
なく燃焼器２に回収される。The compressor inlet air 41 is pressurized by the compressor 1 and supplied to the combustor 2. Further, a part of the air discharged from the compressor is cooled by the precooler 31. The air whose temperature has been reduced by the precooler 31 is boosted by the boost compressor 32 and used for cooling the high temperature part 33 of the gas turbine. Gas turbine high temperature section 33
The cooled air is recovered in the combustor 2 without being released into the turbine gas path.
【００２８】燃焼器２では圧縮機吐出空気と回収した冷
却空気で燃料４２を燃焼し、高温高圧の燃焼ガスを生成
する。燃焼ガスはタービン３で仕事をし、排気ガスが経
路８を通って、排熱回収ボイラ９に供給される。排熱回
収ボイラ９で熱回収された排気ガスは大気４５に放出さ
れる。In the combustor 2, the fuel 42 is burned by the compressor discharge air and the recovered cooling air to generate high temperature and high pressure combustion gas. The combustion gas works in the turbine 3, and the exhaust gas is supplied to the exhaust heat recovery boiler 9 through the path 8. The exhaust gas whose heat is recovered by the exhaust heat recovery boiler 9 is released to the atmosphere 45.
【００２９】復水器３０からの給水は、給水ポンプ２５
を通り排熱回収ボイラ９内の低圧節炭器１０に流入す
る。低圧節炭器１０の出口給水は低圧ドラム１１に供給
されると同時に、中圧ポンプ２６および再循環ポンプ２
８へ供給される。再循環ポンプ２８出口の給水は低圧節
炭器１０入口に合流し、低圧節炭器入口給水温度を上げ
て露結による低圧節炭器１０の低温腐食を防止してい
る。The water supplied from the condenser 30 is supplied by the water supply pump 25.
Through the exhaust heat recovery boiler 9 into the low pressure economizer 10. The outlet water supply of the low-pressure economizer 10 is supplied to the low-pressure drum 11, and at the same time, the medium-pressure pump 26 and the recirculation pump 2
8 is supplied. The feed water at the outlet of the recirculation pump 28 joins the inlet of the low-pressure economizer 10 and raises the temperature of the inlet water of the low-pressure economizer to prevent low temperature corrosion of the low-pressure economizer 10 due to condensation.
【００３０】中圧ポンプ２６出口の給水は中圧節炭器１
３に導かれ中圧ドラム１４と高圧ポンプ２７に供給され
る。高圧ポンプ２７出口の給水は、高圧節炭器１７を通
って高圧ドラム１９へ供給される。高圧ドラム１９の給
水は高圧蒸発器２０で飽和蒸気となり高圧１次過熱器２
１に供給される。The water supply at the outlet of the medium pressure pump 26 is the medium pressure economizer 1.
3 is supplied to the medium pressure drum 14 and the high pressure pump 27. The water supply at the outlet of the high pressure pump 27 is supplied to the high pressure drum 19 through the high pressure economizer 17. The water supplied to the high-pressure drum 19 becomes saturated steam in the high-pressure evaporator 20 and the high-pressure primary superheater 2
1 is supplied.
【００３１】高圧１次過熱器２１を出た蒸気は高圧ポン
プ２７出口給水の一部と温度調節器３４で合流し高圧２
次過熱器２４に供給される。高圧２次過熱器２４出口の
温度が適正温度となるように温度調節器３４への高圧ポ
ンプ出口給水量を調節する。高圧２次過熱器２４出口蒸
気は主蒸気配管３５と通って高圧蒸気タービン４に供給
される。高圧蒸気タービン４で仕事をした蒸気は配管３
６を通って１次再熱器２２に供給される。The steam leaving the high-pressure primary superheater 21 joins with a part of the feed water at the outlet of the high-pressure pump 27 at the temperature controller 34, and the high-pressure 2
It is supplied to the next superheater 24. The high-pressure pump outlet water supply amount to the temperature controller 34 is adjusted so that the outlet temperature of the high-pressure secondary superheater 24 becomes an appropriate temperature. The high-pressure secondary superheater 24 outlet steam is supplied to the high-pressure steam turbine 4 through the main steam pipe 35. The steam that worked in the high-pressure steam turbine 4 is pipe 3
It is supplied to the primary reheater 22 through 6.
【００３２】１次再熱器２２を出た蒸気は中圧ポンプ２
６出口給水の一部と温度調節器３７で合流し２次再熱器
２３に供給される。２次再熱器２３を出た蒸気は配管３
８を通って再熱蒸気タービン５に供給される。２次再熱
器２３出口の温度が適正温度となるように温度調節器３
７への中圧ポンプ出口給水量を調節する。再熱蒸気ター
ビン５で仕事をした蒸気は配管３９を通って低圧蒸気タ
ービン６入口に供給される。The steam leaving the primary reheater 22 is the intermediate pressure pump 2.
A part of the 6 outlet water supply is joined by the temperature controller 37 and is supplied to the secondary reheater 23. The steam exiting the secondary reheater 23 is pipe 3
It is supplied to the reheat steam turbine 5 through 8. The temperature controller 3 so that the temperature at the outlet of the secondary reheater 23 becomes an appropriate temperature.
Adjust the medium pressure pump outlet water supply to 7. The steam that has worked in the reheat steam turbine 5 is supplied to the low pressure steam turbine 6 inlet through the pipe 39.
【００３３】一方、低圧ドラム１１に供給された給水は
低圧蒸発器１２で蒸発し低圧過熱器１６に導かれる。低
圧過熱器１６を出た蒸気は配管４０を通って低圧蒸気タ
ービン６入口で再熱蒸気タービン出口からの蒸気と合流
し低圧蒸気タービン６に供給される。低圧タービン６を
でた蒸気は復水器３０で水となり、給水ポンプ２５によ
り排熱回収ボイラ９へ供給される。On the other hand, the feed water supplied to the low-pressure drum 11 is evaporated in the low-pressure evaporator 12 and guided to the low-pressure superheater 16. The steam exiting the low-pressure superheater 16 joins the steam from the reheat steam turbine outlet at the inlet of the low-pressure steam turbine 6 through the pipe 40 and is supplied to the low-pressure steam turbine 6. The steam leaving the low-pressure turbine 6 becomes water in the condenser 30, and is supplied to the exhaust heat recovery boiler 9 by the water supply pump 25.
【００３４】プリクーラの熱回収系統について説明す
る。プリクーラ３１は高温側熱交換器４３と低温側熱交
換器４４の二つに分割されている。高温側熱交換器４３
には中圧蒸発器１５、中圧過熱器を通過した蒸気と高圧
蒸気タービン４出口蒸気を混合した蒸気が供給される。
高温側熱交換器４３で高温部３３の冷却用空気と熱交換
し温度上昇した蒸気は１次再熱器出口に合流する。低温
側熱交換器４４には中圧節炭器１３出口から分岐し、供
給ポンプ２９で昇圧された給水が導かれる。低温側熱交
換器４４で温度上昇した給水は高圧節炭器１７出口に合
流する。The heat recovery system of the precooler will be described. The precooler 31 is divided into a high temperature side heat exchanger 43 and a low temperature side heat exchanger 44. High temperature side heat exchanger 43
Is supplied with the steam that has passed through the medium-pressure evaporator 15 and the medium-pressure superheater and the mixed steam of the high-pressure steam turbine 4 outlet steam.
The steam whose temperature has risen due to heat exchange with the cooling air in the high temperature section 33 in the high temperature side heat exchanger 43 joins the outlet of the primary reheater. The low temperature side heat exchanger 44 is branched from the outlet of the medium pressure economizer 13, and the feed water whose pressure is increased by the supply pump 29 is introduced. The feed water whose temperature has risen in the low temperature side heat exchanger 44 joins the outlet of the high pressure economizer 17.
【００３５】本実施例では高圧蒸気タービン４出口蒸気
は１次再熱器２２と高温側熱交換器４３に分配され温度
調節器３７手前で合流している。すなわち高温側熱交換
器４３に蒸気を分岐させた分だけ１次再熱器２２に供給
される蒸気流量が減少するため、１次再熱器２２での熱
回収量が減少する事により１次再熱器２２を通過した排
ガス温度が上昇し高圧蒸発器２０での蒸発量が増加す
る。すなわち蒸気タービンの出力が増加してプラント効
率が上昇する。In the present embodiment, the high pressure steam turbine 4 outlet steam is distributed to the primary reheater 22 and the high temperature side heat exchanger 43 and merges before the temperature controller 37. That is, since the flow rate of steam supplied to the primary reheater 22 is reduced by the amount of steam branched to the high temperature side heat exchanger 43, the amount of heat recovered in the primary reheater 22 is reduced, and The temperature of the exhaust gas passing through the reheater 22 rises and the amount of evaporation in the high pressure evaporator 20 increases. That is, the output of the steam turbine is increased and the plant efficiency is increased.
【００３６】高温側熱交換器４３を通過した冷却空気は
高温側熱交換器４３に供給された蒸気温度以下には下が
らず、十分に冷却空気温度の低減がなされていないこと
が有り得る。本実施例では低温側熱交換器４４を設けて
温度の低い冷媒を供給しさらに冷却空気温度を下げてい
る。これによりブースト圧縮機３２の動力が低減され、
ガスタービン高温部３３冷却の面からも有利となる。The cooling air that has passed through the high temperature side heat exchanger 43 does not fall below the temperature of the steam supplied to the high temperature side heat exchanger 43, and it is possible that the cooling air temperature has not been sufficiently reduced. In this embodiment, a low temperature side heat exchanger 44 is provided to supply a low temperature refrigerant to further lower the cooling air temperature. This reduces the power of the boost compressor 32,
It is also advantageous in terms of cooling the high temperature part 33 of the gas turbine.
【００３７】本実施例では中圧節炭器１３出口給水は高
圧節炭器１７と低温側熱交換器４４に分配され高圧節炭
器１７出口で合流している。すなわち低温側熱交換器４
４に給水を分岐させた分だけ高圧節炭器１７に供給され
る給水量が減少するため、高圧節炭器１７を通過した排
ガス温度が上昇し中圧蒸発器１５での蒸発量が増加す
る。すなわち蒸気タービンの出力が増加してプラント効
率が上昇する。In this embodiment, the feed water at the outlet of the medium pressure economizer 13 is distributed to the high pressure economizer 17 and the low temperature side heat exchanger 44 and joins at the exit of the high pressure economizer 17. That is, the low temperature side heat exchanger 4
Since the amount of water supplied to the high-pressure economizer 17 is reduced by the amount of branching the water supply to 4, the temperature of the exhaust gas that has passed through the high-pressure economizer 17 rises and the amount of evaporation in the medium-pressure evaporator 15 increases. . That is, the output of the steam turbine is increased and the plant efficiency is increased.
【００３８】また、圧縮機吐出空気温度は圧力比２５程
度で５００℃レベル、一方、２次再熱器出口蒸気温度は
５３８℃から５９３℃レベル、１次再熱器出口蒸気温度
レベルは４００℃から５００℃レベルなので、高温側熱
交換器４３出口蒸気は温度のマッチングのとれる１次再
熱器出口に回収している。Further, the compressor discharge air temperature is at a pressure ratio of about 25 at the 500 ° C. level, while the secondary reheater outlet steam temperature is at 538 ° C. to 593 ° C. and the primary reheater outlet steam temperature level is at 400 ° C. Since the temperature is in the range of 500 ° C. to 500 ° C., the high temperature side heat exchanger 43 outlet steam is recovered at the primary reheater outlet where the temperature can be matched.
【００３９】本発明のもう一つの例が図２に示されてい
る。この実施例が図１の実施例と異なるのは高温側熱交
換器４３へ高圧蒸発器２０からの蒸気を供給し、熱回収
した蒸気を高圧１次過熱器２１出口に回収している点で
ある。本実施例においても図１の実施例と同様に高圧蒸
気発生量が増加し、プラント効率が上昇する。本実施例
においても、高温側熱交換器４３出口蒸気を温度のマッ
チングのとれる高圧１次過熱器出口に回収している。Another example of the present invention is shown in FIG. This embodiment is different from the embodiment of FIG. 1 in that the steam from the high pressure evaporator 20 is supplied to the high temperature side heat exchanger 43, and the heat recovered steam is recovered at the outlet of the high pressure primary superheater 21. is there. Also in this embodiment, as in the embodiment of FIG. 1, the amount of high-pressure steam generated increases and the plant efficiency rises. Also in this embodiment, the high temperature side heat exchanger 43 outlet steam is recovered to the outlet of the high pressure primary superheater capable of matching the temperature.
【００４０】本発明の他の実施例を図３に示す。本実施
例が図１の実施例と異なるのは低温側熱交換器４４へ中
圧ポンプ２６出口の給水を供給し、熱回収した給水を中
圧節炭器１３出口に回収している点である。本実施例に
おいてはプリクーラ３１に供給される冷媒は排熱回収ボ
イラ９の中圧系統であり、プリクーラ３１を通過する冷
却空気の圧力よりも低く設定することができる。すなわ
ち高温側熱交換器４３若しくは低温側熱交換器４４にク
ラックが生じた場合、冷却空気が蒸気若しくは給水にリ
ークするので、後流に位置するブースト圧縮機３２への
水混入による損傷を防止でき、運転の信頼性が向上す
る。Another embodiment of the present invention is shown in FIG. The present embodiment is different from the embodiment of FIG. 1 in that the feed water at the outlet of the intermediate pressure pump 26 is supplied to the low temperature side heat exchanger 44, and the recovered water is recovered at the outlet of the intermediate pressure economizer 13. is there. In the present embodiment, the refrigerant supplied to the precooler 31 is the medium pressure system of the exhaust heat recovery boiler 9, and can be set lower than the pressure of the cooling air passing through the precooler 31. That is, when a crack occurs in the high temperature side heat exchanger 43 or the low temperature side heat exchanger 44, the cooling air leaks to the steam or the water supply, so that damage to the boost compressor 32 located downstream can be prevented. , Driving reliability is improved.
【００４１】本発明の他の実施例を図４に示す。本実施
例が図１の実施例と異なるのは低温側熱交換器４４で温
度上昇した給水を燃料加熱器４５に供給し、燃料４２に
熱回収している点である。本実施例によれば、燃料加熱
による温度上昇分だけ燃焼器２に供給する燃料量を少な
くする事ができるため、プラント効率は上昇する。燃料
の温度は給水や蒸気の温度に比べても十分に温度が低い
ため、低温熱回収に効果的でかつ回収熱量が燃料量の低
減に直接的に作用するので最もプラント効率向上効果が
大きい。Another embodiment of the present invention is shown in FIG. The present embodiment differs from the embodiment of FIG. 1 in that the feed water whose temperature has risen in the low temperature side heat exchanger 44 is supplied to the fuel heater 45 and heat is recovered in the fuel 42. According to the present embodiment, the amount of fuel supplied to the combustor 2 can be reduced by the amount of temperature increase due to heating of the fuel, so that the plant efficiency is increased. Since the temperature of fuel is sufficiently lower than the temperatures of feed water and steam, it is effective for low-temperature heat recovery and the amount of recovered heat directly affects the reduction of the amount of fuel, so the effect of improving plant efficiency is greatest.
【００４２】本発明の他の実施例を図５に示す。本実施
例が図１の実施例と異なるのは高温側熱交換器４３を蒸
発器としている点である。低温側熱交換器４４へは供給
ポンプ２９で昇圧された給水が導かれる。低温側熱交換
器４４で温度上昇した給水はドラム４６に供給され高温
側熱交換器４３で蒸発して高圧１次過熱器２１入口に供
給される。本実施例においても図１の実施例と同様に高
圧蒸気発生量が増加し、プラント効率が上昇する。Another embodiment of the present invention is shown in FIG. The present embodiment differs from the embodiment of FIG. 1 in that the high temperature side heat exchanger 43 is an evaporator. The feed water whose pressure is increased by the feed pump 29 is guided to the low temperature side heat exchanger 44. The feed water whose temperature has risen in the low temperature side heat exchanger 44 is supplied to the drum 46, evaporated in the high temperature side heat exchanger 43 and supplied to the high pressure primary superheater 21 inlet. Also in this embodiment, as in the embodiment of FIG. 1, the amount of high-pressure steam generated increases and the plant efficiency rises.
【００４３】本発明の他の実施例を図６に示す。排熱回
収ボイラ９から高温側熱交換器４３への冷媒供給配管上
に流量調節弁４８を設置して、高温側熱交換器４３から
排熱回収ボイラ９へ回収される冷媒の温度Ｔ1と排熱回
収ボイラ側の合流前温度Ｔ2を検出し、Ｔ1とＴ2の温度
差が熱応力が問題とならない許容温度差以内に納まる様
に流量調節弁４８で高温側熱交換器４３への冷媒流入量
を調整する。Another embodiment of the present invention is shown in FIG. A flow rate control valve 48 is installed on the refrigerant supply pipe from the exhaust heat recovery boiler 9 to the high temperature side heat exchanger 43 to set the temperature T 1 of the refrigerant recovered from the high temperature side heat exchanger 43 to the exhaust heat recovery boiler 9. Detect the pre-combining temperature T 2 on the exhaust heat recovery boiler side and use the flow rate control valve 48 to the high temperature side heat exchanger 43 so that the temperature difference between T 1 and T 2 is within the allowable temperature difference where thermal stress does not matter. Adjust the amount of refrigerant inflow.
【００４４】図７に起動から定格運転に至るまでの排熱
回収ボイラ入口排ガスとプリクーラ入口空気の温度、お
よびＧＴ回転数、プラント出力変化を示す。この図から
Ａ点からＢ点の間ではプリクーラ入口空気温度が排ガス
温度よりも高く、定格運転時とは温度関係が逆転してい
る。FIG. 7 shows the temperature of the exhaust heat recovery boiler inlet exhaust gas and the precooler inlet air, the GT rotation speed, and the plant output change from startup to rated operation. From this figure, the air temperature at the precooler inlet is higher than the exhaust gas temperature between points A and B, and the temperature relationship is reversed from that during the rated operation.
【００４５】もし仮に流量調節弁４８により分岐点４７
での分配量を制御しなかったとすれば、定格運転時に合
流点４９の温度差が許容値以内であったとしても、Ａ点
からＢ点付近ではプリクーラの回収熱量が排ガスからの
回収熱量よりも相対的に増加するため高温側熱交換器４
３出口温度Ｔ1が排熱回収ボイラの合流前温度Ｔ2よりも
高温となりその温度差が許容値を超えてしまう可能性が
ある。ゆえに、このような場合は流量調節弁４８の開度
を大きくし高温側熱交換器４３への分配割合を増加させ
ることにより高温側熱交換器４３出口温度の上昇を抑制
しＴ１とＴ２の温度差を許容値内におさえることができ
る。If the flow control valve 48 is used, a branch point 47
Assuming that the distribution amount at the time of rated operation is not controlled, even if the temperature difference at the confluence point 49 is within the allowable value at the time of rated operation, the recovered heat amount of the precooler is closer than the recovered heat amount from the exhaust gas from the point A to the point B The heat exchanger 4 on the high temperature side increases relatively
3 The outlet temperature T 1 becomes higher than the pre-merge temperature T 2 of the exhaust heat recovery boiler, and the temperature difference may exceed the allowable value. Therefore, in such a case, by increasing the opening degree of the flow rate control valve 48 and increasing the distribution ratio to the high temperature side heat exchanger 43, the rise of the high temperature side heat exchanger 43 outlet temperature is suppressed and the temperatures of T1 and T2 are suppressed. The difference can be kept within tolerance.
【００４６】本発明の他の実施例を図８に示す。本実施
例が図６の実施例と異なるのは合流点４９の過大な温度
差を抑制するために高温側熱交換器４３から合流点４９
に向かう配管上に温度調節器５１を設置した点である。
高温側熱交換器４３から排熱回収ボイラ９へ回収される
冷媒の温度Ｔ1と排熱回収ボイラ側の合流前温度Ｔ2を検
出し、Ｔ１とＴ２の温度差が熱応力が問題とならない許
容温度差以内に納まる様に水若しくは蒸気を供給流量調
整弁５０を通して温度調節器５１に供給する。Another embodiment of the present invention is shown in FIG. This embodiment differs from the embodiment of FIG. 6 in that the high temperature side heat exchanger 43 is connected to the confluence point 49 in order to suppress an excessive temperature difference at the confluence point 49.
This is the point where the temperature controller 51 is installed on the pipe heading toward.
The temperature T 1 of the refrigerant recovered from the high temperature side heat exchanger 43 to the exhaust heat recovery boiler 9 and the pre-merging temperature T 2 on the exhaust heat recovery boiler side are detected, and the temperature difference between T1 and T2 does not cause a thermal stress. Water or steam is supplied to the temperature controller 51 through the supply flow rate adjusting valve 50 so as to be within the allowable temperature difference.
【００４７】また、本実施例ではブースト圧縮機３２の
入口およびガスタービン高温部３３に供給する冷却空気
温度を設定温度に保つようにプリクーラ３１の出口空気
温度Ｔ3を検出し、流量調整弁５２により低温側熱交換
器４４への冷媒供給量を調節する。Further, in this embodiment, the outlet air temperature T 3 of the precooler 31 is detected so that the temperature of the cooling air supplied to the inlet of the boost compressor 32 and the high temperature portion of the gas turbine 33 is kept at the set temperature, and the flow rate adjusting valve 52 is detected. The refrigerant supply amount to the low temperature side heat exchanger 44 is adjusted by.
【００４８】さらに、本実施例では低温側熱交換器４４
出口に再循環ポンプ５３を設置している。低温側熱交換
器４４出口の温度上昇した冷媒を低温側熱交換器４４入
口に合流することにより低温側熱交換器４４入口冷媒温
度を上げてプリクーラ出口空気の露結を防止することが
できる。すなわち、ブースト圧縮機３２への水滴の流入
によるブースト圧縮機３２の損傷を防止することができ
るので信頼性が向上する。Further, in this embodiment, the low temperature side heat exchanger 44
A recirculation pump 53 is installed at the outlet. By combining the refrigerant whose temperature has risen at the outlet of the low temperature side heat exchanger 44 with the inlet of the low temperature side heat exchanger 44, it is possible to raise the temperature of the refrigerant at the inlet of the low temperature side heat exchanger 44 and prevent condensation of the precooler outlet air. That is, damage to the boost compressor 32 due to the inflow of water droplets into the boost compressor 32 can be prevented, so that reliability is improved.
【００４９】本発明の他の実施例を図９に示す。本実施
例ではガスタービン排ガス温度Ｔを検出し、排ガス温度
Ｔに応じてブースト圧縮機３２の駆動モータ５４の回転
数を制御している。正常な運転状態では排ガス温度Ｔは
ガスタービン高温部３３の温度にリンクしているので、
排ガス温度が上昇するとガスタービン高温部３３も温度
上昇するので駆動モータ５４の回転数を上げて冷却空気
量を増加して必要な流量を確保する。本運転法によりガ
スタービン高温部３３に適正な冷却空気量を供給するこ
とができる。Another embodiment of the present invention is shown in FIG. In this embodiment, the gas turbine exhaust gas temperature T is detected, and the rotation speed of the drive motor 54 of the boost compressor 32 is controlled according to the exhaust gas temperature T. Since the exhaust gas temperature T is linked to the temperature of the gas turbine high temperature section 33 in a normal operating state,
When the temperature of the exhaust gas rises, the temperature of the gas turbine high temperature section 33 also rises. Therefore, the rotational speed of the drive motor 54 is increased to increase the amount of cooling air to secure the required flow rate. With this operation method, an appropriate amount of cooling air can be supplied to the high temperature part 33 of the gas turbine.
【００５０】本発明の他の実施例を図１０に示す。本実
施例ではガスタービン回転数Ｎおよびプラント出力Ｗを
検出し、スタービン回転数Ｎおよびプラント出力Ｗに応
じてブースト圧縮機３２の駆動モータ５４の回転数を制
御している。大気の状態によっては若干の変動はあるも
のの、正常な運転状態では図７に示しているように、ガ
スタービン回転数とプラント出力を知ることができれば
排ガス温度を知ることができる。すなわち、ガスタービ
ン回転数Ｎおよびプラント出力Ｗから排ガス温度を介し
てガスタービン高温部３３の温度を予測し、駆動モータ
５４の回転数を制御する。本運転法により適正な冷却空
気量を供給することができる。Another embodiment of the present invention is shown in FIG. In this embodiment, the gas turbine rotation speed N and the plant output W are detected, and the rotation speed of the drive motor 54 of the boost compressor 32 is controlled according to the turbine rotation speed N and the plant output W. Although there are some fluctuations depending on the atmospheric conditions, under normal operating conditions, the exhaust gas temperature can be known if the gas turbine speed and plant output can be known, as shown in FIG. 7. That is, the temperature of the gas turbine high temperature portion 33 is predicted from the gas turbine rotation speed N and the plant output W via the exhaust gas temperature, and the rotation speed of the drive motor 54 is controlled. With this operation method, an appropriate amount of cooling air can be supplied.
【００５１】本発明の他の実施例を図１１に示す。本実
施例ではガスタービン排ガス温度Ｔを検出し、排ガス温
度Ｔに応じて冷却空気供給量調節弁５５を制御してい
る。正常な運転状態では、排ガス温度Ｔはガスタービン
高温部３３の温度にリンクしているので、排ガス温度が
上昇するとガスタービン高温部３３も温度上昇するの
で、冷却空気供給量調節弁５５の弁開度を大きくして冷
却空気量を増加する。本運転法によってもガスタービン
高温部３３に適正な冷却空気量を供給することができ
る。Another embodiment of the present invention is shown in FIG. In this embodiment, the gas turbine exhaust gas temperature T is detected, and the cooling air supply amount adjusting valve 55 is controlled according to the exhaust gas temperature T. In a normal operating state, the exhaust gas temperature T is linked to the temperature of the gas turbine high temperature section 33, and therefore, when the exhaust gas temperature rises, the temperature of the gas turbine high temperature section 33 also rises, so the cooling air supply control valve 55 is opened. To increase the cooling air volume. This operation method can also supply an appropriate amount of cooling air to the high temperature part 33 of the gas turbine.
【００５２】本発明の他の実施例を図１２に示す。本実
施例が図１１の実施例と異なる点はブースト圧縮機３２
の駆動源をガスタービン回転軸５６としている点であ
る。ガスタービン軸駆動とすることによってガスタービ
ンが回転している間は常にブースト圧縮機を稼働するこ
とができるので停電によるブースト圧縮機の停止の恐れ
も無く信頼性が向上する。Another embodiment of the present invention is shown in FIG. This embodiment is different from the embodiment of FIG. 11 in that the boost compressor 32
The drive source is the gas turbine rotating shaft 56. By driving the gas turbine shaft, the boost compressor can always be operated while the gas turbine is rotating, so that there is no fear of stopping the boost compressor due to a power failure and reliability is improved.
【００５３】本発明の他の実施例を図１３に示す。ガス
タービン高温部３３から何らかの原因で許容値以上のリ
ークが発生した場合、燃焼器２に回収される冷却空気量
は減少する。回収される冷却空気量の減少によりタービ
ン第１段静翼入口燃焼ガス量も減少し第１段静翼入口圧
力が低下する。第１段静翼入口圧力の低下に応じて回収
冷却空気圧力Ｐも低下する。Another embodiment of the present invention is shown in FIG. When the gas turbine high temperature section 33 leaks more than the allowable value for some reason, the amount of cooling air recovered in the combustor 2 decreases. Due to the reduction in the amount of recovered cooling air, the combustion gas amount in the turbine first stage vane inlet also decreases and the pressure in the first stage vane inlet decreases. The recovered cooling air pressure P also decreases as the first stage stationary blade inlet pressure decreases.
【００５４】第１段静翼入口圧力の低下によるプラント
出力が低下を防止するために、燃料量が増加する。回収
される冷却空気量が減少し供給空気量が少なくなったに
もかかわらず燃料量が増加すると、燃焼温度が上昇しガ
スタービン高温部３３を損傷することになる。クローズ
ド空気冷却ガスタービンでは冷却空気のリークにより燃
焼温度が上昇しても、リーク空気がガス温度を低下させ
るので排ガス温度Ｔ１の上昇により燃焼温度の上昇を検
出できない可能性がある。The amount of fuel is increased in order to prevent the plant output from decreasing due to the decrease in the inlet pressure of the first stage vane. If the amount of fuel is increased even though the amount of recovered cooling air is reduced and the amount of supplied air is reduced, the combustion temperature rises and the gas turbine high temperature part 33 is damaged. In the closed air cooling gas turbine, even if the combustion temperature rises due to the leakage of the cooling air, the leak air lowers the gas temperature, and therefore the rise in exhaust gas temperature T1 may not detect the rise in combustion temperature.
【００５５】図１４に示すようにクローズド冷却空気が
リークすると前記の理由で燃料流量Ｇの増加、回収空気
圧力すなわち燃焼器圧力Ｐの低下という状態になるの
で、燃料流量Ｇと燃焼器圧力Ｐを監視することによりク
ローズド冷却空気のリークを検出することができる。As shown in FIG. 14, when the closed cooling air leaks, the fuel flow rate G increases and the recovered air pressure, that is, the combustor pressure P decreases due to the above reasons. By monitoring, the leak of the closed cooling air can be detected.
【００５６】すなわち、燃料流量Ｇ、燃焼器圧力Ｐ、排
ガス温度Ｔ１、プラント出力Ｗを検出し、正常運転時に
は排ガス温度Ｔ１が制限値を超えない範囲でプラント出
力Ｗが設定値となるよに燃料流量調節弁５８により燃料
供給量を調節する。ただし、燃料量Ｇが単位時間内に許
容値以上供給された場合、もしくは燃焼器圧力Ｐが単位
時間内に許容値以上温度低下が生じた場合は、クローズ
ド冷却空気が許容値以上にリークしている可能性がある
として燃料流量調節弁制御装置５７からの信号により燃
料流量調節弁５８を閉としてプラントを停止する。That is, the fuel flow rate G, the combustor pressure P, the exhaust gas temperature T1, and the plant output W are detected, and the plant output W reaches the set value within the range where the exhaust gas temperature T1 does not exceed the limit value during normal operation. The fuel supply amount is adjusted by the flow rate adjusting valve 58. However, if the fuel amount G is supplied within the permissible value within the unit time, or if the combustor pressure P drops within the per unit time within the permissible value, the closed cooling air leaks above the permissible value. Since there is a possibility that the fuel flow rate control valve 57 is present, the fuel flow rate control valve 58 is closed by the signal from the fuel flow rate control valve controller 57 to stop the plant.
【００５７】本運転方法により、クロース゛ド冷却空気
がリークしたとしてもガスタービン高温部を損傷するこ
と無く安全にプラントを停止することができる。According to this operation method, even if the closed cooling air leaks, the plant can be safely stopped without damaging the high temperature part of the gas turbine.
【００５８】以上説明してきたようにこのように形成さ
れたクローズド空気冷却ガスタービンシステムである
と、プリクーラの熱交換器を複数設け、プリクーラ上流
側熱交換器には温度の高い冷媒を給し温度の高い箇所に
回収することにより高効率化を図ると同時に、十分に冷
却空気温度が下らない分は下流側の熱交換器に低温の冷
媒を供給することによりガスタービン高温部の冷却効果
を高めているので、コンハ゛インドサイクル高効率観点
からのプリクーラ排熱回収系統の最適化と、ガスタービ
ン高温部冷却上の観点からのプリクーラ出口空気温度低
減化を満たすことができる。As described above, in the closed air cooling gas turbine system formed as described above, a plurality of heat exchangers of the precooler are provided, and a high temperature refrigerant is supplied to the heat exchanger upstream of the precooler. At the same time as improving the efficiency by collecting it in a high temperature area, the cooling effect of the high temperature part of the gas turbine can be improved by supplying the low temperature refrigerant to the heat exchanger on the downstream side to the extent that the cooling air temperature does not fall sufficiently. Therefore, it is possible to satisfy the optimization of the precooler exhaust heat recovery system from the viewpoint of high efficiency of the combined cycle and the reduction of the precooler outlet air temperature from the viewpoint of cooling the high temperature part of the gas turbine.
【００５９】本発明によれば、ブースト圧縮機の駆動装
置を電気モータとし、前記ガスタービンの排気ガス温度
またはガスタービン回転数に応じてブースト圧縮機の回
転数を変化させているので、ガスタービン高温部の冷却
に必要な冷却空気量を調節することができる。According to the present invention, the drive device of the boost compressor is an electric motor, and the rotation speed of the boost compressor is changed according to the exhaust gas temperature of the gas turbine or the rotation speed of the gas turbine. The amount of cooling air required for cooling the high temperature part can be adjusted.
【００６０】本発明によれば、ガスタービンの排気ガス
温度またはガスタービン回転数に応じて冷却空気供給配
管上に設けた空気流量調節装置を設けているので、ガス
タービン高温部の冷却に必要な冷却空気量を調節するこ
とができる。According to the present invention, since the air flow rate adjusting device provided on the cooling air supply pipe is provided according to the exhaust gas temperature of the gas turbine or the gas turbine rotation speed, it is necessary to cool the high temperature part of the gas turbine. The amount of cooling air can be adjusted.
【００６１】本発明によれば、排熱回収ボイラからプリ
クーラへの冷媒供給配管またはプリクーラから排熱回収
ボイラへの冷媒回収配管上にプリクーラへの冷媒流量を
調整する装置を設け、プリクーラ出口空気温度を計測し
その温度が設定値となるようにプリクーラ冷媒流量調整
装置によりプリクーラへの冷媒供給流量を調整している
ので、様々な運転状態でプリクーラ出口冷却空気温度を
設定値に維持することができる。According to the present invention, a device for adjusting the refrigerant flow rate to the precooler is provided on the refrigerant supply pipe from the exhaust heat recovery boiler to the precooler or on the refrigerant recovery pipe from the precooler to the exhaust heat recovery boiler, and the precooler outlet air temperature is adjusted. Because the precooler refrigerant flow rate adjustment device adjusts the refrigerant supply flow rate to the precooler so that the temperature becomes the set value, it is possible to maintain the precooler outlet cooling air temperature at the set value in various operating conditions. .
【００６２】本発明によれば、排熱回収ボイラからプリ
クーラへの供給配管またはプリクーラから排熱回収ボイ
ラへの回収配管上にプリクーラへの供給冷媒流量を調整
する装置を設け、回収配管と排熱回収ボイラ配管との合
流点で温度差が許容値以下となるようにプリクーラ供給
流量調整装置によりプリクーラへの冷媒流量を調整して
いるので、プリクーラで使用され温度上昇した冷媒を回
収するとき、冷媒の温度と回収先の温度との差を許容値
内におさえて熱応力を低減することができる。According to the present invention, a device for adjusting the flow rate of the refrigerant supplied to the precooler is provided on the supply pipe from the exhaust heat recovery boiler to the precooler or the recovery pipe from the precooler to the exhaust heat recovery boiler. Since the refrigerant flow rate to the precooler is adjusted by the precooler supply flow rate adjustment device so that the temperature difference at the confluence point with the recovery boiler pipe is below the allowable value, the refrigerant used when the precooler and the temperature rise are recovered. It is possible to reduce the thermal stress by keeping the difference between the temperature of 1 and the temperature of the recovery destination within an allowable value.
【００６３】本発明によれば、プリクーラから排熱回収
ボイラへの回収配管上に蒸気若しくは水を混入して排熱
回収ボイラへの回収温度を調整する装置を設け、回収配
管と排熱回収ボイラ配管との合流点で温度差が許容値以
下となるように回収温度調整装置により蒸気若しくは水
の混入量を変化させているので、プリクーラで使用され
温度上昇した冷媒を回収するとき、冷媒の温度と回収先
の温度との差を許容値内におさえて熱応力を低減するこ
とができる。According to the present invention, the recovery pipe and the exhaust heat recovery boiler are provided with a device for adjusting the recovery temperature of the exhaust heat recovery boiler by mixing steam or water on the recovery pipe from the precooler to the exhaust heat recovery boiler. Since the amount of steam or water mixed is changed by the recovery temperature adjustment device so that the temperature difference at the confluence with the pipe is less than the allowable value, the temperature of the refrigerant used when recovering the temperature of the refrigerant used in the precooler is recovered. The thermal stress can be reduced by keeping the difference between the recovery temperature and the recovery temperature within an allowable value.
【００６４】本発明によれば、燃料流量の変動または回
収空気圧力を監視しているので、冷却空気のリークを検
知することができる。According to the present invention, since the fluctuation of the fuel flow rate or the recovered air pressure is monitored, the leakage of the cooling air can be detected.
【００６５】[0065]
【発明の効果】以上説明してきたように本発明によれ
ば、プリクーラの排熱がプラントに有効に回収され、高
効率化を図ることが可能であり、さらにクローズド空気
冷却ガスタービンの様々な運転モードにおいて適正な運
転状態を保ち信頼性の向上を図ることが可能なこの種の
空気冷却ガスタービンシステムを得ることができる。As described above, according to the present invention, the exhaust heat of the precooler can be effectively recovered in the plant, the efficiency can be improved, and various operations of the closed air cooling gas turbine can be achieved. In this mode, it is possible to obtain an air-cooled gas turbine system of this type capable of maintaining an appropriate operating state and improving reliability.
【図１】本発明のクローズド空気冷却ガスタービンシス
テムの一実施例を示す系統図である。FIG. 1 is a system diagram showing an embodiment of a closed air cooling gas turbine system of the present invention.
【図２】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 2 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図３】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 3 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図４】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 4 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図５】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 5 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図６】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 6 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図７】起動から定格に至るガスタービン特性図であ
る。FIG. 7 is a gas turbine characteristic diagram from start to rating.
【図８】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 8 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図９】本発明のクローズド空気冷却ガスタービンシス
テムの他の実施例を示す系統図である。FIG. 9 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図１０】本発明のクローズド空気冷却ガスタービンシ
ステムの他の実施例を示す系統図である。FIG. 10 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図１１】本発明のクローズド空気冷却ガスタービンシ
ステムの他の実施例を示す系統図である。FIG. 11 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図１２】本発明のクローズド空気冷却ガスタービンシ
ステムの他の実施例を示す系統図である。FIG. 12 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図１３】本発明のクローズド空気冷却ガスタービンシ
ステムの他の実施例を示す系統図である。FIG. 13 is a system diagram showing another embodiment of the closed air cooling gas turbine system of the present invention.
【図１４】クローズド冷却空気リーク時のガスタービン
特性図である。FIG. 14 is a gas turbine characteristic diagram at the time of closed cooling air leak.
４…高圧蒸気タービン、１３…中圧節炭器、１５…中圧
蒸発器、１７…高圧節炭器、２０…高圧蒸発器、２２…
１次再熱器、３２…ブースト圧縮機、３３…ガスタービ
ン高温部、３７…温度調節器、４３…高温側熱交換器、
４４…低温側熱交換器、２１…高圧１次過熱器、９…排
熱回収ボイラ、２６…中圧ポンプ、３１…プリクーラ、
２…燃焼器、４２…燃料、４５…燃料加熱器、２９…供
給ポンプ、４６…ドラム、４７…分岐点、４８…流量調
節弁、４９…合流点、５０…供給流量調節弁、５１…温
度調節器、５２…流量調整弁、５３…再循環ポンプ、５
４…駆動モータ、５５…冷却空気供給流量調節弁、５６
…ガスタービン回転軸、５７…燃料流量調整弁制御装
置、５８…燃料流量調節弁。4 ... High-pressure steam turbine, 13 ... Medium-pressure economizer, 15 ... Medium-pressure evaporator, 17 ... High-pressure economizer, 20 ... High-pressure evaporator, 22 ...
Primary reheater, 32 ... Boost compressor, 33 ... Gas turbine high temperature part, 37 ... Temperature controller, 43 ... High temperature side heat exchanger,
44 ... Low temperature side heat exchanger, 21 ... High pressure primary superheater, 9 ... Exhaust heat recovery boiler, 26 ... Medium pressure pump, 31 ... Precooler,
2 ... Combustor, 42 ... Fuel, 45 ... Fuel heater, 29 ... Supply pump, 46 ... Drum, 47 ... Branch point, 48 ... Flow control valve, 49 ... Confluence point, 50 ... Supply flow control valve, 51 ... Temperature Regulator, 52 ... Flow control valve, 53 ... Recirculation pump, 5
4 ... Drive motor, 55 ... Cooling air supply flow rate control valve, 56
... Gas turbine rotating shaft, 57 ... Fuel flow rate adjusting valve control device, 58 ... Fuel flow rate adjusting valve.
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ Ｆ０２Ｃ 7/18 Ｆ０２Ｃ 7/18 Ｚ (72)発明者 川池 和彦 茨城県日立市大みか町七丁目２番１号 株式会社日立製作所 電力・電機開発本 部内 (72)発明者 池口 隆 茨城県日立市大みか町七丁目２番１号 株式会社日立製作所 電力・電機開発本 部内 (72)発明者 樋口 眞一 茨城県日立市大みか町七丁目２番１号 株式会社日立製作所 電力・電機開発本 部内 (72)発明者 野田 雅美 茨城県日立市大みか町七丁目２番１号 株式会社日立製作所 電力・電機開発本 部内 (56)参考文献 特開 平６−212910（ＪＰ，Ａ) 特開 平４−76205（ＪＰ，Ａ) 特開 平８−270459（ＪＰ，Ａ) 特開 平７−4263（ＪＰ，Ａ) 特開 平５−321610（ＪＰ，Ａ) 特開 平２−30904（ＪＰ，Ａ) 特開 昭54−82518（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) F01K 23/10 F01K 23/14 F02C 6/18 F02C 7/18 ─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. 7 Identification code FI F02C 7/18 F02C 7/18 Z (72) Inventor Kazuhiko Kawaike 7-2-1, Omika-cho, Hitachi-shi, Ibaraki Hitachi, Ltd. Electric Power & Electric Machinery Development Headquarters (72) Inventor Takashi Ikeguchi 7-2-1 Omika-cho, Hitachi City, Ibaraki Hitachi Ltd. Electric Power & Electric Machinery Development Headquarters (72) Inventor Shinichi Higuchi 7-chome, Omika-cho, Ibaraki Prefecture 2-1 Hitachi Ltd., Power & Electrical Development Division (72) Inventor Masami Noda 7-2-1 Omika-cho, Hitachi City, Hitachi, Ibaraki Prefecture Hitachi, Ltd. Power & Electrical Development Division (56) References JP-A-6-212910 (JP, A) JP-A-4-76205 (JP, A) JP-A-8-270459 (JP, A) JP-A-7-4263 (JP, A) JP-A -321610 (JP, A) JP flat 2-30904 (JP, A) JP Akira 54-82518 (JP, A) (58 ) investigated the field (Int.Cl. 7, DB name) F01K 23/10 F01K 23/14 F02C 6/18 F02C 7/18
Claims (5)
ブースト圧縮機により昇圧した空気をガスタービン高温
部へ冷却媒体として供給し、前記ガスタービン高温部を
冷却後の空気を燃焼空気として燃焼器に回収するクロー
ズド空気冷却ガスタービンと、前記クローズド空気冷却
ガスタービンの排ガスにより蒸気を発生する排熱回収ボ
イラと、前記排熱回収ボイラで発生した蒸気を動力に変
換する蒸気タービンとを備えたコンバインド発電プラン
トにおいて、 前記クローズド空気冷却ガスタービンの前記プリクーラ
は、それぞれ冷却媒体の温度が異なる複数の熱交換器を
備え、前記プリクーラの上流側熱交換器には他の熱交換
器より温度の高い冷媒が供給され、かつ、温度の高い箇
所に回収されるように形成したことを特徴とするコンバ
インド発電プラント。1. A compressor discharge air is cooled by a precooler,
High temperature gas turbine high temperature air boosted by boost compressor
As a cooling medium to the high temperature part of the gas turbine.
And closed air cooling gas turbine for recovering the air after cooling the combustor as combustion air, the exhaust heat recovery boiler for generating steam by exhaust gas of the closed air cooling <br/> gas turbine, generated in the exhaust heat recovery boiler And a steam turbine for converting the generated steam into power, the precooler of the closed air-cooled gas turbine.
Is provided with a plurality of heat exchangers have different temperatures of the respective cooling medium, other heat exchange upstream heat exchanger of said precooler
A combined power generation plant, characterized in that a refrigerant having a higher temperature is supplied from a container and is collected at a location having a higher temperature.
として、圧縮機吐出空気をプリクーラで冷却しブースト
圧縮機にて昇圧した空気を用い、冷却後の空気を燃焼空
気として燃焼器に回収するクローズド空気冷却ガスター
ビン、クローズド空気冷却ガスタービンの排ガスにより
蒸気を発生する排熱回収ボイラと、前記排熱回収ボイラ
で発生した蒸気を動力に変換する蒸気タービンとを備え
たコンバインド発電プラントにおいて、 前記クローズド空気冷却ガスタービンの前記プリクーラ
に複数の熱交換器を備えるとともに、前記プリクーラの
冷却媒体として前記排熱回収ボイラからの蒸気と給水の
両方を用い、冷却後の温度上昇した蒸気、給水を再び前
記排熱回収ボイラに供給するようにしたことを特徴とす
るコンバインド発電プラント。2. A closed system in which air discharged from a compressor is cooled by a precooler and boosted by a boost compressor is used as a cooling medium for cooling a high temperature part of a gas turbine, and the cooled air is recovered as combustion air in a combustor. air cooling the gas turbine, an exhaust heat recovery boiler for generating steam by the exhaust gas of the closed air cooling gas turbine, in the combined power generation plant with a steam turbine the steam generated by the exhaust heat recovery boiler for converting the power, the closed provided with a plurality of heat exchangers in the precooler of an air cooling gas turbine, both steam and water from the exhaust heat recovery boiler used as a cooling medium of the precooler, the temperature rise steam after cooling, the water supply again the A combined power generation plant characterized by being supplied to an exhaust heat recovery boiler.
として、圧縮機吐出空気をプリクーラで冷却しブースト
圧縮機にて昇圧した空気を用い、冷却後の空気を燃焼空
気として燃焼器に回収するクローズド空気冷却ガスター
ビンと、前記クローズド空気冷却ガスタービンの排ガス
により高圧、中圧、低圧の三種類の圧力の蒸気を発生す
るために節炭器、蒸発器、過熱器を高圧、中圧、低圧蒸
気に対してそれぞれ備え、前記高圧蒸気により駆動した
高圧蒸気タービン出口の蒸気を再熱する再熱器を備えた
排熱回収ボイラと、前記排熱回収ボイラからの蒸気を動
力に変換する蒸気タービンと備えたコンバインド発電プ
ラントにおいて、 前記空気冷却ガスタービンの前記プリクーラに複数の熱
交換器を備えるとともに、前記プリクーラの冷却媒体と
して前記高圧蒸気タービン出口の蒸気と前記排熱回収ボ
イラの中圧節炭器出口給水を昇圧した高圧給水の両方を
用い、プリクーラ冷却後の温度上昇した前記蒸気、給水
をそれぞれ前記再熱器出口と高圧蒸発器入口に供給する
ようにしたことを特徴とするコンバインド発電プラン
ト。3. A closed system in which air discharged from a compressor is cooled by a precooler and boosted by a boost compressor is used as a cooling medium for cooling a high temperature portion of a gas turbine, and the cooled air is recovered as combustion air in a combustor. Air-cooling gas turbine and high-pressure, medium-pressure, low-pressure steam are used to generate steam of three kinds of pressure of high pressure, medium pressure and low pressure by the exhaust gas of the closed air cooling gas turbine. For each, an exhaust heat recovery boiler equipped with a reheater for reheating steam at the outlet of the high pressure steam turbine driven by the high pressure steam, and a steam turbine for converting steam from the exhaust heat recovery boiler into power. in the combined power generation plant with, provided with a plurality of heat exchangers in the precooler of the air cooling gas turbine, a cooling medium of the precooler Using both the steam at the outlet of the high-pressure steam turbine and the high-pressure feed water that has pressurized the outlet water of the medium-pressure economizer of the exhaust heat recovery boiler, the steam and the feed water whose temperature has risen after cooling the precooler are respectively discharged at the reheater outlet. And a high pressure evaporator inlet to supply the combined power plant.
として、圧縮機吐出空気をプリクーラで冷却しブースト
圧縮機にて昇圧した空気を用い、冷却後の空気を燃焼空
気として燃焼器に回収するクローズド空気冷却ガスター
ビンと、前記クローズド空気冷却ガスタービンの排ガス
により高圧、中圧、低圧の三種類の圧力の蒸気を発生す
るために節炭器、蒸発器、過熱器を高圧、中圧、低圧蒸
気に対してそれぞれ備え、前記高圧蒸気により駆動した
高圧蒸気タービン出口の蒸気を再熱する再熱器を備えた
排熱回収ボイラと、前記排熱回収ボイラからの蒸気を動
力に変換する蒸気タービンとを有するコンバインド発電
プラントにおいて、前記クローズド 空気冷却ガスタービンのプリクーラに複
数の熱交換器を備えるとともに、前記プリクーラの冷却
媒体として高圧蒸発器出口の蒸気と前記排熱回収ボイラ
の中圧節炭器出口給水を昇圧した高圧給水の両方を用
い、プリクーラ冷却後の温度上昇した前記蒸気、給水を
それぞれ前記高圧過熱器出口と高圧蒸発器入口に供給す
るようにしたことを特徴とするコンバインド発電プラン
ト。4. A closed system in which air discharged from a compressor is cooled by a precooler and boosted by a boost compressor is used as a cooling medium for cooling a high temperature portion of a gas turbine, and the cooled air is recovered as combustion air in a combustor. Air-cooling gas turbine and high-pressure, medium-pressure, low-pressure steam are used to generate steam of three kinds of pressure of high pressure, medium pressure and low pressure by the exhaust gas of the closed air cooling gas turbine. For each, an exhaust heat recovery boiler equipped with a reheater for reheating steam at the outlet of the high pressure steam turbine driven by the high pressure steam, and a steam turbine for converting steam from the exhaust heat recovery boiler into power. in the combined power generation plant having a, provided with a plurality of heat exchangers precooler of the closed air cooling gas turbine, cooling of the precooler Both the steam at the outlet of the high-pressure evaporator and the high-pressure feed water at the outlet of the medium pressure economizer at the exhaust heat recovery boiler are used as the medium, and the steam and the feed water whose temperature has risen after cooling the precooler are respectively discharged at the outlet of the high-pressure superheater. And a high pressure evaporator inlet to supply the combined power plant.
として、圧縮機吐出空気をプリクーラで冷却しブースト
圧縮機にて昇圧した空気を用い、冷却後の空気を燃焼空
気として燃焼器に回収するクローズド空気冷却ガスター
ビンと、前記クローズド空気冷却ガスタービンの排ガス
により高圧、中圧、低圧の三種類の圧力の蒸気を発生す
るために節炭器、蒸発器、過熱器を高圧、中圧、低圧蒸
気に対してそれぞれ備え、前記高圧蒸気により駆動した
高圧蒸気タービン出口の蒸気を再熱する再熱器を備えた
排熱回収ボイラと、前記排熱回収ボイラからの蒸気を動
力に変換する蒸気タービンとを有するコンバインド発電
プラントにおいて、 前記空気冷却ガスタービンのプリクーラに複数の熱交換
器を備えるとともに、前記プリクーラの冷却媒体として
前記高圧蒸気タービン出口の蒸気と前記排熱回収ボイラ
の低圧節炭器出口給水を昇圧した中圧給水の両方を用
い、プリクーラ冷却後の温度上昇した前記蒸気、給水
を、それぞれ前記再熱器出口と中圧節炭器出口に供給す
るようにしたことを特徴とするコンバインド発電プラン
ト。5. A closed system in which air discharged from a compressor is cooled by a precooler and boosted by a boost compressor is used as a cooling medium for cooling a high temperature part of a gas turbine, and the cooled air is recovered as combustion air in a combustor. Air-cooling gas turbine and high-pressure, medium-pressure, low-pressure steam are used to generate steam of three kinds of pressure of high pressure, medium pressure and low pressure by the exhaust gas of the closed air cooling gas turbine. For each, an exhaust heat recovery boiler equipped with a reheater for reheating steam at the outlet of the high pressure steam turbine driven by the high pressure steam, and a steam turbine for converting steam from the exhaust heat recovery boiler into power. In a combined power generation plant having a plurality of heat exchangers in a precooler of the air-cooled gas turbine, and a cooling medium of the precooler. Using both the steam at the outlet of the high-pressure steam turbine and the intermediate-pressure feed water that has boosted the feed water at the outlet of the low-pressure economizer of the exhaust heat recovery boiler, the steam and the feed water whose temperature has risen after precooler cooling are respectively fed to the reheater outlet. The combined power plant is characterized in that the power is supplied to the outlet of the medium pressure economizer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00036797A JP3431435B2 (en) | 1997-01-06 | 1997-01-06 | Combined power plant and closed air-cooled gas turbine system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00036797A JP3431435B2 (en) | 1997-01-06 | 1997-01-06 | Combined power plant and closed air-cooled gas turbine system |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002277403A Division JP3872407B2 (en) | 2002-09-24 | 2002-09-24 | Combined power plant and closed air cooled gas turbine system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10196316A JPH10196316A (en) | 1998-07-28 |
| JP3431435B2 true JP3431435B2 (en) | 2003-07-28 |
Family
ID=11471832
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP00036797A Expired - Lifetime JP3431435B2 (en) | 1997-01-06 | 1997-01-06 | Combined power plant and closed air-cooled gas turbine system |
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| Country | Link |
|---|---|
| JP (1) | JP3431435B2 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000328962A (en) | 1999-05-19 | 2000-11-28 | Mitsubishi Heavy Ind Ltd | Turbine system |
| JP3652962B2 (en) * | 1999-11-25 | 2005-05-25 | 三菱重工業株式会社 | Gas turbine combined cycle |
| JP4488631B2 (en) * | 2001-01-18 | 2010-06-23 | 株式会社東芝 | Combined cycle power generation facility and operation method thereof |
| JP3716188B2 (en) | 2001-04-10 | 2005-11-16 | 三菱重工業株式会社 | Gas turbine combined plant |
| JP3849473B2 (en) | 2001-08-29 | 2006-11-22 | 株式会社日立製作所 | Method for cooling a high-temperature part of a gas turbine |
| US6935120B2 (en) * | 2002-05-09 | 2005-08-30 | General Electric Company | Approach to extending life of gas turbine engine |
| GB2484254A (en) * | 2010-08-04 | 2012-04-11 | Combined Cycle Enhancements Ltd | Gas turbine apparatus with energy recovery heat exchange system |
| JP6071271B2 (en) * | 2012-06-28 | 2017-02-01 | 三菱日立パワーシステムズ株式会社 | Turbine blade cooling system and gas turbine |
| US9341113B2 (en) * | 2012-10-23 | 2016-05-17 | General Electric Company | Atomizing air heat exchange for heating attemperation feed water in a combined cycle turbine |
| JP6203652B2 (en) * | 2014-01-31 | 2017-09-27 | 三菱重工業株式会社 | COOLING DEVICE CONTROL DEVICE, COOLING DEVICE, GAS TURBINE, COOLING DEVICE CONTROL METHOD, AND GAS TURBINE CONTROL METHOD |
| JP6265536B2 (en) * | 2014-03-24 | 2018-01-24 | 三菱日立パワーシステムズ株式会社 | Exhaust heat recovery system, gas turbine plant equipped with the same, and exhaust heat recovery method |
| JP6265535B2 (en) * | 2014-03-24 | 2018-01-24 | 三菱日立パワーシステムズ株式会社 | Feed water preheating device, gas turbine plant equipped with the same, and feed water preheating method |
| JP2015183597A (en) * | 2014-03-24 | 2015-10-22 | 三菱日立パワーシステムズ株式会社 | Exhaust heat recovery system, gas turbine plant including the same, and exhaust heat recovery method |
| JP6390067B2 (en) * | 2017-10-18 | 2018-09-19 | 三菱日立パワーシステムズ株式会社 | Exhaust heat recovery system, gas turbine plant equipped with the same, and exhaust heat recovery method |
| CN110173356A (en) * | 2019-06-10 | 2019-08-27 | 中节能城市节能研究院有限公司 | A kind of gas turbine inlet gas compressor group cooling based on refrigerant |
-
1997
- 1997-01-06 JP JP00036797A patent/JP3431435B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10196316A (en) | 1998-07-28 |
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