JP2004324513A - Combined cycle power generation plant and its starting method - Google Patents

Combined cycle power generation plant and its starting method Download PDF

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JP2004324513A
JP2004324513A JP2003119666A JP2003119666A JP2004324513A JP 2004324513 A JP2004324513 A JP 2004324513A JP 2003119666 A JP2003119666 A JP 2003119666A JP 2003119666 A JP2003119666 A JP 2003119666A JP 2004324513 A JP2004324513 A JP 2004324513A
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steam
main steam
temperature
reheat
main
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JP4481586B2 (en
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Shoichiro Fujioka
昭一郎 藤岡
Yoshiaki Sakai
義明 酒井
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Toshiba Corp
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Toshiba Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Abstract

<P>PROBLEM TO BE SOLVED: To restrain a vain thermal energy consumption by reducing a starting operation time till each temperature of main steam and reheat steam generated from one train becomes respectively equal to each temperature of a main steam and reheat steam generated from the other train when the one train is in operation and the other train is made to start actuating. <P>SOLUTION: This combined power generation plant is constituted such that a steam turbine plant 3 is combined to the plurality of trains constituted by gas turbine plants 1a, 1b and exhaust heat recovery boilers 2a, 2b. Among the plurality of trains, a second main steam desuperheater 41b for connecting a second high pressure superheater 9b of the second exhaust heat recovery boiler 2b in the second train B<SB>0</SB>to a first main steam system, a first high temperature reheated steam desuperheater 50a for connecting a first reheater 10a of the first exhaust heat recovery boiler in the first train to an intermediate pressure turbine 23, and a second high pressure reheated steam desuperheater 50b in the second train are provided. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、コンバインドサイクル発電プラントのうち、ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にし、この複数系列に対し、蒸気タービンプラントを別軸として組み合わせたコンバインドサイクル発電プラントおよびその起動方法に関する。
【０００２】
【従来の技術】
最近の火力発電プラントでは、プラント熱効率のより一層の向上を図るため、ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にし、この複数系列に対し、１台の蒸気タービンプラントを別軸として組み合わせた、いわゆる多軸コンバインドサイクル発電プラントが出現している。
【０００３】
この多軸コンバインドサイクル発電プラントは、蒸気タービンプラントを主体に置き、蒸気タービンプラントの持つ大容量化（高出力化）を巧みに利用するものであり、容量が大きくなっている分だけ定格運転時のプラント熱効率がガスタービンと蒸気タービンとを軸結合させた、いわゆる一軸タイプに較べて高く、有利になっている。
【０００４】
このように、定格運転時のプラント熱効率が一軸タイプに較べて高い多軸コンバインドサイクル発電プラントでも、より一層のプラント熱効率の向上を求めてガスタービン入口燃焼ガス温度の高温化が図られている。このガスタービン入口燃焼ガス温度の高温化に対処して多軸コンバインドサイクル発電プラントでは、構成部品の強度保証の点から蒸気による冷却が試行錯誤を繰り返しながら進められており、例えば、特開平１０−３３９１０９号公報（特許文献１）、特開平１１−６２５１５号公報（特許文献２）等、数多くの発明が開示されている。
【０００５】
【特許文献１】
特開平１０−３３９１０９号公報
【０００６】
【特許文献２】
特開平１１−６２５１５号公報
【０００７】
【発明が解決しようとする課題】
多軸コンバインドサイクル発電プラントは、上述の特許公報に開示されているように、蒸気冷却技術の進展に伴ってガスタービン入口燃焼ガスの高温化を図り、プラント熱効率をより一層向上させることができるものの、それでも幾つかの問題を抱えており、その１つに第１系列の排熱回収ボイラから発生した主蒸気および再熱蒸気のそれぞれに第２系列の排熱回収ボイラから発生した主蒸気および再熱蒸気のそれぞれを合流させて蒸気タービンプラントに供給する際、主蒸気温度の等温化および再熱蒸気温度の等温化がある。
【０００８】
従来、例えば、第１系列が運転中であり、第２系列が起動運転または再起動運転に入る場合、多軸コンバインドサイクル発電プラントは、第１系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれと、第２系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれとの間の温度差が大きいと、各機器に過大な熱応力を発生させ、強度低下等の要因になることを考慮して第１系列の負荷（出力）を強制的に低下して待機させ、第２系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの温度が予め定められた温度差の範囲に収まったとき、第１系列の排熱回収ボイラから発生した主蒸気および再熱蒸気のそれぞれと第２系列の排熱回収ボイラから発生した主蒸気および再熱蒸気のそれぞれとを合流させて蒸気タービンプラントに供給していた。
【０００９】
しかし、このような運転手法は、第１系列から発生する主蒸気および再熱蒸気のそれぞれの温度を、第２系列から発生する主蒸気および再熱蒸気のそれぞれの温度とに合わせる場合に、長時間を要するとともに無駄な熱エネルギを消費する等の不都合があった。
【００１０】
また、第１系列から発生する主蒸気および再熱蒸気のそれぞれの温度を第２系列から発生する主蒸気および再熱蒸気のそれぞれの温度に合わせるために、第１系列の負荷を低下して待機させておくことは、その分だけ熱エネルギを無駄に消費することになり、結局、プラント熱効率低下の要因にもなっていた。
【００１１】
このため、多軸コンバインドサイクル発電プラントでは、例えば、第１系列運転中に、例えば、第２系列に起動または再起動運転を開始させる場合、第１系列から発生する主蒸気温度および再熱蒸気温度のそれぞれと、第２系列から発生する主蒸気温度および再熱蒸気温度のそれぞれとが同温になるまでの運転時間をより一層短くする何らかの新たな改善が求められていた。
【００１２】
本発明は、このような事情に基づいてなされたもので、一方の系列が運転中で、他方の系列が起動する場合、一方の系列から発生する主蒸気および再熱蒸気のそれぞれの温度と、他方の系列から発生する主蒸気および再熱蒸気のそれぞれの温度とが同温になるまでの運転時間をより一層短くして無駄な熱エネルギの消費を抑制するコンバインドサイクル発電プラントおよびその起動方法を提案することを目的とする。
【００１３】
【課題を解決するための手段】
本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項１に記載したように、ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にして備え、これら複数系列に蒸気タービンプラントを組み合わせたコンバインドサイクル発電プラントにおいて、前記複数系列のうち、第１系列における第１排熱回収ボイラの第１高圧過熱器を前記蒸気タービンプラントの高圧蒸気タービンに接続させる第１主蒸気系に設けた第１主蒸気減温器と、前記複数系列のうち、第２系列における第２排熱回収ボイラの第２高圧過熱器を前記第１主蒸気系に接続させる第２主蒸気系に設けた第２主蒸気減温器と、前記第１系列における第１排熱回収ボイラの第１再熱器を前記蒸気タービンプラントの中圧蒸気タービンに接続させる第１高温再熱系に設けた第１高温再熱蒸気減温器と、前記第２系列における第２排熱回収ボイラの第２再熱器を前記第１高温再熱系に接続させる第２高温再熱系に設けた第２高温再熱蒸気減温器とを備えたものである。
【００１４】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項２に記載したように、第１主蒸気減温器は、第１排熱回収ボイラの第１高圧給水系に接続する第１主蒸気減温系を設けるとともに、この第１主蒸気減温系に第１主蒸気減温調節弁を備えたものである。
【００１５】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項３に記載したように、第２主蒸気減温器は、第２排熱回収ボイラの第２高圧給水系に接続する第２主蒸気減温系を設けるとともに、この第２主蒸気減温系に第２主蒸気減温調節弁を備えたものである。
【００１６】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項４に記載したように、第１高温再熱蒸気減温器は、第１排熱回収ボイラの第１高圧給水系に接続する第１主蒸気減温系から分岐して第１高温再熱蒸気減温系を設けるとともに、この第１高温再熱蒸気減温系に第１高温再熱蒸気減温調節弁を備えたものである。
【００１７】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項５に記載したように、第２高温再熱蒸気減温器、第２排熱回収ボイラの第２高圧給水系に接続する第２主蒸気減温系から分岐して第２高温再熱蒸気減温系を設けるとともに、この第２高温再熱蒸気減温系に第２高温再熱蒸気減温調節弁を備えたものである。
【００１８】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項６に記載したように、第１主蒸気減温調節弁は、第１主蒸気系を流れる主蒸気の温度と、前記第１主蒸気系を流れる主蒸気と第２主蒸気系を流れる主蒸気との合流主蒸気の温度とに基づいて弁開閉信号を演算する第１主蒸気制御装置を備えたものである。
【００１９】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項７に記載したように、第２主蒸気減温調節弁は、第２主蒸気系を流れる主蒸気の温度と、前記第２主蒸気系を流れる主蒸気と第１主蒸気系を流れる主蒸気との合流主蒸気の温度とに基づいて弁開閉信号を演算する第２主蒸気制御装置を備えたものである。
【００２０】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項８に記載したように、第１高温再熱蒸気減温調節弁は、第１高温再熱系を流れる高温再熱蒸気と、前記第１高温再熱系を流れる高温再熱蒸気と第２高温再熱系を流れる高温再熱蒸気との合流再熱蒸気の温度とに基づいて弁開閉信号を演算する第１高温再熱蒸気制御装置を備えたものである。
【００２１】
また、本発明に係るコンバインドサイクル発電プラントは、上述の目的を達成するために、請求項９に記載したように、第２高温再熱蒸気減温調節弁は、第２高温再熱系を流れる高温再熱蒸気と、前記第２高温再熱系を流れる高温再熱蒸気と第１高温再熱系を流れる高温再熱蒸気との合流再熱蒸気の温度とに基づいて弁開閉信号を演算する第２高温再熱蒸気制御装置を備えたものである。
【００２２】
また、本発明に係るコンバインドサイクル発電プラントの起動方法は、上述の目的を達成するために、請求項１０に記載したように、ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にして備え、これら複数系列に蒸気タービンプラントを組み合わせるとともに、前記複数系列のうち、第１系列が運転中で、第２系列を起動させるコンバインドサイクル発電プラントの起動方法において、前記第１系列における第１排熱回収ボイラの第１高圧過熱器からの主蒸気に、前記第２系列における第２排熱回収ボイラの第２高圧過熱器からの主蒸気を合流させて前記蒸気タービンプラントの高圧蒸気タービンに供給する一方、前記第１系列における前記第１排熱回収ボイラの第１再熱器からの高温再熱蒸気に、前記第２系列における前記第２排熱回収ボイラの第２再熱器からの高温再熱蒸気を合流させて前記蒸気タービンプラントの中圧蒸気タービンに供給するとき、前記第１高圧過熱器の下流側に設けた第１主蒸気減温器に冷却媒体を供給し、前記第１主蒸気減温器からの主蒸気と、前記第１主蒸気減温器からの主蒸気と前記第２高圧過熱器からの主蒸気との合流主蒸気の温度差が予め定められた温度差の範囲に入ったとき、前記第１主蒸気減温器に供給する冷却媒体を断つとともに、前記第１再熱器の下流側に設けた第１高温再熱蒸気減温器に冷却媒体を供給し、前記第１高温再熱蒸気減温器からの高温再熱蒸気と、前記第１高温再熱蒸気減温器からの高温再熱蒸気と前記第２再熱器からの高温再熱蒸気との合流再熱蒸気の温度差とが予め定められた温度差の範囲に入ったとき、前記第１高温再熱蒸気減温器に供給する冷却媒体を断つ方法である。
【００２３】
【発明の実施の形態】
以下、本発明に係るコンバインドサイクル発電プラントおよびその起動方法の実施形態を図面および図面に付した符号を引用して説明する。
【００２４】
図１は、本発明に係るコンバインドサイクル発電プラントおよびその起動方法を多軸型に適用した実施形態を示す概略系統図である。
【００２５】
なお、本実施形態に係るコンバインドサイクル発電プラントは、蒸気タービンプラントを、ガスタービンプラントおよび排熱回収ボイラで構成する系列に組み合わせた例示として表わしている。
【００２６】
本実施形態に係るコンバインドサイクル発電プラントは、第１ガスタービンプラント１ａと、第１排熱回収ボイラ２ａを備える第１系列Ａ０と、第１系列Ａ０から切り離して別軸とする蒸気タービンプラント３と、さらに蒸気タービンプラント３から切り離して別軸とする第２ガスタービンプラント１ｂと、第２排熱回収ボイラ２ｂとを備える第２系列Ｂ０とで構成される。
【００２７】
第１ガスタービンプラント１ａは、発電機４ａ、空気圧縮機５ａ、ガスタービン燃焼器６ａ、ガスタービン７ａを備え、空気圧縮機５ａで吸い込んだ空気を圧縮して高圧化し、その高圧空気をガスタービン燃焼器６ａに供給し、ここで高圧空気とともに燃料を加えて燃焼ガスを生成し、その燃焼ガスをガスタービン７ａに供給して膨張仕事をさせ、その際に発生する動力で発電機４ａを回転駆動するとともに、膨張仕事を終えたガスタービン排気（排熱）を第１排熱回収ボイラ２ａに供給し、蒸気発生の熱源として使用している。
【００２８】
なお、第２ガスタービンプラント１ｂは、各構成部品が第１ガスタービンプラント１ａのそれと同一なので、部品に同一番号を付した部品番号に添字ｂを付し、その重複説明を省略する。
【００２９】
また、第１排熱回収ボイラ２ａは、例えば横長筒状のケーシング８ａ内を流れるガスタービン７ａからの排ガスの流れに沿って順に、第１高圧過熱器９ａ、第１再熱器１０ａ、第１高圧ドラム１１ａに接続する第１高圧蒸発器１２ａ、第１中圧過熱器１３ａ、第１高圧節炭器１４ａ、第１低圧過熱器１５ａ、第１中圧ドラム１６ａに接続する第１中圧蒸発器１７ａ、第１中圧節炭器１８ａ、第１低圧ドラム１９ａに接続する第１低圧蒸発器２０ａ、第１低圧節炭器２１ａを収容し、高，中，低の各蒸発器１２ａ，１７ａ，２０ａで蒸発した飽和蒸気を高，中，低の各ドラム１１ａ，１６ａ，１９ａで気液分離を行った後、第１高圧過熱器９ａで過熱蒸気にして蒸気タービンプラント３に供給している。
【００３０】
なお、第２排熱回収ボイラ２ｂは、各構成部品が第１排熱回収ボイラ１ｂのそれと同一なので、部品に同一番号を付した構成部品番号に添字ｂを付し、その重複説明を省略する。
【００３１】
また、蒸気タービンプラント３は、互いを軸結合させた高圧蒸気タービン２２、中圧蒸気タービン２３、低圧蒸気タービン２４、発電機２５を備え、第１排熱回収ボイラ１ａの第１高圧過熱器９ａから第１主蒸気系２６ａを介して供給される過熱蒸気に、第２排熱回収ボイラ１ｂの第１高圧過熱器９ｂから第２主蒸気系２６ｂを介して供給される過熱蒸気を点Ａで合流させ、合流させた過熱蒸気を合流主蒸気系２６の高圧加減弁２７を介して高圧蒸気タービン２２に供給し、ここで膨張仕事をさせている。
【００３２】
また、蒸気タービンプラント３は、第１排熱回収ボイラ２ａの第１再熱器１０ａに接続する第１低温再熱系２９ａと第２排熱回収ボイラ２ｂの第２再熱器１０ｂに接続する第２低温再熱系２９ｂとのそれぞれを備え、高圧蒸気タービン２２で膨張仕事を終えたタービン排気を共用低温再熱系２９の点Ｂで分流させ、分流させた一方のタービン排気を第１低温再熱系２９ａを介して第１排熱器１０ａに供給し、ここで再び過熱させて再熱蒸気にし、その再熱蒸気を第１高温再熱系３０ａと第２高温再熱系３０ｂとの合流点Ｃで第２再熱器１０ｂからの再熱蒸気と合流させ、その合流再熱蒸気を合流高温再熱系３０のインターセプト弁２８を介して中圧蒸気タービン２３に供給している。
【００３３】
中圧蒸気タービン２３は、合流再熱蒸気に膨張仕事をさせ、膨張仕事を終えたタービン排気を中圧蒸気タービン排気系３１を介して低圧蒸気タービン２４に供給している。
【００３４】
低圧蒸気タービン２４は、第１排熱回収ボイラ２ａの第１低圧過熱器１５ａに接続する第１低圧蒸気系３２ａと第２排熱回収ボイラ２ｂの第２低圧過熱器１５ｂに接続する第２低圧蒸気系３２ｂとのそれぞれを備え、点Ｄで第１低圧過熱器１５ａからの低圧蒸気を第２低圧過熱器１５ｂからの低圧蒸気に合流させ、その合流低圧蒸気を低圧加減弁３３を介して点Ｅで再び中圧蒸気タービン排気系３１からのタービン排気に合流させた後、その合流蒸気に膨張仕事をさせている。
【００３５】
また、低圧蒸気タービン２４は、復水器３４、低圧給水ポンプ３５を備える共用低圧給水系３６、点Ｆで給水を分流させ、分流させた一方の給水を第１排熱回収ボイラ２ａの第１低圧節炭器２１ａに供給する第１低圧給水系３６ａと、分流させた他方の給水を第２排熱回収ボイラ２ｂの第２低圧節炭器２１ｂに供給する第２低圧給水系３６ｂとを備え、膨張仕事を終えたタービン排気を復水器３４で凝縮して復水にし、低圧給水ポンプ３５で昇圧して給水にし、その給水を共用低圧給水系３６の点Ｆで分流させ、分流させた給水の一方を第１低圧節炭器２１ａに供給するとともに、分流させた給水の残りを第２低圧節炭器２１ｂに供給している。
【００３６】
第１低圧節炭器２１ａは、第１低圧給水系３６ａから供給された給水を第１ガスタービンプラント１ａからの排ガスを熱源として加熱させた後、第１低圧ドラム１９ａから第１中圧給水ポンプ３７ａを備える第１中圧給水系３８ａを介して第１中圧節炭器１８ａに供給するとともに、第１高圧給水ポンプ３９ａを備える第１高圧給水系４０ａを介して第１高圧節炭器１４ａにそれぞれ供給している。
【００３７】
なお、第２低圧節炭器２１ｂも、第１低圧節炭器２１ａと同様の系統を備えているので、系統を構成する部品に同一番号を付した部品番号に添字ｂを付し、その重複説明を省略する。
【００３８】
一方、第１主蒸気系２６ａは、第１主蒸気減温器４１ａ、第１主蒸気逆止弁４２ａ、第１主蒸気止め弁４３ａを備えて第２主蒸気系２６ｂの点Ａに接続するとともに、第１主蒸気減温器４１ａの出口から分岐し、途中に第１高圧タービンバイパス弁４４ａを介装して第１低温再熱系２９ａに接続する第１高圧タービンバイパス系４５ａを備え、定格運転時、第１排熱回収ボイラ２ａの第１高圧過熱器９ａから出る過熱蒸気（主蒸気）を第１主蒸気減温器４１ａで適温、適圧にして、蒸気タービンプラント３の高圧加減弁２７を介して高圧蒸気タービン２２に供給する一方、起動運転時、第１高圧過熱器９ａから出る蒸気の温度・圧力が予め定められた設定値よりも低いとき、第１高圧タービンバイパス系４５ａの第１高圧タービンバイパス弁４４ａを介して第１低温再熱系２９ａに供給している。
【００３９】
また、第１主蒸気減温器４１ａは、途中に第１主蒸気減温調節弁４６ａを介装する第１主蒸気減温系４７ａを備え、この第１主蒸気減温系４７ａを第１排熱回収ボイラ２ａにおける第１高圧給水系４０ａの第１高圧給水ポンプ３９ａの出口側に接続し、第１主蒸気系２６ａの過熱蒸気（主蒸気）の減温・減圧を行っている。
【００４０】
なお、第２主蒸気系２６ｂも第１主蒸気系２６ａと同様の系統を備えているので、系統を構成する部品に同一番号を付した部品番号に添字ｂを付し、その重複説明を省略する。
【００４１】
他方、蒸気タービンプラント３の高圧蒸気タービン２２の出口から共用低温再熱系２９、第１低温再熱蒸気止め弁４８ａおよび第１低温再熱逆止弁４９ａを備えた第１低温再熱系２９ａを介して接続する第１排熱回収ボイラ２ａの第１再熱器１０ａは、第１高温再熱系３０ａ、第１高温再熱蒸気減温器５０ａ、第１高温再熱逆止弁５１ａ、第１高温再熱蒸気止め弁５２ａ、点Ｃで第２高温再熱系３０ｂからの再熱蒸気と合流させる合流高温再熱系３０、インターセプト弁２８を介して中圧蒸気タービン２３に接続している。
【００４２】
また、第１高温再熱蒸気減温器５０ａは、途中に第１高温再熱蒸気減温調節弁５３ａを介装する第１主蒸気減温系４７ａから分岐する第１高温再熱蒸気減温系５４ａを備えている。
【００４３】
また、第１高温再熱蒸気減温器５０ａは、その出口側から分岐し、途中に第１高温再熱蒸気タービンバイパス弁５５ａを介して蒸気タービンプラント３の復水器３４に接続する第１高温再熱蒸気タービンバイパス系５６ａを備えている。
【００４４】
なお、第２高温再熱蒸気減温器５０ｂも、第１高温再熱蒸気減温器５０ａと同様の系統を備えているので、系統を構成する部品に同一番号を付した部品番号に添字ｂを付し、その重複説明を省略する。
【００４５】
図２は、第１排熱回収ボイラ２ａの第１主蒸気系２６ａに設けた第１主蒸気減温器４１ａに第１主蒸気減温系４７ａの第１主蒸気減温調節弁４６ａから供給される冷却媒体（給水）と、第２排熱回収ボイラ２ｂの第２主蒸気系２６ｂに設けた第２主蒸気減温器４１ｂに第２主蒸気減温系４７ｂの第２主蒸気減温調節弁４６ｂから供給される冷却媒体（給水）とのそれぞれを制御する制御系統図である。
【００４６】
本実施形態は、第１主蒸気系２６ａの第１主蒸気減温器４１ａの下流側に第１主蒸気温度センサ５７ａと第１主蒸気圧力センサ５８ａとを備えるとともに、点Ａで第１主蒸気系２６ａからの主蒸気に第２主蒸気系２６ｂからの主蒸気を合流させ、その合流主蒸気を高圧加減弁２７に供給する合流主蒸気系２６に合流主蒸気温度センサ５９と合流主蒸気圧力センサ６０とを備える一方、第１主蒸気温度センサ５７ａから検出する温度信号と合流主蒸気温度センサ５９ａから検出する温度信号とに基づいて第１主蒸気減温器４１ａに第１主蒸気減温系４７ａからの冷却媒体を供給する第１主蒸気減温調節弁４６ａの弁開閉信号を演算する第１主蒸気制御装置６１ａを備えている。
【００４７】
また、本実施形態は、第１主蒸気系２６ａの構成と同様に、第２主蒸気系２６ｂの第２主蒸気減温器４１ｂの後流側に第２主蒸気温度センサ５７ｂと第１主蒸気圧力センサ５８ｂとを備えるとともに、第２主蒸気温度センサ５７ｂから検出する温度信号と合流主蒸気温度センサ５９ｂから検出する温度信号とに基づいて第２主蒸気減温器４１ｂに第２主蒸気減温系４７ｂからの冷却媒体を供給する第２主蒸気減温調節弁４６ｂの弁開閉信号を演算する第２主蒸気制御装置６１ｂを備えている。
【００４８】
なお、第１高温再熱系３０ａおよび第２高温再熱系３０ｂも第１主蒸気系２６ａおよび第２主蒸気系２６ｂの構成と同一なので、図１に示した部品番号と同一番号を採るとともに括弧内の部品番号に添字ａまたはｂを付すだけにとどめ、その重複説明を省略する。
【００４９】
次に、上述の構成を備えるコンバインドサイクル発電プラントの起動方法を説明する。
【００５０】
本実施形態に係るコンバインドサイクル発電プラントの起動方法は、例えば、第１ガスタービンプラント１ａと第１排熱回収ボイラ２ａとで構成される第１系列Ａ０が定格運転中で、例えば、第２ガスタービンプラント１ｂと第２排熱回収ボイラ２ｂとで構成される第２系列Ｂ０が起動または再起動を開始する例示として説明する。
【００５１】
第２系列Ｂ０は、第２排熱回収ボイラ２ｂの起動または再起動に先立ち、まず、第２高圧タービンバイパス系４５ｂの第２高圧タービンバイパス弁４４ｂと第２高温再熱蒸気タービンバイパス系５６ｂの第２高温再熱蒸気タービンバイパス弁５５ｂとを開弁させている。
【００５２】
次に、第２系列Ｂ０は、第２排熱回収ボイラ２ｂの第２高圧過熱器９ｂから発生する蒸気の圧力が高まってくると、図２に示す第１主蒸気圧力センサ５８ａ、第１高温再熱圧力センサ６３ａのそれぞれから検出する圧力と、第２主蒸気圧力センサ５８ｂ、第２高温再熱圧力センサ６３ｂのそれぞれから検出する圧力とが予め定められた圧力差の範囲内に入ると、図１および図２に示す第２主蒸気系２６ｂの第２主蒸気止め弁４３ｂ、第２高圧再熱系３０ｂの第２高温再熱蒸気止め弁５２ｂ、第２低温再熱系２９ｂの第２低温再熱蒸気止め弁４８ｂを開弁させ、第２高圧タービンバイパス弁４４ｂ、第２高温再熱蒸気タービンバイパス弁５５ｂを閉弁させる。
【００５３】
第２高圧タービンバイパス弁４４ｂ、第２高温再熱蒸気タービンバイパス弁５５ｂが閉弁すると、第１系列Ａ０の第１主蒸気制御装置６１ａは、図２に示すように、第１主蒸気系２６ａの第１主蒸気温度センサ５７ａで検出した主蒸気温度信号と合流主蒸気温度センサ５９ａで検出した合流主蒸気温度信号とに基づいて弁開閉信号を演算し、主蒸気温度信号と合流主蒸気温度信号とが予め定められた温度差の範囲に入ったとき、その演算信号を第１主蒸気減温系４７ａの第１主蒸気減温調節弁４６ａに与えて第１主蒸気減温調節弁４６ａを開弁させる。
【００５４】
また、同時に、第１系列Ａ０の第１高温再熱制御装置６４ａは、第１高温再熱系３０ａの第１高温再熱温度センサ６２ａで検出した主蒸気温度信号と合流再熱蒸気温度センサ５９ｂで検出した合流再熱蒸気温度信号とに基づいて弁開閉信号を演算し、再熱蒸気温度信号と合流再熱蒸気温度信号とが予め定められた温度差の範囲に入ったとき、その演算信号を第１高温再熱蒸気減温系５４ａの第１高温再熱蒸気減温調節弁５３ａに与えて第１高温再熱蒸気減温調節弁５３ａを開弁させる。
【００５５】
第１主蒸気減温系４７ａの第１主蒸気減温調節弁４６ａを開弁させ、図１に示す第１高圧給水系４０ａから抽水し、第１主蒸気減温系４７ａの第１主蒸気減温調節弁４６ａを介して第１主蒸気減温器４１ａに供給される冷却媒体は、ここで第１主蒸気系２６ａからの主蒸気（過熱蒸気）を減温、減圧し、高圧加減弁２７を介して高圧蒸気タービン２２に供給される。
【００５６】
第１主蒸気減温器４１ａで減温、減圧させた主蒸気を、第２主蒸気系２６ｂからの主蒸気に点Ａで合流させ、その合流主蒸気を合流主蒸気系２６を介して高圧蒸気タービン２２に流している間、第１主蒸気系２６ａからの主蒸気と第２主蒸気系２６ｂからの主蒸気とが同温になると、第１系列Ａ０の第１主蒸気制御装置６１ａは、第１主蒸気温度センサ５７ａからの温度信号と合流主蒸気系２６の合流主蒸気温度センサ５９ａからの温度信号とに基づいて弁開閉信号を演算し、その演算信号を第１主蒸気減温調節弁４６ａに与えて第１主蒸気減温調節弁４６ａを閉弁させる。
【００５７】
また、第１高温再熱蒸気減温器５０ａで減温、減圧させた再熱蒸気を、第２高温再熱系３０ｂからの再熱蒸気に点Ｃで合流させ、その合流再熱蒸気を合流高温再熱系３０を介して中圧蒸気タービン２３に流している間に、第１高温再熱系３０ａからの再熱蒸気と第２高温再熱系３０ｂからの再熱蒸気とが同温になると、第１系列Ａ０の第１高温再熱蒸気制御装置６４ａは、第１高温再熱蒸気温度センサ６２ａからの温度信号と合流高温再熱系３０の合流再熱蒸気センサ５９ｂからの温度信号とに基づいて弁開閉信号を演算し、その演算信号を第１高温再熱蒸気減温調節弁５３ａに与えて第１高温再熱蒸気減温調節弁５３ａを閉弁させる。
【００５８】
このように、本実施形態は、例えば、第１系列Ａ０の第１排熱回収ボイラ２ａが運転中で、第２系列Ｂ０の第２排熱回収ボイラ２ｂが起動または再起動の運転を開始させる際、第１排熱回収ボイラ２ａから発生する主蒸気と再熱蒸気とのそれぞれが第２排熱回収ボイラ２ｂから発生する主蒸気と再熱蒸気とのそれぞれとほぼ同温になるまで第１排熱回収ボイラ２ａから発生する主蒸気と再熱蒸気とのそれぞれを減温・減圧させるので、従来のように第１系列Ａ０の負荷（出力）を強制的に低下させてエネルギを無駄に使用することもなく、従来に較べてより一層高いプラント熱効率を維持させることができる。
【００５９】
【発明の効果】
以上のとおり、本発明に係るコンバインドサイクル発電プラントおよびその起動方法は、複数系列のうち、一方の系列の排熱回収ボイラが運転中で、他方の系列の排熱回収ボイラを起動または再起動の運転を開始させる際、一方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれに一方の系列の排熱回収ボイラにおける高圧給水系から抽水する冷却媒体を加えて減温・減圧させ、他方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの温度が一方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの温度と予め定められ温度差範囲内に入ったとき、一方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの減温・減圧を停止させるので、従来のように一方の系列の排熱回収ボイラの負荷（出力）を強制的に低下させて一方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの温度を他方の系列の排熱回収ボイラから発生する主蒸気および再熱蒸気のそれぞれの温度とほぼ同温になるまで待機させて無駄なエネルギを消費することがなく、プラント熱効率を高く維持させた運転を行うことができる。
【図面の簡単な説明】
【図１】本発明に係るコンバインドサイクル発電プラントの実施形態を示す概略系統図。
【図２】本発明に係るコンバインドサイクル発電プラントおよびその起動方法の実施形態を示す制御系統図。
【符号の説明】
１ａ…第１ガスタービンプラント、１ｂ…第２ガスタービンプラント、２ａ…第１排熱回収ボイラ、２ｂ…第２排熱回収ボイラ、３…蒸気タービンプラント、４ａ，４ｂ…発電機、５ａ，５ｂ…空気圧縮機、６ａ，６ｂ…ガスタービン燃焼器、７ａ，７ｂ…ガスタービン、８ａ，８ｂ…ケーシング、９ａ…第１高圧過熱器、９ｂ…第２高圧過熱器、１０ａ…第１再熱器、１０ｂ…第２再熱器、１１ａ…第１高圧ドラム、１１ｂ…第２高圧ドラム、１２ａ…第１高圧蒸発器、１２ｂ…第２高圧蒸発器、１３ａ…第１中圧過熱器、１３ｂ…第２中圧過熱器、１４ａ…第１高圧節炭器、１４ｂ…第２高圧節炭器、１５ａｂ…第１低圧過熱器、１５ｂ…第２低圧過熱器、１６ａ…第１中圧ドラム、１６ｂ…第２中圧ドラム、１７ａ…第１中圧蒸発器、１７ｂ…第２中圧蒸発器、１８ａ…第１中圧節炭器、１８ｂ…第２中圧節炭器、１９ａ…第１低圧ドラム、１９ｂ…第２低圧ドラム、２０ａ…第１低圧蒸発器、２０ｂ…第２低圧蒸発器、２１ａ…第１低圧節炭器、２１ｂ…第２低圧節炭器、２２…高圧蒸気タービン、２３…中圧蒸気タービン、２４…低圧蒸気タービン、２５…発電機、２６ａ，２６ｂ…合流主蒸気系、２７…高圧加減弁、２８…インターセプト弁、２９…共用低温再熱系、２９ａ…第１低温再熱系、２９ｂ…第２低温再熱系、３０…合流高温再熱系、３０ａ…第１合流高温再熱系、３０ｂ…第２合流高温再熱系、３１…中圧蒸気タービン排気系、３２ａ…第１低圧蒸気系、３２ｂ…第２低圧蒸気系、３３…低圧加減弁、３４…復水器、３５…低圧給水ポンプ、３６ａ…第１共用低圧給水系、３６ｂ…第２共用低圧給水系、３７ｂ…第１中圧給水ポンプ、３７ｂ…第２中圧給水ポンプ、３８ａ…第１中圧給水系、３８ｂ…第２中圧給水系、３９ａ…第１高圧給水ポンプ、３９ｂ…第２高圧給水ポンプ、４０ａ…第１高圧給水系、４０ｂ…第２高圧給水系、４１ａ…第１主蒸気減温器、４１ｂ…第２主蒸気減温器、４２ａ…第１主蒸気逆止弁、４２ｂ…第２主蒸気逆止弁、４３ａ…第１主蒸気止め弁、４３ｂ…第２主蒸気止め弁、４４ａ…第１高圧タービンバイパス弁、４４ｂ…第２高圧タービンバイパス弁、４５ａ…第１高圧タービンバイパス弁、４５ｂ…第２高圧タービンバイパス弁、４６ａ…第１主蒸気減温調節弁、４６ｂ…第２主蒸気減温調節弁、４７ａ…第１主蒸気減温系、４７ｂ…第２主蒸気減温系、４８ａ…第１低温再熱蒸気止め弁、４８ｂ…第２低温再熱蒸気止め弁、４９ａ…第１低温再熱逆止弁、４９ｂ…第２低温再熱逆止弁、５０ａ…第１高温再熱蒸気減温器、５０ｂ…第２高温再熱蒸気減温器、５１ａ…第１高温再熱逆止弁、５１ｂ…第２高温再熱逆止弁、５２ａ…第１高温再熱蒸気止め弁、５２ｂ…第２高温再熱蒸気止め弁、５３ａ…第１高温再熱蒸気減温調節弁、５３ｂ…第２高温再熱蒸気減温調節弁、５４ａ…第１高温再熱蒸気減温系、５４ｂ…第２高温再熱蒸気減温系、５５ａ…第１高温再熱蒸気タービンバイパス弁、５５ｂ…第２高温再熱蒸気タービンバイパス弁、５６ａ…第１高温再熱蒸気タービンバイパス系、５６ｂ…第２高温再熱蒸気タービンバイパス系、５７ａ…第１主蒸気温度センサ、５７ｂ…第２主蒸気温度センサ、５８ａ…第１主蒸気圧力センサ、５８ｂ…第２主蒸気圧力センサ、５９ａ…合流主蒸気温度センサ、５９ｂ…合流再熱蒸気温度センサ、６０ａ…合流主蒸気圧力センサ、６０ｂ…合流主蒸気圧力センサ、６１ａ…第１主蒸気制御装置、６１ｂ…第２主蒸気制御装置、６２ａ…第１高温再熱蒸気温度センサ、６２ｂ…第２高温再熱蒸気温度センサ、６３ａ…第１高温再熱蒸気圧力センサ、６３ｂ…第２高温再熱蒸気圧力センサ、６４ａ…第１高温再熱蒸気制御装置、６４ｂ…第２高温再熱蒸気制御装置。[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention provides a combined cycle power plant in which a gas turbine plant and an exhaust heat recovery boiler are combined into a plurality of series, and the combined cycle power plant is combined with a steam turbine plant as a separate axis. Regarding how to start.
[0002]
[Prior art]
In recent thermal power plants, in order to further improve plant thermal efficiency, a gas turbine plant and a waste heat recovery boiler are divided into multiple lines, and one steam turbine plant is separated from the multiple lines. So-called multi-shaft combined cycle power plants combined as shafts have emerged.
[0003]
This multi-shaft combined cycle power plant mainly uses a steam turbine plant and skillfully utilizes the large capacity (high output) of the steam turbine plant. Is higher and more advantageous than a so-called single-shaft type in which a gas turbine and a steam turbine are axially connected.
[0004]
As described above, even in a multi-shaft combined cycle power generation plant in which the plant thermal efficiency at the time of rated operation is higher than that of the single-shaft type, the combustion gas temperature at the inlet of the gas turbine has been increased in order to further improve the thermal efficiency of the plant. In order to cope with the increase in the combustion gas temperature at the inlet of the gas turbine, in a multi-shaft combined cycle power plant, cooling with steam is being performed by trial and error in order to guarantee the strength of components. Many inventions have been disclosed, such as 339109 (Patent Document 1) and JP-A-11-62515 (Patent Document 2).
[0005]
[Patent Document 1]
JP-A-10-339109
[0006]
[Patent Document 2]
JP-A-11-62515
[0007]
[Problems to be solved by the invention]
As disclosed in the above-mentioned patent publication, the multi-shaft combined cycle power plant can increase the temperature of the combustion gas at the gas turbine inlet with the progress of steam cooling technology, and can further improve the plant thermal efficiency. However, there are still some problems, one of which is that the main steam and the reheat steam generated from the first series of waste heat recovery boilers are respectively replaced with the main steam generated from the second series of heat recovery steam generators and the reheat steam. When each of the hot steams is combined and supplied to the steam turbine plant, there are isothermal main steam temperatures and reheat steam temperatures.
[0008]
Conventionally, for example, when the first series is in operation and the second series enters the start-up operation or the restart operation, the multi-shaft combined cycle power plant uses the main steam generated from the exhaust heat recovery boiler of the first series and the recycle steam. If the temperature difference between each of the hot steam and each of the main steam and the reheat steam generated from the second series of waste heat recovery boiler is large, excessive heat stress is generated in each device, and the strength is reduced. Considering becoming a factor, the load (output) of the first series is forcibly reduced and put on standby, and the temperatures of the main steam and the reheat steam generated from the exhaust heat recovery boiler of the second series are predetermined. The main steam and the reheat steam generated from the first series of exhaust heat recovery boilers and the main steam and the reheat steam generated from the second series of exhaust heat recovery boilers, respectively, when the temperature falls within the range of the set temperature difference. And merge It was supplied to the steam turbine plant.
[0009]
However, such an operation method requires a long time when the respective temperatures of the main steam and the reheat steam generated from the first series are matched with the respective temperatures of the main steam and the reheat steam generated from the second series. There are inconveniences such as the time required and wasteful heat energy being consumed.
[0010]
Further, in order to match the respective temperatures of the main steam and the reheat steam generated from the first stream with the respective temperatures of the main steam and the reheat steam generated from the second stream, the load of the first stream is reduced and the standby is performed. Leaving it unnecessarily consumes thermal energy, and eventually causes a reduction in plant thermal efficiency.
[0011]
For this reason, in the multi-shaft combined cycle power plant, for example, when starting or restarting the second line during the first line operation, for example, the main steam temperature and the reheat steam temperature generated from the first line And some new improvements have been required to further shorten the operation time until the main steam temperature and the reheat steam temperature generated from the second series become the same.
[0012]
The present invention has been made based on such circumstances, and when one system is in operation and the other system is started, the respective temperatures of main steam and reheat steam generated from one system, A combined cycle power plant that suppresses wasteful heat energy consumption by further shortening the operation time until the respective temperatures of the main steam and the reheat steam generated from the other series become the same temperature, and a start-up method thereof The purpose is to propose.
[0013]
[Means for Solving the Problems]
In order to achieve the above object, the combined cycle power plant according to the present invention includes, as described in claim 1, a plurality of series including a gas turbine plant and an exhaust heat recovery boiler. In a combined cycle power plant in which a steam turbine plant is combined with a series, a first high-pressure superheater of a first exhaust heat recovery boiler in a first series of the plurality of series is connected to a high-pressure steam turbine of the steam turbine plant. A first main steam desuperheater provided in a main steam system, and a second main steamer for connecting a second high-pressure superheater of a second exhaust heat recovery boiler in a second series of the plurality of series to the first main steam system. A second main steam desuperheater provided in the steam system, and a first reheater of the first exhaust heat recovery boiler in the first series, which is a medium-pressure steam turbine of the steam turbine plant. A first high-temperature reheat steam dehumidifier provided in a first high-temperature reheat system connected to a first high-temperature reheat system, and a second reheater of a second exhaust heat recovery boiler in the second series connected to the first high-temperature reheat system And a second high-temperature reheat steam dehumidifier provided in the second high-temperature reheat system to be operated.
[0014]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above object, as described in claim 2, the first main steam desuperheater is provided with the first high-pressure feedwater of the first exhaust heat recovery boiler. A first main steam cooling system connected to the system is provided, and the first main steam cooling system is provided with a first main steam cooling control valve.
[0015]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above object, as described in claim 3, the second main steam desuperheater is provided with a second high-pressure feedwater of the second exhaust heat recovery boiler. The system is provided with a second main steam cooling system connected to the system, and the second main steam cooling system is provided with a second main steam cooling control valve.
[0016]
Further, in order to achieve the above object, the combined cycle power plant according to the present invention is configured such that the first high-temperature reheat steam desuperheater is provided with the first exhaust heat recovery boiler. A first high-temperature reheat steam decooling system is provided by branching from the first main steam deheater connected to the high-pressure water supply system, and the first high-temperature reheat steam deheater is provided in the first high-temperature reheat steam deheater. It is equipped with a valve.
[0017]
Further, in order to achieve the above object, the combined cycle power plant according to the present invention, as described in claim 5, has a second high-temperature reheat steam desuperheater and a second high-pressure reheat steam generator. A second high-temperature reheat steam decooling system is provided branching from a second main steam deheater connected to the water supply system, and a second high-temperature reheat steam deheat control valve is provided in the second high-temperature reheat steam deheater. It is provided with.
[0018]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above object, as described in claim 6, the first main steam deceleration control valve is provided with a main steam degassing control valve for the main steam flowing through the first main steam system. A first main steam control device for calculating a valve opening / closing signal based on a temperature and a temperature of a combined main steam of the main steam flowing through the first main steam system and the main steam flowing through the second main steam system It is.
[0019]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above-described object, as described in claim 7, the second main steam deceleration control valve is configured to control the main steam flowing through the second main steam system. A second main steam control device for calculating a valve opening / closing signal based on a temperature and a temperature of a combined main steam of the main steam flowing through the second main steam system and the main steam flowing through the first main steam system It is.
[0020]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above-described object, as described in claim 8, the first high-temperature reheat steam deceleration control valve flows through the first high-temperature reheat system. A valve opening / closing signal is calculated based on the high-temperature reheat steam and the temperature of the combined reheat steam of the high-temperature reheat steam flowing through the first high-temperature reheat system and the high-temperature reheat steam flowing through the second high-temperature reheat system. It has a first high-temperature reheat steam control device.
[0021]
Further, in the combined cycle power plant according to the present invention, in order to achieve the above object, as described in claim 9, the second high-temperature reheat steam deceleration control valve flows through the second high-temperature reheat system. A valve opening / closing signal is calculated based on the high-temperature reheat steam and the temperature of the combined reheat steam of the high-temperature reheat steam flowing through the second high-temperature reheat system and the high-temperature reheat steam flowing through the first high-temperature reheat system. A second high-temperature reheat steam control device is provided.
[0022]
In addition, in order to achieve the above-described object, the method for starting a combined cycle power plant according to the present invention includes, as described in claim 10, dividing a gas turbine plant and a waste heat recovery boiler into a plurality of systems. A steam turbine plant is combined with the plurality of lines, and the first line of the plurality of lines is in operation, and the start-up method of the combined cycle power generation plant for starting the second line is the first line in the first line. The main steam from the second high-pressure superheater of the second exhaust heat recovery boiler in the second series is combined with the main steam from the first high-pressure superheater of the exhaust heat recovery boiler to form a high-pressure steam turbine of the steam turbine plant. In the second series, high-temperature reheat steam from the first reheater of the first exhaust heat recovery boiler in the first series is supplied to the high-temperature reheat steam in the second series. When the high-temperature reheated steam from the second reheater of the second exhaust heat recovery boiler is combined and supplied to the medium-pressure steam turbine of the steam turbine plant, a second reheater is provided downstream of the first high-pressure superheater. A cooling medium is supplied to the first main steam desuperheater, the main steam from the first main steam desuperheater, the main steam from the first main steam desuperheater, and the main steam from the second high-pressure superheater When the temperature difference of the main steam merged with the temperature falls within a predetermined temperature difference range, the cooling medium to be supplied to the first main steam desuperheater is cut off, and the cooling medium is provided downstream of the first reheater. Supplying a cooling medium to the first high-temperature reheat steam desuperheater, the high-temperature reheat steam from the first high-temperature reheat steam deheater, and the high-temperature reheat from the first high-temperature reheat steam deheater. The temperature difference between the combined reheated steam and the high-temperature reheated steam from the second reheater falls within a predetermined temperature difference range. When Tsu, a method of cutting off the cooling medium supplied to the first high-temperature reheat steam desuperheater.
[0023]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of a combined cycle power plant and a method for starting the same according to the present invention will be described with reference to the drawings and reference numerals attached to the drawings.
[0024]
FIG. 1 is a schematic system diagram showing an embodiment in which a combined cycle power plant according to the present invention and a startup method thereof are applied to a multi-shaft type.
[0025]
In addition, the combined cycle power plant according to the present embodiment is illustrated as an example in which a steam turbine plant is combined with a system including a gas turbine plant and an exhaust heat recovery boiler.
[0026]
The combined cycle power plant according to the present embodiment is a first series A including a first gas turbine plant 1a and a first exhaust heat recovery boiler 2a. 0 And the first series A 0 A second series B including a steam turbine plant 3 separated from the steam turbine and having a separate axis, a second gas turbine plant 1b separated from the steam turbine plant 3 and having a separate axis, and a second exhaust heat recovery boiler 2b 0 It is composed of
[0027]
The first gas turbine plant 1a includes a power generator 4a, an air compressor 5a, a gas turbine combustor 6a, and a gas turbine 7a. The air sucked by the air compressor 5a is compressed to a high pressure, and the high-pressure air is converted into a gas turbine. The fuel is supplied to the combustor 6a, where fuel is added together with the high-pressure air to generate combustion gas. The combustion gas is supplied to the gas turbine 7a to perform expansion work, and the generator 4a is rotated by the power generated at that time. The gas turbine exhaust (exhaust heat) that has been driven and has completed the expansion work is supplied to the first exhaust heat recovery boiler 2a and used as a heat source for generating steam.
[0028]
In the second gas turbine plant 1b, since each component is the same as that of the first gas turbine plant 1a, a subscript "b" is added to a component number having the same number assigned to the component, and the overlapping description is omitted.
[0029]
Further, the first exhaust heat recovery boiler 2a includes, for example, a first high-pressure superheater 9a, a first reheater 10a, and a first reheater 10a along a flow of exhaust gas from a gas turbine 7a flowing in a horizontally long cylindrical casing 8a. First high-pressure evaporator 12a connected to high-pressure drum 11a, first medium-pressure superheater 13a, first high-pressure economizer 14a, first low-pressure superheater 15a, and first medium-pressure evaporation connected to first medium-pressure drum 16a Housing 17a, a first medium-pressure economizer 18a, a first low-pressure evaporator 20a connected to the first low-pressure drum 19a, and a first low-pressure economizer 21a, and high, medium, and low evaporators 12a, 17a. , 20a are subjected to gas-liquid separation by high, medium, and low drums 11a, 16a, and 19a, and then superheated by a first high-pressure superheater 9a and supplied to the steam turbine plant 3. .
[0030]
In addition, since each component of the second heat recovery steam generator 2b is the same as that of the first heat recovery steam generator 1b, the same component number is assigned to the component with the suffix b, and redundant description is omitted. .
[0031]
Further, the steam turbine plant 3 includes a high-pressure steam turbine 22, a medium-pressure steam turbine 23, a low-pressure steam turbine 24, and a power generator 25 which are axially connected to each other, and the first high-pressure superheater 9a of the first exhaust heat recovery boiler 1a. The superheated steam supplied from the first high-pressure superheater 9b of the second exhaust heat recovery boiler 1b to the superheated steam supplied through the first main steam system 26a through the second main steam system 26b at a point A. The combined superheated steam is supplied to the high-pressure steam turbine 22 via the high-pressure control valve 27 of the combined main steam system 26, where the expansion work is performed.
[0032]
Further, the steam turbine plant 3 is connected to a first low-temperature reheat system 29a connected to the first reheater 10a of the first exhaust heat recovery boiler 2a and to a second reheater 10b of the second exhaust heat recovery boiler 2b. The turbine exhaust having the second low-temperature reheating system 29b and having completed the expansion work in the high-pressure steam turbine 22 is diverted at the point B of the common low-temperature reheating system 29, and one of the diverted turbine exhausts is supplied to the first low-temperature reheating system 29b. The reheat steam is supplied to the first exhaust unit 10a via the reheat system 29a, where it is superheated again to reheat steam, and the reheat steam is supplied to the first high temperature reheat system 30a and the second high temperature reheat system 30b. At the confluence point C, the reheat steam from the second reheater 10 b is merged, and the merged reheat steam is supplied to the intermediate-pressure steam turbine 23 via the intercept valve 28 of the merged high-temperature reheat system 30.
[0033]
The medium-pressure steam turbine 23 causes the combined reheat steam to perform expansion work, and supplies the turbine exhaust having completed the expansion work to the low-pressure steam turbine 24 via the medium-pressure steam turbine exhaust system 31.
[0034]
The low-pressure steam turbine 24 has a first low-pressure steam system 32a connected to the first low-pressure superheater 15a of the first exhaust heat recovery boiler 2a and a second low-pressure steam system connected to the second low-pressure superheater 15b of the second exhaust heat recovery boiler 2b. And the low-pressure steam from the first low-pressure superheater 15a is merged with the low-pressure steam from the second low-pressure superheater 15b at a point D, and the merged low-pressure steam is supplied through the low-pressure control valve 33 to the point D. After being joined again to the turbine exhaust from the intermediate pressure steam turbine exhaust system 31 at E, the combined steam is allowed to expand.
[0035]
Further, the low-pressure steam turbine 24 is provided with a condenser 34, a common low-pressure water supply system 36 including a low-pressure water supply pump 35, and diverts the water supply at the point F, and supplies one of the divided waters to the first exhaust heat recovery boiler 2a. A first low-pressure water supply system 36a for supplying the low-pressure economizer 21a, and a second low-pressure water supply system 36b for supplying the other divided water supply to the second low-pressure economizer 21b of the second exhaust heat recovery boiler 2b. The turbine exhaust having completed the expansion work is condensed by a condenser 34 to be condensed water, and the pressure is increased by a low-pressure water supply pump 35 to supply water. The water is divided at a point F of a common low-pressure water supply system 36 and divided. One of the supply water is supplied to the first low-pressure economizer 21a, and the remainder of the diverted feedwater is supplied to the second low-pressure economizer 21b.
[0036]
The first low-pressure economizer 21a heats water supplied from the first low-pressure water supply system 36a using exhaust gas from the first gas turbine plant 1a as a heat source, and then supplies the first medium-pressure water supply pump from the first low-pressure drum 19a. The first high-pressure economizer 18a is supplied to the first medium-pressure economizer 18a via a first medium-pressure ecosystem 38a provided with a first high-pressure water supply system 40a including a first high-pressure water supply pump 39a. Respectively.
[0037]
Since the second low-pressure economizer 21b also has the same system as that of the first low-pressure economizer 21a, the same reference numerals are given to the same component numbers as those of the components constituting the system, and the same reference numerals are used. Description is omitted.
[0038]
On the other hand, the first main steam system 26a includes a first main steam desuperheater 41a, a first main steam check valve 42a, and a first main steam stop valve 43a, and is connected to a point A of the second main steam system 26b. A first high-pressure turbine bypass system 45a that branches off from the outlet of the first main steam desuperheater 41a and is connected to the first low-temperature reheating system 29a with a first high-pressure turbine bypass valve 44a interposed on the way; At the time of rated operation, superheated steam (main steam) from the first high-pressure superheater 9a of the first exhaust heat recovery boiler 2a is adjusted to an appropriate temperature and an appropriate pressure by the first main steam desuperheater 41a, and the high-pressure control of the steam turbine plant 3 is performed. On the other hand, when the steam is supplied to the high-pressure steam turbine 22 through the valve 27 and the temperature and pressure of the steam discharged from the first high-pressure superheater 9a are lower than a predetermined set value during the start-up operation, the first high-pressure turbine bypass system 45a First high pressure turbine bypass valve It is supplied to the first cold reheat system 29a via 4a.
[0039]
Further, the first main steam desuperheater 41a includes a first main steam decooling system 47a in which a first main steam decooling control valve 46a is interposed. The first high-pressure water supply system 40a of the exhaust heat recovery boiler 2a is connected to the outlet side of the first high-pressure water supply pump 39a to reduce and depressurize superheated steam (main steam) of the first main steam system 26a.
[0040]
Since the second main steam system 26b also has the same system as that of the first main steam system 26a, the components constituting the system are given the same reference numerals with the same reference numerals, and the subscripts b are added thereto, and redundant description is omitted. I do.
[0041]
On the other hand, a common low-temperature reheat system 29, a first low-temperature reheat steam stop valve 48a, and a first low-temperature reheat system 29a provided with a first low-temperature reheat check valve 49a from the outlet of the high-pressure steam turbine 22 of the steam turbine plant 3. The first reheater 10a of the first exhaust heat recovery boiler 2a connected via a first high temperature reheat system 30a, a first high temperature reheat steam deheater 50a, a first high temperature reheat check valve 51a, A first high-temperature reheat steam stop valve 52a, a merging high-temperature reheat system 30 that joins the reheat steam from the second high-temperature reheat system 30b at point C, and a connection to the medium-pressure steam turbine 23 via an intercept valve 28; I have.
[0042]
Further, the first high-temperature reheat steam desuperheater 50a is a first high-temperature reheat steam deheater that branches off from a first main steam deheater system 47a in which a first high-temperature reheat steam deheat control valve 53a is interposed. A system 54a is provided.
[0043]
The first high-temperature reheat steam desuperheater 50a branches from the outlet side, and connects to the condenser 34 of the steam turbine plant 3 on the way via the first high-temperature reheat steam turbine bypass valve 55a. A high temperature reheat steam turbine bypass system 56a is provided.
[0044]
The second high-temperature reheat steam desuperheater 50b also has the same system as the first high-temperature reheat steam deheater 50a. And the duplicated description is omitted.
[0045]
FIG. 2 shows a state in which the first main steam desuperheater 41a provided in the first main steam system 26a of the first exhaust heat recovery boiler 2a is supplied from the first main steam deheat control valve 46a of the first main steam deheat system 47a. Cooling medium (supply water) to be supplied to the second main steam desuperheater 41b provided in the second main steam system 26b of the second exhaust heat recovery boiler 2b, and the second main steam deheat system 47b It is a control system diagram which controls each of the cooling medium (water supply) supplied from the control valve 46b.
[0046]
In the present embodiment, a first main steam temperature sensor 57a and a first main steam pressure sensor 58a are provided on the downstream side of the first main steam desuperheater 41a of the first main steam system 26a. The main steam from the second main steam system 26b is combined with the main steam from the steam system 26a, and the combined main steam is supplied to the high-pressure control valve 27. While the pressure sensor 60 is provided, the first main steam desuperheater 41a supplies the first main steam desuperheater 41a based on the temperature signal detected from the first main steam temperature sensor 57a and the temperature signal detected from the combined main steam temperature sensor 59a. A first main steam control device 61a is provided for calculating a valve opening / closing signal of the first main steam deceleration control valve 46a for supplying a cooling medium from the temperature system 47a.
[0047]
Further, in the present embodiment, similarly to the configuration of the first main steam system 26a, the second main steam temperature sensor 57b and the first main steam temperature sensor 57b are provided downstream of the second main steam desuperheater 41b of the second main steam system 26b. And a second main steam desuperheater 41b based on a temperature signal detected from the second main steam temperature sensor 57b and a temperature signal detected from the combined main steam temperature sensor 59b. A second main steam control device 61b is provided for calculating a valve opening / closing signal of the second main steam decooling control valve 46b for supplying a cooling medium from the temperature reduction system 47b.
[0048]
Note that the first high-temperature reheating system 30a and the second high-temperature reheating system 30b also have the same configuration as the first main steam system 26a and the second main steam system 26b, and therefore have the same numbers as the part numbers shown in FIG. Only the subscripts a or b are added to the part numbers in parentheses, and a duplicate description thereof will be omitted.
[0049]
Next, a starting method of the combined cycle power plant having the above-described configuration will be described.
[0050]
The method for starting up the combined cycle power plant according to the present embodiment includes, for example, a first system A including a first gas turbine plant 1a and a first exhaust heat recovery boiler 2a. 0 Is in rated operation, for example, in the second system B including the second gas turbine plant 1b and the second exhaust heat recovery boiler 2b. 0 Will be described as an example of starting or restarting.
[0051]
Second series B 0 Before starting or restarting the second exhaust heat recovery boiler 2b, first, the second high-pressure turbine bypass valve 44b of the second high-pressure turbine bypass system 45b and the second high-temperature re-heating steam turbine bypass system 56b The hot steam turbine bypass valve 55b is opened.
[0052]
Next, the second series B 0 When the pressure of the steam generated from the second high-pressure superheater 9b of the second exhaust heat recovery boiler 2b increases, each of the first main steam pressure sensor 58a and the first high temperature reheating pressure sensor 63a shown in FIG. 1 and FIG. 2 when the pressure detected from the pressure sensor and the pressure detected from each of the second main steam pressure sensor 58b and the second high temperature reheat pressure sensor 63b fall within a predetermined pressure difference range. The second main steam stop valve 43b of the second main steam system 26b, the second high temperature reheat steam stop valve 52b of the second high pressure reheat system 30b, the second low temperature reheat steam stop valve 48b of the second low temperature reheat system 29b And the second high-pressure turbine bypass valve 44b and the second high-temperature reheat steam turbine bypass valve 55b are closed.
[0053]
When the second high-pressure turbine bypass valve 44b and the second high-temperature reheat steam turbine bypass valve 55b are closed, the first series A 0 As shown in FIG. 2, the first main steam control device 61a of the first main steam controller 61a has a main steam temperature signal detected by a first main steam temperature sensor 57a of the first main steam system 26a and a merging main detected by a main steam temperature sensor 59a. A valve opening / closing signal is calculated based on the steam temperature signal, and when the main steam temperature signal and the combined main steam temperature signal fall within a predetermined temperature difference range, the calculated signal is sent to the first main steam cooling system. The first main steam deceleration control valve 46a is provided to the first main steam deceleration control valve 46a to open it.
[0054]
At the same time, the first series A 0 The first high-temperature reheat control device 64a of the first high-temperature reheat system 30a, the main steam temperature signal detected by the first high-temperature reheat temperature sensor 62a of the first high-temperature reheat system 30a and the combined reheat steam temperature detected by the combined reheat steam temperature sensor 59b A valve opening / closing signal is calculated based on the signals, and when the reheat steam temperature signal and the combined reheat steam temperature signal fall within a predetermined temperature difference range, the calculated signal is reduced by the first high temperature reheat steam reduction. The temperature is supplied to the first high-temperature reheat steam deceleration control valve 53a of the temperature system 54a to open the first high-temperature reheat steam deceleration control valve 53a.
[0055]
The first main steam cooling system 47a of the first main steam cooling system 47a is opened to extract water from the first high pressure water supply system 40a shown in FIG. 1, and the first main steam of the first main steam cooling system 47a. The cooling medium supplied to the first main steam desuperheater 41a via the temperature reduction control valve 46a here cools and depressurizes the main steam (superheated steam) from the first main steam system 26a, and the high pressure control valve The high-pressure steam turbine 22 is supplied to the high-pressure steam turbine 22.
[0056]
The main steam whose temperature has been reduced and decompressed by the first main steam desuperheater 41a is merged with the main steam from the second main steam system 26b at a point A, and the merged main steam is subjected to high pressure through the merged main steam system 26. When the main steam from the first main steam system 26a and the main steam from the second main steam system 26b have the same temperature while flowing through the steam turbine 22, the first series A 0 The first main steam controller 61a calculates a valve opening / closing signal based on the temperature signal from the first main steam temperature sensor 57a and the temperature signal from the merged main steam temperature sensor 59a of the merged main steam system 26, The operation signal is supplied to the first main steam decooling control valve 46a to close the first main steam decooling control valve 46a.
[0057]
Further, the reheat steam whose temperature has been reduced and reduced by the first high temperature reheat steam desuperheater 50a is joined at point C to the reheat steam from the second high temperature reheat system 30b, and the combined reheat steam is joined. While flowing to the intermediate-pressure steam turbine 23 via the high-temperature reheat system 30, the reheat steam from the first high-temperature reheat system 30a and the reheat steam from the second high-temperature reheat system 30b have the same temperature. Then, the first series A 0 The first high-temperature reheat steam control device 64a generates a valve opening / closing signal based on the temperature signal from the first high-temperature reheat steam temperature sensor 62a and the temperature signal from the merged reheat steam sensor 59b of the merged high-temperature reheat system 30. Is given to the first high-temperature reheat steam deceleration control valve 53a to close the first high-temperature reheat steam detemperature control valve 53a.
[0058]
As described above, in the present embodiment, for example, the first stream A 0 Of the first exhaust heat recovery boiler 2a of the second series B 0 When the second waste heat recovery boiler 2b starts the operation of starting or restarting, the main steam and the reheat steam generated from the first waste heat recovery boiler 2a are generated from the second waste heat recovery boiler 2b. Each of the main steam and the reheat steam generated from the first exhaust heat recovery boiler 2a is depressurized and decompressed until the temperature becomes substantially the same as that of each of the main steam and the reheat steam. A 0 Without forcibly lowering the load (output) of the fuel cell and wastefully using energy, thereby maintaining a higher plant thermal efficiency than before.
[0059]
【The invention's effect】
As described above, the combined cycle power plant and the method for starting the same according to the present invention provide a method for starting or restarting the exhaust heat recovery boiler of one of the multiple systems while the other system is operating. At the start of operation, the cooling medium extracted from the high-pressure water supply system in the waste heat recovery boiler of one series is added to each of the main steam and reheat steam generated from the waste heat recovery boiler of one series to reduce the temperature and pressure. The temperature of the main steam and the reheat steam generated from the waste heat recovery boiler of the other series is set to the predetermined temperature of the main steam and the reheat steam generated from the waste heat recovery boiler of the one series. When the temperature falls within the difference range, the temperature reduction and decompression of the main steam and the reheat steam generated from the exhaust heat recovery boiler of one system are stopped. The load (output) of the waste heat recovery boiler is forcibly reduced, and the temperatures of the main steam and the reheat steam generated from one of the waste heat recovery boilers are generated from the other heat recovery steam generator. It is possible to perform operation while maintaining high plant thermal efficiency without waiting until the temperature of the main steam and the reheated steam becomes substantially the same as each other, and consuming unnecessary energy.
[Brief description of the drawings]
FIG. 1 is a schematic system diagram showing an embodiment of a combined cycle power plant according to the present invention.
FIG. 2 is a control system diagram showing an embodiment of a combined cycle power plant and a start-up method thereof according to the present invention.
[Explanation of symbols]
1a: First gas turbine plant, 1b: Second gas turbine plant, 2a: First heat recovery steam generator, 2b: Second heat recovery steam generator, 3 ... Steam turbine plant, 4a, 4b ... Generator, 5a, 5b ... air compressor, 6a, 6b ... gas turbine combustor, 7a, 7b ... gas turbine, 8a, 8b ... casing, 9a ... 1st high pressure superheater, 9b ... 2nd high pressure superheater, 10a ... 1st reheater 10b: second reheater, 11a: first high-pressure drum, 11b: second high-pressure drum, 12a: first high-pressure evaporator, 12b: second high-pressure evaporator, 13a: first medium-pressure superheater, 13b ... 2nd medium pressure superheater, 14a: 1st high pressure economizer, 14b ... 2nd high pressure economizer, 15ab ... 1st low pressure superheater, 15b ... 2nd low pressure superheater, 16a ... 1st intermediate pressure drum, 16b ... a second medium pressure drum, 17a ... a first medium pressure evaporator, 7b: 2nd medium pressure evaporator, 18a: 1st medium pressure economizer, 18b: 2nd medium pressure economizer, 19a: 1st low pressure drum, 19b: 2nd low pressure drum, 20a: 1st low pressure evaporator , 20b: second low-pressure evaporator, 21a: first low-pressure economizer, 21b: second low-pressure economizer, 22: high-pressure steam turbine, 23: medium-pressure steam turbine, 24: low-pressure steam turbine, 25: generator 26a, 26b ... main steam system, 27 ... high pressure control valve, 28 ... intercept valve, 29 ... common low temperature reheating system, 29a ... first low temperature reheating system, 29b ... second low temperature reheating system, 30 ... confluence High temperature reheating system, 30a: first combined high temperature reheating system, 30b: second combined high temperature reheating system, 31: medium pressure steam turbine exhaust system, 32a: first low pressure steam system, 32b: second low pressure steam system, 33 ... Low pressure control valve, 34 ... Condenser, 35 ... Low pressure feed pump, 36a ... First Low-pressure water supply system, 36b: second common low-pressure water supply system, 37b: first medium-pressure water supply pump, 37b: second medium-pressure water supply pump, 38a: first medium-pressure water supply system, 38b: second medium-pressure water supply system, 39a: first high-pressure water supply pump, 39b: second high-pressure water supply pump, 40a: first high-pressure water supply system, 40b: second high-pressure water supply system, 41a: first main steam cooler, 41b: second main steam cooler , 42a ... first main steam check valve, 42b ... second main steam check valve, 43a ... first main steam stop valve, 43b ... second main steam stop valve, 44a ... first high pressure turbine bypass valve, 44b ... second high-pressure turbine bypass valve, 45a ... first high-pressure turbine bypass valve, 45b ... second high-pressure turbine bypass valve, 46a ... first main steam de-cooling control valve, 46b ... second main steam de-cooling control valve, 47a ... First main steam cooling system, 47b... Second main steam cooling system, 48 a ... first low temperature reheat steam stop valve, 48b ... second low temperature reheat steam stop valve, 49a ... first low temperature reheat check valve, 49b ... second low temperature reheat check valve, 50a ... first high temperature reheat valve Hot steam desuperheater, 50b: second high temperature reheat steam deheater, 51a: first high temperature reheat check valve, 51b: second high temperature reheat check valve, 52a: first high temperature reheat steam stop valve 52b: second high-temperature reheat steam stop valve, 53a: first high-temperature reheat steam temperature control valve, 53b: second high-temperature reheat steam temperature control valve, 54a: first high-temperature reheat steam temperature control system, 54b: second high-temperature reheat steam cooling system, 55a: first high-temperature reheat steam turbine bypass valve, 55b: second high-temperature reheat steam turbine bypass valve, 56a: first high-temperature reheat steam turbine bypass system, 56b ... Second high-temperature reheat steam turbine bypass system, 57a: first main steam temperature sensor, 57b: second main steam temperature sensor , 58a: first main steam pressure sensor, 58b: second main steam pressure sensor, 59a: combined main steam temperature sensor, 59b: combined reheat steam temperature sensor, 60a: combined main steam pressure sensor, 60b: combined main steam Pressure sensor, 61a: first main steam controller, 61b: second main steam controller, 62a: first high-temperature reheat steam temperature sensor, 62b: second high-temperature reheat steam temperature sensor, 63a: first high-temperature reheat Steam pressure sensor, 63b: second high temperature reheat steam pressure sensor, 64a: first high temperature reheat steam control device, 64b: second high temperature reheat steam control device.

Claims (10)

ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にして備え、これら複数系列に蒸気タービンプラントを組み合わせたコンバインドサイクル発電プラントにおいて、前記複数系列のうち、第１系列における第１排熱回収ボイラの第１高圧過熱器を前記蒸気タービンプラントの高圧蒸気タービンに接続させる第１主蒸気系に設けた第１主蒸気減温器と、前記複数系列のうち、第２系列における第２排熱回収ボイラの第２高圧過熱器を前記第１主蒸気系に接続させる第２主蒸気系に設けた第２主蒸気減温器と、前記第１系列における第１排熱回収ボイラの第１再熱器を前記蒸気タービンプラントの中圧蒸気タービンに接続させる第１高温再熱系に設けた第１高温再熱蒸気減温器と、前記第２系列における第２排熱回収ボイラの第２再熱器を前記第１高温再熱系に接続させる第２高温再熱系に設けた第２高温再熱蒸気減温器とを備えたことを特徴とするコンバインドサイクル発電プラント。In a combined cycle power plant in which a gas turbine plant and a waste heat recovery boiler are provided in a plurality of lines, and a steam turbine plant is combined with the plurality of lines, a first exhaust heat in a first line among the plurality of lines is provided. A first main steam desuperheater provided in a first main steam system for connecting a first high-pressure superheater of the recovery boiler to a high-pressure steam turbine of the steam turbine plant, and a second exhaust system in a second series of the plurality of series. A second main steam desuperheater provided in a second main steam system for connecting a second high pressure superheater of the heat recovery boiler to the first main steam system, and a first exhaust heat recovery boiler in the first series. A first high-temperature reheat steam desuperheater provided in a first high-temperature reheat system for connecting a reheater to a medium-pressure steam turbine of the steam turbine plant; and a second exhaust heat recovery boiler in the second series. Combined cycle power plant, characterized in that a provided 2 reheater second hot reheat system that is connected to the first hot reheat system second hot reheat steam desuperheater. 第１主蒸気減温器は、第１排熱回収ボイラの第１高圧給水系に接続する第１主蒸気減温系を設けるとともに、この第１主蒸気減温系に第１主蒸気減温調節弁を備えたことを特徴とする請求項１記載のコンバインドサイクル発電プラント。The first main steam desuperheater is provided with a first main steam decooling system connected to the first high pressure water supply system of the first exhaust heat recovery boiler, and the first main steam deheater is provided in the first main steam deheater. The combined cycle power plant according to claim 1, further comprising a control valve. 第２主蒸気減温器は、第２排熱回収ボイラの第２高圧給水系に接続する第２主蒸気減温系を設けるとともに、この第２主蒸気減温系に第２主蒸気減温調節弁を備えたことを特徴とする請求項１記載のコンバインドサイクル発電プラント。The second main steam desuperheater is provided with a second main steam deheater connected to the second high-pressure water supply system of the second exhaust heat recovery boiler, and the second main steam deheater is provided with the second main steam deheater. The combined cycle power plant according to claim 1, further comprising a control valve. 第１高温再熱蒸気減温器は、第１排熱回収ボイラの第１高圧給水系に接続する第１主蒸気減温系から分岐して第１高温再熱蒸気減温系を設けるとともに、この第１高温再熱蒸気減温系に第１高温再熱蒸気減温調節弁を備えたことを特徴とする請求項１記載のコンバインドサイクル発電プラント。The first high-temperature reheat steam desuperheater is provided with a first high-temperature reheat steam deheat system that branches off from a first main steam deheat system connected to the first high-pressure water supply system of the first exhaust heat recovery boiler, The combined cycle power plant according to claim 1, wherein the first high-temperature reheat steam deheating system includes a first high-temperature reheat steam deheat control valve. 第２高温再熱蒸気減温器、第２排熱回収ボイラの第２高圧給水系に接続する第２主蒸気減温系から分岐して第２高温再熱蒸気減温系を設けるとともに、この第２高温再熱蒸気減温系に第２高温再熱蒸気減温調節弁を備えたことを特徴とする請求項１記載のコンバインドサイクル発電プラント。A second high-temperature reheat steam deheater, a second high-temperature reheat steam deheater branched from a second main steam deheater connected to the second high-pressure water supply system of the second exhaust heat recovery boiler, and 2. The combined cycle power plant according to claim 1, wherein the second high-temperature reheat steam deheating system includes a second high-temperature reheat steam deheat control valve. 3. 第１主蒸気減温調節弁は、第１主蒸気系を流れる主蒸気の温度と、前記第１主蒸気系を流れる主蒸気と第２主蒸気系を流れる主蒸気との合流主蒸気の温度とに基づいて弁開閉信号を演算する第１主蒸気制御装置を備えたことを特徴とする請求項３記載のコンバインドサイクル発電プラント。The first main steam deceleration control valve is configured to control a temperature of the main steam flowing through the first main steam system and a temperature of a combined main steam of the main steam flowing through the first main steam system and the main steam flowing through the second main steam system. The combined cycle power plant according to claim 3, further comprising a first main steam control device that calculates a valve opening / closing signal based on the first and the second main steam control devices. 第２主蒸気減温調節弁は、第２主蒸気系を流れる主蒸気の温度と、前記第２主蒸気系を流れる主蒸気と第１主蒸気系を流れる主蒸気との合流主蒸気の温度とに基づいて弁開閉信号を演算する第２主蒸気制御装置を備えたことを特徴とする請求項４記載のコンバインドサイクル発電プラント。The second main steam deceleration control valve is configured to control a temperature of the main steam flowing through the second main steam system, and a temperature of a main steam that is a combination of the main steam flowing through the second main steam system and the main steam flowing through the first main steam system. The combined cycle power plant according to claim 4, further comprising a second main steam control device that calculates a valve opening / closing signal based on the following. 第１高温再熱蒸気減温調節弁は、第１高温再熱系を流れる高温再熱蒸気と、前記第１高温再熱系を流れる高温再熱蒸気と第２高温再熱系を流れる高温再熱蒸気との合流再熱蒸気の温度とに基づいて弁開閉信号を演算する第１高温再熱蒸気制御装置を備えたことを特徴とするコンバインドサイクル発電プラント。The first high-temperature reheat steam deceleration control valve includes a high-temperature reheat steam flowing through the first high-temperature reheat system, a high-temperature reheat steam flowing through the first high-temperature reheat system, and a high-temperature reheat steam flowing through the second high-temperature reheat system. A combined cycle power plant comprising: a first high-temperature reheat steam control device that calculates a valve opening / closing signal based on a temperature of reheat steam combined with hot steam. 第２高温再熱蒸気減温調節弁は、第２高温再熱系を流れる高温再熱蒸気と、前記第２高温再熱系を流れる高温再熱蒸気と第１高温再熱系を流れる高温再熱蒸気との合流再熱蒸気の温度とに基づいて弁開閉信号を演算する第２高温再熱蒸気制御装置を備えたことを特徴とするコンバインドサイクル発電プラント。The second high-temperature reheat steam deceleration control valve includes a high-temperature reheat steam flowing through the second high-temperature reheat system, a high-temperature reheat steam flowing through the second high-temperature reheat system, and a high-temperature reheat steam flowing through the first high-temperature reheat system. A combined cycle power plant including a second high-temperature reheat steam control device that calculates a valve opening / closing signal based on the temperature of reheat steam combined with hot steam. ガスタービンプラントと排熱回収ボイラとで構成する系列を複数系列にして備え、これら複数系列に蒸気タービンプラントを組み合わせるとともに、前記複数系列のうち、第１系列が運転中で、第２系列を起動させるコンバインドサイクル発電プラントの起動方法において、前記第１系列における第１排熱回収ボイラの第１高圧過熱器からの主蒸気に、前記第２系列における第２排熱回収ボイラの第２高圧過熱器からの主蒸気を合流させて前記蒸気タービンプラントの高圧蒸気タービンに供給する一方、前記第１系列における前記第１排熱回収ボイラの第１再熱器からの高温再熱蒸気に、前記第２系列における前記第２排熱回収ボイラの第２再熱器からの高温再熱蒸気を合流させて前記蒸気タービンプラントの中圧蒸気タービンに供給するとき、前記第１高圧過熱器の下流側に設けた第１主蒸気減温器に冷却媒体を供給し、前記第１主蒸気減温器からの主蒸気と、前記第１主蒸気減温器からの主蒸気と前記第２高圧過熱器からの主蒸気との合流主蒸気の温度差が予め定められた温度差の範囲に入ったとき、前記第１主蒸気減温器に供給する冷却媒体を断つとともに、前記第１再熱器の下流側に設けた第１高温再熱蒸気減温器に冷却媒体を供給し、前記第１高温再熱蒸気減温器からの高温再熱蒸気と、前記第１高温再熱蒸気減温器からの高温再熱蒸気と前記第２再熱器からの高温再熱蒸気との合流再熱蒸気の温度差とが予め定められた温度差の範囲に入ったとき、前記第１高温再熱蒸気減温器に供給する冷却媒体を断つことを特徴とするコンバインドサイクル発電プラントの起動方法。A plurality of lines composed of a gas turbine plant and an exhaust heat recovery boiler are provided, a steam turbine plant is combined with the plurality of lines, a first line of the plurality of lines is in operation, and a second line is started. In the method for starting a combined cycle power plant, the main steam from the first high-pressure superheater of the first exhaust heat recovery boiler in the first series is supplied to the second high-pressure superheater of the second waste heat recovery boiler in the second series. From the first reheater of the first waste heat recovery boiler in the first series while the second steam is supplied to the high pressure steam turbine of the steam turbine plant. When the high-temperature reheated steam from the second reheater of the second waste heat recovery boiler in the series is combined and supplied to the medium-pressure steam turbine of the steam turbine plant Supplying a cooling medium to a first main steam desuperheater provided downstream of the first high-pressure superheater, and supplying a main steam from the first main steam desuperheater and a first main steam desuperheater from the first main steam desuperheater. When the temperature difference between the combined main steam of the main steam and the main steam from the second high-pressure superheater falls within a predetermined temperature difference range, the cooling medium supplied to the first main steam desuperheater is Along with the disconnection, a cooling medium is supplied to a first high-temperature reheat steam desuperheater provided downstream of the first reheater, and the high-temperature reheat steam from the first high-temperature reheat steam deheater, The temperature difference of the combined reheat steam between the high-temperature reheat steam from the first high-temperature reheat steam desuperheater and the high-temperature reheat steam from the second reheater falls within a predetermined temperature difference range. A method of starting a combined cycle power plant, wherein a cooling medium supplied to the first high-temperature reheat steam desuperheater is cut off.
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