JP3700075B2 - Pressurized fluidized bed combined power plant - Google Patents

Pressurized fluidized bed combined power plant Download PDF

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JP3700075B2
JP3700075B2 JP01293399A JP1293399A JP3700075B2 JP 3700075 B2 JP3700075 B2 JP 3700075B2 JP 01293399 A JP01293399 A JP 01293399A JP 1293399 A JP1293399 A JP 1293399A JP 3700075 B2 JP3700075 B2 JP 3700075B2
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fluidized bed
pressurized fluidized
gas
valve
air
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JP2000213306A (en
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行正 吉成
孝志 麻尾
健 上野
信義 三島
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Hitachi Ltd
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Hitachi Ltd
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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]

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Description

【０００１】
【発明の属する技術分野】
本発明は、加圧流動床ボイラとガスタービンと蒸気タービンとを含む加圧流動床複合発電プラントに係り、特に、プラント通常停止時および緊急停止時の信頼性を向上させるとともに、所内動力を低減する手段に関する。
【０００２】
【従来の技術】
図８は、従来の加圧流動床複合発電プラントの系統構成の一例を示す系統図である。この加圧流動床複合発電プラントにおいては、空気圧縮機１と加圧流動床ボイラ６との間の空気供給配管２４および加圧流動床ボイラ６とガスタービン２と間の高温ガス供給配管２５にボイラバイパス配管４１を設置するとともに、高温ガス供給配管２５とボイラバイパス配管４１との合流点とガスタービン出口配管２８との間に高温ガス排出配管２９および高温ガス排出弁３０を設置し、障害時にボイラバイパス配管４１と高温ガス排出配管２９に空気および高温ガスを流すことが提案されている。なお、この種の装置として関連するものには、例えば特開平９−５０１０７など挙げられる。
【０００３】
【発明が解決しようとする課題】
このような従来の方法では、空気および高温ガスの混合ガスが煙突１０に排出されるため、ガスタービン出口配管２８から煙突１０までの系統を高温のガスに対応可能な設備とする必要がある。
【０００４】
この混合ガスを冷却するため、高温ガス排出配管３０の接続先を高温排熱回収熱交換器８の入口側に回収することも考えられるが、６０％から１００％程度のガスを処理する必要があるため、高温排熱回収器８出口の給水がフラッシュしてスチーミングが発生し、機器を損傷することが予想される。また、障害発生時の数秒間は、圧力を制御する必要があり、制御が非常に複雑になることが予想される。さらに、空気圧縮機１と加圧流動床ボイラ６との間の圧力が、一定圧力に保持されるので、ガスタービン停止時に加圧流動床ボイラ６とガスタービン２との間の高温ガスが空気圧縮機１に逆流し、空気圧縮機１を損傷することが予想される。したがって、加圧流動床ボイラ６のガス温度および金属の温度が低下するまで、ガスタービン２を連続的に運転する必要がある。
【０００５】
本発明の目的は、プラント通常停止時および緊急停止時、低温排熱回収熱交換器出口の復水および高温排熱回収熱交換器出口の給水のスチーミングを防止し、プラントの信頼性を上げ、停止時の所内動力を低減する手段を備えた加圧流動床複合発電プラントを提供することである。
【０００６】
【課題を解決するための手段】
本発明は、上記目的を達成するために、加圧流動床ボイラと加圧流動床ボイラに空気を供給する空気圧縮機と加圧流動床ボイラの高温ガスにより駆動されるガスタービンと加圧流動床ボイラの蒸気により駆動される蒸気タービンとガスタービンおよび蒸気タービンにより駆動される発電機とを含み、空気圧縮機から加圧流動床ボイラに圧縮空気を供給する空気供給配管と加圧流動床ボイラからガスタービンに高温ガスを供給する高温ガス配管とを接続する空気供給弁を設置したボイラバイパス管路を有する空気加圧流動床複合発電プラントにおいて、プラント通常停止時または緊急停止時に閉じる空気圧縮機出口弁を空気供給配管に設け、プラント通常停止時または緊急停止時に閉じるガスタービン入口弁を高温ガス配管に設け、プラント通常停止時または緊急停止時に開き空気圧縮機の出口からガスタービン入口までの間の空気および高温ガスをガスタービンの排ガス出口部に排出する高温ガス排出配管および高温ガス排出弁を設けた加圧流動床複合発電プラントを提案する。
【０００７】
本発明は、また、加圧流動床ボイラと加圧流動床ボイラに空気を供給する空気圧縮機と加圧流動床ボイラの高温ガスにより駆動されるガスタービンと加圧流動床ボイラの蒸気により駆動される蒸気タービンとガスタービンおよび蒸気タービンにより駆動される発電機とを含み、空気圧縮機から加圧流動床ボイラに圧縮空気を供給する空気供給配管と加圧流動床ボイラからガスタービンに高温ガスを供給する高温ガス配管とを接続する空気供給弁を設置したボイラバイパス管路を有する空気加圧流動床複合発電プラントにおいて、プラント通常停止時または緊急停止時に閉じる空気圧縮機出口弁を空気供給配管に設け、プラント通常停止時または緊急停止時に閉じるガスタービン入口弁を高温ガス配管に設け、プラント通常停止時または緊急停止時に開き空気圧縮機の出口からガスタービン入口までの間の空気および高温ガスをガスタービンの入口部に排出する高温ガス排出配管および高温ガス排出弁をガスタービン入口弁と並列に設けた加圧流動床複合発電プラントを提案する。
【０００８】
いずれの場合も、排出した高温ガスを冷却し希釈するために窒素または空気を供給するガス供給配管およびガス供給弁を追加して設置できる。
【０００９】
本発明は、さらに、加圧流動床ボイラと加圧流動床ボイラに空気を供給する空気圧縮機と加圧流動床ボイラの高温ガスにより駆動されるガスタービンと加圧流動床ボイラの蒸気により駆動される蒸気タービンとガスタービンおよび蒸気タービンにより駆動される発電機とを含み、空気圧縮機から加圧流動床ボイラに圧縮空気を供給する空気供給配管と加圧流動床ボイラからガスタービンに高温ガスを供給する高温ガス配管とを接続する空気供給弁を設置したボイラバイパス管路を有する空気加圧流動床複合発電プラントにおいて、プラント通常停止時または緊急停止時に閉じる空気圧縮機出口弁を空気供給配管に設け、プラント通常停止時または緊急停止時に閉じるガスタービン入口弁を高温ガス配管に設け、プラント通常停止時または緊急停止時に開き空気圧縮機出口からガスタービンまでの間の空気および高温ガスを大気に排出する高温ガス排出配管および高温ガス排出弁を設け、排出した高温ガスを冷却し希釈するために窒素または空気を供給するガス供給配管およびガス供給弁を設けた加圧流動床複合発電プラントを提案する。
【００１０】
上記いずれの加圧流動床複合発電プラントにおいても、加圧流動床ボイラの圧力および出口温度と、空気圧縮機出口弁，ガスタービン入口弁，空気供給弁の開閉状態とに応じて、空気圧縮機出口弁，ガスタービン入口弁，空気供給弁，高温ガス排出弁，ガス供給弁の開度を制御する高温ガス排出制御装置を設ける。
【００１１】
この高温ガス排出制御装置は、空気圧縮機からガスタービン入口弁までの間の減圧完了後、高温ガス排出弁を全閉してからの自然放熱の経過時間を計測するタイマを備えてもよい。
【００１２】
【発明の実施の形態】
次に、図１〜図７を参照して、本発明による加圧流動床複合発電プラントの実施例を説明する。
【００１３】
《実施例１》
図１は、本発明による加圧流動床複合発電プラントの実施例１の構成を示す系統図である。起動用電動機４を備えた空気圧縮機１は、空気入口弁２２から吸い込んだ空気を圧縮し、空気圧縮機出口弁２３，空気供給配管２４を介して、圧縮空気を加圧流動床ボイラ圧力容器５内の加圧流動床ボイラ６に供給する。加圧流動床ボイラ６からの高圧ガスは、高温ガス配管２５，高温ガス除塵装置７，ガスタービン入口弁２６を介して、ガスタービン２に供給され、ガスタービン２を駆動し、ガスタービン発電機３により、エネルギーを電力に変換される。ガスタービン２で仕事をした高圧ガスは、ガスタービン出口配管２８，高温排熱回収熱交換器８，低温排熱回収熱交換器９を通り、煙突１０から大気に排出される。
【００１４】
一方、加圧流動床ボイラ６で加熱された水は、汽水分離器２１により、水蒸気のみとなり、主蒸気配管３４により高圧タービン１１に導かれる。高圧タービン１１で仕事をした蒸気は、低温再熱蒸気配管３５で加圧流動床ボイラ６に戻されて再加熱され、高温再熱蒸気配管３６で中圧タービン１２に導かれる。中圧タービン１２で仕事をした蒸気は、低圧タービン１３に導かれる。高圧タービン１１，中圧タービン１２，低圧タービン１３には、共軸の蒸気タービン用発電機１４を設置してあり、蒸気エネルギーを電力に変換する。低圧タービン１３を通過した蒸気は、復水器１５により冷却され、復水される。復水された水は、復水ポンプ１６により加圧されて、低圧給水加熱器１７，上記低温排熱回収熱交換器９を通り、脱気器１８で脱気される。さらに、給水ポンプ１９により加圧されて、高圧給水加熱器２０，上記高温排熱回収熱交換器８を通り、再び、加圧流動床ボイラ圧力容器５内の加圧流動床ボイラ６に供給される。なお、汽水分離器２１は、汽水分離器レベル調節弁３７を備えた配管により、復水器１５に接続されている。
【００１５】
空気圧縮機１の出口とガスタービン２の入口との間には、空気供給弁２７を設けたバイパス配管を接続してある。また、加圧流動床ボイラ圧力容器５には、加圧流動床ボイラ圧力容器圧力検出器３１を取り付け、高温ガス配管２５には、加圧流動床ボイラ温度検出器３２を取り付けてある。
【００１６】
本実施例１においては、特に、ガスタービン入口弁２６よりも上流の高温ガス配管２５とガスタービン出口配管２８との間に、高温ガス排出弁３０を持った高温ガス排出配管２９を接続してある。
【００１７】
少なくとも加圧流動床ボイラ圧力容器圧力検出器３１および加圧流動床ボイラ温度検出器３２などからの信号を取り込む高温ガス排出制御装置３３は、検出信号に応じて、空気圧縮機出口弁２３，ガスタービン入口弁２６，空気供給弁２７，高温ガス排出弁３０の開閉を制御する。
【００１８】
本実施例１において、通常運転時、空気圧縮機入口弁２２から空気圧縮機１に取り込まれた空気は、空気供給配管２４により加圧流動床ボイラ圧力容器５内の加圧流動床ボイラ６に導かれる。加圧流動床ボイラ６からの高温ガスは、高温ガス配管２５により高温ガス除塵装置７に導かれ、灰などを除去した後、高温ガス配管２５によりガスタービン２に供給され、ガスタービン用発電機３を駆動し、発電する。ガスタービン２からの排ガスは、ガスタービン出口配管２８により高温排熱回収熱交換器８および低温排熱回収熱交換器９に導かれ、蒸気タービン系に熱回収された後、煙突１０から大気に放出される。
【００１９】
一方、加圧流動床ボイラ６で発生した蒸気は、主蒸気配管３４，高圧タービン１１，低温再熱蒸気配管３５，加圧流動床ボイラ６，高温再熱蒸気配管３６，中圧タービン１２，低圧タービン１３を通り、復水器１５に至る間に、蒸気タービン用発電機１４を駆動し、発電する。復水器１５で冷却され凝縮し復水となった水は、復水ポンプ１６で昇圧され、低圧給水加熱器１７および低温排熱回収熱交換器９で昇温され、脱気器１８に供給される。脱気器１８に供給された給水は、給水ポンプ１９でさらに昇圧され、高圧給水加熱器２０および高温排熱回収熱交換器８で昇温された後、加圧流動床ボイラ６に再び供給される。
【００２０】
プラント通常停止時は、加圧流動床ボイラ６内の燃料を燃焼させた後、空気圧縮機出口弁２３およびガスタービン入口弁２６を全閉し、空気供給弁２７を開くので、加圧流動床ボイラ６側は、隔離状態となる。これに対して、ガスタービン２側は、起動用電動機４により、ガスタービン２の回転数を１０％に降下させて運転される。その際、加圧流動床ボイラ６側の系統は、高温ガス排出配管２９の高温ガス排出弁３０を開き、ガスタービン出口配管２８に高温ガスを排出し、高温排熱回収熱交換器８および低温排熱回収熱交換器９により蒸気タービン系に熱を回収し、煙突１０から大気に排気し、減圧する。加圧流動床ボイラ６側の減圧が完了したら、ガスタービン２を停止させまたは低速ターニングさせる。
【００２１】
この場合に、高温ガス排出弁３０からの排出量は、高温ガスが空気圧縮機１に逆流することを防止するために、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下にする必要がある。高温ガス排出制御装置３３は、加圧流動床ボイラ圧力容器圧力検出器３１からの信号と加圧流動床ボイラ出口温度検出器３２からの信号とに応じて、高温ガス排出量を制御し、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下に、高温ガス排出量を制御する。さらに、高温ガス排出弁３０からの排出温度は、加圧流動床ボイラ６の温度検出器３２からの信号に応じて、ガスタービン出口の設備計画値以内に制御する。
【００２２】
一方、蒸気タービン系では、加圧流動床ボイラ６の発生蒸気量が減少し、汽水分離器２１の水位が上昇するので、汽水分離器レベル調節弁３７を介して、復水器１５に復水を十分に回収する。復水器１５に回収された給水は、復水器１５で冷却し、復水ポンプ１６で昇圧し、低圧給水加熱器１７および低温排熱回収熱交換器９を介して、脱気器１８に供給される。脱気器１８に供給された給水は、給水ポンプ１９で昇圧し、高圧給水加熱器２０および高温排熱回収熱交換器８で昇温した後、汽水分離器２１，汽水分離器レベル調節弁３７を介して、復水器１５に供給され、循環運転状態になる。
【００２３】
その結果、加圧流動床ボイラ６側の減圧時の高温ガスは、低温排熱回収熱交換器９および高温排熱回収熱交換器８で復水および給水に熱回収し、復水器１５により回収熱を冷却できることになる。
【００２４】
特に、加圧流動床ボイラ６側の減圧時の高温ガス量は、回転数が１０％の空気圧縮機１の風量と煙突１のドラフト風量と高温ガス排出量およびガスタービン入口弁２６の合計値となるが、通常運転時のガス量と比べて非常に少ないために、低温排熱回収熱交換器９出口の復水のスチーミングと高温排熱回収熱交換器８出口の給水のスチーミングとを防止できる。
【００２５】
さらに、復水ポンプ１６および給水ポンプ１９が動作可能であり高温排熱回収熱交換器９および低温排熱回収熱交換器９に給水を供給可能なモードの緊急停止時には、加圧流動床ボイラ６側の減圧時の高温ガスは、低温排熱回収熱交換器９および高温排熱回収熱交換器８で復水および給水に熱回収し、復水器１５により回収熱を冷却できるため、プラント通常停止と同様に運転できる。
【００２６】
《実施例２》
図２は、本発明による加圧流動床複合発電プラントの実施例２の構成を示す系統図である。実施例２は、ガスタービン出口配管２８ではなく、空気供給弁２７よりも上流の高温ガス配管２５に、高温ガス排出弁３０を持った高温ガス排出配管２９を接続し、ガスタービン入口弁２６をバイパスするようにしてある点が、実施例１と異なっている。
【００２７】
実施例２において、プラント通常停止時は、加圧流動床ボイラ６内の燃料を燃焼させた後、空気圧縮機出口弁２３およびガスタービン入口弁２６を全閉し、空気供給弁２７を開くので、加圧流動床ボイラ６側は、隔離状態となる。これに対して、ガスタービン２側は、起動用電動機４により、ガスタービン２の回転数を１０％に降下させて運転される。その際、加圧流動床ボイラ６側の系統は、高温ガス排出配管２９の高温ガス排出弁３０を開き、ガスタービン２の入口部に高温ガスを排出し、ガスタービン２を通過させ、高温排熱回収熱交換器８および低温排熱回収熱交換器９により蒸気タービン系に熱回収し、煙突１０から大気に排気し、減圧する。加圧流動床ボイラ６側の減圧が完了したら、ガスタービン２を停止させまたは低速ターニングさせる。
【００２８】
実施例２においても、実施例１と同様に運転できるため、低温排熱回収熱交換器９出口の復水のスチーミングと高温排熱回収熱交換器８出口の給水のスチーミングとを防止し、プラント通常停止時および緊急停止時に、プラントの信頼性を高め、停止時の所内動力を低減できる。
【００２９】
《実施例３》
図３は、本発明による加圧流動床複合発電プラントの実施例３の構成を示す系統図である。実施例３は、ガスタービン出口配管２８ではなく、高温ガス排出弁３０を持った高温ガス排出配管２９を大気に開放するように接続するとともに、ガス供給弁３８を備えたガス供給配管３９を併設した点が、実施例１と異なっている。
【００３０】
実施例３において、プラント通常停止時は、加圧流動床ボイラ６内の燃料を燃焼させた後、空気圧縮機出口弁２３およびガスタービン入口弁２６を全閉し、空気供給弁２７を開くので、加圧流動床ボイラ６側は、隔離状態となる。これに対して、ガスタービン２側は、起動用電動機４により、ガスタービン２の回転数を１０％に降下させて運転される。その際、加圧流動床ボイラ６側の系統は、高温ガス排出配管２９の高温ガス排出弁３０とガス供給弁３８とを開き、ガス供給配管３９からのガスにより高温ガスを冷却または希釈した後、大気に排出する。加圧流動床ボイラ６側の減圧が完了したら、ガスタービン２を停止させまたは低速ターニングさせる。
【００３１】
この場合に、高温ガス排出弁３０からの排出量は、高温ガスが空気圧縮機１に逆流することを防止するために、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下にする必要がある。高温ガス排出制御装置３３は、加圧流動床ボイラ圧力容器圧力検出器３１からの信号と加圧流動床ボイラ出口温度検出器３２からの信号とに応じて、高温ガス排出量を制御し、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下に、高温ガス排出量を制御する。さらに、高温ガス排出弁３０からの排出温度は、加圧流動床ボイラ６の温度検出器３２からの信号に応じて、ガスタービン出口の設備計画値以内に制御する。
【００３２】
また、高温ガス排出制御装置３３は、ガス供給弁３８からの冷却および希釈に必要なガスすなわち窒素または空気も制御するので、高温ガス中の一酸化炭素などの有害成分を希釈し、大気に排出できる。
【００３３】
一方、ガスタービン２側は、回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量とガスタービン入口弁２６のリーク量との合計値を、低温排熱回収熱交換器９および高温排熱回収熱交換器８の出口を介して、煙突１０から大気に放出する。この場合は、ガス量が通常運転時のガス量と比べて非常に少ないので、低温排熱回収熱交換器９出口の復水のスチーミングと高温排熱回収熱交換器８出口の給水のスチーミングとを防止できる。
【００３４】
《実施例４》
図４は、本発明による加圧流動床複合発電プラントの実施例４の構成を示す系統図である。実施例４は、実施例１と同様に、ガスタービン入口弁２６よりも上流の高温ガス配管２５とガスタービン出口配管２８との間に、高温ガス排出弁３０を持った高温ガス排出配管２９を接続した上に、高温ガス排出弁３０よりも下流に、ガス供給弁３８を備えたガス供給配管３９を併設してある。
【００３５】
実施例４において、プラント通常停止時は、加圧流動床ボイラ６内の燃料を燃焼させた後、空気圧縮機出口弁２３およびガスタービン入口弁２６を全閉し、空気供給弁２７を開くので、加圧流動床ボイラ６側は、隔離状態となる。これに対して、ガスタービン２側は、起動用電動機４により、ガスタービン２の回転数を１０％に降下させて、転される。その際、加圧流動床ボイラ６側の系統は、高温ガス排出配管２９の高温ガス排出弁３０とガス供給弁３８とを開き、ガス供給配管３９からのガスにより高温ガスを冷却または希釈しながら、ガスタービン出口配管２８を介して、高温排熱回収熱交換器８および低温排熱回収熱交換器９により蒸気タービン系に熱回収した後、煙突１０から大気に排出する。加圧流動床ボイラ６側の減圧が完了したら、ガスタービン２を停止させまたは低速ターニングさせる。
【００３６】
この場合に、高温ガス排出弁３０からの排出量は、高温ガスが空気圧縮機１に逆流することを防止するために、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下にする必要がある。高温ガス排出制御装置３３は、加圧流動床ボイラ圧力容器圧力検出器３１からの信号と加圧流動床ボイラ出口温度検出器３２からの信号とに応じて、高温ガス排出量を制御し、ガスタービン入口弁２６のリーク量と高温ガス排出量との合計値を回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量との合計値以下に、高温ガス排出量を制御する。さらに、高温ガス排出弁３０からの排出温度は、加圧流動床ボイラ６の温度検出器３２からの信号に応じて、ガスタービン出口の設備計画値以内に制御する。
【００３７】
また、高温ガス排出制御装置３３は、ガス供給弁３８からの冷却および希釈に必要なガスすなわち窒素または空気も制御するので、高温ガス中の一酸化炭素などの有害成分を希釈し、大気に排出できる。
【００３８】
一方、ガスタービン２側は、回転数が１０％の空気圧縮機１の風量と煙突１０のドラフト風量とガスタービン入口弁２６のリーク量との合計値を、低温排熱回収熱交換器９および高温排熱回収熱交換器８の出口を介して、煙突１０から大気に放出する。この場合は、ガス量が通常運転時のガス量と比べて非常に少ないので、低温排熱回収熱交換器９出口の復水のスチーミングと高温排熱回収熱交換器８出口の給水のスチーミングとを防止できる。
【００３９】
なお、実施例４は、実施例１の高温ガス排出弁３０よりも下流に、ガス供給弁３８を備えたガス供給配管３９を併設した例であったが、実施例２の高温ガス排出弁３０よりも下流に、ガス供給弁３８を備えたガス供給配管３９を併設してもよいことは、明らかであろう。
【００４０】
また、上記各実施例において、空気圧縮機１の回転数を１０％に維持することは、単なる例示であって、本発明は、この数値に限定されない。
【００４１】
図５は、本発明による加圧流動床複合発電プラントの各実施例における高温ガス排出制御装置３３の制御ロジックの系統構成を示す図である。高温ガス排出弁３０(およびガス供給弁３８)は、ガスの状態値すなわち加圧流動床ボイラ圧力容器５の圧力検出値３１および加圧流動床ボイラ６の温度検出値３２と、空気圧縮機出口弁２３，ガスタービン入口弁２６，空気供給弁２７の開閉状態とに応じて制御される。
【００４２】
特に、加圧流動床ボイラ６の温度検出値３２は、ガスの自燃温度を基準値とするため、高温ガス排出弁３０が開いて高温ガスが流れても、局部的な温度上昇を回避できるように制御する。すなわち、未燃分のガスが高温ガス配管２５または機器に残っていても、自燃温度以下とし、未燃分の燃焼による温度上昇を防止できるようにする。
【００４３】
さらに、空気圧縮機１からガスタービン入口弁２６までの間の減圧完了後に、高温ガス排出弁３０を全閉すると、空気圧縮機１からガスタービン入口弁２６までの間の金属の温度に応じて、空気圧縮機１からガスタービン入口弁２６までの間の圧力が上昇することが考えられるが、このような現象に対しては、タイマを設けて自然放熱すると、十分に冷却できる。
【００４４】
図６は、本発明による加圧流動床複合発電プラントの各実施例における風量の時間的変化を示す図である。図７は、本発明による加圧流動床複合発電プラントの各実施例における弁２３，２６，２７，３０の開閉状態と加圧流動床ボイラ圧力容器６の圧力値３１とガスタービン回転数との関係を示す図である。
【００４５】
図６および図７に示すように、空気圧縮機出口弁２３とガスタービン入口弁２６とを全閉にして、空気供給弁２７と高温ガス排出弁３０とを開くと、加圧流動床ボイラ６の圧力が低下し、ガスタービン回転数が低下する。一方、風量は、高温ガス排出弁３０からの風量とガスタービン入口弁２６からのリーク量との合計値以下、または、空気圧縮機１の風量と煙突１０のドラフト量との合計値以下になるので、高温ガスが、空気圧縮機１の側に逆流することがない。なお、ドラフト量は、煙突１０の入口のガス温度と大気温度とに基づいて算出できる。
【００４６】
【発明の効果】
本発明によれば、加圧流動床ボイラとガスタービンと蒸気タービンとからなる加圧流動床複合発電プラントにおいて、低温排熱回収熱交換器，高温排熱回収熱交換器出口の復水および給水のスチーミングを防止し、プラント通常停止時および緊急停止時に、プラントの信頼性を高め、停止時の所内動力を低減できる。
【図面の簡単な説明】
【図１】本発明による加圧流動床複合発電プラントの実施例１の構成を示す系統図である。
【図２】本発明による加圧流動床複合発電プラントの実施例２の構成を示す系統図である。
【図３】本発明による加圧流動床複合発電プラントの実施例３の構成を示す系統図である。
【図４】本発明による加圧流動床複合発電プラントの実施例４の構成を示す系統図である。
【図５】本発明による加圧流動床複合発電プラントの各実施例における高温ガス排出制御装置の制御ロジックの系統構成を示す図である。
【図６】本発明による加圧流動床複合発電プラントの各実施例における風量の時間的変化を示す図である。
【図７】本発明による加圧流動床複合発電プラントの各実施例における弁開閉状態と加圧流動床ボイラ圧力容器側圧力とガスタービン回転数との関係を示す図である。
【図８】従来の加圧流動床複合発電プラントの系統構成の一例を示す系統図である。
【符号の説明】
１ 空気圧縮機
２ ガスタービン
３ ガスタービン発電機
４ 起動用電動機
５ 加圧流動床ボイラ圧力容器
６ 加圧流動床ボイラ
７ 高温ガス除塵装置
８ 高温排熱回収熱交換器
９ 低温排熱回収熱交換器
１０ 煙突
１１ 高圧タービン
１２ 中圧タービン
１３ 低圧タービン
１４ 蒸気タービン用発電機
１５ 復水器
１６ 復水ポンプ
１７ 低圧給水加熱器
１８ 脱気器
１９ 給水ポンプ
２０ 高圧給水加熱器
２１ 汽水分離器
２２ 空気入口弁
２３ 空気圧縮機出口弁
２４ 空気供給配管
２５ 高温ガス配管
２６ ガスタービン入口弁
２７ 空気供給弁
２８ ガスタービン出口配管
２９ 高温ガス排出配管
３０ 高温ガス排出弁
３１ 加圧流動床ボイラ圧力容器圧力検出器
３２ 加圧流動床ボイラ温度検出器
３３ 高温ガス排出制御装置
３４ 主蒸気配管
３５ 低温再熱蒸気配管
３６ 高温再熱蒸気配管
３７ 汽水分離器レベル調節弁
３８ ガス供給弁
３９ ガス供給配管
４０ 加圧流動床ボイラバイパス弁
４１ 加圧流動床ボイラバイパス配管[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pressurized fluidized bed combined power plant including a pressurized fluidized bed boiler, a gas turbine, and a steam turbine, and in particular, improves the reliability at the time of normal stop and emergency stop of the plant and reduces in-house power. It is related with the means to do.
[0002]
[Prior art]
FIG. 8 is a system diagram showing an example of a system configuration of a conventional pressurized fluidized bed combined power plant. In this pressurized fluidized bed combined power plant, an air supply pipe 24 between the air compressor 1 and the pressurized fluidized bed boiler 6 and a high temperature gas supply pipe 25 between the pressurized fluidized bed boiler 6 and the gas turbine 2 are provided. A boiler bypass pipe 41 is installed, and a high temperature gas discharge pipe 29 and a high temperature gas discharge valve 30 are installed between the junction of the high temperature gas supply pipe 25 and the boiler bypass pipe 41 and the gas turbine outlet pipe 28. It has been proposed that air and high-temperature gas flow through the boiler bypass pipe 41 and the high-temperature gas discharge pipe 29. An example of a device of this type is JP-A-9-50107.
[0003]
[Problems to be solved by the invention]
In such a conventional method, since a mixed gas of air and high-temperature gas is discharged to the chimney 10, the system from the gas turbine outlet pipe 28 to the chimney 10 needs to be equipment capable of handling high-temperature gas.
[0004]
In order to cool this mixed gas, it is conceivable to recover the connection destination of the high temperature gas discharge pipe 30 to the inlet side of the high temperature exhaust heat recovery heat exchanger 8, but it is necessary to process about 60% to 100% of the gas. Therefore, it is expected that the water supply at the outlet of the high-temperature exhaust heat recovery unit 8 is flushed, steaming occurs, and the equipment is damaged. Further, it is necessary to control the pressure for a few seconds when the failure occurs, and it is expected that the control becomes very complicated. Furthermore, since the pressure between the air compressor 1 and the pressurized fluidized bed boiler 6 is maintained at a constant pressure, the hot gas between the pressurized fluidized bed boiler 6 and the gas turbine 2 is air when the gas turbine is stopped. It is expected that the air flows back to the compressor 1 and damages the air compressor 1. Therefore, it is necessary to operate the gas turbine 2 continuously until the gas temperature and the metal temperature of the pressurized fluidized bed boiler 6 are lowered.
[0005]
The object of the present invention is to prevent steaming of the condensate at the outlet of the low-temperature exhaust heat recovery heat exchanger and the feed water at the outlet of the high-temperature exhaust heat recovery heat exchanger at the time of normal stoppage and emergency stop of the plant, thereby improving the reliability of the plant. Another object of the present invention is to provide a pressurized fluidized bed combined power plant provided with means for reducing in-house power when stopped.
[0006]
[Means for Solving the Problems]
To achieve the above object, the present invention provides a pressurized fluidized bed boiler, an air compressor for supplying air to the pressurized fluidized bed boiler, a gas turbine driven by the high temperature gas of the pressurized fluidized bed boiler, and a pressurized fluidized An air supply pipe and a pressurized fluidized bed boiler for supplying compressed air from an air compressor to a pressurized fluidized bed boiler, including a steam turbine driven by the steam of the floor boiler, a gas turbine and a generator driven by the steam turbine Air compressor closed at normal or emergency stop in an air pressurized fluidized bed combined power plant having a boiler bypass line installed with an air supply valve for connecting a high temperature gas pipe for supplying a high temperature gas to the gas turbine An outlet valve is provided in the air supply piping, and a gas turbine inlet valve that is closed during normal plant shutdown or emergency shutdown is installed in the high-temperature gas piping. Pressurized fluidized bed with high-temperature gas discharge piping and high-temperature gas discharge valve for discharging air and high-temperature gas from the outlet of the air compressor to the gas turbine inlet at the time of stoppage or emergency stop to the exhaust gas outlet of the gas turbine A combined power plant is proposed.
[0007]
The present invention also includes a pressurized fluidized bed boiler, an air compressor that supplies air to the pressurized fluidized bed boiler, a gas turbine driven by the hot gas of the pressurized fluidized bed boiler, and a steam of the pressurized fluidized bed boiler. A gas turbine and a generator driven by the steam turbine, an air supply pipe for supplying compressed air from the air compressor to the pressurized fluidized bed boiler, and a hot gas from the pressurized fluidized bed boiler to the gas turbine In an air pressurized fluidized bed combined power plant with a boiler bypass line installed with an air supply valve that connects to the hot gas pipe that supplies the air compressor outlet valve that closes at the time of normal or emergency stop of the plant A gas turbine inlet valve is installed in the hot gas piping that closes at a normal or emergency stop of the plant. Pressurized flow with a high-temperature gas discharge pipe and a high-temperature gas discharge valve in parallel with the gas turbine inlet valve that are sometimes opened from the outlet of the air compressor to the gas turbine inlet and discharge the air and hot gas to the inlet of the gas turbine A floor combined power plant is proposed.
[0008]
In either case, a gas supply pipe and a gas supply valve for supplying nitrogen or air can be additionally installed to cool and dilute the discharged hot gas.
[0009]
The present invention further includes a pressurized fluidized bed boiler, an air compressor for supplying air to the pressurized fluidized bed boiler, a gas turbine driven by the hot gas of the pressurized fluidized bed boiler, and a steam of the pressurized fluidized bed boiler. A gas turbine and a generator driven by the steam turbine, an air supply pipe for supplying compressed air from the air compressor to the pressurized fluidized bed boiler, and a hot gas from the pressurized fluidized bed boiler to the gas turbine In an air pressurized fluidized bed combined power plant with a boiler bypass line installed with an air supply valve that connects to the hot gas pipe that supplies the air compressor outlet valve that closes at the time of normal or emergency stop of the plant A gas turbine inlet valve is installed in the hot gas piping that closes when the plant is normally stopped or emergency stopped, and when the plant is normally stopped or emergency A high-temperature gas discharge pipe and a high-temperature gas discharge valve are provided to discharge air and high-temperature gas from the outlet of the air compressor to the gas turbine to the atmosphere at the time of shutdown, and nitrogen or air is supplied to cool and dilute the discharged high-temperature gas. A pressurized fluidized bed combined power plant with a gas supply pipe and a gas supply valve is proposed.
[0010]
In any of the above pressurized fluidized bed combined power plants, depending on the pressure and outlet temperature of the pressurized fluidized bed boiler and the open / closed states of the air compressor outlet valve, gas turbine inlet valve, and air supply valve, the air compressor An outlet valve, a gas turbine inlet valve, an air supply valve, a hot gas discharge valve, and a hot gas discharge control device for controlling the opening degree of the gas supply valve are provided.
[0011]
The high temperature gas discharge control device may include a timer that measures the elapsed time of natural heat radiation after the high temperature gas discharge valve is fully closed after completion of pressure reduction from the air compressor to the gas turbine inlet valve.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
Next, an embodiment of a pressurized fluidized bed combined power plant according to the present invention will be described with reference to FIGS.
[0013]
Example 1
FIG. 1 is a system diagram showing the configuration of Example 1 of a pressurized fluidized bed combined power plant according to the present invention. The air compressor 1 having the starter motor 4 compresses the air sucked from the air inlet valve 22, and compresses the compressed air through the air compressor outlet valve 23 and the air supply pipe 24. 5 is supplied to the pressurized fluidized bed boiler 6. The high-pressure gas from the pressurized fluidized bed boiler 6 is supplied to the gas turbine 2 via the high-temperature gas pipe 25, the high-temperature gas dust removing device 7, and the gas turbine inlet valve 26, and drives the gas turbine 2, thereby generating a gas turbine generator. 3 converts energy into electric power. The high-pressure gas that has worked in the gas turbine 2 passes through the gas turbine outlet pipe 28, the high-temperature exhaust heat recovery heat exchanger 8, and the low-temperature exhaust heat recovery heat exchanger 9, and is discharged from the chimney 10 to the atmosphere.
[0014]
On the other hand, the water heated by the pressurized fluidized bed boiler 6 becomes only steam by the brackish water separator 21 and is led to the high-pressure turbine 11 by the main steam pipe 34. The steam that has worked in the high-pressure turbine 11 is returned to the pressurized fluidized bed boiler 6 through the low-temperature reheat steam pipe 35 and reheated, and is guided to the intermediate-pressure turbine 12 through the high-temperature reheat steam pipe 36. The steam that has worked in the intermediate pressure turbine 12 is guided to the low pressure turbine 13. The high-pressure turbine 11, the intermediate-pressure turbine 12, and the low-pressure turbine 13 are provided with a coaxial steam turbine generator 14 that converts steam energy into electric power. The steam that has passed through the low-pressure turbine 13 is cooled by the condenser 15 and condensed. The condensed water is pressurized by the condensate pump 16, passes through the low-pressure feed water heater 17 and the low-temperature exhaust heat recovery heat exchanger 9, and is deaerated by the deaerator 18. Further, it is pressurized by the feed water pump 19, passes through the high pressure feed water heater 20 and the high temperature exhaust heat recovery heat exchanger 8, and is supplied again to the pressurized fluidized bed boiler 6 in the pressurized fluidized bed boiler pressure vessel 5. The The brackish water separator 21 is connected to the condenser 15 by a pipe provided with a brackish water separator level control valve 37.
[0015]
A bypass pipe provided with an air supply valve 27 is connected between the outlet of the air compressor 1 and the inlet of the gas turbine 2. A pressurized fluidized bed boiler pressure vessel pressure detector 31 is attached to the pressurized fluidized bed boiler pressure vessel 5, and a pressurized fluidized bed boiler temperature detector 32 is attached to the high temperature gas pipe 25.
[0016]
In the first embodiment, in particular, a high-temperature gas discharge pipe 29 having a high-temperature gas discharge valve 30 is connected between the high-temperature gas pipe 25 upstream of the gas turbine inlet valve 26 and the gas turbine outlet pipe 28. is there.
[0017]
The high-temperature gas discharge control device 33 that takes in signals from at least the pressurized fluidized bed boiler pressure vessel pressure detector 31 and the pressurized fluidized bed boiler temperature detector 32, etc. The opening and closing of the turbine inlet valve 26, the air supply valve 27, and the hot gas discharge valve 30 are controlled.
[0018]
In the first embodiment, during normal operation, air taken into the air compressor 1 from the air compressor inlet valve 22 is supplied to the pressurized fluidized bed boiler 6 in the pressurized fluidized bed boiler pressure vessel 5 through the air supply pipe 24. Led. The high-temperature gas from the pressurized fluidized bed boiler 6 is guided to the high-temperature gas dust removing device 7 through the high-temperature gas pipe 25 and, after removing ash and the like, is supplied to the gas turbine 2 through the high-temperature gas pipe 25 and is a gas turbine generator. 3 is driven to generate electricity. The exhaust gas from the gas turbine 2 is led to the high-temperature exhaust heat recovery heat exchanger 8 and the low-temperature exhaust heat recovery heat exchanger 9 by the gas turbine outlet pipe 28 and is recovered by the steam turbine system, and then is discharged from the chimney 10 to the atmosphere. Released.
[0019]
On the other hand, the steam generated in the pressurized fluidized bed boiler 6 is the main steam pipe 34, the high pressure turbine 11, the low temperature reheat steam pipe 35, the pressurized fluidized bed boiler 6, the high temperature reheat steam pipe 36, the intermediate pressure turbine 12, the low pressure. While passing through the turbine 13 and reaching the condenser 15, the steam turbine generator 14 is driven to generate power. The water cooled and condensed by the condenser 15 and condensed into condensate is boosted by the condensate pump 16, heated by the low-pressure feed water heater 17 and the low-temperature exhaust heat recovery heat exchanger 9, and supplied to the deaerator 18. Is done. The feed water supplied to the deaerator 18 is further pressurized by a feed water pump 19, heated by a high-pressure feed water heater 20 and a high-temperature exhaust heat recovery heat exchanger 8, and then supplied again to the pressurized fluidized bed boiler 6. The
[0020]
When the plant is normally stopped, the fuel in the pressurized fluidized bed boiler 6 is burned, and then the air compressor outlet valve 23 and the gas turbine inlet valve 26 are fully closed and the air supply valve 27 is opened. The boiler 6 side is in an isolated state. On the other hand, the gas turbine 2 side is operated by lowering the rotational speed of the gas turbine 2 to 10% by the starting electric motor 4. At that time, the system on the pressurized fluidized bed boiler 6 side opens the high temperature gas discharge valve 30 of the high temperature gas discharge pipe 29, discharges the high temperature gas to the gas turbine outlet pipe 28, and discharges the high temperature exhaust heat recovery heat exchanger 8 and the low temperature. Heat is recovered in the steam turbine system by the exhaust heat recovery heat exchanger 9, exhausted from the chimney 10 to the atmosphere, and decompressed. When the pressure reduction on the pressurized fluidized bed boiler 6 side is completed, the gas turbine 2 is stopped or turned at a low speed.
[0021]
In this case, the discharge amount from the high temperature gas discharge valve 30 is the sum of the leak amount of the gas turbine inlet valve 26 and the high temperature gas discharge amount in order to prevent the high temperature gas from flowing back to the air compressor 1. It is necessary to make it equal to or less than the total value of the air volume of the air compressor 1 whose rotational speed is 10% and the draft volume of the chimney 10. The hot gas discharge control device 33 controls the hot gas discharge amount according to the signal from the pressurized fluidized bed boiler pressure vessel pressure detector 31 and the signal from the pressurized fluidized bed boiler outlet temperature detector 32, and the gas The high-temperature gas discharge amount is controlled so that the total value of the leak amount of the turbine inlet valve 26 and the high-temperature gas discharge amount is equal to or less than the total value of the air amount of the air compressor 1 and the draft amount of the chimney 10 having a rotation speed of 10%. Furthermore, the discharge temperature from the hot gas discharge valve 30 is controlled within the planned facility value of the gas turbine outlet according to the signal from the temperature detector 32 of the pressurized fluidized bed boiler 6.
[0022]
On the other hand, in the steam turbine system, the amount of steam generated in the pressurized fluidized bed boiler 6 decreases, and the water level of the brackish water separator 21 rises, so the condensate 15 is condensed via the brackish water separator level control valve 37. Fully recover. The feed water recovered in the condenser 15 is cooled by the condenser 15, boosted by the condensate pump 16, and supplied to the deaerator 18 through the low-pressure feed water heater 17 and the low-temperature exhaust heat recovery heat exchanger 9. Supplied. The feed water supplied to the deaerator 18 is boosted by the feed water pump 19 and heated by the high-pressure feed water heater 20 and the high-temperature exhaust heat recovery heat exchanger 8, and then the brackish water separator 21 and the brackish water separator level control valve 37. And is supplied to the condenser 15 through a circulation operation state.
[0023]
As a result, the high-temperature gas at the time of depressurization on the pressurized fluidized bed boiler 6 side is recovered by the low-temperature exhaust heat recovery heat exchanger 9 and the high-temperature exhaust heat recovery heat exchanger 8 to condensate and feed water. The recovered heat can be cooled.
[0024]
In particular, the amount of high-temperature gas at the time of pressure reduction on the pressurized fluidized bed boiler 6 side is the sum of the air volume of the air compressor 1 whose rotational speed is 10%, the draft volume of the chimney 1, the high-temperature gas discharge amount, and the gas turbine inlet valve 26. However, since it is very small compared to the amount of gas during normal operation, steaming of the condensate at the outlet of the low temperature exhaust heat recovery heat exchanger 9 and steaming of the feed water at the outlet of the high temperature exhaust heat recovery heat exchanger 8 Can be prevented.
[0025]
Further, during an emergency stop in a mode in which the condensate pump 16 and the feed water pump 19 are operable and the feed water can be supplied to the high temperature exhaust heat recovery heat exchanger 9 and the low temperature exhaust heat recovery heat exchanger 9, the pressurized fluidized bed boiler 6 The high-temperature gas at the time of decompression on the side can be recovered in the condensate and feed water by the low-temperature exhaust heat recovery heat exchanger 9 and the high-temperature exhaust heat recovery heat exchanger 8, and the recovered heat can be cooled by the condenser 15. You can drive as well as stop
[0026]
Example 2
FIG. 2 is a system diagram showing a configuration of a second embodiment of the pressurized fluidized bed combined power plant according to the present invention. In the second embodiment, a high temperature gas discharge pipe 29 having a high temperature gas discharge valve 30 is connected to the high temperature gas pipe 25 upstream of the air supply valve 27 instead of the gas turbine outlet pipe 28, and the gas turbine inlet valve 26 is connected to the high temperature gas discharge pipe 30. The second embodiment is different from the first embodiment in that it is bypassed.
[0027]
In Example 2, when the plant is normally stopped, the fuel in the pressurized fluidized bed boiler 6 is burned, and then the air compressor outlet valve 23 and the gas turbine inlet valve 26 are fully closed and the air supply valve 27 is opened. The pressurized fluidized bed boiler 6 side is in an isolated state. On the other hand, the gas turbine 2 side is operated by lowering the rotational speed of the gas turbine 2 to 10% by the starting electric motor 4. At that time, the system on the pressurized fluidized bed boiler 6 side opens the high-temperature gas discharge valve 30 of the high-temperature gas discharge pipe 29, discharges the high-temperature gas to the inlet of the gas turbine 2, passes the gas turbine 2, and Heat is recovered in the steam turbine system by the heat recovery heat exchanger 8 and the low-temperature exhaust heat recovery heat exchanger 9, exhausted from the chimney 10 to the atmosphere, and decompressed. When the pressure reduction on the pressurized fluidized bed boiler 6 side is completed, the gas turbine 2 is stopped or turned at a low speed.
[0028]
In Example 2, since it can be operated in the same manner as in Example 1, steaming of the condensate at the outlet of the low temperature exhaust heat recovery heat exchanger 9 and steaming of the feed water at the outlet of the high temperature exhaust heat recovery heat exchanger 8 are prevented. It is possible to improve the reliability of the plant and reduce the in-house power at the time of the stop at the time of normal stop and emergency stop of the plant.
[0029]
Example 3
FIG. 3 is a system diagram showing a configuration of a third embodiment of the pressurized fluidized bed combined power plant according to the present invention. In the third embodiment, not a gas turbine outlet pipe 28 but a high-temperature gas discharge pipe 29 having a high-temperature gas discharge valve 30 is connected to open to the atmosphere, and a gas supply pipe 39 having a gas supply valve 38 is also provided. This is different from the first embodiment.
[0030]
In Example 3, when the plant is normally stopped, the fuel in the pressurized fluidized bed boiler 6 is burned, and then the air compressor outlet valve 23 and the gas turbine inlet valve 26 are fully closed and the air supply valve 27 is opened. The pressurized fluidized bed boiler 6 side is in an isolated state. On the other hand, the gas turbine 2 side is operated by lowering the rotational speed of the gas turbine 2 to 10% by the starting electric motor 4. At that time, the system on the pressurized fluidized bed boiler 6 side opens the high-temperature gas discharge valve 30 and the gas supply valve 38 of the high-temperature gas discharge pipe 29 and cools or dilutes the high-temperature gas with the gas from the gas supply pipe 39. , Exhaust to the atmosphere. When the pressure reduction on the pressurized fluidized bed boiler 6 side is completed, the gas turbine 2 is stopped or turned at a low speed.
[0031]
In this case, the discharge amount from the high temperature gas discharge valve 30 is the sum of the leak amount of the gas turbine inlet valve 26 and the high temperature gas discharge amount in order to prevent the high temperature gas from flowing back to the air compressor 1. It is necessary to make it equal to or less than the total value of the air volume of the air compressor 1 whose rotational speed is 10% and the draft volume of the chimney 10. The hot gas discharge control device 33 controls the hot gas discharge amount according to the signal from the pressurized fluidized bed boiler pressure vessel pressure detector 31 and the signal from the pressurized fluidized bed boiler outlet temperature detector 32, and the gas The high-temperature gas discharge amount is controlled so that the total value of the leak amount of the turbine inlet valve 26 and the high-temperature gas discharge amount is equal to or less than the total value of the air amount of the air compressor 1 and the draft amount of the chimney 10 having a rotation speed of 10%. Furthermore, the discharge temperature from the hot gas discharge valve 30 is controlled within the planned facility value of the gas turbine outlet according to the signal from the temperature detector 32 of the pressurized fluidized bed boiler 6.
[0032]
The high-temperature gas discharge control device 33 also controls the gas necessary for cooling and dilution from the gas supply valve 38, that is, nitrogen or air, so that harmful components such as carbon monoxide in the high-temperature gas are diluted and discharged to the atmosphere. it can.
[0033]
On the other hand, the gas turbine 2 side calculates the total value of the air volume of the air compressor 1 whose rotational speed is 10%, the draft volume of the chimney 10 and the leak volume of the gas turbine inlet valve 26, and the low-temperature exhaust heat recovery heat exchanger 9 and It is discharged from the chimney 10 to the atmosphere via the outlet of the high-temperature exhaust heat recovery heat exchanger 8. In this case, since the amount of gas is very small compared to the amount of gas during normal operation, steaming of the condensate at the outlet of the low-temperature exhaust heat recovery heat exchanger 9 and steaming of the feed water at the outlet of the high-temperature exhaust heat recovery heat exchanger 8 are performed. Teaming can be prevented.
[0034]
Example 4
FIG. 4 is a system diagram showing a configuration of a fourth embodiment of the pressurized fluidized bed combined power plant according to the present invention. In the fourth embodiment, similarly to the first embodiment, a high-temperature gas discharge pipe 29 having a high-temperature gas discharge valve 30 is provided between the high-temperature gas pipe 25 upstream of the gas turbine inlet valve 26 and the gas turbine outlet pipe 28. In addition, a gas supply pipe 39 provided with a gas supply valve 38 is provided downstream of the hot gas discharge valve 30.
[0035]
In the fourth embodiment, when the plant is normally stopped, the fuel in the pressurized fluidized bed boiler 6 is burned, and then the air compressor outlet valve 23 and the gas turbine inlet valve 26 are fully closed and the air supply valve 27 is opened. The pressurized fluidized bed boiler 6 side is in an isolated state. On the other hand, the gas turbine 2 is rotated by lowering the rotational speed of the gas turbine 2 to 10% by the starting electric motor 4. At that time, the system on the pressurized fluidized bed boiler 6 side opens the high temperature gas discharge valve 30 and the gas supply valve 38 of the high temperature gas discharge pipe 29 while cooling or diluting the high temperature gas with the gas from the gas supply pipe 39. Then, heat is recovered in the steam turbine system by the high-temperature exhaust heat recovery heat exchanger 8 and the low-temperature exhaust heat recovery heat exchanger 9 via the gas turbine outlet pipe 28 and then discharged from the chimney 10 to the atmosphere. When the pressure reduction on the pressurized fluidized bed boiler 6 side is completed, the gas turbine 2 is stopped or turned at a low speed.
[0036]
In this case, the discharge amount from the high temperature gas discharge valve 30 is the sum of the leak amount of the gas turbine inlet valve 26 and the high temperature gas discharge amount in order to prevent the high temperature gas from flowing back to the air compressor 1. It is necessary to make it equal to or less than the total value of the air volume of the air compressor 1 whose rotational speed is 10% and the draft volume of the chimney 10. The hot gas discharge control device 33 controls the hot gas discharge amount according to the signal from the pressurized fluidized bed boiler pressure vessel pressure detector 31 and the signal from the pressurized fluidized bed boiler outlet temperature detector 32, and the gas The high-temperature gas discharge amount is controlled so that the total value of the leak amount of the turbine inlet valve 26 and the high-temperature gas discharge amount is equal to or less than the total value of the air amount of the air compressor 1 and the draft amount of the chimney 10 having a rotation speed of 10%. Furthermore, the discharge temperature from the hot gas discharge valve 30 is controlled within the planned facility value of the gas turbine outlet according to the signal from the temperature detector 32 of the pressurized fluidized bed boiler 6.
[0037]
The high-temperature gas discharge control device 33 also controls the gas necessary for cooling and dilution from the gas supply valve 38, that is, nitrogen or air, so that harmful components such as carbon monoxide in the high-temperature gas are diluted and discharged to the atmosphere. it can.
[0038]
On the other hand, the gas turbine 2 side calculates the total value of the air volume of the air compressor 1 whose rotational speed is 10%, the draft volume of the chimney 10 and the leak volume of the gas turbine inlet valve 26, and the low-temperature exhaust heat recovery heat exchanger 9 and It is discharged from the chimney 10 to the atmosphere via the outlet of the high-temperature exhaust heat recovery heat exchanger 8. In this case, since the amount of gas is very small compared to the amount of gas during normal operation, steaming of condensate at the outlet of the low-temperature exhaust heat recovery heat exchanger 9 and steaming of the water supply at the outlet of the high-temperature exhaust heat recovery heat exchanger 8 are performed. Teaming can be prevented.
[0039]
The fourth embodiment is an example in which the gas supply pipe 39 including the gas supply valve 38 is provided downstream of the high temperature gas discharge valve 30 of the first embodiment, but the high temperature gas discharge valve 30 of the second embodiment is also provided. It will be apparent that a gas supply pipe 39 including a gas supply valve 38 may be provided downstream of the gas supply valve 38.
[0040]
Moreover, in each said Example, maintaining the rotation speed of the air compressor 1 to 10% is a mere illustration, Comprising: This invention is not limited to this figure.
[0041]
FIG. 5 is a diagram showing a system configuration of the control logic of the hot gas discharge control device 33 in each embodiment of the pressurized fluidized bed combined power plant according to the present invention. The hot gas discharge valve 30 (and the gas supply valve 38) includes a gas state value, that is, a pressure detection value 31 of the pressurized fluidized bed boiler pressure vessel 5, a temperature detection value 32 of the pressurized fluidized bed boiler 6, and an air compressor outlet. Control is performed according to the open / closed state of the valve 23, the gas turbine inlet valve 26, and the air supply valve 27.
[0042]
In particular, since the temperature detection value 32 of the pressurized fluidized bed boiler 6 is based on the self-combustion temperature of the gas, even if the hot gas discharge valve 30 is opened and the hot gas flows, a local temperature rise can be avoided. To control. That is, even if unburned gas remains in the high-temperature gas pipe 25 or the equipment, the temperature is set to the self-burning temperature or less so that temperature rise due to unburned gas combustion can be prevented.
[0043]
Further, after the decompression between the air compressor 1 and the gas turbine inlet valve 26 is completed, when the hot gas discharge valve 30 is fully closed, the temperature of the metal between the air compressor 1 and the gas turbine inlet valve 26 depends on the temperature of the metal. It is conceivable that the pressure between the air compressor 1 and the gas turbine inlet valve 26 increases. However, for such a phenomenon, it is possible to cool sufficiently by providing a timer and naturally dissipating heat.
[0044]
FIG. 6 is a diagram showing temporal changes in the air volume in each example of the pressurized fluidized bed combined power plant according to the present invention. FIG. 7 shows the open / closed state of the valves 23, 26, 27, 30 in each embodiment of the pressurized fluidized bed combined power plant according to the present invention, the pressure value 31 of the pressurized fluidized bed boiler pressure vessel 6, and the rotational speed of the gas turbine. It is a figure which shows a relationship.
[0045]
As shown in FIGS. 6 and 7, when the air compressor outlet valve 23 and the gas turbine inlet valve 26 are fully closed and the air supply valve 27 and the hot gas discharge valve 30 are opened, the pressurized fluidized bed boiler 6 The pressure of the gas turbine decreases, and the rotational speed of the gas turbine decreases. On the other hand, the air volume is equal to or less than the total value of the air volume from the high-temperature gas discharge valve 30 and the leak volume from the gas turbine inlet valve 26 or the total value of the air volume of the air compressor 1 and the draft amount of the chimney 10. Therefore, the hot gas does not flow backward to the air compressor 1 side. The draft amount can be calculated based on the gas temperature at the inlet of the chimney 10 and the atmospheric temperature.
[0046]
【The invention's effect】
According to the present invention, in a pressurized fluidized bed combined power plant composed of a pressurized fluidized bed boiler, a gas turbine, and a steam turbine, the low temperature exhaust heat recovery heat exchanger, the condensate and the feed water at the outlet of the high temperature exhaust heat recovery heat exchanger This prevents the steaming of the plant, improves the reliability of the plant when the plant is normally stopped and during an emergency stop, and reduces the in-house power when the plant is stopped.
[Brief description of the drawings]
FIG. 1 is a system diagram showing a configuration of a first embodiment of a pressurized fluidized bed combined power plant according to the present invention.
FIG. 2 is a system diagram showing a configuration of a second embodiment of the pressurized fluidized bed combined power plant according to the present invention.
FIG. 3 is a system diagram showing a configuration of Example 3 of a pressurized fluidized bed combined power plant according to the present invention.
FIG. 4 is a system diagram showing a configuration of a fourth embodiment of the pressurized fluidized bed combined power plant according to the present invention.
FIG. 5 is a diagram showing a system configuration of a control logic of a hot gas discharge control device in each embodiment of a pressurized fluidized bed combined power plant according to the present invention.
FIG. 6 is a diagram showing temporal changes in air volume in each example of the pressurized fluidized bed combined power plant according to the present invention.
FIG. 7 is a diagram showing a relationship among a valve open / close state, a pressurized fluidized bed boiler pressure vessel side pressure, and a gas turbine rotation speed in each example of the pressurized fluidized bed combined power plant according to the present invention.
FIG. 8 is a system diagram showing an example of a system configuration of a conventional pressurized fluidized bed combined power plant.
[Explanation of symbols]
1 Air compressor
2 Gas turbine
3 Gas turbine generator
4 Starter motor
5 Pressurized fluidized bed boiler pressure vessel
6 Pressurized fluidized bed boiler
7 High temperature gas dust remover
8 High-temperature exhaust heat recovery heat exchanger
9 Low temperature exhaust heat recovery heat exchanger
10 Chimney
11 High-pressure turbine
12 Medium pressure turbine
13 Low pressure turbine
14 Steam turbine generator
15 Condenser
16 Condensate pump
17 Low pressure water heater
18 Deaerator
19 Water supply pump
20 High-pressure feed water heater
21 Brackish water separator
22 Air inlet valve
23 Air compressor outlet valve
24 Air supply piping
25 Hot gas piping
26 Gas turbine inlet valve
27 Air supply valve
28 Gas turbine outlet piping
29 Hot gas discharge piping
30 Hot gas discharge valve
31 Pressurized fluidized bed boiler pressure vessel pressure detector
32 Pressurized fluidized bed boiler temperature detector
33 High-temperature gas discharge control device
34 Main steam piping
35 Low temperature reheat steam piping
36 High-temperature reheat steam piping
37 Brackish water separator level control valve
38 Gas supply valve
39 Gas supply piping
40 Pressurized fluidized bed boiler bypass valve
41 Pressurized fluidized bed boiler bypass piping

Claims (4)

加圧流動床ボイラと前記加圧流動床ボイラに空気を供給する空気圧縮機と前記加圧流動床ボイラの高温ガスにより駆動されるガスタービンと前記加圧流動床ボイラの蒸気により駆動される蒸気タービンと前記ガスタービンおよび蒸気タービンにより駆動される発電機とを含み、前記空気圧縮機から前記加圧流動床ボイラに圧縮空気を供給する空気供給配管と前記加圧流動床ボイラから前記ガスタービンに高温ガスを供給する高温ガス配管とを接続する空気供給弁を設置したボイラバイパス管路を有する空気加圧流動床複合発電プラントにおいて、
プラント通常停止時または緊急停止時に閉じる空気圧縮機出口弁を前記空気供給配管に設け、
プラント通常停止時または緊急停止時に閉じるガスタービン入口弁を前記高温ガス配管に設け、
プラント通常停止時または緊急停止時に開き前記空気圧縮機の出口から前記ガスタービン入口までの間の空気および高温ガスを前記ガスタービンの入口部に排出する高温ガス排出配管および高温ガス排出弁を前記ガスタービン入口弁と並列に設けたことを特徴とする加圧流動床複合発電プラント。A pressurized fluidized bed boiler, an air compressor for supplying air to the pressurized fluidized bed boiler, a gas turbine driven by the hot gas of the pressurized fluidized bed boiler, and a steam driven by the steam of the pressurized fluidized bed boiler An air supply pipe for supplying compressed air from the air compressor to the pressurized fluidized bed boiler and the pressurized fluidized bed boiler to the gas turbine. In an air pressurized fluidized bed combined power plant having a boiler bypass line installed with an air supply valve for connecting a high temperature gas pipe for supplying a high temperature gas,
An air compressor outlet valve that closes at the time of a normal plant stop or emergency stop is provided in the air supply pipe,
A gas turbine inlet valve that closes at the time of a normal plant stop or emergency stop is provided in the hot gas pipe,
A hot gas discharge pipe and a hot gas discharge valve for opening air and high-temperature gas from the outlet of the air compressor to the gas turbine inlet to the inlet of the gas turbine, which are opened at the time of normal plant stop or emergency stop. A pressurized fluidized bed combined power plant characterized by being provided in parallel with a turbine inlet valve. 請求項１に記載の加圧流動床複合発電プラントにおいて、
排出した高温ガスを冷却し希釈するために窒素または空気を供給するガス供給配管およびガス供給弁を設けたことを特徴とする加圧流動床複合発電プラント。 In the pressurized fluidized bed combined power plant according to claim 1 ,
A pressurized fluidized bed combined power plant comprising a gas supply pipe for supplying nitrogen or air and a gas supply valve for cooling and diluting the discharged high-temperature gas. 請求項１または２に記載の加圧流動床複合発電プラントにおいて、
前記加圧流動床ボイラの圧力および出口温度と、前記空気圧縮機出口弁，前記ガスタービン入口弁，前記空気供給弁の開閉状態とに応じて、前記空気圧縮機出口弁，前記ガスタービン入口弁，前記空気供給弁，前記高温ガス排出弁，前記ガス供給弁の開度を制御する高温ガス排出制御装置を設けたことを特徴とする加圧流動床複合発電プラント。 In the pressurized fluidized bed combined power plant according to claim 1 or 2 ,
Depending on the pressure and outlet temperature of the pressurized fluidized bed boiler and the open / closed state of the air compressor outlet valve, the gas turbine inlet valve, and the air supply valve, the air compressor outlet valve, the gas turbine inlet valve A pressurized fluidized bed combined power plant, comprising: an air supply valve; the high temperature gas discharge valve; and a high temperature gas discharge control device for controlling an opening degree of the gas supply valve. 請求項３に記載の加圧流動床複合発電プラントにおいて、
前記高温ガス排出制御装置が、前記空気圧縮機から前記ガスタービン入口弁までの間の減圧完了後、前記高温ガス排出弁を全閉してからの自然放熱の経過時間を計測するタイマを備えたことを特徴とする加圧流動床複合発電プラント。 In the pressurized fluidized bed combined power plant according to claim 3 ,
The high-temperature gas discharge control device includes a timer that measures an elapsed time of natural heat radiation after the high-temperature gas discharge valve is fully closed after completion of pressure reduction from the air compressor to the gas turbine inlet valve. A pressurized fluidized bed combined power plant characterized by that.
JP01293399A 1999-01-21 1999-01-21 Pressurized fluidized bed combined power plant Expired - Fee Related JP3700075B2 (en)

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