JP7153498B2 - Combined cycle power plant - Google Patents

Combined cycle power plant Download PDF

Info

Publication number
JP7153498B2
JP7153498B2 JP2018149382A JP2018149382A JP7153498B2 JP 7153498 B2 JP7153498 B2 JP 7153498B2 JP 2018149382 A JP2018149382 A JP 2018149382A JP 2018149382 A JP2018149382 A JP 2018149382A JP 7153498 B2 JP7153498 B2 JP 7153498B2
Authority
JP
Japan
Prior art keywords
compressed air
outlet
way valve
heat exchanger
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2018149382A
Other languages
Japanese (ja)
Other versions
JP2020023942A (en
Inventor
肇 青木
辰也 星野
善幸 長谷川
哲也 原田
光 佐野
正憲 笠
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kawasaki Motors Ltd
Original Assignee
Kawasaki Jukogyo KK
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kawasaki Jukogyo KK filed Critical Kawasaki Jukogyo KK
Priority to JP2018149382A priority Critical patent/JP7153498B2/en
Priority to KR1020217005227A priority patent/KR102420538B1/en
Priority to PCT/JP2019/029167 priority patent/WO2020031715A1/en
Priority to CN201980051956.5A priority patent/CN112534120B/en
Priority to TW108128111A priority patent/TWI705183B/en
Publication of JP2020023942A publication Critical patent/JP2020023942A/en
Application granted granted Critical
Publication of JP7153498B2 publication Critical patent/JP7153498B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/003—Arrangements for testing or measuring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16—Control of working fluid flow
    • F02C9/18—Control of working fluid flow by bleeding, bypassing or acting on variable working fluid interconnections between turbines or compressors or their stages
    • 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]
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Description

本発明は、コンバインドサイクル発電プラントに関する。 The present invention relates to combined cycle power plants.

近年、エネルギーをより効率的に利用するために、コンバインドサイクル発電プラントが使用されている。コンバインドサイクル発電プラントは、ガスタービン、蒸気タービン、排熱回収ボイラ等を備えており、ガスタービンと蒸気タービンとを組み合わせた発電方式を採用するものである。このようなコンバインドサイクル発電プラントでは、ガスタービンにて仕事をした後の排ガスを排熱回収ボイラに導き、排ガスの熱を利用して蒸気を発生させ、その蒸気により蒸気タービンを駆動する。 In recent years, combined cycle power plants have been used to utilize energy more efficiently. A combined cycle power plant is equipped with a gas turbine, a steam turbine, an exhaust heat recovery boiler, etc., and employs a power generation system that combines the gas turbine and the steam turbine. In such a combined cycle power plant, the exhaust gas after working in the gas turbine is led to the heat recovery steam generator, and the heat of the exhaust gas is used to generate steam, which drives the steam turbine.

例えば特許文献１の図９に記載されたコンバインドサイクル発電プラントにおける排熱回収ボイラには、高圧の蒸気を生成する高圧熱交換器および低圧の蒸気を生成する低圧熱交換器が上流側からこの順に設けられている。高圧熱交換器により生成された蒸気および低圧熱交換器により生成された蒸気は、蒸気タービンに送られて回転エネルギーの生成に寄与する。 For example, in the heat recovery boiler in the combined cycle power plant described in FIG. 9 of Patent Document 1, a high-pressure heat exchanger that generates high-pressure steam and a low-pressure heat exchanger that generates low-pressure steam are arranged in this order from the upstream side. is provided. Steam produced by the high pressure heat exchanger and steam produced by the low pressure heat exchanger are channeled to the steam turbine to contribute to the production of rotational energy.

特開２０１７－３１８５９号公報JP 2017-31859 A

特許文献１の蒸気タービンは、高圧蒸気により駆動される高圧蒸気タービンと、高圧蒸気タービンにシャフトにより連結され低圧蒸気により駆動される低圧蒸気タービンを含む二段タイプのものである。しかし、蒸気タービンには、高圧蒸気の膨張過程の途中で低圧蒸気が導入される一段タイプのものもある。 The steam turbine of Patent Document 1 is of a two-stage type including a high-pressure steam turbine driven by high-pressure steam and a low-pressure steam turbine connected to the high-pressure steam turbine by a shaft and driven by low-pressure steam. However, some steam turbines are of the single-stage type, in which low-pressure steam is introduced during the expansion process of high-pressure steam.

ところで、排熱回収ボイラの起動時には、ガスタービンからの排ガスによって高圧熱交換器および低圧熱交換器の順で温められる。そのため、低圧熱交換器から蒸気が生成されるのは、高圧熱交換器から蒸気が生成された後となる。ここで、高圧熱交換器により生成される蒸気および低圧熱交換器により生成される蒸気の両方による仕事によって、蒸気タービンの出力が定格出力に達する。従って、迅速に発電を行う観点から、低圧熱交換器により蒸気が生成されるまでの時間を短縮することが望まれる。 By the way, when the heat recovery boiler is started, the high-pressure heat exchanger and the low-pressure heat exchanger are heated in this order by the exhaust gas from the gas turbine. Therefore, steam is produced from the low pressure heat exchanger after steam is produced from the high pressure heat exchanger. Here, work by both the steam produced by the high pressure heat exchanger and the steam produced by the low pressure heat exchanger brings the power of the steam turbine to its rated power. Therefore, from the viewpoint of quick power generation, it is desired to shorten the time until steam is generated by the low-pressure heat exchanger.

そこで、本発明は、排熱回収ボイラの低圧熱交換器により蒸気が生成されるまでの時間を短縮することができるコンバインドサイクル発電プラントを提供することを目的とする。 SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a combined cycle power plant capable of shortening the time until steam is generated by a low-pressure heat exchanger of a heat recovery boiler.

本発明のコンバインドサイクル発電プラントは、空気を圧縮し、圧縮途中の空気である第１圧縮空気の出口である抽気口および圧縮終了の空気である第２圧縮空気の出口である吐出口を有する圧縮機と、排気口を有し、燃料と前記第２圧縮空気との燃焼によって生成された燃焼ガスにより駆動され、前記排気口から排ガスを排出するタービンとを有するガスタービンと、前記排ガスから熱を回収して、第１圧力の蒸気を生成する高圧熱交換器、および前記第１圧力よりも低い第２圧力の蒸気を生成し、前記高圧熱交換器の下流側に配置された低圧熱交換器を有する排熱回収ボイラと、前記排熱回収ボイラにより生成された前記蒸気により駆動される蒸気タービンと、一端が前記圧縮機の前記抽気口に接続され、他端が前記排熱回収ボイラ内の前記高圧熱交換器と前記低圧熱交換器との間の領域に配置された第１抽気配管と、前記第１抽気配管に設けられた第１流量調整弁と、一端が前記圧縮機の前記吐出口に接続され、他端が前記第１抽気配管に接続された第２抽気配管と、前記第２抽気配管に設けられた第２流量調整弁と、前記ガスタービンの起動時に、前記第１流量調整弁又は前記第２流量調整弁を開状態とする制御装置とを備えているものである。 The combined cycle power plant of the present invention compresses air and has a bleed port that is an outlet for first compressed air that is air in the process of being compressed and a discharge port that is an outlet for second compressed air that is air after compression. and a turbine driven by combustion gases produced by combustion of fuel and said second compressed air, having an exhaust port, for discharging exhaust gas from said exhaust port, and extracting heat from said exhaust gas. A high pressure heat exchanger recovering to produce steam at a first pressure and a low pressure heat exchanger producing steam at a second pressure lower than said first pressure and located downstream of said high pressure heat exchanger. a steam turbine driven by the steam generated by the heat recovery steam generator, one end of which is connected to the bleed port of the compressor and the other end of which is in the heat recovery steam generator; a first bleed pipe disposed in a region between the high-pressure heat exchanger and the low-pressure heat exchanger; a first flow control valve provided in the first bleed pipe; a second bleed pipe connected to an outlet and having the other end connected to the first bleed pipe; a second flow control valve provided in the second bleed pipe; and a control device for opening the adjustment valve or the second flow rate adjustment valve.

本発明に従えば、ガスタービンの起動時に、圧縮機により生成された第１圧縮空気が第１抽気配管を介して排熱回収ボイラ内の高圧熱交換器と低圧熱交換器との間の領域に送られ、又は、第２圧縮空気が第２抽気配管を介して前記領域に送られる。これにより、低圧熱交換器は第１圧縮空気又は第２圧縮空気によって温められる。これによって、低圧熱交換器により蒸気が生成されるまでの時間を短縮することができる。 According to the present invention, when the gas turbine is started, the first compressed air generated by the compressor passes through the first bleed pipe to the area between the high-pressure heat exchanger and the low-pressure heat exchanger in the heat recovery steam generator. or a second compressed air is sent to said area via a second bleed line. Thereby, the low-pressure heat exchanger is warmed by the first compressed air or the second compressed air. This can shorten the time until steam is produced by the low pressure heat exchanger.

上記発明において、本発明のコンバインドサイクル発電プラントは、前記第１抽気配管において前記第１流量調整弁の下流側に設けられ、前記第１圧縮空気が流入する流入口、前記第１圧縮空気を流出させる第１流出口、および前記第１圧縮空気を前記排熱回収ボイラ内の前記領域に流出させる第２流出口を有する第１三方弁と、前記第１三方弁の前記第１流出口と前記排熱回収ボイラとを接続する第１ボイラ上流側接続配管と、前記第２抽気配管において前記第２流量調整弁の下流側に設けられ、前記第２圧縮空気が流入する流入口、前記第２圧縮空気を流出させる第１流出口、および前記第２圧縮空気を前記第１抽気配管の方に流出させる第２流出口を有する第２三方弁と、前記第２三方弁の前記第１流出口と前記排熱回収ボイラとを接続する第２ボイラ上流側接続配管と、前記領域の雰囲気温度を検出する第１温度センサと、前記第１抽気配管において前記第１流量調整弁よりも上流側に設けられ、前記第１圧縮空気の温度を検出する第２温度センサと、前記第２抽気配管において前記第２流量調整弁よりも上流側に設けられ、前記第２圧縮空気の温度を検出する第３温度センサと、をさらに備え、前記制御装置は、第１処理又は第２処理を行うように構成され、前記第１処理は、前記第２温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が第１所定値よりも高い場合に、前記第１流量調整弁を開状態とすると共に前記第１三方弁の前記第１流出口を閉状態にしかつ前記第１三方弁の前記第２流出口を開状態にし、前記第２温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が前記第１所定値以下になった際に、前記第１三方弁の前記第２流出口を閉状態にしかつ前記第１三方弁の前記第１流出口を開状態にする、又は前記第１流量調整弁を閉状態とすると共に前記第２流量調整弁を開状態にしかつ前記第２三方弁の前記第１流出口を開状態にして前記第２三方弁の前記第２流出口を閉状態にする処理であり、前記第２処理は、前記第３温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が第２所定値よりも高い場合に、前記第２流量調整弁を開状態とすると共に前記第２三方弁の前記第１流出口を閉状態にしかつ前記第２三方弁の前記第２流出口を開状態にし、前記第３温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が前記第２所定値以下になった際に、前記第２三方弁の前記第２流出口を閉状態にしかつ前記第２三方弁の前記第１流出口を開状態にする、又は前記第２流量調整弁を閉状態とすると共に前記第１流量調整弁を開状態にしかつ前記第１三方弁の前記第１流出口を開状態にして前記第１三方弁の前記第２流出口を閉状態にする処理であってもよい。 In the above invention, the combined cycle power plant of the present invention is provided downstream of the first flow control valve in the first bleed pipe, and includes an inlet into which the first compressed air flows and an inlet through which the first compressed air flows out. a first three-way valve having a first outlet for allowing the first compressed air to flow out to the region in the heat recovery steam generator; and the first outlet of the first three-way valve and the a first boiler upstream connection pipe that connects to an exhaust heat recovery boiler; an inlet that is provided downstream of the second flow control valve in the second extraction pipe and into which the second compressed air flows; a second three-way valve having a first outlet through which compressed air flows out and a second outlet through which the second compressed air flows out toward the first bleed pipe; and the first outlet of the second three-way valve. and the exhaust heat recovery boiler, a second boiler upstream connecting pipe, a first temperature sensor for detecting the ambient temperature of the region, and the first bleed pipe on the upstream side of the first flow control valve a second temperature sensor provided to detect the temperature of the first compressed air; and a second temperature sensor provided upstream of the second flow control valve in the second bleed pipe to detect the temperature of the second compressed air. and 3 temperature sensors, wherein the control device is configured to perform a first process or a second process, wherein the first process is the temperature detected by the second temperature sensor and the temperature detected by the first temperature sensor is higher than a first predetermined value, the first flow control valve is opened, the first outlet of the first three-way valve is closed, and the first When the second outlet of the three-way valve is opened and the difference between the temperature detected by the second temperature sensor and the temperature detected by the first temperature sensor becomes equal to or less than the first predetermined value, closing the second outflow port of the first three-way valve and opening the first outflow port of the first three-way valve, or closing the first flow control valve and the second flow rate; a process of opening a regulating valve, opening the first outlet of the second three-way valve, and closing the second outlet of the second three-way valve; When the difference between the temperature detected by the third temperature sensor and the temperature detected by the first temperature sensor is higher than a second predetermined value, the second flow control valve is opened and the second three-way closing the first outlet of the valve and opening the second outlet of the second three-way valve; 1 When the difference from the temperature detected by the temperature sensor becomes equal to or less than the second predetermined value, the second outlet of the second three-way valve is closed and the first flow of the second three-way valve is opened. The outlet is opened, or the second flow rate adjustment valve is closed, the first flow rate adjustment valve is opened, and the first outflow port of the first three-way valve is opened, and the first flow rate adjustment valve is opened. The processing may include closing the second outflow port of the three-way valve.

上記構成に従えば、低圧熱交換器が第１圧縮空気又は第２圧縮空気により温まった際には、排熱回収ボイラ内に第１圧縮空気又は第２圧縮空気が抽気される。これにより、ガスタービンの起動時にはサージを防止することができ、ガスタービンの運転時には低ＮＯｘ運転を行うことができる。 According to the above configuration, when the low-pressure heat exchanger is warmed by the first compressed air or the second compressed air, the first compressed air or the second compressed air is bled into the heat recovery steam generator. As a result, a surge can be prevented when the gas turbine is started, and a low NOx operation can be performed when the gas turbine is in operation.

本発明によれば、排熱回収ボイラの低圧熱交換器により蒸気が生成されるまでの時間を短縮することができる。 According to the present invention, it is possible to shorten the time until steam is generated by the low-pressure heat exchanger of the heat recovery boiler.

本発明の第１実施形態に係るコンバインドサイクル発電プラントの概略構成図である。1 is a schematic configuration diagram of a combined cycle power plant according to a first embodiment of the present invention; FIG. 第１実施形態の制御装置の処理の流れを示すフローチャートである。4 is a flow chart showing the flow of processing of the control device of the first embodiment; 本発明の第２実施形態に係るコンバインドサイクル発電プラントの概略構成図である。FIG. 5 is a schematic configuration diagram of a combined cycle power plant according to a second embodiment of the present invention;

（第１実施形態）
以下、本発明に係る実施形態のコンバインドサイクル発電プラント（ＣＣＰＰ：Combined Cycle Power Plant）について図面を参照して説明する。以下に説明するコンバインドサイクル発電プラントは、本発明の一実施形態に過ぎない。従って、本発明は実施形態に限定されず、発明の趣旨を逸脱しない範囲で追加、削除、変更が可能である。 (First embodiment)
Hereinafter, a combined cycle power plant (CCPP) of an embodiment according to the present invention will be described with reference to the drawings. The combined cycle power plant described below is but one embodiment of the present invention. Therefore, the present invention is not limited to the embodiments, and additions, deletions, and modifications can be made without departing from the spirit of the invention.

図１に示すように、本発明の第１実施形態に係るコンバインドサイクル発電プラント１は、図示しない発電機に接続されたガスタービン２と、排ガスから熱を回収して蒸気を生成する竪型構造の排熱回収ボイラ３と、ダクト４と、抽気配管５，２６と、ボイラ上流側接続配管８，１７と、三方弁６，１６と、流量調整弁９，１９と、温度センサ１０，１１，１８と、制御装置１２と、蒸気タービン５０とを備えている。制御装置１２は、例えばＲＯＭやＲＡＭなどのメモリおよびＣＰＵを有するコンピュータであり、ＲＯＭに格納されたプログラムがＣＰＵにより実行される。 As shown in FIG. 1, a combined cycle power plant 1 according to the first embodiment of the present invention includes a gas turbine 2 connected to a generator (not shown) and a vertical structure for generating steam by recovering heat from exhaust gas. exhaust heat recovery boiler 3, duct 4, extraction pipes 5, 26, boiler upstream connection pipes 8, 17, three-way valves 6, 16, flow control valves 9, 19, temperature sensors 10, 11, 18 , a controller 12 and a steam turbine 50 . The control device 12 is, for example, a computer having a memory such as ROM or RAM and a CPU, and the CPU executes programs stored in the ROM.

ガスタービン２は、圧縮機２１、図示しない燃焼器、および排気口２３が設けられたタービン２２を備えている。圧縮機２１は、圧縮途中の空気（圧縮機途中段の空気）である第１圧縮空気の出口である抽気口２４、および圧縮終了の空気である第２圧縮空気の出口である吐出口２５を有している。 The gas turbine 2 includes a compressor 21 , a combustor (not shown), and a turbine 22 provided with an exhaust port 23 . The compressor 21 has a bleed port 24, which is the outlet of first compressed air, which is air in the middle of compression (air in the intermediate stage of the compressor), and a discharge port 25, which is the outlet of second compressed air which is air after compression. have.

ガスタービン２においては、圧縮機２１で生成された第２圧縮空気と燃料とを上記燃焼器で混合燃焼させ、発生した燃焼ガスをタービン２２へ供給してタービン２２の羽根を回転させることにより、燃焼ガスの熱エネルギーを回転運動エネルギーに変換する。タービン２２からの排ガス（燃焼ガス）は排気口２３から排出される。なお、ガスタービン２の燃料として、ＬＮＧ（天然ガス）、水素ガス、副生ガス、および液体燃料等が挙げられる。 In the gas turbine 2, the second compressed air generated by the compressor 21 and the fuel are mixed and burned in the combustor, and the generated combustion gas is supplied to the turbine 22 to rotate the blades of the turbine 22. It converts the thermal energy of the combustion gas into rotational kinetic energy. Exhaust gas (combustion gas) from the turbine 22 is discharged from an exhaust port 23 . Fuels for the gas turbine 2 include LNG (natural gas), hydrogen gas, by-product gas, liquid fuel, and the like.

ダクト４の一端は排気口２３に接続されており、ダクト４の他端は排熱回収ボイラ３の下部に接続されている。排気口２３から排出された排ガスはダクト４を通じて排熱回収ボイラ３内に流入される。 One end of the duct 4 is connected to the exhaust port 23 and the other end of the duct 4 is connected to the lower portion of the heat recovery steam generator 3 . Exhaust gas discharged from the exhaust port 23 flows into the heat recovery boiler 3 through the duct 4 .

また、コンバインドサイクル発電プラント１は、ダクト４に接続されガスタービン２からの排ガスを大気中に放出する煙管１３と、ダクト４に設けられた排気バイパスダンパ４１とをさらに備えている。 The combined cycle power plant 1 further includes a smoke pipe 13 connected to the duct 4 for releasing exhaust gas from the gas turbine 2 into the atmosphere, and an exhaust bypass damper 41 provided in the duct 4 .

排気バイパスダンパ４１は、制御装置１２の制御によって、排ガスを煙管１３に流入させると共に排熱回収ボイラ３への排ガスの流入を遮断する第１位置Ｐ１又は排熱回収ボイラ３へ排ガスを流入させると共に煙管１３への排ガスの流入を遮断する第２位置Ｐ２に位置される。排気バイパスダンパ４１が第１位置Ｐ１に位置される場合とは、排ガスが排熱回収ボイラ３内に流入しないため、排熱回収ボイラ３による蒸気の生成が行われない場合である。即ち、蒸気タービン５０に接続された図示しない発電機による発電が行われない場合である。これに対して、排気バイパスダンパ４１が第２位置Ｐ２に位置される場合とは、排ガスが排熱回収ボイラ３内に流入するため、ガスタービン２に接続された図示しない発電機による発電と蒸気タービン５０に接続された上記発電機による発電とが複合されて行われる場合である。なお、図１では、排気バイパスダンパ４１が第１位置Ｐ１に位置された状態が実線により図示され、排気バイパスダンパ４１が第２位置Ｐ２に位置された状態が二点鎖線により図示されている。 Under the control of the control device 12, the exhaust gas bypass damper 41 causes the exhaust gas to flow into the smoke pipe 13 and to the first position P1 that blocks the flow of the exhaust gas into the heat recovery boiler 3 or into the heat recovery boiler 3. It is positioned at a second position P2 that blocks the inflow of exhaust gas into the smoke pipe 13 . When the exhaust bypass damper 41 is positioned at the first position P1, the exhaust heat recovery boiler 3 does not generate steam because the exhaust gas does not flow into the heat recovery boiler 3 . In other words, this is the case where a power generator (not shown) connected to the steam turbine 50 does not generate power. On the other hand, when the exhaust bypass damper 41 is positioned at the second position P2, the exhaust gas flows into the heat recovery boiler 3, so that the generator (not shown) connected to the gas turbine 2 generates electricity and steam. This is the case where power generation by the generator connected to the turbine 50 is combined. In FIG. 1, the solid line indicates the state where the exhaust bypass damper 41 is positioned at the first position P1, and the two-dot chain line indicates the state where the exhaust bypass damper 41 is positioned at the second position P2.

排熱回収ボイラ３は、高圧熱交換器３１および低圧熱交換器３２を有している。高圧熱交換器３１は、排ガスと、水および蒸気の一方又は両方との間で熱交換を行うことにより第１圧力（高圧）の蒸気を生成する。また、低圧熱交換器３２は、高圧熱交換器３１の下流側に配置されており、排ガスと、水および蒸気の一方又は両方との間で熱交換を行うことにより第１圧力よりも低い第２圧力（低圧）の蒸気を生成する。 The heat recovery boiler 3 has a high pressure heat exchanger 31 and a low pressure heat exchanger 32 . The high pressure heat exchanger 31 generates steam at a first pressure (high pressure) by exchanging heat between the exhaust gas and one or both of water and steam. In addition, the low-pressure heat exchanger 32 is arranged downstream of the high-pressure heat exchanger 31, and performs heat exchange between the exhaust gas and one or both of water and steam to provide a first pressure lower than the first pressure. 2 pressure (low pressure) steam is produced.

高圧熱交換器３１と蒸気タービン５０とは配管５１により接続されている。また、低圧熱交換器３２と蒸気タービン５０とは、蒸気タービン５０において下流端が配管５１の下流端よりも下流側に配置された配管５２により接続されている。高圧熱交換器３１により生成された蒸気は配管５１により蒸気タービン５０に送られ、低圧熱交換器３２により生成された蒸気は配管５２により蒸気タービン５０に送られる。 The high pressure heat exchanger 31 and the steam turbine 50 are connected by a pipe 51 . The low-pressure heat exchanger 32 and the steam turbine 50 are connected by a pipe 52 whose downstream end is located downstream of the downstream end of the pipe 51 in the steam turbine 50 . Steam generated by the high-pressure heat exchanger 31 is sent to the steam turbine 50 through a pipe 51 , and steam generated by the low-pressure heat exchanger 32 is sent to the steam turbine 50 through a pipe 52 .

抽気配管５の一端は圧縮機２１の抽気口２４に接続され、その他端は排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に配置されている。本実施形態では、抽気配管５のうち、他端を含め排熱回収ボイラ３内に配置された部分（以下、予熱部分と記載）は低圧熱交換器３２の図示しない管群のガス上流側全面を後述の圧縮空気によって覆えるように配置されている。上記の予熱部分には、低圧熱交換器３２に向けて開口された複数の図示しない孔部が設けられており、この孔部から流出した第１圧縮空気又は後述の第２圧縮空気が低圧熱交換器３２に向けて供給されるようになっている。これによって、低圧熱交換器３２は第１圧縮空気又は第２圧縮空気により温められる。 One end of the bleed pipe 5 is connected to the bleed port 24 of the compressor 21 , and the other end is arranged in the region between the high-pressure heat exchanger 31 and the low-pressure heat exchanger 32 in the heat recovery boiler 3 . In the present embodiment, the portion of the extraction pipe 5, including the other end, disposed inside the heat recovery steam generator 3 (hereinafter referred to as the preheating portion) is the entire surface of the gas upstream side of the tube group (not shown) of the low-pressure heat exchanger 32. are covered with compressed air, which will be described later. The preheating portion is provided with a plurality of holes (not shown) that open toward the low-pressure heat exchanger 32, and the first compressed air flowing out from the holes or the second compressed air (to be described later) flows into the low-pressure heat. It is supplied toward the exchanger 32 . Thereby, the low-pressure heat exchanger 32 is warmed by the first compressed air or the second compressed air.

流量調整弁１９は、抽気配管５に設けられており、抽気配管５内を流れる第１圧縮空気の量を制御する。流量調整弁１９の動作は制御装置１２により制御される。 The flow control valve 19 is provided in the extraction pipe 5 and controls the amount of the first compressed air flowing through the extraction pipe 5 . The operation of the flow control valve 19 is controlled by the controller 12 .

三方弁１６は、抽気配管５において流量調整弁１９よりも下流側の位置に設けられている。この三方弁１６は、第１圧縮空気が流入する流入口１６ａ、第１圧縮空気を流出させる第１流出口１６ｂ、および第１圧縮空気を排熱回収ボイラ３内の上記領域に流出させる第２流出口１６ｃを有している。三方弁１６の動作は制御装置１２により制御される。ボイラ上流側接続配管１７は、三方弁１６の第１流出口１６ｂとダクト４の排気バイパスダンパ４１よりも上流側の部分とを接続している。 The three-way valve 16 is provided downstream of the flow control valve 19 in the extraction pipe 5 . The three-way valve 16 has an inlet 16a through which the first compressed air flows, a first outlet 16b through which the first compressed air flows out, and a second outlet 16b through which the first compressed air flows out to the above regions in the heat recovery steam generator 3. It has an outflow port 16c. The operation of the three-way valve 16 is controlled by the controller 12 . The boiler upstream connection pipe 17 connects the first outflow port 16 b of the three-way valve 16 and a portion of the duct 4 upstream of the exhaust bypass damper 41 .

抽気配管２６の一端は圧縮機２１の吐出口２５に接続され、その他端は抽気配管５のうち三方弁１６よりも下流側の部分に接続されている。この構成により、圧縮機２１からの第２圧縮空気が抽気配管２６，５を介して排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に供給されるようになっている。 One end of the bleed pipe 26 is connected to the discharge port 25 of the compressor 21 , and the other end is connected to a portion of the bleed pipe 5 downstream of the three-way valve 16 . With this configuration, the second compressed air from the compressor 21 is supplied to the area between the high-pressure heat exchanger 31 and the low-pressure heat exchanger 32 in the heat recovery boiler 3 via the extraction pipes 26 and 5. It has become.

流量調整弁９は、抽気配管２６に設けられており、抽気配管２６内を流れる第２圧縮空気の量を制御する。流量調整弁９の動作は制御装置１２により制御される。 The flow control valve 9 is provided in the extraction pipe 26 and controls the amount of the second compressed air flowing through the extraction pipe 26 . The operation of the flow control valve 9 is controlled by the controller 12 .

三方弁６は、抽気配管２６において流量調整弁９よりも下流側の位置に設けられている。この三方弁６は、第２圧縮空気が流入する流入口６ａ、第２圧縮空気を流出させる第１流出口６ｂ、および第２圧縮空気を排熱回収ボイラ３内の上記領域に流出させる第２流出口６ｃを有している。三方弁６の動作は制御装置１２により制御される。ボイラ上流側接続配管８は、三方弁６の第１流出口６ｂとダクト４の排気バイパスダンパ４１よりも上流側の部分とを接続する。 The three-way valve 6 is provided downstream of the flow control valve 9 in the extraction pipe 26 . The three-way valve 6 has an inlet 6a through which the second compressed air flows, a first outlet 6b through which the second compressed air flows out, and a second outlet 6b through which the second compressed air flows out to the above regions in the heat recovery steam generator 3. It has an outflow port 6c. The operation of the three-way valve 6 is controlled by the controller 12 . The boiler upstream connection pipe 8 connects the first outflow port 6 b of the three-way valve 6 and the portion of the duct 4 upstream of the exhaust bypass damper 41 .

温度センサ１０は、排熱回収ボイラ３内の上記領域の排ガス温度を検出し、その検出結果の信号を制御装置１２に出力する。温度センサ１８は、抽気配管５において流量調整弁１９の上流側に配置され、抽気配管５内を流れる第１圧縮空気の温度を検出し、その検出結果の信号を制御装置１２に出力する。温度センサ１１は、抽気配管２６において流量調整弁９の上流側に配置され、抽気配管２６内を流れる第２圧縮空気の温度を検出し、その検出結果の信号を制御装置１２に出力する。 The temperature sensor 10 detects the exhaust gas temperature in the above-mentioned region inside the heat recovery boiler 3 and outputs a signal of the detection result to the control device 12 . The temperature sensor 18 is arranged upstream of the flow control valve 19 in the bleed pipe 5 , detects the temperature of the first compressed air flowing through the bleed pipe 5 , and outputs a signal of the detection result to the control device 12 . The temperature sensor 11 is arranged upstream of the flow control valve 9 in the extraction pipe 26 , detects the temperature of the second compressed air flowing through the extraction pipe 26 , and outputs a signal of the detection result to the control device 12 .

このような構成において、ガスタービン２の起動時、即ち温度センサ１８により検出された温度と温度センサ１０により検出された温度との差が所定値（第１所定値）よりも高い場合に、制御装置１２は、抽気配管５を開放するように流量調整弁１９を開状態とすると共に三方弁１６の第１流出口１６ｂを閉状態にしかつ第２流出口１６ｃを開状態にする（第１予熱処理）。これにより、圧縮機２１からの第１圧縮空気が抽気配管５を通じて排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に送られる。これによって、低圧熱交換器３２は第１圧縮空気により温められる。なお、第１予熱処理および後述の第２予熱処理は、排気バイパスダンパ４１が第２位置Ｐ２に位置する場合に行われる。 In such a configuration, when the gas turbine 2 is started, that is, when the difference between the temperature detected by the temperature sensor 18 and the temperature detected by the temperature sensor 10 is higher than a predetermined value (first predetermined value), the control The device 12 opens the flow control valve 19 so as to open the extraction pipe 5, closes the first outflow port 16b of the three-way valve 16, and opens the second outflow port 16c (first preliminary Heat treatment). Thereby, the first compressed air from the compressor 21 is sent to the area between the high pressure heat exchanger 31 and the low pressure heat exchanger 32 in the heat recovery boiler 3 through the extraction pipe 5 . Thereby, the low-pressure heat exchanger 32 is warmed by the first compressed air. Note that the first preheating process and the second preheating process described later are performed when the exhaust bypass damper 41 is positioned at the second position P2.

その後、制御装置１２は、温度センサ１８により検出された温度と温度センサ１０により検出された温度との差が所定値以下になった際には、流量調整弁１９の開状態を維持すると共に三方弁１６の第２流出口１６ｃを閉状態にしかつ第１流出口１６ｂを開状態にする。これにより、圧縮機２１からの第１圧縮空気は、ボイラ上流側接続配管１７を通じて排熱回収ボイラ３内に流入する。このことによって、ガスタービン２の起動時のサージを防止することができる。 After that, when the difference between the temperature detected by the temperature sensor 18 and the temperature detected by the temperature sensor 10 becomes equal to or less than a predetermined value, the control device 12 keeps the flow control valve 19 open and The second outlet 16c of the valve 16 is closed and the first outlet 16b is opened. Thereby, the first compressed air from the compressor 21 flows into the exhaust heat recovery boiler 3 through the boiler upstream connection pipe 17 . This makes it possible to prevent surges when the gas turbine 2 is started.

ここで、制御装置１２は、上記の第１予熱処理の代わりに、以下の第２予熱処理を行ってもよい。制御装置１２は、温度センサ１１により検出された温度と温度センサ１０により検出された温度との差が所定値（第２所定値）よりも高い場合に、制御装置１２は、抽気配管２６を開放するように流量調整弁９を開状態とすると共に三方弁６の第１流出口６ｂを閉状態にしかつ第２流出口６ｃを開状態にする。これにより、圧縮機２１からの第２圧縮空気が抽気配管２６，５を通じて排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に送られる。これによって、低圧熱交換器３２は第２圧縮空気により温められる。その後、制御装置１２は、温度センサ１１により検出された温度と温度センサ１０により検出された温度との差が所定値以下になった際には、流量調整弁９の開状態を維持すると共に三方弁６の第２流出口６ｃを閉状態にしかつ第１流出口６ｂを開状態にする。これにより、圧縮機２１からの第２圧縮空気は、ボイラ上流側接続配管８を通じて排熱回収ボイラ３内に流入する。このことによって、ガスタービン２の低ＮＯｘ運転を行うことができる。 Here, the control device 12 may perform the following second preheating instead of the above first preheating. The control device 12 opens the extraction pipe 26 when the difference between the temperature detected by the temperature sensor 11 and the temperature detected by the temperature sensor 10 is higher than a predetermined value (second predetermined value). The flow regulating valve 9 is opened, the first outlet 6b of the three-way valve 6 is closed, and the second outlet 6c is opened. Thereby, the second compressed air from the compressor 21 is sent to the area between the high pressure heat exchanger 31 and the low pressure heat exchanger 32 in the heat recovery boiler 3 through the extraction pipes 26 and 5 . Thereby, the low-pressure heat exchanger 32 is warmed by the second compressed air. After that, when the difference between the temperature detected by the temperature sensor 11 and the temperature detected by the temperature sensor 10 becomes equal to or less than a predetermined value, the control device 12 keeps the flow control valve 9 open and the three-way The second outlet 6c of the valve 6 is closed and the first outlet 6b is opened. As a result, the second compressed air from the compressor 21 flows into the heat recovery boiler 3 through the boiler upstream connection pipe 8 . As a result, low NOx operation of the gas turbine 2 can be performed.

続いて、制御装置１２による制御方法について説明する。図２は制御装置１２による上述の第１予熱処理の流れを示すフローチャートである。 Next, a control method by the control device 12 will be described. FIG. 2 is a flow chart showing the flow of the above-described first preheating by the control device 12. As shown in FIG.

制御装置１２は、抽気配管５を開放するように流量調整弁１９を開状態とすると共に三方弁１６の第１流出口１６ｂを閉状態にしかつ第２流出口１６ｃを開状態にする（ステップＳ１）。これにより、圧縮機２１からの第１圧縮空気が抽気配管５を通じて排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に流入する。これによって、低圧熱交換器３２は第１圧縮空気により温められる。 The control device 12 opens the flow control valve 19 so as to open the bleed pipe 5, closes the first outflow port 16b of the three-way valve 16, and opens the second outflow port 16c (step S1). ). As a result, the first compressed air from the compressor 21 flows into the area between the high-pressure heat exchanger 31 and the low-pressure heat exchanger 32 in the heat recovery boiler 3 through the extraction pipe 5 . Thereby, the low-pressure heat exchanger 32 is warmed by the first compressed air.

続いて、制御装置１２は、温度センサ１８により検出された温度（図２ではＴ２と記載）と温度センサ１０により検出された温度（図２ではＴ１と記載）との差が所定値よりも高いか否かを判別する（ステップＳ２）。上記差が所定値よりも高い場合には（ステップＳ２でＹＥＳ）、ステップＳ３に進み、上記差が所定値以下である場合には（ステップＳ２でＮＯ）、ステップＳ２の処理を繰り返す。 Subsequently, the controller 12 determines that the difference between the temperature detected by the temperature sensor 18 (described as T2 in FIG. 2) and the temperature detected by the temperature sensor 10 (described as T1 in FIG. 2) is higher than a predetermined value. It is determined whether or not (step S2). If the difference is higher than the predetermined value (YES in step S2), the process proceeds to step S3, and if the difference is equal to or less than the predetermined value (NO in step S2), the process of step S2 is repeated.

ステップＳ３では、制御装置１２は、流量調整弁１９の開状態を維持すると共に三方弁１６の第２流出口１６ｃを閉状態にしかつ第１流出口１６ｂを開状態にする。これにより、圧縮機２１からの第１圧縮空気はボイラ上流側接続配管１７を通じて排熱回収ボイラ３内に流入する。 In step S3, the controller 12 maintains the open state of the flow control valve 19, closes the second outflow port 16c of the three-way valve 16, and opens the first outflow port 16b. Thereby, the first compressed air from the compressor 21 flows into the exhaust heat recovery boiler 3 through the boiler upstream connection pipe 17 .

以上説明したように、本実施形態のコンバインドサイクル発電プラント１においては、圧縮機２１からの第１圧縮空気又は第２圧縮空気が排熱回収ボイラ３内の高圧熱交換器３１と低圧熱交換器３２との間の領域に送られる。これにより、低圧熱交換器３２は第１圧縮空気又は第２圧縮空気によって温められる。これによって、低圧熱交換器３２により蒸気が生成されるまでの時間を短縮することができる。 As described above, in the combined cycle power plant 1 of the present embodiment, the first compressed air or the second compressed air from the compressor 21 passes through the high-pressure heat exchanger 31 and the low-pressure heat exchanger in the heat recovery steam generator 3. 32 to the area between Thereby, the low-pressure heat exchanger 32 is warmed by the first compressed air or the second compressed air. Thereby, the time until steam is generated by the low-pressure heat exchanger 32 can be shortened.

また、制御装置１２による上述の第１予熱処理が終了した後、第１圧縮空気がボイラ上流側接続配管１７を介して排熱回収ボイラ３内に送られる。或いは、制御装置１２による上述の第２予熱処理が終了した後、第２圧縮空気がボイラ上流側接続配管１８を介して排熱回収ボイラ３内に送られる。このような構成によって、ガスタービン２の起動時にはサージを防止することができ、ガスタービン２の運転時には低ＮＯｘ運転を行うことができる。 Further, after the above-described first preheat treatment by the control device 12 is completed, the first compressed air is sent into the exhaust heat recovery boiler 3 through the boiler upstream connection pipe 17 . Alternatively, after the above-described second preheat treatment by the control device 12 is completed, the second compressed air is sent into the heat recovery boiler 3 through the boiler upstream connection pipe 18 . With such a configuration, it is possible to prevent a surge when the gas turbine 2 is started, and to perform a low NOx operation when the gas turbine 2 is in operation.

（第２実施形態）
次に、本発明の第２実施形態に係るコンバインドサイクル発電プラント１ａについて図面を参照しつつ説明する。なお、本実施形態においては、上述の第１実施形態と同一の構成部材には同一の符号を付与し、その説明を省略する。 (Second embodiment)
Next, a combined cycle power plant 1a according to a second embodiment of the present invention will be described with reference to the drawings. In addition, in this embodiment, the same code|symbol is provided to the same component member as above-mentioned 1st Embodiment, and the description is abbreviate|omitted.

図３に示すように、第２実施形態に係るコンバインドサイクル発電プラント１ａは、排熱回収ボイラ３内において、高圧熱交換器３１と低圧熱交換器３２との間に中圧熱交換器３３を備えている。中圧熱交換器３３は、上述した第１圧力と第２圧力との間の圧力の蒸気を生成する。中圧熱交換器３３と蒸気タービン５０とは、蒸気タービン５０において下流端が配管５１の下流端よりも下流側であってかつ配管５２の下流端よりも上流側に配置された配管５３により接続されている。中圧熱交換器３３により生成された蒸気は配管５３により蒸気タービン５０に送られる。 As shown in FIG. 3, the combined cycle power plant 1a according to the second embodiment includes a medium pressure heat exchanger 33 between a high pressure heat exchanger 31 and a low pressure heat exchanger 32 in the heat recovery boiler 3. I have. The intermediate pressure heat exchanger 33 produces steam at a pressure between the first pressure and the second pressure described above. The intermediate pressure heat exchanger 33 and the steam turbine 50 are connected by a pipe 53 whose downstream end is located downstream of the downstream end of the pipe 51 and upstream of the downstream end of the pipe 52 in the steam turbine 50 . It is Steam generated by the intermediate pressure heat exchanger 33 is sent to the steam turbine 50 through a pipe 53 .

抽気配管５の一端は、第１実施形態と同様に圧縮機２１の抽気口２４に接続され、その他端は排熱回収ボイラ３内の中圧熱交換器３３と低圧熱交換器３２との間の領域に配置されている。抽気配管５のうち、他端を含め排熱回収ボイラ３内に配置された部分（予熱部分）は低圧熱交換器３２の図示しない管群のガス上流側全面を圧縮空気によって覆えるように配置されている。上記の予熱部分には、低圧熱交換器３２に向けて開口された複数の図示しない孔部が設けられており、この孔部から流出した第１圧縮空気又は第２圧縮空気が低圧熱交換器３２に向けて供給される。これによって、低圧熱交換器３２は温められる。 One end of the extraction pipe 5 is connected to the extraction port 24 of the compressor 21 as in the first embodiment, and the other end is connected between the intermediate pressure heat exchanger 33 and the low pressure heat exchanger 32 in the heat recovery steam generator 3. are located in the area of The portion (preheating portion) of the extraction pipe 5, including the other end, arranged in the heat recovery boiler 3 is arranged so that the entire surface of the gas upstream side of the tube group (not shown) of the low-pressure heat exchanger 32 is covered with compressed air. It is The preheating portion is provided with a plurality of holes (not shown) that open toward the low-pressure heat exchanger 32, and the first compressed air or the second compressed air that flows out from the holes flows into the low-pressure heat exchanger. 32. This warms the low-pressure heat exchanger 32 .

第２実施形態のコンバインドサイクル発電プラント１ａにおいても、第１実施形態のコンバインドサイクル発電プラント１と同様に、ガスタービン２の起動時に、圧縮機２１からの第１圧縮空気又は第２圧縮空気が排熱回収ボイラ３内の中圧熱交換器３３と低圧熱交換器３２との間の領域に送られる。これにより、低圧熱交換器３２は温められる。これによって、低圧熱交換器３２により蒸気が生成されるまでの時間を短縮することができる。また、ガスタービン２の起動時にはサージを防止することができ、ガスタービン２の運転時には低ＮＯｘ運転を行うことができるという効果も第１実施形態と同様に奏される。 Also in the combined cycle power plant 1a of the second embodiment, as in the combined cycle power plant 1 of the first embodiment, the first compressed air or the second compressed air from the compressor 21 is discharged when the gas turbine 2 is started. It is sent to the area between the intermediate pressure heat exchanger 33 and the low pressure heat exchanger 32 in the heat recovery boiler 3 . This warms the low-pressure heat exchanger 32 . Thereby, the time until steam is generated by the low-pressure heat exchanger 32 can be shortened. In addition, similar to the first embodiment, it is possible to prevent a surge when the gas turbine 2 is started, and to perform a low NOx operation when the gas turbine 2 is in operation.

（他の実施形態）
本発明は上述した実施形態に限定されるものではなく、本発明の要旨を逸脱しない範囲で種々の変形が可能である。例えば以下の通りである。 (Other embodiments)
The present invention is not limited to the embodiments described above, and various modifications are possible without departing from the gist of the present invention. For example:

上記第１および第２実施形態では、竪型構造の排熱回収ボイラ３を採用したが、これに限らず、横型構造の排熱回収ボイラを採用してもよい。 In the above-described first and second embodiments, the exhaust heat recovery boiler 3 having a vertical structure is adopted.

また、上記第１および第２実施形態では、煙管１３が設けられたコンバインドサイクル発電プラント１、１ａについて説明したが、煙管１３が設けられていないコンバインドサイクル発電プラントについても本発明を同様に適用することができる。 Further, in the first and second embodiments, the combined cycle power plants 1 and 1a provided with the smoke pipe 13 have been described, but the present invention is similarly applied to a combined cycle power plant without the smoke pipe 13. be able to.

また、上記第１および第２実施形態では、高圧蒸気の膨張過程の途中で低圧蒸気が導入される一段タイプの蒸気タービン５０について例を挙げて説明したが、蒸気タービン５０の構成はこれに限定されるものではなく、高圧蒸気により駆動される高圧蒸気タービンと、高圧蒸気タービンにシャフトにより連結され低圧蒸気により駆動される低圧蒸気タービンを含む二段タイプのものを採用してもよい。 In addition, in the above-described first and second embodiments, the single-stage steam turbine 50 in which low-pressure steam is introduced during the expansion process of high-pressure steam has been described as an example, but the configuration of the steam turbine 50 is limited to this. Instead, a two-stage type including a high-pressure steam turbine driven by high-pressure steam and a low-pressure steam turbine connected to the high-pressure steam turbine by a shaft and driven by low-pressure steam may be adopted.

また、上記第１および第２実施形態では、三方弁６，１６を採用したが、これに限定されるものではなく、三方弁６の代わりに、ボイラ上流側接続配管８に開閉弁を設けかつ抽気配管２６の下流端の上流側に開閉弁を設けてもよい。また、三方弁１６の代わりに、ボイラ上流側接続配管１７に開閉弁を設けかつ抽気配管５の下流側部分に開閉弁を設けてもよい。 In addition, although the three-way valves 6 and 16 are employed in the first and second embodiments, the present invention is not limited to this. An on-off valve may be provided upstream of the downstream end of the extraction pipe 26 . Further, instead of the three-way valve 16, an on-off valve may be provided in the boiler upstream connection pipe 17 and an on-off valve may be provided in the downstream portion of the extraction pipe 5.

また、上記第１および第２実施形態では、第１圧縮空気により低圧熱交換器３２を温めた後、その第１圧縮空気を排熱回収ボイラ３内に抽気するようにしたが、第２圧縮空気を排熱回収ボイラ３内に抽気してもよい。また、第２圧縮空気により低圧熱交換器３２を温めた後、その第２圧縮空気を排熱回収ボイラ３内に抽気するようにしたが、第１圧縮空気を排熱回収ボイラ３内に抽気してもよい。 Further, in the first and second embodiments, after the low-pressure heat exchanger 32 is warmed by the first compressed air, the first compressed air is bled into the heat recovery steam generator 3. Air may be bled into the heat recovery steam generator 3 . Also, after warming the low-pressure heat exchanger 32 with the second compressed air, the second compressed air is bled into the heat recovery boiler 3, but the first compressed air is bled into the heat recovery boiler 3. You may

さらに、上記第１および第２実施形態では、三方弁６，１６および流量調整弁９，１９を制御装置１２により制御するように構成したが、これらを別個独立して制御する各制御装置を設けてもよい。 Furthermore, in the above-described first and second embodiments, the three-way valves 6, 16 and the flow control valves 9, 19 are configured to be controlled by the control device 12. may

１ コンバインドサイクル発電プラント
２ ガスタービン
３ 排熱回収ボイラ
４ ダクト
５ 抽気配管（第１抽気配管）
６ 三方弁（第２三方弁）
６ａ，１６ａ 流入口
６ｂ，１６ｂ 第１流出口
６ｃ，１６ｃ 第２流出口
８ ボイラ上流側接続配管（第２ボイラ上流側接続配管）
９ 流量調整弁（第２流量調整弁）
１０ 温度センサ（第１温度センサ）
１１ 温度センサ（第３温度センサ）
１２ 制御装置
１６ 三方弁（第１三方弁）
１７ ボイラ上流側接続配管（第１ボイラ上流側接続配管）
１８ 温度センサ（第２温度センサ）
１９ 流量調整弁（第１流量調整弁）
２１ 圧縮機
２２ タービン
２３ 排気口
２４ 抽気口
２５ 吐出口
３１ 高圧熱交換器
３２ 低圧熱交換器
５０ 蒸気タービン 1 combined cycle power plant 2 gas turbine 3 heat recovery boiler 4 duct 5 extraction pipe (first extraction pipe)
6 three-way valve (second three-way valve)
6a, 16a inlet 6b, 16b first outlet 6c, 16c second outlet 8 boiler upstream connection pipe (second boiler upstream connection pipe)
9 flow control valve (second flow control valve)
10 temperature sensor (first temperature sensor)
11 temperature sensor (third temperature sensor)
12 control device 16 three-way valve (first three-way valve)
17 Boiler upstream connection pipe (1st boiler upstream connection pipe)
18 temperature sensor (second temperature sensor)
19 flow control valve (first flow control valve)
21 compressor 22 turbine 23 exhaust port 24 extraction port 25 discharge port 31 high pressure heat exchanger 32 low pressure heat exchanger 50 steam turbine

Claims (2)

空気を圧縮し、圧縮途中の空気である第１圧縮空気の出口である抽気口および圧縮終了の空気である第２圧縮空気の出口である吐出口を有する圧縮機と、排気口を有し、燃料と前記第２圧縮空気との燃焼によって生成された燃焼ガスにより駆動され、前記排気口から排ガスを排出するタービンとを有するガスタービンと、
前記排ガスから熱を回収して、第１圧力の蒸気を生成する高圧熱交換器、および前記第１圧力よりも低い第２圧力の蒸気を生成し、前記高圧熱交換器の下流側に配置された低圧熱交換器を有する排熱回収ボイラと、
前記排熱回収ボイラにより生成された前記蒸気により駆動される蒸気タービンと、
一端が前記圧縮機の前記抽気口に接続され、他端が前記排熱回収ボイラ内の前記高圧熱交換器と前記低圧熱交換器との間の領域に配置された第１抽気配管と、
前記第１抽気配管に設けられた第１流量調整弁と、
一端が前記圧縮機の前記吐出口に接続され、他端が前記第１抽気配管に接続された第２抽気配管と、
前記第２抽気配管に設けられた第２流量調整弁と、
前記ガスタービンの起動時に、前記第１流量調整弁又は前記第２流量調整弁を開状態とする制御装置とを備えている、コンバインドサイクル発電プラント。 A compressor that compresses air and has a bleed port that is an outlet for first compressed air that is air in the process of being compressed and a discharge port that is an outlet for second compressed air that is air that has been compressed; a gas turbine driven by combustion gases produced by combustion of the fuel and the second compressed air and exhausting exhaust gases from the exhaust port;
a high pressure heat exchanger for recovering heat from the exhaust gas to produce steam at a first pressure; and a high pressure heat exchanger for producing steam at a second pressure lower than the first pressure and positioned downstream of the high pressure heat exchanger. a heat recovery steam generator having a low pressure heat exchanger;
a steam turbine driven by the steam generated by the heat recovery steam generator;
a first bleed pipe having one end connected to the bleed port of the compressor and the other end arranged in a region between the high pressure heat exchanger and the low pressure heat exchanger in the heat recovery boiler;
a first flow control valve provided in the first extraction pipe;
a second bleed pipe having one end connected to the discharge port of the compressor and the other end connected to the first bleed pipe;
a second flow control valve provided in the second extraction pipe;
and a control device that opens the first flow control valve or the second flow control valve when the gas turbine is started. 前記第１抽気配管において前記第１流量調整弁の下流側に設けられ、前記第１圧縮空気が流入する流入口、前記第１圧縮空気を流出させる第１流出口、および前記第１圧縮空気を前記排熱回収ボイラ内の前記領域に流出させる第２流出口を有する第１三方弁と、
前記第１三方弁の前記第１流出口と前記排熱回収ボイラとを接続する第１ボイラ上流側接続配管と、
前記第２抽気配管において前記第２流量調整弁の下流側に設けられ、前記第２圧縮空気が流入する流入口、前記第２圧縮空気を流出させる第１流出口、および前記第２圧縮空気を前記第１抽気配管の方に流出させる第２流出口を有する第２三方弁と、
前記第２三方弁の前記第１流出口と前記排熱回収ボイラとを接続する第２ボイラ上流側接続配管と、
前記領域の雰囲気温度を検出する第１温度センサと、
前記第１抽気配管において前記第１流量調整弁よりも上流側に設けられ、前記第１圧縮空気の温度を検出する第２温度センサと、
前記第２抽気配管において前記第２流量調整弁よりも上流側に設けられ、前記第２圧縮空気の温度を検出する第３温度センサと、をさらに備え、
前記制御装置は、第１処理又は第２処理を行うように構成され、
前記第１処理は、前記第２温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が第１所定値よりも高い場合に、前記第１流量調整弁を開状態とすると共に前記第１三方弁の前記第１流出口を閉状態にしかつ前記第１三方弁の前記第２流出口を開状態にし、前記第２温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が前記第１所定値以下になった際に、前記第１三方弁の前記第２流出口を閉状態にしかつ前記第１三方弁の前記第１流出口を開状態にする、又は前記第１流量調整弁を閉状態とすると共に前記第２流量調整弁を開状態にしかつ前記第２三方弁の前記第１流出口を開状態にして前記第２三方弁の前記第２流出口を閉状態にする処理であり、
前記第２処理は、前記第３温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が第２所定値よりも高い場合に、前記第２流量調整弁を開状態とすると共に前記第２三方弁の前記第１流出口を閉状態にしかつ前記第２三方弁の前記第２流出口を開状態にし、前記第３温度センサにより検出された温度と前記第１温度センサにより検出された温度との差が前記第２所定値以下になった際に、前記第２三方弁の前記第２流出口を閉状態にしかつ前記第２三方弁の前記第１流出口を開状態にする、又は前記第２流量調整弁を閉状態とすると共に前記第１流量調整弁を開状態にしかつ前記第１三方弁の前記第１流出口を開状態にして前記第１三方弁の前記第２流出口を閉状態にする処理である、請求項１に記載のコンバインドサイクル発電プラント。
The first bleed pipe is provided on the downstream side of the first flow rate control valve, and includes an inlet into which the first compressed air flows, a first outlet through which the first compressed air flows out, and the first compressed air. a first three-way valve having a second outlet for flowing out to the region in the heat recovery steam generator;
a first boiler upstream connection pipe that connects the first outflow port of the first three-way valve and the heat recovery boiler;
An inflow port provided downstream of the second flow control valve in the second bleed pipe, into which the second compressed air flows, a first outflow port from which the second compressed air flows out, and the second compressed air. a second three-way valve having a second outlet for flowing out toward the first bleed pipe;
a second boiler upstream connection pipe that connects the first outlet of the second three-way valve and the heat recovery boiler;
a first temperature sensor that detects the ambient temperature of the region;
a second temperature sensor provided upstream of the first flow control valve in the first bleed pipe and detecting the temperature of the first compressed air;
a third temperature sensor provided upstream of the second flow control valve in the second bleed pipe and detecting the temperature of the second compressed air;
The control device is configured to perform a first process or a second process,
The first process includes opening the first flow control valve when a difference between the temperature detected by the second temperature sensor and the temperature detected by the first temperature sensor is higher than a first predetermined value. and closing the first outlet of the first three-way valve and opening the second outlet of the first three-way valve, the temperature detected by the second temperature sensor and the first temperature When the difference from the temperature detected by the sensor becomes equal to or less than the first predetermined value, the second outlet of the first three-way valve is closed and the first outlet of the first three-way valve is closed. The second three-way valve is opened, or the first flow rate adjustment valve is closed, the second flow rate adjustment valve is opened, and the first outflow port of the second three-way valve is opened. A process of closing the second outlet of
In the second process, when a difference between the temperature detected by the third temperature sensor and the temperature detected by the first temperature sensor is higher than a second predetermined value, the second flow control valve is opened. and closing the first outlet of the second three-way valve and opening the second outlet of the second three-way valve, the temperature detected by the third temperature sensor and the first temperature When the difference from the temperature detected by the sensor becomes equal to or less than the second predetermined value, the second outflow port of the second three-way valve is closed and the first outflow port of the second three-way valve is closed. The first three-way valve is opened, or the second flow rate adjustment valve is closed, the first flow rate adjustment valve is opened, and the first outflow port of the first three-way valve is opened. 2. The combined cycle power plant according to claim 1, wherein the process is to close said second outlet of .
JP2018149382A 2018-08-08 2018-08-08 Combined cycle power plant Active JP7153498B2 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
JP2018149382A JP7153498B2 (en) 2018-08-08 2018-08-08 Combined cycle power plant
KR1020217005227A KR102420538B1 (en) 2018-08-08 2019-07-25 Combined Cycle Power Plant
PCT/JP2019/029167 WO2020031715A1 (en) 2018-08-08 2019-07-25 Combined cycle power plant
CN201980051956.5A CN112534120B (en) 2018-08-08 2019-07-25 Combined cycle power plant
TW108128111A TWI705183B (en) 2018-08-08 2019-08-07 Combined cycle power plant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2018149382A JP7153498B2 (en) 2018-08-08 2018-08-08 Combined cycle power plant

Publications (2)

Publication Number Publication Date
JP2020023942A JP2020023942A (en) 2020-02-13
JP7153498B2 true JP7153498B2 (en) 2022-10-14

Family

ID=69414136

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2018149382A Active JP7153498B2 (en) 2018-08-08 2018-08-08 Combined cycle power plant

Country Status (5)

Country Link
JP (1) JP7153498B2 (en)
KR (1) KR102420538B1 (en)
CN (1) CN112534120B (en)
TW (1) TWI705183B (en)
WO (1) WO2020031715A1 (en)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013142393A (en) 2012-01-10 2013-07-22 General Electric Co <Ge> Combined cycle power plant
JP2015081560A (en) 2013-10-23 2015-04-27 三菱日立パワーシステムズ株式会社 Combined cycle plant
JP2017031859A (en) 2015-07-31 2017-02-09 三菱日立パワーシステムズ株式会社 Combined cycle power plant and control method thereof

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS592770B2 (en) * 1977-07-20 1984-01-20 株式会社日立製作所 Ammonia injection device for gas turbine denitrification
JPS64326A (en) * 1987-06-23 1989-01-05 Hitachi Ltd Nox abating type gas turbine plant
JP2653610B2 (en) * 1992-07-09 1997-09-17 株式会社東芝 Combined cycle power plant
JP2000130108A (en) * 1998-10-28 2000-05-09 Toshiba Corp Starting method for combined cycle power plant
JP4202583B2 (en) * 2000-06-06 2008-12-24 株式会社東芝 Denitration control method and apparatus for combined cycle power plant
KR102471507B1 (en) 2015-09-11 2022-11-29 엘지디스플레이 주식회사 Organic light emitting device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013142393A (en) 2012-01-10 2013-07-22 General Electric Co <Ge> Combined cycle power plant
JP2015081560A (en) 2013-10-23 2015-04-27 三菱日立パワーシステムズ株式会社 Combined cycle plant
JP2017031859A (en) 2015-07-31 2017-02-09 三菱日立パワーシステムズ株式会社 Combined cycle power plant and control method thereof

Also Published As

Publication number Publication date
CN112534120A (en) 2021-03-19
WO2020031715A1 (en) 2020-02-13
CN112534120B (en) 2023-05-16
TWI705183B (en) 2020-09-21
TW202012767A (en) 2020-04-01
KR20210033517A (en) 2021-03-26
KR102420538B1 (en) 2022-07-13
JP2020023942A (en) 2020-02-13

Similar Documents

Publication Publication Date Title
US20100170218A1 (en) Method for expanding compressor discharge bleed air
JP5476003B2 (en) Apparatus and method for start-up of a power plant
JP2010216477A (en) System and method for prewarming heat recovery steam generator and associated steam line
EP2587007A2 (en) System and method for operating heat recovery steam generators
JP6870970B2 (en) Steam generation system by turbine extraction
US10287921B2 (en) Combined cycle plant, method for controlling same, and device for controlling same
US20100281870A1 (en) System and method for heating fuel for a gas turbine
JP5050013B2 (en) Combined power plant and control method thereof
JP7153498B2 (en) Combined cycle power plant
JP2017110649A (en) System and method for controlling gas turbine exhaust energy via exhaust gas damper and compressed gas supply
US20180080347A1 (en) System and method for recovering turbine system extractions
JP5321340B2 (en) Steam injection gas turbine generator
JP5734117B2 (en) Combined cycle power plant and operation method thereof
JP7137397B2 (en) Combined cycle power plant
JP6877216B2 (en) Power generation system
JP7137398B2 (en) Combined cycle power plant
JP3065794B2 (en) Feed water heating device
JP2004346945A (en) Steam temperature control method and device of combined cycle plant
KR20160147243A (en) Waste heat recovery apparatus for combustion furnace and method thereof

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20210624

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20220607

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20220927

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20221003

R150 Certificate of patent or registration of utility model

Ref document number: 7153498

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150