JP3117424B2 - Gas turbine combined plant - Google Patents
Gas turbine combined plantInfo
- Publication number
- JP3117424B2 JP3117424B2 JP09288171A JP28817197A JP3117424B2 JP 3117424 B2 JP3117424 B2 JP 3117424B2 JP 09288171 A JP09288171 A JP 09288171A JP 28817197 A JP28817197 A JP 28817197A JP 3117424 B2 JP3117424 B2 JP 3117424B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- heat recovery
- recovery boiler
- heater
- gas turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ガスタービンと蒸
気タービンとを組み合わせたガスタービンコンバインド
プラントに関するものである。The present invention relates to a gas turbine combined plant in which a gas turbine and a steam turbine are combined.
【０００２】[0002]
【従来の技術】一般に、図２に示すようなガスタービン
コンバインドプラントにおいては、空気Ａを空気圧縮機
５１で圧縮して燃焼器５２に送り、該燃焼器５２内に供
給された燃料ガスＧを燃焼させ（約１４００〜１５００
゜Ｃ）、生じた高温高圧ガスをガスタービン５３中で膨
張させることにより発電機５４の動力を生み出し、更
に、このガスタービン５３の排気ガスの排熱（約６００
゜Ｃ）を利用すべくボトミングサイクルＢの排熱回収ボ
イラ（ＨＲＳＧ）５５に送り、該排熱回収ボイラ５５に
て発生させた蒸気により蒸気タービン５６を駆動させて
発電機５７の動力を生み出すようになっている。そし
て、蒸気タービン５６から排出された蒸気は、復水器５
８の熱交換部に導かれ、該熱交換部において海水等の冷
却水で冷却されて凝縮され、復水として排熱回収ボイラ
５５への給水系統に導かれている。2. Description of the Related Art Generally, in a gas turbine combined plant as shown in FIG. 2, air A is compressed by an air compressor 51 and sent to a combustor 52, and fuel gas G supplied to the combustor 52 is supplied to the combustor 52. Burn (about 1400-1500
゜ C), the generated high-temperature and high-pressure gas is expanded in the gas turbine 53 to generate the power of the generator 54, and further, the exhaust heat of the exhaust gas of the gas turbine 53 (about 600
(C) is sent to an exhaust heat recovery boiler (HRSG) 55 of the bottoming cycle B to utilize the steam, and the steam generated by the exhaust heat recovery boiler 55 drives a steam turbine 56 to generate power for a generator 57. It has become. The steam discharged from the steam turbine 56 is supplied to the condenser 5
In the heat exchange section, the water is cooled by condensed water such as seawater and condensed, and is condensed as condensed water into a water supply system to the exhaust heat recovery boiler 55.
【０００３】このようなガスタービンコンバインドプラ
ントでは、ＧＴロータ冷却空気を通常の空気冷却器にて
大気温度より冷却すると冷却後の温度まで熱を系外にそ
のまま放出することになり、約１．５％の燃料損失を招
くことから、系外に放出する空気Ａで燃料ガスＧを加熱
し、７割程度回収するＴＣＡによる空冷加熱システム
（タービン冷却空気システム）の空気冷却兼燃料加熱器
（ＴＣＡクーラ）５９が設けられている。この空気冷却
兼燃料加熱器５９は、図２および図３に示す如く、空気
圧縮機５１とガスタービン５３との間に設備されてお
り、外部下方には空冷のためのファン６０が設置されて
いる。しかして、ＧＴロータ冷却空気は空気圧縮機５１
から空気冷却兼燃料加熱器５９に送られ温度Ｔ1 （約４
４０゜Ｃ）の空気Ａは、ファン６０から送給される温度
３０゜Ｃの大気で冷却されて温度Ｔ2 （約２００゜Ｃ）
となり、ガスタービン５３に送られてタービンロータな
どを冷却し、タービン損傷を防止している。一方、空気
冷却兼燃料加熱器５９内に送られてくる温度Ｔ3 （約６
０゜Ｃ）の燃料ガスＧは、ロータ冷却空気冷却後の大気
（約２２０゜Ｃ）によって温度Ｔ4 （約２００゜Ｃ）に
加熱されて、燃焼器５２に供給されるようになってい
る。In such a gas turbine combined plant, if the cooling air of the GT rotor is cooled from the ambient temperature by a normal air cooler, the heat is released to the cooled temperature as it is outside the system. % Of the fuel loss, the fuel gas G is heated by the air A released to the outside of the system, and the air cooling and fuel heater (TCA cooler) of the air-cooling heating system (turbine cooling air system) by TCA recovers about 70%. ) 59 are provided. The air cooling and fuel heater 59 is provided between the air compressor 51 and the gas turbine 53, as shown in FIGS. 2 and 3, and a fan 60 for air cooling is installed below the outside. I have. Thus, the GT rotor cooling air is supplied to the air compressor 51.
Sent to the air cooling and fuel heater 59 from the temperature T 1 (about 4
The air A at 40 ° C. is cooled by the air at a temperature of 30 ° C. supplied from the fan 60 and the temperature T 2 (about 200 ° C.)
Is sent to the gas turbine 53 to cool the turbine rotor and the like, thereby preventing turbine damage. On the other hand, the temperature T 3 (about 6) sent into the air cooling and fuel heater 59.
The fuel gas G at 0 ° C. is heated to a temperature T 4 (about 200 ° C.) by the atmosphere (about 220 ° C.) after cooling the rotor cooling air, and is supplied to the combustor 52. .
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、上述し
た従来のガスタービンコンバインドプラントの空気冷却
兼燃料加熱器５９による熱回収では、冷却後の大気温度
が約２２０゜Ｃであり、燃料ガス加熱媒体（空気）上限
による空気―ガス熱交換器の制約があるため、約０．４
％程度の燃料損失が依然として残存しており、更なる改
善が要望されていた。However, in the above-described heat recovery by the air cooling and fuel heater 59 of the conventional gas turbine combined plant, the ambient temperature after cooling is about 220 ° C., and the fuel gas heating medium ( (Air) Approximately 0.4
% Of fuel loss still remains, and further improvements have been requested.
【０００５】本発明はこのような実状に鑑みてなされた
ものであって、その目的は、従来の空冷加熱システムに
比べて更に熱効率を改善し、運転コストを低減させるこ
とが可能なガスタービンコンバインドプラントを提供す
ることにある。The present invention has been made in view of such circumstances, and has as its object to provide a gas turbine combined system capable of further improving thermal efficiency and reducing operating costs as compared with a conventional air-cooled heating system. To provide a plant.
【０００６】[0006]
【課題を解決するための手段】上記従来技術の有する課
題を解決するために、本発明においては、空気圧縮機、
燃焼器および空気冷却器を有するガスタービンの排気ガ
スを排熱回収ボイラに送り、該排熱回収ボイラにて発生
させた蒸気により蒸気タービンを駆動するガスタービン
コンバインドプラントにおいて、前記ガスタービンの燃
焼器の上流側に加熱器を設け、該加熱器と前記排熱回収
ボイラの中圧エコノマイザまたは低圧エバポレータとを
接続するとともに、前記加熱器と脱気器とを接続し、か
つ前記空気冷却器と前記排熱回収ボイラの高圧エコノマ
イザとを接続するとともに、前記空気冷却器と高圧ドラ
ムとを接続し、前記排熱回収ボイラの高圧エコノマイザ
へ送られる第１作動流体によって前記空気圧縮機から送
られる前記空気冷却器内の空気を冷却し、熱交換後にお
ける前記空気冷却器内の第１作動流体を前記高圧ドラム
に送給する一方、前記排熱回収ボイラの中圧エコノマイ
ザまたは低圧エバポレータから送られる第２作動流体に
よって前記加熱器内の燃料ガスを加熱して前記燃焼器に
供給し、燃料ガスを加熱した前記加熱器内の第２作動流
体を前記脱気器に送給して戻すように構成している。In order to solve the above-mentioned problems of the prior art, the present invention provides an air compressor,
In a gas turbine combined plant in which exhaust gas of a gas turbine having a combustor and an air cooler is sent to an exhaust heat recovery boiler and a steam turbine is driven by steam generated in the exhaust heat recovery boiler, the combustor of the gas turbine A heater is provided on the upstream side, and the heater is connected to the medium-pressure economizer or the low-pressure evaporator of the exhaust heat recovery boiler, and the heater is connected to the deaerator.
One said while connected to the air cooler and the high pressure economizer of the waste heat recovery boiler, the air cooler and the high pressure Dora
The air in the air cooler sent from the air compressor is cooled by the first working fluid sent to the high-pressure economizer of the exhaust heat recovery boiler .
The first working fluid in the air cooler to the high pressure drum
While feeding the said heated fuel gas in the heater by a second working fluid sent from intermediate pressure economizer or low pressure evaporator of the waste heat recovery boiler is supplied to the combustor, and heat the fuel gas the Second working flow in heater
The body is configured to be fed back to the deaerator .
【０００７】[0007]
【発明の実施の形態】以下、本発明を図示の実施の形態
に基づいて詳細に説明する。ここで、図１は本発明の実
施の形態に係るガスタービンコンバインドプラントの説
明図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail based on illustrated embodiments. Here, FIG. 1 is an explanatory diagram of a gas turbine combined plant according to an embodiment of the present invention.
【０００８】本発明の実施形態のガスタービンコンバイ
ンドプラントは、図１に示す如く、主として空気圧縮機
１、燃焼器２、空気冷却器３、ガスタービン４および加
熱器５が設備されるトッピングサイクルＴと、主として
排熱回収ボイラ（ＨＲＳＧ）６、蒸気タービン７および
復水器８が設備されるボトミングサイクルＢとを組み合
わせたもので、ガスタービン４の排気ガスを排熱回収ボ
イラ６に送り、この排熱回収ボイラ６にて発生させた蒸
気により蒸気タービン７を駆動する発電プラントであ
る。As shown in FIG. 1, a gas turbine combined plant according to an embodiment of the present invention mainly includes a topping cycle T in which an air compressor 1, a combustor 2, an air cooler 3, a gas turbine 4 and a heater 5 are installed. And a bottoming cycle B in which a heat recovery steam generator (HRSG) 6, a steam turbine 7 and a condenser 8 are installed, and the exhaust gas of the gas turbine 4 is sent to the heat recovery steam generator 6. This is a power plant that drives a steam turbine 7 with steam generated by the exhaust heat recovery boiler 6.
【０００９】上記トッピングサイクルＴは、従来のＴＣ
Ａによる空冷加熱システムを採用しておらず、これに代
えてボトミングサイクルＢによるロータ冷却空気の冷却
と、ボトミングサイクルＢによる燃料ガスＧの加熱を行
うシステムを採用している。空気圧縮機１は、供給され
た空気Ａを圧縮するもので、その下流側は２系統に分岐
されており、それぞれの経路には燃焼器２または空気冷
却器３が設けられている。燃焼器２は、供給された燃焼
ガスＧを加熱燃焼するもので、その下流側には生じた高
温高圧ガスを送給するガスタービン４が設けられてい
る。このガスタービン４は、内部で高温高圧ガスを膨張
させることにより駆動され、発電機９を回して発電する
ように構成されている。The above-mentioned topping cycle T is the same as the conventional TC
An air-cooled heating system according to A is not employed, and instead, a system that cools the rotor cooling air by the bottoming cycle B and heats the fuel gas G by the bottoming cycle B is employed. The air compressor 1 compresses the supplied air A, and its downstream side is branched into two systems, and each path is provided with a combustor 2 or an air cooler 3. The combustor 2 heats and burns the supplied combustion gas G, and a gas turbine 4 for supplying the generated high-temperature and high-pressure gas is provided downstream thereof. The gas turbine 4 is driven by expanding a high-temperature and high-pressure gas inside, and is configured to rotate a generator 9 to generate power.
【００１０】また、空気冷却器３は、ＴＣＡクーラでな
い通常の冷却器であって、空気圧縮機１から送られてく
る高温の空気Ａを内部で強制的に冷却するものであり、
冷却された空気Ａは下流側に設置されたガスタービン４
に送られてタービンロータなどを冷却している。このた
め、上記空気冷却器３と上記ボトミングサイクルＢの排
熱回収ボイラ６とは互いに接続されており、該排熱回収
ボイラ６から高温の空気Ａを冷却する第１作動流体Ｗ1
が空気冷却器３内に送給されるように構成されている。The air cooler 3 is a normal cooler that is not a TCA cooler, and forcibly cools the high-temperature air A sent from the air compressor 1 inside.
The cooled air A is supplied to the gas turbine 4 installed on the downstream side.
To cool the turbine rotor. Therefore, the air cooler 3 and the exhaust heat recovery boiler 6 of the bottoming cycle B are connected to each other, and the first working fluid W 1 for cooling the high-temperature air A from the exhaust heat recovery boiler 6.
Is supplied into the air cooler 3.
【００１１】一方、上記加熱器５は、燃焼器２の上流側
に設けられているとともに、排熱回収ボイラ６と互いに
接続されており、該排熱回収ボイラ６から燃料ガスＧを
加熱する第２作動流体Ｗ2 が加熱器５内に送給されるよ
うに構成されている。なお、加熱器５は脱気器１０に接
続されており、加熱後における加熱器５内の第２作動流
体Ｗ2 は脱気器１０に送給されるようになっている。On the other hand, the heater 5 is provided on the upstream side of the combustor 2 and is connected to the exhaust heat recovery boiler 6 to heat the fuel gas G from the exhaust heat recovery boiler 6. The two working fluids W 2 are configured to be supplied into the heater 5. Incidentally, the heater 5 is connected to Datsukiki 10, second working fluid W 2 in the heater 5 after heating is adapted to be delivered to Datsukiki 10.
【００１２】上記ボトミングサイクルＢの排熱回収ボイ
ラ６は、ボイラ本体の内部に供給されているボイラ水を
加熱することにより所定の圧力および温度の蒸気を発生
させるものであり、高圧（ＨＰ）・中圧（ＩＰ）・低圧
（ＬＰ）に分かれた三重圧方式構造となっている。そし
て、本実施形態に係る排熱回収ボイラ６の内部には、そ
れぞれの圧力と対応して図示しない節炭器のエコノマイ
ザ（ＥＣＯ）、蒸発器のエバポレータ（ＥＶＡ）および
スーパヒータ（ＳＨ）等が設けられている。本実施形態
では、空気冷却器３が排熱回収ボイラ６の高圧エコノマ
イザ（ＨＰ―ＥＣＯ）の入口と接続され、該高圧エコノ
マイザの入口への給水（約１３８゜Ｃ）を第１作動流体
Ｗ1 として使用しており、第１作動流体（水）Ｗ1 は空
気冷却器３に送給されるようになっている。そして、熱
交換後における空気冷却器３内の第１作動流体Ｗ1 は、
高圧ドラムに送給されるようになっている。また、本実
施形態では、加熱器５が排熱回収ボイラ６の中圧エコノ
マイザ（ＩＰ―ＥＣＯ）の出口と接続され、該中圧エコ
ノマイザの出口から排出される抽水（約２４０゜Ｃ）を
第２作動流体Ｗ2 として使用しており、第２作動流体
（水）Ｗ2 は加熱器５に送給され燃料を加熱した後、脱
気器の貯水槽へ戻される。The exhaust heat recovery boiler 6 of the bottoming cycle B generates steam at a predetermined pressure and temperature by heating boiler water supplied to the inside of the boiler main body. It has a triple pressure type structure divided into medium pressure (IP) and low pressure (LP). Inside the exhaust heat recovery boiler 6 according to the present embodiment, an economizer (ECO) of a economizer, an evaporator (EVA) of an evaporator, a superheater (SH), and the like (not shown) are provided corresponding to the respective pressures. Have been. In the present embodiment, the air cooler 3 is connected to the inlet of the high-pressure economizer (HP-ECO) of the exhaust heat recovery boiler 6, and supplies water (about 138 ° C.) to the inlet of the high-pressure economizer with the first working fluid W 1. The first working fluid (water) W 1 is supplied to the air cooler 3. Then, the first working fluid W 1 in the air cooler 3 after the heat exchange is:
It is fed to a high pressure drum. Further, in the present embodiment, the heater 5 is connected to the outlet of the medium pressure economizer (IP-ECO) of the exhaust heat recovery boiler 6 and extracts the extracted water (about 240 ° C.) from the outlet of the medium pressure economizer. are used as a second working fluid W 2, the second working fluid (water) W 2 after heating the fuel is fed to the heater 5, it is returned to the reservoir of the deaerator.
【００１３】なお、排熱回収ボイラ６の下流側には、蒸
気により駆動されて発電機１１を回す動力を生み出す蒸
気タービン７が設置されており、該蒸気タービン７の下
流側にはタービン排気を凝縮させ、復水として排熱回収
ボイラ６への給水系統に導く復水器８が設置されてい
る。A steam turbine 7 which is driven by steam to generate power for rotating the generator 11 is provided downstream of the exhaust heat recovery boiler 6, and turbine exhaust is provided downstream of the steam turbine 7. A condenser 8 is provided to condense the water and lead it to a water supply system to a waste heat recovery boiler 6 as condensate.
【００１４】本実施形態のガスタービンコンバインドプ
ラントにおいて、空気Ａが空気圧縮機１に供給される
と、この空気Ａは空気圧縮機１で圧縮されるとともに、
燃焼器２および空気冷却器３に送られる。空気冷却器３
に送られてくる空気Ａは、温度が約４４０゜Ｃとなって
いるが、排熱回収ボイラ６の高圧エコノマイザから第１
作動流体（１３８゜Ｃ）Ｗ1 が空気冷却器３内に送給さ
れており、この第１作動流体Ｗ1 で約２００゜Ｃに冷却
されて、ガスタービン４に送られる。また、上記加熱器
５には、排熱回収ボイラ６の中圧エコノマイザから第２
作動流体（約２４０゜Ｃ）Ｗ2 が送られており、加熱器
５内の燃料ガスＧは、当該第２作動流体Ｗ2 によって加
熱される（約２２０゜Ｃ）。この加熱された燃料ガスＧ
は、燃焼器２に供給されて空気圧縮機１からの圧縮空気
と一緒に加熱燃焼され、高温高圧ガスとなってガスター
ビン４に送給される。しかる後、従来例と同様の手順
で、ガスタービン４は発電機９の動力を生み出し、その
排気ガスは排熱回収ボイラ６に送られて排熱が利用さ
れ、該排熱回収ボイラ６の蒸気で蒸気タービン７が駆動
される。In the gas turbine combined plant of the present embodiment, when air A is supplied to the air compressor 1, this air A is compressed by the air compressor 1 and
It is sent to the combustor 2 and the air cooler 3. Air cooler 3
The temperature of the air A sent to the exhaust gas is about 440 ° C.
The working fluid (138 ° C.) W 1 is supplied into the air cooler 3, cooled to about 200 ° C. by the first working fluid W 1 , and sent to the gas turbine 4. Further, the heater 5 is provided with the second heat from the medium pressure economizer
The working fluid (about 240 ° C.) W 2 is sent, and the fuel gas G in the heater 5 is heated by the second working fluid W 2 (about 220 ° C.). This heated fuel gas G
Is supplied to the combustor 2 and is heated and burned together with the compressed air from the air compressor 1 to be supplied to the gas turbine 4 as a high-temperature high-pressure gas. Thereafter, in the same procedure as in the conventional example, the gas turbine 4 generates the power of the generator 9, and the exhaust gas is sent to the exhaust heat recovery boiler 6 to use the exhaust heat, and the steam of the exhaust heat recovery boiler 6 is used. Drives the steam turbine 7.
【００１５】本実施形態のガスタービンコンバインドプ
ラントでは、ロータ冷却空気が排熱回収ボイラ６の第１
作動流体Ｗ1 によって冷却され、加熱器５内の燃料ガス
Ｇが排熱回収ボイラ６の第２作動流体Ｗ2 によって加熱
され、従来の燃料ガス温度（約２００゜Ｃ）に比べて、
約３０〜６０゜Ｃ程度高めることが可能になるため、元
来の損失の相対値で約０．４％程度を改善することがで
きる。この改善による経済的な利益は約４億円に相当す
る。In the gas turbine combined plant of the present embodiment, the rotor cooling air is supplied to the first heat recovery boiler 6
Cooled by working fluid W 1, the fuel gas G in the heater 5 is heated by the second working fluid W 2 of the exhaust heat recovery boiler 6, as compared with the conventional fuel gas temperature (about 200 ° C),
Since the temperature can be increased by about 30 to 60 ° C., the relative value of the original loss can be improved by about 0.4%. The economic benefit of this improvement is about 400 million yen.
【００１６】以上、本発明の実施の形態につき述べた
が、本発明は既述の実施の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内において種々の変
形および変更を加え得るものである。例えば、既述の実
施の形態では、加熱器５内で燃焼ガスＧを加熱する第２
作動流体Ｗ2 として排熱回収ボイラ６からの中圧エコノ
マイザから抽水された水を使用したが、確実に燃焼ガス
Ｇを加熱できるものであれば、低圧エバポレータの蒸気
などを作動流体として使用しても良い。Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications and changes may be made without departing from the spirit of the present invention. What you get. For example, in the above-described embodiment, the second heating of the combustion gas G in the heater 5 is performed.
While using emergent water from pressure economizer among the exhaust heat recovery boiler 6 as the working fluid W 2, as long as it can heat reliably combustion gas G, it was used as such a working fluid vapor of the low-pressure evaporator Is also good.
【００１７】[0017]
【発明の効果】上述の如く、本発明に係るガスタービン
コンバインドプラントは、空気圧縮機、燃焼器および空
気冷却器を有するガスタービンの排気ガスを排熱回収ボ
イラに送り、該排熱回収ボイラにて発生させた蒸気によ
り蒸気タービンを駆動するガスタービンコンバインドプ
ラントにおいて、前記ガスタービンの燃焼器の上流側に
加熱器を設け、該加熱器と前記排熱回収ボイラの中圧エ
コノマイザまたは低圧エバポレータとを接続するととも
に、前記加熱器と脱気器とを接続し、かつ前記空気冷却
器と前記排熱回収ボイラの高圧エコノマイザとを接続す
るとともに、前記空気冷却器と高圧ドラムとを接続し、
前記排熱回収ボイラの高圧エコノマイザへ送られる第１
作動流体によって前記空気圧縮機から送られる前記空気
冷却器内の空気を冷却し、熱交換後における前記空気冷
却器内の第１作動流体を前記高圧ドラムに送給する一
方、前記排熱回収ボイラの中圧エコノマイザまたは低圧
エバポレータから送られる第２作動流体によって前記加
熱器内の燃料ガスを加熱して前記燃焼器に供給し、燃焼
ガスを加熱した前記加熱器内の第２作動流体を前記脱気
器に送給して戻すように構成しているので、次のような
種々の効果が得られる。すなわち、本発明のガスタービ
ンコンバインドプラントによれば、従来の空冷加熱シス
テムに比べて、プラント熱効率が改善され、運転コスト
の低減化を図ることができる。しかも、本発明のガスタ
ービンコンバインドプラントでは、燃焼器やガスタービ
ンへの水の漏洩に対する検知精度を向上させて高圧の給
水等レベルまでの圧力で回収熱を高圧の飽和温度程度ま
で上げることを可能にし、空気冷却器内のロータ冷却空
気の冷却を排熱回収ボイラの作動流体を利用して行い、
かつ冷却後の作動流体を高圧ドラムに戻し蒸気として回
収し得る上、加熱器内の燃料ガスの熱源として排熱回収
ボイラの作動流体を利用して行い、かつ加熱後の作動流
体をボイラ水として使用し得るので、設備費が安価で済
み、経済的に有利である。As described above, the gas turbine combined plant according to the present invention sends the exhaust gas of a gas turbine having an air compressor, a combustor, and an air cooler to an exhaust heat recovery boiler, and sends the exhaust gas to the exhaust heat recovery boiler. In a gas turbine combined plant that drives a steam turbine by using the generated steam, a heater is provided upstream of a combustor of the gas turbine, and the heater and the medium-pressure economizer or the low-pressure evaporator of the exhaust heat recovery boiler are provided. While connecting, the heater and the deaerator are connected, and the air cooler and the high-pressure economizer of the exhaust heat recovery boiler are connected, and the air cooler and the high-pressure drum are connected,
First sent to the high pressure economizer of the waste heat recovery boiler
The air in the air cooler sent from the air compressor is cooled by a working fluid, and the first working fluid in the air cooler after heat exchange is supplied to the high-pressure drum, while the exhaust heat recovery boiler is used. The fuel gas in the heater is heated by the second working fluid sent from the medium-pressure economizer or the low-pressure evaporator and supplied to the combustor, and the second working fluid in the heater that heats the combustion gas is removed from the heater. Since it is configured to be fed back to the gastrointestinal tract, the following various effects can be obtained. That is, according to the gas turbine combined plant of the present invention, the plant thermal efficiency can be improved and the operating cost can be reduced as compared with the conventional air-cooled heating system. Moreover, in the gas turbine combined plant of the present invention, it is possible to improve the detection accuracy of water leakage to the combustor and the gas turbine, and to increase the recovered heat to a high pressure saturation temperature at a pressure up to a high pressure water supply level. The cooling of the rotor cooling air in the air cooler is performed using the working fluid of the exhaust heat recovery boiler,
In addition to returning the cooled working fluid to the high-pressure drum and recovering it as steam, the working fluid of the exhaust heat recovery boiler is used as a heat source for the fuel gas in the heater, and the heated working fluid is used as boiler water. Since it can be used, the equipment cost is low and it is economically advantageous.
【図１】本発明の実施の形態に係るガスタービンコンバ
インドプラントを示す概略図である。FIG. 1 is a schematic diagram showing a gas turbine combined plant according to an embodiment of the present invention.
【図２】従来のガスタービンコンバインドプラントを示
す概略図である。FIG. 2 is a schematic view showing a conventional gas turbine combined plant.
【図３】従来のガスタービンコンバインドプラントに設
備される空気冷却兼燃料加熱器を示す概略図である。FIG. 3 is a schematic diagram showing an air cooling and fuel heater installed in a conventional gas turbine combined plant.
１ 空気圧縮機 ２ 燃焼器 ３ 空気冷却器 ４ ガスタービン ５ 加熱器 ６ 排熱回収ボイラ ７ 蒸気タービン ８ 復水器 ９，１１ 発電機 Ａ 空気 Ｇ 燃料ガス Ｗ1 第１作動流体 Ｗ2 第２作動流体DESCRIPTION OF SYMBOLS 1 Air compressor 2 Combustor 3 Air cooler 4 Gas turbine 5 Heater 6 Waste heat recovery boiler 7 Steam turbine 8 Condenser 9, 11 Generator A Air G Fuel gas W 1 First working fluid W 2 Second working fluid
フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F01K 23/10 F02C 6/18 F02C 7/143 F02C 7/224 Continuation of the front page (58) Field surveyed (Int.Cl. 7 , DB name) F01K 23/10 F02C 6/18 F02C 7/143 F02C 7/224
Claims (1)
有するガスタービンの排気ガスを排熱回収ボイラに送
り、該排熱回収ボイラにて発生させた蒸気により蒸気タ
ービンを駆動するガスタービンコンバインドプラントに
おいて、前記ガスタービンの燃焼器の上流側に加熱器を
設け、該加熱器と前記排熱回収ボイラの中圧エコノマイ
ザまたは低圧エバポレータとを接続するとともに、前記
加熱器と脱気器とを接続し、かつ前記空気冷却器と前記
排熱回収ボイラの高圧エコノマイザとを接続するととも
に、前記空気冷却器と高圧ドラムとを接続し、前記排熱
回収ボイラの高圧エコノマイザへ送られる第１作動流体
によって前記空気圧縮機から送られる前記空気冷却器内
の空気を冷却し、熱交換後における前記空気冷却器内の
第１作動流体を前記高圧ドラムに送給する一方、前記排
熱回収ボイラの中圧エコノマイザまたは低圧エバポレー
タから送られる第２作動流体によって前記加熱器内の燃
料ガスを加熱して前記燃焼器に供給し、燃料ガスを加熱
した前記加熱器内の第２作動流体を前記脱気器に送給し
て戻すように構成したことを特徴とするガスタービンコ
ンバインドプラント。An exhaust gas from a gas turbine having an air compressor, a combustor, and an air cooler is sent to an exhaust heat recovery boiler, and the steam turbine is driven by steam generated by the exhaust heat recovery boiler. in the plant, together with the heater on the upstream side of the combustor of a gas turbine is provided, connected to the the heating device and the intermediate pressure economizer or low pressure evaporator of the heat recovery steam generator, wherein
Connecting the heater and the deaerator, and connects Then together the high pressure economizer of the waste heat recovery boiler and the air cooler
Connecting the air cooler and a high-pressure drum, cooling the air in the air cooler sent from the air compressor by the first working fluid sent to the high-pressure economizer of the exhaust heat recovery boiler , and exchanging heat. Later in the air cooler
The first working fluid is supplied to the high-pressure drum, and the fuel gas in the heater is heated by the second working fluid sent from the medium-pressure economizer or the low-pressure evaporator of the exhaust heat recovery boiler and supplied to the combustor. And heat the fuel gas
Supplying the second working fluid in the heater to the deaerator.
A gas turbine combined plant characterized by being configured to return .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP09288171A JP3117424B2 (en) | 1997-10-21 | 1997-10-21 | Gas turbine combined plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP09288171A JP3117424B2 (en) | 1997-10-21 | 1997-10-21 | Gas turbine combined plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11117714A JPH11117714A (en) | 1999-04-27 |
| JP3117424B2 true JP3117424B2 (en) | 2000-12-11 |
Family
ID=17726738
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP09288171A Expired - Lifetime JP3117424B2 (en) | 1997-10-21 | 1997-10-21 | Gas turbine combined plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3117424B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4488631B2 (en) | 2001-01-18 | 2010-06-23 | 株式会社東芝 | Combined cycle power generation facility and operation method thereof |
| JP3716188B2 (en) | 2001-04-10 | 2005-11-16 | 三菱重工業株式会社 | Gas turbine combined plant |
| JP5787857B2 (en) | 2012-09-27 | 2015-09-30 | 三菱日立パワーシステムズ株式会社 | Control method for gas turbine cooling system, control device for executing the method, and gas turbine equipment equipped with the control device |
| KR101784553B1 (en) * | 2015-04-16 | 2017-11-06 | 두산중공업 주식회사 | Hybrid power generation system using a supercritical CO2 cycle |
-
1997
- 1997-10-21 JP JP09288171A patent/JP3117424B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11117714A (en) | 1999-04-27 |
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