JP2003269188A - Steam injection reheat gas turbine generator - Google Patents
Steam injection reheat gas turbine generatorInfo
- Publication number
- JP2003269188A JP2003269188A JP2002075494A JP2002075494A JP2003269188A JP 2003269188 A JP2003269188 A JP 2003269188A JP 2002075494 A JP2002075494 A JP 2002075494A JP 2002075494 A JP2002075494 A JP 2002075494A JP 2003269188 A JP2003269188 A JP 2003269188A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- combustor
- gas turbine
- power generation
- gas
- 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.)
- Pending
Links
- 238000010793 Steam injection (oil industry) Methods 0.000 title claims abstract description 37
- 239000007789 gas Substances 0.000 claims abstract description 92
- 238000010248 power generation Methods 0.000 claims abstract description 42
- 239000000446 fuel Substances 0.000 claims abstract description 17
- 239000000567 combustion gas Substances 0.000 claims abstract description 13
- 238000011084 recovery Methods 0.000 claims description 13
- 230000006835 compression Effects 0.000 claims 1
- 238000007906 compression Methods 0.000 claims 1
- 230000007423 decrease Effects 0.000 abstract description 11
- 230000001052 transient effect Effects 0.000 abstract description 7
- 230000004044 response Effects 0.000 abstract description 6
- 238000002347 injection Methods 0.000 abstract description 5
- 239000007924 injection Substances 0.000 abstract description 5
- 239000000243 solution Substances 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 6
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 6
- 239000003638 chemical reducing agent Substances 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
(57)【要約】
【課題】 始動性、発電出力と熱効率、及び過渡応答性
に優れ、かつ蒸気噴射を行なわない時でも、ガス流量、
圧力比、回転速度の低下が少なく、高い発電出力と熱効
率を維持できる蒸気噴射再熱ガスタービン発電装置を提
供する。
【解決手段】 吸気を圧縮する圧縮機１２と、圧縮した
空気で燃料を燃焼させる第１燃焼器１３と、第１燃焼器
の燃焼ガスで駆動され前記圧縮機を駆動する圧縮機用タ
ービン１４とを有する第１ガスタービン装置２０と、圧
縮機用タービンの排ガスで燃料を燃焼させる第２燃焼器
１５と、第２燃焼器の燃焼ガスで駆動され発電機１８を
駆動する発電用タービン１６とを有する第２ガスタービ
ン装置２２と、第２燃焼器１５に水蒸気を噴射する蒸気
噴射装置２４とを備え、発電用タービンの回転速度を一
定速度に保持し、かつ、第２燃焼器１５への水蒸気の噴
射量により発電出力を制御する。
(57) [Summary] [PROBLEMS] The gas flow rate, even when steam injection is not performed, is excellent in startability, power generation output and thermal efficiency, and transient response.
Provided is a steam injection reheat gas turbine power generation device capable of maintaining a high power generation output and a high thermal efficiency with a small decrease in a pressure ratio and a rotation speed. SOLUTION: A compressor 12 for compressing intake air, a first combustor 13 for burning fuel with compressed air, a compressor turbine 14 driven by combustion gas of the first combustor and driving the compressor, and A first gas turbine device 20 having a gas turbine, a second combustor 15 for burning fuel with exhaust gas from a compressor turbine, and a power generation turbine 16 driven by combustion gas of the second combustor and driving a generator 18. A second gas turbine device 22 and a steam injection device 24 for injecting steam into the second combustor 15, the rotation speed of the power generation turbine is maintained at a constant speed, and the steam is supplied to the second combustor 15. The power generation output is controlled by the amount of injection.
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、再熱ガスタービン
に係り、更に詳しくは、蒸気噴射により発電出力と熱効
率を高めることができる蒸気噴射再熱ガスタービン発電
装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reheat gas turbine, and more particularly to a steam injection reheat gas turbine power generator capable of increasing power generation output and thermal efficiency by steam injection.
【０００２】[0002]
【従来の技術】ガスタービンへ水蒸気を注入する従来の
蒸気噴射ガスタービン発電装置は、図３に例示するよう
に、大気中から吸入した空気を圧縮機２で圧縮して燃焼
室３に供給し、この圧縮空気で燃料を燃焼させて高温の
燃焼ガスを発生し、この燃焼ガスによりタービン４を駆
動して圧縮機２及び発電機１を駆動し、更にタービン４
を出た燃焼ガスにより排熱回収ボイラ６で水蒸気を発生
させ、排気を大気中に放出するようになっている。な
お、この図で５は発電機用の減速機である。2. Description of the Related Art In a conventional steam injection gas turbine power generator for injecting steam into a gas turbine, air sucked from the atmosphere is compressed by a compressor 2 and supplied to a combustion chamber 3 as shown in FIG. , The compressed air is used to burn fuel to generate high-temperature combustion gas, and the combustion gas drives the turbine 4 to drive the compressor 2 and the generator 1.
The exhaust gas is generated in the exhaust heat recovery boiler 6 by the generated combustion gas and the exhaust gas is discharged into the atmosphere. In this figure, 5 is a reducer for a generator.
【０００３】かかる従来の蒸気噴射ガスタービン発電装
置は、燃焼室３に排熱回収ボイラ６で発生した水蒸気Ｓ
を噴射するためタービンに流入する燃焼ガスの流量が増
大し、かつ燃焼ガスの比熱が増大することからタービン
の出力と熱効率を高めることができる特徴を有してい
る。In such a conventional steam injection gas turbine power generator, steam S generated in the exhaust heat recovery boiler 6 in the combustion chamber 3 is used.
Since the fuel is injected, the flow rate of the combustion gas flowing into the turbine is increased, and the specific heat of the combustion gas is increased, so that the output and thermal efficiency of the turbine can be increased.
【０００４】[0004]
【発明が解決しようとする課題】しかし、図３に示した
従来の蒸気噴射ガスタービン発電装置は、１軸式ガスタ
ービンであるため、以下の問題点があった。
（１）始動時に圧縮機２及びタービン４だけでなく、負
荷（発電機１）をも駆動する必要があり、大容量の始動
モータ（又はエアタービン）が必要となり、負荷との間
にクラッチが必要となる。従って始動性が悪い。
（２）負荷と直接結合されているため、負荷の要求回転
速度にリンクした回転速度で運転することが必要にな
る。このため、必要動力に関わらず圧縮機２は一定量の
空気を取り込んでしまい、出力制御は主として燃焼量に
よるためサージに陥りやすい。また、特に部分負荷で
は、最適条件での運転はできず燃費に不利である。
（３）圧縮機２及びタービン４の慣性が大きく、一旦変
化した回転速度の回復が遅く、過渡応答性が低い。However, since the conventional steam injection gas turbine power generator shown in FIG. 3 is a single-shaft gas turbine, it has the following problems. (1) It is necessary to drive not only the compressor 2 and the turbine 4 but also the load (generator 1) at the time of starting, a large capacity starting motor (or air turbine) is required, and a clutch between the load and Will be needed. Therefore, startability is poor. (2) Since it is directly connected to the load, it is necessary to operate at a rotation speed linked to the required rotation speed of the load. For this reason, the compressor 2 takes in a fixed amount of air regardless of the required power, and the output control mainly depends on the combustion amount, so that a surge easily occurs. Further, particularly under partial load, it is not possible to operate under optimum conditions, which is disadvantageous in fuel consumption. (3) The inertia of the compressor 2 and the turbine 4 is large, the recovery of the once changed rotation speed is slow, and the transient response is low.
【０００５】上述した１軸式ガスタービンの問題点を解
決するために、図４に例示するような、２軸式ガスター
ビンが提案されている。この２軸式ガスタービンは、圧
縮機２は高圧タービン４ａとのみ連結しており、負荷
（発電機１）は、低圧タービン４ｂと減速機５を介して
連結している。この構成により、２軸式ガスタービン
は、以下の特徴を有する。
（１）始動時に圧縮機２と高圧タービン４ａのみの駆動
でよいため、小型の始動用モータの使用ができる。従っ
て始動性が良い。
（２）負荷の要求回転速度とは関係なく圧縮機２と高圧
タービン４ａは最も効率の良い最適回転速度で運転がで
きる。従って部分負荷でも効率の低下が少なく燃費が良
い。圧縮機２の回転速度を変化させ必要出力に応じた最
適空気取り入れ量での運転が可能なため、サージマージ
ンが大きく安定した運転が可能である。
（３）圧縮機２及び高圧タービン４の慣性が小さく、か
つ最適回転速度での運転が可能なため変動時の回復が早
く、過渡応答性が高い。In order to solve the above-mentioned problems of the one-shaft type gas turbine, a two-shaft type gas turbine as illustrated in FIG. 4 has been proposed. In this two-shaft gas turbine, the compressor 2 is connected only to the high-pressure turbine 4a, and the load (generator 1) is connected to the low-pressure turbine 4b via the speed reducer 5. With this configuration, the two-shaft gas turbine has the following features. (1) Since only the compressor 2 and the high pressure turbine 4a need be driven at the time of starting, a small starting motor can be used. Therefore, the startability is good. (2) The compressor 2 and the high-pressure turbine 4a can be operated at the most efficient optimum rotation speed regardless of the required rotation speed of the load. Therefore, the efficiency is small and the fuel consumption is good even with partial load. Since the operation can be performed with the optimum air intake amount according to the required output by changing the rotation speed of the compressor 2, the surge margin is large and stable operation is possible. (3) Since the inertia of the compressor 2 and the high-pressure turbine 4 is small, and the compressor 2 and the high-pressure turbine 4 can be operated at an optimum rotation speed, recovery at the time of fluctuation is fast and transient response is high.
【０００６】しかし、この２軸式ガスタービンの燃焼器
３に水蒸気を噴射して、蒸気噴射型再熱ガスタービン発
電装置を構成した場合、以下の問題点がある。蒸気噴射
を行う時には全体のガス流量が大きく、圧力比が高く、
所定の回転速度を維持でき、高い発電出力と熱効率が得
られる。しかし、蒸気噴射を停止すると、高圧タービン
４ａと低圧タービン４ｂのガス流量が大幅に低下し、回
転速度も大幅に低下するため、圧力比も大きく低下し、
この結果、低圧タービン４ｂは所定の回転速度を維持で
きなくなり、発電出力と熱効率の両方が大きく低下して
しまう。However, when steam is injected into the combustor 3 of the two-shaft gas turbine to construct a steam injection type reheat gas turbine power generator, there are the following problems. When performing steam injection, the total gas flow rate is high, the pressure ratio is high,
A predetermined rotation speed can be maintained and high power generation output and thermal efficiency can be obtained. However, when the steam injection is stopped, the gas flow rates of the high-pressure turbine 4a and the low-pressure turbine 4b are significantly reduced, and the rotation speed is also significantly reduced, so that the pressure ratio is also significantly reduced.
As a result, the low-pressure turbine 4b cannot maintain a predetermined rotation speed, and both the power generation output and the thermal efficiency are greatly reduced.
【０００７】本発明はかかる問題点を解決するために創
案されたものである。すなわち、本発明の目的は、始動
性、発電出力と熱効率、及び過渡応答性に優れ、かつ蒸
気噴射を行なわない時でも、ガス流量、圧力比、回転速
度の低下が少なく、高い発電出力と熱効率を維持できる
蒸気噴射再熱ガスタービン発電装置を提供することにあ
る。The present invention was created to solve such problems. That is, the object of the present invention is to have excellent startability, power generation output and thermal efficiency, and transient response, and even when steam injection is not performed, there is little decrease in gas flow rate, pressure ratio, rotational speed, and high power generation output and thermal efficiency. It is an object of the present invention to provide a steam injection reheat gas turbine power generator that can maintain the above.
【０００８】[0008]
【課題を解決するための手段】本発明によれば、吸気を
圧縮する圧縮機（１２）と、圧縮した空気で燃料を燃焼
させる第１燃焼器（１３）と、第１燃焼器の燃焼ガスで
駆動され前記圧縮機を駆動する圧縮機用タービン（１
４）とを有する第１ガスタービン装置（２０）と、前記
圧縮機用タービンの排ガスで燃料を燃焼させる第２燃焼
器（１５）と、第２燃焼器の燃焼ガスで駆動され発電機
（１８）を駆動する発電用タービン（１６）とを有する
第２ガスタービン装置（２２）と、前記第２燃焼器（１
５）に水蒸気を噴射する蒸気噴射装置（２４）とを備
え、前記発電用タービンの回転速度を一定速度に保持
し、かつ、第２燃焼器（１５）への水蒸気の噴射量によ
り発電出力を制御することを特徴とする蒸気噴射再熱ガ
スタービン発電装置が提供される。According to the present invention, a compressor (12) for compressing intake air, a first combustor (13) for combusting fuel with compressed air, and a combustion gas for the first combustor. A turbine for a compressor (1
4), a first gas turbine device (20), a second combustor (15) for combusting fuel with the exhaust gas of the compressor turbine, and a generator (18) driven by combustion gas of the second combustor. A second gas turbine device (22) having a power generation turbine (16) for driving the second combustor (1).
5) is provided with a steam injection device (24) for injecting steam, the rotation speed of the power generation turbine is maintained at a constant speed, and the power generation output is generated by the amount of steam injected into the second combustor (15). There is provided a steam injection reheat gas turbine power generation device characterized by controlling.
【０００９】上記本発明の構成によれば、発電機（１
８）に直接連結されない第１ガスタービン装置（２０）
を備えるので、上述した２軸式ガスタービンと同様に、
（１）始動時に第１ガスタービン装置のみの駆動でよい
ため、小型の始動用モータの使用ができ、始動性が良
く、（２）負荷の要求回転速度とは関係なく第１ガスタ
ービン装置は最も効率の良い最適回転速度で運転ができ
るので、部分負荷でも効率の低下が少なく燃費が良く、
（３）第１ガスタービン装置の慣性が小さく、かつ最適
回転速度での運転が可能なため変動時の回復が早く、過
渡応答性が高い。According to the above configuration of the present invention, the generator (1
8) A first gas turbine device (20) not directly connected to
Therefore, like the two-shaft gas turbine described above,
(1) Since only the first gas turbine device needs to be driven at the time of starting, a small starting motor can be used and the startability is good, and (2) the first gas turbine device is independent of the required rotation speed of the load. Since it can be operated at the most efficient optimum rotation speed, there is little decrease in efficiency even at partial load and fuel consumption is good,
(3) Since the inertia of the first gas turbine device is small and the first gas turbine device can be operated at the optimum rotation speed, recovery at the time of fluctuation is fast and the transient response is high.
【００１０】また、第２ガスタービン装置（２２）のみ
が発電機（１８）を駆動し、蒸気噴射装置（２４）によ
り第２ガスタービン装置の第２燃焼器（１５）のみに水
蒸気が噴射されるので、発電出力は第２燃焼器（１５）
への水蒸気の噴射量により容易に制御できる。Further, only the second gas turbine device (22) drives the generator (18), and the steam injector (24) injects steam only into the second combustor (15) of the second gas turbine device. Therefore, the power generation output is the second combustor (15).
It can be easily controlled by the injection amount of water vapor to the.
【００１１】更に、発電用タービンの回転速度を一定速
度に保持するので、蒸気噴射を行なわない時でも、第２
ガスタービン装置の回転速度は維持され、圧力比を維持
でき、水蒸気分のガス流量は低下するが、出力の低下が
少なく、高い発電出力と熱効率を維持できる。Further, since the rotation speed of the turbine for power generation is maintained at a constant speed, the second speed is maintained even when steam injection is not performed.
The rotation speed of the gas turbine device can be maintained, the pressure ratio can be maintained, and the gas flow rate of the water vapor component decreases, but the decrease in output is small and high power generation output and thermal efficiency can be maintained.
【００１２】本発明の好ましい実施形態によれば、前記
発電用タービン（１６）の排ガスで水蒸気を発生させる
排熱回収ボイラ（２６）を備える。この構成により、発
電用タービン（１６）の排ガスのエネルギーを回収し、
発生する大量の余剰蒸気を有効利用して、発電出力と熱
効率を向上させることができる。According to a preferred embodiment of the present invention, there is provided an exhaust heat recovery boiler (26) for generating steam from the exhaust gas of the power generation turbine (16). With this configuration, the energy of the exhaust gas of the power generation turbine (16) is recovered,
By effectively utilizing the large amount of surplus steam that is generated, it is possible to improve power generation output and thermal efficiency.
【００１３】[0013]
【発明の実施の形態】以下、本発明の好ましい実施形態
を図面を参照して説明する。なお、各図において共通す
る部分には同一の符号を使用する。BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of the present invention will be described below with reference to the drawings. The same reference numerals are used for the common parts in each drawing.
【００１４】図１は、本発明の蒸気噴射再熱ガスタービ
ン発電装置の全体構成図である。この図に示すように、
本発明の蒸気噴射再熱ガスタービン発電装置１０は、第
１ガスタービン装置２０、第２ガスタービン装置２２、
蒸気噴射装置２４及び排熱回収ボイラ２６を備える。FIG. 1 is an overall configuration diagram of a steam injection reheat gas turbine power generator of the present invention. As shown in this figure,
The steam injection reheat gas turbine power generator 10 of the present invention includes a first gas turbine device 20, a second gas turbine device 22,
A steam injection device 24 and an exhaust heat recovery boiler 26 are provided.
【００１５】第１ガスタービン装置２０は、圧縮機１
２、第１燃焼器１３及び圧縮機用タービン１４からな
る。圧縮機１２は、吸気（外気）を圧縮する好ましくは
軸流圧縮機である。第１燃焼器１３は、圧縮機１２で圧
縮した空気で燃料を燃焼させる燃焼装置である。この第
１燃焼器１３には、燃料のみが圧縮機用タービン１４の
回転速度を制御するように流量制御して供給され、水蒸
気の噴射は行わない。圧縮機用タービン１４は、第１燃
焼器１３の燃焼ガスで駆動され、圧縮機１２と機械的に
連結されこれを回転駆動する。またこの圧縮機用タービ
ン１４には後述する発電機は連結されていない。上述し
た構成により、第１ガスタービン装置２０を単独に、始
動、運転し、その回転速度を最適速度に常時維持するこ
とができる。The first gas turbine device 20 includes a compressor 1
2, the first combustor 13 and the compressor turbine 14. The compressor 12 is preferably an axial flow compressor that compresses intake air (outside air). The first combustor 13 is a combustion device that burns fuel with the air compressed by the compressor 12. Only fuel is supplied to the first combustor 13 with its flow rate controlled so as to control the rotational speed of the compressor turbine 14, and no steam is injected. The compressor turbine 14 is driven by the combustion gas of the first combustor 13, is mechanically connected to the compressor 12, and rotationally drives this. Further, a generator described later is not connected to the compressor turbine 14. With the configuration described above, the first gas turbine device 20 can be independently started and operated, and the rotation speed thereof can be constantly maintained at the optimum speed.
【００１６】第２ガスタービン装置２２は、第２燃焼器
１５及び発電用タービン１６からなる。第２燃焼器１５
は、圧縮機用タービン１４の排ガスで燃料を燃焼させる
燃焼装置である。この第２燃焼器１５には、燃料と水蒸
気が発電用タービン１６の回転速度を制御するように流
量制御して供給される。発電用タービン１６は、第２燃
焼器１５の燃焼ガスで駆動され、減速機１７を介して発
電機１８を駆動する。発電用タービン１６の回転速度
は、図示しない制御装置により、発電機１８に適した一
定速度に保持される。上述した構成により、第２ガスタ
ービン装置２２を単独運転し、その回転速度を燃料と水
蒸気により最適速度に常時維持することができる。The second gas turbine device 22 comprises a second combustor 15 and a power generation turbine 16. Second combustor 15
Is a combustion device that burns fuel with exhaust gas from the compressor turbine 14. Fuel and water vapor are supplied to the second combustor 15 at a flow rate controlled so as to control the rotation speed of the power generation turbine 16. The power generation turbine 16 is driven by the combustion gas of the second combustor 15, and drives the power generator 18 via the speed reducer 17. The rotation speed of the power generation turbine 16 is maintained at a constant speed suitable for the power generator 18 by a control device (not shown). With the configuration described above, the second gas turbine device 22 can be operated independently, and its rotation speed can be constantly maintained at the optimum speed by the fuel and the steam.
【００１７】蒸気噴射装置２４は、第２燃焼器１５に水
蒸気を噴射し、その噴射量により発電出力を制御する。
この水蒸気は、発電用タービン１６の排ガスで水蒸気を
発生させる排熱回収ボイラ２６から供給される。The steam injection device 24 injects steam into the second combustor 15 and controls the power generation output by the injection amount.
This steam is supplied from an exhaust heat recovery boiler 26 that generates steam from the exhaust gas of the power generation turbine 16.
【００１８】図２は、１軸式と２軸式ガスタービンの特
性比較図である。この図において、横軸は発生蒸気量に
対する外部への送気蒸気量の比率であり、０は発生蒸気
量全量をガスタービンの燃焼器に噴射した場合、１は逆
に噴射をしない場合である。また縦軸は、全量噴射時を
基準（１）とする空気流量、圧力比、回転数（回転速
度）、出力の比率である。FIG. 2 is a characteristic comparison diagram of a single-shaft type and a double-shaft type gas turbine. In this figure, the horizontal axis is the ratio of the amount of steam to be sent to the outside with respect to the amount of generated steam, 0 is the case where the entire amount of generated steam is injected into the combustor of the gas turbine, and 1 is the case where it is not injected conversely. . The vertical axis represents the ratio of the air flow rate, the pressure ratio, the rotation speed (rotation speed), and the output with reference to the time of full injection (1).
【００１９】図２において、Ａは、従来の１軸式ガスタ
ービンの空気流量、圧力比、回転数（回転速度）であ
り、Ｂはその出力である。この従来の１軸式ガスタービ
ンは本発明の第２ガスタービン装置２２に相当する。ま
た、Ｃは従来の２軸式ガスタービンの空気流量及び回転
数（回転速度）であり、Ｄはその圧力比、Ｅはその出力
である。In FIG. 2, A is the air flow rate, pressure ratio, and rotation speed (rotation speed) of the conventional single-shaft gas turbine, and B is its output. This conventional single-shaft gas turbine corresponds to the second gas turbine device 22 of the present invention. Further, C is the air flow rate and the rotation speed (rotation speed) of the conventional two-shaft gas turbine, D is the pressure ratio thereof, and E is the output thereof.
【００２０】この図から、１軸式ガスタービン及び本発
明の第２ガスタービン装置２２では、蒸気噴射量を全量
から０に変化させても、空気流量、圧力比、回転数（回
転速度）は低下せず、出力が約３８％低下するにすぎな
い。これに対して、従来の２軸式ガスタービンでは、蒸
気噴射量を全量から０に変化させると、空気流量及び回
転数（回転速度）は約４２％低下し、圧力比は約５０
％、出力は約７０％低下してしまうことがわかる。From this figure, in the single-shaft gas turbine and the second gas turbine device 22 of the present invention, the air flow rate, the pressure ratio, and the rotation speed (rotation speed) can be changed even if the steam injection amount is changed from the total amount to zero. There is no reduction, only about 38% reduction in output. On the other hand, in the conventional two-shaft gas turbine, when the steam injection amount is changed from the total amount to 0, the air flow rate and the rotation speed (rotation speed) are reduced by about 42%, and the pressure ratio is about 50.
%, The output decreases by about 70%.
【００２１】上述したように、本発明の構成によれば、
発電機１８に直接連結されない第１ガスタービン装置２
０を備えるので、従来の２軸式ガスタービンと同様に、
（１）始動時に第１ガスタービン装置のみの駆動でよい
ため、小型の始動用モータの使用ができ、始動性が良
く、（２）負荷の要求回転速度とは関係なく第１ガスタ
ービン装置は最も効率の良い最適回転速度で運転ができ
るので、部分負荷でも効率の低下が少なく燃費が良く、
（３）第１ガスタービン装置の慣性が小さく、かつ最適
回転速度での運転が可能なため変動時の回復が早く、過
渡応答性が高い。As described above, according to the configuration of the present invention,
First gas turbine device 2 that is not directly connected to the generator 18
Since it has 0, like the conventional two-shaft gas turbine,
(1) Since only the first gas turbine device needs to be driven at the time of starting, a small starting motor can be used and the startability is good, and (2) the first gas turbine device is independent of the required rotation speed of the load. Since it can be operated at the most efficient optimum rotation speed, there is little decrease in efficiency even at partial load and fuel consumption is good,
(3) Since the inertia of the first gas turbine device is small and the first gas turbine device can be operated at the optimum rotation speed, recovery at the time of fluctuation is fast and the transient response is high.
【００２２】また、第２ガスタービン装置２２のみが発
電機１８を駆動し、蒸気噴射装置２４により第２ガスタ
ービン装置の第２燃焼器１５のみに水蒸気が噴射される
ので、発電出力は第２燃焼器１５への水蒸気の噴射量に
より容易に制御できる。Further, since only the second gas turbine device 22 drives the generator 18, and the steam is injected by the steam injection device 24 only into the second combustor 15 of the second gas turbine device, the power generation output is the second. It can be easily controlled by the injection amount of water vapor to the combustor 15.
【００２３】更に、発電用タービンの回転速度を一定速
度に保持するので、蒸気噴射を行なわない時でも、第２
ガスタービン装置の回転速度は維持され、圧力比を維持
でき、水蒸気分のガス流量は低下するが、出力の低下が
少なく、高い発電出力と熱効率を維持できる。Further, since the rotating speed of the power generation turbine is maintained at a constant speed, the second speed is maintained even when steam injection is not performed.
The rotation speed of the gas turbine device can be maintained, the pressure ratio can be maintained, and the gas flow rate of the water vapor component decreases, but the decrease in output is small and high power generation output and thermal efficiency can be maintained.
【００２４】また、発電用タービン１６の排ガスで水蒸
気を発生させる排熱回収ボイラ２６を備える構成によ
り、発電用タービン１６の排ガスのエネルギーを回収
し、発生する大量の余剰蒸気を有効利用して、発電出力
と熱効率を向上させることができる。Further, the exhaust heat recovery boiler 26 for generating water vapor from the exhaust gas of the power generation turbine 16 is used to recover the energy of the exhaust gas of the power generation turbine 16 and effectively utilize the large amount of surplus steam generated. Power generation output and thermal efficiency can be improved.
【００２５】なお、本発明は上述した実施形態に限定さ
れず、本発明の要旨を逸脱しない範囲で種々変更できる
ことは勿論である。It should be noted that the present invention is not limited to the above-described embodiment, and it goes without saying that various changes can be made without departing from the gist of the present invention.
【００２６】[0026]
【発明の効果】上述したように、本発明によれば、第２
ガスタービン装置２２の第２燃焼器１５に蒸気噴射を行
うことにより、発電用タービン１６は負荷（発電機１
８）と直結しているので、第２燃焼器１５に蒸気噴射を
行わない場合でも出力タービンの回転数は一定のままと
なり、全体の効率低下を抑え、高い熱効率を維持でき
る。また、第１ガスタービン装置２０の第１燃焼器１３
には蒸気噴射を行わないので、負荷の要求回転数とは関
係なく最も効率の良い最適回転数で運転が可能なため、
高い熱効率を維持できる。As described above, according to the present invention, the second
By performing steam injection to the second combustor 15 of the gas turbine device 22, the power generation turbine 16 is loaded (power generator 1
Since it is directly connected to 8), the rotational speed of the output turbine remains constant even when the steam is not injected into the second combustor 15, and it is possible to suppress a decrease in overall efficiency and maintain high thermal efficiency. In addition, the first combustor 13 of the first gas turbine device 20.
Since steam injection is not performed on the engine, it is possible to operate at the most efficient optimum rotation speed regardless of the required rotation speed of the load.
High thermal efficiency can be maintained.
【００２７】従って、本発明の蒸気噴射再熱ガスタービ
ン発電装置は、始動性、発電出力と熱効率、及び過渡応
答性に優れ、かつ蒸気噴射を行なわない時でも、ガス流
量、圧力比、回転速度の低下が少なく、高い発電出力と
熱効率を維持できる、等の優れた効果を有する。Therefore, the steam injection reheat gas turbine power generator of the present invention is excellent in startability, power generation output and thermal efficiency, and transient responsiveness, and even when steam injection is not performed, gas flow rate, pressure ratio, rotation speed. It has an excellent effect such as a decrease in power consumption and a high power generation output and thermal efficiency can be maintained.
【図１】本発明の蒸気噴射再熱ガスタービン発電装置の
全体構成図である。FIG. 1 is an overall configuration diagram of a steam injection reheat gas turbine power generator of the present invention.
【図２】１軸式と２軸式ガスタービンの特性比較図であ
る。FIG. 2 is a characteristic comparison diagram of a single-shaft type and a double-shaft type gas turbine.
【図３】従来の蒸気噴射ガスタービン発電装置（１軸式
ガスタービン）の全体構成図である。FIG. 3 is an overall configuration diagram of a conventional steam injection gas turbine power generator (single-shaft gas turbine).
【図４】従来の蒸気噴射ガスタービン発電装置（２軸式
ガスタービン）の全体構成図である。FIG. 4 is an overall configuration diagram of a conventional steam injection gas turbine power generator (two-shaft gas turbine).
１ 発電機、２ 圧縮機、３ 燃焼器、４ タービン、
４ａ 高圧タービン、４ｂ 低圧タービン、５ 減速
機、６ 排熱回収ボイラ、１０ 蒸気噴射再熱ガスター
ビン発電装置、１２ 圧縮機、１３ 第１燃焼器、１４
圧縮機用タービン、１５ 第２燃焼器、１６ 発電用
タービン、１７ 減速機、１８ 発電機、２０ 第１ガ
スタービン装置、２２ 第２ガスタービン装置、２４
蒸気噴射装置、２６ 排熱回収ボイラ1 generator, 2 compressor, 3 combustor, 4 turbine,
4a high-pressure turbine, 4b low-pressure turbine, 5 speed reducer, 6 exhaust heat recovery boiler, 10 steam injection reheat gas turbine power generator, 12 compressor, 13 first combustor, 14
Turbine for compressor, 15 2nd combustor, 16 Turbine for power generation, 17 Reducer, 18 Generator, 20 1st gas turbine apparatus, 22 2nd gas turbine apparatus, 24
Steam injection device, 26 Exhaust heat recovery boiler
Claims (2)
した空気で燃料を燃焼させる第１燃焼器（１３）と、第
１燃焼器の燃焼ガスで駆動され前記圧縮機を駆動する圧
縮機用タービン（１４）とを有する第１ガスタービン装
置（２０）と、 前記圧縮機用タービンの排ガスで燃料を燃焼させる第２
燃焼器（１５）と、第２燃焼器の燃焼ガスで駆動され発
電機（１８）を駆動する発電用タービン（１６）とを有
する第２ガスタービン装置（２２）と、 前記第２燃焼器（１５）に水蒸気を噴射する蒸気噴射装
置（２４）とを備え、 前記発電用タービンの回転速度を一定速度に保持し、か
つ、第２燃焼器（１５）への水蒸気の噴射量により発電
出力を制御する、ことを特徴とする蒸気噴射再熱ガスタ
ービン発電装置。1. A compressor (12) for compressing intake air, a first combustor (13) for combusting fuel with compressed air, and a compression driven by combustion gas of the first combustor to drive the compressor. A first gas turbine device (20) having an engine turbine (14); and a second gas turbine device (20) for combusting fuel with exhaust gas of the compressor turbine.
A second gas turbine device (22) having a combustor (15) and a power generation turbine (16) driven by combustion gas of the second combustor to drive a generator (18); and the second combustor ( 15) is provided with a steam injection device (24) for injecting steam, the rotational speed of the turbine for power generation is maintained at a constant speed, and the power generation output is generated by the amount of steam injected into the second combustor (15). A steam injection reheat gas turbine power generation device characterized by controlling.
水蒸気を発生させる排熱回収ボイラ（２６）を備える、
ことを特徴とする請求項１に記載の蒸気噴射再熱ガスタ
ービン発電装置。2. An exhaust heat recovery boiler (26) for generating steam in the exhaust gas of the power generation turbine (16),
The steam-injection reheat gas turbine power generator according to claim 1, characterized in that.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002075494A JP2003269188A (en) | 2002-03-19 | 2002-03-19 | Steam injection reheat gas turbine generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002075494A JP2003269188A (en) | 2002-03-19 | 2002-03-19 | Steam injection reheat gas turbine generator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003269188A true JP2003269188A (en) | 2003-09-25 |
Family
ID=29204553
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002075494A Pending JP2003269188A (en) | 2002-03-19 | 2002-03-19 | Steam injection reheat gas turbine generator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003269188A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009031747A1 (en) * | 2007-09-06 | 2009-03-12 | Korea Institute Of Machinery And Materials | Power plant having pure oxygen combustor |
| JP2009531643A (en) * | 2006-03-31 | 2009-09-03 | アルストム テクノロジー リミテッド | Fuel lance used in gas turbine equipment and method for operating the fuel lance |
| JP2010511123A (en) * | 2006-12-01 | 2010-04-08 | アルストム テクノロジー リミテッド | How to operate a gas turbine |
| JP2013015146A (en) * | 2008-05-15 | 2013-01-24 | Hitachi Ltd | Two-shaft gas turbine |
| CN107503810A (en) * | 2017-07-20 | 2017-12-22 | 上海发电设备成套设计研究院有限责任公司 | A kind of near-zero release power circulation system |
| CN110770421A (en) * | 2017-04-14 | 2020-02-07 | 安内克萨能源公司 | Cogeneration system and method of operation |
| CN112334636A (en) * | 2018-06-29 | 2021-02-05 | 三菱动力株式会社 | Composite power generation facility and method for operating same |
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2002
- 2002-03-19 JP JP2002075494A patent/JP2003269188A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009531643A (en) * | 2006-03-31 | 2009-09-03 | アルストム テクノロジー リミテッド | Fuel lance used in gas turbine equipment and method for operating the fuel lance |
| JP2010511123A (en) * | 2006-12-01 | 2010-04-08 | アルストム テクノロジー リミテッド | How to operate a gas turbine |
| WO2009031747A1 (en) * | 2007-09-06 | 2009-03-12 | Korea Institute Of Machinery And Materials | Power plant having pure oxygen combustor |
| JP2013015146A (en) * | 2008-05-15 | 2013-01-24 | Hitachi Ltd | Two-shaft gas turbine |
| CN110770421A (en) * | 2017-04-14 | 2020-02-07 | 安内克萨能源公司 | Cogeneration system and method of operation |
| CN110770421B (en) * | 2017-04-14 | 2022-02-18 | 安内克萨能源公司 | Cogeneration system and method of operation |
| CN107503810A (en) * | 2017-07-20 | 2017-12-22 | 上海发电设备成套设计研究院有限责任公司 | A kind of near-zero release power circulation system |
| CN107503810B (en) * | 2017-07-20 | 2019-10-29 | 上海发电设备成套设计研究院有限责任公司 | A kind of near-zero release power circulation system |
| CN112334636A (en) * | 2018-06-29 | 2021-02-05 | 三菱动力株式会社 | Composite power generation facility and method for operating same |
| CN112334636B (en) * | 2018-06-29 | 2022-10-28 | 三菱重工业株式会社 | Composite power generation facility and method for operating same |
| WO2022105213A1 (en) * | 2020-11-18 | 2022-05-27 | 至玥腾风科技集团有限公司 | Multi-rotor micro gas turbine, and starting method therefor |
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