JP2999119B2 - Gas turbine exhaust cooling system for a combined plant - Google Patents
Gas turbine exhaust cooling system for a combined plantInfo
- Publication number
- JP2999119B2 JP2999119B2 JP6102598A JP10259894A JP2999119B2 JP 2999119 B2 JP2999119 B2 JP 2999119B2 JP 6102598 A JP6102598 A JP 6102598A JP 10259894 A JP10259894 A JP 10259894A JP 2999119 B2 JP2999119 B2 JP 2999119B2
- Authority
- JP
- Japan
- Prior art keywords
- gas turbine
- turbine
- exhaust gas
- steam
- pressure
- 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 - Fee Related
Links
Classifications
-
- 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]
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Description
【0001】[0001]
【産業上の利用分野】本発明は、ガスタービンの排気を
ボイラ火炉に導いて、同排気中の残存酸素により燃料を
燃焼させ、その燃焼熱で発生した蒸気により蒸気タービ
ンを駆動する、ガスタービン・蒸気タービン複合プラン
トに適用される、ガスタービン排ガス冷却装置および蒸
気タービン・ボイラの復水・給水系統に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine in which exhaust gas from a gas turbine is guided to a boiler furnace, fuel is burned by residual oxygen in the exhaust gas, and a steam turbine is driven by steam generated by the combustion heat. The present invention relates to a gas turbine exhaust gas cooling device and a condensate / water supply system for a steam turbine / boiler applied to a steam turbine combined plant.
【0002】[0002]
【従来の技術】図3は従来の複合プラントの一例を示す
系統図である。図中 (1)はボイラ, (2)はガスタービ
ン, (3)は復水器, (4)は脱気器, (5)は煙突, (6),
(7)はボイラ排ガス冷却装置, (8)はガスタービン排ガ
ス冷却装置, (9)は低圧給水加熱器,(10)は高圧給水加
熱器をそれぞれ示す。このように、従来はガスタービン
排ガス冷却装置(8) が脱気器(4) の下流の高圧給水系統
に、ボイラ排ガス冷却装置(7) と直列に設置されてい
た。2. Description of the Related Art FIG. 3 is a system diagram showing an example of a conventional combined plant. In the figure, (1) is a boiler, (2) is a gas turbine, (3) is a condenser, (4) is a deaerator, (5) is a chimney, (6),
(7) is a boiler exhaust gas cooling system, (8) is a gas turbine exhaust gas cooling system, (9) is a low-pressure feedwater heater, and (10) is a high-pressure feedwater heater. As described above, conventionally, the gas turbine exhaust gas cooling device (8) is installed in series with the boiler exhaust gas cooling device (7) in the high-pressure water supply system downstream of the deaerator (4).
【0003】[0003]
【発明が解決しようとする課題】従来は、ガスタービン
排ガス冷却装置(8) が高圧給水系統にボイラ排ガス冷却
装置(7) と直列に設置されているため、これらの排ガス
から給水への熱吸収量が多い。したがってある負荷以
下、特に部分負荷においては、ボイラへの給水全量(あ
るいは高圧給水加熱器ミニマムフローを差し引いた分)
をこれら排ガス冷却装置(7),(8) へ流しても、出口給水
温度が高くなり過ぎる。そこで、出口給水温度を抑える
よう余分に流し、余剰分は当該排ガス冷却装置出口から
復水器等へ再循環させる必要を生ずる。ところが、上記
のように給水の熱吸収量が多いので、その再循環を開始
すべき負荷(その負荷以下では再循環が必要)が高目と
なる。高圧給水系の圧力は亜臨界圧でも200atg程度、超
臨界圧では300atg以上となるから、これを常時フラッシ
ュさせながら制御弁で逃がすことは通常運用としては成
立しない。したがってその再循環開始負荷が事実上の最
低負荷となり、ガスタービン複合運転時の運用域が狭ま
ることになる。Conventionally, since a gas turbine exhaust gas cooling device (8) is installed in series with a boiler exhaust gas cooling device (7) in a high-pressure water supply system, heat absorption from these exhaust gases to the feedwater is performed. Large amount. Therefore, below a certain load, especially under partial load, the total amount of water supplied to the boiler (or the amount obtained by subtracting the minimum flow of the high pressure feed water heater)
Even though the exhaust gas flows into these exhaust gas cooling devices (7) and (8), the outlet feedwater temperature becomes too high. Therefore, it is necessary to flow extra water so as to suppress the outlet water supply temperature, and to recycle the surplus from the exhaust gas cooling device outlet to a condenser or the like. However, since the heat absorption amount of the feedwater is large as described above, the load at which the recirculation is to be started (recycling is required below the load) becomes high. Since the pressure of the high-pressure water supply system is about 200 atg even at the subcritical pressure and 300 atg or more at the supercritical pressure, it is not possible to release the control valve while constantly flushing it as a normal operation. Therefore, the recirculation starting load becomes the practical minimum load, and the operating range in the combined operation of the gas turbine is narrowed.
【0004】[0004]
【課題を解決するための手段】本発明者は、前記従来の
課題を解決するために、ガスタービンの排気をボイラ火
炉に導いて、同排気中の残存酸素により燃料を燃焼さ
せ、その燃焼熱で発生した蒸気により蒸気タービンを駆
動する蒸気タービン・ガスタービン複合プラントにおい
て、蒸気タービンとガスタービンの通常複合運転時に、
上記蒸気タービンの復水器から脱気器に至る間の復水に
よって上記ガスタービンの排気を冷却することを特徴と
する複合プラントのガスタービン排気冷却装置を提案す
るものである。In order to solve the above-mentioned conventional problems, the present inventor guides an exhaust gas of a gas turbine to a boiler furnace, burns fuel by residual oxygen in the exhaust gas, and generates a heat of combustion. in in generated steam turbine and gas turbine combined plant for driving a steam turbine by the steam, the normal composite operation of the steam turbine and gas turbine,
The present invention proposes a gas turbine exhaust cooling system for a combined plant, wherein exhaust gas of the gas turbine is cooled by condensing water from a condenser to a deaerator of the steam turbine.
【0005】[0005]
【作用】本発明においては、蒸気タービンとガスタービ
ンの通常複合運転時に、ガスタービンの排気を、脱気器
の下流の高圧給水によってでなく、蒸気タービンの復水
器から脱気器に至る間の復水によって冷却するので、高
圧給水がガスタービンの排気から吸収する熱量が軽減さ
れ、これにより高圧系において再循環が必要となる負荷
すなわちプラントの最低負荷を大幅に低下させることが
できる。In the present invention, a steam turbine and a gas turbine
During normal combined operation of the gas turbine , the gas turbine exhaust is cooled not by the high-pressure feedwater downstream of the deaerator but by the condensate from the steam turbine condenser to the deaerator, so that the high-pressure feedwater The amount of heat absorbed from the exhaust of the turbine is reduced, which can significantly reduce the load that requires recirculation in the high pressure system, i.e. the minimum load on the plant.
【0006】[0006]
【実施例】図1は本発明の第1の実施例を示す系統図で
ある。本実施例においては、ガスタービン排ガス冷却装
置(8) が脱気器(7) の下流の高圧給水系統でなく、その
上流の低圧復水系統に、ボイラ排ガス冷却装置(6) と直
列且つその上流側に設置される。このようにガスタービ
ン排ガス冷却装置(8) を低圧復水系統に設置することに
よって、高圧給水系統への排ガスからの熱吸収量を抑
え、前記再循環開始負荷すなわちプラント最低負荷を大
幅に低減して、運用性を向上させることができる。FIG. 1 is a system diagram showing a first embodiment of the present invention. In this embodiment, the gas turbine exhaust gas cooling device (8) is not connected to the high-pressure water supply system downstream of the deaerator (7), but to a low-pressure condensate system upstream of the deaerator (7) in series with the boiler exhaust gas cooling device (6). Installed upstream. By installing the gas turbine exhaust gas cooling device (8) in the low-pressure condensing system in this way, the amount of heat absorbed from the exhaust gas into the high-pressure water supply system is suppressed, and the recirculation starting load, that is, the plant minimum load is significantly reduced. Thus, operability can be improved.
【0007】図2は本発明の第2の実施例を示す系統図
である。この実施例においても、ガスタービン排ガス冷
却装置(8) は低圧復水系統にボイラ排ガス冷却装置(6)
と直列ただしその下流側に設置される。作用・効果は前
記第1の実施例と同様である。FIG. 2 is a system diagram showing a second embodiment of the present invention. Also in this embodiment, the gas turbine exhaust gas cooling device (8) is connected to the low-pressure condensing system with the boiler exhaust gas cooling device (6).
It is installed in series but downstream of it. The operation and effect are the same as those of the first embodiment.
【0008】[0008]
【発明の効果】本発明においては、ガスタービンの排ガ
スを、脱気器の下流のボイラ給水ではなく、その上流の
低圧復水によって冷却することにより、高圧給水系統へ
の排ガスからの熱吸収量を大幅に低減できるため、高圧
系の再循環開始負荷ひいては最低負荷を30〜40%以
上も大幅に低減することができる。According to the present invention, the amount of heat absorbed from the exhaust gas into the high-pressure water supply system is cooled by cooling the exhaust gas of the gas turbine not by the boiler feedwater downstream of the deaerator but by the low-pressure condensate upstream of the boiler. Can be greatly reduced, so that the recirculation start load of the high-pressure system and, consequently, the minimum load can be significantly reduced by 30 to 40% or more.
【図1】図1は本発明の第1の実施例を示す系統図であ
る。FIG. 1 is a system diagram showing a first embodiment of the present invention.
【図2】図2は本発明の第2の実施例を示す系統図であ
る。FIG. 2 is a system diagram showing a second embodiment of the present invention.
【図3】図3は従来の複合プラントの一例を示す系統図
である。FIG. 3 is a system diagram showing an example of a conventional combined plant.
(1) ボイラ (2) ガスタービン (3) 復水器 (4) 脱気器 (5) 煙突 (6),(7) ボイラ排ガス冷却装置 (8) ガスタービン排ガス冷却装置 (9) 低圧給水加熱器 (10) 高圧給水加熱器 (1) Boiler (2) Gas turbine (3) Condenser (4) Deaerator (5) Chimney (6), (7) Boiler exhaust gas cooling device (8) Gas turbine exhaust gas cooling device (9) Low pressure feed water heating (10) High pressure feed water heater
───────────────────────────────────────────────────── 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 F01K 11/00 F02C 6/18 F22B 33/18 ──────────────────────────────────────────────────の Continued on the front page (58) Field surveyed (Int. Cl. 7 , DB name) F01K 23/10 F01K 11/00 F02C 6/18 F22B 33/18
Claims (1)
て、同排気中の残存酸素により燃料を燃焼させ、その燃
焼熱で発生した蒸気により蒸気タービンを駆動する蒸気
タービン・ガスタービン複合プラントにおいて、蒸気タ
ービンとガスタービンの通常複合運転時に、上記蒸気タ
ービンの復水器から脱気器に至る間の復水によって上記
ガスタービンの排気を冷却することを特徴とする複合プ
ラントのガスタービン排気冷却装置。In a combined steam turbine and gas turbine plant, an exhaust gas of a gas turbine is guided to a boiler furnace, fuel is burned by residual oxygen in the exhaust gas, and a steam turbine is driven by steam generated by the combustion heat. Steam tank
A gas turbine exhaust cooling system for a combined plant, wherein exhaust gas of the gas turbine is cooled by condensing water from a condenser to a deaerator of the steam turbine during normal combined operation of the turbine and the gas turbine .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6102598A JP2999119B2 (en) | 1994-05-17 | 1994-05-17 | Gas turbine exhaust cooling system for a combined plant |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6102598A JP2999119B2 (en) | 1994-05-17 | 1994-05-17 | Gas turbine exhaust cooling system for a combined plant |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH07310507A JPH07310507A (en) | 1995-11-28 |
JP2999119B2 true JP2999119B2 (en) | 2000-01-17 |
Family
ID=14331681
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP6102598A Expired - Fee Related JP2999119B2 (en) | 1994-05-17 | 1994-05-17 | Gas turbine exhaust cooling system for a combined plant |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2999119B2 (en) |
-
1994
- 1994-05-17 JP JP6102598A patent/JP2999119B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JPH07310507A (en) | 1995-11-28 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 19991005 |
|
LAPS | Cancellation because of no payment of annual fees |