JP4619563B2 - Ultra turbine - Google Patents
Ultra turbine Download PDFInfo
- Publication number
- JP4619563B2 JP4619563B2 JP2001091405A JP2001091405A JP4619563B2 JP 4619563 B2 JP4619563 B2 JP 4619563B2 JP 2001091405 A JP2001091405 A JP 2001091405A JP 2001091405 A JP2001091405 A JP 2001091405A JP 4619563 B2 JP4619563 B2 JP 4619563B2
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- compressor
- working gas
- combustor
- 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.)
- Expired - Fee Related
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Classifications
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Description
【0001】
【産業上の利用分野】
産業用ガスタービンは熱効率に優れているので近年、分散型などの小型、ホテルや病院などの非常用電源としての中型、大規模発電所の複合サイクルとしての大型にますます使われ始めた。本発明はこれらガスタービンの熱効率のさらなる向上手段として利用できるが、主としてマイクロタービンといわれる出力30kw程度またはそれ以下の小型ガスタービンを対象にしている。
【0002】
【従来の技術】
図1は現用のガスタービンの作動サイクルを温度とエントロピーの関係で示した。エントロピーは流体損失を表す熱力学のパラメーターである。図中の1の状態で大気を吸い込み2まで圧縮し2から3まで加熱し3から4にかけてタービンで膨張させ4の状態で大気に放出して一つのサイクルが完了する。これらの過程はすべて大気より高圧の状態で行われている。4の状態の排出ガスは600度C程度の高温なのでボイラーに再び入れ蒸気または温水にして排熱回収するコージェネレーションの普及が進んでいる。今一つの効率向上の技術としては図1の4の状態の排熱と2の状態の圧縮空気との間で熱交換し2の空気温度を高めて投入燃料の量を少なくする試みが小型ガスタービンでなされている。
【0003】
【発明が解決しようとする課題と手段】
ガスタービンの熱効率向上には、前述したように圧縮機からの高温ガスをタービン排気ガスで予熱する方式が現在、唯一絶対的なものになっているが、圧縮機出口の作動ガスはすでに高温になっており、熱交換の効率が悪い。そのため30kwの市販されている小型ガスタービンの熱効率は25%を超える事が出来ない。小型ガスタービンでも3から5気圧程度の燃料ポンプを必要とし取り扱いが面倒で普及の妨げになっている。排熱回収にボイラー設備を必要とする。
本発明はこれらの欠点を解決するものである。まず請求項1の発明の概念図を図2に示す。熱交換のために設けた外気吸入の低温側熱交換器部4で予熱された新鮮な空気は大気圧より多少低い圧力で燃焼器1に流入するので、特別の燃料ポンプを必要とせず、家庭用のガス配管等から直接供給できる利点がある。熱力学の計算を出力30kwの小型ガスタービンを想定して行ってみた。圧力比3、タービン2と圧縮機3の断熱効率を85%、タービン入り口温度900度C、出口温度600度C、熱交換温度効率を80%とすると問題の熱効率は35%になる。このような比較的高い熱効率が得られたのは、大気温度から予熱しているためである。本発明は通常のガスタービンとは逆の順序で燃焼器1、タービンお2よび圧縮機3を配置しているから大気温度の空気を加熱出来るので、従来の方式より熱効率が優る。
請求項1は簡潔なシステムであるが、熱効率の点などまだ改良の余地が残されているので、請求項2の発明で新たな機能を付加し、その概念図を図3に示す。タービン2出口から圧縮機3出口までの作動ガスの冷却を空気と流体の2段階で行う。すなわちタービン出口直後のガスがまだ比較的高温の間は新鮮な空気で行い、この予熱空気を作動ガスとして利用する。たとえばタービン出口600度Cの作動ガスが冷却されて200度Cになるまで外部から取り入れた空気で行い、その後は流体を用いて圧縮機入り口の作動ガスの温度を20度C近くに冷却し、さらに圧縮機3を熱交換器5で中間冷却する。先に挙げた30kwの小型ガスタービンのとき、このようにすると圧縮に要する仕事が軽減され熱効率45%に出来る。流体に水を用いれば温水がえられ、ボイラーが不要になる。流体に天然ガスを用いれば気化プラントになる。
請求項3は作動ガスの冷却を流体のみで行うもので発明の概念を図4に示す。このときは作動ガスは予熱されないので効率は悪く、ただ熱交換器5で中間冷却されているので30%程度の熱効率は保つ。気化ガスまたは温水が多量に必要なときにのみつかう。
【0004】
【発明の効果】
ガスタービンはエネルギー問題や炭酸ガス排出削減問題と深く関連するエネルギー変換のための有望な熱機関である。熱効率の向上は人類にとってますます重要度を増してくる。本発明により圧縮空気を排気ガスで加熱していた従来の方式の概念を覆し、小型のガスタービンでは今まで到達できなかった高い数値の熱効率45%を達成できる。その効果は、従来の方式では圧縮機を中間冷却しても、燃焼前の空気温度が下がり効率向上につながらない。しかし本発明では、燃焼器がタービン前方にあるので、圧縮機を中間冷却すれば確実に熱効率が向上する。さらに本発明の最大の効果は、当該タービンを出た作動ガスを軸出力増加のため冷却する外気を予熱空気として燃料節約に都合2回活用できることにある。そのため小型ガスタービンでは不可能とされてきた高い熱効率45%がでる。排ガスで温水または蒸気をえるためにボイラーを必要としない。燃焼器への燃料投入に特別の装置を必要としない。燃焼が大気圧に近い状態で行え安全である。温水や天然ガスの気化が発電の副産物として得られる。
【図面の簡単な説明】
【図1】従来のガスタービンのサイクル線図
【図2】請求項1の概本発明の概念を示す断面図
【図3】請求項2の概念図
【図4】請求項3の概念図
【符号の説明】
B 燃焼器
C 圧縮機
T タービン
G 発電機[0001]
[Industrial application fields]
Industrial gas turbines, which have excellent thermal efficiency, have begun to be increasingly used in recent years, as small as a distributed type, as a medium size as an emergency power source for hotels and hospitals, and as a large size as a combined cycle in a large-scale power plant. The present invention can be used as a means for further improving the thermal efficiency of these gas turbines, but is mainly intended for small gas turbines having an output of about 30 kW or less, which are referred to as microturbines.
[0002]
[Prior art]
FIG. 1 shows the operating cycle of a current gas turbine in relation to temperature and entropy. Entropy is a thermodynamic parameter that represents fluid loss. In the state of 1 in the figure, the atmosphere is sucked in, compressed to 2, heated from 2 to 3, expanded by a turbine from 3 to 4, and released into the atmosphere in the state of 4 to complete one cycle. All of these processes are performed at a higher pressure than the atmosphere. Since the exhaust gas in the state No. 4 has a high temperature of about 600 ° C., cogeneration that re-enters the boiler and recovers the exhaust heat by using steam or hot water is spreading. As another technology for improving efficiency, an attempt to reduce the amount of input fuel by exchanging heat between the exhaust heat in the
[0003]
[Problems and Means to be Solved by the Invention]
In order to improve the thermal efficiency of gas turbines, the method of preheating the high-temperature gas from the compressor with the turbine exhaust gas as described above is currently the only absolute method, but the working gas at the outlet of the compressor is already at a high temperature. The heat exchange efficiency is poor. Therefore, the thermal efficiency of a 30 kW commercially available small gas turbine cannot exceed 25%. Even small gas turbines require a fuel pump of about 3 to 5 atm, which is cumbersome and hinders its spread. Boiler equipment is required for exhaust heat recovery.
The present invention solves these drawbacks. First, a conceptual diagram of the invention of
Although
[0004]
【The invention's effect】
Gas turbines are promising heat engines for energy conversion that are closely related to energy problems and carbon dioxide emission reduction problems. Increasing thermal efficiency is becoming increasingly important for humanity. According to the present invention, the concept of the conventional system in which compressed air is heated with exhaust gas is reversed, and a high thermal efficiency of 45%, which has not been achieved with a small gas turbine, can be achieved. The effect is that, even if the compressor is intercooled in the conventional system, the air temperature before combustion is lowered and the efficiency is not improved. However, in the present invention, since the combustor is located in front of the turbine, if the compressor is intercooled, the thermal efficiency is reliably improved. Furthermore, the greatest effect of the present invention is that the outside air that cools the working gas exiting the turbine for increasing the shaft output can be used twice as a preheated air for fuel saving. Therefore, high thermal efficiency of 45%, which has been impossible with a small gas turbine, is achieved. No boiler is required to get hot water or steam from the exhaust gas. No special equipment is required for fuel input to the combustor. It is safe to perform combustion in a state close to atmospheric pressure. Evaporation of hot water and natural gas is obtained as a by-product of power generation.
[Brief description of the drawings]
FIG. 1 is a cycle diagram of a conventional gas turbine. FIG. 2 is a cross-sectional view showing the concept of the present invention in
B Combustor C Compressor T Turbine G Generator
Claims (3)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001091405A JP4619563B2 (en) | 2001-02-20 | 2001-02-20 | Ultra turbine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001091405A JP4619563B2 (en) | 2001-02-20 | 2001-02-20 | Ultra turbine |
Publications (2)
Publication Number | Publication Date |
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JP2002242700A JP2002242700A (en) | 2002-08-28 |
JP4619563B2 true JP4619563B2 (en) | 2011-01-26 |
Family
ID=18946026
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Application Number | Title | Priority Date | Filing Date |
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JP2001091405A Expired - Fee Related JP4619563B2 (en) | 2001-02-20 | 2001-02-20 | Ultra turbine |
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Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3734759B2 (en) * | 2002-03-07 | 2006-01-11 | 川崎重工業株式会社 | Normal pressure gasification power generation device and exhaust circulation type normal pressure power generation device |
JP4179496B2 (en) * | 2002-10-08 | 2008-11-12 | 川崎重工業株式会社 | Atmospheric pressure combustion turbine system |
JP4002976B2 (en) * | 2003-06-10 | 2007-11-07 | 独立行政法人産業技術総合研究所 | Reheat gas turbine equipment expanding to negative pressure |
JP4833793B2 (en) * | 2006-10-23 | 2011-12-07 | 川崎重工業株式会社 | Lubricating device for atmospheric turbine |
JP4987427B2 (en) * | 2006-11-06 | 2012-07-25 | 川崎重工業株式会社 | Atmospheric pressure combustion turbine system with cooling structure for working gas inlet |
CN104011347A (en) * | 2011-12-22 | 2014-08-27 | 川崎重工业株式会社 | Gas turbine engine provided with heat exchanger, and method for starting gas turbine engine |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS594866A (en) * | 1982-06-29 | 1984-01-11 | 株式会社島津製作所 | Thermal energy utilizing system |
JPS59120721A (en) * | 1982-12-27 | 1984-07-12 | Osaka Gas Co Ltd | Exhaust heat collecting device |
JPH01280638A (en) * | 1988-03-31 | 1989-11-10 | Aisin Seiki Co Ltd | Gas turbine cogeneration system |
-
2001
- 2001-02-20 JP JP2001091405A patent/JP4619563B2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS594866A (en) * | 1982-06-29 | 1984-01-11 | 株式会社島津製作所 | Thermal energy utilizing system |
JPS59120721A (en) * | 1982-12-27 | 1984-07-12 | Osaka Gas Co Ltd | Exhaust heat collecting device |
JPH01280638A (en) * | 1988-03-31 | 1989-11-10 | Aisin Seiki Co Ltd | Gas turbine cogeneration system |
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Publication number | Publication date |
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JP2002242700A (en) | 2002-08-28 |
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