JP3095680B2 - Hydrogen-oxygen combustion turbine plant - Google Patents
Hydrogen-oxygen combustion turbine plantInfo
- Publication number
- JP3095680B2 JP3095680B2 JP08085098A JP8509896A JP3095680B2 JP 3095680 B2 JP3095680 B2 JP 3095680B2 JP 08085098 A JP08085098 A JP 08085098A JP 8509896 A JP8509896 A JP 8509896A JP 3095680 B2 JP3095680 B2 JP 3095680B2
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- hydrogen
- heat exchanger
- oxygen combustion
- plant
- 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
-
- 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
- F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
- F01K25/005—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the working fluid being steam, created by combustion of hydrogen with oxygen
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
【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION
【０００１】[0001]
【発明の属する技術分野】本発明は、ＮＯX やＣＯ2 を
発生しない無公害の水素酸素燃焼を利用したタービンプ
ラントに関する。The present invention relates to relates to a turbine plant using hydrogen and oxygen combustion pollution-free which does not generate NO X and CO 2.
【０００２】[0002]
【従来の技術】図３に示すサイクルが現在考えられてい
る中で高効率であり実現性の高い水素酸素燃焼タービン
プラントのサイクルの１つである。図３において、２０
０は圧縮機、２０４は燃焼器、２０５は第１タービン
で、圧縮機２００で圧縮されたガスは燃焼器２０４に供
給された水素および酸素と混合されて燃焼され、燃焼に
より発生した高温の燃焼ガス（水蒸気）は第１タービン
２０５を駆動する。2. Description of the Related Art The cycle shown in FIG. 3 is one of the cycles of a hydrogen-oxygen combustion turbine plant which is highly efficient and highly feasible among the currently considered ones. In FIG.
Reference numeral 0 denotes a compressor, 204 denotes a combustor, 205 denotes a first turbine, and the gas compressed by the compressor 200 is mixed with hydrogen and oxygen supplied to the combustor 204 and burned. The gas (steam) drives the first turbine 205.
【０００３】２０７，２０８は熱交換器で、第１タービ
ン２０５を出た燃焼ガス（水蒸気）はこの熱交換器２０
７，２０８を経て圧縮機２００へ流れる。２０９は第２
タービンで、熱交換器２０７を出た燃焼ガス（水蒸気）
の一部が導かれ第２タービン２０９を出た燃焼ガス（水
蒸気）は復水器２１１へ導かれる。[0003] Reference numerals 207 and 208 denote heat exchangers, and the combustion gas (steam) exiting the first turbine 205 is supplied to the heat exchanger 20.
It flows to the compressor 200 via 7,208. 209 is the second
Combustion gas (steam) exiting the heat exchanger 207 in the turbine
Of the combustion gas (steam) exiting the second turbine 209 is guided to the condenser 211.
【０００４】復水器２１１を出た復水は第１及び第２給
水加熱器２１７及び２１８で加熱されたのち第１ポンプ
２１２により熱交換器２０８，２０７に送られて更に加
熱されて蒸気となって第３タービン２１０に供給されて
これを駆動する。第３タービン２１０を出た排気の一部
は第１タービン２０５の冷却蒸気として用いられ、残部
の排気は燃焼器２０４へ導かれる。図中、２１５と２１
６は発電機を示している。The condensate that has exited the condenser 211 is heated by the first and second feed water heaters 217 and 218 and then sent to the heat exchangers 208 and 207 by the first pump 212 and further heated to produce steam. Then, it is supplied to the third turbine 210 to drive it. Part of the exhaust gas leaving the third turbine 210 is used as cooling steam for the first turbine 205, and the remaining exhaust gas is guided to the combustor 204. In the figure, 215 and 21
Reference numeral 6 denotes a generator.
【０００５】図４は図３に示したタービンプラントのサ
イクル図であるが、図中の数字は上記図３中の数字に対
応する。以下、その数字を使って説明すると、燃焼器２
０４における燃焼によって発生した水蒸気は、第１ター
ビン２０５を駆動して膨張し２１から２２となり、熱交
換器２０７及び２０８で給水を加熱して大気圧以上の等
圧のまま２４の状態となる。そして圧縮機２００に吸気
され圧縮機２００の仕事により２５の状態に圧縮され
て、再び燃焼器２０４に入る。FIG. 4 is a cycle diagram of the turbine plant shown in FIG. 3, and the numbers in the figure correspond to the numbers in FIG. Hereinafter, using the figures, the combustor 2
The steam generated by the combustion in 04 expands from 21 to 22 by driving the first turbine 205, and the feed water is heated by the heat exchangers 207 and 208 to be in the state of 24 at an equal pressure equal to or higher than the atmospheric pressure. Then, the air is sucked into the compressor 200, compressed by the work of the compressor 200 to a state of 25, and then enters the combustor 204 again.
【０００６】熱交換器２０７を出た２３の状態の蒸気の
一部は、第２タービン２０９を駆動して膨張し、３０の
状態の排気となって復水器２１１で復水２９となる。そ
の後復水は、給水加熱器２１７，２１８、熱交換器２０
７，２０８で加熱されて飽和蒸気２８から過熱蒸気２７
となり、第３タービン２１０を駆動し排気３１となって
再び燃焼器２０４に戻る。A part of the steam in the state 23 exiting the heat exchanger 207 is expanded by driving the second turbine 209, becomes exhausted in the state 30, and becomes condensed water 29 in the condenser 211. Thereafter, the condensate is supplied to the feedwater heaters 217 and 218 and the heat exchanger 20.
7, the superheated steam 27
And drives the third turbine 210 to become the exhaust gas 31 and returns to the combustor 204 again.
【０００７】[0007]
【発明が解決しようとする課題】図３に示す従来の水素
酸素燃焼タービンプラントの更なる高効率化のために
は、圧縮機２００の高圧力比化が必要となるが、高圧力
比化は、圧縮機２００および第１タービン２０５の段数
の増大によるコスト高、起動の課題、タービン入口翼高
さが小さくなることによる冷却翼製作の課題、圧縮機出
口温度が高くなることによる圧縮機最終段ディスク強度
に問題が生じることなど様々な問題が生ずる。In order to further increase the efficiency of the conventional hydrogen-oxygen combustion turbine plant shown in FIG. 3, it is necessary to increase the pressure ratio of the compressor 200. Cost, start-up problem due to increase in the number of stages of the compressor 200 and the first turbine 205, cooling blade manufacturing problem due to a decrease in turbine inlet blade height, compressor final stage due to a high compressor outlet temperature Various problems arise, such as a problem with the disk strength.
【０００８】そこで本発明は、圧縮機を高圧力比化せず
に高効率化すると共に製作の容易な水素、酸素燃焼ター
ビンプラントを提供することを課題としている。Accordingly, an object of the present invention is to provide a hydrogen / oxygen combustion turbine plant which is highly efficient without increasing the pressure ratio of the compressor and which is easy to manufacture.
【０００９】[0009]
【課題を解決するための手段】本発明は前記課題を解決
するため、燃焼器と直結する第１のタービンと、同第１
のタービンの排ガスの熱にて駆動する第１のタービン以
外のタービンを有する水素酸素燃焼タービンプラントに
おいて、前記第１のタービンの排ガスの一部を、同排ガ
スと第１のタービン以外のタービンの上流側との熱交換
を行う熱交換器に抽気すると共に、第１のタービンの排
ガスの残部を、同排ガスと燃焼器上流側との熱交換を行
う熱交換器に抽気するように構成した水素酸素燃焼ター
ビンプラントを提供する。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a first turbine directly connected to a combustor, and a first turbine.
The first turbine driven by the heat of the exhaust gas of the other turbine
Hydrogen-oxygen combustion turbine plant with external turbine
Here, a part of the exhaust gas of the first turbine is
Exchange between the turbine and the upstream side of the turbine other than the first turbine
While extracting air to the heat exchanger that performs
The remaining gas is exchanged heat between the exhaust gas and the upstream side of the combustor.
The present invention provides a hydrogen-oxygen combustion turbine plant configured to extract air to a heat exchanger .
【００１０】[0010]
【００１１】[0011]
【００１２】このように構成した本発明による水素酸素
燃焼タービンプラントにおいては、前記したように第１
のタービン以外のタービンの上流側と第１タービンの排
ガスの一部との間で熱交換させると共に第１タービンの
排ガスの残部と燃焼器上流側とを熱交換させることによ
り、低圧力比でＨ2 ，Ｏ2 量を減少させ高効率化させる
作用があり、また、これによりプラント全体出力を同一
とした場合には第１タービン入口流量を従来サイクルよ
りも増加させることができ、第１タービン第１段冷却翼
製作に有利となる作用がある。In the hydrogen-oxygen combustion turbine plant according to the present invention having the above-described structure, the first
By exchanging heat between the upstream side of the turbines other than the turbine and part of the exhaust gas of the first turbine and exchanging heat between the remaining part of the exhaust gas of the first turbine and the upstream side of the combustor, the H pressure is reduced at a low pressure ratio. 2 , has the effect of reducing the amount of O 2 and increasing the efficiency. In addition, when the output of the entire plant is the same, the first turbine inlet flow rate can be increased as compared with the conventional cycle. There is an operation that is advantageous for manufacturing a one-stage cooling blade.
【００１３】本発明による水素酸素燃焼タービンプラン
トにおいては、ガスタービン圧縮機の中間段、または複
数に分割された圧縮機の間に中間冷却器を設けた構成と
するのが好ましい。このように中間冷却器を設け、復水
器下流の水を噴射することにより圧縮機出口温度を低下
させ、圧縮機実現性を高める作用がある。[0013] In the hydrogen-oxygen combustion turbine plant according to the present invention, it is preferable that an intermediate cooler is provided between the gas turbine compressor intermediate stages or a plurality of divided compressors. By providing the intercooler and injecting water downstream of the condenser in this way, the compressor outlet temperature is reduced, and the effect of increasing the compressor feasibility is obtained.
【００１４】[0014]
【発明の実施の形態】以下、本発明による水素酸素燃焼
タービンプラントを図１に示した一実施形態について説
明する。図１に示した水素酸素燃焼タービンプラントで
は、圧縮機が低圧圧縮機１００と高圧圧縮機１０２に分
けられていて、その間に中間冷却器１０１が設けられて
いる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of a hydrogen-oxygen combustion turbine plant according to the present invention shown in FIG. 1 will be described below. In the hydrogen-oxygen combustion turbine plant shown in FIG. 1, the compressor is divided into a low-pressure compressor 100 and a high-pressure compressor 102, and an intercooler 101 is provided therebetween.
【００１５】１０４は燃焼器、１０５は第１タービン、
１０９は第２タービン、１１０は第３タービンである。
１１４，１１５，１１６は、それぞれ、第１タービン１
０５，第２タービン１０９、第３タービン１１０によっ
て駆動される第１，第２，第３発電機を示している。１
０３，１０６，１０７，１０８は、それぞれ、第１，第
２，第３，第４熱交換器、１１７，１１８は第１，第２
給水加熱器を示している。[0015] 104 is a combustor, 105 is a first turbine,
Reference numeral 109 denotes a second turbine, and 110 denotes a third turbine.
114, 115, and 116 are the first turbine 1 respectively.
05, the first, second and third generators driven by the second turbine 109 and the third turbine 110 are shown. 1
Reference numerals 03, 106, 107, and 108 denote first, second, third, and fourth heat exchangers, respectively, and 117 and 118 denote first and second heat exchangers, respectively.
3 shows a feedwater heater.
【００１６】１１１は復水器、１１２及び１１３は第１
及び第２ポンプを示している。高圧圧縮機１０２を出た
ガスは第１熱交換器１０３で加熱されて燃焼器１０４へ
供給され、ここに供給された水素、酸素と混合されて燃
焼され、燃焼により発生した高温の燃焼ガスは第１ター
ビン１０５へ供給され第１発電機１１４を駆動する。[0016] 111 is a condenser, 112 and 113 are first condensers.
And a second pump. The gas exiting the high-pressure compressor 102 is heated in the first heat exchanger 103 and supplied to the combustor 104, where it is mixed with the hydrogen and oxygen supplied thereto and burned. The power is supplied to the first turbine 105 and drives the first generator 114.
【００１７】第１タービン１０５の排気は２つに分けら
れ、一部は第１熱交換器１０３へ流れ、他の一部は第２
熱交換器１０６へ流れる。第１及び第２熱交換器１０３
及び１０６を出た排気は合流して第３熱交換器１０７、
第４熱交換器１０８に流れて後記するように第３タービ
ン１１０に流れる水蒸気を加熱したのち低圧圧縮機１０
０へ供給される。The exhaust gas of the first turbine 105 is divided into two parts, a part of which flows to the first heat exchanger 103 and a part of which is the second heat exchanger.
It flows to the heat exchanger 106. First and second heat exchanger 103
, And 106, are combined into a third heat exchanger 107,
After heating the steam flowing through the fourth heat exchanger 108 and flowing through the third turbine 110 as described later, the low-pressure compressor 10
0.
【００１８】また、第３熱交換器１０７を出た排気の一
部は第２タービン１０９へ流れて同第２タービン１０９
を駆動する。第２タービン１０９の排気は復水器１１１
で復水となり、その復水は第１給水加熱器１１７、第２
給水加熱器１１８で加熱されたのち、第４熱交換器１０
８、第３熱交換器１０７及び第２熱交換器１０６で更に
加熱されて第３タービン１１０へ供給されて同第３ター
ビン１１０を駆動する。A part of the exhaust gas having exited the third heat exchanger 107 flows to the second turbine 109 and the second turbine 109
Drive. The exhaust of the second turbine 109 is supplied to the condenser 111
The condensate is supplied to the first feedwater heater 117 and the second
After being heated by the feed water heater 118, the fourth heat exchanger 10
8, further heated by the third heat exchanger 107 and the second heat exchanger 106 and supplied to the third turbine 110 to drive the third turbine 110.
【００１９】第３タービン１１０の排気は、その一部が
第１タービン１０５の冷却蒸気として、残部は高圧圧縮
機１０２の出口に合流される。以上説明した図１のター
ビンプラントのサイクル図を図２に示してあり、図中の
数字は図１中の数字に対応する。A part of the exhaust gas of the third turbine 110 is combined with the cooling steam of the first turbine 105, and the remainder is joined to the outlet of the high-pressure compressor 102. The cycle diagram of the turbine plant of FIG. 1 described above is shown in FIG. 2, and the numbers in the figure correspond to the numbers in FIG.
【００２０】図２において、トッピングサイクルは８−
９−１−２−３−４−５−６−７−８で構成された閉サ
イクルを示す。またボトミングサイクルは、８−９−１
−２−３−４−１６−１７，１８−１１−１２−１３−
１４−８で構成する閉サイクルを示す。８−９−１−２
−３−４の部分ではトッピングとボトミングサイクルが
重なっている。In FIG. 2, the topping cycle is 8-
9 shows a closed cycle composed of 9-1-2-3-4-5-6-7-8. The bottoming cycle is 8-9-1.
-2-3-4-16-17, 18-11-12-13
Figure 14 shows a closed cycle consisting of 14-8. 8-9-1-2
In the section of -3-4, the topping and the bottoming cycle overlap.
【００２１】トッピングサイクルは、燃焼器１０４では
９から１への温度上昇があり、第１タービン１０５では
１から２へ膨張する。その後、第１熱交換器１０３と第
２熱交換器１０６により、第１タービン１０５の排ガス
を８−９と１２−１３へ再生する。In the topping cycle, the temperature rises from 9 to 1 in the combustor 104 and expands from 1 to 2 in the first turbine 105. Thereafter, the first heat exchanger 103 and the second heat exchanger 106 regenerate the exhaust gas of the first turbine 105 into 8-9 and 12-13.
【００２２】第３および第４熱交換器１０７，１０８に
よりボトミングの１１−１２と１８−１１へ再生する。
その後、低圧圧縮機１００により５から６へ加圧され中
間冷却器１０１により所定の温度まで冷却される。その
後、７から８へ高圧圧縮機１０２により加圧された後、
８−９でタービン排ガスの再生熱を受け取り加温され
る。The third and fourth heat exchangers 107 and 108 regenerate the bottoming to 11-12 and 18-11.
Thereafter, the pressure is increased from 5 to 6 by the low-pressure compressor 100 and cooled to a predetermined temperature by the intercooler 101. Then, after being pressurized by the high-pressure compressor 102 from 7 to 8,
In step 8-9, the regenerative heat of the turbine exhaust gas is received and heated.
【００２３】ボトミングでは、トッピングと８−９−１
−２−３−４において重なっており、その後１５から１
６へ第２タービン１０９により膨張する。その後、復水
器１１１を経たのち第１給水加熱器１１７と第２給水加
熱器１１８により加温された後、第１加圧ポンプ１１２
により加圧される。In bottoming, topping and 8-9-1
-2-3-4, then 15 to 1
The second turbine 109 expands to 6. Then, after passing through the condenser 111, it is heated by the first feed water heater 117 and the second feed water heater 118, and then the first pressurizing pump 112
Pressurized.
【００２４】その後第４熱交換器１０８、第３熱交換器
１０７と第２熱交換器１０６により加温された後、第３
タービン１１０で膨張して第３発電機１１６で出力を得
る。その後、蒸気の一部を第１タービン１０５の冷却に
使用し、その残りを高圧圧縮機１０２の出口蒸気と混合
される。After being heated by the fourth heat exchanger 108, the third heat exchanger 107 and the second heat exchanger 106,
The power is expanded by the turbine 110 and the output is obtained by the third generator 116. Thereafter, part of the steam is used for cooling the first turbine 105, and the rest is mixed with the outlet steam of the high-pressure compressor 102.
【００２５】復水器１１１を出た給水は燃焼器１０４で
供給されたＨ2 およびＯ2 と同じ質量流量分が排水され
る。その後、一部の凝縮水が中間冷却器１０１へ供給さ
れ低圧圧縮機１００からでてきた蒸気温度を低下させ
る。The feed water leaving the condenser 111 is drained by the same mass flow rate as H 2 and O 2 supplied by the combustor 104. After that, a part of the condensed water is supplied to the intercooler 101 to lower the temperature of the steam output from the low-pressure compressor 100.
【００２６】第１タービン１０５の排ガスを第１熱交換
器１０３により、図２の２から３で再生するが、再生す
る先を１２から１３だけでなく、第１熱交換器１０３に
より８から９へ再生することにより図１のサイクルの発
電端効率を向上させることができる（ボトミングではな
くトッピングへ再生することにより発電端効率を向上さ
せることができる）。この点が、従来のサイクルよりも
優れている点である。Exhaust gas from the first turbine 105 is regenerated by the first heat exchanger 103 at 2 to 3 in FIG. 2, but not only at 12 to 13 but also at 8 to 9 by the first heat exchanger 103. The power generation end efficiency of the cycle shown in FIG. 1 can be improved by regenerating to the power generation end (the power generation end efficiency can be improved by regenerating to the topping instead of the bottoming). This is an advantage over the conventional cycle.
【００２７】次に、図１に示した水素酸素燃焼タービン
プラントと、図３に示した従来の水素酸素燃焼タービン
プラントについてサイクル計算を行った結果を、表１，
表２に示す。ただし、計算上の仮定には表３に示した条
件を使用した。表１，表２より以下のことがいえる。Next, the results of cycle calculations for the hydrogen-oxygen combustion turbine plant shown in FIG. 1 and the conventional hydrogen-oxygen combustion turbine plant shown in FIG.
It is shown in Table 2. However, the conditions shown in Table 3 were used for the calculation assumptions. The following can be said from Tables 1 and 2.
【００２８】図１に示した本発明の水素酸素燃焼タービ
ンプラントの全体効率は６０．３％（ＨＨＶ基準）とな
り従来のプラントの５９．４％より相対値で１．５％高
効率化された。図１の本発明のプラントは中間冷却器１
０１を設置したことにより高圧圧縮機１０２の出口温度
を５５０℃と低温にすることができ、これにより従来の
プラントの７１８℃よりも圧縮機の実現性が高くなっ
た。The overall efficiency of the hydrogen-oxygen combustion turbine plant of the present invention shown in FIG. 1 is 60.3% (based on HHV), which is 1.5% higher in relative value than 59.4% of the conventional plant. . The plant of the present invention shown in FIG.
By installing 01, the outlet temperature of the high-pressure compressor 102 can be lowered to 550 ° C., which makes the compressor more feasible than 718 ° C. in the conventional plant.
【００２９】また、図１の本発明のプラントは、第１タ
ービン１０５入口流量が２３７kg/sとなり、従来プラン
トの２２５kg/sより約５％増加するため、第１段冷却翼
の翼高さを高くでき、冷却翼製作に有利となることがわ
かる。In the plant of the present invention shown in FIG. 1, the flow rate at the inlet of the first turbine 105 is 237 kg / s, which is about 5% higher than that of the conventional plant at 225 kg / s. It can be seen that the height can be increased, which is advantageous for manufacturing the cooling blade.
【００３０】[0030]
【表１】 [Table 1]
【００３１】[0031]
【表２】 [Table 2]
【００３２】[0032]
【表３】 [Table 3]
【００３３】[0033]
【発明の効果】以上具体的に説明したように、本発明に
よる水素酸素燃焼タービンプラントにおいては、タービ
ン出口と水素酸素燃焼器の上流部とを熱交換器で熱交換
させることにより、低圧力比でＨ2 ，Ｏ2 量を減少させ
高効率化することを特徴としており、このように構成し
た本発明の水素酸素燃焼タービンプラントは以下の効果
がある。As described above, in the hydrogen-oxygen combustion turbine plant according to the present invention, the low pressure ratio is achieved by exchanging heat between the turbine outlet and the upstream of the hydrogen-oxygen combustor by the heat exchanger. in H 2, O 2 amount is characterized by a high efficiency reduces, hydrogen-oxygen combustion turbine plant of the present invention constructed as described above has the following effects.
【００３４】（１）全体効率（発電端効率）を向上させ
る効果。 表１，表２に例示するように、本発明の水素酸素燃焼タ
ービンプラントの全体効率は６０．３％（ＨＨＶ基準）
となり従来のプラント５９．４％より相対値で１．５％
高効率化させる効果がある。(1) The effect of improving the overall efficiency (power generation end efficiency). As exemplified in Tables 1 and 2, the overall efficiency of the hydrogen-oxygen combustion turbine plant of the present invention is 60.3% (based on HHV).
1.5% relative value compared to 59.4% of the conventional plant
This has the effect of increasing efficiency.
【００３５】（２）圧縮機実現性を高める効果。 本発明のプラントは中間冷却を設けた構成を付加するこ
とにより高圧圧縮機出口温度を５５０℃と低温にするこ
とにより従来のプラントの７１８℃よりも圧縮機の実現
性を高めることができる。(2) The effect of increasing the feasibility of the compressor. The plant of the present invention can increase the feasibility of the compressor more than 718 ° C. of the conventional plant by lowering the high-pressure compressor outlet temperature to 550 ° C. by adding a configuration provided with intermediate cooling.
【００３６】（３）タービン冷却翼製作を容易にする効
果。 本発明のプラントの第１タービン入口流量が２３７kg/s
となり、従来プラントのそれの２２５kg/sより約５％増
加するため、第１段冷却翼、翼高さを高くでき冷却翼製
作を容易とする効果がある。(3) Effect of facilitating the manufacture of turbine cooling blades. The first turbine inlet flow rate of the plant of the present invention is 237 kg / s
This is approximately 5% higher than that of the conventional plant, which is 225 kg / s. Therefore, the height of the first stage cooling blade and the blade can be increased, and there is an effect of facilitating the manufacturing of the cooling blade.
【図１】本発明の実施の一形態に係る水素酸素燃焼ター
ビンの系統図。FIG. 1 is a system diagram of a hydrogen-oxygen combustion turbine according to one embodiment of the present invention.
【図２】図１に示した水素酸素燃焼タービンプラントの
温度−エントロピ線図。FIG. 2 is a temperature-entropy diagram of the hydrogen-oxygen combustion turbine plant shown in FIG.
【図３】従来の水素酸素燃焼タービンプラントの系統
図。FIG. 3 is a system diagram of a conventional hydrogen-oxygen combustion turbine plant.
【図４】図３に示した水素酸素燃焼タービンプラントの
温度−エントロピ線図。FIG. 4 is a temperature-entropy diagram of the hydrogen-oxygen combustion turbine plant shown in FIG. 3;
１００ 低圧圧縮機 １０１ 中間冷却器 １０２ 高圧圧縮機 １０３ 第１熱交換器 １０４ 燃焼器 １０５ 第１タービン １０６ 第２熱交換器 １０７ 第３熱交換器 １０８ 第４熱交換器 １０９ 第２タービン １１０ 第３タービン １１１ 復水器 １１２ 第１ポンプ １１３ 第２ポンプ １１４ 第１発電機 １１５ 第２発電機 １１６ 第３発電機 １１７ 第１給水加熱器 １１８ 第２給水加熱器 REFERENCE SIGNS LIST 100 low-pressure compressor 101 intercooler 102 high-pressure compressor 103 first heat exchanger 104 combustor 105 first turbine 106 second heat exchanger 107 third heat exchanger 108 fourth heat exchanger 109 second turbine 110 third Turbine 111 Condenser 112 First pump 113 Second pump 114 First generator 115 Second generator 116 Third generator 117 First feedwater heater 118 Second feedwater heater
フロントページの続き (56)参考文献 特開 平７−208192（ＪＰ，Ａ) 特開 平７−293207（ＪＰ，Ａ) 特開 昭54−31814（ＪＰ，Ａ) 特開 平８−254107（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) F01K 25/00 F02C 3/34 F02C 7/08 F02C 3/22 Continuation of front page (56) References JP-A-7-208192 (JP, A) JP-A-7-293207 (JP, A) JP-A-54-31814 (JP, A) JP-A 8-254107 (JP) , A) (58) Fields investigated (Int. Cl. 7 , DB name) F01K 25/00 F02C 3/34 F02C 7/08 F02C 3/22
Claims (2)
第１のタービンの排ガスの熱にて駆動する第１のタービ
ン以外のタービンを有する水素酸素燃焼ガスタービンプ
ラントにおいて、前記第１のタービンの排ガスの一部
を、同排ガスと第１のタービン以外のタービンの上流側
との熱交換を行う熱交換器に抽気すると共に、第１のタ
ービンの排ガスの残部を、同排ガスと燃焼器上流側との
熱交換を行う熱交換器に抽気することを特徴とする水素
酸素燃焼タービンプラント。A first turbine directly connected to a combustor;
First turbine driven by heat of exhaust gas of first turbine
Hydrogen-oxygen combustion gas turbine
Part of the exhaust gas of the first turbine in the runt
And the upstream side of the exhaust gas and turbines other than the first turbine.
Bleeds into a heat exchanger that exchanges heat with
The rest of the exhaust gas from the bin
Hydrogen characterized by extracting air to a heat exchanger that performs heat exchange
Oxygen combustion turbine plant .
に分割された圧縮機の間に中間冷却器を設けたことを特
徴とする請求項１に記載の水素酸素燃焼タービンプラン
ト。 2. An intermediate stage or plurality of gas turbine compressors.
That an intercooler was provided between the compressors
The hydrogen-oxygen combustion turbine plan according to claim 1, wherein
G.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08085098A JP3095680B2 (en) | 1996-04-08 | 1996-04-08 | Hydrogen-oxygen combustion turbine plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08085098A JP3095680B2 (en) | 1996-04-08 | 1996-04-08 | Hydrogen-oxygen combustion turbine plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09273402A JPH09273402A (en) | 1997-10-21 |
| JP3095680B2 true JP3095680B2 (en) | 2000-10-10 |
Family
ID=13849144
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP08085098A Expired - Fee Related JP3095680B2 (en) | 1996-04-08 | 1996-04-08 | Hydrogen-oxygen combustion turbine plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3095680B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT201700015175A1 (en) * | 2017-02-10 | 2018-08-10 | Spada S R L | Semi-closed first internal combustion engine and semi-closed thermodynamic process for power production |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3051678B2 (en) * | 1996-09-30 | 2000-06-12 | 三菱重工業株式会社 | Low temperature hydrogen combustion turbine |
| JP4521202B2 (en) | 2004-02-24 | 2010-08-11 | 株式会社東芝 | Steam turbine power plant |
-
1996
- 1996-04-08 JP JP08085098A patent/JP3095680B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT201700015175A1 (en) * | 2017-02-10 | 2018-08-10 | Spada S R L | Semi-closed first internal combustion engine and semi-closed thermodynamic process for power production |
| WO2018146624A1 (en) * | 2017-02-10 | 2018-08-16 | Spada Srl | Semi-closed cycle internal combustion prime mover and semi-closed thermodynamic process for the production of power |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH09273402A (en) | 1997-10-21 |
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