JPH09273402A - Hydrogen-oxygen combustion turbine plant - Google Patents
Hydrogen-oxygen combustion turbine plantInfo
- Publication number
- JPH09273402A JPH09273402A JP8509896A JP8509896A JPH09273402A JP H09273402 A JPH09273402 A JP H09273402A JP 8509896 A JP8509896 A JP 8509896A JP 8509896 A JP8509896 A JP 8509896A JP H09273402 A JPH09273402 A JP H09273402A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- exhaust gas
- heat exchanger
- hydrogen
- compressor
- 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.)
- Granted
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)
Abstract
Description
【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 highly efficient and highly feasible hydrogen-oxygen combustion turbine plant cycles currently under consideration. In FIG.
Reference numeral 0 is a compressor, 204 is a combustor, 205 is a first turbine, and the gas compressed by the compressor 200 is mixed with hydrogen and oxygen supplied to the combustor 204 and combusted. The gas (water vapor) 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。Reference numerals 207 and 208 denote heat exchangers, and the combustion gas (steam) leaving the first turbine 205 is the heat exchanger 20.
It flows to the compressor 200 through 7,208. 209 is the second
Combustion gas (water vapor) exiting the heat exchanger 207 in the turbine
Of the combustion gas (steam) that has been discharged from the second turbine 209 and 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 discharged from 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 to be further heated and converted into steam. Then, it is supplied to the third turbine 210 to drive it. Part of the exhaust gas from 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. 215 and 21 in the figure
6 has shown the 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. The numbers in the figure correspond to the numbers in FIG. Explaining the numbers below, the combustor 2
The steam generated by the combustion in 04 drives the first turbine 205 and expands to become 21 to 22, and the feed water is heated by the heat exchangers 207 and 208 to be in the state of 24 at a constant pressure equal to or higher than the atmospheric pressure. Then, the air is taken into the compressor 200, compressed by the work of the compressor 200 into a state of 25, and 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。[0006] A part of the steam in the state of 23, which has exited the heat exchanger 207, drives the second turbine 209 to expand, becomes exhaust in the state of 30, and becomes the condensed water 29 in the condenser 211. After that, the condensate is supplied to the feed water heaters 217 and 218 and the heat exchanger 20.
7,208 heated to saturate steam 28 to superheated steam 27
Then, the third turbine 210 is driven and the exhaust gas 31 is returned 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 improve 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. , High cost due to increase in the number of stages of the compressor 200 and the first turbine 205, start-up problem, problem of manufacturing cooling blade due to reduction of turbine inlet blade height, compressor final stage due to increase of compressor outlet temperature There are various problems such as a problem with the disc 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。[0008] Therefore, an object of the present invention is to provide a hydrogen / oxygen combustion turbine plant that is highly efficient without increasing the pressure ratio of the compressor and 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、燃焼器上流側のガスとタービン出口からの排
気とを熱交換させる熱交換器を設けた水素酸素燃焼ター
ビンプラントを提供する。In order to solve the above-mentioned problems, the present invention provides a hydrogen-oxygen combustion turbine plant provided with a heat exchanger for exchanging heat between the gas on the upstream side of the combustor and the exhaust gas from the turbine outlet. .
【００１０】このように、水素酸素燃焼器上流部とター
ビン出口とを熱交換させる熱交換器を設けることによっ
て低圧力比で、Ｈ2 ，Ｏ2 量を減少させ高効率化させる
ことができる。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、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、タービン第１段冷却翼製作
に有利となる。As described above, by providing the heat exchanger for exchanging heat between the upstream part of the hydrogen-oxygen combustor and the outlet of the turbine, it is possible to reduce the amounts of H 2 and O 2 and improve the efficiency at a low pressure ratio. Further, this makes it possible to increase the turbine inlet flow rate as compared with the conventional cycle when the entire plant output is the same, which is advantageous for manufacturing the turbine first stage cooling blade.
【００１１】前記した本発明による水素酸素燃焼タービ
ンプラントは、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具体化した構成とする
ことができる。The hydrogen-oxygen combustion turbine plant according to the present invention described above has hydrogen-oxygen having a first turbine directly connected to a combustor and a turbine other than the first turbine driven by heat of exhaust gas from the first turbine. In a combustion turbine plant, a part of the exhaust gas of the first turbine is extracted into a heat exchanger that performs heat exchange between the exhaust gas and the upstream side of a turbine other than the first turbine, and the exhaust gas of the first turbine is also extracted. The remaining part can be embodied so as to be extracted into a heat exchanger that exchanges heat between the exhaust gas and the upstream side of the combustor.
【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-mentioned structure, as described above,
Of the exhaust gas of the first turbine and at the same time, the remaining part of the exhaust gas of the first turbine and the upstream side of the combustor are heat-exchanged with each other at a low pressure ratio. 2 has the effect of reducing the amount of O 2 and O 2 to improve efficiency, and when this makes the output of the entire plant the same, the first turbine inlet flow rate can be increased compared to the conventional cycle. It has an advantageous effect in manufacturing the first-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。In the hydrogen-oxygen combustion turbine plant according to the present invention, it is preferable that an intermediate cooler is provided between an intermediate stage of the gas turbine compressor or a plurality of divided compressors. By thus providing the intercooler and injecting the water downstream of the condenser, the compressor outlet temperature is lowered, and the compressor feasibility is enhanced.
【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。BEST MODE FOR CARRYING OUT THE INVENTION A hydrogen-oxygen combustion turbine plant according to the present invention will be described below with reference to an embodiment shown in FIG. 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 between them.
【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。104 is a combustor, 105 is a first turbine,
109 is a second turbine and 110 is a third turbine.
114, 115, 116 are respectively the first turbine 1
05, the 2nd turbine 109, and the 1st, 2nd, 3rd generator driven by the 3rd turbine 110 are shown. 1
03, 106, 107 and 108 are first, second, third and fourth heat exchangers 117 and 118 are first and second
The feed water heater is shown.
【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。111 is a condenser, and 112 and 113 are the first
And the second pump is shown. The gas discharged from the high-pressure compressor 102 is heated by the first heat exchanger 103 and supplied to the combustor 104, mixed with hydrogen and oxygen supplied thereto and combusted, and the high-temperature combustion gas generated by the combustion is It is supplied to the first turbine 105 to drive 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。Exhaust gas from the first turbine 105 is divided into two parts, a part of which flows to the first heat exchanger 103, and another part of which is the second part.
It flows to the heat exchanger 106. First and second heat exchanger 103
Exhaust gas that exits from the first heat exchanger 107 and the second heat exchanger 107 merges,
After heating the steam flowing to the fourth heat exchanger 108 and flowing to 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 from 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 the condenser 111
Condensed water at the first feed water heater 117, 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 from the third turbine 110 is used as cooling steam for the first turbine 105, and the rest is combined with the outlet of the high-pressure compressor 102. A 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-
14 shows a closed cycle composed of 14-8. 8-9-1-2
In the part -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。The topping cycle has a temperature rise from 9 to 1 in the combustor 104 and expands from 1 to 2 in the first turbine 105. After that, the exhaust gas of the first turbine 105 is regenerated to 8-9 and 12-13 by the first heat exchanger 103 and the second heat exchanger 106.
【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。Regeneration into bottoming 11-12 and 18-11 is performed by the third and fourth heat exchangers 107 and 108.
Then, the low-pressure compressor 100 pressurizes the pressure from 5 to 6, and the intercooler 101 cools it to a predetermined temperature. Then, after being pressurized by the high-pressure compressor 102 from 7 to 8,
At 8-9, the heat of regeneration 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 overlap, then 15 to 1
It is expanded to 6 by the second turbine 109. Then, after passing through the condenser 111, after being heated by the first feed water heater 117 and the second feed water heater 118, 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 heating by the fourth heat exchanger 108, the third heat exchanger 107 and the second heat exchanger 106, the third heat exchanger 108 is heated.
The turbine 110 expands and the third generator 116 obtains an output. Then, a 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 exiting the condenser 111 is discharged by the same mass flow rate as H 2 and O 2 supplied by the combustor 104. Then, a part of the condensed water is supplied to the intercooler 101 to lower the vapor temperature coming out of 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 in 2 to 3 of FIG. 2, but not only 12 to 13 but also 8 to 9 by the first heat exchanger 103. It is possible to improve the power generation end efficiency of the cycle of FIG. 1 by regenerating to (not to bottoming but topping to improve the power generation end efficiency). 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, Table 1 shows the results of cycle calculation 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% (HHV standard), which is a relative efficiency improvement of 1.5% from 59.4% of the conventional plant. . The plant of the present invention in FIG. 1 has an intercooler 1
By installing 01, the outlet temperature of the high-pressure compressor 102 can be made as low as 550 ° C., which makes the compressor more feasible than the conventional plant of 718 ° C.
【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。Further, in the plant of the present invention shown in FIG. 1, the inlet flow rate of the first turbine 105 is 237 kg / s, which is approximately 5% higher than the 225 kg / s of the conventional plant. Therefore, the blade height of the first-stage cooling blade is increased. 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 in detail above, in the hydrogen-oxygen combustion turbine plant according to the present invention, the turbine outlet and the upstream portion of the hydrogen-oxygen combustor are heat-exchanged by the heat exchanger, so that the low pressure ratio is reduced. It is characterized by reducing the amounts of H 2 and O 2 to improve the efficiency. The hydrogen-oxygen combustion turbine plant of the present invention thus configured 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 illustrated in Table 1 and Table 2, the overall efficiency of the hydrogen-oxygen combustion turbine plant of the present invention is 60.3% (HHV standard).
Becomes 1.5% in relative value from the conventional plant of 59.4%
It 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 improving the feasibility of the compressor. In the plant of the present invention, the high temperature compressor outlet temperature can be set to a low temperature of 550 ° C. by adding the configuration in which the intermediate cooling is provided.
【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 manufacture of turbine cooling blades. The first turbine inlet flow rate of the plant of the present invention is 237 kg / s
This is about 5% higher than that of the conventional plant, which is 225 kg / s, so that the height of the first-stage cooling blade and the blade height can be increased, which has the 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 an 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。4 is a temperature-entropy diagram of the hydrogen-oxygen combustion turbine plant shown in FIG.
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 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 feed water heater 118 Second feed water heater
Claims (3)
いて、燃焼器上流側とタービン下流側との熱交換を行う
熱交換器を設けたことを特徴とする水素酸素燃焼タービ
ンプラント。1. A hydrogen-oxygen combustion gas turbine plant, comprising a heat exchanger for exchanging heat between a combustor upstream side and a turbine downstream side.
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。2. A hydrogen-oxygen combustion gas turbine plant having a first turbine directly connected to a combustor and a turbine other than the first turbine driven by heat of exhaust gas of the first turbine, wherein A part of the exhaust gas of the turbine is extracted to a heat exchanger that performs heat exchange between the exhaust gas and the upstream side of the turbine other than the first turbine, and the remaining part of the exhaust gas of the first turbine is extracted from the exhaust gas and the combustor. A hydrogen-oxygen combustion turbine plant characterized by extracting air to a heat exchanger for heat exchange with the upstream side.
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または２に記載の水素酸素燃焼タービ
ンプラント。3. The hydrogen-oxygen combustion turbine plant according to claim 1, wherein an intercooler is provided between an intermediate stage of the gas turbine compressor or a plurality of divided compressors.
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 true JPH09273402A (en) | 1997-10-21 |
| JP3095680B2 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 (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10103021A (en) * | 1996-09-30 | 1998-04-21 | Mitsubishi Heavy Ind Ltd | Low temperature type hydrogen burning turbine |
| EP1580483A1 (en) * | 2004-02-24 | 2005-09-28 | Kabushiki Kaisha Toshiba | Steam turbine plant |
| 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 |
-
1996
- 1996-04-08 JP JP08085098A patent/JP3095680B2/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10103021A (en) * | 1996-09-30 | 1998-04-21 | Mitsubishi Heavy Ind Ltd | Low temperature type hydrogen burning turbine |
| EP1580483A1 (en) * | 2004-02-24 | 2005-09-28 | Kabushiki Kaisha Toshiba | Steam turbine plant |
| US7278267B2 (en) | 2004-02-24 | 2007-10-09 | Kabushiki Kaisha Toshiba | Steam turbine plant |
| 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 |
|---|---|
| JP3095680B2 (en) | 2000-10-10 |
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