JPH10299417A - Hydrogen combustion turbine plant - Google Patents
Hydrogen combustion turbine plantInfo
- Publication number
- JPH10299417A JPH10299417A JP9107688A JP10768897A JPH10299417A JP H10299417 A JPH10299417 A JP H10299417A JP 9107688 A JP9107688 A JP 9107688A JP 10768897 A JP10768897 A JP 10768897A JP H10299417 A JPH10299417 A JP H10299417A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- turbine
- steam
- pressure turbine
- medium
- 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
-
- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Landscapes
- 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、水素を燃料とし、
純酸素を酸化剤とする水素燃焼タービンプラントに係
り、特に、多段再熱ランキンサイクルをベースとし、水
素の純酸素燃焼により発生する蒸気をタービンの構成部
品の冷却に利用する水素燃焼タービンプラントに関す
る。[0001] The present invention relates to the use of hydrogen as a fuel,
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydrogen combustion turbine plant using pure oxygen as an oxidant, and more particularly to a hydrogen combustion turbine plant based on a multi-stage reheat Rankine cycle and utilizing steam generated by pure oxygen combustion of hydrogen for cooling components of a turbine.
【０００２】[0002]
【従来の技術】最近の火力発電プラントでは、プラント
の高熱効率化，プラントの起動時間短縮化が高く評価さ
れ、ガスタービンに、蒸気タービンプラントおよび排熱
回収ボイラを組み合せたコンバインドサイクル発電プラ
ントが実用機として数多く運転されている。2. Description of the Related Art In recent thermal power plants, high thermal efficiency of the plant and shortening of the start-up time of the plant are highly evaluated, and a combined cycle power plant in which a steam turbine plant and an exhaust heat recovery boiler are combined with a gas turbine is practically used. Many machines are in operation.
【０００３】しかし、このコンバインドサイクル発電プ
ラントにおいては、ガスタービンプラントの燃料に、液
化天然ガスや石油（灯油）等の天然資源を使用している
が、何分にもガスタービンプラントの燃料が時間当り数
百トンと多量に消費することを考えると、天然資源の埋
蔵量に限界があり、自ずと代替燃料が必要になってきて
いる。また、天然資源は、クリーンなエネルギと言えど
も、ＮＯｘ，ＣＯ等の有害廃棄物を皆無にすることがで
きず、高出力化が求められている今日、その燃料消費を
考えると、有害廃棄物の極めて少ない代替燃料が必要で
ある。また、各家庭を含めた民生部門での電力消費が依
然として延びている今日、この需要に応えるために、ガ
スタービンプラントよりも高い出力が出せる代替原動機
が必要である。[0003] In this combined cycle power plant, however, natural resources such as liquefied natural gas and petroleum (kerosene) are used as fuel for the gas turbine plant. Considering the large consumption of several hundred tons per hour, the reserves of natural resources are limited and alternative fuels are naturally needed. Also, natural resources are clean energy, but harmful wastes such as NOx and CO cannot be completely eliminated, and high output is demanded today. Very few alternative fuels are needed. In addition, today's electricity consumption in the consumer sector, including households, is still growing, and to meet this demand, alternative prime movers that can produce higher power than gas turbine plants are needed.
【０００４】このような社会的ニーズ・シーズに対し、
最近、燃料に水素を用い、また酸化剤に純酸素を用い、
水素の純酸素燃焼により生成される廃棄物をクリーン化
させ、さらに発生する蒸気を超高温化させ、この超高温
蒸気をタービン駆動蒸気にする水素燃焼タービンプラン
トに、蒸気発生器（排熱回収ボイラとしての熱交換器）
を組み合せたコンバインドサイクル発電プラントが公表
され（特開平７−２９３２０７号公報）、商業ベースへ
の実現性を高い期待をもって見守られている。[0004] Such social needs seeds,
Recently, using hydrogen as fuel and pure oxygen as oxidizer,
A steam generator (exhaust heat recovery boiler) is installed in a hydrogen combustion turbine plant that cleans the waste generated by the pure oxygen combustion of hydrogen, raises the generated steam to ultra-high temperature, and turns this ultra-high temperature steam into turbine-driven steam. Heat exchanger)
A combined cycle power plant combining the above has been published (Japanese Patent Application Laid-Open No. 7-293207), and its commercial viability has been watched with high expectation.
【０００５】この水素燃焼タービンプラントは、図３に
示すように、高圧タービン１と低圧タービン２との間
に、中高圧タービン３ａと中低圧タービン３ｂを組み合
せた中圧タービン３を備え、中高圧タービン３ａ、中低
圧タービン３ｂのそれぞれに高圧水素燃焼器４ａ、低圧
水素燃焼器４ｂから発生する超高温蒸気（水蒸気）を供
給させるようになっている。As shown in FIG. 3, this hydrogen combustion turbine plant includes a medium-pressure turbine 3 in which a medium-high-pressure turbine 3a and a medium-low-pressure turbine 3b are combined between a high-pressure turbine 1 and a low-pressure turbine 2, Ultra-high-temperature steam (steam) generated from the high-pressure hydrogen combustor 4a and the low-pressure hydrogen combustor 4b is supplied to each of the turbine 3a and the medium- and low-pressure turbines 3b.
【０００６】また、中圧タービン３の中高圧タービン３
ａおよび中低圧タービン３ｂの出口側には、蒸気発生器
としての第１熱交換器（排熱回収ボイラ）５ａ、第２熱
交換器（排熱回収ボイラ）５ｂをそれぞれ備えている。[0006] The medium-pressure turbine 3
The first heat exchanger (exhaust heat recovery boiler) 5a and the second heat exchanger (exhaust heat recovery boiler) 5b as steam generators are provided at the outlet side of the turbine a and the low- and middle-pressure turbine 3b, respectively.
【０００７】第１熱交換器５ａ、第２熱交換器５ｂは、
ともに蒸気タービンプラント６の給水系６ａからの給水
が供給されており、中高圧タービン３ａの排気蒸気およ
び中低圧タービン３ｂの排気蒸気のそれぞれを加熱源に
して、図４に示すように、給水を高温化させている。The first heat exchanger 5a and the second heat exchanger 5b
In both cases, feedwater from a feedwater system 6a of the steam turbine plant 6 is supplied, and as shown in FIG. 4, the feedwater is supplied by using the exhaust steam of the medium-high pressure turbine 3a and the exhaust steam of the medium-low pressure turbine 3b as heating sources. High temperature.
【０００８】また、第１熱交換器５ａは、図３に示すよ
うに、蒸気を過熱器７で再び高温化させ、その高温蒸気
を第２熱交換器５ｂから供給される高温蒸気に合流さ
せ、高圧タービン１に駆動蒸気として供給する一方、低
圧水素燃焼器４ｂにも供給し、再び超高温化させて中低
圧タービン３ｂに供給している。また、第２熱交換器５
ｂは、蒸気を高温化させ、駆動蒸気として低圧タービン
２に供給している。As shown in FIG. 3, the first heat exchanger 5a raises the temperature of the steam again by the superheater 7, and merges the high-temperature steam with the high-temperature steam supplied from the second heat exchanger 5b. , And is also supplied to the low-pressure hydrogen combustor 4b while being heated to an ultra-high temperature again and supplied to the medium- and low-pressure turbine 3b. In addition, the second heat exchanger 5
b raises the temperature of the steam and supplies it to the low-pressure turbine 2 as driving steam.
【０００９】このように、最近、開示された水素燃焼タ
ービンプラントは、高低圧水素燃焼器４ａ，４ｂを備
え、水素の純酸素燃焼により１７００℃以上の超高温蒸
気を発生させることができるようになっており、この超
高温化に伴って４８万ＫＷ以上の電気出力が出せ、民生
部門の電力需要に応えようとしている。なお、４８万Ｋ
Ｗ以上の電気出力は、この種の単機容量として世界最大
級である。As described above, the recently disclosed hydrogen combustion turbine plant is provided with the high and low pressure hydrogen combustors 4a and 4b so that ultrahigh temperature steam of 1700 ° C. or more can be generated by the pure oxygen combustion of hydrogen. With this ultra-high temperature, electric power of more than 480,000 KW can be output, and it is trying to meet the electric power demand of the consumer sector. 480,000K
An electric output of W or more is one of the largest in the world as this type of single unit capacity.
【００１０】[0010]
【発明が解決しようとする課題】特開平７−２９３２０
７号公報に開示された水素燃焼タービンプラントは、タ
ービン駆動蒸気が１７００℃以上の超高温になっている
ため、従来の構成機器の一つ一つを見直すと、解決すべ
き課題が数多く含まれており、その一つにタービン構成
部品、例えばタービン静翼、タービン動翼の効果的な冷
却化と、これに関連する冷却蒸気の供給・回収がある。SUMMARY OF THE INVENTION Japanese Patent Application Laid-Open No. 7-29320
In the hydrogen combustion turbine plant disclosed in Japanese Patent Publication No. 7, since the turbine driving steam is at an extremely high temperature of 1700 ° C. or more, a review of each of the conventional components includes many problems to be solved. One of them is effective cooling of turbine components such as turbine vanes and turbine blades, and supply and recovery of cooling steam related thereto.
【００１１】従来、タービン静翼、タービン動翼等のタ
ービン構成部品は、耐熱材料の開発と冷却技術の進歩に
より高温、例えば１３００℃の燃焼ガス温度でも充分に
対処できるようになっているが、何分にも未だ未経験の
超高温のタービン駆動蒸気を冷却用蒸気として使用する
ものであってみれば、翼内を過不足なく冷却できるかど
うか、一抹の不安がある。Conventionally, turbine components such as turbine vanes and turbine blades can sufficiently cope with high temperatures, for example, a combustion gas temperature of 1300 ° C. due to the development of heat-resistant materials and advances in cooling technology. If ultra-high-temperature turbine-driven steam, which has not yet been experienced for many minutes, is used as cooling steam, there is some uncertainty as to whether the inside of the blade can be cooled without excess or shortage.
【００１２】また、翼内に供給する冷却用蒸気の供給源
を何処に求めるか、あるいは翼内冷却後の冷却用蒸気を
何処に回収させるかは、冷却用蒸気の消費に伴うプラン
ト熱清算の考察およびタービン駆動蒸気が超高温である
こととのバランス等主要な検討項目であり、その供給源
および回収源の選定を誤れば、冷却用蒸気の無駄なエネ
ルギ消費、ひいてはプラント熱効率の低下に繋るおそれ
がある。Further, where to find the supply source of the cooling steam to be supplied to the blade or where to collect the cooling steam after cooling the blade is determined by the plant heat liquidation accompanying the consumption of the cooling steam. This is a major study item such as the balance between consideration and the fact that turbine-driven steam is at an extremely high temperature.Incorrect selection of the supply source and recovery source leads to wasteful energy consumption of cooling steam and, consequently, a reduction in plant thermal efficiency. May be affected.
【００１３】本発明は、このような検討結果からなされ
たもので、効果的なタービン構成部品の冷却と、適正な
冷却用蒸気の供給源の選定およびその回収の検討を充分
に行った水素燃焼タービンプラントを提供することを目
的とする。The present invention has been made based on the above-described study results. Hydrogen combustion which has been sufficiently studied for effective cooling of turbine component parts, selection of an appropriate cooling steam supply source and its recovery. It is intended to provide a turbine plant.
【００１４】[0014]
【課題を解決するための手段】本発明に係る水素燃焼タ
ービンプラントは、上述した課題を解決するために、請
求項１に記載したように、高圧タービンと低圧タービン
との間に少なくとも２段以上の中圧タービンを設け、各
中圧タービンの入口蒸気を、水素と純酸素とを当量燃焼
させる水素燃焼器により再加熱する水素燃焼タービンプ
ラントにおいて、上記中圧タービンの少なくとも一方に
はタービン排気側に熱交換器を設け、この熱交換器は復
水給水系から案内される給水を蒸気化させ、この蒸気の
一部を上記中圧タービンの構成部品に冷却用として供給
する冷却用蒸気供給系を備えたものである。In order to solve the above-mentioned problems, a hydrogen combustion turbine plant according to the present invention has at least two or more stages between a high-pressure turbine and a low-pressure turbine. In a hydrogen combustion turbine plant in which intermediate pressure turbines are provided and the inlet steam of each intermediate pressure turbine is reheated by a hydrogen combustor that burns hydrogen and pure oxygen in an equivalent amount, at least one of the intermediate pressure turbines has a turbine exhaust side. And a cooling steam supply system that supplies a part of the steam to the components of the medium pressure turbine for cooling. It is provided with.
【００１５】本発明に係る水素燃焼タービンプラント
は、上述した課題を解決するために、請求項２に記載し
たように、中圧タービンは、少なくとも中高圧タービン
と中低圧タービンとを備え、上記中高圧タービンおよび
中低圧タービンへの入口蒸気をそれぞれ過熱する高圧水
素燃焼器および低圧水素燃焼器を設け、中高圧タービン
からのタービン排気側に高圧タービン駆動用蒸気を発生
させる高圧熱交換器を設ける一方、中低圧タービンから
のタービン排気側に、上記高圧熱交換器からの高圧ター
ビン駆動蒸気に合流させる低圧熱交換器を設け、上記高
圧熱交換器および低圧熱交換器のそれぞれで発生させる
蒸気の一部を上記中高圧タービンの構成部品および中低
圧タービンの構成部品のそれぞれに冷却用として供給す
る冷却用高圧蒸気供給系と冷却用低圧蒸気供給系とをそ
れぞれ備えたものである。According to a second aspect of the present invention, there is provided a hydrogen combustion turbine plant comprising at least an intermediate high pressure turbine and an intermediate low pressure turbine. A high-pressure hydrogen combustor and a low-pressure hydrogen combustor that superheat the inlet steam to the high-pressure turbine and the medium- and low-pressure turbine, respectively; and a high-pressure heat exchanger that generates high-pressure turbine driving steam on the turbine exhaust side from the medium- and high-pressure turbine. A low-pressure heat exchanger that merges with the high-pressure turbine driving steam from the high-pressure heat exchanger on the turbine exhaust side from the medium- and low-pressure turbine, and includes one of the high-pressure heat exchanger and the low-pressure heat exchanger. The high-pressure steam supply for cooling supplies the cooling part to each of the components of the medium-to-high pressure turbine and the components of the medium-to-low pressure turbine. System and the cooling low pressure steam supply system and the those having respectively.
【００１６】本発明に係る水素燃焼タービンプラント
は、上述した課題を解決するために、請求項３に記載し
たように、中高圧タービンの構成部品および中低圧ター
ビンの構成部品に供給される冷却用の蒸気は、各構成部
品冷却後、上記中高圧タービンの駆動蒸気および中低圧
タービンの駆動蒸気のそれぞれに合流させるか、上記高
圧熱交換器および低圧熱交換器のそれぞれに回収させる
かいずれかを選択したものである。According to a third aspect of the present invention, there is provided a hydrogen-fired turbine plant for cooling which is supplied to components of a medium-to-high pressure turbine and components of a medium-to-low pressure turbine. After cooling each component, either the driving steam for the medium-to-high pressure turbine and the driving steam for the medium-to-low pressure turbine are combined, or the steam is recovered in each of the high-pressure heat exchanger and the low-pressure heat exchanger. It is the one you have chosen.
【００１７】[0017]
【発明の実施の形態】以下、本発明に係る水素燃焼ター
ビンプラントの一実施形態を図面を参照して説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a hydrogen combustion turbine plant according to the present invention will be described below with reference to the drawings.
【００１８】図１は、エネルギ供給プラントとして本発
明に係る水素燃焼タービンプラントを発電プラントに適
用した系統図を示す。FIG. 1 shows a system diagram in which a hydrogen combustion turbine plant according to the present invention is applied to a power plant as an energy supply plant.
【００１９】この水素燃焼タービンプラント１０は、高
圧タービン１１と低圧タービン１２との間に中高圧ター
ビン１３ａと中低圧タービン１３ｂからなる２段の中圧
タービン１３が設けられる。This hydrogen combustion turbine plant 10 is provided with a two-stage intermediate pressure turbine 13 consisting of an intermediate high pressure turbine 13a and an intermediate low pressure turbine 13b between a high pressure turbine 11 and a low pressure turbine 12.
【００２０】中圧タービン１３を構成する中高圧タービ
ン１３ａおよび中低圧タービン１３ｂのタービン入口側
に高圧水素燃焼器１５および低圧水素燃焼器１６がそれ
ぞれ設置される。各水素燃焼器１５，１６は水素と純酸
素とを当量燃焼させ、例えば１６００℃程度あるいはそ
れ以上の超高温蒸気を中高圧タービン１３ａあるいは中
低圧タービン１３ｂに供給するようになっている。A high-pressure hydrogen combustor 15 and a low-pressure hydrogen combustor 16 are installed on the turbine inlet side of the medium- and high-pressure turbines 13a and 13b constituting the medium-pressure turbine 13, respectively. Each of the hydrogen combustors 15 and 16 combusts hydrogen and pure oxygen in an equivalent amount, and supplies ultra-high-temperature steam of, for example, about 1600 ° C. or more to the medium-high pressure turbine 13a or the medium-low pressure turbine 13b.
【００２１】また、中高圧タービン１３ａおよび中低圧
タービン１３ｂのタービン排気側に、高温のタービン排
気の排熱を熱回収する高圧熱交換器１７および低圧熱交
換器１８がそれぞれ設置される。A high-pressure heat exchanger 17 and a low-pressure heat exchanger 18 for recovering the exhaust heat of the high-temperature turbine exhaust are provided on the turbine exhaust side of the intermediate-high pressure turbine 13a and the intermediate-low pressure turbine 13b, respectively.
【００２２】高圧熱交換器１７は、中高圧タービン１３
ａの排気を加熱源として復水給水系１９からの給水を加
熱して蒸気を発生させ、その蒸気を中高圧タービン１３
ａの構成部品、例えばタービン静翼、タービン動翼等に
冷却用として供給する冷却用高圧蒸気供給系１７ａを備
えている。The high-pressure heat exchanger 17 includes a medium-to-high pressure turbine 13
The steam from the condensate water supply system 19 is heated by using the exhaust gas a as a heat source to generate steam, and the steam is
A cooling high-pressure steam supply system 17a is provided for cooling components such as turbine stationary blades and turbine blades.
【００２３】また、低圧熱交換器１８は、中低圧タービ
ン１３ｂの排気を加熱源として復水給水系１９からの給
水を加熱して蒸気を発生させ、その蒸気を中低圧タービ
ン１３ｂの構成部品、例えばタービン静翼、タービン動
翼等に冷却用として供給する冷却用低圧蒸気供給系１８
ａを備えている。The low-pressure heat exchanger 18 heats water supplied from the condensate water supply system 19 using the exhaust gas of the medium-low pressure turbine 13b as a heating source to generate steam, and uses the steam as a component of the medium-low pressure turbine 13b. For example, a low-pressure steam supply system 18 for cooling supplied to a turbine stationary blade, a turbine moving blade, etc.
a.
【００２４】この水素燃焼タービンプラント１０は、発
電プラントとして機能し、高圧タービン１１、各中圧タ
ービン１３および低圧タービン１２を駆動させることに
より、各タービン１１，１２，１３が仕事をし、発電機
２０を回転駆動させ、電気出力を得るようにするととも
に、中圧タービン１３を構成する中高圧タービン１３ａ
および中低圧タービン１３ｂのそれぞれの構成部品の冷
却化に対処できるようになっている。The hydrogen combustion turbine plant 10 functions as a power plant, and drives the high-pressure turbine 11, each medium-pressure turbine 13 and the low-pressure turbine 12 so that the turbines 11, 12, and 13 work and the generator 20 is rotated to obtain an electric output, and a medium-pressure turbine 13 a
It is possible to cope with the cooling of each component of the medium and low pressure turbine 13b.
【００２５】また、低圧タービン１２で仕事をし、膨張
した蒸気は、続いて復水器２１に案内され、ここで冷却
され、凝縮作用を受けて復水となる。この復水は復水ポ
ンプ２２により復水給水系１９に案内される。一部の復
水は必要に応じて系外に排出される。The steam that has worked in the low-pressure turbine 12 and expanded is subsequently guided to a condenser 21 where it is cooled and condensed to be condensed. This condensate is guided to the condensate water supply system 19 by the condensate pump 22. Some condensate is discharged out of the system as needed.
【００２６】一方、復水給水系１９には多段式の低圧給
水加熱器２３、脱気器２４、中圧給水加熱器２５および
高圧給水加熱器２６が順次設置される。復水給水系１９
を通る復水（給水）は低圧給水加熱器２３、中圧給水加
熱器２５および高圧給水加熱器２６で、それぞれ順次加
熱され、段階的に温度上昇する。給水の加熱蒸気は低圧
タービン１２や中圧タービン１３からのタービン抽気で
ある。一方、復水給水系１９を通る復水や給水は復水ポ
ンプ２２および多段の給水ポンプ２８，２９によりポン
プアップされ、加圧される。On the other hand, in the condensate water supply system 19, a multi-stage low-pressure water heater 23, a deaerator 24, a medium-pressure water heater 25, and a high-pressure water heater 26 are sequentially installed. Condensate water supply system 19
The condensate (water supply) passing through is heated by the low-pressure feedwater heater 23, the medium-pressure feedwater heater 25, and the high-pressure feedwater heater 26, respectively, in order, and the temperature rises stepwise. The heating steam of the feedwater is turbine bleed air from the low-pressure turbine 12 and the medium-pressure turbine 13. On the other hand, the condensed water and water supplied through the condensed water supply system 19 are pumped up by the condensate pump 22 and the multi-stage water supply pumps 28 and 29 and pressurized.
【００２７】なお、この復水給水系１９では復水（給
水）を低圧、中圧および高圧の給水加熱器で多段に加熱
する例を示したが、給水を多段加熱する際、中圧給水加
熱器２５やこの加熱器に給水を送り込む給水ポンプ２８
は必ずしも必要としない。In the condensate water supply system 19, the condensate (water supply) is heated in multiple stages by low, medium and high pressure feed water heaters. Water pump 28 for feeding water to the heater 25 or this heater
Is not necessarily required.
【００２８】復水給水系１９の各給水加熱器２３，２
５，２６で多段加熱された高温（例えば３５０℃程度）
で高圧（例えば３５０ata 〜５００ata ）の給水は、排
熱回収ボイラ１７に送られ、この排熱回収ボイラ１７に
て中高圧タービン１３ａで膨張したタービン排気（例え
ば圧力１９ata、温度１２５０℃程度）と熱交換し、よ
り高温・高圧の高圧タービン駆動用蒸気が生成される。
この蒸気は高圧タービン１１の入口側に戻され、２段再
熱ランキンサイクルが構成される。従来の水素燃焼ター
ビンプラントで用いられた過熱器は不要となる。Each feed water heater 23, 2 of the condensate feed water system 19
High temperature (for example, about 350 ° C) heated in multiple stages at 5, 26
The high-pressure (for example, 350 to 500 at) feed water is sent to an exhaust heat recovery boiler 17, where the exhaust gas is expanded by a medium-to-high pressure turbine 13a to generate turbine exhaust (for example, a pressure of 19 at a temperature of about 1250 ° C.) and heat. In exchange, higher-temperature, high-pressure steam for driving the high-pressure turbine is generated.
This steam is returned to the inlet side of the high-pressure turbine 11 to form a two-stage reheat Rankine cycle. The superheater used in the conventional hydrogen combustion turbine plant becomes unnecessary.
【００２９】次に、水素燃焼タービンプラントの作用を
説明する。Next, the operation of the hydrogen combustion turbine plant will be described.
【００３０】この水素燃焼タービンプラント１０は、図
２で示すＴ−Ｓ線図に基づいて運転される。復水給水系
１９を通る給水は、給水加熱器２３，２５，２６により
多段加熱され、高温高圧（例えば３５０℃、３７０ata
程度）となり、この給水は続いて高圧熱交換器１７で中
高圧タービン１３ａからのタービン排気により過熱さ
れ、過熱蒸気となる。その際、過熱途中の一部の蒸気
は、冷却用の蒸気として冷却用高圧蒸気供給系１７を介
して中高圧タービン１３ａの構成部品に供給され、その
構成部品を冷却後、中高圧タービン１３ａの駆動蒸気に
合流させるか、あるいは再び高圧熱交換器１７に戻され
るかのいずれかが選択される。この選択は、計画時の熱
清算から決定される。高圧熱交換器１７を出た加熱蒸気
は、例えば６５０℃、８５０ata 程度の高圧タービン駆
動用蒸気となって高圧タービン１１に供給され、この高
圧タービン１１を駆動する。The hydrogen combustion turbine plant 10 is operated based on the TS diagram shown in FIG. The feedwater passing through the condensate feedwater system 19 is heated in multiple stages by feedwater heaters 23, 25, 26, and has a high temperature and high pressure (for example, 350 ° C., 370 at
The feedwater is subsequently superheated in the high-pressure heat exchanger 17 by the turbine exhaust from the medium-to-high-pressure turbine 13a to become superheated steam. At this time, a part of the steam during the superheating is supplied to the components of the medium and high pressure turbine 13a through the high pressure steam supply system for cooling 17 as cooling steam, and after cooling the components, the steam of the medium and high pressure turbine 13a is cooled. Either merging with the driving steam or returning again to the high-pressure heat exchanger 17 is selected. This choice is determined from the heat clearing at the time of planning. The heated steam exiting the high-pressure heat exchanger 17 is supplied to the high-pressure turbine 11 as high-pressure turbine driving steam at, for example, 650 ° C. and about 850 at, and drives the high-pressure turbine 11.
【００３１】高圧タービン１１で膨張し、仕事をしたタ
ービン排気は、例えば３８５℃、７５ata程度の排気蒸
気となって高圧水素燃焼器１５に供給される。このター
ビン排気は高圧水素燃焼器１５で水素と純酸素との当量
燃焼により温度上昇し、例えば１６００℃〜１７００℃
程度、７０ata程度の超高温蒸気となって中圧タービン
１３の中高圧タービン１３ａに導かれ、この中高圧ター
ビン１３ａを超高温蒸気で駆動させる。The turbine exhaust expanded and worked by the high-pressure turbine 11 is supplied to the high-pressure hydrogen combustor 15 as exhaust steam of, for example, 385 ° C. and about 75 ata. The temperature of this turbine exhaust rises due to the equivalent combustion of hydrogen and pure oxygen in the high-pressure hydrogen combustor 15, for example, 1600 ° C. to 1700 ° C.
Ultra high temperature steam of about 70 ata is guided to the medium pressure turbine 13a of the medium pressure turbine 13, and this medium high pressure turbine 13a is driven by the ultra high temperature steam.
【００３２】中高圧タービン１３ａで膨張し、仕事をし
た蒸気は、例えば１２５０°、１９ata 程度のタービン
排気となって高圧熱交換器１７に案内され、ここで上述
復水給水系１９からの給水を加熱して中高圧タービン１
３ａの構成部品の冷却用としての蒸気を生成する。給水
の加熱により温度降下したタービン排気は、例えば６０
０°程度の蒸気となって低圧水素燃焼器１６に案内さ
れ、ここで水素と純酸素の当量燃焼により、例えば１７
ata ，１７００°以上に再加熱され、過熱蒸気として中
低圧タービン１３ｂに供給され、中低圧タービン１３ｂ
を駆動させる。The steam that has expanded and worked in the medium-to-high pressure turbine 13a becomes turbine exhaust of, for example, about 1250 ° and 19 at, and is guided to the high pressure heat exchanger 17, where the water supplied from the condensate water supply system 19 is supplied. Heated and high pressure turbine 1
Generate steam for cooling the components of 3a. Turbine exhaust whose temperature has dropped due to heating of the feedwater is, for example, 60
The steam is guided to the low-pressure hydrogen combustor 16 in the form of steam of about 0 °.
ata, reheated to 1700 ° or more, supplied as superheated steam to the medium / low pressure turbine 13b,
Drive.
【００３３】中低圧タービン１３ｂで仕事をしたタービ
ン排気は、例えば１．１ata 、１０００°程度になって
低圧熱交換器１８に案内され、ここで復水給水系１９か
らの給水を加熱させる。タービン排気により加熱される
復水給水系１９からの給水に基づく蒸気は、その一部を
冷却用低圧蒸気供給系１８ａを介して中低圧タービン１
３ｂの構成部品を冷却し、冷却後、中低圧タービン１３
ｂの駆動蒸気に合流させるか、あるいは再び低圧熱交換
器１８に戻されるかのいずれかが選択される。この選択
は、計画時の熱清算により決定される。The turbine exhaust that has worked in the medium- and low-pressure turbine 13b is guided to the low-pressure heat exchanger 18 at, for example, about 1.1 ata and about 1000 °, where the water supplied from the condensate water supply system 19 is heated. A part of the steam based on the water supplied from the condensate water supply system 19 heated by the turbine exhaust is passed through the low-pressure steam supply system 18a for cooling.
3b, and after cooling, the medium and low pressure turbine 13
b is combined with the driving steam of b or returned to the low-pressure heat exchanger 18 again. This choice is determined by the heat clearing at the time of planning.
【００３４】中低圧タービン１３ｂのタービン排気によ
り過熱された復水給水系１９からの給水に基づく過熱蒸
気は、上述高圧熱交換器１７からの過熱蒸気と合流し、
その合流過熱蒸気で高圧タービン１１を駆動させる。The superheated steam based on the water supply from the condensate water supply system 19, which has been superheated by the turbine exhaust of the middle and low pressure turbine 13b, merges with the superheated steam from the high pressure heat exchanger 17 described above.
The high-pressure turbine 11 is driven by the combined superheated steam.
【００３５】また、復水給水系１９からの給水の加熱に
より昇温降下した中低圧タービン１３ｂからのタービン
排気は、低圧タービン１２に案内され、ここで再び膨張
仕事をさせる。各タービン１１，１２，１３の駆動によ
り発電機２０が回転駆動され、電気出力が得られる。低
圧タービン１２で仕事をした蒸気は、温度が１００°以
下、例えば５８℃でほぼ大気圧となって復水器２１に案
内され、この復水器２１で冷却され、復水となる。The turbine exhaust from the medium- and low-pressure turbine 13b whose temperature has been lowered by heating the feedwater from the condensate water supply system 19 is guided to the low-pressure turbine 12, where the work is expanded again. The generators 20 are rotationally driven by the driving of the turbines 11, 12, and 13, and an electric output is obtained. The steam that has worked in the low-pressure turbine 12 has a temperature of 100 ° C. or less, for example, 58 ° C., and becomes almost atmospheric pressure, is guided to the condenser 21, is cooled by the condenser 21, and is condensed.
【００３６】この復水は、復水給水系１９の各給水加熱
器２３，２５，２６を通る間に多段に加熱されるととも
に、復水ポンプ２２、給水ポンプ２８，２９で加圧さ
れ、高温（３５０℃程度）高圧（３７０ata 程度）とな
って高圧熱交換器１７、低圧熱交換器１８のそれぞれに
案内される。This condensate is heated in multiple stages while passing through the feed water heaters 23, 25 and 26 of the condensate water supply system 19, and is pressurized by the condensate pump 22, and the feed water pumps 28 and 29, and It becomes high pressure (about 350 ° C.) (about 370 ata) and is guided to each of the high-pressure heat exchanger 17 and the low-pressure heat exchanger 18.
【００３７】表１は、本実施形態に係る水素燃焼タービ
ンプラントと、ガスタービンプラントに蒸気タービンプ
ラントを組み合せ、ガスタービン燃焼器の燃料に、例え
ばＬＮＧ等の気体燃料を使用する従来のコンバインドサ
イクル発電プラントとを比較したものである。Table 1 shows a conventional combined cycle power generation using a hydrogen combustion turbine plant according to the present embodiment, a gas turbine plant combined with a steam turbine plant, and using gaseous fuel such as LNG as fuel for the gas turbine combustor. It is a comparison with a plant.
【００３８】[0038]
【表１】 [Table 1]
【００３９】本実施形態は、中高圧タービン１３ａの出
口側に高圧熱交換器１７を設ける一方、中低圧タービン
１３ｂの出口側に低圧熱交換器１８を設け、復水給水系
１９からの給水を高圧熱交換器１７および低圧熱交換器
１８のそれぞれに案内し、ここで生成される蒸気の一部
を各タービン１３ａ，１３ｂの構成部品の冷却用として
案内し、その構成部品を冷却後、各タービン１３ａ，１
３ｂの駆動蒸気に合流させるか、あるいは各熱交換器１
７，１８に戻すかのいずれかを選択しているので、各タ
ービン１３ａ，１３ｂの駆動蒸気の超高温化が図られ、
また冷却用の蒸気の適正な温度の選定化と相俟って効果
的な熱回収化が図られる。In the present embodiment, a high-pressure heat exchanger 17 is provided at the outlet side of the medium-to-high pressure turbine 13a, while a low-pressure heat exchanger 18 is provided at the outlet side of the medium-to-low pressure turbine 13b to supply water from the condensate water supply system 19. The steam is guided to each of the high-pressure heat exchanger 17 and the low-pressure heat exchanger 18, and a part of the steam generated here is guided for cooling the components of the turbines 13a and 13b. Turbine 13a, 1
3b or the heat exchanger 1
7 or 18, the drive steam for each of the turbines 13a and 13b is heated to an extremely high temperature.
Further, effective heat recovery can be achieved in combination with selection of an appropriate temperature of the cooling steam.
【００４０】したがって、表１からも認められるよう
に、本実施形態では、従来に較べプラント熱高率を大幅
に向上させることができる。Accordingly, as can be seen from Table 1, in the present embodiment, the heat rate of the plant can be greatly improved as compared with the conventional case.
【００４１】[0041]
【発明の効果】以上の説明の通り、本発明に係る水素燃
焼タービンプラントは、高圧タービンと低圧タービンと
の間に設けた少なくとも二段以上の中圧タービンの排気
側に熱交換器を少なくとも一つ以上を設置し、各熱交換
器に復水給水系の給水を案内し、各タービンの排気を加
熱源として、その給水から蒸気を生成せしめ、その蒸気
の一部を各タービンの構成部品の冷却用に供し、冷却後
の蒸気を各タービンの駆動蒸気に合流させるか、再び各
熱交換器に戻すかの選択を行なったので、各タービンの
構成部品の冷却化に伴う各タービンの駆動蒸気の超高温
化、冷却用の蒸気の効果的な熱回収化を図ることがで
き、従来に較べプラント熱効率の大幅な向上を図ること
ができる。As described above, in the hydrogen combustion turbine plant according to the present invention, at least one heat exchanger is provided on the exhaust side of at least two or more stages of the intermediate pressure turbine provided between the high pressure turbine and the low pressure turbine. More than one turbine, guide the condensate water supply to each heat exchanger, use the exhaust gas from each turbine as a heat source, generate steam from the water supply, and use a portion of the steam for the components of each turbine. Since the choice was made between cooling steam and merging the steam after cooling with the driving steam of each turbine or returning the steam to each heat exchanger again, the driving steam of each turbine accompanying the cooling of the components of each turbine was selected. It is possible to achieve an extremely high temperature and effective heat recovery of the cooling steam, and it is possible to greatly improve the thermal efficiency of the plant as compared with the related art.
【図１】本発明に係る水素燃焼タービンプラントの実施
形態を示す概略系統図。FIG. 1 is a schematic system diagram showing an embodiment of a hydrogen combustion turbine plant according to the present invention.
【図２】図１に示された水素燃焼タービンプラントに相
当するＴ−Ｓ線図。FIG. 2 is a TS diagram corresponding to the hydrogen combustion turbine plant shown in FIG.
【図３】従来の水素燃焼タービンプラントの実施形態を
示す概略系統図。FIG. 3 is a schematic system diagram showing an embodiment of a conventional hydrogen combustion turbine plant.
【図４】図３に示された水素燃焼タービンプラントに相
当するＴ−Ｓ線図。FIG. 4 is a TS diagram corresponding to the hydrogen combustion turbine plant shown in FIG. 3;
１ 高圧タービン ２ 低圧タービン ３ 中圧タービン ３ａ 中高圧タービン ３ｂ 中低圧タービン ４ａ 高圧水素燃焼器 ４ｂ 低圧水素燃焼器 ５ａ 第１熱交換器 ５ｂ 第２熱交換器 ６ 蒸気タービンプラント ６ａ 給水系 １０ 水素燃焼タービンプラント １１ 高圧タービン １２ 低圧タービン １３ 中圧タービン １３ａ 中高圧タービン １３ｂ 中低圧タービン １５ 高圧水素燃焼器 １６ 低圧水素燃焼器 １７ 高圧熱交換器 １７ａ 冷却用高圧蒸気供給源 １８ 低圧熱交換器 １８ａ 冷却用低圧蒸気供給源 １９ 復水給水系 ２０ 発電機 ２１ 復水器 ２２ 復水ポンプ ２３ 低圧給水加熱器 ２４ 脱気器 ２５ 中圧給水加熱器 ２６ 高圧給水加熱器 ２８，２９ 給水ポンプ Reference Signs List 1 high-pressure turbine 2 low-pressure turbine 3 medium-pressure turbine 3a medium-high-pressure turbine 3b medium-low-pressure turbine 4a high-pressure hydrogen combustor 4b low-pressure hydrogen combustor 5a first heat exchanger 5b second heat exchanger 6 steam turbine plant 6a water supply system 10 hydrogen combustion Turbine plant 11 High pressure turbine 12 Low pressure turbine 13 Medium pressure turbine 13a Medium high pressure turbine 13b Medium low pressure turbine 15 High pressure hydrogen combustor 16 Low pressure hydrogen combustor 17 High pressure heat exchanger 17a High pressure steam supply source 18 for cooling 18 Low pressure heat exchanger 18a For cooling Low-pressure steam supply source 19 Condensate feedwater system 20 Generator 21 Condenser 22 Condensate pump 23 Low-pressure feedwater heater 24 Deaerator 25 Medium-pressure feedwater heater 26 High-pressure feedwater heater 28, 29 Feedwater pump
Claims (3)
なくとも２段以上の中圧タービンを設け、各中圧タービ
ンの入口蒸気を、水素と純酸素とを当量燃焼させる水素
燃焼器により再加熱する水素燃焼タービンプラントにお
いて、上記中圧タービンの少なくとも一方にはタービン
排気側に熱交換器を設け、この熱交換器は復水給水系か
ら案内される給水を蒸気化させ、この蒸気の一部を上記
中圧タービンの構成部品に冷却用として供給する冷却用
蒸気供給系を備えたことを特徴とする水素燃焼タービン
プラント。At least two stages of intermediate-pressure turbines are provided between a high-pressure turbine and a low-pressure turbine, and inlet steam of each of the intermediate-pressure turbines is reheated by a hydrogen combustor for burning equivalent amounts of hydrogen and pure oxygen. In the hydrogen combustion turbine plant, at least one of the medium-pressure turbines is provided with a heat exchanger on the turbine exhaust side, and the heat exchanger vaporizes feed water guided from a condensate water supply system, and partially converts the steam. A hydrogen combustion turbine plant, comprising: a cooling steam supply system for supplying cooling components to the components of the intermediate pressure turbine.
ビンと中低圧タービンとを備え、上記中高圧タービンお
よび中低圧タービンへの入口蒸気をそれぞれ過熱する高
圧水素燃焼器および低圧水素燃焼器を設け、中高圧ター
ビンからのタービン排気側に高圧タービン駆動用蒸気を
発生させる高圧熱交換器を設ける一方、中低圧タービン
からのタービン排気側に、上記高圧熱交換器からの高圧
タービン駆動蒸気に合流させる低圧熱交換器を設け、上
記高圧熱交換器および低圧熱交換器のそれぞれで発生さ
せる蒸気の一部を上記中高圧タービンの構成部品および
中低圧タービンの構成部品のそれぞれに冷却用として供
給する冷却用高圧蒸気供給系と冷却用低圧蒸気供給系と
をそれぞれ備えたことを特徴とする請求項１記載の水素
燃焼タービンプラント。2. The medium-pressure turbine includes at least a medium-high-pressure turbine and a medium-low-pressure turbine, and includes a high-pressure hydrogen combustor and a low-pressure hydrogen combustor that superheat inlet steam to the medium-high-pressure turbine and the medium-low-pressure turbine, respectively. A high-pressure heat exchanger that generates high-pressure turbine driving steam is provided on the turbine exhaust side from the medium-high pressure turbine, while a low-pressure A cooling unit for providing a heat exchanger and supplying a part of steam generated in each of the high-pressure heat exchanger and the low-pressure heat exchanger to each of the components of the medium-high pressure turbine and the components of the medium-low pressure turbine for cooling The hydrogen combustion turbine plan according to claim 1, further comprising a high-pressure steam supply system and a low-pressure steam supply system for cooling. G.
タービンの構成部品に供給される冷却用の蒸気は、各構
成部品冷却後、上記中高圧タービンの駆動蒸気および中
低圧タービンの駆動蒸気のそれぞれに合流させるか、上
記高圧熱交換器および低圧熱交換器のそれぞれに回収さ
せるかいずれかを選択したことを特徴とする請求項２記
載の水素燃焼タービンプラント。3. The cooling steam supplied to the components of the medium-to-high pressure turbine and the components of the medium-to-low pressure turbine is, after cooling of each component, the driving steam of the medium-to-high pressure turbine and the driving steam of the medium-to-low pressure turbine, respectively. 3. The hydrogen combustion turbine plant according to claim 2, wherein either one of the two is selected, or the high-pressure heat exchanger and the low-pressure heat exchanger are collected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9107688A JP3059115B2 (en) | 1997-04-24 | 1997-04-24 | Hydrogen combustion turbine plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9107688A JP3059115B2 (en) | 1997-04-24 | 1997-04-24 | Hydrogen combustion turbine plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10299417A true JPH10299417A (en) | 1998-11-10 |
| JP3059115B2 JP3059115B2 (en) | 2000-07-04 |
Family
ID=14465455
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9107688A Expired - Fee Related JP3059115B2 (en) | 1997-04-24 | 1997-04-24 | Hydrogen combustion turbine plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3059115B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110234847A (en) * | 2017-02-03 | 2019-09-13 | 川崎重工业株式会社 | Hydrogen-oxygen equivalent combustion turbine system |
-
1997
- 1997-04-24 JP JP9107688A patent/JP3059115B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110234847A (en) * | 2017-02-03 | 2019-09-13 | 川崎重工业株式会社 | Hydrogen-oxygen equivalent combustion turbine system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3059115B2 (en) | 2000-07-04 |
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