JPH0275731A - Turbine plant - Google Patents
Turbine plantInfo
- Publication number
- JPH0275731A JPH0275731A JP22469888A JP22469888A JPH0275731A JP H0275731 A JPH0275731 A JP H0275731A JP 22469888 A JP22469888 A JP 22469888A JP 22469888 A JP22469888 A JP 22469888A JP H0275731 A JPH0275731 A JP H0275731A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- turbine
- cooling
- combustor
- air
- 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
- 238000001816 cooling Methods 0.000 claims abstract description 89
- 238000011084 recovery Methods 0.000 claims abstract description 28
- 239000007789 gas Substances 0.000 claims description 29
- 239000000446 fuel Substances 0.000 claims description 10
- 239000000567 combustion gas Substances 0.000 claims description 6
- 238000007789 sealing Methods 0.000 abstract description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 46
- 239000012530 fluid Substances 0.000 description 12
- 238000002485 combustion reaction Methods 0.000 description 4
- 239000002918 waste heat Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 230000005514 two-phase flow Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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
- F01K21/00—Steam engine plants not otherwise provided for
- F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
- F01K21/047—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas having at least one combustion gas turbine
-
- 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]
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、二流体タービンプラント、水素燃焼タービン
プラント、再生式ガスタービンプラント、圧縮酸素貯蔵
タービンプラント等のタービンプラントに関し、より詳
細にはそのタービン高温部を冷却する技術に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to turbine plants such as two-fluid turbine plants, hydrogen combustion turbine plants, regenerative gas turbine plants, compressed oxygen storage turbine plants, etc. Related to technology for cooling parts.
従来の技術
従来のタービンプラントとして、例えば第２図及び第３
図に示すようなものがある。2. Prior Art As a conventional turbine plant, for example, FIGS.
There is something like the one shown in the figure.
第２図に示すものはガスタービン−蒸気タービン複合方
式と呼ばれるもので、■がガスタービン（二流体タービ
ン）、２が蒸気タービンである。The system shown in FIG. 2 is called a gas turbine-steam turbine combined system, where ◯ indicates a gas turbine (two-fluid turbine), and 2 indicates a steam turbine.
ガスタービン１は、空気圧縮機３にて圧縮された空気と
燃料供給管４及び燃料制御弁５を通して送られてきた燃
料とを燃焼器６で燃焼させて得た燃焼ガスにより駆動さ
れる。そして、蒸気ター°ビン２は、このガスタービン
ｌから排気ダクト７を通して送られてくる排ガスの熱を
回収して蒸気を発生する貫流形の排熱回収蒸気発生器（
ボイラ）８からの蒸気により駆動される。The gas turbine 1 is driven by combustion gas obtained by burning air compressed by an air compressor 3 and fuel sent through a fuel supply pipe 4 and a fuel control valve 5 in a combustor 6. The steam turbine 2 is a once-through type exhaust heat recovery steam generator (
It is driven by steam from boiler 8.
なお、第２図において、９は吸込空気制御ダンパ、ｔＯ
，Ｕは発電機、１２は復水器、１３は給水管、１４は給
水ポンプ、１５は排ガスダクト、１６は煙突である。In addition, in FIG. 2, 9 is a suction air control damper, tO
, U is a generator, 12 is a condenser, 13 is a water supply pipe, 14 is a water supply pump, 15 is an exhaust gas duct, and 16 is a chimney.
これに対し、第３図に示すものは、蒸気投入ガスタービ
ン方式と呼ばれるもので、排熱回収蒸気発生器８にて発
生した蒸気が主蒸気管２１、蒸気制御弁２２及び投入蒸
気管２３を通して燃焼器６へ投入されるようになってい
る。そして、この発生蒸気の一部又は全部が、必要に応
じて補助蒸気管２４及び蒸気制御弁２５を通して系外へ
補助蒸気として供給できるようにもされている。On the other hand, the system shown in FIG. 3 is called a steam input gas turbine system, in which steam generated in the exhaust heat recovery steam generator 8 passes through the main steam pipe 21, the steam control valve 22, and the input steam pipe 23. It is designed to be input into the combustor 6. A part or all of this generated steam can be supplied outside the system as auxiliary steam through an auxiliary steam pipe 24 and a steam control valve 25 as needed.
なお、第３図において１１２６は給水タンクであり、ま
た第２図に示したものと同一の部分には同一の符号を付
しである。In addition, in FIG. 3, 1126 is a water supply tank, and the same parts as shown in FIG. 2 are given the same reference numerals.
しかして、第２図及び第３図に示した従来のタービンプ
ラントにおいて、°ガスタービン１の冷却及びシールは
空気圧縮機３にて圧縮した空気の一部を利用して行われ
、空気圧縮＃Ｉ３の中間段より抽気したタービン冷却及
びシール用の圧縮空気が管１７を通して燃焼器６をバイ
パスしてガスタービンＩへ導入され、タービン作動流体
１こ混入されるようになっている。Therefore, in the conventional turbine plants shown in FIGS. 2 and 3, cooling and sealing of the gas turbine 1 are performed using a part of the air compressed by the air compressor 3, and the air compressor # Compressed air for turbine cooling and sealing extracted from the intermediate stage of I3 is introduced into the gas turbine I through a pipe 17, bypassing the combustor 6, and is mixed with the turbine working fluid.
また、このようなタービン空気冷却方式の他に、従来技
術として、タービン翼を蒸気で冷却する方式もあり、そ
の冷却用の蒸気はタービン翼を冷却後タービン作動流体
に混入されるか、又は冷却凝縮されて回収されるように
なっている。In addition to this type of turbine air cooling system, there is also a conventional technology that cools turbine blades with steam, and the cooling steam is either mixed into the turbine working fluid after cooling the turbine blades, or It is condensed and collected.
発明が解決しようとする課題
以上述べた従来技術は、しかし、次のような問題点があ
った。Problems to be Solved by the Invention The prior art described above, however, has the following problems.
まず、第２図及び第３図に示したタービン空気冷却方式
においては、空気は熱輸送能力、それ故冷却能力が小さ
い（比熱が小さい、熱伝達性能が劣る）ので、メタル温
度の低下が難しく、したがってタービン入口温度を低く
抑えなければならず、よってタービンプラント効率が低
くなる。First, in the turbine air cooling system shown in Figures 2 and 3, air has a small heat transport capacity and therefore a small cooling capacity (low specific heat, poor heat transfer performance), so it is difficult to lower the metal temperature. , thus the turbine inlet temperature must be kept low, resulting in low turbine plant efficiency.
第４図に理解しやすいように、タービン圧力比を調整し
て同一排気温度条件で比較したタービン入口温度とエン
トロピとの関係の一例を示すが、タービン入口温度の高
い方が同一熱損失に対し仕事量が大きいことがわかるで
あろう。To make it easier to understand, Figure 4 shows an example of the relationship between the turbine inlet temperature and entropy when the turbine pressure ratio is adjusted and compared under the same exhaust temperature condition. You can see that the amount of work is large.
タービン空気冷却方式は、また、その冷却空気量が一般
に空気圧縮機出口空気量のおおよそ３０％にも及ぶため
、空気圧縮機の動力が大きくなり、しｔこがってタービ
ンプラント出力が低くなる。In the turbine air cooling method, the amount of cooling air is generally approximately 30% of the air amount at the outlet of the air compressor, so the power of the air compressor increases, which in turn reduces the turbine plant output. .
一方、従来のタービン蒸気冷却方式は、タービンを蒸気
で冷却するので、タービン入口温度を上昇することがで
きるとともに、空気圧縮機の動力を低減することができ
、したがってタービンプラント効率を向上することがで
きる。On the other hand, the conventional turbine steam cooling method cools the turbine with steam, which can increase the turbine inlet temperature and reduce the power of the air compressor, thus improving the turbine plant efficiency. can.
しかし、この冷却用の蒸気をタービン冷却後作動流体に
混入したり、又は凝縮回収する場合、タービン排気損失
が増大し・たり、又は凝縮熱損失となり、したがってタ
ービン入口温度の上昇及び空気圧縮機の動力低減による
タービンプラント効率の向上のメリットが相殺されるこ
とになる。However, when this cooling steam is mixed into the working fluid after cooling the turbine or is condensed and recovered, the turbine exhaust loss increases or condensation heat loss occurs, resulting in an increase in the turbine inlet temperature and the air compressor. The benefits of improved turbine plant efficiency due to reduced power will be offset.
課題を解決するための手段
本発明によるタービンプラントは、このような従来技術
の課題を解決するために、空気圧縮機と、この空気圧縮
機にて圧縮された空気と燃料とが導入されて燃焼する燃
焼器と、この燃焼器からの燃焼ガスで駆動するタービン
と、このタービンからの排ガスの熱を利用する排熱回収
蒸気発生器と、この排熱回収蒸気発生器にて発生した蒸
気を前記燃焼器と前記タービンの蒸気冷却部とへ送給す
る第１の蒸気流路と、前記タービンの蒸気冷却部下流と
前記第１の蒸気流路における燃焼器への蒸気送給流路と
を接続する第２の蒸気流路とを具備してなる。Means for Solving the Problems In order to solve the problems of the prior art, the turbine plant according to the present invention includes an air compressor, and air and fuel compressed by the air compressor are introduced to perform combustion. a combustor, a turbine driven by combustion gas from the combustor, an exhaust heat recovery steam generator that utilizes the heat of exhaust gas from the turbine, and a steam generator that uses the steam generated by the exhaust heat recovery steam generator to A first steam flow path that supplies steam to a combustor and a steam cooling section of the turbine, and a steam supply flow path that connects downstream of the steam cooling section of the turbine and the first steam flow path to the combustor. and a second steam flow path.
作用
このようなタービンプラントにおいては、したがって、
排熱回収蒸気発生器にて発生した蒸気の一部が、タービ
ンの蒸気冷却部へ送給されてタービンを冷却し、その後
排熱回収蒸気発生器にて発生した残りの蒸気と一緒に燃
焼器へ投入され、これによりタービンプラント効率を上
昇することができる。In such a turbine plant, therefore:
A part of the steam generated in the heat recovery steam generator is sent to the steam cooling section of the turbine to cool the turbine, and then sent to the combustor together with the remaining steam generated in the heat recovery steam generator. This can increase the efficiency of the turbine plant.
実施例
以下第１図を参照して本発明の一実施例について詳述す
る。なお、第１図において、第２図及び第３図に示した
ものと同一の部分には同一の符号を付して、その詳細な
説明は省略する。EXAMPLE Hereinafter, an example of the present invention will be described in detail with reference to FIG. In FIG. 1, the same parts as those shown in FIGS. 2 and 3 are given the same reference numerals, and detailed explanation thereof will be omitted.
しかして、本実施例によれば、排熱回収蒸気発生器８に
て発生した蒸気を燃焼器６側へ送給する主蒸気管２１に
おける燃焼器投入蒸気制御弁２２上流側部分からタービ
ン冷却蒸気供給管３１が分岐されて、ガスタービンｌの
高温部タービン翼等の蒸気冷却部３２へ接続され、この
蒸気供給管３１の途中にはタービン冷却蒸気制御弁３３
が設けられている。According to this embodiment, the turbine cooling steam is supplied from the upstream portion of the combustor input steam control valve 22 in the main steam pipe 21 that supplies the steam generated in the exhaust heat recovery steam generator 8 to the combustor 6 side. The supply pipe 31 is branched and connected to a steam cooling part 32 such as a high-temperature turbine blade of the gas turbine l, and a turbine cooling steam control valve 33 is installed in the middle of the steam supply pipe 31.
is provided.
また、ガスタービン１の蒸気冷却部３２下流と燃焼器投
入蒸気管２３とを接続するタービン冷却蒸気戻り管３４
が設けられている。そして、タービン冷却蒸気供給管３
１を流れる蒸気とタービン冷却蒸気戻り管３４を流れる
蒸気との温度差を検出して、燃焼器投入蒸気制御弁２２
を制御し、これによりかかる温度差が所定の値となるよ
うにする温度差制御器３５が設けられている。Additionally, a turbine cooling steam return pipe 34 connects the downstream side of the steam cooling section 32 of the gas turbine 1 and the combustor input steam pipe 23.
is provided. And the turbine cooling steam supply pipe 3
The temperature difference between the steam flowing through the combustor input steam control valve 22 and the steam flowing through the turbine cooling steam return pipe 34 is detected.
A temperature difference controller 35 is provided to control the temperature difference so that the temperature difference becomes a predetermined value.
更に、前述したタービン冷却蒸気供給管３１におけるタ
ービン冷却蒸気制御弁３３下流側部分には、タービン冷
却・シール空気管１７から分岐されたタービン冷却空気
管３６が接続され、その途中にはタービン冷却空気制御
弁３７が設けられている。Further, a turbine cooling air pipe 36 branched from the turbine cooling/sealing air pipe 17 is connected to the downstream portion of the turbine cooling steam control valve 33 in the turbine cooling steam supply pipe 31 described above, and a turbine cooling air pipe 36 is connected to the turbine cooling air pipe 36 branched from the turbine cooling/sealing air pipe 17. A control valve 37 is provided.
一方、排熱回収蒸気発生器８と主蒸気管２１との間には
気水分離器４１が設けられ、その分離水管４２は燃焼器
６へ接続され、その途中には燃焼器投入分離水制御弁４
３が設けられている。また、この燃焼器投入分離水管４
２から分岐された分離水管４４が給水タンク２６へ接続
され、その途中には給水タンク回収分離水制御弁４５が
設けられている。On the other hand, a steam/water separator 41 is provided between the exhaust heat recovery steam generator 8 and the main steam pipe 21, and the separated water pipe 42 is connected to the combustor 6. valve 4
3 is provided. In addition, this combustor input separation water pipe 4
A separated water pipe 44 branched from 2 is connected to the water supply tank 26, and a water supply tank recovery separated water control valve 45 is provided in the middle thereof.
そして、給水タンク２６には給水管４６が接続され、そ
の途中には水位制御器４７により制御される水位制御弁
４８が設けられている。また、給水タンク２６と排熱回
収蒸気発生器７の伝熱管４９とを接続する給水管１３の
途中には、蒸気温度制御器５１により制御される給水制
御弁５２が設けられている。A water supply pipe 46 is connected to the water supply tank 26, and a water level control valve 48 controlled by a water level controller 47 is provided in the middle thereof. Further, a water supply control valve 52 controlled by a steam temperature controller 51 is provided in the middle of the water supply pipe 13 that connects the water supply tank 26 and the heat transfer tube 49 of the waste heat recovery steam generator 7 .
次に、作用について説明する。Next, the effect will be explained.
吸込空気制御ダンパ９により制御されて空気圧縮機３に
導入された燃焼用空気はこの空気圧縮機３にて圧縮され
、その大部分は燃焼器６に供給されるが、その一部分は
中間段から油気され、タービン冷却・シール空気管１７
とタービン冷却空気管３６、タービン冷却空気制御弁３
７及びタービン冷却蒸気供給管３１の一部とを通してガ
スタービンｌへ供給される。Combustion air controlled by the intake air control damper 9 and introduced into the air compressor 3 is compressed by the air compressor 3, and most of it is supplied to the combustor 6, but a part of it is supplied from the intermediate stage. Oiled, turbine cooling and sealing air pipe 17
and turbine cooling air pipe 36, turbine cooling air control valve 3
7 and a part of the turbine cooling steam supply pipe 31 to the gas turbine l.
おいて、排熱回収蒸気発生器８にて蒸気を発生させター
ビン冷却蒸気供給管３１を通してガスタービンｌの蒸気
冷却部３２へ供給するタービン冷却蒸気量が必要量確保
されるまで行われる。そして、この必要量のタービン冷
却蒸気が確保されると、タービン冷却空気制御弁３７が
閉じられ、タービン冷却蒸気供給管３１を通しての蒸気
冷却方式に切替えられる。そして、その後は、タービン
冷却・シール空気管１７を通してはタービンの高温部以
外の部分（低温部）の冷却及びタービンシールのための
空気のみがガスタービン１へ供給される。Steam is generated in the exhaust heat recovery steam generator 8 and supplied to the steam cooling section 32 of the gas turbine I through the turbine cooling steam supply pipe 31 until the required amount of turbine cooling steam is secured. When this required amount of turbine cooling steam is secured, the turbine cooling air control valve 37 is closed, and the system is switched to a steam cooling method through the turbine cooling steam supply pipe 31. Thereafter, only air for cooling parts other than the high temperature part (low temperature part) of the turbine and for turbine sealing is supplied to the gas turbine 1 through the turbine cooling/sealing air pipe 17.
一方、燃料は、燃料供給管４及び燃料制御弁５を通して
燃焼器６に供給され、前述した圧縮空気とともに燃焼す
る。この燃焼器６には、排熱回収蒸気発生器８にて発生
した蒸気の大部分が気水分離器４１、主蒸気管２１、燃
焼器投入蒸気制御弁２２及び燃焼器投入蒸気管２３を通
して供給される。On the other hand, fuel is supplied to the combustor 6 through the fuel supply pipe 4 and the fuel control valve 5, and is combusted together with the aforementioned compressed air. Most of the steam generated in the exhaust heat recovery steam generator 8 is supplied to the combustor 6 through a steam separator 41, a main steam pipe 21, a combustor input steam control valve 22, and a combustor input steam pipe 23. be done.
定常運転時は、後述するように、排熱回収蒸気発生器８
は最高温度で最大蒸気量が得られるように運転されてお
り、その発生蒸気中の一部がタービン冷却用に使用され
るが、起動時及び低負荷時にはこれを含めて全量が燃焼
器６に投入される。During steady operation, as described later, the exhaust heat recovery steam generator 8
is operated to obtain the maximum amount of steam at the highest temperature, and a portion of the generated steam is used for cooling the turbine, but the entire amount, including this, is sent to the combustor 6 at startup and at low loads. Injected.
そしてガスタービンｌは、この運転状態で、タービン入
口温度を定格温度で運転した時定格出力となるように設
計される。In this operating state, the gas turbine 1 is designed so that the rated output is achieved when the turbine inlet temperature is operated at the rated temperature.
ガスタービン（二流体タービン）１に流入した燃焼ガス
と蒸気との混合二流体ガスは、このガスタービンｌで略
大気圧まで膨張し、仕事をした後、排気ダクト７を通し
て排熱回収蒸気発生器８に導入される。The mixed two-fluid gas of combustion gas and steam that has flowed into the gas turbine (two-fluid turbine) 1 is expanded to approximately atmospheric pressure in the gas turbine 1, and after doing work, is passed through the exhaust duct 7 to the exhaust heat recovery steam generator. 8 will be introduced.
この排熱回収蒸気発生器８の伝熱管４９の面積（伝熱面
積）は、定格負荷時最高温度Ｔｓｏ ’すなわち”Ｓｏ
”ＴＴＥ−α（ＴＴＥニガスタービン排気温度、α：
最少終端温度差）の蒸気を最大量発生するように設計さ
れている。The area (heat transfer area) of the heat transfer tube 49 of this waste heat recovery steam generator 8 is the maximum temperature Tso' at rated load, that is, "So
"TTE-α (TTE gas turbine exhaust temperature, α:
It is designed to generate the maximum amount of steam with a minimum terminal temperature difference).
排熱回収蒸気発生器８で熱回収された二流体ガスは、そ
れから、排ガスダクト１５を経て煙突１６から大気中へ
放出される。The two-fluid gas whose heat has been recovered by the exhaust heat recovery steam generator 8 is then discharged into the atmosphere from the chimney 16 via the exhaust gas duct 15.
加を要する場合には、制御弁４３にて流量を制御されな
がら、分離水管４２を通して燃焼器６に投入される。し
かし、通常運転時には、分離水は管４４を通して給水タ
ンク２６へ回収される。If additional water is required, the water is introduced into the combustor 6 through the separation water pipe 42 while the flow rate is controlled by the control valve 43. However, during normal operation, separated water is collected through pipe 44 to water tank 26.
他方、前述した主蒸気管２１を通して供給される蒸気の
一部は蒸気管２３を通して燃焼器６に投入され、また残
りの蒸気はタービン冷却蒸気供給管３１を通してガスタ
ービン１の蒸気冷却部３２へ供給され、冷却後タービン
冷却蒸気戻り管３４を経て燃焼器投入蒸気管２３へ導入
される。On the other hand, a part of the steam supplied through the main steam pipe 21 mentioned above is input to the combustor 6 through the steam pipe 23, and the remaining steam is supplied to the steam cooling section 32 of the gas turbine 1 through the turbine cooling steam supply pipe 31. After cooling, the steam is introduced into the combustor input steam pipe 23 via the turbine cooling steam return pipe 34.
この場合、ガスタービンｌの蒸気冷却部３２へ供給され
る蒸気量が必要量確保されるように、タービン冷却蒸気
戻り管３４を流れる蒸気の温度とタービン冷却蒸気供給
管３１を流れる蒸気の温度との差が所定の温度差となる
ように、温度差制御器３５により燃焼器投入蒸気制御弁
２２が制御される。そして、この制御弁２２と連動して
、制御弁３３がタービン冷却蒸気量を制御する。In this case, the temperature of the steam flowing through the turbine cooling steam return pipe 34 and the temperature of the steam flowing through the turbine cooling steam supply pipe 31 are adjusted so that the required amount of steam is supplied to the steam cooling section 32 of the gas turbine l. The combustor input steam control valve 22 is controlled by the temperature difference controller 35 so that the difference in temperature becomes a predetermined temperature difference. In conjunction with this control valve 22, a control valve 33 controls the amount of turbine cooling steam.
蒸気管２３を通しての燃焼器６への蒸気投入は空気流路
部、燃料ノズル周囲及び内筒を通して３段この場合、図
示していないが、排ガスダクト１５の途中に排ガス凝縮
器を設けて、燃焼器投入蒸気を凝縮回収し、この回収水
を水処理して排熱回収蒸気発生器８の給水として使用す
ることもできる。Steam is introduced into the combustor 6 through the steam pipe 23 in three stages through the air flow path, around the fuel nozzle, and through the inner cylinder. It is also possible to condense and recover the steam input into the reactor, treat the recovered water, and use it as feed water for the exhaust heat recovery steam generator 8.
一方、給水タンク２６には系外から給水管４６を通して
水が供給され、そのタンク内水位は水位制御器４７及び
水位制御弁４８の手段により一定に保たれるように制御
される。On the other hand, water is supplied to the water tank 26 from outside the system through a water supply pipe 46, and the water level in the tank is controlled to be kept constant by means of a water level controller 47 and a water level control valve 48.
この給水タンク２６内の給水は、給水ポンプ１４により
給水管１３を通して排熱回収蒸気発生器８の伝熱管４９
に供給される。その給水量は、蒸気温度制御器５１及び
給水制御弁５２の手段により、蒸気発生器出口蒸気の温
度が前述した最高温度となるように制御される。The water in the water supply tank 26 is supplied to the heat transfer pipe 49 of the waste heat recovery steam generator 8 through the water supply pipe 13 by the water supply pump 14.
is supplied to The amount of water supplied is controlled by the steam temperature controller 51 and the water supply control valve 52 so that the temperature of the steam at the steam generator outlet reaches the maximum temperature described above.
低負荷時等においては、給水量は最低給水量に維持され
て、蒸気発生器出口蒸気が二相流となる場合があるが、
この二相流は気水分離器４１にて蒸気と水とに分離され
、蒸気は主蒸気管２１に供給される。At times of low load, etc., the water supply amount is maintained at the minimum water supply amount, and the steam at the steam generator outlet may become a two-phase flow.
This two-phase flow is separated into steam and water by a steam separator 41, and the steam is supplied to the main steam pipe 21.
これに対し、分離水は、ガスタービン出力の増階で行わ
れ、これにより内筒の冷却、ＮＯｘの低減及び安定燃焼
が確保される。そして、燃焼器６に投入された蒸気は燃
焼ガスと一様に混合して、燃焼ガスと水蒸気との混合二
流体となって、ガスタービン１に導入される。On the other hand, separated water is generated by increasing the gas turbine output, thereby ensuring cooling of the inner cylinder, reduction of NOx, and stable combustion. The steam input into the combustor 6 is uniformly mixed with combustion gas to become a two-fluid mixture of combustion gas and steam, which is introduced into the gas turbine 1.
なお、変形例として、タービン冷却蒸気戻り管３４を、
燃焼器投入蒸気管２３の途中部分に接続しないで、燃焼
器６に直接接続することもできる。In addition, as a modified example, the turbine cooling steam return pipe 34 is
It is also possible to connect directly to the combustor 6 without connecting to the middle part of the combustor input steam pipe 23.
発明の効果
以上述べた如く、本発明によれば、排熱回収蒸気発生器
にて発生した蒸気の一部を利用して、ガスタービンの高
温部例えば１段翼を冷却するようにしているが、蒸気は
空気よりも熱容量が太き（て伝熱性能が優れ、それ故冷
却能力に優れているので、メタル温度を効果的に低減す
ることができ、よってタービン入口温度を上昇させて、
タービン排気温度が適度になるような圧力比の設計とす
ることにより、タービンプラント効率を大巾に向上させ
ることができる。Effects of the Invention As described above, according to the present invention, a part of the steam generated in the exhaust heat recovery steam generator is used to cool the high temperature part of the gas turbine, such as the first stage blade. , steam has a larger heat capacity than air (and has better heat transfer performance and therefore better cooling capacity), so it can effectively reduce the metal temperature, thus increasing the turbine inlet temperature,
By designing the pressure ratio so that the turbine exhaust temperature is moderate, the efficiency of the turbine plant can be greatly improved.
そして、本発明によれば、このガスタービンの高温部を
冷却した後の蒸気を燃焼器に投入して、高温のタービン
作動流体とし、排熱回収蒸気発生器から燃焼器に直接投
入した蒸気と同じ仕事をさせるので、タービンプラント
効率を一層上昇させることができる。According to the present invention, the steam after cooling the high-temperature section of the gas turbine is input into the combustor and used as a high-temperature turbine working fluid. Since the same work is done, the efficiency of the turbine plant can be further increased.
すなわち、排熱回収蒸気発生器における発生蒸気量をＷ
８４、この蒸気発生器から燃焼器に直接投入される蒸気
量をＷ タービン冷却蒸気量をＳＣ２
胃 とすると、”Ｓｔ ” ”ＳＣ＋’ＳＢとなる。In other words, the amount of steam generated in the exhaust heat recovery steam generator is W
84. If the amount of steam directly input from the steam generator to the combustor is W and the amount of steam for cooling the turbine is SC2, then "St""SC+'SB" is obtained.
Ｂ
また、燃焼器出口水蒸気のエンタルピをｉＳｔ １蒸気
発生器出口蒸気のエンタルピを、ｉＳＧ、タービン冷却
蒸気のエンタルピをＩｓＢ ｓタービン排気中の水蒸気
のエンタルピをｉＳＥとすると、タービン冷却蒸気を燃
焼器に投入しない場合の蒸気の仕事効率は、次の（１）
式で表わされる。B Also, the enthalpy of the steam at the combustor outlet is iSt, 1 the enthalpy of the steam at the steam generator outlet is iSG, and the enthalpy of the turbine cooling steam is IsB. The work efficiency of steam without input is as follows (1)
It is expressed by the formula.
一方、タービン冷却蒸気もタービン冷却後燃焼器に投入
する場合、タービン冷却蒸気はタービン冷却後タービン
入口温度まで加熱されてタービン作動流体となるので、
燃焼器投入蒸気の仕事効率は、タービン冷却後の戻り蒸
気のエンタルピをｉ’ｓＢとすると、次の（２）式で表
わされる。On the other hand, when turbine cooling steam is also input into the combustor after cooling the turbine, the turbine cooling steam is heated to the turbine inlet temperature after cooling the turbine and becomes the turbine working fluid.
The work efficiency of the steam input to the combustor is expressed by the following equation (2), where i'sB is the enthalpy of the return steam after cooling the turbine.
（１ｓｔ−’Ｓｔ ＋ １ＳＢ−ｖｓＢ＋ （ｉｓｔ
−ｉ’ＳＢ）そして、（１）式と（２）式とを比較する
と、１ｓｔ−ｉ’ｓＢ＞ ０であることから、（り式〈
（２）式となる。すなわち、タービン冷却蒸気をタービ
ン冷却後燃焼器に投入することにより、タービンプラン
ト効率を改善することができる。(1st-'St + 1SB-vsB+ (ist
-i'SB) Then, when comparing equations (1) and (2), since 1st-i'sB>0,
The equation (2) is obtained. That is, by injecting the turbine cooling steam into the combustor after cooling the turbine, the efficiency of the turbine plant can be improved.
しかも、このように排熱回収蒸気発生器にて発生した蒸
気を燃焼器に直接投入するに加えて、タービン冷却蒸気
をタービン冷却後燃焼器に投入して、燃焼器投入蒸気量
を増大することにより、空気量を減少して、空気圧縮機
の動力を減少し、したがってタービンプラント出力を増
加することができるとともに、ＮＯｘの発生量を低減す
ることができる。Moreover, in addition to directly injecting the steam generated in the waste heat recovery steam generator into the combustor, turbine cooling steam is injected into the combustor after cooling the turbine to increase the amount of steam input into the combustor. This allows the amount of air to be reduced, reducing the power of the air compressor and thus increasing the turbine plant output, as well as reducing the amount of NOx produced.
また、前述した実施例によれば、次のような効果もある
。Further, according to the above-mentioned embodiment, there are also the following effects.
すなわち、タービン冷却蒸気をタービン冷却後燃焼器に
投入する場合において、タービン冷却蒸気量を確実に供
給する必要があるが、タービン冷却蒸気の冷却前後の温
度差を監視し、これに基づき燃焼器投入蒸気量を制御す
ることにより、最適量のタービン冷却蒸気量を確保でき
、これによりタービンプラントの信頼性の向上と効率の
向上とを図ることができる。In other words, when introducing turbine cooling steam into the combustor after cooling the turbine, it is necessary to reliably supply the amount of turbine cooling steam, but the temperature difference before and after cooling the turbine cooling steam is monitored and the combustor injection is performed based on this. By controlling the amount of steam, an optimal amount of turbine cooling steam can be ensured, thereby improving the reliability and efficiency of the turbine plant.
また、圧力比の高い設計では、タービン排気温度が低く
なるため、排熱回収蒸気発生器における発生蒸気温度が
低く、二相流となるが、この場合この発生蒸気量だけで
はタービン作動流体が不足してタービン入口温度の制御
ができなくなる。このような場合、気水分離器で蒸気か
ら分離された飽和水を燃焼器に投入することにより、空
気量を過剰とする方式に比べて高効率で大出力が得られ
る。In addition, in a design with a high pressure ratio, the turbine exhaust temperature is low, so the temperature of the steam generated in the heat recovery steam generator is low, resulting in a two-phase flow, but in this case, the amount of steam generated is insufficient for the turbine working fluid. This makes it impossible to control the turbine inlet temperature. In such a case, by injecting saturated water separated from steam in a steam-water separator into the combustor, higher efficiency and greater output can be obtained than in a system in which the amount of air is excessive.
第１図は本発明によるタービンプラントの一例を示す系
統図、第２図及び第３図は従来のタービンプラントの異
なる二例を示す系統図、第４図は図である。
■・・ガスタービン、３・・空気圧縮機、４・・燃料供
給管、６・・燃焼器、８・・排熱回収蒸気発生器、１７
・・タービン冷却・シール空気管、２１・・主蒸気管、
２３・・燃焼器投入蒸気管、２４・・補助蒸気管、２６
・・給水タンク、３１・・タービン冷却蒸気供給管、３
２・・タービンの蒸気冷却部、３４・・タービン冷却蒸
気戻し管、３５・・温度差制御器、３６・・タービン冷
却空気管、４１・・気水分離器、４２・・燃焼器投入分
離水管、４４・・給水り（ほか１名）FIG. 1 is a system diagram showing an example of a turbine plant according to the present invention, FIGS. 2 and 3 are system diagrams showing two different examples of conventional turbine plants, and FIG. 4 is a diagram. ■...Gas turbine, 3...Air compressor, 4...Fuel supply pipe, 6...Combustor, 8...Exhaust heat recovery steam generator, 17
...Turbine cooling/sealing air pipe, 21...Main steam pipe,
23...Combustor input steam pipe, 24...Auxiliary steam pipe, 26
... Water supply tank, 31 ... Turbine cooling steam supply pipe, 3
2... Turbine steam cooling section, 34... Turbine cooling steam return pipe, 35... Temperature difference controller, 36... Turbine cooling air pipe, 41... Steam water separator, 42... Combustor input separation water pipe , 44...Water supply (1 other person)
Claims (1)
料とが導入されて燃焼する燃焼器と、この燃焼器からの
燃焼ガスで駆動するタービンと、このタービンからの排
ガスの熱を利用する排熱回収蒸気発生器と、この排熱回
収蒸気発生器にて発生した蒸気を前記燃焼器と前記ター
ビンの蒸気冷却部とへ送給する第１の蒸気流路と、前記
タービンの蒸気冷却部下流と前記第１の蒸気流路におけ
る燃焼器への蒸気送給流路とを接続する第２の蒸気流路
とを具備してなるタービンプラント。An air compressor, a combustor into which the air and fuel compressed by the air compressor are introduced and combusted, a turbine that is driven by the combustion gas from the combustor, and the heat of the exhaust gas from the turbine is used. a first steam flow path for delivering steam generated in the exhaust heat recovery steam generator to the combustor and the steam cooling section of the turbine; A turbine plant comprising: a second steam flow path connecting a downstream portion of the steam flow path to a steam supply flow path to a combustor in the first steam flow path.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63224698A JP2544453B2 (en) | 1988-09-09 | 1988-09-09 | Turbin plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63224698A JP2544453B2 (en) | 1988-09-09 | 1988-09-09 | Turbin plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0275731A true JPH0275731A (en) | 1990-03-15 |
| JP2544453B2 JP2544453B2 (en) | 1996-10-16 |
Family
ID=16817839
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63224698A Expired - Lifetime JP2544453B2 (en) | 1988-09-09 | 1988-09-09 | Turbin plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2544453B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0396628A (en) * | 1989-07-28 | 1991-04-22 | General Electric Co <Ge> | Cooling gas turbine engine by steam |
| JP2010077930A (en) * | 2008-09-26 | 2010-04-08 | Toyota Motor Corp | Bleed type gas turbine engine |
| WO2020003708A1 (en) * | 2018-06-29 | 2020-01-02 | 三菱日立パワーシステムズ株式会社 | Combined power generation facility and operation method thereof |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1041261A4 (en) * | 1997-12-15 | 2003-07-16 | Hitachi Ltd | Gas turbine for power generation, and combined power generation system |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS506910A (en) * | 1973-05-24 | 1975-01-24 | ||
| JPS6267239A (en) * | 1985-09-20 | 1987-03-26 | Toyo Eng Corp | Power generating method for gas turbine |
-
1988
- 1988-09-09 JP JP63224698A patent/JP2544453B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS506910A (en) * | 1973-05-24 | 1975-01-24 | ||
| JPS6267239A (en) * | 1985-09-20 | 1987-03-26 | Toyo Eng Corp | Power generating method for gas turbine |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0396628A (en) * | 1989-07-28 | 1991-04-22 | General Electric Co <Ge> | Cooling gas turbine engine by steam |
| JP2010077930A (en) * | 2008-09-26 | 2010-04-08 | Toyota Motor Corp | Bleed type gas turbine engine |
| WO2020003708A1 (en) * | 2018-06-29 | 2020-01-02 | 三菱日立パワーシステムズ株式会社 | Combined power generation facility and operation method thereof |
| JP2020002895A (en) * | 2018-06-29 | 2020-01-09 | 三菱日立パワーシステムズ株式会社 | Combined-cycle power generation facility and operation method therefor |
| CN112334636A (en) * | 2018-06-29 | 2021-02-05 | 三菱动力株式会社 | Composite power generation facility and method for operating same |
| CN112334636B (en) * | 2018-06-29 | 2022-10-28 | 三菱重工业株式会社 | Composite power generation facility and method for operating same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2544453B2 (en) | 1996-10-16 |
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