JPH06221503A - Waste heat recovery heat exchanger - Google Patents
Waste heat recovery heat exchangerInfo
- Publication number
- JPH06221503A JPH06221503A JP2620893A JP2620893A JPH06221503A JP H06221503 A JPH06221503 A JP H06221503A JP 2620893 A JP2620893 A JP 2620893A JP 2620893 A JP2620893 A JP 2620893A JP H06221503 A JPH06221503 A JP H06221503A
- Authority
- JP
- Japan
- Prior art keywords
- heat transfer
- heat
- power generation
- heat exchanger
- steam
- 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.)
- Pending
Links
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- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、排熱回収熱交換器に関
するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust heat recovery heat exchanger.
【０００２】[0002]
【従来の技術】現在、ボイラ発電設備とガスタービン発
電設備とを並設することにより、設備全体としての出力
増大を図ると共に、ガスタービン発電設備で発生した排
ガスの熱を利用してボイラ発電設備の蒸気を過熱させる
ことにより、設備全体としての熱効率向上を図るように
した複合発電設備が検討されている。2. Description of the Related Art At present, by installing a boiler power generation facility and a gas turbine power generation facility in parallel, the output of the entire facility is increased and the heat of exhaust gas generated in the gas turbine power generation facility is used to make the boiler power generation facility. Combined power generation equipment is being studied to improve the thermal efficiency of the entire equipment by overheating the steam of.
【０００３】図２は、現在検討中の複合発電設備を示し
ており、図中、１はボイラ発電設備、２はガスタービン
発電設備、３は排熱回収熱交換器である。FIG. 2 shows a combined power generation facility under consideration. In the figure, 1 is a boiler power generation facility, 2 is a gas turbine power generation facility, and 3 is an exhaust heat recovery heat exchanger.
【０００４】そして、上記ボイラ発電設備１では、復水
器４に溜まったボイラ水５を復水ポンプ６で低圧給水加
熱器７へ送り、低圧給水加熱器７で後述する蒸気タービ
ン１７，２０からの蒸気（いわゆるタービン抽気８）に
より加熱し、脱気器９で脱気した後、給水ポンプ１０で
高圧化して高圧給水加熱器１１へ送り、高圧給水加熱器
１１で前記タービン抽気８によって更に加熱して、ボイ
ラ本体１２へと送る。In the boiler power generation facility 1, the boiler water 5 collected in the condenser 4 is sent to the low-pressure feed water heater 7 by the condensate pump 6, and the low-pressure feed water heater 7 is used by the steam turbines 17 and 20 to be described later. After being deaerated by the deaerator 9, it is pressurized to a high pressure by the feed water pump 10 and sent to the high pressure feed water heater 11, which is further heated by the turbine bleed air 8 by the high pressure feed water heater 11. Then, it is sent to the boiler body 12.
【０００５】ボイラ本体１２へ送られたボイラ水５は、
節炭器１３、蒸発器１４で加熱・蒸発され、図示しない
気水分離器で気水分離された後、分離された蒸気１５が
過熱器１６で過熱され、高圧蒸気タービン１７へ送られ
て、発電機１８を駆動するのに用いられる。The boiler water 5 sent to the boiler body 12 is
After being heated / evaporated by the economizer 13 and the evaporator 14 and separated by the steam separator (not shown), the separated steam 15 is superheated by the superheater 16 and sent to the high-pressure steam turbine 17, It is used to drive the generator 18.
【０００６】高圧蒸気タービン１７を駆動した蒸気１５
は、再び、ボイラ本体１２の再熱器１９へ送られ、再熱
器１９で再過熱された後、低圧蒸気タービン２０へ送ら
れ、発電機１８の駆動に利用された後、前記復水器４へ
送られ、復水器４で凝縮されてボイラ水５とされる。Steam 15 that drives the high-pressure steam turbine 17
Is again sent to the reheater 19 of the boiler body 12, is reheated by the reheater 19, is sent to the low-pressure steam turbine 20, is used to drive the generator 18, and is then returned to the condenser. 4 and is condensed in the condenser 4 to be boiler water 5.
【０００７】一方、前記ガスタービン発電設備２で発生
された排ガス２１は、排ガスダクト２２を介して煙突２
３へと送られて、煙突２３から大気へ放出される。On the other hand, the exhaust gas 21 generated in the gas turbine power generation facility 2 is passed through the exhaust gas duct 22 to the chimney 2
3 is discharged to the atmosphere through the chimney 23.
【０００８】途中、排ガス２１は、排ガスダクト２２に
設けられた排熱回収熱交換器３によって、前記ボイラ発
電設備１の過熱器１６、及び、再熱器１９の入側から分
岐されてその出側へ戻される蒸気１５を、それぞれ、排
熱回収熱交換器３の熱交換器本体３０内部に設けられた
過熱器２４，２５、再熱器２６，２７などの伝熱装置で
過熱するようになっている。On the way, the exhaust gas 21 is branched from the inlet side of the superheater 16 and the reheater 19 of the boiler power generation facility 1 by the exhaust heat recovery heat exchanger 3 provided in the exhaust gas duct 22 and its output. The steam 15 returned to the side is superheated by heat transfer devices such as superheaters 24 and 25 and reheaters 26 and 27 provided inside the heat exchanger body 30 of the exhaust heat recovery heat exchanger 3, respectively. Has become.
【０００９】そして、排熱回収熱交換器３における蒸気
温度制御は、ボイラ発電設備１の高圧給水加熱器１１入
側等からスプレー流路２８，２９を介してボイラ水５を
取出し、過熱器２４，２５、再熱器２６，２７の中間位
置へスプレーすることによって行われていた。For controlling the steam temperature in the exhaust heat recovery heat exchanger 3, the boiler water 5 is taken out from the inlet side of the high-pressure feed water heater 11 of the boiler power generation facility 1 through the spray passages 28 and 29, and the superheater 24 , 25, and reheaters 26, 27 by spraying to an intermediate position.
【００１０】尚、排熱回収熱交換器３には、過熱器２
４，２５から成る過熱器系Ａと、再熱器２６，２７から
成る再熱器系Ｂの二つの伝熱系があり、各伝熱系Ａ，Ｂ
を構成する過熱器２４，２５及び再熱器２６，２７など
の伝熱装置は、排ガス２１の流れ方向に対して交互に位
置するよう配設されている。The exhaust heat recovery heat exchanger 3 includes a superheater 2
There are two heat transfer systems, a superheater system A composed of 4, 25 and a reheater system B composed of reheaters 26 and 27.
The heat transfer devices such as the superheaters 24 and 25 and the reheaters 26 and 27 that constitute the above are arranged so as to be alternately positioned in the flow direction of the exhaust gas 21.
【００１１】又、排熱回収熱交換器３の伝熱系には、上
記した過熱器系Ａや再熱器系Ｂの他にも、ボイラ水５を
利用して排ガス２１を冷却するようにした、図示しない
スタックガスクーラから成るガスクーラ系などがある。In addition to the above-mentioned superheater system A and reheater system B, the boiler water 5 is used in the heat transfer system of the exhaust heat recovery heat exchanger 3 to cool the exhaust gas 21. Also, there is a gas cooler system including a stack gas cooler (not shown).
【００１２】[0012]
【発明が解決しようとする課題】しかしながら、上記従
来の排熱回収熱交換器には、以下のような問題があっ
た。However, the above-mentioned conventional exhaust heat recovery heat exchanger has the following problems.
【００１３】即ち、ボイラ発電設備１では、一般に効率
面、設備面から、図３に実線イ（再熱器１９側）、ロ
（過熱器１６側）で示すように、高負荷時（ａ点）には
再熱器１９の方が高くなり、低負荷時（ｂ点）には過熱
器１６の方が高くなるような蒸気温度特性とすることが
要求される。That is, in general, in the boiler power generation facility 1, in view of efficiency and facility, as shown by a solid line B (reheater 19 side) and B (superheater 16 side) in FIG. ), The steam temperature characteristics are required such that the reheater 19 has a higher temperature and the superheater 16 has a higher temperature when the load is low (point b).
【００１４】従って、ボイラ発電設備１の蒸気１５の一
部を過熱している排熱回収熱交換器３でも、ボイラ発電
設備１と同様の、高負荷時には再熱器系Ｂの方が高くな
り、低負荷時には過熱器系Ａの方が高くなるような蒸気
温度特性を持たせる必要があるが、上記排熱回収熱交換
器３では、最終の再熱器２７が最終の過熱器２５よりも
排ガス２１の流れ方向上流側の、より高温の排ガス２１
と熱交換できる位置に配置されているので、再熱器系Ｂ
の収熱が常に過熱器系Ａの収熱よりも上回ってしまうこ
ととなり、よって、排熱回収熱交換器３における蒸気温
度特性を、図３に実線イ、ロで示すものと同じにするこ
とができなかった。Therefore, even in the exhaust heat recovery heat exchanger 3 that partially heats the steam 15 of the boiler power generation facility 1, the reheater system B becomes higher at the time of high load, similar to the boiler power generation facility 1. It is necessary to have the steam temperature characteristic that the superheater system A becomes higher when the load is low, but in the exhaust heat recovery heat exchanger 3, the final reheater 27 is more than the final superheater 25. Higher temperature exhaust gas 21 on the upstream side in the flow direction of the exhaust gas 21
It is located in a position where it can exchange heat with the reheater system B.
The heat collection temperature of the exhaust heat recovery heat exchanger 3 is always the same as that shown by the solid lines a and b in FIG. 3. I couldn't.
【００１５】尚、図３中、破線ハは排熱回収熱交換器３
の過熱器系Ａの蒸気温度特性である。In FIG. 3, the broken line C indicates the exhaust heat recovery heat exchanger 3
2 is a steam temperature characteristic of the superheater system A.
【００１６】本発明は、上述の実情に鑑み、複数系統設
けられた各伝熱系の蒸気温度特性を変更させ得るように
した排熱回収熱交換器を提供することを目的とするもの
である。In view of the above situation, it is an object of the present invention to provide an exhaust heat recovery heat exchanger capable of changing the steam temperature characteristic of each heat transfer system provided in a plurality of systems. .
【００１７】[0017]
【課題を解決するための手段】本発明は、熱交換器本体
に、ガスタービン発電設備からの排ガスと、ボイラ発電
設備からのボイラ水或いは蒸気とを熱交換させるための
伝熱系を複数系統設けると共に、複数の伝熱系を構成す
る伝熱装置のうち、排ガスの流れ方向最上流に位置する
伝熱装置の入出側間にバイパス流路を接続し、バイパス
流路に流量調整弁を設けたことを特徴とする排熱回収熱
交換器にかかるものである。According to the present invention, a plurality of heat transfer systems are provided in a heat exchanger body for exchanging heat between exhaust gas from a gas turbine power generation facility and boiler water or steam from a boiler power generation facility. In addition to providing a heat transfer device that constitutes a plurality of heat transfer systems, a bypass flow path is connected between the inlet and outlet sides of the heat transfer device located in the uppermost stream of the exhaust gas flow direction, and a flow rate adjustment valve is provided in the bypass flow path. The present invention relates to an exhaust heat recovery heat exchanger.
【００１８】[0018]
【作用】本発明の作用は以下の通りである。The operation of the present invention is as follows.
【００１９】ボイラ発電設備とガスタービン発電設備と
を並設することにより出力増大を図ると共に、ガスター
ビン発電設備からの排ガスとボイラ発電設備からのボイ
ラ水或いは蒸気を、排熱回収熱交換器の複数系統設けら
れた伝熱系で熱交換させることにより、設備全体として
の熱効率の向上を図るようにする。The output is increased by arranging the boiler power generation equipment and the gas turbine power generation equipment in parallel, and the exhaust gas from the gas turbine power generation equipment and the boiler water or steam from the boiler power generation equipment are transferred to the exhaust heat recovery heat exchanger. By exchanging heat with a heat transfer system provided in a plurality of systems, the thermal efficiency of the entire equipment is improved.
【００２０】ここで、各伝熱系における蒸気温度特性を
変化したい場合には、流量調整弁を開き、バイパス流路
を介して、排ガスの流れ方向最上流に位置する伝熱装置
の入出側間に伝熱媒体をバイパスさせる。Here, when it is desired to change the steam temperature characteristic in each heat transfer system, the flow rate adjusting valve is opened, and the heat transfer device between the inlet and outlet sides of the heat transfer device located at the uppermost stream in the exhaust gas flow direction is opened via the bypass flow path. To bypass the heat transfer medium.
【００２１】すると、排ガスの流れ方向最上流に位置す
る伝熱装置の収熱が低下し、且つ、当該伝熱装置の出側
の排ガスの温度が上昇して出側に設けられた別の伝熱系
を構成する伝熱装置の収熱が向上するので、各伝熱系に
おける伝熱媒体の温度特性が相対的に変化される。Then, the heat collection of the heat transfer device located in the uppermost stream in the flow direction of the exhaust gas decreases, and the temperature of the exhaust gas on the outlet side of the heat transfer device rises to cause another heat transfer on the outlet side. Since the heat collection of the heat transfer device constituting the heat system is improved, the temperature characteristics of the heat transfer medium in each heat transfer system are relatively changed.
【００２２】[0022]
【実施例】以下、本発明の実施例を図面を参照しつつ説
明する。Embodiments of the present invention will be described below with reference to the drawings.
【００２３】図１は、本発明の一実施例である。FIG. 1 shows an embodiment of the present invention.
【００２４】図中、２はガスタービン発電設備、３は排
熱回収熱交換器、１５は排熱回収熱交換器３で過熱され
る蒸気、２１はガスタービン発電設備２で発生した排ガ
ス、２２はガスタービン発電設備２の排ガスダクト、２
３は排ガスダクト２２を流れる排ガス２１を大気に放出
させる煙突である。In the figure, 2 is a gas turbine power generation facility, 3 is an exhaust heat recovery heat exchanger, 15 is steam superheated in the exhaust heat recovery heat exchanger 3, 21 is exhaust gas generated in the gas turbine power generation facility 2, 22 Is an exhaust gas duct of the gas turbine power generation facility 2, 2
Reference numeral 3 denotes a chimney that discharges the exhaust gas 21 flowing through the exhaust gas duct 22 to the atmosphere.
【００２５】２４，２５は排熱回収熱交換器３の熱交換
器本体３０内部に設けられた過熱器などの伝熱装置、２
６，２７は熱交換器本体３０内部に過熱器２４，２５と
交互に配置された再熱器などの伝熱装置、２８，２９は
スプレー流路、Ａは過熱器２４，２５から成る過熱器
系、Ｂは再熱器２６，２７から成る再熱器系である。Reference numerals 24 and 25 denote heat transfer devices such as a superheater provided inside the heat exchanger body 30 of the exhaust heat recovery heat exchanger 3.
Reference numerals 6 and 27 denote heat transfer devices such as reheaters, which are alternately arranged with the superheaters 24 and 25 inside the heat exchanger body 30, 28 and 29 are spray passages, and A is a superheater composed of the superheaters 24 and 25. System B is a reheater system consisting of reheaters 26 and 27.
【００２６】そして、排熱回収熱交換器３の熱交換器本
体３０内部に設けられた各伝熱装置２４，２５，２６，
２７のうち、排ガス２１の流れ方向最上流に位置する伝
熱装置（即ち、最終の再熱器２７）の入出側間にバイパ
ス流路３１を接続し、該バイパス流路３１に流量調整弁
３２を設ける。The heat transfer devices 24, 25, 26 provided inside the heat exchanger body 30 of the exhaust heat recovery heat exchanger 3
A bypass flow passage 31 is connected between the inlet and outlet sides of the heat transfer device (that is, the final reheater 27) located in the uppermost stream of the exhaust gas 21 in the flow direction of the exhaust gas 21, and the flow control valve 32 is connected to the bypass flow passage 31. To provide.
【００２７】次に、作動について説明する。Next, the operation will be described.
【００２８】ボイラ発電設備１及びガスタービン発電設
備２で発電を行わせる過程、及び、排熱回収熱交換器３
でガスタービン発電設備２からの排ガス２１とボイラ発
電設備１の蒸気１５とを熱交換させる過程については図
２と同様なので説明を省略する。The process of generating electricity in the boiler power generation facility 1 and the gas turbine power generation facility 2, and the exhaust heat recovery heat exchanger 3
The process of exchanging heat between the exhaust gas 21 from the gas turbine power generation facility 2 and the steam 15 of the boiler power generation facility 1 is the same as in FIG.
【００２９】本発明では、以下のようにして排熱回収熱
交換器３の過熱器系Ａと再熱器系Ｂの蒸気温度特性を変
化させる。In the present invention, the steam temperature characteristics of the superheater system A and the reheater system B of the exhaust heat recovery heat exchanger 3 are changed as follows.
【００３０】即ち、高負荷時には、流量調整弁３２を閉
じて、バイパス流路３１に蒸気１５が流れないようにす
る。That is, when the load is high, the flow rate adjusting valve 32 is closed to prevent the steam 15 from flowing into the bypass passage 31.
【００３１】すると、最終の再熱器２７が排ガス２１の
流れ方向の最も上流に位置し、最終の過熱器２５がその
下流に位置するため、最終の再熱器２７内部を流れる蒸
気１５が最終の過熱器２５内部を流れる蒸気１５よりも
高温の排ガス２１によって熱交換されることとなり、再
熱器系Ｂの方が過熱器系Ａよりも収熱が良くなるので、
再熱器系Ｂの方が過熱器系Ａよりも高い蒸気温度特性が
得られる。Then, since the final reheater 27 is located at the most upstream in the flow direction of the exhaust gas 21 and the final superheater 25 is located downstream thereof, the steam 15 flowing inside the final reheater 27 is the final product. Since the heat is exchanged by the exhaust gas 21 having a temperature higher than that of the steam 15 flowing inside the superheater 25, the reheater system B has a better heat collection than the superheater system A.
The reheater system B has higher steam temperature characteristics than the superheater system A.
【００３２】そして、低負荷時には、流量調整弁３２を
開いて、前段の再熱器２６を流れてきた蒸気１５の一部
がバイパス流路３１をバイパスされるようにする。When the load is low, the flow rate adjusting valve 32 is opened so that a part of the steam 15 flowing through the reheater 26 at the preceding stage is bypassed through the bypass passage 31.
【００３３】すると、最終の再熱器２７へ流入する蒸気
１５の量が減少するので、その分、再熱器２７における
収熱が低下し、再熱器系Ｂの蒸気温度が低下すると共
に、再熱器２７出側（即ち、最終の過熱器２５入側）の
排ガス２１の温度が上昇して、最終の過熱器２５におけ
る収熱が向上するので、過熱器系Ａの方が再熱器系Ｂよ
りも高い蒸気温度特性が得られる。Then, since the amount of the steam 15 flowing into the final reheater 27 decreases, the heat collection in the reheater 27 decreases correspondingly, and the steam temperature of the reheater system B decreases, and at the same time, Since the temperature of the exhaust gas 21 on the outlet side of the reheater 27 (that is, the inlet side of the final superheater 25) rises and the heat collection in the final superheater 25 is improved, the superheater system A is more reheater. A vapor temperature characteristic higher than that of the system B is obtained.
【００３４】このように、流量調整弁３２によって最終
の再熱器２７と過熱器２５の収熱を変化することによ
り、両者の蒸気温度特性が改善されるので、低負荷時で
も、過熱器系Ａ及び再熱器系Ｂにおける蒸気温度を調節
可能となり、さらにきめ細かくスプレーなどでボイラ発
電設備の要求する蒸気温度に調節することが可能とな
る。As described above, by changing the heat absorption of the final reheater 27 and the superheater 25 by the flow rate adjusting valve 32, the steam temperature characteristics of both are improved, so that the superheater system can be operated even under a low load. It becomes possible to adjust the steam temperature in A and the reheater system B, and further finely adjust to the steam temperature required by the boiler power generation facility by spraying or the like.
【００３５】又、流量調整弁３２によって、過熱器系Ａ
及び再熱器系Ｂにおける蒸気温度特性を変更することに
より、過熱器系Ａ及び再熱器系Ｂで得られる蒸気温度が
変化するので、流量調整弁３２を用いて、負荷変化中の
蒸気温度を制御させることも可能である。The superheater system A is controlled by the flow rate adjusting valve 32.
By changing the steam temperature characteristic in the reheater system B and the steam temperature obtained in the superheater system A and the reheater system B, the flow rate adjusting valve 32 is used to change the steam temperature during the load change. Can also be controlled.
【００３６】尚、本発明は、上述の実施例にのみ限定さ
れるものではなく、流量調整弁３２による蒸気温度制御
によりスプレーを不要化し得ること、過熱器系と再熱器
系から成る伝熱系統以外にもガスクーラ系などを含む伝
熱系統にも適用し得ること、その他、本発明の要旨を逸
脱しない範囲内において種々変更を加え得ることは勿論
である。The present invention is not limited to the above-mentioned embodiments, but the spray temperature can be controlled by the flow rate adjusting valve 32 to eliminate the need for spraying, and the heat transfer system comprising a superheater system and a reheater system. It is needless to say that the present invention can be applied to a heat transfer system including a gas cooler system in addition to the system, and that various changes can be made without departing from the scope of the present invention.
【００３７】[0037]
【発明の効果】以上説明したように、本発明の排熱回収
熱交換器によれば、複数系統設けられた各伝熱系の温度
特性を変更させることができるという優れた効果を奏し
得る。As explained above, according to the exhaust heat recovery heat exchanger of the present invention, it is possible to obtain the excellent effect that the temperature characteristics of each heat transfer system provided in a plurality of systems can be changed.
【図１】本発明の一実施例の概略系統図である。FIG. 1 is a schematic system diagram of an embodiment of the present invention.
【図２】現在検討中の複合発電設備の全体概略系統図で
ある。FIG. 2 is an overall schematic system diagram of an integrated power generation facility currently under consideration.
【図３】ボイラ発電設備における負荷と蒸気温度との関
係を示すグラフである。FIG. 3 is a graph showing a relationship between load and steam temperature in a boiler power generation facility.
１ ボイラ発電設備 ２ ガスタービン発電設備 ５ ボイラ水 １５ 蒸気（伝熱媒体） ２１ 排ガス ２４，２５ 過熱器（伝熱装置） ２６，２７ 再熱器（伝熱装置） ３０ 熱交換器本体 ３１ バイパス流路 ３２ 流量調整弁 Ａ 過熱器系（伝熱系） Ｂ 再熱器系（伝熱系） 1 Boiler power generation equipment 2 Gas turbine power generation equipment 5 Boiler water 15 Steam (heat transfer medium) 21 Exhaust gas 24, 25 Superheater (heat transfer device) 26, 27 Reheater (heat transfer device) 30 Heat exchanger body 31 Bypass flow Line 32 Flow rate control valve A Superheater system (heat transfer system) B Reheater system (heat transfer system)
Claims (1)
からの排ガスと、ボイラ発電設備からのボイラ水或いは
蒸気とを熱交換させるための伝熱系を複数系統設けると
共に、複数の伝熱系を構成する伝熱装置のうち、排ガス
の流れ方向最上流に位置する伝熱装置の入出側間にバイ
パス流路を接続し、バイパス流路に流量調整弁を設けた
ことを特徴とする排熱回収熱交換器。1. The heat exchanger body is provided with a plurality of heat transfer systems for exchanging heat between exhaust gas from a gas turbine power generation facility and boiler water or steam from the boiler power generation facility, and a plurality of heat transfer systems. Among the heat transfer devices constituting the above, the exhaust heat is characterized in that a bypass flow passage is connected between the inlet and outlet sides of the heat transfer device located at the uppermost stream in the exhaust gas flow direction, and a flow rate adjustment valve is provided in the bypass flow passage. Recovery heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2620893A JPH06221503A (en) | 1993-01-21 | 1993-01-21 | Waste heat recovery heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2620893A JPH06221503A (en) | 1993-01-21 | 1993-01-21 | Waste heat recovery heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06221503A true JPH06221503A (en) | 1994-08-09 |
Family
ID=12187038
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2620893A Pending JPH06221503A (en) | 1993-01-21 | 1993-01-21 | Waste heat recovery heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06221503A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007163126A (en) * | 2005-12-12 | 2007-06-28 | General Electric Co <Ge> | Composite cycle power generation system improved in efficiency |
-
1993
- 1993-01-21 JP JP2620893A patent/JPH06221503A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007163126A (en) * | 2005-12-12 | 2007-06-28 | General Electric Co <Ge> | Composite cycle power generation system improved in efficiency |
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