JPH0131012B2 - - Google Patents
Info
- Publication number
- JPH0131012B2 JPH0131012B2 JP19936281A JP19936281A JPH0131012B2 JP H0131012 B2 JPH0131012 B2 JP H0131012B2 JP 19936281 A JP19936281 A JP 19936281A JP 19936281 A JP19936281 A JP 19936281A JP H0131012 B2 JPH0131012 B2 JP H0131012B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- heat recovery
- liquid phase
- phase water
- compressed 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.)
- Expired
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 55
- 238000011084 recovery Methods 0.000 claims description 41
- 239000007791 liquid phase Substances 0.000 claims description 31
- 239000000203 mixture Substances 0.000 claims description 18
- 238000001816 cooling Methods 0.000 claims description 9
- 239000002826 coolant Substances 0.000 claims description 6
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 29
- 239000000446 fuel Substances 0.000 description 13
- 238000000034 method Methods 0.000 description 8
- 238000002347 injection Methods 0.000 description 7
- 239000007924 injection Substances 0.000 description 7
- 238000012546 transfer Methods 0.000 description 7
- 239000007788 liquid Substances 0.000 description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 4
- 239000002912 waste gas Substances 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000000567 combustion gas Substances 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 239000003345 natural gas Substances 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000003303 reheating Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
- F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
- F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/211—Heat transfer, e.g. cooling by intercooling, e.g. during a compression cycle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
【発明の詳細な説明】
本発明は新規な熱回収の方法を用いてなる水注
入ガスタービンサイクルに関し、空気もしくは空
気を主体とするガスを圧縮機で圧縮してなる圧縮
空気の一部もしくは全部に液相水を接触させて得
た空気／水蒸気の混合物によるタービン排気の熱
回収および該接触操作にて得られる冷却された液
相水を熱回収媒体として用いタービン排気の熱回
収、圧縮機の中間冷却を行うとともに、該接触操
作で蒸発し冷却との混合物として圧縮空気中に移
行した量に当たる液相水を該中間冷却器の後流の
冷却媒体として用いることを特徴とするものであ
り、好ましい態様においてはタービン入口温度
1000℃で49％（LHV基準）以上の熱効率を達成
できるガスタービンサイクルであり、この熱効率
は従来の単純ガスタービンサイクルの熱効率の約
1.9倍であり、このことは燃料消費量が約1/2に減
少することを意味する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a water-injected gas turbine cycle using a novel heat recovery method. Heat recovery from turbine exhaust gas using an air/steam mixture obtained by contacting liquid phase water with the turbine exhaust gas, and heat recovery from turbine exhaust gas using the cooled liquid phase water obtained in the contact operation as a heat recovery medium, It is characterized by performing intercooling and using liquid phase water corresponding to the amount that evaporated in the contact operation and transferred into the compressed air as a mixture with the cooling as a cooling medium downstream of the intercooler, In a preferred embodiment, the turbine inlet temperature
It is a gas turbine cycle that can achieve a thermal efficiency of 49% or more (LHV standard) at 1000℃, and this thermal efficiency is about the same as that of a conventional simple gas turbine cycle.
1.9 times, which means that fuel consumption is reduced by about 1/2.
従来ガスタービンサイクルにおけるタービン排
気の熱回収は空気の予熱、廃熱ボイラーによる熱
媒蒸気の回収、吸収冷凍による冷凍エネルギーの
回収等が行なわれており、空気の予熱の一種とし
て圧縮空気に水を混合して得た空気／水蒸気の混
合物による方法も行なわれている。 Conventionally, heat recovery from turbine exhaust in a gas turbine cycle involves preheating the air, recovering heat medium vapor using a waste heat boiler, and recovering refrigeration energy using absorption refrigeration. A method using a mixed air/steam mixture has also been used.
従来の水注入ガスタービンサイクルとしては、
米国特許第2095991号、同第2115112号、同第
2115338号、同第2678532号、同第2869324号、ス
イス特許第457039号、フランス特許第1007140号
等がある。 As a conventional water injection gas turbine cycle,
U.S. Patent No. 2095991, U.S. Patent No. 2115112, U.S. Patent No.
No. 2115338, No. 2678532, No. 2869324, Swiss Patent No. 457039, French Patent No. 1007140, etc.
これら特許文献を評価した報文として、
Gasparovic、Ｎらによる「GAS TURBINES
WITH HEAT EXCHANGER AND WATER
INJECTION IN THE COMPRESSED AIR」
（Combustion u44 n6 Dec.1972 P32−40；以下
報文Ａと記す。およびCombustion u45 n6
Dec.1973 P6−16；以下報文Ｂと記す）がある。 As a report evaluating these patent documents,
“GAS TURBINES” by Gasparovic, N. et al.
WITH HEAT EXCHANGER AND WATER
INJECTION IN THE COMPRESSED AIR”
(Combustion u44 n6 Dec.1972 P32-40; hereinafter referred to as Report A. and Combustion u45 n6
Dec.1973 P6-16; hereinafter referred to as Report B).
これらの文献には、圧縮空気への水の注入およ
び中間段圧縮空気への水の注入の態様の記載があ
り、圧縮空気／水蒸気の混合物による熱回収の方
法を開示するもので、そしてこれら特許を評価し
た報文ＡおよびＢによると、比出力の大幅向上に
対して熱効率は従来の単純ガスタービンサイクル
の熱効率の1.5倍程度にすぎない。この熱効率の
向上は必ずしも十分なものではなく、かつ実用性
を加味した総合動力プラントの観点からはいわゆ
るガスタービン−蒸気タービン複合サイクルに比
べ見劣りするものとなつており、近年の燃料価格
の大幅な上昇（20倍／10年）により熱効率の大幅
向上を計るための動力プラントの開発方向はもつ
ぱらガスタービン−蒸気タービン複合サイクルの
実用化を指向している。 These documents describe aspects of water injection into compressed air and water injection into intermediate stage compressed air, and disclose methods for heat recovery with compressed air/steam mixtures, and these patents According to reports A and B that evaluated the specific output, the thermal efficiency is only about 1.5 times that of the conventional simple gas turbine cycle. This improvement in thermal efficiency is not necessarily sufficient, and from the perspective of a comprehensive power plant that takes practicality into consideration, it is inferior to the so-called gas turbine-steam turbine combined cycle, and fuel prices have increased significantly in recent years. The direction of development of power plants that aims to significantly improve thermal efficiency by increasing heat efficiency (20 times per 10 years) is primarily toward the practical application of a gas turbine-steam turbine combined cycle.
また上記報文ＡおよびＢには触れられていない
が水注入ガスタービンサイクルに関する特許とし
ては米国特許第2186706号およびドイツ特許第
717711号がある。これらの特許の中には各々接触
操作で蒸発し空気との混合物として圧縮空気中に
移行した量に当たる液相水を熱回収媒体として用
いタービン排気の熱回収に利用すること、および
圧縮機の中間冷却を該接触操作にて得られる冷却
された液相水の他にサイクル外からの冷却水によ
り行うという記載があるが、いずれの方法もガス
タービンサイクルの熱効率という観点からは、本
発明より劣るものである。 Although not mentioned in the above reports A and B, patents related to water injection gas turbine cycles include US Patent No. 2186706 and German Patent No.
There is number 717711. These patents include the use of liquid phase water as a heat recovery medium to recover heat from turbine exhaust air, which corresponds to the amount of liquid water that evaporates during the contact operation and transfers into the compressed air as a mixture with air; There is a description that cooling is performed using cooling water from outside the cycle in addition to the cooled liquid phase water obtained in the contact operation, but both methods are inferior to the present invention from the viewpoint of thermal efficiency of the gas turbine cycle. It is something.
本発明者は、この水注入ガスタービンサイクル
において圧縮空気の一部もしくは全部に液相水を
注入して得られる圧縮空気／水／水蒸気の混相混
合物によりタービン排気の熱回収を行なうととも
に補給する液相水で圧縮機の中間冷却を行なうこ
とにより、熱効率が向上することを見い出し、先
に特許出願した。（特願昭55−155399他）その後
水の注入方法と熱回収、更には熱回収媒体の製造
方法について検討を続けた結果、熱回収媒体とし
て用い加熱された液相水と圧縮空気とを直接接触
させ熱および物質（水分）移動を行なわせる交換
塔などの接触操作手段と該接触操作により冷却さ
れた液相水を熱回収媒体としてタービン排気の熱
回収および圧縮機の中間冷却に用いるとともに該
接触操作で蒸発し圧縮空気との混合物として圧縮
空気中に移行した量に当たる液相水を該中間冷却
器の後流の冷却媒体として用いることにより前記
報文における水注入ガスタービンサイクル以上の
熱効率の向上が計れることを見い出し本発明を完
成させた。この熱効率は、前記の再熱ガスタービ
ン−蒸気タービン複合サイクル以上である。 In this water-injected gas turbine cycle, the present inventors recovered heat from the turbine exhaust gas using a multiphase mixture of compressed air/water/steam obtained by injecting liquid phase water into part or all of the compressed air, and also recovered the heat from the turbine exhaust gas by injecting liquid water into part or all of the compressed air. They discovered that thermal efficiency could be improved by performing intermediate cooling of the compressor with phase water, and filed a patent application earlier. (Patent Application No. 55-155399, etc.) After that, we continued to study water injection methods and heat recovery, as well as methods for producing heat recovery media. Contact operation means such as an exchange tower to transfer heat and mass (moisture) through contact and liquid phase water cooled by the contact operation are used as a heat recovery medium for heat recovery of turbine exhaust and intermediate cooling of the compressor. By using the amount of liquid-phase water that evaporated during the contact operation and transferred into the compressed air as a mixture with the compressed air as a cooling medium downstream of the intercooler, thermal efficiency higher than that of the water-injection gas turbine cycle described in the above paper can be achieved. The present invention was completed based on the discovery that improvements could be made. This thermal efficiency is higher than the reheat gas turbine-steam turbine combined cycle described above.
すなわち、本発明は、支燃剤ガス・作動媒体ガ
ス等として用いる空気もしくは空気を主体とする
ガスを圧縮機で圧縮してなる圧縮空気の一部もし
くは全部と熱回収媒体として用い加熱された液相
水とを接触させ、空気／水蒸気の混合物および冷
却された液相水を得て、空気／水蒸気の混合物で
タービン排気の熱回収を、また冷却された液相水
を熱回収媒体としてタービン排気の熱回収および
圧縮機の中間冷却を行うガスタービンサイクルに
おいて、該接触操作で蒸発し空気との混合物とし
て圧縮空気中に移行した量に当たる液相水を該接
触操作で得られる冷却された液相水による圧縮機
の中間冷却器の後流の冷却媒体として使用し該接
触操作および該熱回収操作に供せられる液相水中
に補給するごとくしてなるガスタービンサイクル
である。 That is, the present invention relates to a part or all of compressed air obtained by compressing air or air-based gas used as a combustion support gas, working medium gas, etc. with a compressor, and a heated liquid phase used as a heat recovery medium. water to obtain an air/steam mixture and cooled liquid phase water. In a gas turbine cycle that performs heat recovery and intermediate cooling of the compressor, the amount of liquid phase water that evaporates in the contact operation and transfers into the compressed air as a mixture with air is converted into cooled liquid phase water obtained in the contact operation. This is a gas turbine cycle in which the liquid phase water is used as a downstream cooling medium of the intercooler of the compressor and is replenished into the liquid phase water used for the contact operation and the heat recovery operation.
本発明は、上記のごとく接触操作で蒸発し空気
との混合物として圧縮空気中に移行した量に当た
る液相水を圧縮機の中間冷却器の後流の冷却媒体
として用いるものであり、中間冷却による圧縮動
力の低減がサイクル外に熱を捨てることなく達成
できるものである。 The present invention uses the amount of liquid phase water that evaporates during the contact operation and transfers into the compressed air as a mixture with air as a cooling medium downstream of the intercooler of the compressor as described above, A reduction in compression power can be achieved without discarding heat outside the cycle.
以下添付図面により本発明のフローシートの一
例を説明する。 An example of a flow sheet of the present invention will be explained below with reference to the accompanying drawings.
図面は、圧縮空気と液相水とを接触させる接触
交換塔（以下交換塔と記す）１、熱回収器３、中
間冷却器１、空気圧縮機２、タービン１の場合で
ある。空気圧縮機AC1により吸入された大気空気
３は、断熱圧縮され管４より中間冷却器ICに入
る。中間冷却器ICで冷却された中間段圧縮空気
５は空気圧縮機AC2で再び断熱圧縮され管６より
吐出される。圧縮空気の一部は管７より交換塔
EXT下部に導入され、残部は管８より高温側熱
回収器R1に導入される。交換塔EXTでは中間冷
却器IC、低温側熱回収器R2にて予熱された液相
水が管１７，２１を通して上部より入り、下部よ
り入る前記管７からの圧縮空気との直接接触によ
り熱および物質（水分）移動が同時に行なわれ、
頂部からは通常飽和〜やや乾いた空気／水蒸気の
混合物が管９より、底部からは該接触操作により
冷却された液相水が管１８よりそれぞれ出る。交
換塔EXT底部より管１８を通して出る冷却され
た液相水は、中間冷却器IC、低温側熱回収器R2
への熱回収媒体として管１９，２０を通して導入
される。また該接触操作で蒸発し圧縮空気との混
合物として圧縮空気中に移行した量に当たる液相
水が中間冷却器ICの熱回収媒体として加圧水導
入管２を通じ導入され、前記１９よりの液相水中
に管１６において補給される。一方交換塔EXT
頂部より管９を通して出る圧縮空気／水蒸気の混
合物は、管８の昇圧空気とともに高温側熱回収器
R1に導入され熱回収されて管１０より燃焼器CC
に導入される。燃焼器CCには管１よりの燃料が
熱回収器R3で予熱されて加えられており、所定
温度の燃焼ガスとなり管１１よりタービンETに
導入される。燃焼ガスは断熱膨張し、空気圧縮機
AC1，AC2および負荷Ｌの駆動力を発生し管１２
より排出され、一部は管１５より燃料の予熱器
R3に、他は管１３より高温側熱回収器R1、次い
で低温側熱回収器R2を経て熱回収され低温の廃
ガス１４となる。尚、空気圧縮機AC1，AC2およ
びタービンETに導入されるシール空気およびタ
ービンETに導入される冷却空気は当然機械の設
計上別途必要とされる。但し、本発明の操作の過
程においては、低温の圧縮空気が得られるため、
タービン冷却用圧縮空気の必要量は従来のガスタ
ービンサイクルより少なくすることが可能であ
り、本効果は一層の熱効率の向上に寄与するもの
である。 The drawing shows the case of a contact exchange tower (hereinafter referred to as an exchange tower) 1 that brings compressed air and liquid phase water into contact, a heat recovery device 3, an intercooler 1, an air compressor 2, and a turbine 1. Atmospheric air 3 taken in by the air compressor AC 1 is adiabatically compressed and enters the intercooler IC through the pipe 4. The intermediate stage compressed air 5 cooled by the intercooler IC is adiabatically compressed again by the air compressor AC 2 and discharged from the pipe 6. A part of the compressed air is sent to the exchange tower via pipe 7.
The remaining part is introduced into the high temperature side heat recovery device R1 through pipe 8. In the exchange tower EXT, liquid phase water preheated in the intercooler IC and low-temperature side heat recovery unit R 2 enters from the top through pipes 17 and 21, and is heated by direct contact with the compressed air from the pipe 7 that enters from the bottom. and mass (moisture) transfer occur simultaneously,
A normally saturated to slightly dry air/steam mixture exits from the top through tube 9, and liquid water cooled by the contacting operation exits from the bottom through tube 18. The cooled liquid phase water exiting from the bottom of the exchange tower EXT through pipe 18 is transferred to the intercooler IC and the low temperature side heat recovery unit R2.
through pipes 19, 20 as a heat recovery medium. In addition, the amount of liquid phase water that evaporated during the contact operation and transferred into the compressed air as a mixture with the compressed air is introduced through the pressurized water introduction pipe 2 as a heat recovery medium of the intercooler IC, and is introduced into the liquid phase water from 19 above. It is replenished in tube 16. Meanwhile exchange tower EXT
The compressed air/steam mixture exiting from the top through tube 9 is sent together with the pressurized air in tube 8 to the hot side heat recovery device.
The heat is introduced into R1 , is recovered and sent to the combustor CC through pipe 10.
will be introduced in The fuel from the pipe 1 is preheated by the heat recovery device R 3 and added to the combustor CC, and becomes combustion gas at a predetermined temperature, which is introduced into the turbine ET through the pipe 11. The combustion gas expands adiabatically, and the air compressor
AC 1 , AC 2 and the driving force of the load L are generated and the pipe 12
A part of the fuel is discharged from the pipe 15 to the fuel preheater.
The remaining heat is recovered from the pipe 13 through the high-temperature side heat recovery device R 1 and then through the low-temperature side heat recovery device R 2 and becomes a low-temperature waste gas 14 . Incidentally, the sealing air introduced into the air compressors AC 1 and AC 2 and the turbine ET, and the cooling air introduced into the turbine ET are naturally required separately due to the design of the machine. However, in the process of operation of the present invention, since low-temperature compressed air is obtained,
The required amount of compressed air for turbine cooling can be reduced compared to conventional gas turbine cycles, and this effect contributes to further improvement of thermal efficiency.
以上図面によつて本発明のフローの一例を示し
たが本発明は接触操作で蒸発し空気との混合物と
して圧縮空気中に移行した量に当たる液相水を圧
縮機の中間冷却器の後流の冷却媒体として用いる
ことを特徴とするものであつてこの操作を用いる
限りにおいては種々の変更を加えうるものであ
る。例えば中間冷却に更に燃料を併用すること、
再熱サイクル化、廃ガス中の水の凝縮回収装置の
付加、燃料が天然ガスおよび石炭のガス化装置か
らのガス等の場合にNOX抑制や熱回収を有効に
行うために該燃料とガスタービンサイクル内で熱
回収媒体として循環使用されている液相水の一部
とを接触させ、該接触操作にて得られる燃料／水
蒸気および液相水を熱回収媒体として使用する
（特公昭63−29091号）などである。 An example of the flow of the present invention has been shown above with reference to the drawings, and the present invention is to transfer the amount of liquid phase water, which is evaporated during the contact operation and transferred into the compressed air as a mixture with air, to the downstream of the intercooler of the compressor. It is characterized by being used as a cooling medium, and various modifications can be made as long as this operation is used. For example, using fuel for intercooling,
Reheat cycle, addition of a condensation recovery device for water in waste gas, and when the fuel is gas from natural gas or coal gasification equipment, to effectively suppress NOx and recover heat, the fuel and gas A part of the liquid phase water that is circulated as a heat recovery medium in the turbine cycle is brought into contact with the liquid phase water, and the fuel/steam and liquid phase water obtained through the contact operation are used as the heat recovery medium (Japanese Patent Publication No. 63- 29091) etc.
本発明のガスタービンサイクルの基本的なフロ
ーとその適用の一例を上記に示したが、操作条件
の点からは、圧縮空気と液相水との直接接触によ
る熱および物質（水分）移動がより有利に利用で
きる範囲としては、まず、該接触操作に用いる圧
縮空気量は熱回収率の面からは通常全量用いるこ
とが好ましいが、タービン排気の熱回収、中間冷
却などで使用される該接触操作で得られる冷却さ
れた液相水を得るための所望量および接触操作の
実用的条件から用いる機器の大きさや廃ガス温度
の制限などから適宜高温側熱回収器に分流させる
ものである。また圧縮空気との接触操作で蒸発し
圧縮空気／水蒸気の混合物として圧縮空気中に移
行させる水量、すなわちサイクルへの補給すべき
水量についても実施に当り好適な量を選定する。 Although the basic flow of the gas turbine cycle of the present invention and an example of its application have been shown above, from the point of view of operating conditions, heat and mass (moisture) transfer through direct contact between compressed air and liquid water is more efficient. As for the range that can be used advantageously, firstly, from the standpoint of heat recovery rate, it is usually preferable to use the entire amount of compressed air used for the contact operation, but the contact operation used for heat recovery of turbine exhaust, intercooling, etc. The flow is diverted to the high-temperature side heat recovery device as appropriate based on the desired amount to obtain the cooled liquid phase water obtained in the above process, the practical conditions of the contact operation, the size of the equipment used, and restrictions on the exhaust gas temperature. In addition, the amount of water to be evaporated by contact with compressed air and transferred into the compressed air as a mixture of compressed air/steam, that is, the amount of water to be replenished into the cycle, is selected to be a suitable amount in practice.
この好適操作範囲は中間冷却に更に燃料を併用
すること、再熱サイクル化、廃ガス中の水の凝縮
回収装置の付加など、あるいはタービン入口条件
などによつて当然変わるものである。たとえば、
図面のフローシートにおいて、タービン入口条件
として圧力6at、温度1000℃では、圧縮空気への
補給すべき水量は全吸入空気１Kgmolあたり0.1
〜0.2Kgmol、好ましくは0.11〜0.15Kgmolの範囲
である。また圧縮機において、中間冷却を施すべ
き段前後の圧力配分は、中間冷却による圧縮動力
の低減効果をより大きくするとの点より判断され
るべきのものである。 This preferred operating range naturally changes depending on the use of fuel for intercooling, reheating cycle, addition of a condensation recovery device for water in waste gas, or turbine inlet conditions. for example,
In the flow sheet of the drawing, when the turbine inlet conditions are 6at pressure and 1000℃ temperature, the amount of water to be added to the compressed air is 0.1 per kgmol of total intake air.
~0.2Kgmol, preferably 0.11-0.15Kgmol. Further, in the compressor, the pressure distribution before and after the stage to which intercooling is to be performed should be determined from the viewpoint of increasing the compression power reduction effect due to intercooling.
以下に本発明の効果をより具体的に説明するた
めに検討例を示す。 Below, a study example will be shown to more specifically explain the effects of the present invention.
検討例
() 条件
(a) 効率
圧縮機断熱効率 ηC＝0.89
タービン断熱効率 ηT＝0.91
機械効率 ηn＝0.99
発電機効率 ηG＝0.985
燃焼効率 ηB＝0.999
(b) 大気吸入条件
温度 15℃
圧力 1.033at
湿度 60％
流量Dry Air １Kgmol／ｓ
H2O 0.0101Kgmol／ｓ
(c) 燃料
種類 天然ガス
温度 15℃
高位発熱量（０℃） 245200Kcal／Kgmol
低位発熱量（０℃） 221600Kcal／Kgmol
(d) 総圧力損失率 0.152
(e) 補給水
温度 15℃
流量 0.123Kgmol／ｓ
(f) タービン入口条件
圧力 6at
温度 1000℃
(g) 熱交換器最小温度差
高温側熱回収器R1 30℃
低温側熱回収器R2 20℃
燃料予熱器R3 30℃
中間冷却器 20℃
(h) その他
燃料、補給水および交換塔底部水の圧縮動
力は無視したが、所内動力として発電端出力
の0.3％を考慮した。又、タービン冷却空気
の必要量は本サイクルにては低温の圧縮空気
が得られることを考慮して設定した。Study example () Conditions (a) Efficiency Compressor adiabatic efficiency η C =0.89 Turbine adiabatic efficiency η T =0.91 Mechanical efficiency η n =0.99 Generator efficiency η G =0.985 Combustion efficiency η B =0.999 (b) Air intake conditions Temperature 15℃ Pressure 1.033at Humidity 60% Flow rate Dry Air 1Kgmol/s H 2 O 0.0101Kgmol/s (c) Fuel Type Natural gas Temperature 15℃ Higher calorific value (0℃) 245200Kcal/Kgmol Lower calorific value (0℃) 221600Kcal/ Kgmol (d) Total pressure loss rate 0.152 (e) Make-up water Temperature 15℃ Flow rate 0.123Kgmol/s (f) Turbine inlet conditions Pressure 6at Temperature 1000℃ (g) Heat exchanger minimum temperature difference High temperature side heat recovery unit R 1 30 ℃ Low-temperature side heat recovery device R 2 20℃ Fuel preheater R 3 30℃ Intercooler 20℃ (h) Others Although the compression power of fuel, make-up water, and exchange tower bottom water was ignored, the power generation end output was 0.3% was considered. In addition, the required amount of turbine cooling air was set considering that low-temperature compressed air can be obtained in this cycle.
() 結果 (a) 廃ガス 温度 96.2℃ 流量 1.14Kgmol／ｓ (b) 圧縮機AC2出口温度 153℃ (c) 送電端出力 8500KW (d) 送電端熱効率 49.5％() Results (a) Waste gas temperature 96.2℃ Flow rate 1.14Kgmol/s (b) Compressor AC 2 outlet temperature 153℃ (c) Sending end output 8500KW (d) Sending end thermal efficiency 49.5%
図面は本発明の一例を示すフローシートであ
る。
２は加圧水導入管、３は大気空気、５は中間段
圧縮空気、６，７，８，９，１７，１８，１９，
２０，２１は管、R1は高温側熱回収器、R2は低
温側熱回収器、R3は熱回収器、ICは中間冷却器、
EXTは交換塔、AC1，AC2は空気圧縮機、CCは
燃焼器、ETはタービン、Ｌは負荷を示す。
The drawing is a flow sheet showing an example of the present invention. 2 is a pressurized water introduction pipe, 3 is atmospheric air, 5 is intermediate stage compressed air, 6, 7, 8, 9, 17, 18, 19,
20 and 21 are tubes, R 1 is a high temperature side heat recovery device, R 2 is a low temperature side heat recovery device, R 3 is a heat recovery device, IC is an intercooler,
EXT is an exchange tower, AC 1 and AC 2 are air compressors, CC is a combustor, ET is a turbine, and L is a load.
Claims (1)
気もしくは空気を主体とするガスを圧縮機で圧縮
してなる圧縮空気の一部もしくは全部と熱回収媒
体として用い加熱された液相水とを接触させ、空
気／水蒸気の混合物および冷却された液相水を得
て、空気／水蒸気の混合物でタービン排気の熱回
収を、また冷却された液相水を熱回収媒体として
タービン排気の熱回収および圧縮機の中間冷却を
行うガスタービンサイクルにおいて、該接触操作
で蒸発し空気との混合物として圧縮空気中に移行
した量に当たる液相水を該接触操作で得られる冷
却された液相水による圧縮機の中間冷却器の後流
の冷却媒体として使用し該接触操作および該熱回
収操作に供せられる液相水中に補給するごとくし
てなるガスタービンサイクル。1 Part or all of the compressed air obtained by compressing air or air-based gas used as a combustion support gas, working medium gas, etc. with a compressor and heated liquid phase water used as a heat recovery medium are brought into contact. , obtain an air/steam mixture and cooled liquid phase water, and use the air/steam mixture for heat recovery of turbine exhaust, and use the cooled liquid phase water as a heat recovery medium for turbine exhaust heat recovery and compressor. In a gas turbine cycle that performs intermediate cooling, the amount of liquid phase water that is evaporated in the contact operation and transferred into the compressed air as a mixture with air is cooled by the cooled liquid phase water obtained in the contact operation. A gas turbine cycle in which liquid phase water is used as a cooling medium downstream of a cooler and is supplied to the contact operation and the heat recovery operation.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19936281A JPS58101226A (en) | 1981-12-10 | 1981-12-10 | Gas turbine cycle |
| US06/448,322 US4537023A (en) | 1981-12-10 | 1982-12-09 | Regenerative gas turbine cycle |
| DE8282306607T DE3279086D1 (en) | 1981-12-10 | 1982-12-10 | Regenerative gas turbine cycle |
| EP82306607A EP0081996B1 (en) | 1981-12-10 | 1982-12-10 | Regenerative gas turbine cycle |
| CA000417429A CA1218240A (en) | 1981-12-10 | 1982-12-10 | Regenerative gas turbine cycle |
| US06/744,238 US4610137A (en) | 1981-12-10 | 1985-06-13 | Regenerative gas turbine cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19936281A JPS58101226A (en) | 1981-12-10 | 1981-12-10 | Gas turbine cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58101226A JPS58101226A (en) | 1983-06-16 |
| JPH0131012B2 true JPH0131012B2 (en) | 1989-06-22 |
Family
ID=16406494
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19936281A Granted JPS58101226A (en) | 1981-12-10 | 1981-12-10 | Gas turbine cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58101226A (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ZA85528B (en) * | 1984-02-01 | 1986-12-30 | Fluor Corp | Process for producing power |
| JPH061056B2 (en) * | 1984-10-29 | 1994-01-05 | 三菱瓦斯化学株式会社 | Motorized recovery method of process waste heat |
| BE905234R (en) * | 1985-11-21 | 1986-12-01 | Fluor Corp | PROCESS FOR PRODUCING ENERGY. |
| EP0361065A1 (en) * | 1988-09-28 | 1990-04-04 | Westinghouse Electric Corporation | Power generating method using solid fuel for a gas turbine |
| US8051654B2 (en) * | 2008-01-31 | 2011-11-08 | General Electric Company | Reheat gas and exhaust gas regenerator system for a combined cycle power plant |
| JP5412205B2 (en) * | 2009-07-31 | 2014-02-12 | 三菱重工業株式会社 | Gas turbine plant and gasification fuel power generation facility equipped with the same |
| JP2013253611A (en) * | 2013-09-17 | 2013-12-19 | Mitsubishi Heavy Ind Ltd | Gas turbine plant, method of operating the same, and gasification fuel power generation facility including gas turbine plant |
-
1981
- 1981-12-10 JP JP19936281A patent/JPS58101226A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58101226A (en) | 1983-06-16 |
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