JPH0131013B2 - - Google Patents
Info
- Publication number
- JPH0131013B2 JPH0131013B2 JP19936481A JP19936481A JPH0131013B2 JP H0131013 B2 JPH0131013 B2 JP H0131013B2 JP 19936481 A JP19936481 A JP 19936481A JP 19936481 A JP19936481 A JP 19936481A JP H0131013 B2 JPH0131013 B2 JP H0131013B2
- Authority
- JP
- Japan
- Prior art keywords
- heat recovery
- air
- liquid phase
- compressed air
- phase water
- 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 62
- 238000011084 recovery Methods 0.000 claims description 53
- 239000007791 liquid phase Substances 0.000 claims description 36
- 239000000203 mixture Substances 0.000 claims description 14
- 238000001816 cooling Methods 0.000 claims description 12
- 238000002485 combustion reaction Methods 0.000 claims description 5
- 238000012546 transfer Methods 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 3
- 239000012071 phase Substances 0.000 claims 1
- 239000007789 gas Substances 0.000 description 27
- 239000000446 fuel Substances 0.000 description 12
- 238000002347 injection Methods 0.000 description 7
- 239000007924 injection Substances 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 239000002912 waste gas Substances 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 239000003345 natural gas Substances 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
- 239000000498 cooling water Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 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
- 239000002826 coolant Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000003303 reheating Methods 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予め熱回収媒体として
用い加熱された液相水を接触させて得た空気／水
蒸気の混合物でタービン排気の熱回収を行なうと
ともに、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タービン排気の熱回収およ
び必要に応じて圧縮機の中間冷却に用いるのみで
なく、該接触操作に用いる圧縮空気の冷却にも用
いて該接触操作にてより低温の液相水を得ること
を特長とするもので、好ましい態様においてはタ
ービン入口温度1000℃で50％（燃料天然ガス、
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 is recovered from the turbine exhaust using the air/steam mixture obtained by contacting liquid phase water that has been heated in advance as a heat recovery medium, and the cooled liquid phase water obtained through the contact operation is also used for heat recovery. It is not only used as a medium for heat recovery of turbine exhaust and intermediate cooling of the compressor as necessary, but also used to cool the compressed air used in the contact operation to obtain lower temperature liquid phase water in the contact operation. In a preferred embodiment, the turbine inlet temperature is 50% (fuel natural gas,
It is a gas turbine cycle that can achieve thermal efficiency higher than the LHV standard, and this thermal efficiency is approximately 1.9 times that of a conventional simple gas turbine cycle.
This 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 HITH HEAT EXCHANGER AND
WATER INJECTION IN THE
COMPRESSED AIR」（Combustion v44 n6
Dec.1972 p32−40；以下報文Ａと記す。および
Combustion v45 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 HITH HEAT EXCHANGER AND
WATER INJECTION IN THE
COMPRESSED AIR” (Combustion v44 n6
Dec.1972 p32-40; Hereafter referred to as Report A. and
Combustion v45 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）による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 pressure 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 a 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 account, 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 aimed at significantly improving 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圧縮機最
終段出口で圧縮空気の一部もしくは全部を冷却す
るという記載があるがその冷却媒体である冷却水
はいずれも該接触操作にて得られる液相水ではな
くサイクル外からの冷却水であり圧縮空気を冷却
後再びサイクル内で利用されることなくサイクル
外に捨てられるため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. Some of these patents mention that some or all of the compressed air is cooled at the outlet of the final stage of the compressor, but the cooling water used as the cooling medium is not liquid water obtained through the contact operation. Since the cooling water is from outside the cycle and is discarded outside the cycle without being used again in the cycle after cooling the compressed air, it is inferior to the present invention from the viewpoint of thermal efficiency of the gas turbine cycle.
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。（特許昭55−155399号他）
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の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への適用と
の組合せを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
液相水の補給に供せられる液相水を圧縮機の中間
冷却に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、更に、該接触操作に用いる圧
縮空気の冷却を該接触操作にて冷却される液相水
の一部で行なう方法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 inventor recovers and replenishes the heat of 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. They discovered that thermal efficiency could be improved by performing intermediate cooling of the compressor with liquid phase water, and filed a patent application earlier. (Patent No. 55-155399, etc.) After that, we continued to study methods for water injection and heat recovery, and furthermore, methods for producing heat recovery media. Application of 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 as a heat recovery medium for heat recovery of turbine exhaust and intercooling of compressors. using a combination of and evaporating in the contact operation,
By using the liquid phase water, which is used to replenish the liquid phase water that has migrated into the compressed air as a mixture with the compressed air, for intermediate cooling of the compressor, it is possible to improve thermal efficiency over the water injection gas turbine cycle described in the above report. They discovered this, and further discovered a method for cooling the compressed air used in the contacting operation with a portion of the liquid phase water cooled in the contacting operation, thereby completing the present invention. 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
必要に応じ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、該接触操作で得られる冷却さ
れた液相水を熱回収媒体として該接触操作に用い
る圧縮空気の冷却に用い、かつ該接触操作で蒸発
し空気との混合物として圧縮空気中に移行した量
に当たる液相水を必要に応じ熱回収媒体とし使用
して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, if necessary, intermediate cooling of the compressor, the cooled liquid phase water obtained in the contact operation is used as a heat recovery medium to cool the compressed air used in the contact operation, and the contact The amount of liquid phase water that evaporates during the operation and transfers into the compressed air as a mixture with air is used as a heat recovery medium as necessary to replenish the liquid phase water provided for the contact operation and the heat recovery operation. This is a gas turbine cycle.
本発明は、上記のごとく接触操作にて得られる
冷却された液相水を該接触操作に用いる圧縮空気
の冷却にも用いることにより、より温度レベルの
低下した該液相水を得、各部熱回収器における熱
回収をより有効に達成できるごとくするものであ
る。 The present invention uses the cooled liquid phase water obtained in the contact operation as described above to cool the compressed air used in the contact operation, thereby obtaining the liquid phase water at a lower temperature level, and heats each part. This allows heat recovery in the recovery device to be achieved more effectively.
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。 Hereinafter, an example of a flow sheet of the present invention will be explained with reference to the accompanying drawings.
第１図は、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、接触操作に用いる圧縮空気の冷却に用いる熱
交換器（以下、自己熱交換器と記す）１、中間冷
却器１、空気圧縮器２、タービン１の場合であ
る。 Figure 1 shows 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, and a heat exchanger (hereinafter referred to as a self-contained heat exchanger) used for cooling the compressed air used in the contact operation. This is the case of a heat exchanger) 1, an intercooler 1, an air compressor 2, and a turbine 1.
第２図は第１図において交換塔EXTを２段式
EXT1，EXT2としてタービン排気の熱回収器R2
の液相水による熱回収側を２段とするという変更
を行なつた場合である。 Figure 2 shows the exchange tower EXT as a two-stage type in Figure 1.
EXT 1 , EXT 2 as turbine exhaust heat recovery device R 2
This is a case where the heat recovery side using liquid phase water is changed to two stages.
第１図において、空気圧縮器AC1に吸入された
大気空気３は断熱圧縮され管４より中間冷却器
ICに入り、ここで交換器EXTよりの液相水２４
と加圧水導入管２からの補給液相水とからなる液
相水１７により冷却され管５より空気圧縮機AC2
で再び断熱圧縮され圧縮空気６とされる。圧縮空
気６の一部は必要に応じて管８より高温側熱回収
器R1に導かれ、残部は管７より自己交換器SRに
入り冷却され管９より交換塔EXTに導入される。
交換塔EXTには熱回収器R2、自己熱交換器SRお
よび中間冷却器ICにてそれぞれ熱回収媒体とし
て用い加熱された液相水が管２２，１９，１８よ
り導入されており、ここで圧縮空気と該液相水と
が向流形の直接接触を行ない、管１０より水蒸気
分圧を行められた圧縮空気／水蒸気の混合物とし
て高温側熱回収器R1に導入される。また、該接
触操作で冷却された液相水は起２０からそれぞれ
自己熱交換器SR、熱回収器R2、中間冷却器ICへ
管２３，２１，２４を経て送られ熱回収された液
相水となつて交換塔EXTへ還流される。高温側
熱回収器R1に導入された圧縮空気／水蒸気の混
合物は必要に応じて空気圧縮機AC2より直接８か
ら導入される圧縮空気とともに熱回収を行なつた
後、管１１より燃焼器CCに導入される。燃焼器
CCには熱回収器R3にて熱回収を行なつて燃料１
が管２５より導入されており、所定温度の燃焼ガ
スとなり１２よりタービンETに導入される。燃
焼ガスはタービンETにて断熱膨張し、空気圧縮
機AC1，AC2、および負荷Ｌの駆動力を発生し１
３より排出され、一部は管２６より燃料の熱回収
器R3に、残部は１４より高温側熱回収器R1、更
に管１５を介して低温側熱回収器R2で熱回収さ
れて、管１６を介し廃ガス２７としてサイクル外
に排出される。 In Figure 1, atmospheric air 3 taken into air compressor AC 1 is adiabatically compressed and sent to intercooler via pipe 4.
Enters the IC, where the liquid phase water 24 from the exchanger EXT
The air compressor AC 2 is cooled by the liquid phase water 17 consisting of the liquid phase water and make-up liquid phase water from the pressurized water introduction pipe 2,
The air is then adiabatically compressed again to form compressed air 6. A part of the compressed air 6 is guided to the high-temperature side heat recovery unit R 1 through a pipe 8 as required, and the remaining part enters the self-exchanger SR through a pipe 7 and is cooled, and then introduced through a pipe 9 to the exchange tower EXT.
Liquid phase water heated as a heat recovery medium in the heat recovery unit R 2 , the self-heat exchanger SR and the intercooler IC is introduced into the exchange tower EXT through pipes 22, 19 and 18. The compressed air and the liquid phase water are brought into direct contact in a countercurrent manner, and are introduced into the high-temperature side heat recovery device R1 through a pipe 10 as a compressed air/steam mixture with a partial pressure of water vapor. In addition, the liquid phase water cooled by the contact operation is sent from the generator 20 to the self-heat exchanger SR, the heat recovery device R 2 , and the intercooler IC via pipes 23, 21, and 24, and the liquid phase water from which the heat is recovered is It becomes water and is returned to the exchange tower EXT. The compressed air/steam mixture introduced into the high-temperature side heat recovery device R 1 undergoes heat recovery together with the compressed air introduced directly from the air compressor AC 2 from the air compressor AC 2 as required, and then is transferred to the combustor from the pipe 11. Introduced to CC. combustor
For CC, heat is recovered in heat recovery device R3 and fuel 1
is introduced through pipe 25, and becomes combustion gas at a predetermined temperature, which is then introduced into turbine ET through 12. The combustion gas expands adiabatically in the turbine ET and generates the driving force for the air compressors AC 1 , AC 2 and the load L.
A part of the fuel is discharged from the fuel heat recovery unit R 3 through the pipe 26, and the remainder is recovered through the high temperature side heat recovery unit R 1 from the pipe 14 and further through the low temperature side heat recovery unit R 2 via the pipe 15. , is discharged out of the cycle as waste gas 27 via pipe 16.
次に第２図は、上記した交換塔操作を２段とし
たフローシートであり、交換塔EXT1，EXT2の
中間からの液相水をもタービン排気の熱回収に適
用し、より有効な熱回収をするごとくしたもので
あり、又、空気圧縮機AC2よりの圧縮空気の一部
が高温側熱回収器R1に導かれる場合に、交換塔
操作にて生ずる圧力損失に見合う圧縮のための圧
縮機AC3も付加した他は、第１図と同様である。
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。 Next, Figure 2 is a flow sheet in which the above exchange tower operation is performed in two stages, and the liquid phase water from the middle of the exchange towers EXT 1 and EXT 2 is also applied to heat recovery from the turbine exhaust gas, making it more effective. It is designed to recover heat, and when a part of the compressed air from the air compressor AC 2 is led to the high temperature side heat recovery device R 1 , the compression rate is sufficient to compensate for the pressure loss caused by the exchange tower operation. The structure is the same as that shown in Fig. 1, except that a compressor AC 3 is also added.
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, because 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 results in further improvements in thermal efficiency. This contributes to improvement.
以上、図面によつて本発明のフローの一例を示
したが、本発明は圧縮空気の一部もしくは全部に
液相水を接触させて得られる液相水で該接触操作
に用いる圧縮空気の冷却タービン排気の熱回収お
よび必要に応じて圧縮機の中間冷却とを行うもの
であつて、この操作を用いるかぎりにおいて種々
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抑制が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）
などがあり、圧縮比と熱効率との関係からは高圧
縮比においても熱効率の低下率が従来のガスター
ビンサイクルに比べてより小さいという特徴のあ
るものであり、高比出力化あるいは再熱サイクル
化したときのメリツトが大きい。 An example of the flow of the present invention has been shown above with reference to the drawings, but the present invention cools the compressed air used in the contact operation with liquid phase water obtained by contacting part or all of the compressed air with liquid phase water. The system performs heat recovery from the turbine exhaust gas and, if necessary, intermediate cooling of the compressor, and various modifications can be made as long as this operation is used. For example, when using fuel for intercooling, reheating cycle, adding a condensation recovery device for water in waste gas, when the fuel is gas from natural gas or coal gasification equipment, etc.
In order to effectively recover heat for NO and liquid phase water as a heat recovery medium (Special Publication No. 63-29091)
From the relationship between compression ratio and thermal efficiency, the rate of decrease in thermal efficiency is smaller than that of conventional gas turbine cycles even at high compression ratios. There are great benefits when you do.
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）移動がより有利に利用でき
る範囲としてまず、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、自己熱交換器、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 (water) transfer through direct contact between compressed air and liquid water is more efficient. As for the range that can be advantageously used, 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 it is used in self-heat exchangers, turbine exhaust heat recovery, intercooling, etc. The water is diverted to the high-temperature heat recovery device as appropriate based on the desired amount of cooled liquid phase water obtained in the contact operation, the practical conditions of the contact operation, the size of the equipment used, and restrictions on exhaust gas temperature. . Further, the amount of water that is evaporated by contact with compressed air and transferred into the compressed air as a mixture of compressed air/steam is also selected in accordance with the implementation.
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、第１図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／水蒸気の混合物として圧縮空気中に移行させ
る水量は、全吸入空気１Kgmolあたり0.1〜0.2Kg
mol、好ましくは0.12〜0.16Kgmolの範囲である。
また、圧縮機において、中間冷却を施す場合の段
前後の圧力配分は、中間冷却による圧縮動力の低
減効率をより大きくするとの点より判断されるべ
きものである。 This preferred operating range naturally changes depending on the use of fuel for intercooling, reheat cycle, addition of a condensation recovery device for water in waste gas, or turbine inlet conditions. For example, in the flow sheet shown in Figure 1, when the turbine inlet conditions are 6at pressure and a temperature of 1000℃, the amount of water transferred into the compressed air as a mixture of compressed air/steam is 0.1 to 0.2Kg per 1Kgmol of total intake air.
mol, preferably in the range of 0.12 to 0.16 Kgmol.
Further, in a compressor, the pressure distribution before and after stages when performing intercooling should be determined from the viewpoint of increasing the compression power reduction efficiency 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 0.132Kgmol／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 IC 20℃
自己熱交換器 SR 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。また、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 0.132Kgmol/s (f) Turbine inlet conditions Pressure 6at Temperature 1000℃ (g) Heat exchanger minimum temperature difference High temperature side heat recovery device R 1 30 ℃ Low-temperature side heat recovery device R 2 20℃ Fuel preheater R 3 30℃ Intercooler IC 20℃ Self-heat exchanger SR 20℃ (h) Others Compression power of fuel, make-up water, and exchange tower bottom water is ignored. , 0.3% of the generating end output was considered as the in-house power. In addition, the required amount of turbine cooling air was set taking into consideration that low-temperature compressed air can be obtained in this cycle.
() 結果 (a) 廃ガス 温度 82.7℃ 流量 1.15Kgmol／ｓ (b) 圧縮機AC2出力温度 148℃ (c) 送電端出力 8690KW (d) 送電端熱効率 50.2％() Results (a) Waste gas temperature 82.7℃ Flow rate 1.15Kgmol/s (b) Compressor AC 2 output temperature 148℃ (c) Sending end output 8690KW (d) Sending end thermal efficiency 50.2%
第１図は本発明の一例を示すフローシート、第
２図は第１図の変更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、６は圧縮空
気、７，８，９，１０，１８，１９，２０，２
１，２２，２３，２４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、SRは自己熱交換器、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。
FIG. 1 is a flow sheet showing an example of the present invention, and FIG. 2 is a flow sheet showing a modification of FIG. 2 is a pressurized water introduction pipe, 3 is atmospheric air, 6 is compressed air, 7, 8, 9, 10, 18, 19, 20, 2
1, 22, 23, and 24 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, SR is a self-heat exchanger, and EXT is a heat recovery device. Exchange tower, AC 1 , AC 2 are air compressors, CC is combustor, ET
indicates the turbine, and L indicates the 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必要に応じ圧縮機の
中間冷却を行うガスタービンサイクルにおいて、
該接触操作で得られる冷却された液相水を熱回収
媒体として該接触操作に用いる圧縮空気の冷却に
用い、かつ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必
要に応じ熱回収媒体とし使用して該接触操作およ
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 the turbine exhaust, and use the cooled liquid phase water as a heat recovery medium for heat recovery of the turbine exhaust and as needed. In the gas turbine cycle, which performs intermediate cooling of the compressor,
The cooled liquid phase water obtained in the contact operation is used as a heat recovery medium to cool the compressed air used in the contact operation, and the amount of liquid that evaporates in the contact operation and transfers into the compressed air as a mixture with air. A gas turbine cycle in which phase water is used as a heat recovery medium as necessary to replenish liquid phase water used for the contact operation and the heat recovery operation.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19936481A JPS58101228A (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 |
| CA000417429A CA1218240A (en) | 1981-12-10 | 1982-12-10 | Regenerative gas turbine cycle |
| EP82306607A EP0081996B1 (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 |
|---|---|---|---|
| JP19936481A JPS58101228A (en) | 1981-12-10 | 1981-12-10 | Gas turbine cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58101228A JPS58101228A (en) | 1983-06-16 |
| JPH0131013B2 true JPH0131013B2 (en) | 1989-06-22 |
Family
ID=16406524
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19936481A Granted JPS58101228A (en) | 1981-12-10 | 1981-12-10 | Gas turbine cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58101228A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998048159A1 (en) * | 1997-04-22 | 1998-10-29 | Hitachi, Ltd. | Gas turbine equipment |
| JP2004360700A (en) * | 2003-06-06 | 2004-12-24 | General Electric Co <Ge> | Method and apparatus for operating a gas turbine engine |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6093133A (en) * | 1983-10-28 | 1985-05-24 | Mitsubishi Gas Chem Co Inc | gas turbine cycle |
| ZA85528B (en) * | 1984-02-01 | 1986-12-30 | Fluor Corp | Process for producing power |
| WO2013069111A1 (en) * | 2011-11-09 | 2013-05-16 | 株式会社日立製作所 | Gas turbine electricity generation device and operating method therefor |
-
1981
- 1981-12-10 JP JP19936481A patent/JPS58101228A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998048159A1 (en) * | 1997-04-22 | 1998-10-29 | Hitachi, Ltd. | Gas turbine equipment |
| JP2004360700A (en) * | 2003-06-06 | 2004-12-24 | General Electric Co <Ge> | Method and apparatus for operating a gas turbine engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58101228A (en) | 1983-06-16 |
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