JPS60138214A - Gas turbine composite cycle power generating plant - Google Patents
Gas turbine composite cycle power generating plantInfo
- Publication number
- JPS60138214A JPS60138214A JP24928683A JP24928683A JPS60138214A JP S60138214 A JPS60138214 A JP S60138214A JP 24928683 A JP24928683 A JP 24928683A JP 24928683 A JP24928683 A JP 24928683A JP S60138214 A JPS60138214 A JP S60138214A
- Authority
- JP
- Japan
- Prior art keywords
- organic medium
- temperature side
- steam
- condenser
- pipe
- 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
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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
-
- 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]
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)
Abstract
Description
【発明の詳細な説明】
〔発明の分野〕
本発明はガスタービン複合サイクル発電プラントに係シ
、特に低沸点有機媒体を用いたサイクルを組み合せた廃
熱回収方式の複合サイクル発電プラントに関する。DETAILED DESCRIPTION OF THE INVENTION [Field of the Invention] The present invention relates to a gas turbine combined cycle power plant, and more particularly to a waste heat recovery combined cycle power plant combining a cycle using a low boiling point organic medium.
第１図に廃熱回収方式のガスタービン複合サイクル発電
プラントの一般的な例を示す。第１図において、燃焼用
空気１が低圧コンプレッサ２に与えられ、次いで高圧コ
ンプレッサ３により圧縮された後、燃焼器４に供給され
る。なお、低圧コンプレッサ２と高圧コンプレッサ３と
の中間段には中間冷却器（熱交換器）５が設けられてい
る。この中間冷却器５は、低圧および高圧コンプレッサ
２．３での圧縮比が大きくなると材料面や効率面で好ま
しくないので中間段において圧縮空気を冷却するための
ものである。すなわち、コンプレッサは本来的に断熱変
化があるため、作動流体（空気）温度（絶対温度）に比
例して断熱圧縮動力が増大することとなり、この増大は
ガスタービン発電において損失となるため、極力低減す
ることが望ましいからである。一般に冷却媒体６として
水が用いられ、水に回収された熱は大気に放散させてい
る。Figure 1 shows a typical example of a gas turbine combined cycle power plant using the waste heat recovery method. In FIG. 1, combustion air 1 is applied to a low pressure compressor 2, then compressed by a high pressure compressor 3, and then supplied to a combustor 4. Note that an intermediate cooler (heat exchanger) 5 is provided at an intermediate stage between the low-pressure compressor 2 and the high-pressure compressor 3. This intercooler 5 is for cooling the compressed air in the intermediate stage, since it is undesirable in terms of materials and efficiency if the compression ratio of the low-pressure and high-pressure compressors 2.3 increases. In other words, since compressors inherently undergo adiabatic changes, the adiabatic compression power increases in proportion to the working fluid (air) temperature (absolute temperature), and this increase results in loss in gas turbine power generation, so it should be reduced as much as possible. This is because it is desirable to do so. Generally, water is used as the cooling medium 6, and the heat recovered in the water is dissipated into the atmosphere.
さて、燃焼器４からの燃焼ガスはガスタービン７に供給
されて仕事をし、排ガスとして廃熱回収ボイラ８を経て
煙突９から排出される。なお、４６は発電機である。Now, the combustion gas from the combustor 4 is supplied to the gas turbine 7 to do work, and is discharged from the chimney 9 via the waste heat recovery boiler 8 as exhaust gas. Note that 46 is a generator.
廃熱回収ボイラ８にはガスタービン７からの排ガスの廃
熱を利用する発電、システムＩＯが設ケラれている。こ
の廃熱回収方式と１．て良く知られているものに多段圧
力式ランキンサイクルがある。The waste heat recovery boiler 8 is equipped with a power generation system IO that utilizes the waste heat of the exhaust gas from the gas turbine 7. This waste heat recovery method and 1. A well-known example is the multi-stage pressure Rankine cycle.
これは、廃熱回収ボイラ８において入口側から出口側に
向かって徐々に排ガス温度が降下するに応じた圧力で蒸
気を発生させ、その発生蒸気をその圧力に応じたタービ
ンの段落に投入することにより、タービンを駆動するも
のである。ガスタービンの排ガスについて考えた場合、
一般に２段圧力式が経済的見地からして限度とされる。This involves generating steam at a pressure that corresponds to the temperature of the exhaust gas gradually decreasing from the inlet side to the outlet side in the waste heat recovery boiler 8, and injecting the generated steam into the turbine stage that corresponds to the pressure. This is what drives the turbine. When considering gas turbine exhaust gas,
Generally, a two-stage pressure type is considered to be the upper limit from an economical point of view.
つまり、さらに低圧段を増設しても水（Ｈ，Ｏ）を媒体
とする多段ランキンサイクルでは物性的にあまり高い出
力が望めず、非現実的なものとなるからである。In other words, even if a low-pressure stage is added, a multi-stage Rankine cycle using water (H, O) as a medium cannot expect a very high output due to its physical properties, making it unrealistic.
通常、ガスタービンの排気ガスの温度は４５０〜５００
℃である。このレベルの温度のエネルギを有効な機械的
仕事に変換するランキンサイクルの媒体とｌ〜てけ、安
定物質の面および安全性の面から「水」あるいけ［低沸
点有機媒体であるフロリノール８５Ｊが実用化されてい
る。なお、低沸点有機媒体としては上記の他に［フレオ
ンＪ。Normally, the temperature of the exhaust gas of a gas turbine is 450 to 500.
It is ℃. Water is considered the medium of the Rankine cycle that converts energy at this level of temperature into useful mechanical work, from the standpoint of stability and safety. has been made into In addition to the above, examples of the low boiling point organic medium include [Freon J.
「イソブタン」等の炭化水素系有機物質でもよい。Hydrocarbon-based organic substances such as "isobutane" may also be used.
また、上記フロリノールは実際には作動温度３００〜３
５０℃程度で若干低目の温度で使用されている。In addition, the above Florinol actually has an operating temperature of 300 to 3
It is used at a slightly lower temperature of around 50°C.
ここで、ランキンサイクルの媒体として「水」を用いた
廃熱回収方式の発電システムの従来の例を第２図に示す
。このシステム（第２図）は、廃熱回収ボイラ８の高温
側の廃熱を利用する発電システム（以下、高温側システ
ムという。）１１と、低温側の廃熱を利用する発電シス
テム（以下、低温側システムという。）１２により廃熱
回収ボイラ８内の温度降下に応じて高低の２段で構成さ
れている。すなわち、高温側はエクセルギー（機械的有
効仕事と定義される。）が高く、低温側はエクセルギー
が低いのでそれぞれを有効なエネルギに変換するために
上述の如く２段構成としているのである。Here, FIG. 2 shows a conventional example of a waste heat recovery type power generation system using "water" as the medium of the Rankine cycle. This system (Fig. 2) consists of a power generation system (hereinafter referred to as the high temperature side system) 11 that utilizes waste heat on the high temperature side of the waste heat recovery boiler 8, and a power generation system (hereinafter referred to as the high temperature side system) that utilizes the waste heat on the low temperature side of the waste heat recovery boiler 8. (referred to as a low-temperature side system) 12, it is configured with two stages, one high and one low, depending on the temperature drop within the waste heat recovery boiler 8. That is, the high temperature side has high exergy (defined as mechanical effective work), and the low temperature side has low exergy, so in order to convert each into effective energy, the two-stage configuration is used as described above.
第２図において、廃熱回収ボイラ８内には、入口側から
出口側に向かって（つまり、高温側から低温側に向かっ
て）第１加熱管１３、第１予熱管１４、第２加熱管１５
、第２予熱管１６が順次設置されている。第１加熱管１
３および第１予熱管１４け高温側システム１１に属し、
第２加熱管１５および第２予熱管１６け低温側システム
１２に属する。高圧蒸気ドラム１７で発生した蒸気は第
１加熱管１３に送られ、廃熱により加熱されて過熱蒸気
となって蒸気タービン１８の高圧段に導入される。蒸気
タービン１８からの排気は復水器１９により復水されそ
の復水は脱気器２０を介して低圧給水ポンプ２１により
、第２予熱管１６に供給される。予熱された復水は低圧
蒸気ドラム２２に送られる。なお、低圧蒸気ドラム２２
の缶水は缶水循環ポンプ２３により缶水予熱管２４に送
られて予熱される一方、高圧給水ポンプ２５により第２
予熱管１４に送られて予熱された後、高圧蒸気ドラム１
７に戻される。高圧蒸気ドラム１７の缶水も缶水循環ポ
ンプ２６により缶水予熱管２７により予熱される。一方
、低圧蒸気ドラム２２により発生した蒸気は第２加熱管
１５により加熱された後、蒸気タービン１８の低圧段に
供給される。In FIG. 2, inside the waste heat recovery boiler 8, from the inlet side to the outlet side (that is, from the high temperature side to the low temperature side), there is a first heating pipe 13, a first preheating pipe 14, and a second heating pipe. 15
, and second preheating tube 16 are installed in sequence. First heating tube 1
3 and the first preheating pipe 14 belong to the high temperature side system 11,
The second heating pipe 15 and the second preheating pipe 16 belong to the low temperature side system 12 . The steam generated in the high-pressure steam drum 17 is sent to the first heating pipe 13, heated by waste heat, becomes superheated steam, and is introduced into the high-pressure stage of the steam turbine 18. Exhaust gas from the steam turbine 18 is condensed by a condenser 19, and the condensate is supplied to the second preheating pipe 16 via a deaerator 20 by a low-pressure feed water pump 21. The preheated condensate is sent to the low pressure steam drum 22. In addition, the low pressure steam drum 22
The canned water is sent to the canned water preheating pipe 24 by the canned water circulation pump 23 and preheated, while the canned water is sent to the canned water preheating pipe 24 by the high pressure water supply pump 25.
After being sent to the preheating pipe 14 and preheated, the high pressure steam drum 1
It will be returned to 7. The canned water in the high-pressure steam drum 17 is also preheated by the canned water preheating pipe 27 by the canned water circulation pump 26 . On the other hand, the steam generated by the low-pressure steam drum 22 is heated by the second heating pipe 15 and then supplied to the low-pressure stage of the steam turbine 18.
２８目、発電機を示している。Number 28 shows a generator.
次に、水と低沸点有機媒体の物性に着目してみる。水の
場合は蒸発潜熱が大きく有機媒体の場合は小さい。第３
図は廃熱回収ボイラ８における熱流線図を示したもので
「実＃ＪＦ′ｉ水の場合、「鎖線」は有機媒体の場合を
それぞれ示したものである。Ｔ１け廃熱回収ボイラ８の
入口ガス温度、ＴＯは水の場合の出口ガス温度、Ｔｏ′
は有機媒体の場合の出口ガス温度である。まだ、ｒＷは
水の蒸発潜熱、ｒｆけ有機媒体の蒸発潜熱を示している
。この第３図の熱流線図によれば、水の場合と有機媒体
でｄ廃熱回収ボイラでのピンチポイントΔＴを一定とし
、かつ、ある一定の圧力レベルを維持した場合（なお、
圧力を高める程うンキンザイクルの効率は良くなる。）
廃熱回収ボイラ８の出口ガス温度は水の場合（ＴＯ）よ
りも有機媒体の場合（Ｔｏ’）の方が低下していること
がわかる。このことは、廃熱回収ボイラの低温側のエク
セルギーを機械的エネルギに効率良く変換するためには
低沸点有機媒体が有利となることを意味する。このよう
なことから、低温側に有機媒体を用いた発電システムの
例を第４図に示す。Next, we will focus on the physical properties of water and low-boiling organic media. The latent heat of vaporization is large for water and small for organic media. Third
The figure shows a heat flow diagram in the waste heat recovery boiler 8, and the "dotted line" shows the case of "actual #JF'i water" and the "dashed line" shows the case of organic medium, respectively. T1 is the inlet gas temperature of the waste heat recovery boiler 8, TO is the outlet gas temperature in the case of water, To'
is the outlet gas temperature for organic media. Furthermore, rW indicates the latent heat of vaporization of water, rf indicates the latent heat of vaporization of organic medium. According to the heat flow diagram in Fig. 3, when the pinch point ΔT in the d waste heat recovery boiler is constant in the case of water and the organic medium, and a certain pressure level is maintained (
The higher the pressure, the better the efficiency of the engine. )
It can be seen that the outlet gas temperature of the waste heat recovery boiler 8 is lower in the case of organic medium (To') than in the case of water (TO). This means that a low boiling point organic medium is advantageous for efficiently converting exergy on the low temperature side of the waste heat recovery boiler into mechanical energy. For this reason, FIG. 4 shows an example of a power generation system using an organic medium on the low temperature side.
第４図において、高温側システム１１の構成は基本的に
は第３図のものと変りはない。すなわち、廃熱回収ボイ
ラ８内には順次高温側から低温側に向かって、第１加熱
管１３、缶水予熱管２７、第１予熱管１４、第２加熱管
１５が設けられている。In FIG. 4, the configuration of the high temperature side system 11 is basically the same as that in FIG. 3. That is, in the waste heat recovery boiler 8, a first heating pipe 13, a canned water preheating pipe 27, a first preheating pipe 14, and a second heating pipe 15 are provided in order from the high temperature side to the low temperature side.
第２予熱管、１６および缶水予熱管２７は蒸気ドラムが
ないので存在しない。高圧側システム１１において、高
圧蒸気ドラム１７で発生した蒸気は第１加熱管１３によ
り加熱された後、蒸気タービン１８に導入されて仕事を
する。蒸気タービン１８からの排気は復水器１９にて復
水され、その復水は給水ポンプ２９により蒸気ドラム１
７に回収される。一方、低圧側システム１２において、
有機媒体蒸気タービン３０からの排ガスは復水器３１に
て復水され、給水ポンプ３２により第２加熱管１５に送
られる。第２加熱管１５で加熱された有機媒体蒸気は有
機媒体蒸気タービン３０の高圧段に入力されて仕事をす
る。The second preheating pipe 16 and the canned water preheating pipe 27 are not present since there is no steam drum. In the high-pressure side system 11, steam generated in the high-pressure steam drum 17 is heated by the first heating pipe 13, and then introduced into the steam turbine 18 to perform work. The exhaust gas from the steam turbine 18 is condensed in a condenser 19, and the condensed water is sent to the steam drum 1 by a water supply pump 29.
It will be collected on 7th. On the other hand, in the low pressure side system 12,
Exhaust gas from the organic medium steam turbine 30 is condensed in a condenser 31 and sent to the second heating pipe 15 by a feed water pump 32. The organic medium steam heated by the second heating pipe 15 is input to the high pressure stage of the organic medium steam turbine 30 to perform work.
以上の低温側システム１２に有機媒体を用いた発電シス
テム（第４図）によれば、第２図の水のみを用いた発電
システムより廃熱回収効率がよく、したがって結果的に
発電出力を増加させうるものであり、このことは第３図
からも理解できる（出口温度ＴｏとＴｏ’参照）。According to the power generation system (Fig. 4) using an organic medium in the low-temperature side system 12 described above, the waste heat recovery efficiency is better than the power generation system using only water as shown in Fig. 2, and therefore the power generation output is increased as a result. This can be understood from FIG. 3 (see outlet temperatures To and To').
しかしながら、かかる従来のシステム（第４図）であっ
ても低温側のエクセルギーを機械的エネルギに変換する
ものとして充分に効率のよいものではなく、さらに一層
の発電出力の増大が望まれる。However, even such a conventional system (FIG. 4) is not sufficiently efficient in converting exergy on the low temperature side into mechanical energy, and a further increase in power generation output is desired.
そこで、本発明は高温側システムに水を用い、低温側シ
ステムに有機媒体を用いた発電システムにおいて、比較
的簡単な構成で発電出力を一層増大しうるガスタービン
複合サイクル発電プラントを提供することを目的とする
。Therefore, the present invention aims to provide a gas turbine combined cycle power generation plant that can further increase the power generation output with a relatively simple configuration in a power generation system that uses water in the high temperature side system and an organic medium in the low temperature side system. purpose.
上記目的を達成するために、本発明による発電。 In order to achieve the above object, power generation according to the present invention.
プラントは廃熱回収ボイラの高温側に媒体として水を用
いたランキンサイクルで構成される発電システムを用い
、低温側には低沸点有機媒体のランキンサイクルで構成
される発電、システムを組み合せた複合サイクル発電プ
ラントにおいて、高温側システムの復水器（第１復水器
）の冷却流体として低温側システムの有機媒体を導入す
ることにより、高圧側システムの廃熱を低温側システム
に有効に回収しうるようにした点に特徴を有する。The plant uses a power generation system consisting of a Rankine cycle that uses water as a medium on the high temperature side of the waste heat recovery boiler, and a combined cycle system that combines the power generation system and the system that uses a Rankine cycle with a low boiling point organic medium on the low temperature side. In a power generation plant, waste heat from the high-pressure system can be effectively recovered to the low-temperature system by introducing an organic medium from the low-temperature system as a cooling fluid for the condenser (first condenser) of the high-temperature system. It is characterized by the fact that it is made as follows.
以下、本発明によるガスタービン複合サイクル発電プラ
ントの実施例を図面に基づいて説明する。Embodiments of the gas turbine combined cycle power plant according to the present invention will be described below with reference to the drawings.
第５図に本発明の一実施例を示す。なお、第５図におい
て第１図、第２図、第４図に示した部分と重複する部分
には同一符号を附してあり、単線は水ザイクル、複線は
有機媒体サイクルを示している。前述のように、このシ
ステムの特徴は高温側システム１１の復水器（以下、第
１復水器）３３の冷却管３４の入口側に低温側システム
の復水器（以下、第２復水器）３５からの復水有機媒体
を供給する配管３６を配し、かつ、冷却管３４の出口側
に第２加熱管１５に通じる配管３７を配し、低温側シス
テム１２の有機媒体を第１復水器３３の冷却流体として
用いるようにしたものである。FIG. 5 shows an embodiment of the present invention. In FIG. 5, parts that overlap with those shown in FIGS. 1, 2, and 4 are given the same reference numerals, and a single line indicates a water cycle, and a double line indicates an organic medium cycle. As mentioned above, the feature of this system is that the condenser of the low temperature side system (hereinafter referred to as the second condenser) is placed on the inlet side of the cooling pipe 34 of the condenser (hereinafter referred to as the first condenser) 33 of the high temperature side system 11. A pipe 36 is arranged to supply the condensed organic medium from the cooling pipe 35, and a pipe 37 communicating with the second heating pipe 15 is arranged on the outlet side of the cooling pipe 34, so that the organic medium from the low temperature side system 12 is supplied to the first heating pipe 15. It is designed to be used as a cooling fluid for the condenser 33.
したがって、蒸気タービン１８からの排気の熱は第１復
水器３３において有機媒体に回収されることとなり、間
接的に廃熱回収ボイラ８の廃熱を無駄なく低温側におい
て回収することとなり、回収効率が向上する。このこと
はプラント全体としての効率の向上に寄与し、発電出力
の向上を達成できることとなる。３８はコンデンセート
ポンプを示している。Therefore, the heat of the exhaust gas from the steam turbine 18 is recovered into the organic medium in the first condenser 33, and the waste heat of the waste heat recovery boiler 8 is indirectly recovered on the low temperature side without waste. Increased efficiency. This contributes to improving the efficiency of the entire plant, making it possible to improve the power generation output. 38 indicates a condensate pump.
ところで、給水ポンプ３２からの配管は第１復水器３３
に向かう配管３６から分岐されて第１復水器３３のバイ
パス路を形成する配管３９には電磁弁４０が挿入されて
いる。この電磁弁４０はガスタービン７（第１図）の負
荷が下がった場合（熱源が減少したとき）に高圧側シス
テム１１の稼動を停止させて有機媒体による低圧側シス
テム１２のみの廃熱回収発電の運転に切替えるだめのも
のである。（この際、−ヒ流の蒸気サイクルを全く停止
することはボイラ伝熱管の保護の観、点から好ましくな
く、給水のみ循環させ、発生する熱水を蒸気タービン１
８をバイパスする回路４７を設けである。）
さらに、廃熱回収ボイラ８からの廃熱回収効率を向上さ
せるため、第２予熱管１６の入口側にはコンデンセート
ポンプ３８の出口配管から分岐された配管４１が配され
ている。第２予熱管１６の出口側は有機媒体蒸気タービ
ン３０の低圧段に配管４２がなされ、これによって第２
予熱管１６により予熱された有機媒体蒸気が供給される
ようになっている。By the way, the piping from the water supply pump 32 is connected to the first condenser 33.
A solenoid valve 40 is inserted into a pipe 39 that is branched from a pipe 36 leading to the first condenser 33 and forms a bypass path for the first condenser 33 . This electromagnetic valve 40 stops the operation of the high-pressure side system 11 when the load on the gas turbine 7 (Fig. 1) decreases (when the heat source decreases), and generates waste heat recovery power only in the low-pressure side system 12 using an organic medium. This means that you cannot switch to normal operation. (In this case, it is not preferable to completely stop the -H flow steam cycle from the viewpoint of protecting the boiler heat exchanger tubes, so only the feed water is circulated and the generated hot water is transferred to the steam turbine.
A circuit 47 is provided to bypass 8. Furthermore, in order to improve the efficiency of waste heat recovery from the waste heat recovery boiler 8, a pipe 41 branched from the outlet pipe of the condensate pump 38 is arranged on the inlet side of the second preheating pipe 16. The outlet side of the second preheating pipe 16 is connected to a pipe 42 to the low pressure stage of the organic medium steam turbine 30, and thereby the second
A preheating pipe 16 supplies preheated organic medium vapor.
なお、第５図において蒸気タービン１８と有機媒体蒸気
タービン３０とは同軸で発電機２８に連結されているが
、この態様に限らず別々に設け、各々のタービンに発電
機を連結する構成でもよい。Note that although the steam turbine 18 and the organic medium steam turbine 30 are coaxially connected to the generator 28 in FIG. 5, the present invention is not limited to this embodiment, and a configuration may also be adopted in which they are provided separately and a generator is connected to each turbine. .
以上は廃熱回収発電システム廃熱回収ボイラからの廃熱
回収効率に着目した例であるが、次にガスタービンフ側
、すなわちコンプレッサ側の廃熱を回収することによっ
て発電出力を向上しうるようにした実施例について説明
する。第６図にその実施例を示す。なお、以下に述べる
点以外Ｖ↓第５図と同一の構成なので同一の符号を附し
、説明を省略する。ただし、本実施例を適用するに当っ
て母体となる廃熱回収発電プラント自体は第４図の如き
既存設備であってもよく、またこの適用は有効である。The above is an example focusing on the waste heat recovery efficiency from the waste heat recovery boiler of the waste heat recovery power generation system. An example will be described below. An example is shown in FIG. It should be noted that the configuration is the same as V↓ in FIG. 5 except for the points described below, so the same reference numerals are given and the explanation will be omitted. However, in applying this embodiment, the base waste heat recovery power generation plant itself may be an existing facility as shown in FIG. 4, and this application is effective.
その理由り以下の説明から明らかとなる。The reason for this will become clear from the explanation below.
先の〔発明の背景〕の欄における低圧コンプレッサ２と
高圧コンプレッサ３の中間に設けられた中間冷却＆５の
説明で述べたように、従来では中間冷却器５の冷却媒体
６として「水」が用いられ、その回収された熱はしかる
べき手段を講じて大気（放散してい゛るものであった。As mentioned in the explanation of the intercooler &5 provided between the low-pressure compressor 2 and the high-pressure compressor 3 in the [Background of the Invention] column, conventionally, "water" was used as the cooling medium 6 of the intercooler 5. The recovered heat was dissipated into the atmosphere by appropriate means.
しかし、この低圧コンプレッサ２で発生した熱の大気へ
の放散は、低圧コンプレッサ２における断熱圧縮仕事の
一部を全て無駄にすることに等しい。もつとも、この場
合低圧コンプレッサ２の効率の面では問題ないが、しか
し冷却水によって持ち去られる熱量は損失となる。そこ
で、この冷却水の保有する熱の有効利用を図ったのが本
実施例である。However, this dissipation of the heat generated by the low-pressure compressor 2 into the atmosphere is equivalent to wasting part of the adiabatic compression work in the low-pressure compressor 2. Of course, in this case, there is no problem in terms of the efficiency of the low-pressure compressor 2, but the amount of heat carried away by the cooling water becomes a loss. Therefore, this embodiment aims to effectively utilize the heat held by this cooling water.
すなわち、中間冷却器５の温度レベルは廃熱回収ボイラ
８の低温部の温度とほぼ同程度である点に着目し、低温
側システム１２から有機媒体を中間冷却器５の冷却媒体
として導ひき、中間冷却器５の廃熱を低温側システム１
２に導入するものである。有機媒体ｔの導出方法として
は、配管４１の分岐点Ａから中間冷却器５の流入口４４
へ配管し、かつ流出口４５から配管４３０分岐点Ｂに戻
すようにするか、あるいは分岐点Ａから導出して配管４
２の分岐点Ｃに戻すようにする。この分岐点ＡとＢの組
み合せとするか、またはＡとＣの組み合せとするかは、
廃熱回収ボイラ８の低温部の温度レベルと中間冷却器５
の温度レベルとの相対的な差により適宜選択すればよい
。なお、分岐点ＢはＣよりも高温高圧である。That is, focusing on the fact that the temperature level of the intercooler 5 is approximately the same as the temperature of the low temperature section of the waste heat recovery boiler 8, an organic medium is introduced from the low temperature side system 12 as a cooling medium of the intercooler 5, The waste heat of the intercooler 5 is transferred to the low temperature side system 1.
This will be introduced in Section 2. The organic medium t can be led out from the branch point A of the pipe 41 to the inlet 44 of the intercooler 5.
The piping 430 can be routed through the outlet 45 and returned to the branch point B of the piping 430 from the outlet 45, or it can be led out from the branch point A and the piping 4
Return to branch point C in step 2. Whether to combine the branching points A and B or A and C is determined by
Temperature level of low temperature section of waste heat recovery boiler 8 and intercooler 5
It may be selected as appropriate depending on the relative difference from the temperature level. Note that branch point B is at a higher temperature and pressure than C.
このように中間冷却器５の廃熱をも低温側システムのラ
ンキンサイクル中に導入することにより、発電プラント
全体としての発電出力の増大を達成でき、第５図のシス
テムによる発電出力の増大と相まって相剰的に発電出力
の増大が可能となる。In this way, by introducing the waste heat of the intercooler 5 into the Rankine cycle of the low-temperature side system, it is possible to increase the power generation output of the power plant as a whole. It becomes possible to increase the power generation output in a complementary manner.
以上の通り、本発明によれば、水ランキンサイクルで構
成される高温側廃熱回収発電システムと有機媒体ランキ
ンサイクルで構成される低温側廃熱回収発電システムと
をガスタービン発電システムに組み合せた複合サイクル
発電プラントにおいて、−ヒ記高温側システムの廃熱を
当該システムの復水器（第１復水器）を介して低温側シ
ステムに導くようにしたことにより、廃熱の有効利用が
図れ、発電プラントの発電出力を増大させることができ
る。またこのことは、簡単な構成で実現することが可能
である。As described above, according to the present invention, a gas turbine power generation system is combined with a high temperature side waste heat recovery power generation system consisting of a water Rankine cycle and a low temperature side waste heat recovery power generation system consisting of an organic medium Rankine cycle. In a cycle power generation plant, waste heat from the high-temperature side system described in (h) is led to the low-temperature side system via the condenser (first condenser) of the system, thereby making it possible to effectively utilize the waste heat. The power generation output of the power generation plant can be increased. Moreover, this can be realized with a simple configuration.
第１図は一般的なガスタービン複合サイクル発電プラン
トのシステム構成を示すブロック図、第２図は従来の廃
熱回収発電システムの一〇例を示すブロック図、
第３図は廃熱回収ボイラにおいて媒体が水の場合と有機
媒体の場合を比較して示した熱流線図、第４図は従来の
廃熱回収発電システムの他の例を示すブロック図、
第５図は本発明による廃熱回収発電システムの−の実施
例を示すブロック図、
第６図はその他の実施例を示すブロック図である。
ｌ・・・燃焼用空気、 ２・・・低圧コンプレッサ、３
・・・高圧コンプレッサ、
４・・・燃焼器、４′・・・燃料、
５・・・中間冷却器、 ６・・・冷却媒体、７・・・ガ
スタービン、８・・・廃熱回収ボイラ、９・・・煙突、
１０・・・廃熱回収発電システム、
１１・”・・高温側システム、
１２・・・低温側システム、
１３・・・第１加熱管、１４・・・第１予熱管、１５・
・・第２加熱管、１６・・・第２予熱管、１７・・・蒸
気ドラム、１８・・・蒸気タービン、３０・・・有機媒
体蒸気タービン、
３３・・・第１復水器、 ３４・・・冷却管、３５・・
・第２復水器、 ３６・・・配管、３７・・・配管、
４２・・・配管、
４６・・・発電１機。
代理人 鵜 沼 辰 之
（ほか１名）
Ｑ７＋
一ト
第１図
１
第３図
第４図Figure 1 is a block diagram showing the system configuration of a typical gas turbine combined cycle power generation plant, Figure 2 is a block diagram showing 10 examples of a conventional waste heat recovery power generation system, and Figure 3 is a block diagram showing the system configuration of a typical gas turbine combined cycle power generation plant. A heat flow diagram comparing the cases where the medium is water and the case where the organic medium is used. Figure 4 is a block diagram showing another example of the conventional waste heat recovery power generation system. Figure 5 is the waste heat recovery according to the present invention. FIG. 6 is a block diagram showing another embodiment of the power generation system. l...Combustion air, 2...Low pressure compressor, 3
...High pressure compressor, 4...Combustor, 4'...Fuel, 5...Intercooler, 6...Cooling medium, 7...Gas turbine, 8...Waste heat recovery boiler , 9... Chimney, 10... Waste heat recovery power generation system, 11... High temperature side system, 12... Low temperature side system, 13... First heating pipe, 14... First preheating tube, 15・
...Second heating pipe, 16...Second preheating pipe, 17...Steam drum, 18...Steam turbine, 30...Organic medium steam turbine, 33...First condenser, 34 ...Cooling pipe, 35...
・Second condenser, 36... Piping, 37... Piping,
42...Piping, 46...1 power generator. Agent: Tatsuyuki Unuma (and 1 other person) Q7+ Hito Figure 1 Figure 3 Figure 4
Claims (1)
列された第１加熱管、予熱管および第２加熱管を備えた
廃熱回収ボイラと、 蒸気タービンからの排気を第１の復水器により復水し、
その復水を蒸気ドラムに供給して蒸気を発生させ、この
発生蒸気を前記第１加熱管により加熱してその加熱蒸気
を前記蒸気タービンの高圧段に送るようにした水ランキ
ンサイクルで構成される高温側発電システムと、 低沸点有機媒体蒸気タービンからの排気を第２の復水器
により復水し、その有機媒体復水を前記第２加熱管によ
り加熱してその加熱有機媒体蒸気を前記有機媒体蒸気タ
ービンの高圧段に送るようにした有機媒体ランキンサイ
クルで構成される低温側発電システムと、を備えたガス
タービン複合サイクル発電プラントにおいて、 前記第１復水器の冷却管の入口側に前記第２復水器から
の有機媒体復水を供給する配管を設け、かつ、前記冷却
管の出口側に第１復水器によって加熱された加熱有機媒
体復水を第２加熱管に供給する配管を設けたことを特徴
とするガスタービン複合サイクル発電プラント。 （２） 特許請求の範囲第１項記載の発電、プラントに
おいて、廃熱回収ボイラにおける第２過熱管よ ゛り低
温側に第２の予熱管を設け、前記第２復水器からの有機
媒体復水の一部を前記第２予熱管に導入して予熱し、予
熱された有機媒体復水を前記有機媒体蒸気タービンの低
圧段に供給する配管を設けたことを特徴とするガスター
ビン複合サイクル発電プラント。[Claims] (11) A waste heat recovery boiler comprising a first heating pipe, a preheating pipe, and a second heating pipe arranged sequentially from a high temperature side to a low temperature side of an outlet, and an exhaust gas from a steam turbine. is condensed by the first condenser,
It consists of a water Rankine cycle in which the condensate is supplied to a steam drum to generate steam, the generated steam is heated by the first heating pipe, and the heated steam is sent to the high pressure stage of the steam turbine. The exhaust gas from the high-temperature side power generation system and the low-boiling organic medium steam turbine is condensed in a second condenser, the organic medium condensate is heated by the second heating pipe, and the heated organic medium steam is converted into the organic medium steam. A gas turbine combined cycle power generation plant comprising: a low temperature side power generation system configured with an organic medium Rankine cycle in which the medium is sent to a high pressure stage of a medium steam turbine; Piping for supplying organic medium condensate from the second condenser is provided, and piping for supplying heated organic medium condensate heated by the first condenser to the second heating pipe on the outlet side of the cooling pipe. A gas turbine combined cycle power generation plant characterized by being provided with. (2) In the power generation or plant described in claim 1, a second preheating pipe is provided on a lower temperature side than the second superheating pipe in the waste heat recovery boiler, and the organic medium from the second condenser is A gas turbine combined cycle characterized in that a pipe is provided for introducing a part of the condensate into the second preheating pipe to preheat it and supplying the preheated organic medium condensate to the low pressure stage of the organic medium steam turbine. power plant.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24928683A JPS60138214A (en) | 1983-12-26 | 1983-12-26 | Gas turbine composite cycle power generating plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24928683A JPS60138214A (en) | 1983-12-26 | 1983-12-26 | Gas turbine composite cycle power generating plant |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60138214A true JPS60138214A (en) | 1985-07-22 |
Family
ID=17190705
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24928683A Pending JPS60138214A (en) | 1983-12-26 | 1983-12-26 | Gas turbine composite cycle power generating plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60138214A (en) |
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|---|---|---|---|---|
| CN104234763A (en) * | 2014-04-14 | 2014-12-24 | 天津市职业大学 | Organic Rankine cycle system recovering waste heat through heat pipe technology |
| WO2014193604A3 (en) * | 2013-05-30 | 2015-06-18 | General Electric Company | System and method of waste heat recovery |
| WO2014193629A3 (en) * | 2013-05-30 | 2015-07-02 | General Electric Company | System and method of waste heat recovery |
| US9145795B2 (en) | 2013-05-30 | 2015-09-29 | General Electric Company | System and method of waste heat recovery |
| WO2015146669A1 (en) * | 2014-03-24 | 2015-10-01 | 三菱日立パワーシステムズ株式会社 | Waste heat recovery device, gas turbine plant provided with same, and waste heat recovery method |
| US9593597B2 (en) | 2013-05-30 | 2017-03-14 | General Electric Company | System and method of waste heat recovery |
| RU2688342C2 (en) * | 2009-09-28 | 2019-05-21 | Дженерал Электрик Компани | System operating as per rankine cycle, and corresponding method |
| US10844753B2 (en) | 2015-03-31 | 2020-11-24 | Mitsubishi Hitachi Power Systems, Ltd. | Boiler, steam-generating plant provided with same, and method for operating boiler |
-
1983
- 1983-12-26 JP JP24928683A patent/JPS60138214A/en active Pending
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|---|---|---|---|---|
| RU2688342C2 (en) * | 2009-09-28 | 2019-05-21 | Дженерал Электрик Компани | System operating as per rankine cycle, and corresponding method |
| US9593597B2 (en) | 2013-05-30 | 2017-03-14 | General Electric Company | System and method of waste heat recovery |
| WO2014193604A3 (en) * | 2013-05-30 | 2015-06-18 | General Electric Company | System and method of waste heat recovery |
| WO2014193629A3 (en) * | 2013-05-30 | 2015-07-02 | General Electric Company | System and method of waste heat recovery |
| US9145795B2 (en) | 2013-05-30 | 2015-09-29 | General Electric Company | System and method of waste heat recovery |
| RU2658895C2 (en) * | 2013-05-30 | 2018-06-25 | Дженерал Электрик Компани | System and method for waste heat recovery |
| US9260982B2 (en) | 2013-05-30 | 2016-02-16 | General Electric Company | System and method of waste heat recovery |
| RU2637776C2 (en) * | 2013-05-30 | 2017-12-07 | Дженерал Электрик Компани | System and method of waste-heat recovery |
| US9587520B2 (en) | 2013-05-30 | 2017-03-07 | General Electric Company | System and method of waste heat recovery |
| WO2015146669A1 (en) * | 2014-03-24 | 2015-10-01 | 三菱日立パワーシステムズ株式会社 | Waste heat recovery device, gas turbine plant provided with same, and waste heat recovery method |
| EP3124758A4 (en) * | 2014-03-24 | 2017-11-22 | Mitsubishi Hitachi Power Systems, Ltd. | Waste heat recovery device, gas turbine plant provided with same, and waste heat recovery method |
| CN106103913A (en) * | 2014-03-24 | 2016-11-09 | 三菱日立电力***株式会社 | Waste heat recovery plant, the gas turbine complete set of equipments possessing this waste heat recovery plant and waste recovery method |
| KR20180005289A (en) * | 2014-03-24 | 2018-01-15 | 미츠비시 히타치 파워 시스템즈 가부시키가이샤 | Waste heat recovery device, gas turbine plant provided with same, and waste heat recovery method |
| JP2015183595A (en) * | 2014-03-24 | 2015-10-22 | 三菱日立パワーシステムズ株式会社 | Exhaust heat recovery apparatus, gas turbine plant including the same, and exhaust heat recovery method |
| US10480411B2 (en) | 2014-03-24 | 2019-11-19 | Mitsubishi Hitachi Power Systems, Ltd. | Waste heat recovery device, gas turbine plant provided with same, and waste heat recovery method |
| CN104234763A (en) * | 2014-04-14 | 2014-12-24 | 天津市职业大学 | Organic Rankine cycle system recovering waste heat through heat pipe technology |
| US10844753B2 (en) | 2015-03-31 | 2020-11-24 | Mitsubishi Hitachi Power Systems, Ltd. | Boiler, steam-generating plant provided with same, and method for operating boiler |
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