JPH06200709A - Combined cycle power generating plant - Google Patents
Combined cycle power generating plantInfo
- Publication number
- JPH06200709A JPH06200709A JP34909692A JP34909692A JPH06200709A JP H06200709 A JPH06200709 A JP H06200709A JP 34909692 A JP34909692 A JP 34909692A JP 34909692 A JP34909692 A JP 34909692A JP H06200709 A JPH06200709 A JP H06200709A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- temperature
- flow rate
- feed water
- reheater
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
- Control Of Turbines (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
【発明の詳細な説明】Detailed Description of the Invention
【0001】[0001]
【産業上の利用分野】本発明は蒸気タービンプラントと
ガスタービンプラントとを組み合せたコンバインドサイ
クル発電プラントに係り、特にガスタービンからの排ガ
スを排熱回収ボイラで熱交換して蒸気タービンプラント
の復水および給水加熱を行なうようにした排熱回収型コ
ンバインドサイクル発電プラントに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combined cycle power plant in which a steam turbine plant and a gas turbine plant are combined, and in particular, exhaust gas from a gas turbine is heat-exchanged by an exhaust heat recovery boiler to condense the steam turbine plant. And an exhaust heat recovery combined cycle power plant adapted to perform feed water heating.
【0002】[0002]
【従来の技術】近時、電力産業において、消費電力の増
加に伴い、プラント熱効率が優れたコンバインドサイク
ル発電プラントが脚光を浴びている。この発電プラント
は蒸気タービンプラントとガスタービンプラントとを組
み合せてコンバインドサイクル化したものである。2. Description of the Related Art Recently, in the electric power industry, a combined cycle power plant having excellent plant thermal efficiency has been in the limelight as the power consumption increases. This power plant is a combined cycle of a steam turbine plant and a gas turbine plant.
【0003】コンバインドサイクル発電プラントは、新
設のガスタービンプラントと新設の蒸気タービンプラン
トとを組み合せる場合もあるが、立地条件、建設から据
付までの長期間を考慮すると、既に実績を多く積み重ね
た蒸気タービンプラントと新設のガスタービンプラント
とを巧みに組み合せて工期の短縮を図る、いわゆるリパ
ワリング発電プラントが一般的である。A combined cycle power plant may combine a newly installed gas turbine plant and a newly installed steam turbine plant, but in view of site conditions and a long period from construction to installation, steam that has already accumulated many achievements has been accumulated. A so-called repowering power plant is generally used, which aims at shortening the construction period by skillfully combining a turbine plant and a new gas turbine plant.
【0004】既に提唱されているこの種の発電プラント
は、既設の蒸気タービンプラントに新設のガスタービン
プラントを追設して組み合せ、コンバインドサイクル化
したもので、ガスタービンからの排ガスを排熱回収ボイ
ラで熱回収して主蒸気および再熱蒸気の一部を過熱させ
るとともに、排熱回収ボイラの排ガス出口側に低圧ガス
給水加熱器および高圧ガス給水加熱器を設置して蒸気タ
ービンプラントの復水や給水を加熱する排熱回収型コン
バインドサイクル発電プラントである。This type of power plant that has already been proposed is one in which a new gas turbine plant has been added to the existing steam turbine plant and combined together to form a combined cycle. The exhaust gas from the gas turbine is recovered by the exhaust heat recovery boiler. Heat recovery is performed to superheat part of the main steam and reheated steam, and a low pressure gas feed water heater and a high pressure gas feed water heater are installed on the exhaust gas outlet side of the exhaust heat recovery boiler to condense steam in the steam turbine plant and It is an exhaust heat recovery type combined cycle power plant that heats the feed water.
【0005】この発電プラントは、既設の蒸気タービン
プラントに新設のガスタービンプラントを追設してコン
バインドサイクル化することにより、ガスタービン排ガ
スを有効活用できるため、ボイラの燃料使用量を減少で
き、発電効率を向上させることができる。またガスター
ビンプラントを追設するため、発電所全体としての発電
電力量を増加させることができる。In this power plant, a new gas turbine plant is added to an existing steam turbine plant to form a combined cycle, so that the gas turbine exhaust gas can be effectively used, so that the fuel consumption of the boiler can be reduced and The efficiency can be improved. Further, since the gas turbine plant is additionally installed, it is possible to increase the amount of power generated by the power plant as a whole.
【0006】さらに、コンバインドサイクル発電プラン
トは既設の蒸気タービンプラントの改造が少なく、既設
の蒸気タービンプラントに隣接する追加のガスタービン
プラントは、先行的に据付工事等が可能なため、プラン
ト停止期間を短かくできる等の特徴を有する。そして、
近年の大幅な電力需要の伸びや電力需要の伸びに伴なう
各電力会社の電力予備率の急激な減少に対処するため
に、新たな発電設備の早急な立上げの必要性から、既設
蒸気タービンプラントのリパワリングは有効な手段の1
つと考えられている。Further, in the combined cycle power plant, there is little modification of the existing steam turbine plant, and the additional gas turbine plant adjacent to the existing steam turbine plant can be installed in advance, so that the plant suspension period can be reduced. It has features such as shortening. And
In order to cope with the recent significant growth in power demand and the sharp decrease in the power reserve ratio of each power company that accompanies the growth in power demand, the existing steam has been Turbine plant repowering is an effective means
Is considered to be one.
【0007】従来の排熱回収型コンバインドサイクル発
電プラントの一例を図6に示す。FIG. 6 shows an example of a conventional exhaust heat recovery type combined cycle power generation plant.
【0008】このコンバインドサイクル発電プラント
は、既設の蒸気タービンプラント1にガスタービンプラ
ント2を追設してコンバインドサイクル化したものであ
る。In this combined cycle power generation plant, a gas turbine plant 2 is added to the existing steam turbine plant 1 to form a combined cycle.
【0009】蒸気タービンプラント1はボイラ3や蒸気
タービン4、各種熱交換器を順次接続して閉サイクルを
構成している。ボイラ3で発生した蒸気は、蒸気タービ
ン4のタービン高圧部5に導かれ、膨脹仕事をする。蒸
気タービン4のタービン高圧部5で仕事をした蒸気は、
ボイラ再熱器6と排熱回収ボイラ7の再熱器8に送られ
て再熱される。ボイラ再熱器6や排熱回収ボイラ7の再
熱器8で加熱された蒸気はボイラ3出口で再び合流し
て、蒸気タービン4のタービン中圧部9に導かれて仕事
をする。このタービン中圧部9で仕事をした蒸気は、続
いて蒸気タービン4のタービン低圧部10に導かれ、こ
こでさらに仕事をした後、復水器11に案内されて冷却
され復水となる。In the steam turbine plant 1, a boiler 3, a steam turbine 4, and various heat exchangers are sequentially connected to form a closed cycle. The steam generated in the boiler 3 is guided to the turbine high pressure section 5 of the steam turbine 4 and performs expansion work. The steam that has worked in the turbine high pressure section 5 of the steam turbine 4 is
It is sent to the reheater 6 of the boiler reheater 6 and the exhaust heat recovery boiler 7 to be reheated. The steam heated in the reheater 8 of the boiler reheater 6 and the reheater 8 of the exhaust heat recovery boiler 7 joins again at the outlet of the boiler 3 and is guided to the turbine intermediate pressure portion 9 of the steam turbine 4 to perform work. The steam that has worked in the turbine intermediate pressure portion 9 is subsequently guided to the turbine low pressure portion 10 of the steam turbine 4, where it further performs work, and is then guided to the condenser 11 where it is cooled and becomes condensed water.
【0010】そして、蒸気タービン4の各部5,9,1
0で行なわれた仕事は、蒸気タービン軸端に連結された
タービン発電機12を駆動し、この発電機12により電
気エネルギに変えられる。The parts 5, 9, 1 of the steam turbine 4 are
The work done at 0 drives a turbine generator 12 connected to the end of the steam turbine shaft, which is converted into electrical energy.
【0011】一方、復水器11で冷却され、凝縮された
復水は、復水ポンプ13により復水器11から復水給水
系に送出され、低圧給水加熱器14と低圧(第1)ガス
給水加熱器(低圧ガスクーラ)15で加熱されて脱気器
16に送られ、ここで脱気される。脱気器16で脱気さ
れた給水は、給水ポンプ17により昇圧され、さらに高
圧給水加熱器18と高圧(第2)ガス給水加熱器(高圧
ガスクーラ)19により加熱された後、ボイラ3に供給
される、ボイラ3内では、節炭器20にて給水の温度が
上昇し、蒸発器21では蒸気となり、この蒸気がボイラ
過熱器22と排熱回収ボイラ7の過熱器23に送られ
る。ボイラ過熱器22からの過熱蒸気と排熱回収ボイラ
7で過熱された蒸気はボイラ3出口で再び合流し主蒸気
となって、蒸気タービン4のタービン高圧部5に導かれ
る。On the other hand, the condensate cooled and condensed in the condenser 11 is sent from the condenser 11 to the condensate water supply system by the condensate pump 13, and is fed to the low pressure feed water heater 14 and the low pressure (first) gas. It is heated by the feed water heater (low pressure gas cooler) 15 and sent to the deaerator 16, where it is deaerated. The feed water deaerated by the deaerator 16 is boosted by a feed water pump 17, further heated by a high pressure feed water heater 18 and a high pressure (second) gas feed water heater (high pressure gas cooler) 19, and then supplied to the boiler 3. In the boiler 3, the temperature of the feed water rises in the economizer 20, the steam becomes steam in the evaporator 21, and the steam is sent to the boiler superheater 22 and the superheater 23 of the exhaust heat recovery boiler 7. The superheated steam from the boiler superheater 22 and the steam superheated by the exhaust heat recovery boiler 7 merge again at the outlet of the boiler 3 to become main steam, which is guided to the turbine high pressure portion 5 of the steam turbine 4.
【0012】また、追設されたガスタービンプラント2
はガスタービン25部と排熱回収ボイラ7とを備え、開
放サイクルを構成している。Further, the additionally installed gas turbine plant 2
Includes a gas turbine 25 part and an exhaust heat recovery boiler 7, and constitutes an open cycle.
【0013】ガスタービン25は軸端にタービン発電機
26を連結し、このタービン発電機26を駆動させて電
気エネルギを発生させる一方、ガスタービン25から排
出されるガスタービン排ガスを排熱回収ボイラ7に導
き、主蒸気や再熱蒸気の一部を過熱させる。排熱回収ボ
イラ7の排ガス出口側には排ガス熱を有効に利用するた
めに、高圧ガス給水加熱器19や低圧ガス給水加熱器1
5が設置され、これらの給水加熱器19や15で給水や
復水と熱交換され、排ガスを従来プラント並の100℃
前後に降下させてから煙突27より大気へ放出してい
る。In the gas turbine 25, a turbine generator 26 is connected to the shaft end, and the turbine generator 26 is driven to generate electric energy. At the same time, the gas turbine exhaust gas discharged from the gas turbine 25 is exhausted from the exhaust heat recovery boiler 7 To superheat some of the main steam and reheated steam. In order to effectively utilize the exhaust gas heat on the exhaust gas outlet side of the exhaust heat recovery boiler 7, the high pressure gas feed water heater 19 and the low pressure gas feed water heater 1
No. 5 is installed, and heat exchange with feed water and condensate is performed by these feed water heaters 19 and 15, and the exhaust gas is at 100 ° C., which is equivalent to that of conventional plants.
After being dropped back and forth, it is released from the chimney 27 into the atmosphere.
【0014】ガスタービンプラント2は、タービン排気
系統に排熱回収ボイラ7、高圧ガス給水加熱器19およ
び低圧ガス給水加熱器15が順次設置されるため、ガス
タービンプラント2を単独運転させることが不可能とな
り、蒸気タービンプラント1のボイラ3と協調を採った
運転が必要となる。In the gas turbine plant 2, since the exhaust heat recovery boiler 7, the high pressure gas feed water heater 19 and the low pressure gas feed water heater 15 are sequentially installed in the turbine exhaust system, it is not possible to operate the gas turbine plant 2 independently. It becomes possible, and the operation in cooperation with the boiler 3 of the steam turbine plant 1 is required.
【0015】ところで、排熱回収ボイラ7から送り出さ
れる主蒸気や再熱蒸気の温度は、排熱回収ボイラ7が蒸
気温度を制御する機能を持たないために、ガスタービン
25の排ガス温度によってのみ決定される。また、ガス
タービン25の排ガス温度はガスタービン25の負荷に
よって決まるので、排熱回収ボイラ7から送り出される
主蒸気や再熱蒸気温度は、ガスタービン25の負荷によ
って決定される。By the way, the temperatures of the main steam and the reheated steam sent from the exhaust heat recovery boiler 7 are determined only by the exhaust gas temperature of the gas turbine 25 because the exhaust heat recovery boiler 7 does not have the function of controlling the steam temperature. To be done. Further, since the exhaust gas temperature of the gas turbine 25 is determined by the load of the gas turbine 25, the temperatures of the main steam and reheated steam sent from the exhaust heat recovery boiler 7 are determined by the load of the gas turbine 25.
【0016】図6に示された排熱回収型コンバインドサ
イクル発電プラントの排熱回収ボイラ7で発生する主蒸
気および再熱蒸気の温度特性を図7に示す。FIG. 7 shows the temperature characteristics of the main steam and the reheated steam generated in the exhaust heat recovery boiler 7 of the exhaust heat recovery type combined cycle power generation plant shown in FIG.
【0017】[0017]
【発明が解決しようとする課題】従来のコンバインドサ
イクル発電プラントでは、図7からわかるように、ガス
タービン25の部分負荷特性によって、ガスタービン2
5の排ガス温度は、定格負荷より低い負荷で高い温度と
なるため、主蒸気や再熱蒸気温度も定格負荷より低いガ
スタービンの負荷での高い温度となり、排熱回収ボイラ
7から送り出される主蒸気や再熱蒸気の温度が安定せ
ず、不安定となっていた。In the conventional combined cycle power plant, as can be seen from FIG. 7, the partial load characteristic of the gas turbine 25 causes the gas turbine 2
Since the exhaust gas temperature of No. 5 is high at a load lower than the rated load, the main steam and reheat steam temperatures are also high at a gas turbine load lower than the rated load, and the main steam sent from the exhaust heat recovery boiler 7 The temperature of reheated steam was unstable and unstable.
【0018】また、大気温度が変化した場合、ガスター
ビン25の負荷が同一であっても、排熱回収ポイラ7か
ら送り出される主蒸気や再熱蒸気温度が異なり、コンバ
インドサイクル発電プラントを安定運転する上で支障が
ある。Further, when the atmospheric temperature changes, even if the load on the gas turbine 25 is the same, the temperatures of the main steam and reheated steam sent from the exhaust heat recovery boiler 7 are different, and the combined cycle power plant is operated stably. There is a problem above.
【0019】本発明は、上述した事情を考慮してなされ
たもので、排熱回収ボイラから送り出される主蒸気や再
熱蒸気の温度を設定温度に維持し、安定したプラントの
運転を保証することができるコンバインドサイクル発電
プラントを提供することを目的とする。The present invention has been made in view of the above circumstances, and maintains the temperatures of the main steam and the reheated steam sent from the exhaust heat recovery boiler at a set temperature to ensure stable plant operation. The object is to provide a combined cycle power plant capable of
【0020】[0020]
【課題を解決するための手段】本発明に係るコンバイン
ドサイクル発電プラントは、上述した課題を解決するた
めに、請求項1に記載したように、ボイラ、蒸気タービ
ン、復水給水系を備えた蒸気タービンプラントとガスタ
ービンを備えたガスタービンプラントとを組み合せてコ
ンバインドサイクル化する一方、前記ガスタービンから
のタービン排ガス系統に、過熱器および再熱器を備えた
排熱回収ボイラと、前記復水給水系の給水を加熱する高
圧ガス給水加熱器と、復水給水系の復水を加熱する低圧
ガス給水加熱器とをそれぞれ設置したコンバインドサイ
クル発電プラントにおいて、前記排熱回収ボイラの過熱
器出口の蒸気温度を検出する温度検出器と、上記過熱器
へ供給される主蒸気流量を制御する主蒸気流量調節弁
と、前記温度検出器からの温度検出信号を入力して、過
熱器出口蒸気温度が設定値になるように、前記主蒸気流
量調節弁の弁制御を行なう弁制御装置とを有するもので
ある。In order to solve the above-mentioned problems, a combined cycle power plant according to the present invention, as set forth in claim 1, is equipped with a steam generator, a steam turbine, and a condensate water supply system. While combining a turbine plant and a gas turbine plant equipped with a gas turbine into a combined cycle, a turbine exhaust gas system from the gas turbine, an exhaust heat recovery boiler equipped with a superheater and a reheater, and the condensate feed water In a combined cycle power plant equipped with a high-pressure gas feed water heater for heating the system feed water and a low-pressure gas feed water heater for heating the condensate feed water condensate, respectively, steam at the superheater outlet of the exhaust heat recovery boiler A temperature detector for detecting a temperature, a main steam flow control valve for controlling a main steam flow rate supplied to the superheater, and the temperature detector Enter the temperature detection signal al, superheater as outlet steam temperature becomes the set value, and has a valve controller for the valve control of the main steam flow rate adjustment valve.
【0021】また、上述した課題を解決するために、本
発明に係るコンバインドサイクル発電プラントは、請求
項2に記載したように、排熱回収ボイラに組み込まれる
過熱器を上流側過熱器と下流側過熱器とに分割し、分割
された過熱器間に供給される給水の流量を制御する主蒸
気減温用給水流量調節弁を設ける一方、この給水流量調
節弁を弁制御する弁制御装置を設け、この弁制御装置は
過熱器出口蒸気温度検出器からの温度検出信号を入力し
て、過熱器出口蒸気温度が設定値となるように給水流量
調節弁の弁制御を行なうように設定したものである。Further, in order to solve the above-mentioned problems, in the combined cycle power plant according to the present invention, as described in claim 2, the superheater incorporated in the exhaust heat recovery boiler has an upstream superheater and a downstream heat exchanger. It is divided into a superheater and a feed water flow rate control valve for main steam temperature reduction that controls the flow rate of feed water supplied between the divided superheaters is provided, while a valve control device that controls this feed water flow rate control valve is provided. , This valve control device is set to input the temperature detection signal from the superheater outlet steam temperature detector and perform valve control of the feed water flow rate control valve so that the superheater outlet steam temperature becomes a set value. is there.
【0022】さらに、上述した課題を解決するために、
本発明に係るコンバインドサイクル発電プラントは、請
求項3に記載したように、ボイラ、蒸気タービン、復水
給水系を備えた蒸気タービンプラントとガスタービンを
備えたガスタービンプラントとを組み合せてコンバイン
ドサイクル化する一方、前記ガスタービンからのタービ
ン排ガス系統に、過熱器および再熱器を備えた排熱回収
ボイラと、前記復水給水系の給水を加熱する高圧ガス給
水加熱器と、復水給水系の復水を加熱する低圧ガス給水
加熱器とをそれぞれ設置したコンバインドサイクル発電
プラントにおいて、前記排熱回収ボイラの再熱器出口の
蒸気温度を検出する温度検出器と、上記再熱器へ供給さ
れる再熱蒸気流量を制御する再熱蒸気流量調節弁と、前
記温度検出器からの温度検出信号を入力して、再熱器出
口の蒸気温度が設定値となるように、前記再熱蒸気流量
調節弁の弁制御を行なう弁制御装置とを有するものであ
る。Further, in order to solve the above-mentioned problems,
As described in claim 3, the combined cycle power plant according to the present invention is combined with a steam turbine plant including a boiler, a steam turbine, and a condensate water supply system, and a gas turbine plant including a gas turbine to form a combined cycle. On the other hand, in the turbine exhaust gas system from the gas turbine, an exhaust heat recovery boiler equipped with a superheater and a reheater, a high-pressure gas feed water heater for heating feed water of the condensate feed water system, and a condensate feed water system. In a combined cycle power plant that has respectively installed a low-pressure gas feedwater heater for heating the condensate, a temperature detector for detecting the steam temperature at the reheater outlet of the exhaust heat recovery boiler, and the reheater are supplied. Input the temperature detection signal from the temperature detector and the reheat steam flow control valve that controls the reheat steam flow rate to set the steam temperature at the reheater outlet. As a value, and has a valve controller for the valve control of the reheat steam flow control valve.
【0023】さらにまた、本発明に係るコンバインドサ
イクル発電プラントは、上述した課題を解決するため
に、請求項4に記載したように、排熱回収ボイラに組み
込まれる再熱器を上流側再熱器と下流側再熱器とに分割
し、分割された再熱器間に供給される給水の流量を制御
する再熱蒸気減温用給水流量調節弁を設ける一方、この
給水流量調節弁を弁制御する弁制御装置を設け、この弁
制御装置は再熱器出口蒸気温度検出器からの温度検出信
号を入力して、再熱器出口蒸気温度が設定値となるよう
に給水流量調節弁の弁制御を行なうように設定したもの
である。Furthermore, in the combined cycle power generation plant according to the present invention, in order to solve the above-mentioned problems, as described in claim 4, the reheater incorporated in the exhaust heat recovery boiler has an upstream side reheater. And a reheater on the downstream side, and a feed water flow rate control valve for reducing the reheat steam temperature is provided to control the flow rate of the feed water supplied between the divided reheaters, while controlling this feed water flow rate control valve. A valve control device is installed to control the feed water flow rate control valve so that the reheater outlet steam temperature detector receives the temperature detection signal and the reheater outlet steam temperature reaches the set value. Is set to do.
【0024】[0024]
【作用】請求項1に記載のコンバインドサイクル発電プ
ラントによれば、排熱回収ボイラから送り出される主蒸
気温度が設定値と異なった場合に、過熱器出口蒸気温度
検出器からの温度検出信号によって弁制御装置により主
蒸気流量調節弁を弁制御し、この主蒸気流量調節弁で流
量が制御された主蒸気過熱器に供給することによって、
過熱器内の蒸気温度をコントロールし、前記過熱器出口
の主蒸気温度を設定値に抑えることができ、この主蒸気
温度を設定温度に維持して安定したプラント運転を保証
することができる。According to the combined cycle power plant of claim 1, when the main steam temperature sent from the exhaust heat recovery boiler is different from the set value, the valve is detected by the temperature detection signal from the superheater outlet steam temperature detector. By controlling the main steam flow rate control valve by the control device and supplying it to the main steam superheater whose flow rate is controlled by this main steam flow rate control valve,
By controlling the steam temperature in the superheater, the main steam temperature at the outlet of the superheater can be suppressed to a set value, and the main steam temperature can be maintained at the set temperature to ensure stable plant operation.
【0025】また、請求項2に記載のコンバインドサイ
クル発電プラントでは、過熱器出口蒸気温度検出器から
の温度検出信号によって弁制御装置が主蒸気減温用給水
流量調節弁の弁制御を行ない、この給水流量調節弁によ
り分割された過熱器の間に供給される給水の流量が制御
される。この給水流量制御により過熱器内の蒸気温度を
低下させ、前記過熱器出口の主蒸気温度を設定値に急速
に抑えることができ、請求項1記載のコンバインドサイ
クル発電プラントと同様な作用効果を奏する。Further, in the combined cycle power plant according to the second aspect of the present invention, the valve control device performs valve control of the main steam temperature reducing feed water flow rate control valve by the temperature detection signal from the superheater outlet steam temperature detector. The flow rate of feed water supplied between the divided superheaters is controlled by the feed water flow rate control valve. By controlling the feed water flow rate, the steam temperature in the superheater can be lowered, and the main steam temperature at the outlet of the superheater can be quickly suppressed to a set value, and the same effect as that of the combined cycle power plant according to claim 1 can be obtained. .
【0026】また、請求項3に記載のコンバインドサイ
クル発電プラントでは、排熱回収ボイラから送り出され
る再熱蒸気温度が設定値と異なった場合に、再熱器出口
蒸気温度検出器からの温度検出信号によって再熱蒸気流
量調節弁を弁制御し、この流量調節弁で流量制御された
再熱蒸気を再熱器に供給することによって、再熱器内の
蒸気温度をコントロールし、前記再熱器出口の再熱蒸気
温度を設定値に抑えることができ、この再熱蒸気温度を
設定温度に維持して安定したプラント運転を保証するこ
とができる。Further, in the combined cycle power plant according to the third aspect, when the reheat steam temperature sent from the exhaust heat recovery boiler is different from the set value, a temperature detection signal from the reheater outlet steam temperature detector. The reheat steam flow rate control valve is controlled by the flow rate control valve, and the reheat steam whose flow rate is controlled by the flow rate control valve is supplied to the reheater to control the steam temperature in the reheater, and the reheater outlet The reheated steam temperature can be suppressed to a set value, and this reheated steam temperature can be maintained at the set temperature to ensure stable plant operation.
【0027】また、請求項4に記載のコンバインドサイ
クル発電プラントでは、再熱器出口蒸気温度検出器から
の温度検出信号によって弁制御装置が再熱蒸気減温用給
水流量調節弁の弁制御を行ない、この給水流量調節弁に
より分割された再熱器の間に供給される給水の流量が制
御される。この給水流量制御により再熱器内の蒸気温度
を急速に低下させ、前記再熱器出口の再熱蒸気温度を設
定値に抑えることができ、請求項3記載のコンバインド
サイクル発電プラントと同様な作用効果を奏する。Further, in the combined cycle power plant according to a fourth aspect of the present invention, the valve control device performs valve control of the reheated steam temperature reducing feed water flow rate control valve by the temperature detection signal from the reheater outlet steam temperature detector. The flow rate of feed water supplied between the reheaters divided by the feed water flow rate control valve is controlled. By the feed water flow rate control, the steam temperature in the reheater can be rapidly lowered, and the reheated steam temperature at the reheater outlet can be suppressed to a set value. Produce an effect.
【0028】[0028]
【実施例】以下、本発明に係るコンバインドサイクル発
電プラントの一実施例について添付図面を参照して説明
する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a combined cycle power plant according to the present invention will be described below with reference to the accompanying drawings.
【0029】このコンバインドサイクル発電プラント
は、既設の蒸気タービンプラント1に新設のガスタービ
ンプラント2を追設してコンバインドサイクル化した排
熱回収型コンバインドサイクル発電プラントである。蒸
気タービンプラント1やガスタービンプラント2は新設
のもの同士を組み合せてもよい。図6に示す従来のコン
バインドサイクル発電プラントと同じ構成部品には同一
符号を付して説明する。This combined cycle power plant is an exhaust heat recovery type combined cycle power plant in which a newly installed gas turbine plant 2 is added to an existing steam turbine plant 1 to form a combined cycle. The steam turbine plant 1 and the gas turbine plant 2 may be combined with each other. The same components as those of the conventional combined cycle power plant shown in FIG.
【0030】蒸気タービンプラント1は蒸気を発生させ
るボイラ3、蒸気タービン4、復水器11および復水給
水系30等を順次接続して閉サイクルを構成している。The steam turbine plant 1 constitutes a closed cycle by sequentially connecting a boiler 3 for generating steam, a steam turbine 4, a condenser 11, a condensate water supply system 30 and the like.
【0031】蒸気タービンプラント1は、ボイラ3で発
生した主蒸気を主蒸気系31を介して蒸気タービン4の
タービン高圧部5に案内し、このタービン高圧部5で膨
脹し、仕事をしている。タービン高圧部5で仕事をした
蒸気は、再熱蒸気系32のボイラ再熱器6と排熱回収ボ
イラ7の再熱器8に送られて加熱される。ボイラ再熱器
6や再熱器8で加熱された再熱蒸気はボイラ3出口側で
合流して蒸気タービン4のタービン中圧部9に送られ、
このタービン中圧部9で仕事をする。タービン中圧部9
で仕事をした蒸気は、続いてタービン低圧部10に案内
されて、ここでさらに仕事をした後、復水器11に案内
されて冷却され、復水となる。The steam turbine plant 1 guides the main steam generated in the boiler 3 to the turbine high pressure section 5 of the steam turbine 4 via the main steam system 31, and expands and works at the turbine high pressure section 5. . The steam that has worked in the turbine high-pressure section 5 is sent to the boiler reheater 6 of the reheat steam system 32 and the reheater 8 of the exhaust heat recovery boiler 7 to be heated. The reheated steam heated by the boiler reheater 6 and the reheater 8 joins at the outlet side of the boiler 3 and is sent to the turbine intermediate pressure section 9 of the steam turbine 4.
The turbine intermediate pressure section 9 works. Turbine intermediate pressure section 9
The steam that has worked in 1. is subsequently guided to the turbine low-pressure section 10, where it further performs work, and is then guided to the condenser 11 where it is cooled and becomes condensed water.
【0032】蒸気タービン4はタービンシャフトや図示
しないカップリングを介してタービン発電機12に連結
され、蒸気タービン4の各部5,9,10で行なわれた
仕事によりタービン発電機12が駆動され、電気エネル
ギを発生させている。The steam turbine 4 is connected to a turbine generator 12 via a turbine shaft or a coupling (not shown), and the work performed by the respective parts 5, 9 and 10 of the steam turbine 4 drives the turbine generator 12 to generate electricity. Generating energy.
【0033】一方、復水器11で冷却された復水は、復
水ポンプ13により復水給水系30に送られ、多段構造
の低圧給水加熱器14と低圧(第1)ガス給水加熱器
(低圧ガスクーラ)15で第1段の加熱が行なわれる。
加熱された復水は脱気器16に案内されてここで脱気さ
れた後、給水ポンプ17により多段構造の高圧給水加熱
器18と高圧(第2)ガス給水加熱器(高圧ガスクー
ラ)19に送られ、第2段の給水加熱が行なわれ、その
後、ボイラ3に供給される。On the other hand, the condensate cooled by the condenser 11 is sent to the condensate water supply system 30 by the condensate pump 13, and the multi-stage low pressure feed water heater 14 and the low pressure (first) gas feed water heater ( The low pressure gas cooler) 15 performs the first stage heating.
The heated condensate is guided to the deaerator 16 and deaerated there, and then is fed to the high-pressure feed water heater 18 and the high-pressure (second) gas feed water heater (high-pressure gas cooler) 19 having a multistage structure by the feed water pump 17. The water is sent and heated in the second stage, and then supplied to the boiler 3.
【0034】ボイラ3は、節炭器(エコノマイザ)2
0、蒸発器21およびボイラ過熱器22を順次備えてお
り、ボイラ3内に供給された給水は、節炭器20により
温度上昇され、蒸発器21で蒸発せしめられて蒸気とな
る。発生した蒸気は、ボイラ過熱器22と排熱回収ボイ
ラ7の過熱器23に送られてスーパーヒートされる。ボ
イラ過熱器22からの過熱蒸気と排熱回収ボイラ7の過
熱器23からの過熱蒸気は、ボイラ3の出口側で合流し
て蒸気タービン4のタービン高圧部5に導かれる。The boiler 3 is a economizer 2
0, an evaporator 21, and a boiler superheater 22 are sequentially provided, and the temperature of the feed water supplied into the boiler 3 is raised by the economizer 20 and evaporated in the evaporator 21 to become steam. The generated steam is sent to the boiler superheater 22 and the superheater 23 of the exhaust heat recovery boiler 7 to be superheated. The superheated steam from the boiler superheater 22 and the superheated steam from the superheater 23 of the exhaust heat recovery boiler 7 join together at the outlet side of the boiler 3 and are guided to the turbine high pressure section 5 of the steam turbine 4.
【0035】また、ガスタービンプラント2はガスター
ビン25を備え、このガスタービン25の作動によりタ
ービン発電機26を駆動させて発電を行なっている。さ
らに、ガスタービン25のタービン排気系統33に排熱
回収ボイラ7、高圧ガス給水加熱器19および低圧ガス
給水加熱器15が順次設置され、ガスタービン25から
の排ガス熱を有効に利用している。タービン排気系統3
3では排熱回収ボイラ7が過熱器23と再熱器8とを備
え、この過熱器23や再熱器8で蒸気タービンプラント
1の主蒸気や再熱蒸気の一部を過熱している。The gas turbine plant 2 is equipped with a gas turbine 25, and the operation of the gas turbine 25 drives a turbine generator 26 to generate electricity. Further, the exhaust heat recovery boiler 7, the high pressure gas feed water heater 19 and the low pressure gas feed water heater 15 are sequentially installed in the turbine exhaust system 33 of the gas turbine 25, and the exhaust gas heat from the gas turbine 25 is effectively used. Turbine exhaust system 3
In 3, the exhaust heat recovery boiler 7 includes the superheater 23 and the reheater 8, and the superheater 23 and the reheater 8 superheat part of the main steam and the reheated steam of the steam turbine plant 1.
【0036】排熱回収ボイラ7の排ガス出口側(下流
側)に設置される高圧ガス給水加熱器19は復水給水系
30に案内される給水を加熱しており、低圧ガス給水加
熱器15は復水給水系30の復水を加熱している。復水
給水系30の給水や復水と熱交換して温度降下した排ガ
スは100℃前後あるいはそれ以下に降下されて煙突2
7から大気中に放出される。The high pressure gas feedwater heater 19 installed on the exhaust gas outlet side (downstream side) of the exhaust heat recovery boiler 7 heats the feedwater guided to the condensate feedwater system 30, and the low pressure gas feedwater heater 15 Condensed water of the water supply system 30 is heated. Exhaust gas whose temperature has dropped due to heat exchange with the condensate water supply system 30 and condensate is lowered to around 100 ° C or lower and the stack 2
7 is released into the atmosphere.
【0037】また、排熱回収ボイラ7の過熱器出口側
に、過熱器23の出口蒸気温度を検出する温度検出器3
5が設けられており、この温度検出器35からの過熱器
出口蒸気温度T1 の温度検出信号は弁コントローラとし
ての弁制御装置36の減算器37に入力される。この減
算器37には、過熱器出口蒸気温度設定器38から過熱
器出口蒸気温度設定値aも入力され、両者の温度偏差δ
が演算される。演算された温度偏差δは主蒸気流量調節
弁開度演算器39に出力される。On the outlet side of the superheater of the exhaust heat recovery boiler 7, a temperature detector 3 for detecting the outlet steam temperature of the superheater 23.
5 is provided, and the temperature detection signal of the superheater outlet steam temperature T1 from the temperature detector 35 is input to the subtractor 37 of the valve controller 36 as a valve controller. The superheater outlet steam temperature set value a is also input to the subtractor 37 from the superheater outlet steam temperature setter 38, and the temperature deviation δ between them is δ.
Is calculated. The calculated temperature deviation δ is output to the main steam flow control valve opening degree calculator 39.
【0038】このように、弁制御装置36は減算器37
と過熱器蒸気温度設定器38と主蒸気流量調節弁開度演
算器39とを備えており、この開度演算器39からの弁
制御信号が主蒸気流量調節弁40に入力され、この主蒸
気流量調節弁40の弁制御を行なっている。As described above, the valve controller 36 includes the subtractor 37.
And a superheater steam temperature setter 38 and a main steam flow rate control valve opening degree calculator 39. A valve control signal from this opening degree calculator 39 is input to the main steam flow rate regulating valve 40, and this main steam The valve control of the flow control valve 40 is performed.
【0039】主蒸気流量調節弁40は、ボイラ3の蒸発
器21から排熱回収ボイラ7の過熱器23に至る蒸気流
路に設置され、この主蒸気流量調節弁40の弁制御によ
り、過熱器23に案内される主蒸気量がコントロールさ
れる。The main steam flow rate control valve 40 is installed in the steam flow path from the evaporator 21 of the boiler 3 to the superheater 23 of the exhaust heat recovery boiler 7, and the superheater is controlled by the valve control of the main steam flow rate control valve 40. The amount of main steam guided to 23 is controlled.
【0040】次に、図1に示すコンバインドサイクル発
電プラントの蒸気温度コントロール動作について説明す
る。Next, the steam temperature control operation of the combined cycle power plant shown in FIG. 1 will be described.
【0041】過熱器出口蒸気温度T1 が、過熱器出口蒸
気温度設定値aを超えた場合、過熱器出口蒸気温度検出
器35から検出される過熱器出口蒸気温度T1 が、過熱
器出口蒸気温度設定値aよりも大きくなるため、減算器
37から出力される温度偏差δがδ>0となり、主蒸気
流量調節弁開度演算器39が開方向の弁作動指令を主蒸
気流量調節弁40に対して行なうので、主蒸気流量調節
弁40が開くように操作される。When the superheater outlet steam temperature T1 exceeds the superheater outlet steam temperature set value a, the superheater outlet steam temperature T1 detected by the superheater outlet steam temperature detector 35 is set to the superheater outlet steam temperature setting. Since it becomes larger than the value a, the temperature deviation δ output from the subtractor 37 becomes δ> 0, and the main steam flow control valve opening calculator 39 issues a valve operation command in the opening direction to the main steam flow control valve 40. Therefore, the main steam flow rate control valve 40 is operated to open.
【0042】この主蒸気流量調節弁40の弁開方向制御
により、排熱回収ボイラ7の過熱器23に案内される主
蒸気量が増大し、過熱器出口蒸気温度T1 がその設定温
度aに近付き、設定温度aとなるように調節される。By controlling the valve opening direction of the main steam flow control valve 40, the amount of main steam guided to the superheater 23 of the exhaust heat recovery boiler 7 increases, and the superheater outlet steam temperature T1 approaches the set temperature a. , And the temperature is adjusted to the set temperature a.
【0043】過熱器出口蒸気温度T1 が過熱器出口蒸気
温度設定値aよりも低くなった場合、過熱器出口蒸気温
度検出器35から検出される過熱器出口蒸気温度T1
が、過熱器出口蒸気温度設定値aよりも小さくなるた
め、減算器37から出力される温度偏差δがδ<0とな
り、主蒸気流量調節弁開度演算器39が閉方向の弁動作
指令を主蒸気流量調節弁40に対して行なうので、主蒸
気流量調節弁40が閉じるように操作される。When the superheater outlet steam temperature T1 becomes lower than the superheater outlet steam temperature set value a, the superheater outlet steam temperature T1 detected by the superheater outlet steam temperature detector 35
However, since it becomes smaller than the superheater outlet steam temperature set value a, the temperature deviation δ output from the subtractor 37 becomes δ <0, and the main steam flow control valve opening degree calculator 39 issues a valve operation command in the closing direction. Since the main steam flow rate control valve 40 is operated, the main steam flow rate control valve 40 is operated so as to be closed.
【0044】この主蒸気流量調節弁40の弁閉方向制御
により、排熱回収ボイラ7の過熱器23に案内される主
蒸気量が絞られ、過熱器出口蒸気温度T1 がその設定温
度aとなるように温度上昇する。By controlling the valve closing direction of the main steam flow control valve 40, the amount of main steam guided to the superheater 23 of the exhaust heat recovery boiler 7 is throttled, and the superheater outlet steam temperature T1 becomes the set temperature a. So that the temperature rises.
【0045】このようにして、過熱器出口蒸気温度T1
は、図2に示すようにガスタービン負荷の変動に拘ら
ず、常時設定温度a1 、実際には設定温度a1 の許容値
内になるように安定的に制御される。In this way, the superheater outlet steam temperature T1
As shown in FIG. 2, irrespective of fluctuations in the gas turbine load, stable control is performed so that the temperature is always within the permissible value of the set temperature a1, actually set temperature a1.
【0046】図3は、コンバインドサイクル発電プラン
トの第2実施例を示すものである。この実施例に示され
たコンバインドサイクル発電プラントは図1に示すコン
バインドサイクル発電プラントと基本的なサイクル構成
を同じくするので、同一構成部品には同じ符号を付して
説明を省略する。FIG. 3 shows a second embodiment of the combined cycle power plant. Since the combined cycle power generation plant shown in this embodiment has the same basic cycle configuration as the combined cycle power generation plant shown in FIG. 1, the same components are designated by the same reference numerals and the description thereof will be omitted.
【0047】このコンバインドサイクル発電プラント
は、排熱回収ボイラ7に備えられる過熱器23を上流側
と下流側とに分割し、分割された上流側過熱器23aと
下流側過熱器23bとの間に過熱器出口蒸気温度を下げ
るための主蒸気減温器43を設置する。In this combined cycle power plant, the superheater 23 provided in the exhaust heat recovery boiler 7 is divided into an upstream side and a downstream side, and between the divided upstream side superheater 23a and downstream side superheater 23b. A main steam desuperheater 43 for lowering the superheater outlet steam temperature is installed.
【0048】そして、この主蒸気減温器43に蒸気ター
ビンプラント1の復水給水系30から分岐された給水分
岐管44を接続し、この給水分岐管44の途中に主蒸気
減温用給水流量調節弁45を設置する。給水分岐管44
は例えば高圧ガス給水加熱器15の下流側から分岐され
ている。A feed water branch pipe 44 branched from the condensate feed water system 30 of the steam turbine plant 1 is connected to the main steam desuperheater 43, and a main steam dehumidifying feed water flow amount is provided in the middle of the feed water branch pipe 44. The control valve 45 is installed. Water supply branch pipe 44
Is branched from the downstream side of the high pressure gas feed water heater 15, for example.
【0049】この主蒸気減温用給水流量調節弁45は弁
制御装置36Aの給水流量調節弁開度演算器46からの
弁制御信号により弁制御され、この弁制御により分割さ
れた過熱器23a,23bの中間部に供給される給水流
量が制御される。The feed water flow rate adjusting valve 45 for reducing the temperature of the main steam is valve-controlled by a valve control signal from a feed water flow rate adjusting valve opening calculator 46 of a valve control device 36A, and the superheater 23a divided by this valve control, The water supply flow rate supplied to the intermediate portion of 23b is controlled.
【0050】弁制御装置36Aは、図1に示した弁制御
装置36に給水流量調節弁開度演算器46を加設したも
のであり、弁制御装置36Aの減算器37には、過熱器
出口蒸気温度検出器38で検出された過熱器出口蒸気温
度設定値aが入力され、両者の温度偏差δが主蒸気減温
用給水流量調節弁開度演算器46へ出力する。この主蒸
気減温用給水流量調節弁開度演算器46では温度偏差δ
に比例した主蒸気減温用給水流量調節弁開度を求め、主
蒸気減温用給水流量調節弁45を操作するようになって
い。The valve control device 36A is the valve control device 36 shown in FIG. 1 to which a feed water flow rate control valve opening calculator 46 is added. The subtractor 37 of the valve control device 36A has a superheater outlet. The superheater outlet steam temperature set value a detected by the steam temperature detector 38 is input, and the temperature deviation δ between the two is output to the main steam temperature reducing feed water flow rate control valve opening calculator 46. In the main steam temperature reducing feed water flow rate control valve opening calculator 46, the temperature deviation δ
The main steam temperature reducing feed water flow rate control valve opening proportional to is calculated, and the main steam temperature reducing feed water flow rate control valve 45 is operated.
【0051】なお、弁制御装置36Aは、図1に示す弁
制御装置36に給水流量調節弁開度演算器46を設置し
た例を示したが、弁制御装置36Aは必ずしもこれに限
定されず、主蒸気流量調節弁40の弁制御を行なう弁制
御装置と給水流量調節弁45の弁制御を行なう弁制御装
置とをそれぞれ独立させた構成としてもよい。Although the valve control device 36A shows an example in which the feed water flow rate control valve opening calculator 46 is installed in the valve control device 36 shown in FIG. 1, the valve control device 36A is not necessarily limited to this. A valve control device that controls the main steam flow rate control valve 40 and a valve control device that controls the feed water flow rate control valve 45 may be independent of each other.
【0052】次に、このコンバインドサイクル発電プラ
ントの蒸気温度コントロール動作について説明する。Next, the steam temperature control operation of this combined cycle power plant will be described.
【0053】過熱器出口蒸気温度T1 が過熱器出口蒸気
温度設定値aを超えた場合、上記に示すように主蒸気流
量調節弁40が開いて過熱器23へ供給される主蒸気流
量が増加し、過熱器23内の蒸気温度が低下するが、過
熱器出口蒸気温度設定値aになるまでに時間が掛かる。
そこで、主蒸気減温器43に給水を供給して過熱器23
内の蒸気温度を迅速に低下させる。When the superheater outlet steam temperature T1 exceeds the superheater outlet steam temperature set value a, the main steam flow rate control valve 40 opens to increase the main steam flow rate supplied to the superheater 23 as described above. The steam temperature in the superheater 23 decreases, but it takes time to reach the superheater outlet steam temperature set value a.
Therefore, supply water to the main steam desuperheater 43 to supply the superheater 23.
Rapidly reduce the steam temperature inside.
【0054】すなわち、過熱器出口蒸気温度検出器35
から検出される過熱器出口蒸気温度T1 が、過熱器出口
蒸気温度設定値aよりも大きくなるため、減算器37か
ら出力される温度偏差δがδ>0となり、主蒸気減温用
給水流量調節弁開度演算器46が開方向の指令を主蒸気
減温用給水流量調節弁45に対して行なうので、主蒸気
減温用給水流量調節弁45が開くように操作される。That is, the superheater outlet steam temperature detector 35
Since the superheater outlet steam temperature T1 detected from is larger than the superheater outlet steam temperature set value a, the temperature deviation δ output from the subtractor 37 becomes δ> 0, and the main steam temperature decreasing feed water flow rate adjustment Since the valve opening calculator 46 issues an opening direction command to the main steam temperature decreasing feed water flow rate control valve 45, the main steam temperature decreasing feed water flow rate control valve 45 is operated to open.
【0055】過熱器出口蒸気温度T1 が過熱器出口蒸気
温度設定値aよりも低くなった場合、主蒸気流量調節弁
40が閉じて過熱器23へ供給される主蒸気流量が減少
し、過熱器23内の蒸気温度が上昇するが、過熱器出口
蒸気温度設定値aになるまでに時間が掛かる。そこで、
主蒸気減温器43に供給していた給水を停止させて過熱
器23内の蒸気温度を迅速に上昇させる。When the superheater outlet steam temperature T1 becomes lower than the superheater outlet steam temperature set value a, the main steam flow rate control valve 40 is closed and the main steam flow rate supplied to the superheater 23 is reduced, so that the superheater Although the steam temperature in 23 rises, it takes time to reach the superheater outlet steam temperature set value a. Therefore,
The water supply that has been supplied to the main steam desuperheater 43 is stopped to quickly raise the steam temperature in the superheater 23.
【0056】すなわち、過熱器出口蒸気温度検出器35
から検出される過熱器出口蒸気温度T1 が、過熱器出口
蒸気温度設定値aよりも小さくなるため、減算器37か
ら出力される温度偏差δがδ<0となり、主蒸気減温用
給水流量調節弁開度演算器46が開方向の指令を主蒸気
減温用給水流量調節弁45に対して行なうので、主蒸気
減温用給水流量調節弁45が閉じるように操作される。That is, the superheater outlet steam temperature detector 35
Since the superheater outlet steam temperature T1 detected from is smaller than the superheater outlet steam temperature set value a, the temperature deviation δ output from the subtractor 37 becomes δ <0, and the main steam temperature decreasing feed water flow rate adjustment Since the valve opening calculator 46 issues an opening direction command to the main steam temperature decreasing feed water flow rate control valve 45, the main steam temperature decreasing feed water flow rate control valve 45 is operated to close.
【0057】これにより、排熱回収ボイラ7の過熱器2
3から送り出される主蒸気温度T1は急速に設定温度a
となるように調節制御され、ガスタービン25の負荷変
動に拘らず、図2に示すように設定温度に安定的に保持
される。As a result, the superheater 2 of the exhaust heat recovery boiler 7
The temperature T1 of the main steam delivered from the
The temperature is regulated and controlled so that the temperature is stably maintained at the set temperature as shown in FIG. 2 regardless of the load fluctuation of the gas turbine 25.
【0058】図4は、コンバインドサイクル発電プラン
トの第3実施例を示すものである。FIG. 4 shows a third embodiment of the combined cycle power plant.
【0059】この実施例に示されたコンバインドサイク
ル発電プラントも基本的なプラント構成は、図1に示す
コンバインドサイクル発電プラントと異ならないので、
同じ構成部品には同一符号を付して説明を省略する。The combined cycle power plant shown in this embodiment also has the same basic plant configuration as that of the combined cycle power plant shown in FIG.
The same components are assigned the same reference numerals and explanations thereof are omitted.
【0060】この実施例に示されたコンバインドサイク
ル発電プラントは、排熱回収ボイラ7の過熱器23出口
側の主蒸気温度が設定温度になるように制御する代り
に、排熱回収ボイラ7の再熱器8の出口側の再熱蒸気温
度がガスタービン25の負荷変動に拘らず設定温度bと
なるように制御したものである。In the combined cycle power plant shown in this embodiment, instead of controlling the main steam temperature on the outlet side of the superheater 23 of the exhaust heat recovery boiler 7 to reach the set temperature, the exhaust heat recovery boiler 7 is reheated. The reheat steam temperature on the outlet side of the heater 8 is controlled so as to reach the set temperature b regardless of the load fluctuation of the gas turbine 25.
【0061】また、排熱回収ボイラ7の過熱器出口側
に、再熱器8の出口蒸気温度を検出する温度検出器50
が設けられており、この温度検出器50からの再熱器出
口蒸気温度T2 の温度検出信号は弁コントローラとして
の弁制御装置51の減算器52に入力される。この減算
器52には、再熱器出口蒸気温度設定器53からの再熱
器出口蒸気温度設定値bも入力され、両者の温度偏差γ
が演算される。演算された温度偏差γは再熱蒸気流量調
節弁開度演算器53に出力される。A temperature detector 50 for detecting the outlet steam temperature of the reheater 8 is provided on the outlet side of the superheater of the exhaust heat recovery boiler 7.
The temperature detection signal of the reheater outlet steam temperature T2 from the temperature detector 50 is input to the subtractor 52 of the valve controller 51 as a valve controller. The reheater outlet steam temperature set value b from the reheater outlet steam temperature setter 53 is also input to the subtractor 52, and the temperature deviation γ between them is γ.
Is calculated. The calculated temperature deviation γ is output to the reheat steam flow control valve opening degree calculator 53.
【0062】このように、弁制御装置51は減算器52
と再熱器蒸気温度設定器53と再熱蒸気流量調節弁開度
演算器54とを備えており、この開度演算器54からの
弁制御信号が再熱蒸気流量調節弁55に入力され、この
再熱蒸気流量調節弁55の弁制御を行なっている。As described above, the valve control device 51 includes the subtractor 52.
And a reheater steam temperature setting device 53 and a reheat steam flow control valve opening degree calculator 54. A valve control signal from the opening degree calculator 54 is input to the reheat steam flow rate adjusting valve 55. The reheat steam flow control valve 55 is valve-controlled.
【0063】再熱蒸気流量調節弁55は、蒸気タービン
4のタービン高圧部5から排熱回収ボイラ7の再熱器8
に至る蒸気流路に設置され、この再熱蒸気流量調節弁5
5の弁制御により、再熱器8に案内される再熱蒸気量が
コントロールされる。The reheat steam flow rate adjusting valve 55 is provided from the turbine high pressure section 5 of the steam turbine 4 to the reheater 8 of the exhaust heat recovery boiler 7.
This reheat steam flow control valve 5 is installed in the steam flow path leading to
The valve control of No. 5 controls the amount of reheated steam guided to the reheater 8.
【0064】次に、図4に示すコンバインドサイクル発
電プラントの蒸気温度コントロール動作について説明す
る。Next, the steam temperature control operation of the combined cycle power plant shown in FIG. 4 will be described.
【0065】再熱器出口蒸気温度T2 が、再熱器出口蒸
気温度設定値bを超えた場合、再熱器出口蒸気温度検出
器50から検出される過熱器出口蒸気温度T2 が、再熱
器出口蒸気温度設定値bよりも大きくなるため、減算器
52から出力される温度偏差γがγ>0となり、再熱蒸
気流量調節弁開度演算器54が開方向の再熱蒸気流量調
節弁55に対して行なうので、再熱蒸気流量調節弁55
が開くように操作される。When the reheater outlet steam temperature T2 exceeds the reheater outlet steam temperature set value b, the superheater outlet steam temperature T2 detected by the reheater outlet steam temperature detector 50 is Since it becomes larger than the outlet steam temperature set value b, the temperature deviation γ output from the subtractor 52 becomes γ> 0, and the reheat steam flow control valve opening calculator 54 opens the reheat steam flow control valve 55. Reheat steam flow control valve 55
Is operated to open.
【0066】この再熱蒸気流量調節弁55の弁開方向制
御により、排熱回収ボイラ7の再熱器8に案内される再
熱蒸気量が増大し、再熱器出口蒸気温度T2 がその設定
温度bに近付き、設定温度bとなるように調節される。By controlling the valve opening direction of the reheat steam flow control valve 55, the amount of reheat steam guided to the reheater 8 of the exhaust heat recovery boiler 7 increases, and the reheater outlet steam temperature T2 is set to that value. The temperature is adjusted so that it approaches the temperature b and reaches the set temperature b.
【0067】再熱器出口蒸気温度T2 が再熱器出口蒸気
温度設定値bよりも低くなった場合、再熱器出口蒸気温
度検出器50から検出される再熱器出口蒸気温度T2
が、再熱器出口蒸気温度設定値bよりも小さくなるた
め、減算器52から出力される温度偏差γがγ<0とな
り、再熱蒸気流量調節弁開度演算器54が閉方向の弁作
動指令を主蒸気流量調節弁55に対して行なうので、再
熱蒸気流量調節弁55が閉じるように操作される。When the reheater outlet steam temperature T2 becomes lower than the reheater outlet steam temperature set value b, the reheater outlet steam temperature T2 detected by the reheater outlet steam temperature detector 50
However, since it becomes smaller than the reheater outlet steam temperature set value b, the temperature deviation γ output from the subtractor 52 becomes γ <0, and the reheat steam flow control valve opening degree calculator 54 operates the valve in the closing direction. Since the command is issued to the main steam flow control valve 55, the reheat steam flow control valve 55 is operated so as to close.
【0068】この再熱蒸気流量調節弁55の弁閉方向制
御により、排熱回収ボイラ7の再熱器8に案内される再
熱蒸気量が絞られ、再熱器出口蒸気温度T2 がその設定
温度bとなるように温度上昇する。By controlling the valve closing direction of the reheat steam flow control valve 55, the amount of reheat steam guided to the reheater 8 of the exhaust heat recovery boiler 7 is throttled, and the reheater outlet steam temperature T2 is set. The temperature rises to reach the temperature b.
【0069】このようにして、再熱器出口蒸気温度T2
は、図2に示すようにガスタービン負荷の変動に拘ら
ず、常時設定温度bになるように安定的に制御される。In this way, the reheater outlet steam temperature T2
Is stably controlled so as to always be at the set temperature b regardless of the fluctuation of the gas turbine load as shown in FIG.
【0070】図5は、コンバインドサイクル発電プラン
トの第4実施例を示すものである。FIG. 5 shows a fourth embodiment of the combined cycle power plant.
【0071】この実施例に示されたコンバインドサイク
ル発電プラントは図3に示すコンバインドサイクル発電
プラントと基本的なサイクル構成を同じくするので、同
じ構成部品には同一符号を付して説明を省略する。Since the combined cycle power generation plant shown in this embodiment has the same basic cycle configuration as the combined cycle power generation plant shown in FIG. 3, the same components are designated by the same reference numerals and the description thereof will be omitted.
【0072】このコンバインドサイクル発電プラント
は、排熱回収ボイラ7に備えられる再熱器8を上流側と
下流側とに分割し、分割された上流側再熱器8aと下流
側再熱器8bとの間に再熱器8の蒸気温度を下げる再熱
蒸気減温器56を設置する。In this combined cycle power plant, the reheater 8 provided in the exhaust heat recovery boiler 7 is divided into an upstream side and a downstream side, and the upstream side reheater 8a and the downstream side reheater 8b are divided. A reheated steam desuperheater 56 that lowers the steam temperature of the reheater 8 is installed between.
【0073】そして、この再熱蒸気減温器56に復水給
水系30から分岐された給水分岐管57を接続し、この
給水分岐管57の途中に再熱蒸気減温用給水流量調節弁
58を設置する。給水分岐管57は例えば給水ポンプ1
7から分岐されている。A feed water branch pipe 57 branched from the condensate water supply system 30 is connected to the reheat steam desuperheater 56, and a reheat steam dehumidification feed water flow control valve 58 is provided in the middle of the water feed branch pipe 57. Set up. The water supply branch pipe 57 is, for example, the water supply pump 1
It is branched from 7.
【0074】一方、再熱蒸気減温用給水流量調節弁58
は、弁制御装置51Aの給水流量調節弁開度演算器59
からの弁制御信号により弁制御される。この弁制御によ
り分割された再熱器8a,8bの中間部に供給される給
水流量が制御される。On the other hand, the feed water flow rate control valve 58 for reheat steam temperature reduction
Is the water supply flow rate control valve opening degree calculator 59 of the valve control device 51A.
The valve is controlled by a valve control signal from. By this valve control, the flow rate of the feed water supplied to the intermediate portion of the reheaters 8a and 8b divided is controlled.
【0075】弁制御装置51Aは、図4に示した弁制御
装置51に給水流量調節弁開度演算器59を加設したも
のであり、弁制御装置51Aの減算器52には、過熱器
出口蒸気温度検出器50で検出された再熱器出口蒸気温
度T2 と、再熱器出口蒸気温度設定器53からの再熱器
出口蒸気温度設定値bが入力され、両者の温度偏差γが
再熱蒸気減温用給水流量調節弁開度演算器59へ出力す
る。この再熱蒸気減温用給水流量調節弁開度演算器59
では温度偏差γに比例した再熱蒸気減温用給水流量調節
弁開度を求め、再熱蒸気減温用給水流量調節弁58を操
作するようになっている。The valve control device 51A is obtained by adding a feed water flow rate control valve opening calculator 59 to the valve control device 51 shown in FIG. 4, and the subtractor 52 of the valve control device 51A has a superheater outlet. The reheater outlet steam temperature T2 detected by the steam temperature detector 50 and the reheater outlet steam temperature set value b from the reheater outlet steam temperature setting device 53 are input, and the temperature deviation γ of both is reheated. Output to the steam temperature reducing feed water flow rate control valve opening calculator 59. This reheat steam temperature reducing feed water flow rate control valve opening degree calculator 59
Then, the opening degree of the reheated steam temperature reducing feed water flow rate control valve is calculated in proportion to the temperature deviation γ, and the reheated steam temperature reduction feed water flow rate control valve 58 is operated.
【0076】なお、弁制御装置51Aは、図4に示す弁
制御装置51に給水流量調節弁開度演算器59を設置し
た例を示したが、弁制御装置51Aは必ずしもこれに限
定されず、再熱蒸気流量調節弁55の弁制御を行なう弁
制御装置と給水流量調節弁58の弁制御を行なう弁制御
装置とをそれぞれ独立した構成としてもよい。Although the valve control device 51A shows an example in which the feed water flow rate control valve opening calculator 59 is installed in the valve control device 51 shown in FIG. 4, the valve control device 51A is not necessarily limited to this. The valve control device for controlling the reheat steam flow rate adjusting valve 55 and the valve control device for controlling the feedwater flow rate adjusting valve 58 may be independently configured.
【0077】次に、このコンバインドサイクル発電プラ
ントの蒸気温度コントロール動作について説明する。Next, the steam temperature control operation of this combined cycle power plant will be described.
【0078】再熱器出口蒸気温度T2 が再熱器出口蒸気
温度設定値bを超えた場合、上記に示すように再熱蒸気
流量調節弁55が開いて再熱器8へ供給される再熱蒸気
流量が増加し、再熱器8内の蒸気温度が低下するが、再
熱器出口蒸気温度設定値bになるまでに時間が掛かる。
そこで、再熱蒸気減温器56に給水を供給して再熱器8
内の蒸気温度を直ちに迅速に低下させる。When the reheater outlet steam temperature T2 exceeds the reheater outlet steam temperature set value b, the reheat steam flow rate control valve 55 is opened to reheat the reheater 8 as described above. Although the steam flow rate increases and the steam temperature in the reheater 8 decreases, it takes time to reach the reheater outlet steam temperature set value b.
Therefore, supply water to the reheat steam desuperheater 56 to supply the reheater 8
Immediately and quickly reduce the steam temperature inside.
【0079】すなわち、再熱器出口蒸気温度検出器50
から検出される再熱器出口蒸気温度T2 が、再熱器出口
蒸気温度設定値bよりも大きくなるため、減算器52か
ら出力される温度偏差γがγ>0となり、再熱蒸気減温
用給水流量調節弁開度演算器59が開方向の指令を再熱
蒸気減温用給水流量調節弁58に対して行なうので、再
熱蒸気減温用給水流量調節弁58が開くように操作され
る。That is, the reheater outlet steam temperature detector 50
Since the reheater outlet steam temperature T2 detected from the reheater outlet steam temperature setting value b becomes larger than the reheater outlet steam temperature set value b, the temperature deviation γ output from the subtractor 52 becomes γ> 0, and the temperature of the reheat steam is reduced. Since the feed water flow rate adjusting valve opening degree calculator 59 issues an opening direction command to the reheat steam dehumidifying feed water flow rate adjusting valve 58, the reheat steam dehumidifying feed water flow rate adjusting valve 58 is operated to open. .
【0080】再熱器出口蒸気温度T2 が過熱器出口蒸気
温度設定値bよりも低くなった場合、再熱蒸気流量調節
弁55が閉じて再熱器8へ供給される再熱蒸気流量が減
少し、再熱器8内の蒸気温度が上昇するが、再熱器出口
蒸気温度設定値bになるまでに時間が掛かる。そこで、
再熱蒸気減温器56に供給していた給水を停止させて再
熱器8内の蒸気温度を直ぐに上昇させる。When the reheater outlet steam temperature T2 becomes lower than the superheater outlet steam temperature set value b, the reheat steam flow control valve 55 is closed and the reheat steam flow rate supplied to the reheater 8 decreases. Then, the steam temperature in the reheater 8 rises, but it takes time to reach the reheater outlet steam temperature set value b. Therefore,
The water supply supplied to the reheat steam desuperheater 56 is stopped to immediately raise the steam temperature in the reheater 8.
【0081】すなわち、再熱器出口蒸気温度検出器50
から検出される再熱器出口蒸気温度T2 が、再熱器出口
蒸気温度設定値bよりも小さくなるため、減算器52か
ら出力される温度偏差γがγ<0となり、再熱蒸気減温
用給水流量調節弁開度演算器59が閉方向の指令を再熱
蒸気減温用給水流量調節弁58に対して行なうので、再
熱蒸気減温用給水流量調節弁58が閉じるように操作さ
れる。That is, the reheater outlet steam temperature detector 50
Since the reheater outlet steam temperature T2 detected from is smaller than the reheater outlet steam temperature set value b, the temperature deviation γ output from the subtractor 52 is γ <0, and the temperature of the reheat steam is reduced. The feed water flow rate control valve opening calculator 59 issues a closing direction command to the reheat steam dehumidifying feed water flow rate regulating valve 58, so that the reheat steam dehumidifying feed water flow rate regulating valve 58 is operated to be closed. .
【0082】これにより、排熱回収ボイラ7の再熱器8
から送り出される再熱蒸気温度T2は急速に設定温度b
となるように調節制御され、ガスタービンの負荷変動に
拘らず、図2に示すように設定温度bに安定的に保持さ
れる。As a result, the reheater 8 of the exhaust heat recovery boiler 7
The reheated steam temperature T2 sent from the
The temperature is regulated and controlled so that the temperature is stably maintained at the set temperature b as shown in FIG. 2 regardless of the load fluctuation of the gas turbine.
【0083】なお、本発明の一実施例においては、排熱
回収ボイラの過熱器から送りされる主蒸気温度と再熱器
から送り出される再熱蒸気温度とを別個にコントロール
させたが、主蒸気温度と再熱蒸気温度を共にコントロー
ルするようにしてもよい。In the embodiment of the present invention, the main steam temperature sent from the superheater of the exhaust heat recovery boiler and the reheat steam temperature sent from the reheater are controlled separately. Both the temperature and the reheated steam temperature may be controlled.
【0084】[0084]
【発明の効果】以上に述べたように本発明に係るコンバ
インドサイクル発電プラントにおいては、請求項1に記
載したように、排熱回収ボイラの過熱器から送り出され
る主蒸気温度を温度検出器で検出して弁制御装置によ
り、主蒸気流量調節弁の弁制御を行ない、上記過熱器に
案内される主蒸気量をコントロールするようにしたの
で、過熱器出口の主蒸気温度を、ガスタービンの負荷変
動に拘らず、常時設定値に保持でき、安定したプラント
運転を行なうことができる。As described above, in the combined cycle power plant according to the present invention, as described in claim 1, the temperature detector detects the main steam temperature sent from the superheater of the exhaust heat recovery boiler. The valve control device controls the main steam flow control valve to control the amount of main steam guided to the superheater, so that the main steam temperature at the superheater outlet can be adjusted by changing the load on the gas turbine. Regardless of the above, the set value can be always maintained, and stable plant operation can be performed.
【0085】また、本発明に係るコンバインドサイクル
発電プラントは、請求項2に記載したように、過熱器出
口の蒸気温度を検出し、この検出信号により、排熱回収
ボイラ内で分割された上流側および下流側の過熱器の間
に供給される主蒸気減温用給水流量を給水流量調節弁で
制御したので、過熱器出口の主蒸気温度を常に迅速に設
定値に抑えることが可能となり、安定したプラント運転
を行なうことができる。Further, in the combined cycle power plant according to the present invention, as described in claim 2, the steam temperature at the outlet of the superheater is detected, and the upstream side divided in the exhaust heat recovery boiler is detected by this detection signal. Since the feed water flow rate for main steam temperature reduction supplied between the superheater on the downstream side and the downstream side is controlled by the feed water flow rate control valve, the main steam temperature at the outlet of the superheater can always be quickly suppressed to the set value and stable. The plant operation can be performed.
【0086】さらに、本発明に係るコンバインドサイク
ル発電プラントは、請求項3に記載したように、排熱回
収ボイラの再熱器から送り出される再熱蒸気温度を温度
検出器で検出して弁制御装置により、再熱蒸気流量調節
弁の弁制御を行ない、再熱器に案内される再熱蒸気量を
コントロールしたので、再熱器出口の再熱蒸気温度を、
ガスタービンの負荷変動に拘らず、常時設定値に保持で
き、安定したプラント運転を行なうことができる。Further, in the combined cycle power plant according to the present invention, as described in claim 3, the reheat steam temperature sent out from the reheater of the exhaust heat recovery boiler is detected by the temperature detector and the valve control device. By controlling the reheated steam flow rate control valve by controlling the reheated steam amount guided to the reheater, the reheated steam temperature at the reheater outlet is
Regardless of the load fluctuation of the gas turbine, the set value can be always maintained and stable plant operation can be performed.
【0087】さらにまた、本発明に係るコンバインドサ
イクル発電プラントは、請求項4に記載したように、再
熱器出口の蒸気温度を検出し、この検出信号により、排
熱回収ボイラ内で分割された再熱器の間に供給される再
熱蒸気減温用給水流量が制御されるので、ガスタービン
の負荷変動が生じても再熱器出口の再熱蒸気温度を常に
かつ迅速に設定値に抑えることが可能となり、安定した
プラント運転を行なうことができる。Further, in the combined cycle power plant according to the present invention, as described in claim 4, the steam temperature at the outlet of the reheater is detected, and the steam is recovered in the exhaust heat recovery boiler by this detection signal. Since the flow rate of reheated steam reducing water supplied between the reheaters is controlled, the reheated steam temperature at the reheater outlet is always and quickly suppressed to the set value even if the load on the gas turbine changes. Therefore, stable plant operation can be performed.
【図1】本発明に係るコンバインドサイクル発電プラン
トの一実施例を示す系統図。FIG. 1 is a system diagram showing an embodiment of a combined cycle power plant according to the present invention.
【図2】ガスタービンの負荷変動と主蒸気および再熱蒸
気温度特性との関係を示す図。FIG. 2 is a diagram showing a relationship between load fluctuation of a gas turbine and main steam and reheat steam temperature characteristics.
【図3】本発明に係るコンバインドサイクル発電プラン
トの他の実施例を示す系統図。FIG. 3 is a system diagram showing another embodiment of the combined cycle power plant according to the present invention.
【図4】本発明に係るコンバインドサイクル発電プラン
トの第3実施例を示す系統図。FIG. 4 is a system diagram showing a third embodiment of the combined cycle power plant according to the present invention.
【図5】本発明に係るコンバインドサイクル発電プラン
トの第4実施例を示す系統図。FIG. 5 is a system diagram showing a fourth embodiment of the combined cycle power plant according to the present invention.
【図6】従来のコンバインドサイクル発電プラントを示
す系統図。FIG. 6 is a system diagram showing a conventional combined cycle power plant.
【図7】従来のコンバインドサイクル発電プラントの排
熱回収ボイラで発生する主蒸気と再熱蒸気の温度特性を
示す図。FIG. 7 is a diagram showing temperature characteristics of main steam and reheated steam generated in an exhaust heat recovery boiler of a conventional combined cycle power plant.
1 蒸気タービンプラント 2 ガスタービンプラント 3 ボイラ 4 蒸気タービン 5 タービン高圧部 6 ボイラ再熱器 7 排熱回収ボイラ 8 再熱器 8a 上流側再熱器 8b 下流側再熱器 9 タービン中圧部 10 タービン低圧部 11 復水器 12 タービン発電機 14 低圧給水加熱器 15 低圧ガス給水加熱器 16 脱気器 17 給水ポンプ 18 高圧給水加熱器 19 高圧ガス給水加熱器 20 節炭器 21 蒸発器 22 ボイラ過熱器 23 過熱器 23a 上流側過熱器 23b 下流側過熱器 25 ガスタービン 26 タービン発電機 27 煙突 30 復水給水系 31 主蒸気系 32 再熱蒸気系 33 タービン排気系統 35 過熱器出口蒸気温度検出器 36A,36B 弁制御装置 37 減算器 38 過熱器出口蒸気温度設定器 39 主蒸気流量調節弁開度演算器 40 主蒸気流量調節弁 43 主蒸気減温器 44 給水分岐管 45 主蒸気減温用給水流量調節弁 46 給水流量調節弁開度演算器 50 再熱器出口蒸気温度検出器 51,51A 弁制御装置 52 減算器 53 再熱器出口蒸気温度設定器 54 再熱蒸気流量調節弁開度演算器 55 再熱蒸気流量調節弁 56 再熱蒸気減温器 57 給水分岐管 58 再熱蒸気減温用給水流量調節弁 59 給水流量調節弁開度演算器 1 steam turbine plant 2 gas turbine plant 3 boiler 4 steam turbine 5 turbine high pressure part 6 boiler reheater 7 exhaust heat recovery boiler 8 reheater 8a upstream reheater 8b downstream reheater 9 turbine medium pressure part 10 turbine Low-pressure part 11 Condenser 12 Turbine generator 14 Low-pressure feed water heater 15 Low-pressure gas feed water heater 16 Deaerator 17 Water supply pump 18 High-pressure feed water heater 19 High-pressure gas feed water heater 20 Cobber 21 Evaporator 22 Boiler superheater 23 superheater 23a upstream superheater 23b downstream superheater 25 gas turbine 26 turbine generator 27 chimney 30 condensate water supply system 31 main steam system 32 reheat steam system 33 turbine exhaust system 35 superheater outlet steam temperature detector 36A, 36B Valve control device 37 Subtractor 38 Superheater outlet steam temperature setting device 39 Main steam flow control valve opening Calculator 40 Main steam flow control valve 43 Main steam desuperheater 44 Water supply branch pipe 45 Main steam dehumidification feed water flow control valve 46 Supply water flow control valve opening degree calculator 50 Reheater outlet steam temperature detector 51, 51A valve Control device 52 Subtractor 53 Reheater outlet steam temperature setting device 54 Reheat steam flow control valve opening calculator 55 Reheat steam flow control valve 56 Reheat steam desuperheater 57 Water supply branch pipe 58 For reheat steam dehumidification Water supply flow rate control valve 59 Water supply flow rate control valve opening calculator
フロントページの続き (72)発明者 三巻 利夫 神奈川県横須賀市長坂二丁目6番1号 財 団法人電力中央研究所 横須賀研究所内 (72)発明者 田中 泰久 神奈川県横浜市鶴見区末広町2の4 株式 会社東芝京浜事業所内 (72)発明者 古川 俊樹 神奈川県横浜市鶴見区末広町2の4 株式 会社東芝京浜事業所内 (72)発明者 小沢 政弘 東京都江東区豊洲三丁目2番16号 石川島 播磨重工業株式会社豊洲総合事務所内Front page continued (72) Inventor Toshio Maki 2-6-1, Nagasaka, Yokosuka City, Kanagawa Prefecture Central Research Institute of Electric Power Industry, Yokosuka Research Institute (72) Inventor, Yasuhisa Tanaka, 2 Suehiro-cho, Tsurumi-ku, Yokohama-shi, Kanagawa Prefecture 4 Incorporated Toshiba Keihin Office (72) Inventor Toshiki Furukawa 2 Suehirocho, Tsurumi-ku, Yokohama, Kanagawa 4 Incorporated Toshiba Keihin Office (72) Inventor Masahiro Ozawa 3-2-16 Toyosu, Koto-ku, Tokyo Ishikawajima Harima Heavy Industries Co., Ltd.Toyosu General Office
Claims (4)
えた蒸気タービンプラントとガスタービンを備えたガス
タービンプラントとを組み合せてコンバインドサイクル
化する一方、前記ガスタービンからのタービン排ガス系
統に、過熱器および再熱器を備えた排熱回収ボイラと、
前記復水給水系の給水を加熱する高圧ガス給水加熱器
と、復水給水系の復水を加熱する低圧ガス給水加熱器と
をそれぞれ設置したコンバインドサイクル発電プラント
において、前記排熱回収ボイラの過熱器出口の蒸気温度
を検出する温度検出器と、上記過熱器へ供給される主蒸
気流量を制御する主蒸気流量調節弁と、前記温度検出器
からの温度検出信号を入力して、過熱器出口蒸気温度が
設定値になるように、前記主蒸気流量調節弁の弁制御を
行なう弁制御装置とを有することを特徴とするコンバイ
ンドサイクル発電プラント。1. A steam turbine plant equipped with a boiler, a steam turbine, and a condensate water supply system and a gas turbine plant equipped with a gas turbine are combined to form a combined cycle, while the turbine exhaust gas system from the gas turbine is overheated. And a heat recovery steam generator equipped with a reheater,
In a combined cycle power plant in which a high-pressure gas feed water heater that heats the condensate feed water supply water and a low-pressure gas feed water heater that heats the condensate feed water condensate water are installed respectively, the exhaust heat recovery boiler overheat A temperature detector for detecting the steam temperature at the outlet of the vessel, a main steam flow rate control valve for controlling the flow rate of the main steam supplied to the superheater, and a temperature detection signal from the temperature detector are input to the superheater outlet. A combined cycle power plant comprising: a valve control device that controls the valve of the main steam flow control valve so that the steam temperature reaches a set value.
上流側過熱器と下流側過熱器とに分割し、分割された過
熱器間に供給される給水の流量を制御する主蒸気減温用
給水流量調節弁を設ける一方、この給水流量調節弁を弁
制御する弁制御装置を設け、この弁制御装置は過熱器出
口蒸気温度検出器からの温度検出信号を入力して、過熱
器出口蒸気温度が設定値となるように給水流量調節弁の
弁制御を行なうように設定した請求項1記載のコンバイ
ンドサイクル発電プラント。2. A main steam desuperheater for controlling a flow rate of feed water supplied between the divided superheaters by dividing the superheater incorporated in the exhaust heat recovery boiler into an upstream superheater and a downstream superheater. While providing the feed water flow rate control valve, a valve control device for controlling this feed water flow rate control valve is provided, and this valve control device inputs the temperature detection signal from the superheater outlet steam temperature detector to output the superheater outlet steam temperature. 2. The combined cycle power plant according to claim 1, wherein the valve control of the feed water flow rate control valve is set so that is a set value.
えた蒸気タービンプラントとガスタービンを備えたガス
タービンプラントとを組み合せてコンバインドサイクル
化する一方、前記ガスタービンからのタービン排ガス系
統に、過熱器および再熱器を備えた排熱回収ボイラと、
前記復水給水系の給水を加熱する高圧ガス給水加熱器
と、復水給水系の復水を加熱する低圧ガス給水加熱器と
をそれぞれ設置したコンバインドサイクル発電プラント
において、前記排熱回収ボイラの再熱器出口の蒸気温度
を検出する温度検出器と、上記再熱器へ供給される再熱
蒸気流量を制御する再熱蒸気流量調節弁と、前記温度検
出器からの温度検出信号を入力して、再熱器出口の蒸気
温度が設定値となるように、前記再熱蒸気流量調節弁の
弁制御を行なう弁制御装置とを有することを特徴とする
コンバインドサイクル発電プラント。3. A steam turbine plant equipped with a boiler, a steam turbine, and a condensate water supply system and a gas turbine plant equipped with a gas turbine are combined to form a combined cycle, while the turbine exhaust gas system from the gas turbine is overheated. And a heat recovery steam generator equipped with a reheater,
In a combined cycle power plant in which a high-pressure gas feedwater heater for heating the condensate feedwater feedwater and a low-pressure gas feedwater heater for heating the condensate feedwater condensate are installed, respectively, A temperature detector that detects the steam temperature at the outlet of the heat device, a reheat steam flow control valve that controls the reheat steam flow rate supplied to the reheater, and a temperature detection signal from the temperature detector are input. And a valve control device that controls the valve of the reheat steam flow control valve so that the steam temperature at the outlet of the reheater reaches a set value.
上流側再熱器と下流側再熱器とに分割し、分割された再
熱器間に供給される給水の流量を制御する再熱蒸気減温
用給水流量調節弁を設ける一方、この給水流量調節弁を
弁制御する弁制御装置を設け、この弁制御装置は再熱器
出口蒸気温度検出器からの温度検出信号を入力して、再
熱器出口蒸気温度が設定値となるように給水流量調節弁
の弁制御を行なうように設定した請求項3記載のコンバ
インドサイクル発電プラント。4. A reheater incorporated in an exhaust heat recovery boiler is divided into an upstream reheater and a downstream reheater, and a reheater for controlling a flow rate of feed water supplied between the divided reheaters. While providing a feed water flow rate control valve for heat steam temperature reduction, a valve control device for controlling this feed water flow rate control valve is provided, and this valve control device inputs the temperature detection signal from the reheater outlet steam temperature detector. The combined cycle power plant according to claim 3, wherein the feed water flow rate control valve is controlled so that the reheater outlet steam temperature becomes a set value.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP04349096A JP3133183B2 (en) | 1992-12-28 | 1992-12-28 | Combined cycle power plant |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP04349096A JP3133183B2 (en) | 1992-12-28 | 1992-12-28 | Combined cycle power plant |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH06200709A true JPH06200709A (en) | 1994-07-19 |
JP3133183B2 JP3133183B2 (en) | 2001-02-05 |
Family
ID=18401466
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP04349096A Expired - Lifetime JP3133183B2 (en) | 1992-12-28 | 1992-12-28 | Combined cycle power plant |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3133183B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2020125702A (en) * | 2019-02-04 | 2020-08-20 | 株式会社日立製作所 | Cogeneration system |
CN112534121A (en) * | 2018-08-08 | 2021-03-19 | 川崎重工业株式会社 | Combined cycle power plant |
CN114413251A (en) * | 2021-12-09 | 2022-04-29 | 广西电网有限责任公司电力科学研究院 | System for adjusting main steam temperature of Pi type hedging once-through boiler |
-
1992
- 1992-12-28 JP JP04349096A patent/JP3133183B2/en not_active Expired - Lifetime
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112534121A (en) * | 2018-08-08 | 2021-03-19 | 川崎重工业株式会社 | Combined cycle power plant |
JP2020125702A (en) * | 2019-02-04 | 2020-08-20 | 株式会社日立製作所 | Cogeneration system |
US11506115B2 (en) | 2019-02-04 | 2022-11-22 | Hitachi, Ltd. | Cogeneration system |
CN114413251A (en) * | 2021-12-09 | 2022-04-29 | 广西电网有限责任公司电力科学研究院 | System for adjusting main steam temperature of Pi type hedging once-through boiler |
CN114413251B (en) * | 2021-12-09 | 2023-10-27 | 广西电网有限责任公司电力科学研究院 | System for adjusting main steam temperature of Pi-type opposite-flow direct-current boiler |
Also Published As
Publication number | Publication date |
---|---|
JP3133183B2 (en) | 2001-02-05 |
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