JPH094416A - Steam system disconnection control method for multi-axis combined plant - Google Patents
Steam system disconnection control method for multi-axis combined plantInfo
- Publication number
- JPH094416A JPH094416A JP15324695A JP15324695A JPH094416A JP H094416 A JPH094416 A JP H094416A JP 15324695 A JP15324695 A JP 15324695A JP 15324695 A JP15324695 A JP 15324695A JP H094416 A JPH094416 A JP H094416A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- exhaust gas
- gas boiler
- turbine
- turbine bypass
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
(57)【要約】
【目的】 多軸コンバインドプラントにおいて、運転中
のガスタービンを停止する際、この操作を円滑に、しか
も特別の装置を新たに設けることなく実施する方法を得
ること。
【構成】 排ガスボイラ出口蒸気圧力と、タービンバイ
パス弁開度とから、タービンバイパスラインに流れる蒸
気流量を計算して求め、その値を排ガスボイラ発生蒸気
流量の実測値と比較し、両者が一致した時点で排ガスボ
イラ出口弁の閉鎖指令を出すようにしたもの。
(57) [Summary] [Purpose] To obtain a method for smoothly performing this operation when a gas turbine in operation is stopped in a multi-shaft combined plant, without additionally providing a special device. [Structure] Calculate the steam flow rate flowing through the turbine bypass line from the exhaust gas boiler outlet steam pressure and the turbine bypass valve opening, compare that value with the measured value of the exhaust gas boiler generated steam flow rate, and find that both agree. A command to close the exhaust gas boiler outlet valve was issued at that time.
Description
【０００１】[0001]
【産業上の利用分野】本発明は蒸気系の切離し制御を要
する多軸コンバインドプラントに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-screw combined plant requiring separation control of a steam system.
【０００２】[0002]
【従来の技術】ガスタービンと蒸気タービンを組み合せ
たコンバインドプラント発電は、従来火力発電に比べ
て、熱効率が画期的に優れているため、国内外で建設が
進められている。2. Description of the Related Art Combined plant power generation, which combines a gas turbine and a steam turbine, is remarkably superior in thermal efficiency to conventional thermal power generation, so construction is underway in Japan and overseas.
【０００３】ガスタービンと蒸気タービンの組合せ方に
は、主に、次の２通りが採用されている。The following two methods are mainly used to combine the gas turbine and the steam turbine.
【０００４】１）ガスタービンと蒸気タービンを同一の
軸につなげる一軸コンバインドプラント。1) A single-shaft combined plant in which a gas turbine and a steam turbine are connected to the same shaft.
【０００５】２）ガスタービンと蒸気タービンを個別に
配置する多軸コンバインドプラント。 本発明は、上記の内、多軸コンバインドプラントの制御
に適用するものである。2) A multi-shaft combined plant in which a gas turbine and a steam turbine are separately arranged. The present invention is applied to control of a multi-axis combined plant among the above.
【０００６】図２に従来の多軸コンバインドプラントの
概略系統を示す。多軸コンバインドプラントは熱効率を
より高くするため、一般に２台以上のガスタービンから
構成される。図２は、説明を簡略にするため、２台のガ
スタービンから構成されるプラントを示した。FIG. 2 shows a schematic system of a conventional multi-axis combined plant. A multi-shaft combined plant is generally composed of two or more gas turbines in order to improve thermal efficiency. FIG. 2 shows a plant composed of two gas turbines in order to simplify the description.
【０００７】すなわち、それぞれのガスタービン（１，
２）には発電機（３，４）が接続されており、またガス
タービン（１，２）の排ガスは、排ガスボイラ（５，
６）に導かれ蒸気を生み出す。それぞれの排ガスボイラ
（５，６）から発生した蒸気は合流し、蒸気タービン
（７）を駆動することにより蒸気タービン（７）に接続
された発電機（８）にて発電する。That is, each gas turbine (1,
A generator (3, 4) is connected to 2), and the exhaust gas of the gas turbine (1, 2) is discharged from the exhaust gas boiler (5, 5).
It is guided to 6) and produces steam. The steam generated from each of the exhaust gas boilers (5, 6) joins and drives the steam turbine (7) to generate electric power by a generator (8) connected to the steam turbine (7).
【０００８】多軸コンバインドプラントの特徴は、必要
とする発電量に合わせて、運転するガスタービンの台数
を切り替えることにより、プラントの部分負荷において
も高効率を維持出来る点である。A feature of the multi-shaft combined plant is that high efficiency can be maintained even in a partial load of the plant by switching the number of operating gas turbines in accordance with the required power generation amount.
【０００９】したがって、運用においてガスタービンの
台数切替え操作は、頻繁に実施される。その切替え操作
時に、蒸気タービンへの流入蒸気量が突変するなど、急
激に変化することは、プラントの発電量が急変するだけ
でなく、蒸気タービンの寿命を短くすることになりかね
ず、好ましいことではない。すなわち、切替え操作中、
蒸気の行き先をうまく制御することは非常に重要であ
る。Therefore, in operation, the switching operation of the number of gas turbines is frequently carried out. At the time of the switching operation, a sudden change, such as a sudden change in the amount of steam flowing into the steam turbine, may cause not only a sudden change in the power generation amount of the plant but also a shortening of the life of the steam turbine, which is preferable. Not that. That is, during the switching operation,
Good control of steam destination is very important.
【００１０】コンバインドプラントには、プラントの起
動停止時に用いるタービンバイパスライン（１７）があ
り、そのラインにはタービンバイパス弁が設置されてい
る。The combined plant has a turbine bypass line (17) used when starting and stopping the plant, and a turbine bypass valve is installed in the line.
【００１１】図の説明を簡略化するため、蒸気系統を１
系統のみ示すが、実際のプラントにおいては、２系統か
ら３系統有る場合がほとんどである。通常運転中は、排
ガスボイラ出口弁（９，１０）はいずれも全開してお
り、排ガスボイラにて発生する蒸気は全て排ガスボイラ
出口弁（９，１０）、排ガスボイラ出口逆止弁（１１，
１２）をとおり、合流後、蒸気タービン（７）に導かれ
ている。その時タービンバイパス弁（１５，１６）はい
ずれも全閉している。In order to simplify the description of the figure, the steam system is
Only the system is shown, but in most of the actual plants, there are two to three systems. During normal operation, all of the exhaust gas boiler outlet valves (9, 10) are fully opened, and all steam generated in the exhaust gas boiler is exhaust gas boiler outlet valve (9, 10), exhaust gas boiler check valve (11, 10).
After merging through 12), it is led to the steam turbine (7). At that time, the turbine bypass valves (15, 16) are all closed.
【００１２】いま、ここで、ガスタービンの一台、たと
えばガスタービン（１）を停止する場合には、まず、蒸
気タービン（７）への流入蒸気量が急変しないようにタ
ービンバイパス弁（１５）を徐々に開き、排ガスボイラ
（５）の発生蒸気がすべてタービンバイパスライン（１
７）から復水器（１８）へ流れるようにする。Now, when stopping one gas turbine, for example, the gas turbine (1), first, the turbine bypass valve (15) is first prevented so that the amount of steam flowing into the steam turbine (7) does not suddenly change. Gradually open the exhaust gas boiler (5) and all the steam generated in the turbine bypass line (1
Allow flow from 7) to condenser (18).
【００１３】この状態で排ガスボイラ出口弁（９）を閉
めても蒸気タービン（７）への蒸気量変化は無いことに
なるが、排ガスボイラ出口弁（９）を閉め、蒸気系の切
り離し操作を完了し、次いでガスタービン（１）の停止
操作へと移ることとなる。Even if the exhaust gas boiler outlet valve (9) is closed in this state, there is no change in the amount of steam to the steam turbine (7), but the exhaust gas boiler outlet valve (9) is closed and the steam system disconnection operation is performed. It will be completed, and then it will move to the shutdown operation of the gas turbine (1).
【００１４】なお、排ガスボイラ（５）の発生蒸気がす
べてタービンバイパスライン（１７）へ流れていること
を検知することは重要であり、従来は以下のようにして
これを行っていた。It is important to detect that all the steam generated in the exhaust gas boiler (5) is flowing to the turbine bypass line (17), and this has been conventionally done as follows.
【００１５】プラントの計測点には、それぞれの排ガス
ボイラ出口蒸気圧力（１９，２０）、それぞれの排ガス
ボイラ発生蒸気流量（２１，２２）、タービンバイパス
弁開度（２３，２４）、蒸気タービン入口蒸気圧力（２
５）を計測する計器が従来から設置されている。停止す
る排ガスボイラ出口蒸気圧力（１９）が、蒸気タービン
入口蒸気圧力（２５）よりも低くなれば、排ガスボイラ
発生蒸気がすべてタービンバイパスライン（１７）に流
れていると言える。At the measurement points of the plant, respective exhaust gas boiler outlet steam pressures (19, 20), respective exhaust gas boiler generated steam flow rates (21, 22), turbine bypass valve opening (23, 24), steam turbine inlet Steam pressure (2
A measuring instrument for measuring 5) has been conventionally installed. If the exhaust gas boiler outlet steam pressure (19) to be stopped becomes lower than the steam turbine inlet steam pressure (25), it can be said that all the exhaust gas boiler generated steam is flowing to the turbine bypass line (17).
【００１６】この時、運転継続する排ガスボイラ（６）
の発生蒸気は、全量蒸気タービン（７）に流入し、排ガ
スボイラ出口逆止弁（１１）が有るため排ガスボイラ
（５）のタービンバイパスライン（１７）には流入して
こない。At this time, the exhaust gas boiler (6) which continues operation
The entire amount of the generated steam flows into the steam turbine (7) and does not flow into the turbine bypass line (17) of the exhaust gas boiler (5) due to the exhaust gas boiler outlet check valve (11).
【００１７】ところが、この方法は蒸気圧力計測計器の
精度が要求される。通常は配管圧損が有るため、排ガス
ボイラ出口蒸気圧力（１９）が蒸気タービン入口蒸気圧
力（２５）よりも高いが、タービンバイパス弁（１５）
を開くことによって排ガスボイラ出口蒸気圧力（１９）
が低くなって最終的に圧力が逆転する。However, this method requires the accuracy of the vapor pressure measuring instrument. Normally, since there is a pipe pressure loss, the exhaust gas boiler outlet steam pressure (19) is higher than the steam turbine inlet steam pressure (25), but the turbine bypass valve (15)
Exhaust gas boiler outlet steam pressure by opening (19)
Eventually becomes lower and the pressure reverses.
【００１８】一方、蒸気タービン（７）への流入蒸気流
量が低下することにより、蒸気タービン入口蒸気圧力
（２５）も低下する。このため、図３に挙動を示すよう
に、圧力が逆転する時点（Ａ）を正確に捕らえるには、
微小な蒸気圧力差を検出する必要が有る。従来の圧力計
測計器を用いて、二点の正圧を計測してその差を検出す
る方法では、精度上正確さに欠ける。On the other hand, as the flow rate of steam flowing into the steam turbine (7) decreases, the steam turbine inlet steam pressure (25) also decreases. Therefore, as shown in the behavior in FIG. 3, in order to accurately capture the time (A) at which the pressure reverses,
It is necessary to detect minute vapor pressure differences. The conventional method for measuring positive pressure at two points and detecting the difference between them using a pressure measuring instrument lacks accuracy in terms of accuracy.
【００１９】これを改善するには、排ガスボイラ出口逆
止弁（１１，１２）の前後差圧を計測する方法、排ガス
ボイラ出口逆止弁（１１，１２）に全閉リミットスイッ
チを設置する方法などが考えられるが、いずれも計測点
を追加する必要が有り、また計測用計器の信頼性にも問
題が有る。In order to improve this, a method of measuring the differential pressure across the exhaust gas boiler outlet check valve (11, 12) and a method of installing a fully closed limit switch on the exhaust gas boiler outlet check valve (11, 12). However, in both cases, it is necessary to add measurement points, and there is also a problem with the reliability of measuring instruments.
【００２０】[0020]
【発明が解決しようとする課題】上記したように、従来
の技術は、多軸コンバインドプラントにおける、運転中
のガスタービンを停止する操作の過程において、停止す
る排ガスボイラ出口弁を全閉するタイミングを検出する
方法として、排ガスボイラ出口蒸気圧力が蒸気タービン
入口蒸気圧力より下がった事を捕らえようとしていた
が、この方法では、圧力差が非常に小さいことから、圧
力センサの精度上、適切に計測出来ていないという問題
点を有するものだった。As described above, according to the conventional technique, the timing of fully closing the exhaust gas boiler outlet valve to be stopped is set in the process of stopping the operating gas turbine in the multi-shaft combined plant. As a detection method, we were trying to catch that the steam pressure at the exhaust gas boiler outlet dropped below the steam pressure at the steam turbine inlet, but with this method, the pressure difference is extremely small, so it is possible to properly measure it in terms of the accuracy of the pressure sensor. It had the problem that it didn't.
【００２１】本発明は、プラントに新しいセンサを追加
することなく、排ガスボイラの発生蒸気がタービンバイ
パスラインに全て流れていることを検出できる点に着目
し、上記した従来技術の問題点を解消し、その上、プラ
ントの発電量に突変等の外乱を縮めることなく、また、
蒸気タービンに熱応力が発生するなどの原因で寿命を消
費することなく、運転するガスタービンの台数を変更す
ることができるようにした新規な方法を得ることを課題
とするものである。The present invention solves the above-mentioned problems of the prior art by paying attention to the fact that it is possible to detect that all the generated steam of the exhaust gas boiler is flowing in the turbine bypass line without adding a new sensor to the plant. Moreover, without reducing the disturbance such as sudden changes in the power generation of the plant,
An object of the present invention is to obtain a new method capable of changing the number of operating gas turbines without consuming the life of the steam turbine due to thermal stress or the like.
【００２２】[0022]
【課題を解決するための手段】上記した課題を解決する
べく、本発明は、複数のガスタービンを有する多軸コン
バインドプラントにおいて、排ガスボイラ出口蒸気圧力
とタービンバイパス弁開度からタービンバイパスライン
に流れる蒸気流量の計算値を計算して求め、実測して求
めた排ガスボイラ発生蒸気流量の実測値と上記計算値と
を比較し、同計算値と実測値が等しくなった時点で排ガ
スボイラ出口弁閉鎖指令を発生するようにした多軸コン
バインドプラントの蒸気系切離制御方法を提供するもの
である。In order to solve the above-mentioned problems, the present invention is a multi-shaft combined plant having a plurality of gas turbines, in which exhaust gas boiler outlet steam pressure and turbine bypass valve opening flow to a turbine bypass line. Calculate the calculated value of the steam flow rate, compare the measured value of the exhaust gas boiler generated steam flow rate obtained by actual measurement with the above calculated value, and close the exhaust gas boiler outlet valve when the calculated value and the measured value are equal It is intended to provide a steam system disconnection control method for a multi-axis combined plant that generates a command.
【００２３】[0023]
【作用】上記したように本発明では、複数のガスタービ
ンを有する多軸コンバインドプラントに於て、排ガスボ
イラの蒸気出口に備わっている圧力計等で計測した同排
ガスボイラ出口蒸気圧の値と、タービンバイパス弁に併
設されているタービンバイパス弁の開度計等で計測した
開度の値に基づいてタービンバイパスラインに流れる蒸
気流量の値を計算して求め、一方、排ガスボイラの蒸気
出口に備わっている蒸気の流量計等で実測した蒸気流量
の値を知り、この実測値と上記計算値とを比較器等で比
較し、その結果両方の値が等しくなった時点で排ガスボ
イラ出口弁の閉鎖指令を発生して、排ガスボイラ出口弁
を閉めるようにしたものである。As described above, in the present invention, in a multi-shaft combined plant having a plurality of gas turbines, a value of the exhaust gas boiler outlet steam pressure measured by a pressure gauge or the like provided at the steam outlet of the exhaust gas boiler, Calculated by calculating the value of the steam flow rate flowing to the turbine bypass line based on the opening value measured by the opening meter of the turbine bypass valve that is attached to the turbine bypass valve, and provided at the steam outlet of the exhaust gas boiler. Know the value of the steam flow rate actually measured by a steam flow meter, etc., compare this measured value with the above calculated value with a comparator, etc., and close the exhaust gas boiler outlet valve when both values become equal as a result A command is issued to close the exhaust gas boiler outlet valve.
【００２４】[0024]
【実施例】本発明の実施例を図１に基づいて説明する。
なおガスタービンと排ガスボイラと蒸気タービンとで構
成するコンバインドプラントとしての基本構造及びその
系統中に配置されたタービンバイパスライン、バイパス
弁、流量計、圧力計等々の諸機器は従来のものと何ら変
らないので、本実施例の説明に必要な場合には図２の記
載中からその機器名及び部品番号を適宜援用して以下説
明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to FIG.
The basic structure of a combined plant consisting of a gas turbine, an exhaust gas boiler, and a steam turbine, and the turbine bypass line, bypass valve, flow meter, pressure gauge, and other equipment arranged in the system are the same as the conventional ones. Therefore, if necessary for the description of the present embodiment, the device name and the part number will be used from the description of FIG.
【００２５】タービンバイパスライン（１７，１８）に
は、流量計は設置していないので、同タービンバイパス
ライン（１７，１８）に設けたタービンバイパス弁（１
５，１６）の弁開度を検知するＰＯＳ〔ポジショナー〕
（２３，２４）でその開き程度を知り、かつ、排ガスボ
イラ（５，６）の蒸気出口に設けた圧力計〔Ｐ〕（１
９，２０）でその圧力を知ってこの両者からタービンバ
イパス蒸気流量を計算して求める。Since no flow meter is installed in the turbine bypass line (17, 18), the turbine bypass valve (1) installed in the turbine bypass line (17, 18) is
POS (positioner) that detects the valve opening of 5 and 16)
(23, 24) knows the opening degree, and a pressure gauge [P] (1) provided at the steam outlet of the exhaust gas boiler (5, 6)
9 and 20), the pressure is known and the turbine bypass steam flow rate is calculated from both of them.
【００２６】すなわち、タービンバイパス弁は弁の前後
差圧が大きいため、弁を流れる蒸気流量は、弁の前圧と
弁開度に比例する特徴を有している。この特徴に従え
ば、 タービンバイパス蒸気流量＝Ｋ×タービンバイパス弁開
度×排ガスボイラ出口蒸気圧力。 にて計算できる。That is, since the turbine bypass valve has a large differential pressure across the valve, the steam flow rate through the valve is characterized by being proportional to the valve front pressure and the valve opening. According to this feature, turbine bypass steam flow rate = K × turbine bypass valve opening × exhaust gas boiler outlet steam pressure. Can be calculated at.
【００２７】ここに、Ｋはタービンバイパス弁固有のバ
ルブ定数である。また、タービンバイパス弁前蒸気圧力
は、排ガスボイラ出口蒸気圧力（１９，２０）に略々等
しいことを利用している。Here, K is a valve constant unique to the turbine bypass valve. Further, the fact that the steam pressure before the turbine bypass valve is substantially equal to the exhaust gas boiler outlet steam pressure (19, 20) is used.
【００２８】実際のプラント制御装置では、上記の式を
そのままプログラムすればよいが、最近では、制御用Ｐ
ＯＬ〔プログラム，オリエンティド，ランゲィジ〕にて
制御ロジックを表現することが広く用いられているの
で、図１で整理して示すように計測したタービンバイパ
ス弁開度と排ガスボイラ出口蒸気圧力を乗算器（３１）
にてかけ算し、バルブ定数Ｋ（３２）を乗算器（３３）
にてかけ算した結果がタービンバイパス蒸気流量とな
る。In an actual plant control device, the above equation may be programmed as it is, but recently, for control P
Since it is widely used to express the control logic in OL [program, oriented, language], as shown in FIG. 1, the turbine bypass valve opening and the exhaust steam outlet steam pressure are multiplied by a multiplier ( 31)
Multiply by and multiply the valve constant K (32) by the multiplier (33)
The result of multiplying by is the turbine bypass steam flow rate.
【００２９】この値と計測した排ガスボイラ発生蒸気流
量を比較器（３４）にて比較し、タービンバイパス蒸気
流量と排ガスボイラ発生蒸気流量が等しくなったタイミ
ングで排ガスボイラ出口弁に閉鎖指令を出力する。This value is compared with the measured exhaust gas boiler generated steam flow rate by a comparator (34), and a closing command is output to the exhaust gas boiler outlet valve at the timing when the turbine bypass steam flow rate and the exhaust gas boiler generated steam flow rate become equal. .
【００３０】これにより排ガスボイラ出口弁（９，１
０）は閉鎖されるが、この際同排ガスボイラ出口弁
（９，１０）の閉鎖に伴なうショックによる蒸気タービ
ンへの蒸気流入量の急変は起こらない。As a result, the exhaust gas boiler outlet valve (9, 1)
0) is closed, but at this time, a sudden change in the amount of steam flowing into the steam turbine due to a shock accompanying the closing of the exhaust gas boiler outlet valve (9, 10) does not occur.
【００３１】また、排ガスボイラ出口蒸気圧力および蒸
気タービン入口蒸気圧力に従来以上の計測精度を要求さ
れず、しかも、従来から取付けている計器の他に新たな
計器を設置する必要はない。Further, the exhaust gas boiler outlet steam pressure and the steam turbine inlet steam pressure are not required to have higher measurement accuracy than ever, and it is not necessary to install a new instrument in addition to the instrument that has been conventionally attached.
【００３２】なお、図２を援用して説明した都合上、タ
ービンバイパスライン（１７，１８）、タービンバイパ
ス弁（１５，１６）、排ガスボイラ出口弁（９，１０）
等々の様に、部品番号を並記して説明したが、二系列の
場合は一系列毎に、ｎ系列の場合は一系列又は選ばれた
ｍ系列が並行して制御されるものであり、その選択は運
転状況に応じて適宜行なわれるものであることは勿論で
ある。For convenience of explanation with reference to FIG. 2, turbine bypass lines (17, 18), turbine bypass valves (15, 16), exhaust gas boiler outlet valves (9, 10).
As described above, part numbers are described side by side, but in the case of two series, each series is controlled in parallel, and in the case of n series, one series or a selected m series is controlled in parallel. It goes without saying that the selection is made appropriately according to the driving situation.
【００３３】以上、本発明を図示の実施例について説明
したが、本発明はかかる実施例に限定されず、本発明の
範囲内でその具体的構造に種々の変更を加えてよいこと
はいうまでもない。Although the present invention has been described with reference to the illustrated embodiments, it is needless to say that the present invention is not limited to such embodiments and various modifications may be made to the specific structure within the scope of the present invention. Nor.
【００３４】[0034]
【発明の効果】以上、本発明によれば、排ガスボイラ発
生蒸気流量と計算されたタービンバイパス蒸気流量が等
しくなった時点で排ガスボイラ出口弁を閉めるので、排
ガスボイラ出口弁閉止のショックによる蒸気タービンへ
の蒸気流入量の急変は起こらない。As described above, according to the present invention, since the exhaust gas boiler outlet valve is closed when the exhaust gas boiler generated steam flow rate and the calculated turbine bypass steam flow rate become equal, the steam turbine due to the shock of closing the exhaust gas boiler outlet valve There is no sudden change in the amount of steam flowing into the.
【００３５】また、通常のプラントが普通に備えている
計器、機器を用いるだけで新たな計器等を何ら要求する
ことなく初期の効果を奏しうるものであり、経済上の利
点も大きいものである。Moreover, the initial effect can be obtained without using any new instrument or the like simply by using the instrument or device normally provided in the ordinary plant, and the economic advantage is great. .
【００３６】また、最近の多軸コンバインドプラント
は、従来よりさらに熱効率を上げるために、再熱式が採
用されているが、多軸再熱式コンバインドプラントで
は、ガスタービンの停止操作時点の排ガスボイラ出口弁
閉止タイミングが非再熱式プラント以上に正確であるこ
とを要求されることになる。したがって、このようなプ
ラントに本発明を採用することにより、プラント運用に
寄与する相乗的効果は大きいものとなる。Further, the recent multi-screw combined plant adopts a reheat type in order to further improve the thermal efficiency compared with the conventional one, but in the multi-screw reheat combined plant, the exhaust gas boiler at the time of the operation of stopping the gas turbine The outlet valve closing timing will be required to be more accurate than the non-reheat type plant. Therefore, by adopting the present invention in such a plant, the synergistic effect of contributing to plant operation becomes great.
【００３７】尚、上記は、運転中のガスタービンの台数
を減らす操作について説明しているが、蒸気タービンを
含めてプラント全体を停止する手順は、運転中のガスタ
ービンを順次停止していくので、本発明は、プラントを
停止する時にも有効である。Although the above describes the operation of reducing the number of operating gas turbines, the procedure for stopping the entire plant including the steam turbine is that the operating gas turbines are sequentially stopped. The present invention is also effective when shutting down the plant.
【図１】本発明の実施例に係わる制御ロジック図。FIG. 1 is a control logic diagram according to an embodiment of the present invention.
【図２】多軸コンバインドプラントの蒸気系統を含む構
成図。FIG. 2 is a configuration diagram including a steam system of a multi-shaft combined plant.
【図３】蒸気圧力の挙動を示す説明図。FIG. 3 is an explanatory diagram showing the behavior of steam pressure.
１，２ ガスタービン ５，６ 排ガスボイラ ９，１０ 排ガスボイラ出口弁 １５，１６ タービンバイパス弁 １７，１８ タービンバイパスライン １９，２０ 排ガスボイラ出口蒸気圧力計 ２１，２２ 排ガスボイラ発生蒸気流量計 ２３，２４ タービンバイパス弁開度計 ３０，３３ 乗算器 ３４ 比較器 1, 2 Gas turbine 5,6 Exhaust gas boiler 9,10 Exhaust gas boiler outlet valve 15,16 Turbine bypass valve 17,18 Turbine bypass line 19,20 Exhaust gas boiler outlet steam pressure gauge 21,22 Exhaust gas boiler generated steam flow meter 23,24 Turbine bypass valve opening meter 30, 33 Multiplier 34 Comparator
Claims (1)
インドプラントにおいて、排ガスボイラ出口蒸気圧力と
タービンバイパス弁開度からタービンバイパスラインに
流れる蒸気流量の計算値を計算して求め、実測して求め
た排ガスボイラ発生蒸気流量の実測値と上記計算値とを
比較し、同計算値と実測値が等しくなった時点で排ガス
ボイラ出口弁閉鎖指令を発生するようにしたことを特徴
とする多軸コンバインドプラントの蒸気系切離制御方
法。1. In a multi-shaft combined plant having a plurality of gas turbines, a calculated value of a steam flow rate flowing to a turbine bypass line is calculated from an exhaust gas boiler outlet steam pressure and a turbine bypass valve opening degree, and is actually measured. A multi-axis combined plant characterized by comparing the measured value of the exhaust gas boiler generated steam flow rate with the above calculated value and generating an exhaust gas boiler outlet valve closing command when the calculated value and the measured value become equal Steam system disconnection control method.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07153246A JP3073429B2 (en) | 1995-06-20 | 1995-06-20 | Steam system disconnection control method for multi-shaft combined plant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07153246A JP3073429B2 (en) | 1995-06-20 | 1995-06-20 | Steam system disconnection control method for multi-shaft combined plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH094416A true JPH094416A (en) | 1997-01-07 |
| JP3073429B2 JP3073429B2 (en) | 2000-08-07 |
Family
ID=15558263
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07153246A Expired - Lifetime JP3073429B2 (en) | 1995-06-20 | 1995-06-20 | Steam system disconnection control method for multi-shaft combined plant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3073429B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1304735C (en) * | 2000-07-21 | 2007-03-14 | 西门子公司 | Method for primary control in combined gas/steam turbine installation |
| EP2829691A1 (en) * | 2013-07-25 | 2015-01-28 | Siemens Aktiengesellschaft | Method for operating a combined power generation system |
| CN106761968A (en) * | 2017-02-16 | 2017-05-31 | 华电电力科学研究院 | Piping-main scheme back pressure turbine unit style shielding system and heat consumption rate method of testing |
-
1995
- 1995-06-20 JP JP07153246A patent/JP3073429B2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1304735C (en) * | 2000-07-21 | 2007-03-14 | 西门子公司 | Method for primary control in combined gas/steam turbine installation |
| EP2829691A1 (en) * | 2013-07-25 | 2015-01-28 | Siemens Aktiengesellschaft | Method for operating a combined power generation system |
| WO2015010870A3 (en) * | 2013-07-25 | 2015-03-26 | Siemens Aktiengesellschaft | Method for operating a combined cycle power plant |
| CN106761968A (en) * | 2017-02-16 | 2017-05-31 | 华电电力科学研究院 | Piping-main scheme back pressure turbine unit style shielding system and heat consumption rate method of testing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3073429B2 (en) | 2000-08-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7113890B2 (en) | Method and apparatus for detecting faults in steam generator system components and other continuous processes | |
| US7970557B2 (en) | Gas appliance judgment apparatus and method | |
| US20120240589A1 (en) | Power plant and power plant operating method | |
| US8113764B2 (en) | Steam turbine and a method of determining leakage within a steam turbine | |
| CN102680144B (en) | Method for measuring influence of steam leakage rates of middle separation shaft seal of turbine on unit heat consumption rate | |
| KR890013471A (en) | Flow Meter Control of Air Leak Monitor | |
| US6910364B2 (en) | Diagnosis method for detecting ageing symptoms in a steam turbine | |
| Brüggemann et al. | A new emergency stop and control valves design: Part 1—Experimental verification with scaled models | |
| JP3073429B2 (en) | Steam system disconnection control method for multi-shaft combined plant | |
| KR20170114943A (en) | Steam turbine plant | |
| JP5461970B2 (en) | Combined cycle power plant | |
| AU2020286165A1 (en) | Turbine monitoring system and turbine monitoring method | |
| Peet et al. | Development and application of a dynamic simulation model for a drum type boiler with turbine bypass system | |
| Tanuma et al. | A Study of Unsteady Aerodynamic Forces on Last Stage Blades in a Low-Pressure Model Steam Turbine at Very Low Operating Conditions | |
| JPH02236199A (en) | Diagnosing of process | |
| Głuch | Selected problems of determining an efficient operation standard in contemporary heat-and-flow diagnostics | |
| Pronk et al. | Compressor Surge and Positive-Slope Performance Modelling | |
| JPH0814012A (en) | Control equipment for complex plant | |
| Cafaro et al. | Performance monitoring of gas turbine components: a real case study using a micro gas turbine test rig | |
| Kearney et al. | Performance guarantee and testing of steam turbine retrofits | |
| KR101399487B1 (en) | system for monitoring high pressure turbine using smart sensor | |
| CN119198106A (en) | Method and system for quantitatively detecting blockage severity of exhaust system of heavy-duty gas turbine | |
| CN121598756A (en) | Method and device for evaluating outlet temperature of combustion chamber of gas turbine in real time and gas turbine | |
| CN117288398A (en) | Testing system and calculation method for steam leakage rate of intermediate shaft seal of medium and high pressure cylinders | |
| JPH05141266A (en) | Diagnostic device for trouble in fuel supply system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20000425 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090602 Year of fee payment: 9 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100602 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100602 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110602 Year of fee payment: 11 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110602 Year of fee payment: 11 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120602 Year of fee payment: 12 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130602 Year of fee payment: 13 |
|
| S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313111 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
| R370 | Written measure of declining of transfer procedure |
Free format text: JAPANESE INTERMEDIATE CODE: R370 |
|
| EXPY | Cancellation because of completion of term |