JPS58107805A - Control of turbine for combined cycle power generation - Google Patents
Control of turbine for combined cycle power generationInfo
- Publication number
- JPS58107805A JPS58107805A JP20752481A JP20752481A JPS58107805A JP S58107805 A JPS58107805 A JP S58107805A JP 20752481 A JP20752481 A JP 20752481A JP 20752481 A JP20752481 A JP 20752481A JP S58107805 A JPS58107805 A JP S58107805A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- steam
- temperature
- gas
- inlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/101—Regulating means specially adapted therefor
-
- 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]
Abstract
Description
【発明の詳細な説明】
発明の技術分野
本発明はコンバインドサイクル発電用タービンの制御装
置に関する。DETAILED DESCRIPTION OF THE INVENTION Technical Field of the Invention The present invention relates to a control device for a combined cycle power generation turbine.
発明の技術的背景
第１図にコンバインドサイクルによる発電システムを示
す。図示のものは一軸型コンバインドサイクルの一例で
あり、圧縮機２、ガスタービン５、発電機７、蒸気ター
ビン８が一軸に結合されている。捷ず、圧縮機入口可変
静翼１で流量制御された空気は、圧縮機２により高圧に
圧縮される。この圧縮空気は、燃料制御弁４によって流
量制御された燃料と混合され、燃料の燃焼により高温高
圧のガスが形成される。この高温高圧のガスはガスター
ビン５を駆動した後、排熱回収ボイラ６に入（２）
リ、後述するボイラ給水との間で熱交換した後、′
低温となって大気へ放出される。一方、排熱回収ボイ
ラ６に供給されるボイラ給水は、ガスタービン排気ガス
から熱を吸収して過熱蒸気となり、主蒸気止め弁９、蒸
気加減弁１０を通って蒸気タービン８に導かれ、蒸気タ
ービン８を駆動した後、復水器１１で凝縮して水になり
、復水ポンプ１２で再び排熱回収ボイラ６に供給される
。ガスタービン５および蒸気タービン８により駆動され
る発電機７は、ガスタービン５および蒸気タービン８の
出力の合計に相当する出力を発生する。Technical Background of the Invention Figure 1 shows a combined cycle power generation system. The illustrated one is an example of a single-shaft combined cycle, in which a compressor 2, a gas turbine 5, a generator 7, and a steam turbine 8 are connected to one shaft. The air whose flow rate is controlled by the compressor inlet variable stator blade 1 without being separated is compressed to high pressure by the compressor 2. This compressed air is mixed with fuel whose flow rate is controlled by the fuel control valve 4, and high-temperature, high-pressure gas is formed by combustion of the fuel. After driving the gas turbine 5, this high-temperature, high-pressure gas enters the exhaust heat recovery boiler 6 (2), and after exchanging heat with the boiler feed water (described later),
It cools down and is released into the atmosphere. On the other hand, the boiler feed water supplied to the exhaust heat recovery boiler 6 absorbs heat from the gas turbine exhaust gas and becomes superheated steam, which is led to the steam turbine 8 through the main steam stop valve 9 and the steam control valve 10, and is then led to the steam turbine 8, where it is introduced into steam. After driving the turbine 8, the water is condensed into water in the condenser 11, and is supplied to the exhaust heat recovery boiler 6 again by the condensate pump 12. The generator 7 driven by the gas turbine 5 and the steam turbine 8 generates an output corresponding to the sum of the outputs of the gas turbine 5 and the steam turbine 8.
このよう々コン′バイン′ドサイクル発電システムの系
統への併入後の通常運転時には、発電機の負荷が変動し
た場合、圧縮機の入口可変靜ｌＬ１の開度を変え、空気
ｔを燃料消費量に合うように調節することによって最適
の燃焼状態を得、ガスタービン排ガス温度が常に最も高
いある一定の温度になるように制御を行なっている。こ
れは排ガス温度が高いほど排熱回収ボイラ６での熱交換
の効率が良好となり、従ってプラント全体の熱効率が高
（３）
くなるからである−
次に、第２図を参照して、圧縮機入口可変静翼の従来の
制御方法を説明する。まずタービン起動時でタービン回
転数が最小回転数（定格回転数の約９０チ）以下の場合
は、圧縮機の圧力脈動を防止するため、設定信号発生器
１３は一定の値を持つ入口可変静翼開度信号り。８択し
て設定信号λとして出力する。一方フイードバック信号
発生器】５は実際の入口可静翼の開度ＬＸを選択してこ
れをフィードバック信号μとして出力する。設定信号λ
として与えられた入口可変静翼開度信号り。とフィード
バック信号μとして与えられた実際の入口可変静翼の開
度ＬＸとは比較器１６で比較され、両者の偏差信号δが
入口可変静翼のサーボモータ１４に送られる。サーボモ
ータ１４はこの偏差信号が零になると動きを停止する。In this way, during normal operation after the combined cycle power generation system is added to the system, if the load on the generator fluctuates, the opening of the variable inlet valve L1 of the compressor is changed to convert air t into fuel consumption. Optimum combustion conditions are obtained by adjusting the amount to match the amount, and control is performed so that the gas turbine exhaust gas temperature is always at the highest constant temperature. This is because the higher the exhaust gas temperature, the better the efficiency of heat exchange in the waste heat recovery boiler 6, and therefore the higher the thermal efficiency of the entire plant (3). A conventional control method for variable inlet stator vanes will be explained. First, when the turbine is started and the turbine rotation speed is below the minimum rotation speed (approximately 90 degrees of the rated rotation speed), the setting signal generator 13 is activated to prevent pressure pulsations in the compressor. Wing opening signal. 8 are selected and output as a setting signal λ. On the other hand, the feedback signal generator 5 selects the actual opening LX of the inlet movable vane and outputs it as a feedback signal μ. Setting signal λ
The inlet variable stator blade opening signal given as and the actual opening LX of the variable inlet stator vane given as the feedback signal μ are compared by a comparator 16, and a deviation signal δ between the two is sent to the servo motor 14 of the variable inlet stator vane. The servo motor 14 stops moving when this deviation signal becomes zero.
このようにして入口可変静翼の開度は一定値し。に保た
れる。この間は、ガスタービン排気ガス設定信号ｔ。と
実際のガスタービン排気ガス温度Ｔ。Ｘとの比較に基く
ガスタービンの排気ガス温度の制御は行なわれておらず
（４）
排気ガス温度はタービン回転数の上昇とともに上昇する
。In this way, the opening degree of the inlet variable stator vane is kept at a constant value. is maintained. During this time, the gas turbine exhaust gas setting signal t. and the actual gas turbine exhaust gas temperature T. The exhaust gas temperature of the gas turbine is not controlled based on comparison with X (4) The exhaust gas temperature increases as the turbine rotation speed increases.
タービン回転数が最小回転数に達し、ガスタービン排気
温度がある一定の値Ｔ０゜に達すると、設定信号発生器
１３は入口可変静翼開度設定信号り。の代りにガスター
ビン排気温度設定信号ＬＦ、。′（＋−選択してこれを
設定信号として出力する。一方、フィードバック信号発
生器１５は入口可変静翼開度信号ＬＸに代りにガスター
ビン排気温度ＴＥｘを選択し７てフィードバック信号μ
として出力する。この結果、設定信号λとして与えられ
た排気温度設定信号Ｔ。０とフィードバック信号μとし
て与えられた実際の排気温度ＴＥｘとの偏差信号δが入
口可変静翼のサーボモータ１４に送られ、サーボモータ
１４はこの偏差信号が零となる位置で停止する。このよ
うに、ガスタービン排気温度Ｔ。Ｘが設定値Ｔ。０と等
しくなるように入口可変静翼の開度が制御される。即ち
タービン回転数が最小回転数以上で・部分負荷の場合に
は、入口可変静翼はガスタービン排気温度を一定するよ
うに働いている。尚圧縮機の吐出圧力ｐｅａは入口可変
静翼の開度補正を行なうために使用されている。When the turbine rotational speed reaches the minimum rotational speed and the gas turbine exhaust temperature reaches a certain value T0°, the setting signal generator 13 generates an inlet variable stator blade opening setting signal. Gas turbine exhaust temperature setting signal LF, instead of . '(+-) and outputs it as a setting signal. On the other hand, the feedback signal generator 15 selects the gas turbine exhaust temperature TEx instead of the inlet variable stator blade opening signal LX, and outputs the feedback signal μ.
Output as . As a result, the exhaust temperature setting signal T is given as the setting signal λ. A deviation signal δ between 0 and the actual exhaust gas temperature TEx given as the feedback signal μ is sent to the servo motor 14 of the inlet variable stator vane, and the servo motor 14 stops at the position where this deviation signal becomes zero. Thus, the gas turbine exhaust temperature T. X is the set value T. The opening degree of the inlet variable stator vane is controlled to be equal to 0. That is, when the turbine rotational speed is higher than the minimum rotational speed and there is a partial load, the variable inlet stationary vanes work to keep the gas turbine exhaust temperature constant. Note that the discharge pressure pea of the compressor is used to correct the opening degree of the variable inlet stator vanes.
背景技術の問題点
以上のようにして圧縮機の入口可変静翼の開度調整によ
るガスタービン排気温度の制御がなされるが、蒸気ター
ビンのサイクルでは、通常運転時には主蒸気止め弁９お
よび蒸気加減弁１０が全開状態にあり、発電機の負荷変
動が生じたとき、排熱回収ボイラへの給水流量を発生蒸
気量とバランスする量に再調整１／、ドラム水位を一定
に制御するものの、タービンの入口蒸気圧力および温度
が直接制御されない。従って、排熱回収ボイラへの給水
量制御（又はドラム水位制御）の遅れあるいは異常によ
り蒸気タービン入口温度が過度に上昇した場合、効果的
にタービン入口蒸気温度を下げることができず、蒸気タ
ービンを危険立状態に到らせるおそれがあった。Problems with the Background Art As described above, the gas turbine exhaust temperature is controlled by adjusting the opening of the variable inlet stator vanes of the compressor, but in the steam turbine cycle, during normal operation, the main steam stop valve 9 and the steam control When the valve 10 is fully open and the generator load fluctuates, the water flow rate to the waste heat recovery boiler is readjusted to an amount that balances the amount of steam generated. The inlet steam pressure and temperature are not directly controlled. Therefore, if the steam turbine inlet temperature rises excessively due to a delay or abnormality in water supply control (or drum water level control) to the waste heat recovery boiler, the turbine inlet steam temperature cannot be effectively lowered, and the steam turbine There was a risk that this could lead to a dangerous situation.
発明の目的
本発明の目的は、蒸気タービンの入口蒸気温度を効果的
に制御することができるコンパインドサイクル発電プラ
ントの制御方法を提供することにある。OBJECTS OF THE INVENTION An object of the present invention is to provide a method for controlling a combined cycle power plant that can effectively control the inlet steam temperature of a steam turbine.
発明の概要
本発明の制御方法においては、圧縮機の入口可変静翼の
開度設定信号として、ガスタービンの排気ガス温度と蒸
気タービンの入口蒸気温度とに基いて定めたものを用い
ることにより、蒸気タービンの入口蒸気温度が急激に上
昇した場合あるいは異常に高くなった場合に圧縮機の入
口可変静翼の開ｆｅ上げることにより、上記温度の急激
な上昇等を抑制するようにしたものである。Summary of the Invention In the control method of the present invention, by using a signal determined based on the exhaust gas temperature of the gas turbine and the inlet steam temperature of the steam turbine as the opening degree setting signal of the variable inlet stator blade of the compressor, When the steam temperature at the inlet of the steam turbine suddenly rises or becomes abnormally high, the aperture of the compressor's inlet variable stator vanes is increased to suppress the sudden rise in temperature. .
発明の実施例
第３図は本発明に係る制御方法の実施に用いられる装置
を示したものである。同図において、蒸気タービン入口
蒸気温度Ｔ８は微分器２］で微分され、フィルター２２
を通される。蒸気タービン入口蒸気温度Ｔｓはまた演算
器Ｚ４に与えられ、危険獣ＴＨＥとの差に比例した信号
が出力としてフィルター２４を通される。フィルター２
２．２４はそれぞれ入力が負の場合、即ちＴｓの上昇率
がある値以下の（７）
場合＋ＴＳがＴＳＥ以Ｆの場合にはその出力信号を零と
する。フィルター２２．２４の出力は加算器部で加算さ
れる。加算器部の出力は修正信号ＴＭｏとして演ｊ４２
６に与えられる。演算器２６は、ガスタービン排気温度
設定値ＴＦ、ｏを修正信号ＴＭｏで修正して（例えばＫ
を定数とするとき、ＴＳｏ ” ＴＥｏ −ＫＴＭ。Embodiment of the Invention FIG. 3 shows an apparatus used to implement the control method according to the invention. In the same figure, the steam turbine inlet steam temperature T8 is differentiated by a differentiator 2], and a filter 22
will be passed through. The steam turbine inlet steam temperature Ts is also given to a calculator Z4, and a signal proportional to the difference from the dangerous animal THE is passed through a filter 24 as an output. filter 2
In 2.24, when the input is negative, that is, when the rate of increase of Ts is below a certain value (7), when +TS is less than TSE, the output signal is zero. The outputs of filters 22, 24 are summed in an adder section. The output of the adder section is operated as a correction signal TMo.
given to 6. The calculator 26 corrects the gas turbine exhaust temperature set value TF,o using a correction signal TMo (for example, K
When is a constant, TSo ” TEo −KTM.
なる演算を行なって）ＴＦ、。よりも小さい設定信号Ｔ
８ｏを発生する。設定信号ＴＳｏは、第２図の設定信号
発生器１３に、ＴＥｏの代りに与えられる。その結果、
ＴＥｏの代りにＴｓｏを用い、上記と同様に入口可変静
翼の開度調整が行なわれる。) TF. Setting signal T smaller than
Generates 8o. Setting signal TSo is provided to setting signal generator 13 in FIG. 2 instead of TEo. the result,
Using Tso instead of TEo, the opening degree of the inlet variable stator vane is adjusted in the same manner as above.
蒸気タービン入口蒸気温度Ｔ８の上昇率が所定値以下で
またＴｓが危険温度ＴＳＥ以下であれば、加算器部の出
力ＴＭｏは零であり、設定信号ＴＳｏ”Ｅ。If the rate of increase of the steam turbine inlet steam temperature T8 is below a predetermined value and Ts is below the critical temperature TSE, the output TMo of the adder section is zero, and the setting signal TSo''E.
と等しいものとなり、これが設定信号発生器１３に供給
され、上記した従来の場合と同様にして、ガスタービン
排気温度設定値咥。による入口可変静翼１４の開度が調
整される。蒸気タービン入口蒸気温度Ｔ８の上昇率が所
定値を超えると、これに応じた信号がフィルタｎを通り
加算器かに与えられる。This is supplied to the set signal generator 13 to determine the gas turbine exhaust temperature set point in the same manner as in the conventional case described above. The opening degree of the inlet variable stator blade 14 is adjusted. When the rate of increase in the steam turbine inlet steam temperature T8 exceeds a predetermined value, a corresponding signal is passed through a filter n and given to an adder.
（８）
ま７’ｃＴ８がＴＳＥよりも大きくなると、（Ｔｓ−Ｔ
ｓＥ）に比例した信号がフィルター２４ を通り加算器
５に与えられる。フィルター２２．２４の少くとも一方
から出力が加算器部に与えられると、加算器５から修正
信号Ｔ４ｏが発生され演算器２６に与えられる。(8) When 7'cT8 becomes larger than TSE, (Ts-T
A signal proportional to sE) passes through a filter 24 and is applied to an adder 5. When the output from at least one of the filters 22 and 24 is applied to the adder section, a correction signal T4o is generated from the adder 5 and is applied to the arithmetic unit 26.
この結果、演算器部はＴＥｏをＴｌｖｌｏに基いて修正
した値′ｆ、Ｔ８゜とじて出力する。この結果、修正信
号は入口可変静翼を開度を増加するように作用し、蒸気
タービン入口蒸気温度の温度を低下させ、または急激な
上昇を抑制する。As a result, the arithmetic unit outputs TEo as a modified value 'f, T8° based on Tlvlo. As a result, the correction signal acts to increase the opening degree of the inlet variable stator vane, thereby reducing the temperature of the steam turbine inlet steam temperature or suppressing a sudden rise in the temperature.
発明の効果
以上のように本発明によれば、従来直接制御されていな
かった蒸気タービンの入口蒸気温度を圧縮機の入口可変
静翼の開度調整により制御することがでへ、蒸気タービ
ン入口蒸気温度の制御性が良好になり、蒸気タービンを
異常な高温にさらすおそれがなくなり、安全性が向上す
る。Effects of the Invention As described above, according to the present invention, the steam temperature at the inlet of the steam turbine, which has not been directly controlled in the past, can be controlled by adjusting the opening of the variable stator vanes at the inlet of the compressor. Temperature control becomes better, there is no risk of exposing the steam turbine to abnormally high temperatures, and safety is improved.
第１図はコンバインドサイクル発電システムを示す系統
図、第２図は従来の制御方法の実施に用いられる装置を
示すブロック図、第３図は本発明に係る制御方法の実施
に用いられる装置の一部を示すブロック図である。
１・・・圧縮機入口可変静翼、２・・・圧縮機、３・・
・燃焼器、４・・・燃料制御弁、５・・・ガスタービン
、６・・・排熱回収ボイラ、７・・・発電機、８・・・
蒸気タービン、９・・・主蒸気止め弁、１０・・・蒸気
加減弁、１１・・・複水器、１２・・・復水ポンプ、１
３・・・設定信号発生器、１４・・・入口可変静翼サー
ボモータ、１５・・・フィードバック信号発生器、２１
・・・微分器、２２．２４・・・フィルター、２３゜２
６・・・演算器、２５・・・加算器。Fig. 1 is a system diagram showing a combined cycle power generation system, Fig. 2 is a block diagram showing equipment used to implement the conventional control method, and Fig. 3 is an example of equipment used to implement the control method according to the present invention. FIG. 1... Compressor inlet variable stator vane, 2... Compressor, 3...
- Combustor, 4... Fuel control valve, 5... Gas turbine, 6... Exhaust heat recovery boiler, 7... Generator, 8...
Steam turbine, 9... Main steam stop valve, 10... Steam control valve, 11... Double water device, 12... Condensate pump, 1
3... Setting signal generator, 14... Inlet variable stator vane servo motor, 15... Feedback signal generator, 21
...Differentiator, 22.24...Filter, 23゜2
6... Arithmetic unit, 25... Adder.
Claims (1)
とを混合して燃焼させ、燃焼ガスでガスタービンを駆動
するガスタービンサイクルと、ガスタービン排気でボイ
ラ給水を加熱して形成した蒸気で蒸気タービンを駆動す
る蒸気タービンサイクルとを備えたコンバインドサイク
ル発電用タービンの制御方法において、蒸気タービン入
口蒸気温度が急激に上昇したときまたは過度に高くなっ
たときに修正信号を発生し、該修正信号によりガスター
ビン排気温度の設定値を修正して形成された設定信号と
実際のガスタービン排気温度を示す信号との偏差が零に
なるように前記入口可変静翼の開度を調整することを特
徴とするコンバインドサイクル発電用タービンの制御方
法。 （１） リ１２
、前記修正信号による修正は、修正信号の増加に伴って
前記入口可変静翼の開度が増加するようになされること
を特徴とする特許請求の範囲第１項記載の制御方法。[Claims] 1. A gas turbine cycle in which air and fuel whose flow rate is controlled by variable inlet stator blades of a compressor are mixed and combusted, and the combustion gas drives a gas turbine, and the gas turbine exhaust gas is used to supply boiler water. In the control method for a combined cycle power generation turbine equipped with a steam turbine cycle in which the steam turbine is driven by the steam formed by heating the the variable inlet stator vane so that the deviation between the set signal generated by correcting the set value of the gas turbine exhaust temperature using the corrected signal and the signal indicating the actual gas turbine exhaust temperature becomes zero. A method for controlling a combined cycle power generation turbine, the method comprising adjusting the opening degree. (1) Ri12
2. The control method according to claim 1, wherein the correction by the correction signal is performed such that the opening degree of the inlet variable stator vane increases as the correction signal increases.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20752481A JPS58107805A (en) | 1981-12-22 | 1981-12-22 | Control of turbine for combined cycle power generation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20752481A JPS58107805A (en) | 1981-12-22 | 1981-12-22 | Control of turbine for combined cycle power generation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58107805A true JPS58107805A (en) | 1983-06-27 |
Family
ID=16541139
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20752481A Pending JPS58107805A (en) | 1981-12-22 | 1981-12-22 | Control of turbine for combined cycle power generation |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58107805A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63162907A (en) * | 1986-12-26 | 1988-07-06 | Hitachi Ltd | Control for combined power generation plant |
| JPS6466405A (en) * | 1987-09-07 | 1989-03-13 | Hitachi Ltd | Control method and controller of integrated electric power plant |
| JPH01117903A (en) * | 1987-08-24 | 1989-05-10 | Asea Brown Boveri Ag | Output regulator for combined gas-steam turbine-generating set |
| JPH01285608A (en) * | 1988-05-11 | 1989-11-16 | Hitachi Ltd | Method and device of operating combined plant |
-
1981
- 1981-12-22 JP JP20752481A patent/JPS58107805A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63162907A (en) * | 1986-12-26 | 1988-07-06 | Hitachi Ltd | Control for combined power generation plant |
| JPH01117903A (en) * | 1987-08-24 | 1989-05-10 | Asea Brown Boveri Ag | Output regulator for combined gas-steam turbine-generating set |
| JPS6466405A (en) * | 1987-09-07 | 1989-03-13 | Hitachi Ltd | Control method and controller of integrated electric power plant |
| JPH01285608A (en) * | 1988-05-11 | 1989-11-16 | Hitachi Ltd | Method and device of operating combined plant |
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