JPH0658104A - Multishaft combined cycle power plant - Google Patents

Multishaft combined cycle power plant

Info

Publication number
JPH0658104A
JPH0658104A JP21145992A JP21145992A JPH0658104A JP H0658104 A JPH0658104 A JP H0658104A JP 21145992 A JP21145992 A JP 21145992A JP 21145992 A JP21145992 A JP 21145992A JP H0658104 A JPH0658104 A JP H0658104A
Authority
JP
Japan
Prior art keywords
pressure
steam
valve
pipe
axis
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
Application number
JP21145992A
Other languages
Japanese (ja)
Other versions
JP3144440B2 (en
Inventor
Kosei Akiyama
孝生 秋山
Takeshi Kanamaru
剛 金丸
Masayuki Nagasawa
正幸 長澤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP21145992A priority Critical patent/JP3144440B2/en
Publication of JPH0658104A publication Critical patent/JPH0658104A/en
Application granted granted Critical
Publication of JP3144440B2 publication Critical patent/JP3144440B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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

  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

PURPOSE:To easily start and stop a multishaft combined cycle, change the number of operative ones of them, and deal with abnormality or accident by providing CV valves on pipes on the upstream side of common headers, and also providing a control means for controlling the opening and closing amount of the CV valves. CONSTITUTION:Valves 69 to 71 are respectively provided on pipes on the upstream side of common headers 51 to 53 so as to be controlled by steam generated on respective shafts individually. For example, even if failures or accidents are generated on A shaft, the other B and C shafts are so arranged as not to be affected by the failure or accident by shutting off the valve 69 of this shaft. A control means for controlling the shutoff of steam to be flow into steam turbines 7 to 9 of this shaft is provided in the parts for constituting steam shut-off valves. Pressure control from the time when the CV valves are full opened to the time when they are full closed can be performed by the control means. Thereby, pressure on the upstream side of the CV valves can be prevented from drastically varying from the set value. Therefore, starting, stopping, change the number of operative one of the cycles, and dealing with, abnormality and accident of a multishaft combined cycle can be easily performed.

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、多軸複合サイクル発電
プラントに係り、とくに、起動，停止，台数切替，異
常，事故の処理に好適な多軸複合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 multi-axis combined cycle power plant, and more particularly to a multi-axis combined cycle power plant suitable for starting, stopping, switching the number of units, abnormalities and accidents.

【０００２】[0002]

【従来の技術】従来、蒸気発生熱源が１基で、蒸気消費
が１台の蒸気タービンによって行なわれ、発電機によっ
て電気エネルギーに変換される発電設備としては、たと
えば、火力原子力発電誌５月号１９８４、Ｐ８５、複合
発電「コンバインドサイクルの概要」に記載されるよう
に、ガスタービンと、排熱回収ボイラと、蒸気タービン
および発電気からなる一軸型コンバインドサイクルが紹
介されている。2. Description of the Related Art Conventionally, as a power generation facility in which one steam generation heat source is used and steam consumption is performed by one steam turbine, and electric energy is converted by a generator, for example, the May issue of Thermal Power Nuclear Power Magazine 1984, P85, Combined Cycle Power Generation, "Outline of Combined Cycle", a single-shaft combined cycle consisting of a gas turbine, an exhaust heat recovery boiler, a steam turbine and electric power generation is introduced.

【０００３】これに対して、一層の高効率化と運用の平
易性を追求し、蒸気発生源であるガスタービンおよび排
熱回収ボイラを複数台設置した多軸型コンバインドサイ
クルがある。たとえば、特開昭５５−１１４８２１号公
報および特開昭５９−６８５０３号公報に記載されてい
るように、蒸気発生源が複数化した多軸型においても、
一軸型の延長線上の考えとして、各軸（以下、ガスター
ビンと、排熱回収ボイラの１組を“軸”という）で発生
した蒸気を共通連絡管（以下コモンヘッダという）で合
流させ、その総蒸気流量を制御するための圧力調整弁を
コモンヘッダの下流側に設けた構成となっている。各軸
からの発生蒸気を分離させる必要のある場合には、各排
熱回収ボイラからの蒸気をコモンヘッダに導く配管にボ
イラ止め弁を設置する形となっている。しかるに、上記
ボイラ止め弁は、蒸気を漏れさせることなく閉止する目
的で、通常な電気モータで駆動されるが、全閉するのに
１から２分程度の時間を要する。そこで、従来の構成で
は、起動，停止や通常の出力変更などのためにサーポ機
構と有する圧力調整弁（以下、ＣＶ弁という）と、ター
ビンの保護を目的とした蒸気遮断弁（以下、ＭＳＶ弁と
いう）および前記のボイラ止め弁（以下、ＢＳＶ弁とい
う）が設置されている。その１例を図７乃至図９により
説明する。なお、図７は従来の多軸コンバインドサイク
ルシステムを示す図。図８は従来の配管，弁の配列を示
す説明図。図９は高圧タービン内蒸気噴射断面図であ
る。図７に示すように、各軸には、ガスタービン２に燃
料３を供給し、燃焼時のエネルギーを発電機１で取り出
すとともに、高温の排ガスを、排熱回収ボイラ（以下、
ＨＲＳＧという）の入口４から煙突に接続された出口５
に導く。ＨＲＳＧ内部には、その入口４から出口５に向
かって、高圧過熱器１１，再熱加熱器１２，高圧蒸発器
１３，脱硝装置１４，再熱過熱器１５，低圧過熱器１
６，高圧節炭器１７，中圧蒸発器１８，中圧節炭器１
９，低圧蒸発器２０，低圧節炭器２１が配置されてい
る。また、上記低圧過熱器１６よりの過熱蒸気は、ＢＳ
Ｖ弁６０を有するパイプ３４を通ってＢＳＶ弁６０の下
流側に設けたコモンヘッダ５１に達したとき、他の軸系
のパイプ３４Ｂ，３４Ｃからの過熱蒸気と合流し、ＣＶ
弁６５を有するパイプ３５を通り、中圧タービン８に送
られ、中圧タービン８で仕事をした蒸気と合流して低圧
タービン９に供給される。上記パイプ３４のＢＳＶ弁６
０の上流側より分岐した一部の過熱蒸気は、バイパス弁
５５を有するバイパス管７２を通ってコモンヘッダに達
したとき、他の軸のバイパス管７２Ｂ，７２Ｃよりの過
熱蒸気と合流して復水器１０に供給される。上記再熱過
熱器１２よりの過熱蒸気は、ＢＳＶ弁６１を有するパイ
プ４２を通ってＢＳＶ弁６１の下流側に設けたコモンヘ
ッダ５２に達したとき、他の軸のパイプ４２Ｂ，４２Ｃ
よりの過熱蒸気と合流し、ＣＶ６６を有するパイプ４３
を通って中圧タービン８に供給される。上記パイプ４２
のＢＳＶ弁６１の上流側より分岐した一部の過熱蒸気
は、バイパス弁５４を有するバイパス管７３を通ってコ
モンヘッダに達したとき、他の軸のバイパス管７３Ｂ，
７３Ｃよりの過熱蒸気と合流して復水器１０に供給され
る。上記高圧蒸発器１１よりの蒸気はＢＳＶ弁６２を有
するパイプ４７を通ってコモンヘッダ５３に達したと
き、他の軸のパイプ４７Ｂ，４７Ｃよりの蒸気と合流
し、蒸気遮断弁（以下ＭＳＶ弁という）６８およびＣＶ
弁６７を有するパイプ４８を通って高圧タービン７に供
給される。上記パイプ４７のＢＳＶ弁６２の上流側より
分岐した一部の蒸気はバイパス弁５６と有するバイパス
管７４を通ってパイプ６４に供給される。該パイプ６４
は、一端部を上記高圧タービン７からの排気を排出する
排出管４９より分岐するパイプ５０に接続し、他端部を
上記再熱過熱器１２に接続するパイプ４１に接続してい
る。上記のようにして、高圧タービン７，中圧タービン
８および低圧タービン９に蒸気が供給されるが、通常は
パイプの配置上の問題やタービンの羽根への蒸気の噴射
形式すなわち、部分噴射であるか全周噴射であるかによ
って、あるいは制御弁や蒸気遮断弁の容量によって図８
に示すように、各パイプ３５，４３，４８は各タービン
７，８，９に入る直前で適切に分岐して各タービン７，
８，９に導かれる。図９は、図８の高圧タービン７につ
いてタービンケーシング１００をロータケーシング１０
１の周方向に４分割して蒸気の流入路１０２，１０６を
形成した場合である。大型タービンでは、高効率化のた
め、低出力時には、上記４本の流路１０２のうち１部の
みを使用するか、あるいは部分噴射であるが、本発明の
対象とするのは、この個々の流路の流量を独立に制御す
る必要のない全周噴射形のタービンであり、従来のコン
バインドサイクルでは、殆ど全てが全周噴射形である。
上記低圧タービン９で仕事をした低圧，低温の蒸気が復
水器１０に送られると、復水器１０で、蒸気が海水など
の冷却水で冷却され、液化される。液化した復水は、復
水ポンプ２５によりパイプ２９を通って各軸のパイプ３
０，３０Ｂ，３０Ｃに分岐される。分岐され復水パイプ
３０を通る復水は、低圧節炭器２１に供給される。低圧
節炭器２１では復水を加熱し、その一部をポンプ２６に
よりパイプ３６および調整弁６３を通って再び低圧節炭
器２１に再循環させ、これによって上記低圧節炭器２１
の入口温度を制御する。上記低圧節炭器２１よりの残り
の給水は、ドラム水位調整弁５７を有するパイプ３２を
通ってドラム２４に供給される。該ドラム２４は飽和水
を低圧蒸発器２０に送って復水を加熱気化し、発生した
飽和蒸気はパイプ３３を通って再熱過熱器１６に送り、
再熱過熱器１６でさらに過熱したのち、パイプ３４を通
って低圧タービン９に送られる。一方パイプ３６の循環
水の一部はポンプ２８により高圧節炭器１７に送られ、
前記低圧系の場合と同様にパイプ４５の調節弁５９を通
り高圧蒸発器１３のドラム２２に供給され、高圧過熱器
１１によって得られた蒸気をパイプ４７，４８を通って
高圧タービン７に導く。ところが、中圧タービン８への
蒸気は、再熱器１２からパイプ４２，４３を経て供給さ
れるが、上記再熱器１２にパイプ４１を通って流入する
蒸気はパイプ４０とパイプ６４の合流したものである。On the other hand, there is a multi-shaft combined cycle in which a plurality of gas turbines as a steam generation source and a plurality of exhaust heat recovery boilers are installed in pursuit of higher efficiency and ease of operation. For example, as described in JP-A-55-114821 and JP-A-59-68503, even in a multi-axis type in which a plurality of vapor sources are provided,
As an idea on the extension line of the single shaft type, steam generated in each shaft (hereinafter, one set of a gas turbine and an exhaust heat recovery boiler is referred to as a “shaft”) is joined by a common communication pipe (hereinafter referred to as a common header), and A pressure adjusting valve for controlling the total steam flow rate is provided on the downstream side of the common header. When it is necessary to separate the steam generated from each shaft, a boiler stop valve is installed in the pipe that guides the steam from each exhaust heat recovery boiler to the common header. However, the boiler stop valve is driven by an ordinary electric motor for the purpose of closing the steam stop without leaking steam, but it takes about 1 to 2 minutes to fully close the boiler stop valve. Therefore, in the conventional configuration, a pressure regulating valve (hereinafter, referred to as a CV valve) having a support mechanism for starting and stopping, a normal output change, and the like, and a steam shutoff valve (hereinafter, an MSV valve) for the purpose of protecting a turbine are provided. And a boiler stop valve (hereinafter referred to as a BSV valve). One example thereof will be described with reference to FIGS. FIG. 7 is a diagram showing a conventional multi-axis combined cycle system. FIG. 8 is an explanatory view showing a conventional arrangement of pipes and valves. FIG. 9 is a cross-sectional view of steam injection in the high-pressure turbine. As shown in FIG. 7, the fuel 3 is supplied to the gas turbine 2 and the energy at the time of combustion is taken out by the generator 1 to each shaft, and the high temperature exhaust gas is discharged to the exhaust heat recovery boiler (hereinafter,
HRSG) inlet 4 to outlet 5 connected to the chimney
Lead to. Inside the HRSG, from the inlet 4 to the outlet 5, a high pressure superheater 11, a reheat heater 12, a high pressure evaporator 13, a denitration device 14, a reheat superheater 15, a low pressure superheater 1
6, high-pressure economizer 17, medium-pressure evaporator 18, medium-pressure economizer 1
9, a low pressure evaporator 20 and a low pressure economizer 21 are arranged. The superheated steam from the low pressure superheater 16 is BS
When it reaches the common header 51 provided on the downstream side of the BSV valve 60 through the pipe 34 having the V valve 60, it merges with the superheated steam from the pipes 34B and 34C of the other shaft system, and the CV
It is sent to the intermediate-pressure turbine 8 through the pipe 35 having the valve 65, merges with the steam that has worked in the intermediate-pressure turbine 8, and is supplied to the low-pressure turbine 9. BSV valve 6 of the pipe 34
When a part of the superheated steam branched from the upstream side of 0 reaches the common header through the bypass pipe 72 having the bypass valve 55, it joins with the superheated steam from the bypass pipes 72B and 72C of the other shafts and returns. It is supplied to the water container 10. When the superheated steam from the reheat superheater 12 passes through the pipe 42 having the BSV valve 61 and reaches the common header 52 provided on the downstream side of the BSV valve 61, the pipes 42B and 42C of the other shafts.
Pipe 43 with CV66 that merges with superheated steam from
And is supplied to the intermediate pressure turbine 8. The pipe 42
When a part of the superheated steam branched from the upstream side of the BSV valve 61 reaches the common header through the bypass pipe 73 having the bypass valve 54, the other bypass pipes 73B,
The superheated steam from 73C is merged and supplied to the condenser 10. When the steam from the high-pressure evaporator 11 reaches the common header 53 through the pipe 47 having the BSV valve 62, it joins with the steam from the pipes 47B and 47C of the other shafts, and a steam shutoff valve (hereinafter referred to as MSV valve). ) 68 and CV
It is supplied to the high-pressure turbine 7 through a pipe 48 having a valve 67. A part of the steam branched from the upstream side of the BSV valve 62 of the pipe 47 is supplied to the pipe 64 through the bypass pipe 74 having the bypass valve 56. The pipe 64
Has one end connected to a pipe 50 branched from an exhaust pipe 49 for discharging exhaust gas from the high-pressure turbine 7, and the other end connected to a pipe 41 connected to the reheat superheater 12. Although steam is supplied to the high-pressure turbine 7, the intermediate-pressure turbine 8 and the low-pressure turbine 9 as described above, it is usually a problem in the arrangement of the pipes or the type of steam injection to the blades of the turbine, that is, partial injection. Fig. 8 depending on whether it is a full-circle injection or by the capacity of the control valve or steam cutoff valve.
As shown in, each pipe 35, 43, 48 is appropriately branched just before entering each turbine 7, 8, 9, and each turbine 7,
Guided to 8 and 9. FIG. 9 shows the turbine casing 100 of the high pressure turbine 7 of FIG.
This is a case where the steam inflow passages 102 and 106 are formed by dividing into four in the circumferential direction of 1. In a large turbine, in order to improve efficiency, only a part of the above four flow paths 102 is used or a partial injection is performed at the time of low output, but the subject of the present invention is this individual This is a full-circle injection type turbine that does not require independent control of the flow rate in the flow path, and in the conventional combined cycle, almost all are full-circle injection type turbines.
When the low-pressure, low-temperature steam that has worked in the low-pressure turbine 9 is sent to the condenser 10, the steam is cooled in the condenser 10 with cooling water such as seawater and liquefied. The liquefied condensate passes through the pipe 29 by the condensate pump 25 and the pipe 3 of each shaft.
It is branched into 0, 30B and 30C. Condensed water that has been branched and passed through the condensate pipe 30 is supplied to the low-pressure economizer 21. In the low-pressure economizer 21, the condensate is heated, and a part of the condensate is recycled by the pump 26 through the pipe 36 and the adjusting valve 63 to the low-pressure economizer 21.
Control the inlet temperature of the. The remaining water supply from the low pressure economizer 21 is supplied to the drum 24 through a pipe 32 having a drum water level adjusting valve 57. The drum 24 sends saturated water to the low-pressure evaporator 20 to heat and vaporize the condensate, and the generated saturated steam is sent to the reheat superheater 16 through the pipe 33.
After being further superheated by the reheat superheater 16, it is sent to the low-pressure turbine 9 through the pipe 34. On the other hand, a part of the circulating water in the pipe 36 is sent to the high pressure economizer 17 by the pump 28,
As in the case of the low pressure system, the steam that is supplied to the drum 22 of the high pressure evaporator 13 through the control valve 59 of the pipe 45 and is obtained by the high pressure superheater 11 is guided to the high pressure turbine 7 through the pipes 47 and 48. However, the steam to the intermediate pressure turbine 8 is supplied from the reheater 12 through the pipes 42 and 43, but the steam flowing into the reheater 12 through the pipe 41 merges with the pipe 40 and the pipe 64. It is a thing.

【０００４】従来の多軸コンバインドサイクルシステム
は、上記に述べたように構成されているので、低圧，中
圧，高圧のタービン７，８，９への蒸気の圧力を制御す
る場合には、それぞれ、コモンヘッダ５１，５２，５３
の下流側に配置したパイプ３５，４３，４８に有するＣ
Ｖ弁６５，６６，６７により行なっている。Since the conventional multi-shaft combined cycle system is constructed as described above, when controlling the pressure of steam to the low pressure, medium pressure and high pressure turbines 7, 8 and 9, respectively. , Common headers 51, 52, 53
C in pipes 35, 43, and 48 arranged on the downstream side of
It is performed by V valves 65, 66 and 67.

【０００５】また、各タービン７，８，９の異常や事故
が検知された場合および負荷が急激になくなった場合に
は、ＣＶ弁６７の上流側に設けたＭＳＶ弁６８にタービ
ン７，８，９への蒸気の供給を停止して該タービン７，
８，９の過速を防止している。なお、図７および図８に
示す中圧，低圧の調整弁６５，６６はＭＳＶ弁および制
御弁とを１体化した構成になっている。ただし、コンバ
インドサイクルは、基本的に高効率運転を行なうため
に、変圧運転の形態をとっており、１００％定常運転時
には、各ＣＶ弁６５，６６，６７は全開状態に保持さ
れ、圧力が大幅にある一定値まで減少したとき（通常は
定格圧力の２０％から５０％降下）、はじめて圧力を制
御するように設定されている。When an abnormality or an accident in each turbine 7, 8, 9 is detected or when the load suddenly disappears, the MSV valve 68 provided upstream of the CV valve 67 is connected to the turbine 7, 8, 9 to stop the steam supply to the turbine 7,
8 and 9 overspeed is prevented. The intermediate pressure and low pressure adjusting valves 65 and 66 shown in FIGS. 7 and 8 have a configuration in which the MSV valve and the control valve are integrated. However, the combined cycle basically takes the form of a variable pressure operation in order to perform a highly efficient operation, and at the time of 100% steady operation, each CV valve 65, 66, 67 is held in a fully opened state, and the pressure is significantly increased. When the pressure decreases to a certain value (normally, 20% to 50% of the rated pressure drops), the pressure is set to be controlled for the first time.

【０００６】[0006]

【発明が解決しようとする課題】上記従来技術では、
Ａ，Ｂ，Ｃの３軸あるガスタービンのうち、Ａ軸が何ら
かの原因でトリップすると、Ａ軸のボイラ止め弁により
熱源が断たれるため、Ａ軸の高圧，中圧，低圧の蒸気発
生量が急速に減速する。このとき、コモンヘッダは各軸
共連結しているので、Ｂ軸Ｃ軸が正常であってもその蒸
気発生量が急速に低下する。また、変圧運転用のＣＶ弁
６５，６６，６７の運用によっては、ガスタービン３台
のうち２台運転となる過程でも、ＣＶ弁６５，６６，６
７は全開のままである。このため、Ａ軸を切り離すため
にＡ軸のボイラ止め弁６０，６１，６２が閉じるが、通
常ボイラ止め弁６０，６１，６２はモータによって開閉
駆動され、全閉までに数分を要する。この間、コモンヘ
ッダ５１，５２，５３ではＡ軸の圧力降下にともなって
圧力降下を続け、さらに該コモンヘッダ５１，５２，５
３に接続するＢ軸，Ｃ軸に、パイプ３４Ｂ，３４Ｃ，４
２Ｂ，４２Ｃ，４７Ｂ，４８Ｂを通って伝播する。その
ため、Ｂ軸，Ｃ軸のＨＲＳＧは、Ａ軸がトリップしたこ
とにより大幅な状態の変化を受ける。とくに、図７に示
すように、ドラム２２，２３，２４を有する型式では、
圧力降下率が大きくなると、Ｂ軸，Ｃ軸のドラムの水位
が急変化するのにともない、場合によってはドラム水位
“高”あるいは“低”などのプラントトリップ信号を惹
起することもありうる。すなわち、多軸型コンバインド
サイクルの変圧運転時においては、数軸のうちの１軸が
異常，事故を発生すると、コモンヘッダを介して他の軸
への影響が発生する場合がある。In the above prior art,
Of the three-axis gas turbines of A, B, and C, if the A-axis trips for some reason, the heat source is cut off by the boiler stop valve of the A-axis, so high-pressure, medium-pressure, and low-pressure steam generation of the A-axis. Will slow down rapidly. At this time, since the common headers are connected to each other, the steam generation amount thereof rapidly decreases even if the B axis and the C axis are normal. Further, depending on the operation of the CV valves 65, 66, 67 for the variable pressure operation, the CV valves 65, 66, 6 may be operated even in the process of operating two of the three gas turbines.
No. 7 remains fully open. Therefore, the A-axis boiler stop valves 60, 61, 62 are closed in order to disconnect the A-axis, but usually the boiler stop valves 60, 61, 62 are driven to open and close by a motor, and it takes several minutes to be fully closed. During this time, the common headers 51, 52, 53 continue to drop in pressure with the pressure drop of the A-axis, and further, the common headers 51, 52, 5
Pipes 34B, 34C, 4 are connected to the B and C axes connected to
Propagate through 2B, 42C, 47B, 48B. Therefore, the B-axis and C-axis HRSGs undergo a large change in state due to the A-axis tripping. In particular, as shown in FIG. 7, in the type having the drums 22, 23, 24,
When the pressure drop rate becomes large, a plant trip signal such as “high” or “low” of the drum water level may be caused in some cases as the water levels of the B-axis and C-axis drums change rapidly. That is, during the voltage transforming operation of the multi-axis combined cycle, if one of the several axes is abnormal or an accident occurs, the other header may be affected via the common header.

【０００７】本発明の目的は、多軸複合サイクルの起
動，停止，台数切替，異常，事故時の処理を平易にし、
とくに１つの軸の影響が、他の軸に及ぼすのを最小にす
ることを可能とする多軸複合サイクル発電プラントを提
供することにある。An object of the present invention is to simplify the processes of starting, stopping, switching the number of units, abnormalities and accidents of a multi-axis combined cycle,
In particular, it is to provide a multi-shaft combined cycle power plant which makes it possible to minimize the influence of one shaft on the other.

【０００８】[0008]

【課題を解決するための手段】上記目的を達成するため
に、第１の発明は、それぞれ独立して蒸気発生源より発
生した少なくとも２個以上の蒸気を、コモンヘッダで合
流させ、少なくとも１台の蒸気タービンに導き、該蒸気
タービンおよび発電機を駆動させる多軸複合サイクル発
電プラントにおいて、前記蒸気タービンへの蒸気圧力を
調整するＣＶ弁を、前記コモンヘッダの上流側（前記蒸
気発生源側）配管に設けたものである。In order to achieve the above object, the first invention is that at least two or more steams independently generated from steam generators are merged by a common header, and at least one steam generator is merged. In the multi-shaft combined cycle power generation plant that guides the steam turbine and drives the steam turbine and the generator, a CV valve for adjusting the steam pressure to the steam turbine is provided on the upstream side of the common header (on the steam generation source side). It is provided on the pipe.

【０００９】上記目的を達成するために、第２の発明
は、それぞれ独立して蒸気発生源より発生した少なくと
も２個以上の蒸気を、コモンヘッダで合流させ、少なく
とも１台の蒸気タービンに導き、該蒸気タービンおよび
発電機を駆動させる多軸複合サイクル発電プラントにお
いて、前記蒸気タービンへの蒸気圧力を調整するＣＶ弁
を、前記コモンヘッダの上流側配管に設け、かつ前記コ
モンヘッダの上流側配管内の圧力が設定値と等しくなる
ように前記ＣＶ弁の開閉量を制御する制御手段を設けた
ものである。In order to achieve the above object, a second invention is that at least two or more steams independently generated from a steam generation source are merged by a common header, and are led to at least one steam turbine, In a multi-shaft combined cycle power plant that drives the steam turbine and a generator, a CV valve that adjusts the steam pressure to the steam turbine is provided in the upstream pipe of the common header, and in the upstream pipe of the common header. The control means for controlling the opening / closing amount of the CV valve is provided so that the pressure of 1 becomes equal to the set value.

【００１０】上記目的を達成するために、第３の発明
は、それぞれ独立して蒸気発生源より発生した少なくと
も２個以上の蒸気を、コモンヘッダで合流させ、少なく
とも１台の蒸気タービンに導き、該蒸気タービンおよび
発電機を駆動させる多軸複合サイクル発電プラントにお
いて、前記蒸気タービンへの蒸気圧力を調整するＣＶ弁
と、前記蒸気タービンへ流入する蒸気を遮断するＭＳＶ
弁のすべてもしくは一部のいずれか一方とを前記コモン
ヘッダの上流側配管に設けたものである。In order to achieve the above-mentioned object, a third invention is such that at least two or more steams independently generated from a steam generation source are merged by a common header and are led to at least one steam turbine, In a multi-shaft combined cycle power plant that drives the steam turbine and a generator, a CV valve that adjusts the steam pressure to the steam turbine and an MSV that shuts off the steam flowing into the steam turbine.
All or some of the valves are provided in the upstream pipe of the common header.

【００１１】上記目的を達成するために、第４の発明
は、それぞれ独立して蒸気発生源より発生した少なくと
も２個以上の蒸気を、コモンヘッダで合流させ、少なく
とも１台の蒸気タービンに導き、該蒸気タービンおよび
発電機を駆動させる多軸複合サイクル発電プラントにお
いて、前記蒸気タービンへの蒸気圧力を調整するＣＶ弁
と、前記蒸気発生源より発生した蒸気が前記コモンヘッ
ダ上流側配管への流れを停止する止め弁と、前記蒸気タ
ービンへ流入する蒸気を遮断するＭＳＶ弁のすべてもし
くは一部のいずれか一方とを前記コモンヘッダの上流側
配管に設けたものである。In order to achieve the above object, a fourth invention is that at least two or more steams independently generated from a steam generation source are merged at a common header and are led to at least one steam turbine. In a multi-shaft combined cycle power plant that drives the steam turbine and a generator, a CV valve that adjusts the steam pressure to the steam turbine and steam generated from the steam generation source flow to the common header upstream side pipe. A stop valve that stops and an MSV valve that shuts off the steam flowing into the steam turbine are provided in the upstream side pipe of the common header.

【００１２】上記目的を達成するために、第５の発明
は、それぞれ独立して蒸気発生源より発生した少なくと
も２個以上の蒸気を、コモンヘッダで合流させ、少なく
とも１台の蒸気タービンに導き、該蒸気タービンおよび
発電機を駆動させる多軸複合サイクル発電プラントにお
いて、前記蒸気タービンへの蒸気圧力を調整するＣＶ弁
と、前記蒸気発生源より発生した蒸気が前記コモンヘッ
ダ上流側配管への流れを停止する止め弁と、前記蒸気タ
ービンへ流入する蒸気を遮断するＭＳＶ弁のすべてもし
くは一部のいずれか一方とを前記コモンヘッダの上流側
配管に設け、かつ前記コモンヘッダの前記上流側配管内
の圧力が設定値と等しくなるように前記ＣＶ弁の開閉量
を制御する制御手段と、特定な軸で停止や事故が発生し
たとき、当該軸の止め弁を前記ＣＶ弁が閉じたのち、閉
じさせる制御手段と、特定な軸で停止や事故が発生した
とき、当該軸の蒸気遮断弁を閉じさせる制御手段を設け
たものである。In order to achieve the above object, a fifth aspect of the invention is that at least two or more steams independently generated from a steam generation source are merged at a common header and are led to at least one steam turbine, In a multi-shaft combined cycle power plant that drives the steam turbine and a generator, a CV valve that adjusts the steam pressure to the steam turbine and steam generated from the steam generation source flow to the common header upstream side pipe. A stop valve that stops and an MSV valve that shuts off the steam flowing into the steam turbine are provided in an upstream side pipe of the common header, and in the upstream side pipe of the common header. Control means for controlling the opening / closing amount of the CV valve so that the pressure becomes equal to the set value, and the stop of the shaft when a stop or an accident occurs in a specific shaft. After the valve is the CV valve closed, and control means to close, when the stop or an accident at a particular axis has occurred, it is provided with a control means to close the steam shut-off valve of the shaft.

【００１３】また、前記ＣＶ弁用制御手段は、前記コモ
ンヘッダ上流側にあられた台数を追加して起動する場
合、追加軸のコモンヘッダ上流側配置に設けられるとと
もに、圧力設定値を既に運転中の軸のコモンヘッダ上流
側配管のうち、最も小さい圧力にしたものである。Further, the CV valve control means is provided in the common header upstream side arrangement of the additional shaft when the additional number of the common header upstream side is to be started, and the pressure set value is already in operation. This is the one with the lowest pressure in the common header upstream piping of the shaft.

【００１４】また、前記ＣＶ弁用制御手段は、前記コモ
ンヘッダ内の圧力が所定以上の早さで下降あるいは上昇
する現象が発生したことを検知したとき、当該軸以外の
軸の前記ＣＶ弁を検知される直前のコモンヘッダ内の圧
力をもって前記ＣＶ弁の設定値にしたものである。Further, when the CV valve control means detects that a phenomenon in which the pressure in the common header drops or rises at a speed higher than a predetermined value occurs, the CV valve control means operates the CV valves of the other shafts. The pressure in the common header immediately before detection is set as the set value of the CV valve.

【００１５】また、前記ＣＶ弁用制御手段は、前記コモ
ンヘッダ内の前記現象が特定の軸に限定して発生したこ
とを検知したとき、当該軸以外の軸の前記ＣＶ弁の設定
値を、前記現象が収束したのち、変更するものである。Further, when the CV valve control means detects that the phenomenon in the common header is limited to a specific axis, the set values of the CV valves of axes other than the axis are changed to It is to be changed after the above phenomenon is resolved.

【００１６】[0016]

【作用】本発明は前記のように、各蒸気発生源毎にＣＶ
弁が設けられているので、ＣＶ弁が全開から全閉の間で
コモンヘッダの上流側配管内の圧力を制御しうる限りで
は、コモンヘッダの上流側配管内の圧力が制御手段によ
る設定値から大幅に変動することがない。したがって、
コモンヘッダの下流側配管で発生した圧力変動要因によ
って、蒸気発生源の状態たとえばガスタービンの出力変
化などで蒸気発生ドラムの水位などに影響を与えられる
のを減少することができる。コンバインドサイクルで
は、変圧運転すなわちＳＶ弁を全開状態に保持したま
ま、蒸気発生源からの蒸気を、そのときどきの圧力で丸
飲み込みする形でタービンを運転することが行なわれ
る。このような状態で、どれかの軸に事故が発生した場
合には、上記各軸のＣＶ弁のＣＶ弁用制御手段により圧
力制御をすれば、事故発生軸のコモンヘッダ上流側配管
内の圧力と、他の軸のコモンヘッダ上流側配管内の圧力
とを同時に、あるいは独立に望ましい形に制御すること
ができる。また、複数の軸を順次あるいは同時に起動し
たり、停止したりする場合、あるいは運転軸数を変更す
る過程でも、個々の軸の蒸気圧力を独立に、自由に変更
できることは、運用，制御の面でも平易でもあるし、従
来のようにバイパス弁を介して蒸気を復水器に送る量も
少なくすることができる。According to the present invention, as described above, the CV is different for each steam generation source.
Since the valve is provided, as long as the CV valve can control the pressure in the upstream pipe of the common header from the fully open to the fully closed state, the pressure in the upstream pipe of the common header is controlled by the control means. It does not change significantly. Therefore,
It is possible to reduce the influence of the state of the steam generation source, such as the output change of the gas turbine, on the water level of the steam generation drum due to the pressure fluctuation factor generated in the downstream side pipe of the common header. In the combined cycle, the turbine is operated in such a manner that the steam from the steam generation source is swallowed at a pressure at that time while the SV valve is kept fully open. If an accident occurs in any of the axes in such a state, the pressure in the common header upstream side pipe of the accident occurrence axis can be controlled by controlling the pressure by the CV valve control means of the CV valve of each axis. And the pressure in the common header upstream pipe of the other shaft can be controlled simultaneously or independently to a desired shape. Also, when starting or stopping multiple axes sequentially or simultaneously, or in the process of changing the number of operating axes, the steam pressure of each axis can be changed independently and freely. However, it is simple, and the amount of steam sent to the condenser via the bypass valve can be reduced as in the conventional case.

【００１７】[0017]

【実施例】つぎに、本発明の一実施例である多軸複合サ
イクル発電プラントシステムを示す図１乃至図４につい
て説明する。なお、図１が前記図７と異なるのは、図７
ではＣＶ弁６５，６６，７７およびＭＳＶ弁６８をコモ
ンヘッダ５１の下流側パイプ３５，４３，４８にそれぞ
れ設けているのに対して図１では、ＳＶ弁とＭＳＶ弁と
を一体化した弁６９，６９Ｂ，６９Ｃ，７０，７０Ａ，
７０Ｂ，７０Ｃ，７１，７１Ｂ，７１Ｃ，（６９Ｂ，６
９Ｃ，７０Ｂ，７０Ｃ，７１Ｂ，７１Ｃは図示せず）を
コモンヘッダ５１の上流側配管３４，３４Ｂ，３４Ｃ，
４２，４２Ｂ，４２Ｃ，４７，４７Ｂ，４７Ｃにそれぞ
れ設けている点であり、それ以外は同一であるので、同
一符号をもって示す。1 to 4 showing a multi-shaft combined cycle power generation plant system according to an embodiment of the present invention will be described. The difference between FIG. 1 and FIG. 7 is that FIG.
In contrast, the CV valves 65, 66, 77 and the MSV valve 68 are provided on the downstream pipes 35, 43, 48 of the common header 51, respectively, whereas in FIG. 1, the valve 69 in which the SV valve and the MSV valve are integrated. , 69B, 69C, 70, 70A,
70B, 70C, 71, 71B, 71C, (69B, 6
9C, 70B, 70C, 71B, 71C are not shown), and the upstream pipes 34, 34B, 34C of the common header 51,
42, 42B, 42C, 47, 47B, and 47C, respectively, and the other points are the same, and are therefore denoted by the same reference numerals.

【００１８】図１に示す実施例は、上記のように、コモ
ンヘッダ５１，５２，５３の上流側パイプ毎に弁６９，
６９Ｂ，６９Ｃ，７０，７０Ｂ，７０Ｃ，７１，７１
Ｂ，７１Ｃをそれぞれ設け、各軸の発生蒸気毎に制御す
る構成になっているので、たとえばＡ軸で故障や事故が
発生したとき、該軸の弁６９を遮断することにより、他
のＢ軸，Ｃ軸に影響しないようにしてる。なお、上記弁
６９，６９Ｂ，６９Ｃ，７０，７０Ｂ，７０Ｃ，７１，
７１Ｂ，７１Ｃには図示していないが、蒸気遮断弁を構
成する部分には、それぞれ当該軸の蒸気タービン７，
８，９へ流入する蒸気の遮断を制御する制御手段を設け
ている。つぎに、図２に示す低圧系Ａ軸の圧力調整弁の
制御手段の一実施例について説明する。同図に示すよう
にコモンヘッダ５１上流側で弁６９の上流側パイプ３４
の圧力を圧力センサ２００で検知し、該検知された圧力
信号を圧力設定部２０４および比較器２１４に送る。圧
力設定部２０４は、各軸の運転状態に応じて上記でパイ
プ３４内の圧力を設定するもので、その詳細については
図３で説明する。圧力設定部２０４からの圧力設定値Ｐ
ＬＳＥＴが圧力設定点２０１を介して、比較器２０４に
送られると、比較器２１４では、圧力センサ２００から
の検知圧力と、設定圧力とを比較し、両者の圧力差とを
ＰＩ制御部２０２に送る、ＰＩ制御器２０２では圧力差
に基づく弁６９の開閉量を演算して演算結果をアクチェ
ータ２０３を介して弁６９に指令してパイプ３４内の圧
力を設定値２０１と等しくなるように弁６９の開閉す
る。また、変圧運転時には、弁６９の全開指令は、圧力
設定点２０１の値ＰＬＳＥＴを圧力センサ２００による
測定値ＰＬＭＳよりも十分小さい値に設定値を変更する
ことによって構成される。すなわち、プラントの運転状
況に応じて圧力設定値２０１の値を適切に変更すること
によってすべての弁６９，６９Ｂ，６９Ｃ，７０，７０
Ｂ，７０Ｃ，７１，７１Ｂ，７１Ｃの開閉量を調整する
ことができる。そこで、本発明は、各軸毎に図３に示す
構成をした前記圧力設定部２０４を設けている。すなわ
ち、図３についてたとえばＡ軸のガスタービンがトリッ
プした場合を述べると、総括コントローラ３００からの
Ａ軸の運転状況情報２１０，他のＢ軸およびＣ軸の運転
状況情報２１１，蒸気タービン７，８，９などの共通部
分の運転状況情報２１２を入力してＡ軸のみガスタービ
ンがトリップしたことを認識する判定部２０８と、該判
定部２０８の指定により正常運転時閉路し、変圧運転時
開路するスイッチ２０５と、圧力センサ２００で測定さ
れた弁６９の上流側パイプ３４の圧力測定値ＰＬＭＳを
数秒遅れて出力する信号時間遅れ要素２１３と、該信号
時間遅れ要素２１３からの圧力値ＰＬｏＭＳを蓄えるア
ナログメモリ２０６と、正常運転時、判定部２０８から
の指令によりスイッチ部２０９を介してａ接点が接続
し、判定部２０８から圧力設定点２０１に設定圧力値Ｐ
ＬＳＥＴを送り、変圧運転時、判定部２０８からの指令
によりａ接点からｂ接点に切替られ、前記アナログメモ
リ２０６からガスタービン２がトリップする直前の測定
圧力ＰＬＭＳを圧力設定点２０１に送るスイッチ２０７
とから構成されている。前記総括コントローラ３００
は、各軸およびタービンまわりの運転状況に関する情報
を計算機（図示せず）に取り込むと、該計算機では、前
記の情報からプラント全体が「起動」，「停止」，「異
常」，「事故」のどの状態にあるかを算出し、該算出結
果に基づいて当該Ａ軸の運転状況情報２１０，他のＢ軸
およびＣ軸の運転状況情報２１１，蒸気タービン７，
８，９などの共通部分の運転状況情報２１２を前記判定
部２０８に送る。In the embodiment shown in FIG. 1, the valves 69, 69 are provided for the upstream pipes of the common headers 51, 52, 53 as described above.
69B, 69C, 70, 70B, 70C, 71, 71
B and 71C are respectively provided and controlled for each steam generated in each axis. Therefore, for example, when a failure or an accident occurs in the A axis, the valve 69 of the axis is shut off so that the other B axis can be prevented. , C axis is not affected. The valves 69, 69B, 69C, 70, 70B, 70C, 71,
Although not shown in 71B and 71C, the steam turbine 7 and
A control means for controlling the cutoff of the steam flowing into 8 and 9 is provided. Next, an embodiment of the control means of the pressure adjusting valve of the low pressure system A-axis shown in FIG. 2 will be described. As shown in the figure, the upstream side of the common header 51 and the upstream side pipe 34 of the valve 69.
Of the pressure is detected by the pressure sensor 200, and the detected pressure signal is sent to the pressure setting unit 204 and the comparator 214. The pressure setting unit 204 sets the pressure inside the pipe 34 according to the operating state of each shaft, and the details will be described with reference to FIG. Pressure setting value P from the pressure setting unit 204
When LSET is sent to the comparator 204 via the pressure set point 201, the comparator 214 compares the detected pressure from the pressure sensor 200 with the set pressure, and the pressure difference between the two is sent to the PI controller 202. In the PI controller 202, the opening / closing amount of the valve 69 is calculated based on the pressure difference, and the calculation result is instructed to the valve 69 via the actuator 203 so that the pressure in the pipe 34 becomes equal to the set value 201. Open and close. Further, during the variable pressure operation, the command to fully open the valve 69 is configured by changing the set value PLSET of the pressure set point 201 to a value sufficiently smaller than the measured value PLMS of the pressure sensor 200. That is, all the valves 69, 69B, 69C, 70, 70 are changed by appropriately changing the value of the pressure set value 201 according to the operating condition of the plant.
The opening / closing amount of B, 70C, 71, 71B, 71C can be adjusted. Therefore, in the present invention, the pressure setting unit 204 having the configuration shown in FIG. 3 is provided for each axis. That is, referring to FIG. 3, for example, when the A-axis gas turbine trips, the A-axis operating condition information 210 from the general controller 300, the other B-axis and C-axis operating condition information 211, and the steam turbines 7, 8 are described. , 9 and the like to input the operation status information 212 of the common part to recognize that the gas turbine has tripped only for the A-axis, and the normalization operation closes the circuit and the variable voltage operation opens the circuit by the specification of the judgment unit 208. A switch 205, a signal time delay element 213 that outputs the pressure measurement value PLMS of the upstream pipe 34 of the valve 69 measured by the pressure sensor 200 with a delay of several seconds, and an analog that stores the pressure value PLoMS from the signal time delay element 213. During normal operation, the memory 206 is connected to the a contact via the switch unit 209 according to a command from the determination unit 208, and the determination unit 2 Set pressure value P from 8 to a pressure set point 201
A switch 207 that sends LSET and switches the contact point a to the contact point b in response to a command from the determination unit 208 during the pressure change operation, and sends the measured pressure PLMS just before the gas turbine 2 trips from the analog memory 206 to the pressure set point 201.
It consists of and. The general controller 300
Imports information about the operating conditions around each axis and turbine into a computer (not shown), and the computer calculates from the above information that the entire plant is "start", "stop", "abnormal", "accident". Which state is calculated, and based on the calculation result, the operating status information 210 of the A-axis, the operating status information 211 of the other B-axis and C-axis, the steam turbine 7,
The operation status information 212 of common parts such as 8 and 9 is sent to the determination unit 208.

【００１９】つぎに動作について説明する。１００％定
格正常運転中は、総括コントローラ３００からの運転状
況情報２１０，２１１，２１２により判定部２０８が正
常運転状態であることを認識し、スイッチ２０５が閉じ
るとともに、スイッチ２０７がａ接点に接続する。その
ため、圧力センサ２００で測定した圧力測定値ＰＬＭＳ
は信号遅れ時間要素２１３およびスイッチ２０５を通る
アナログメモリ２０６に蓄えられる。同時に判定部２０
８からの圧力設定値ＰＬＳＥＴがスイッチ部２０９およ
びスイッチ２０７を通って圧力設定点２０１に送られ
る。このときの圧力設定点２０１の圧力設定値ＰＬＳＥ
Ｔは、圧力センサ２００で測定した圧力値ＰＬＭＳより
も小さいので、弁６９は全開になっている。また他のＢ
軸，Ｃ軸も同様に弁６９Ｂ，６９Ｃが全開になってい
る。しかるのち、１００％定格正常運転中に、Ａ軸のみ
ガスタービン２がトリップすると、判定部２０８が総括
コントローラ３００からの運転状況情報２１０，２１
１，２１２によりこれを認識するとともにスイッチ２０
５を開路にし、かつスイッチ２０７のａ接点からｂ接点
に切替えられる。そのため、アナログメモリ２０６でガ
スタービン２のトリップ直前に蓄えた圧力をスイッチ２
０７を介して圧力設定点２０１に送り、その圧力設定値
を正常運転中によりも大きい圧力値ＰＬｏＭＳに変更
し、以後Ａ軸のガスタービン２出力が減少するが、前記
の値を保持するので、弁６９は順次閉じていき、全閉後
は放熱により前記の値は小さくなる。また止め弁６０は
弁６９が全閉になってから閉じる。このとき、Ｂ軸，Ｃ
軸においても前記圧力設定点２０１の設定圧力の調整を
Ａ軸と同様な動作を行なうことにより、Ａ軸のガスター
ビン２のトリップ直前の圧力設定値を保持するよう弁６
９Ｂ，６９Ｃを部分的に閉じる。このため、タービンの
出力は減少するが、Ｂ軸およびＣ軸のＨＲＳＧの出力圧
力は、ほとんど変化せず、高圧，中圧，低圧の各ドラム
２２，２３，２４の水位も大幅に変更することがなく、
安定に運転を続けることができる。一般論として、事故
が発生すると、各種のは波及が周囲におよび２次的な事
故を引き起こす可能性がある。これを防止するには、事
故を可能な限り局部範囲に止め、プラントが制定してか
ら、残りの範囲を生かす処理が望ましい。タービンのト
リップの場合でも、事故が発生直後は、前記のように、
まずＢ軸，Ｃ軸の圧力を制定させ、その後本来の２軸運
転状態である変圧運転にゆっくりと移行するのが望まし
い。このためには、Ｂ軸，Ｃ軸の図７の判定部２０８に
対応する部分は、事故後のプラント状態が制定したこと
を判定するか、あるいはタイマ（図示せず）を設けて制
定に要する十分な所定時間経過後に、再びスイッチ２０
５およびスイッチ２０７に対応する部分を元の状態に復
帰させるとともに、圧力設定点を２軸定常運転時に、漸
次減少させることによりプラント状態が大きな変動をす
ることなく、移行できる。このときのＡ軸，Ｂ軸，Ｃ軸
の圧力設定点の変更の状況を図４に示す。なお、図のＡ
点はＡ軸のガスタービンがトリップを発生した時点，Ｂ
点は弁の全閉時点，Ｃ点は止め弁の全閉時点，Ｄ点はＡ
軸を切り離したのちの現象認識した時点，Ｅ点は正常運
転移行完了時点をそれぞれ示す。同図に示すように、Ａ
軸の圧力設定点は、事故発生直前のコモンヘッダ５１の
上流側パイプ内の圧力に保持される。これは、つぎの再
起動時のときには、自然放熱分しか温度が下がらず、急
速起動が可能となるため、都合が良い。またＢ軸，Ｃ軸
は、Ａ軸と同様、トリップ直後に急上昇し、しばらくそ
の値に保持されるが、プラントに大きな影響を及ぼさな
い範囲でゆっくりと設定点を下降させる過程でＣＶ弁を
全開にしてゆく、このように、特定の軸系で事故が発生
した場合に、他の軸に悪影響を及ぼさないように調整す
ることが可能である。運用の立場からも、特定な軸を切
り離す場合には、その軸のＣＶ弁を強制的に閉止してゆ
き、残りの軸は、前記のように切り離し直前の圧力をア
ナログメモリに蓄え、これを設定値として圧力制御視な
がら、影響を最小にすることが可能である。また軸を追
加する場合でも、既設に１００％軸出力で運転中のＡ軸
に、他のＢ軸を追加してコモンヘッダを介してタービン
に蒸気を供給するときには、Ａ軸の主蒸気の圧力をＢ軸
の圧力設定点とした上で、Ｂ軸ガスタービンを起動し、
順次昇圧してゆく、この過程でＢ軸の各バイパス弁の設
定点を主蒸気圧よりも、わずかに高く設定し、待機させ
ながら、バイパス蒸気流量を最小化して、昇圧完了後、
Ａ軸の蒸気流と自動的に合流させることにより燃料経済
性も向上する。プラントの起動操作の場合には、大別し
て同時起動と順次起動があるが、いずれの場合にも、各
軸特有の環境条件下で、最も好ましい圧力条件を作りな
がら起動する。すなわち、同時起動ならば共通の圧力設
定値を各軸の高圧，中圧，低圧のＣＶ弁６９，７０，７
１にそれぞれ与え、余剰蒸気をバイパス弁５４，５５，
５６で逃しながら、スムーズにタービン出力を上昇させ
る。順次起動ならば、最先行軸の高圧，中圧，低圧を後
続の軸の圧力設定目標値として取り込み、これに追従さ
せながら、バイパス弁５４，５５，５６で余剰蒸気を逃
がす。最先行軸の圧力設定値の変更は、あらかじめ設定
した計画値に基づいて制御する。いずれの場合も、ター
ビン７，８，９にとっては各軸のバラバラの動きが、コ
モンヘッダ５１，５２，５３に入る蒸気の圧力をほぼ一
定に制御していることで、また、タービン７，８，９を
含む外乱の影響は各軸で独立に圧力を制御することによ
り、お互いにスムーズな運転が可能となる。Next, the operation will be described. During the 100% rated normal operation, the determination unit 208 recognizes from the operation status information 210, 211, and 212 from the general controller 300 that the determination unit 208 is in the normal operation state, the switch 205 is closed, and the switch 207 is connected to the a contact. . Therefore, the pressure measurement value PLMS measured by the pressure sensor 200
Are stored in analog memory 206 through signal delay time element 213 and switch 205. At the same time, the determination unit 20
The pressure set value PLSET from 8 is sent to the pressure set point 201 through the switch section 209 and the switch 207. Pressure set value PLSE of pressure set point 201 at this time
Since T is smaller than the pressure value PLMS measured by the pressure sensor 200, the valve 69 is fully open. Another B
Similarly, the valves 69B and 69C of the shaft and C shaft are fully opened. Then, if the gas turbine 2 trips only for the A-axis during 100% rated normal operation, the determination unit 208 causes the operation status information 210, 21 from the general controller 300.
1 and 212 recognize this and the switch 20
5 is opened, and the a contact of the switch 207 is switched to the b contact. Therefore, the pressure stored in the analog memory 206 immediately before the trip of the gas turbine 2 is switched to the switch 2
07 to the pressure set point 201, change the pressure set value to a pressure value PLoMS that is larger than that during normal operation, and the output of the gas turbine 2 of the A-axis decreases thereafter, but since the value is maintained, The valve 69 is sequentially closed, and after fully closed, the above value becomes small due to heat radiation. The stop valve 60 is closed after the valve 69 is fully closed. At this time, B axis, C
Also in the shaft, by adjusting the set pressure at the pressure set point 201 by performing the same operation as in the A axis, the valve 6 is held so as to hold the pressure set value immediately before the trip of the gas turbine 2 of the A axis.
Partially close 9B and 69C. Therefore, the output of the turbine decreases, but the output pressure of the HRSG of the B and C axes hardly changes, and the water levels of the high-pressure, medium-pressure, and low-pressure drums 22, 23, 24 are also changed significantly. Without
You can continue driving stably. In general, when an accident occurs, various types of ripples can cause surrounding accidents and secondary accidents. To prevent this, it is desirable to limit the accident to the local area as much as possible, establish the plant, and then utilize the remaining area. Even in the case of a turbine trip, immediately after the accident, as described above,
First, it is desirable to establish the B-axis and C-axis pressures, and then slowly shift to the original two-axis operation state, which is the variable pressure operation. To this end, the portions of the B-axis and the C-axis corresponding to the determination unit 208 in FIG. 7 are required to determine whether the plant state after the accident has been established or to provide a timer (not shown) for establishment. After a sufficient predetermined time has elapsed, the switch 20 is turned on again.
5 and the portion corresponding to the switch 207 are returned to the original state, and the pressure set point is gradually reduced during the two-axis steady operation, so that the plant state can be shifted without making a large change. FIG. 4 shows how the pressure set points of the A-axis, B-axis and C-axis are changed at this time. In addition, A of the figure
The point is when the A-axis gas turbine trips, B
The point is when the valve is fully closed, the point C is when the stop valve is fully closed, and the point D is A.
Point E indicates the time point when the phenomenon is recognized after the axis is cut off, and the point when the normal operation transition is completed. As shown in the figure, A
The shaft pressure set point is maintained at the pressure in the upstream pipe of the common header 51 immediately before the accident. This is convenient because at the time of the next restart, only the natural heat radiation lowers the temperature, which enables quick start. Similarly to the A-axis, the B-axis and C-axis suddenly rise immediately after the trip and are held at that value for a while, but the CV valve is fully opened in the process of slowly lowering the set point within the range that does not significantly affect the plant. In this way, when an accident occurs in a specific axis system, it is possible to make adjustments so as not to adversely affect other axes. From the standpoint of operation, when disconnecting a specific axis, the CV valve of that axis is forcibly closed, and the remaining axes store the pressure immediately before disconnection in the analog memory as described above, and store it in the analog memory. The effect can be minimized while viewing the pressure control as a set value. Even when adding a shaft, when adding another B shaft to the A shaft that is already operating at 100% shaft output and supplying steam to the turbine via the common header, the pressure of the main steam of the A shaft And set the B-axis pressure set point to start the B-axis gas turbine,
The pressure is sequentially increased, and in this process, the set point of each bypass valve on the B shaft is set slightly higher than the main steam pressure, and while standing by, the bypass steam flow rate is minimized, and after the pressurization is completed,
Fuel economy is also improved by automatically combining with the A-axis steam flow. The start-up operation of the plant is roughly divided into simultaneous start-up and sequential start-up. In either case, the start-up operation is started while creating the most preferable pressure condition under the environmental condition peculiar to each axis. That is, for simultaneous startup, the common pressure set value is set to the high, medium, and low pressure CV valves 69, 70, 7 for each axis.
1 to the surplus steam and bypass valves 54, 55,
While increasing at 56, the turbine output is smoothly increased. In the case of sequential activation, the high pressure, the medium pressure, and the low pressure of the most preceding shaft are taken in as the pressure setting target values of the following shafts, and the bypass valves 54, 55, 56 are used to allow the excess steam to escape while following these. The change of the pressure set value of the most advanced axis is controlled based on a preset planned value. In either case, for the turbines 7, 8 and 9, the disparate movements of the respective axes control the pressure of the steam entering the common headers 51, 52 and 53 to be substantially constant. The influences of disturbances including 9 and 9 can be smoothly operated by controlling the pressure independently for each axis.

【００２０】本発明の他の一実施例を示す図５につい
て、説明する。同図に示す実施例では、ＣＶ弁６０，６
１，６２と、ＭＳＶ弁７４，７５，７６とを分離し、Ｍ
ＳＶ弁７５，７６，７７を従来技術と同様にコモンヘッ
ダ５１の下流側パイプ３５，４３，４８で、タービン
７，８，９入口の可能な限り近い位置に設置した場合で
ある。本実施例によれば、蒸気タービン７，８，９の負
荷喪失時にオーバスビードが発生するのを防止すること
ができる。Another embodiment of the present invention will be described with reference to FIG. In the embodiment shown in the figure, the CV valves 60, 6
1, 62 and MSV valves 74, 75, 76 are separated, and M
This is a case where the SV valves 75, 76 and 77 are installed at positions as close as possible to the turbines 7, 8 and 9 inlets by the downstream pipes 35, 43 and 48 of the common header 51 as in the conventional technique. According to the present embodiment, it is possible to prevent the over-beads from being generated when the load on the steam turbines 7, 8 and 9 is lost.

【００２１】本発明のさらに他の一実施例を示す図６に
ついて説明する。同図に示す実施例は、各軸のＨＲＳＧ
が大型化し、高圧，中圧，低圧のコモンヘッダ５１，５
２，５３の上流側パイプ４７，４２，３４，７１，４２
Ｂ，３４Ｂ，７１，４２Ｃ，３４Ｃの上流側がそれぞれ
複数のパイプにて接続しかつ蒸気タービン７，８，９が
複数台設置した場合である。この場合には、ＣＶ弁６
９，７０，７１は、それぞれコモンヘッダ５３の上流側
パイプ３４，４２，４７に設置するとともに、ＭＳＶ弁
６９を前記ＣＶ弁６９，７０，７１と切り離して、各タ
ービン７，８，９の入口近くに設置している。またコン
バインドサイクルは、各種の型式が考えられ、熱発生源
としてＬＮＧ以外にも石炭や石油、とくに石炭流動床を
用いた火炉とガスタービンを組み合わせたものなどが考
えられるが、基本的には、独立の蒸気発生源を複数個備
え、発生する蒸気をコモンヘッダで合流したのち、少な
くとも１台以上の全周噴射型の蒸気タービンに分流する
構成を有するものにおいては、本発明を適用できる。FIG. 6 showing still another embodiment of the present invention will be described. The embodiment shown in the figure shows the HRSG of each axis.
Has become larger, and high, medium and low pressure common headers 51, 5
2,53 upstream pipes 47, 42, 34, 71, 42
This is a case where the upstream sides of B, 34B, 71, 42C and 34C are connected by a plurality of pipes and a plurality of steam turbines 7, 8 and 9 are installed. In this case, the CV valve 6
9, 70, 71 are installed in the upstream pipes 34, 42, 47 of the common header 53, respectively, and the MSV valve 69 is separated from the CV valves 69, 70, 71, and the inlets of the turbines 7, 8, 9 are separated. It is installed nearby. In addition, various types of combined cycle are conceivable, and in addition to LNG as a heat generation source, coal and petroleum, in particular, a combination of a furnace using a coal fluidized bed and a gas turbine can be considered, but basically, The present invention can be applied to a configuration in which a plurality of independent steam generation sources are provided and the generated steam is merged at a common header and then split into at least one or more full-circle injection steam turbines.

【００２２】[0022]

【発明の効果】本発明は、以上説明したように構成され
ているように構成されているので、以下に記載するよう
な効果を奏する。Since the present invention is configured as described above, it has the following effects.

【００２３】第１の発明によれば、ＣＶ弁をコモンヘッ
ダの上流側各配管に設けたので、必要に応じて、複数の
蒸気発源からの蒸気をコモンヘッダに独立して流量制御
することができる。According to the first aspect of the invention, since the CV valve is provided in each pipe on the upstream side of the common header, the flow rate of steam from a plurality of steam sources can be controlled independently of the common header, if necessary. You can

【００２４】第２の発明によれば、ＣＶ弁をコモンヘッ
ダの上流側配管に設け、かつコモンヘッダの上流側配管
内の圧力を設定値と等しくなるようにＣＶ弁の開閉量を
制御する制御手段を設けたので、ＣＶ弁が全開から全閉
までの間の圧力制御を制御手段によって行なうことがで
き、これによってＣＶ弁の上流側圧力が設定値より大幅
に変動するのを防止し、蒸気発生源の状態、たとえば蒸
気発生ドラムの水位などに影響を受けるのを減少するこ
とができる。According to the second aspect of the invention, a control is provided in which the CV valve is provided in the upstream pipe of the common header and the opening / closing amount of the CV valve is controlled so that the pressure in the upstream pipe of the common header becomes equal to the set value. Since the means is provided, the control means can perform the pressure control from the full opening to the full closing of the CV valve, thereby preventing the pressure on the upstream side of the CV valve from fluctuating significantly from the set value. It is possible to reduce the influence of the state of the source, such as the water level of the steam generating drum.

【００２５】第３の発明によれば、ＣＶ弁とＭＳＶ弁の
すべてもしくは一部とをコモンヘッダの上流側配管に設
けたので、あらゆる状況において各軸を独立に制御する
ことができる。According to the third aspect of the invention, the CV valve and all or part of the MSV valve are provided in the upstream pipe of the common header, so that each axis can be controlled independently in all situations.

【００２６】第４の発明によれば、ＣＶ弁と止め弁とＭ
ＳＶ弁のすべてもしくは一部とをコモンヘッダの上流側
配管に設けたので、特定な軸が事故，故障を発生したと
き、他の軸に影響を与えるのを防止することができる。According to the fourth invention, the CV valve, the stop valve and the M
Since all or part of the SV valve is provided in the upstream pipe of the common header, when an accident or failure occurs in a specific shaft, it is possible to prevent the other shafts from being affected.

【００２７】第５の発明によれば、ＣＶ弁と止め弁とＭ
ＳＶ弁のすべてもしくは一部とをコモンヘッダの上流側
配管に設けるとともに各弁に制御手段を設けたので、特
定な軸の運転状態が、他の軸に影響を与えないようにし
て、とくに事故が波及しないようにすることができる。According to the fifth invention, the CV valve, the stop valve and the M
Since all or part of the SV valve is provided in the upstream pipe of the common header and the control means is provided for each valve, the operating state of a specific axis is prevented from affecting other axes, and a particular accident occurs. Can be prevented from spreading.

【００２８】第６の発明によれば、ＣＶ弁用制御手段
を、コモンヘッダ上流側にあらたに台数を追加して起動
する場合、追加軸のコモンヘッダ上流側配管に設けると
ともに、その圧力設定値を既に運転中のコモンヘッダの
上流側配管の最も小さい圧力に設定したので、燃料の経
済性を向上することができる。According to the sixth aspect of the invention, when the CV valve control means is newly activated at the upstream side of the common header to be activated, the control means is provided at the common header upstream side pipe of the additional shaft and its pressure set value is set. Is set to the smallest pressure in the upstream pipe of the common header that is already in operation, so that the fuel economy can be improved.

【００２９】第７の発明によれば、ＣＶ弁用制御手段
が、コモンヘッダ内の圧力が所定以上の早さで下降ある
いは上昇する現象を発生したことを検知したとき、検知
される直前の前記コモンヘッダ内の圧力をもって圧力調
整弁の設定圧力にしたので、さらに特定な軸のみに異
常，事故が他の軸に波及しないようにすることができ
る。According to the seventh aspect of the invention, when the control means for the CV valve detects that the pressure in the common header drops or rises at a speed higher than a predetermined speed, the control means immediately before being detected. Since the pressure in the common header is set to the set pressure of the pressure control valve, it is possible to prevent abnormalities and accidents from affecting only a specific axis and affecting other axes.

【００３０】第８の発明によれば、ＣＶ弁用制御手段
が、前記現象が特定の軸に限定して発生したことを検知
したとき、当該軸以外の軸の圧力設定値を、前記現象の
収束後変更するので、圧力設定値を状況に応じて調整す
ることができる。According to the eighth aspect of the invention, when the CV valve control means detects that the phenomenon occurs only in a specific axis, the pressure set value of the axis other than the axis is set to the one of the phenomenon. Since it is changed after convergence, the pressure set value can be adjusted according to the situation.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の一実施例を示す図。FIG. 1 is a diagram showing an embodiment of the present invention.

【図２】図１に示すＣＶ弁の制御手段を示す図。FIG. 2 is a diagram showing a control means of the CV valve shown in FIG.

【図３】図２に示す圧力設定部の構成回路図。FIG. 3 is a configuration circuit diagram of a pressure setting unit shown in FIG.

【図４】Ａ軸ガスタービントリップ時の圧力設定変更状
況図。FIG. 4 is a status diagram of a pressure setting change at the time of an A-axis gas turbine trip.

【図５】本発明の他の一実施例を示す図。FIG. 5 is a diagram showing another embodiment of the present invention.

【図６】本発明のさらに他の一実施例を示す図。FIG. 6 is a diagram showing still another embodiment of the present invention.

【図７】従来の多軸複合サイクル発電プラントを示す
図。FIG. 7 is a diagram showing a conventional multi-axis combined cycle power plant.

【図８】従来のパイプ，弁の配列を示す図。FIG. 8 is a view showing a conventional arrangement of pipes and valves.

【図９】従来の高圧タービン内蒸気の噴射断面図。FIG. 9 is a cross-sectional view of injection of steam in a conventional high-pressure turbine.

【符号の説明】[Explanation of symbols]

１…発電機，２…ガスタービン，３…燃料，４…ＨＲＳ
Ｇの入口，５…ＨＲＳＧの出口，６０，６１，６２…止
め弁，６９，７０，７１…ＣＶ弁，５１，５２，５３…
コモンヘッダ，７４，７５，７６…蒸気遮断弁，５５，
７２，７３…バイパス管，２００…圧力センサ，２０１
…圧力設定点，２０２…ＰＩ制御器，２０３…アクチュ
エータ，２０４…圧力設定部，２０５，２０７…スイッ
チ，２０６…アナログメモリ，２０８…判定部，２０９
…スイッチ部，２１０…自軸情報，２１１…他軸情報，
２１２…共通情報。1 ... Generator, 2 ... Gas turbine, 3 ... Fuel, 4 ... HRS
G inlet, 5 ... HRSG outlet, 60, 61, 62 ... Stop valve, 69, 70, 71 ... CV valve, 51, 52, 53 ...
Common header, 74, 75, 76 ... Steam cutoff valve, 55,
72, 73 ... Bypass pipe, 200 ... Pressure sensor, 201
... Pressure set point, 202 ... PI controller, 203 ... Actuator, 204 ... Pressure setting section, 205, 207 ... Switch, 206 ... Analog memory, 208 ... Judgment section, 209
... switch section, 210 ... own axis information, 211 ... other axis information,
212 ... Common information.

─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───

【手続補正書】[Procedure amendment]

【提出日】平成４年９月２５日[Submission date] September 25, 1992

【手続補正１】[Procedure Amendment 1]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】特許請求の範囲[Name of item to be amended] Claims

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【特許請求の範囲】[Claims]

【手続補正２】[Procedure Amendment 2]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】０００３[Name of item to be corrected] 0003

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【０００３】これに対して、一層の高効率化と運用の平
易性を追求し、蒸気発生源であるガスタービンおよび排
熱回収ボイラを複数台設置した多軸型コンバインドサイ
クルがある。たとえば、特開昭５５−１１４８２１号公
報および特開昭５９−６８５０３号公報に記載されてい
るように、蒸気発生源が複数化した多軸型においても、
一軸型の延長線上の考えとして、各軸（以下、ガスター
ビンと、排熱回収ボイラの１組を“軸”という）で発生
した蒸気を共通連絡管（以下コモンヘッダという）で合
流させ、その総蒸気流量を制御するための圧力調整弁を
コモンヘッダの下流側に設けた構成となっている。各軸
からの発生蒸気を分離させる必要のある場合には、各排
熱回収ボイラからの蒸気をコモンヘッダに導く配管にボ
イラ止め弁を設置する形となっている。しかるに、上記
ボイラ止め弁は、蒸気を漏れさせることなく閉止する目
的で、通常は電気モータで駆動されるが、全閉するのに
１から２分程度の時間を要する。そこで、従来の構成で
は、起動，停止や通常の出力変更などのためにサーボ機
構と有する圧力調整弁（以下、ＣＶ弁という）と、ター
ビンの保護を目的とした蒸気遮断弁（以下、ＭＳＶ弁と
いう）および前記のボイラ止め弁（以下、ＢＳＶ弁とい
う）が設置されている。その１例を図７乃至図９により
説明する。なお、図７は従来の多軸コンバインドサイク
ルシステムを示す図。図８は従来の配管，弁の配列を示
す説明図。図９は高圧タービン内蒸気噴射断面図であ
る。図７に示すように、各軸には、ガスタービン２に燃
料３を供給し、燃焼時のエネルギーを発電機１で取り出
すとともに、高温の排ガスを、排熱回収ボイラ（以下、
ＨＲＳＧという）の入口４から煙突に接続された出口５
に導く。ＨＲＳＧ内部には、その入口４から出口５に向
かって、高圧過熱器１１，再熱２次過熱器１２，高圧蒸
発器１３，脱硝装置１４，再熱１次過熱器１５，低圧過
熱器１６，高圧節炭器１７，中圧蒸発器１８，中圧節炭
器１９，低圧蒸発器２０，低圧節炭器２１が配置されて
いる。また、上記低圧過熱器１６よりの過熱蒸気は、Ｂ
ＳＶ弁６０を有するパイプ３４を通ってＢＳＶ弁６０の
下流側に設けたコモンヘッダ５１に達したとき、他の軸
系のパイプ３４Ｂ，３４Ｃからの過熱蒸気と合流し、Ｃ
Ｖ弁６５を有するパイプ３５を通り、中圧タービン８に
送られ、中圧タービン８で仕事をした蒸気と合流して低
圧タービン９に供給される。上記パイプ３４のＢＳＶ弁
６０の上流側より分岐した一部の過熱蒸気は、バイパス
弁５５を有するバイパス管７２を通ってコモンヘッダに
達したとき、他の軸のバイパス管７２Ｂ，７２Ｃよりの
過熱蒸気と合流して復水器１０に供給される。上記再熱
過熱器１２よりの過熱蒸気は、ＢＳＶ弁６１を有するパ
イプ４２を通ってＢＳＶ弁６１の下流側に設けたコモン
ヘッダ５２に達したとき、他の軸のパイプ４２Ｂ，４２
Ｃよりの過熱蒸気と合流し、ＣＶ６６を有するパイプ４
３を通って中圧タービン８に供給される。上記パイプ４
２のＢＳＶ弁６１の上流側より分岐した一部の過熱蒸気
は、バイパス弁５４を有するバイパス管７３を通ってコ
モンヘッダに達したとき、他の軸のバイパス管７３Ｂ，
７３Ｃよりの過熱蒸気と合流して復水器１０に供給され
る。上記高圧蒸発器１１よりの蒸気はＢＳＶ弁６２を有
するパイプ４７を通ってコモンヘッダ５３に達したと
き、他の軸のパイプ４７Ｂ，４７Ｃよりの蒸気と合流
し、蒸気遮断弁（以下ＭＳＶ弁という）６８およびＣＶ
弁６７を有するパイプ４８を通って高圧タービン７に供
給される。上記パイプ４７のＢＳＶ弁６２の上流側より
分岐した一部の蒸気はバイパス弁５６と有するバイパス
管７４を通ってパイプ６４に供給される。該パイプ６４
は、一端部を上記高圧タービン７からの排気を排出する
排出管４９より分岐するパイプ５０に接続し、他端部を
上記再熱過熱器１２に接続するパイプ４１に接続してい
る。上記のようにして、高圧タービン７，中圧タービン
８および低圧タービン９に蒸気が供給されるが、通常は
パイプの配置上の問題やタービンの羽根への蒸気の噴射
形式すなわち、部分噴射であるか全周噴射であるかによ
って、あるいは制御弁や蒸気遮断弁の容量によって図８
に示すように、各パイプ３５，４３，４８は各タービン
７，８，９に入る直前で適切に分岐して各タービン７，
８，９に導かれる。図９は、図８の高圧タービン７につ
いてタービンケーシング１００をロータケーシング１０
１の周方向に４分割して蒸気の流入路１０２，１０６を
形成した場合である。大型タービンでは、高効率化のた
め、低出力時には、上記４本の流路１０２のうち１部の
みを使用するか、あるいは部分噴射であるが、本発明の
対象とするのは、この個々の流路の流量を独立に制御す
る必要のない全周噴射形のタービンであり、従来のコン
バインドサイクルでは、殆ど全てが全周噴射形である。
上記低圧タービン９で仕事をした低圧，低温の蒸気が復
水器１０に送られると、復水器１０で、蒸気が海水など
の冷却水で冷却され、液化される。液化した復水は、復
水ポンプ２５によりパイプ２９を通って各軸のパイプ３
０，３０Ｂ，３０Ｃに分岐される。分岐され復水パイプ
３０を通る復水は、低圧節炭器２１に供給される。低圧
節炭器２１では復水を加熱し、その一部をポンプ２６に
よりパイプ３６および調整弁６３を通って再び低圧節炭
器２１に再循環させ、これによって上記低圧節炭器２１
の入口温度を制御する。上記低圧節炭器２１よりの残り
の給水は、ドラム水位調整弁５７を有するパイプ３２を
通ってドラム２４に供給される。該ドラム２４では飽和
水を低圧蒸発器２０に送って復水を加熱気化し、発生し
た飽和蒸気はパイプ３３を通って再熱過熱器１６に送
り、再熱過熱器１６でさらに過熱したのち、パイプ３４
を通って低圧タービン９に送られる。一方パイプ３６の
循環水の一部はポンプ２８により高圧節炭器１７に送ら
れ、前記低圧系の場合と同様にパイプ４５の調節弁５９
を通り高圧蒸発器１３のドラム２２に供給され、高圧過
熱器１１によって得られた蒸気はパイプ４７，４８を通
って高圧タービン７に導かれる。ところが、中圧タービ
ン８への蒸気は、再熱器１２からパイプ４２，４３を経
て供給されるが、上記再熱器１２にパイプ４１を通って
流入する蒸気はパイプ４０とパイプ６４の合流したもの
である。On the other hand, there is a multi-shaft combined cycle in which a plurality of gas turbines as a steam generation source and a plurality of exhaust heat recovery boilers are installed in pursuit of higher efficiency and ease of operation. For example, as described in JP-A-55-114821 and JP-A-59-68503, even in a multi-axis type in which a plurality of vapor sources are provided,
As an idea on the extension line of the single shaft type, steam generated in each shaft (hereinafter, one set of a gas turbine and an exhaust heat recovery boiler is referred to as a “shaft”) is joined by a common communication pipe (hereinafter referred to as a common header), and A pressure adjusting valve for controlling the total steam flow rate is provided on the downstream side of the common header. When it is necessary to separate the steam generated from each shaft, a boiler stop valve is installed in the pipe that guides the steam from each exhaust heat recovery boiler to the common header. However, the boiler stop valve for the purpose of closing without being leaked steam, typically is driven by an electric motor, it takes time from one to two minutes to fully closed. Therefore, in the conventional configuration, activation, pressure regulating valve having a servo motor <br/> structure, such as for stopping or normal output change (hereinafter, referred to as CV valve) and, vapor barrier for protection of turbine A valve (hereinafter, referred to as MSV valve) and the boiler stop valve (hereinafter, referred to as BSV valve) are installed. One example thereof will be described with reference to FIGS. FIG. 7 is a diagram showing a conventional multi-axis combined cycle system. FIG. 8 is an explanatory view showing a conventional arrangement of pipes and valves. FIG. 9 is a cross-sectional view of steam injection in the high-pressure turbine. As shown in FIG. 7, the fuel 3 is supplied to the gas turbine 2 and the energy at the time of combustion is taken out by the generator 1 to each shaft, and the high temperature exhaust gas is discharged to the exhaust heat recovery boiler (hereinafter,
HRSG) inlet 4 to outlet 5 connected to the chimney
Lead to. Inside the HRSG, from the inlet 4 toward the outlet 5, a high pressure superheater 11, a reheat secondary superheater 12, a high pressure evaporator 13, a denitration device 14, a reheat primary superheater 15, a low pressure superheater 16, A high-pressure economizer 17, an intermediate-pressure evaporator 18, an intermediate-pressure economizer 19, a low-pressure evaporator 20, and a low-pressure economizer 21 are arranged. The superheated steam from the low pressure superheater 16 is B
When it reaches the common header 51 provided on the downstream side of the BSV valve 60 through the pipe 34 having the SV valve 60, it joins with the superheated steam from the pipes 34B and 34C of the other shaft system, and C
It is sent to the intermediate pressure turbine 8 through the pipe 35 having the V valve 65, merges with the steam that has worked in the intermediate pressure turbine 8, and is supplied to the low pressure turbine 9. When part of the superheated steam branched from the upstream side of the BSV valve 60 of the pipe 34 reaches the common header through the bypass pipe 72 having the bypass valve 55, the superheated steam from the bypass pipes 72B and 72C of the other shafts. It joins with the steam and is supplied to the condenser 10. When the superheated steam from the reheat superheater 12 passes through the pipe 42 having the BSV valve 61 and reaches the common header 52 provided on the downstream side of the BSV valve 61, the pipes 42B, 42 of the other shafts.
Pipe 4 with CV66 that merges with superheated steam from C
It is supplied to the intermediate-pressure turbine 8 through 3. Above pipe 4
When a part of the superheated steam branched from the upstream side of the BSV valve 61 of No. 2 reaches the common header through the bypass pipe 73 having the bypass valve 54, the bypass pipes 73B of other shafts,
The superheated steam from 73C is merged and supplied to the condenser 10. When the steam from the high-pressure evaporator 11 reaches the common header 53 through the pipe 47 having the BSV valve 62, it joins with the steam from the pipes 47B and 47C of the other shafts, and a steam shutoff valve (hereinafter referred to as MSV valve). ) 68 and CV
It is supplied to the high-pressure turbine 7 through a pipe 48 having a valve 67. A part of the steam branched from the upstream side of the BSV valve 62 of the pipe 47 is supplied to the pipe 64 through the bypass pipe 74 having the bypass valve 56. The pipe 64
Has one end connected to a pipe 50 branched from an exhaust pipe 49 for discharging exhaust gas from the high-pressure turbine 7, and the other end connected to a pipe 41 connected to the reheat superheater 12. Although steam is supplied to the high-pressure turbine 7, the intermediate-pressure turbine 8 and the low-pressure turbine 9 as described above, it is usually a problem in the arrangement of the pipes or the type of steam injection to the blades of the turbine, that is, partial injection. Fig. 8 depending on whether it is a full-circle injection or by the capacity of the control valve or steam cutoff valve.
As shown in, each pipe 35, 43, 48 is appropriately branched just before entering each turbine 7, 8, 9, and each turbine 7,
Guided to 8 and 9. FIG. 9 shows the turbine casing 100 of the high pressure turbine 7 of FIG.
This is a case where the steam inflow passages 102 and 106 are formed by dividing into four in the circumferential direction of 1. In a large turbine, in order to improve efficiency, only a part of the above four flow paths 102 is used or a partial injection is performed at the time of low output, but the subject of the present invention is this individual This is a full-circle injection type turbine that does not require independent control of the flow rate in the flow path, and in the conventional combined cycle, almost all are full-circle injection type turbines.
When the low-pressure, low-temperature steam that has worked in the low-pressure turbine 9 is sent to the condenser 10, the steam is cooled in the condenser 10 with cooling water such as seawater and liquefied. The liquefied condensate passes through the pipe 29 by the condensate pump 25 and the pipe 3 of each shaft.
It is branched into 0, 30B and 30C. Condensed water that has been branched and passed through the condensate pipe 30 is supplied to the low-pressure economizer 21. In the low-pressure economizer 21, the condensate is heated, and a part of the condensate is recycled by the pump 26 through the pipe 36 and the adjusting valve 63 to the low-pressure economizer 21.
Control the inlet temperature of the. The remaining water supply from the low pressure economizer 21 is supplied to the drum 24 through a pipe 32 having a drum water level adjusting valve 57. In the drum 24 is heated vaporized condensate send saturated water to the low pressure evaporator 20, the generated saturated steam is sent to the reheat superheater 16 through the pipe 33, after further overheated by reheat superheater 16 , Pipe 34
Through the low pressure turbine 9. On the other hand, a part of the circulating water in the pipe 36 is sent to the high pressure economizer 17 by the pump 28, and the control valve 59 of the pipe 45 is used as in the case of the low pressure system.
The supplied to the drum 22 of the street pressure evaporator 13, steam obtained by the high-pressure superheater 11 wither electrically to the high-pressure turbine 7 through the pipe 47, 48. However, the steam to the intermediate pressure turbine 8 is supplied from the reheater 12 through the pipes 42 and 43, but the steam flowing into the reheater 12 through the pipe 41 merges with the pipe 40 and the pipe 64. It is a thing.

【手続補正３】[Procedure 3]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】０００６[Correction target item name] 0006

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【０００６】[0006]

【発明が解決しようとする課題】上記従来技術では、
Ａ，Ｂ，Ｃの３軸あるガスタービンのうち、Ａ軸が何ら
かの原因でトリップすると、Ａ軸のボイラ止め弁により
蒸気源が断たれるため、Ａ軸の高圧，中圧，低圧の蒸気
発生量が急速に減速する。このとき、コモンヘッダは各
軸共連結しているので、Ｂ軸Ｃ軸が正常であってもその
蒸気発生量が急速に低下する。また、変圧運転用のＣＶ
弁６５，６６，６７の運用によっては、ガスタービン３
台のうち２台運転となる過程でも、ＣＶ弁６５，６６，
６７は全開のままである。このため、Ａ軸を切り離すた
めにＡ軸のボイラ止め弁６０，６１，６２が閉じるが、
通常ボイラ止め弁６０，６１，６２はモータによって開
閉駆動され、全閉までに数分を要する。この間、コモン
ヘッダ５１，５２，５３ではＡ軸の圧力降下にともなっ
て圧力降下を続け、さらに該コモンヘッダ５１，５２，
５３に接続するＢ軸，Ｃ軸に、パイプ３４Ｂ，３４Ｃ，
４２Ｂ，４２Ｃ，４７Ｂ，４８Ｂを通って伝播する。そ
のため、Ｂ軸，Ｃ軸のＨＲＳＧは、Ａ軸がトリップした
ことにより大幅な状態の変化を受ける。とくに、図７に
示すように、ドラム２２，２３，２４を有する型式で
は、圧力降下率が大きくなると、Ｂ軸，Ｃ軸のドラムの
水位が急変化するのにともない、場合によってはドラム
水位“高”あるいは“低”などのプラントトリップ信号
を惹起することもありうる。すなわち、多軸型コンバイ
ンドサイクルの変圧運転時においては、数軸のうちの１
軸が異常，事故を発生すると、コモンヘッダを介して他
の軸への影響が発生する場合がある。In the above prior art,
Of the gas turbines with three axes A, B, and C, if the A axis trips for some reason, the boiler stop valve of the A axis will
Since the steam source is cut off, the amount of high-pressure, medium-pressure, and low-pressure steam generated on the A-axis is rapidly reduced. At this time, since the common headers are connected to each other, the steam generation amount thereof rapidly decreases even if the B axis and the C axis are normal. In addition, CV for transformer operation
Depending on the operation of the valves 65, 66, 67, the gas turbine 3
Even in the process of operating two of the units, the CV valves 65, 66,
67 remains fully open. For this reason, the A-axis boiler stop valves 60, 61, 62 are closed to disconnect the A-axis.
Normally, the boiler stop valves 60, 61, 62 are driven to open and close by a motor, and it takes several minutes to fully close. During this time, the common headers 51, 52, 53 continue to drop in pressure with the pressure drop of the A-axis, and the common headers 51, 52, 53
The B axis and C axis connected to 53 are connected to the pipes 34B, 34C,
Propagate through 42B, 42C, 47B, 48B. Therefore, the B-axis and C-axis HRSGs undergo a large change in state due to the A-axis tripping. In particular, as shown in FIG. 7, in the type having the drums 22, 23 and 24, when the pressure drop rate becomes large, the water levels of the B-axis and C-axis drums suddenly change. It can also cause plant trip signals such as "high" or "low". That is, in the variable pressure operation of the multi-axis combined cycle, one of several axes is used.
If an axis malfunctions or an accident occurs, it may affect other axes via the common header.

【手続補正４】[Procedure amendment 4]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】００１８[Correction target item name] 0018

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【００１８】図１に示す実施例は、上記のように、コモ
ンヘッダ５１，５２，５３の上流側パイプ毎に弁６９，
６９Ｂ，６９Ｃ，７０，７０Ｂ，７０Ｃ，７１，７１
Ｂ，７１Ｃをそれぞれ設け、各軸の発生蒸気毎に制御す
る構成になっているので、たとえばＡ軸で故障や事故が
発生したとき、該軸の弁６９を遮断することにより、他
のＢ軸，Ｃ軸に影響しないようにしてる。なお、上記弁
６９，６９Ｂ，６９Ｃ，７０，７０Ｂ，７０Ｃ，７１，
７１Ｂ，７１Ｃには図示していないが、蒸気遮断弁を構
成する部分には、それぞれ当該軸の蒸気タービン７，
８，９へ流入する蒸気の遮断を制御する制御手段を設け
ている。つぎに、図２に示す低圧系Ａ軸の圧力調整弁の
制御手段の一実施例について説明する。同図に示すよう
にコモンヘッダ５１上流側で弁６９の上流側パイプ３４
の圧力を圧力センサ２００で検知し、該検知された圧力
信号を圧力設定部２０４および比較器２１４に送る。圧
力設定部２０４は、各軸の運転状態に応じて上記でパイ
プ３４内の圧力を設定するもので、その詳細については
図３で説明する。圧力設定部２０４からの圧力設定値Ｐ
ＬＳＥＴが圧力設定点２０１を介して、比較器２０４に
送られると、比較器２１４では、圧力センサ２００から
の検知圧力と、設定圧力とを比較し、両者の圧力差とを
ＰＩ制御部２０２に送る、ＰＩ制御器２０２では圧力差
に基づく弁６９の開閉量を演算して演算結果をアクチェ
ータ２０３を介して弁６９に指令してパイプ３４内の圧
力を設定値２０１と等しくなるように弁６９の開閉す
る。また、変圧運転時には、弁６９の全開指令は、圧力
設定点２０１の値Ｐ SET L を圧力センサ２００による測定
値Ｐ MS L よりも十分小さい値に設定値を変更することに
よって構成される。すなわち、プラントの運転状況に応
じて圧力設定値２０１の値を適切に変更することによっ
てすべての弁６９，６９Ｂ，６９Ｃ，７０，７０Ｂ，７
０Ｃ，７１，７１Ｂ，７１Ｃの開閉量を調整することが
できる。そこで、本発明は、各軸毎に図３に示す構成を
した前記圧力設定部２０４を設けている。すなわち、図
３についてたとえばＡ軸のガスタービンがトリップした
場合を述べると、総括コントローラ３００からのＡ軸の
運転状況情報２１０，他のＢ軸およびＣ軸の運転状況情
報２１１，蒸気タービン７，８，９などの共通部分の運
転状況情報２１２を入力してＡ軸のみガスタービンがト
リップしたことを認識する判定部２０８と、該判定部２
０８の指定により正常運転時閉路し、変圧運転時開路す
るスイッチ２０５と、圧力センサ２００で測定された弁
６９の上流側パイプ３４の圧力測定値Ｐ MS L を数秒遅れ
て出力する信号時間遅れ要素２１３と、該信号時間遅れ
要素２１３からの圧力値Ｐ MS L0 を蓄えるアナログメモリ
２０６と、正常運転時、判定部２０８からの指令により
スイッチ部２０９を介してａ接点が接続し、判定部２０
８から圧力設定点２０１に設定圧力値Ｐ SET L を送り、変
圧運転時、判定部２０８からの指令によりａ接点からｂ
接点に切替られ、前記アナログメモリ２０６からガスタ
ービン２がトリップする直前の測定圧力Ｐ MS L を圧力設
定点２０１に送るスイッチ２０７とから構成されてい
る。前記総括コントローラ３００は、各軸およびタービ
ンまわりの運転状況に関する情報を計算機（図示せず）
に取り込むと、該計算機では、前記の情報からプラント
全体が「起動」，「停止」，「異常」，「事故」のどの
状態にあるかを算出し、該算出結果に基づいて当該Ａ軸
の運転状況情報２１０，他のＢ軸およびＣ軸の運転状況
情報２１１，蒸気タービン７，８，９などの共通部分の
運転状況情報２１２を前記判定部２０８に送る。In the embodiment shown in FIG. 1, the valves 69, 69 are provided for the upstream pipes of the common headers 51, 52, 53 as described above.
69B, 69C, 70, 70B, 70C, 71, 71
B and 71C are respectively provided and controlled for each steam generated in each axis. Therefore, for example, when a failure or an accident occurs in the A axis, the valve 69 of the axis is shut off so that the other B axis can be prevented. , C axis is not affected. The valves 69, 69B, 69C, 70, 70B, 70C, 71,
Although not shown in 71B and 71C, the steam turbine 7 and
A control means for controlling the cutoff of the steam flowing into 8 and 9 is provided. Next, an embodiment of the control means of the pressure adjusting valve of the low pressure system A-axis shown in FIG. 2 will be described. As shown in the figure, the upstream side of the common header 51 and the upstream side pipe 34 of the valve 69.
Of the pressure is detected by the pressure sensor 200, and the detected pressure signal is sent to the pressure setting unit 204 and the comparator 214. The pressure setting unit 204 sets the pressure inside the pipe 34 according to the operating state of each shaft, and the details will be described with reference to FIG. Pressure setting value P from the pressure setting unit 204
When LSET is sent to the comparator 204 via the pressure set point 201, the comparator 214 compares the detected pressure from the pressure sensor 200 with the set pressure, and the pressure difference between the two is sent to the PI controller 202. In the PI controller 202, the opening / closing amount of the valve 69 is calculated based on the pressure difference, and the calculation result is instructed to the valve 69 via the actuator 203 so that the pressure in the pipe 34 becomes equal to the set value 201. Open and close. Further, during the variable pressure operation, the command to fully open the valve 69 is configured by changing the value P SET L of the pressure set point 201 to a value sufficiently smaller than the value P MS L measured by the pressure sensor 200. That is, all the valves 69, 69B, 69C, 70, 70B, 7 are changed by appropriately changing the value of the pressure set value 201 according to the operating condition of the plant.
The opening / closing amount of 0C, 71, 71B, 71C can be adjusted. Therefore, in the present invention, the pressure setting unit 204 having the configuration shown in FIG. 3 is provided for each axis. That is, referring to FIG. 3, for example, when the A-axis gas turbine trips, the A-axis operating condition information 210 from the general controller 300, the other B-axis and C-axis operating condition information 211, and the steam turbines 7, 8 are described. , Determination unit 208 for recognizing that the gas turbine has tripped only for the A axis by inputting operation status information 212 of common portions such as 9 and 9;
A switch 205 that closes in normal operation and opens in variable pressure operation by specifying 08, and a signal time delay element that outputs the pressure measurement value P MS L of the upstream pipe 34 of the valve 69 measured by the pressure sensor 200 with a delay of several seconds. 213, the analog memory 206 for storing the pressure value P MS L0 from the signal time delay element 213, the a contact is connected via the switch unit 209 by a command from the determination unit 208 during normal operation, and the determination unit 20
The set pressure value P SET L is sent from 8 to the pressure set point 201, and during the transforming operation, from the a contact point to the b point by the command from the determination unit 208.
It is composed of a switch 207 which is switched to a contact point and sends the measured pressure P MS L just before the gas turbine 2 trips from the analog memory 206 to the pressure set point 201. The general controller 300 uses a computer (not shown) to obtain information about operating conditions around each shaft and turbine.
, The computer calculates from the above information whether the whole plant is in the “start”, “stop”, “abnormal” or “accident” state, and based on the calculation result, The operating condition information 210, the operating condition information 211 of the other B and C axes, and the operating condition information 212 of common parts such as the steam turbines 7, 8 and 9 are sent to the determination unit 208.

【手続補正５】[Procedure Amendment 5]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】００１９[Correction target item name] 0019

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【００１９】つぎに動作について説明する。１００％定
格正常運転中は、総括コントローラ３００からの運転状
況情報２１０，２１１，２１２により判定部２０８が正
常運転状態であることを認識し、スイッチ２０５が閉じ
るとともに、スイッチ２０７がａ接点に接続する。その
ため、圧力センサ２００で測定した圧力測定値Ｐ MS L は
信号遅れ時間要素２１３およびスイッチ２０５を通るア
ナログメモリ２０６に蓄えられる。同時に判定部２０８
からの圧力設定値Ｐ SET L がスイッチ部２０９およびスイ
ッチ２０７を通って圧力設定点２０１に送られる。この
ときの圧力設定点２０１の圧力設定値Ｐ SET L は、圧力セ
ンサ２００で測定した圧力値Ｐ MS L よりも小さいので、
弁６９は全開になっている。また他のＢ軸，Ｃ軸も同様
に弁６９Ｂ，６９Ｃが全開になっている。しかるのち、
１００％定格正常運転中に、Ａ軸のみガスタービン２が
トリップすると、判定部２０８が総括コントローラ３０
０からの運転状況情報２１０，２１１，２１２によりこ
れを認識するとともにスイッチ２０５を開路にし、かつ
スイッチ２０７のａ接点からｂ接点に切替えられる。そ
のため、アナログメモリ２０６でガスタービン２のトリ
ップ直前に蓄えた圧力をスイッチ２０７を介して圧力設
定点２０１に送り、その圧力設定値を正常運転中により
も大きい圧力値Ｐ MS L0 に変更し、以後Ａ軸のガスタービ
ン２出力が減少するが、前記の値を保持するので、弁６
９は順次閉じていき、全閉後は放熱により前記の値は小
さくなる。また止め弁６０は弁６９が全閉になってから
閉じる。このとき、Ｂ軸，Ｃ軸においても前記圧力設定
点２０１の設定圧力の調整をＡ軸と同様な動作を行なう
ことにより、Ａ軸のガスタービン２のトリップ直前の圧
力設定値を保持するよう弁６９Ｂ，６９Ｃを部分的に閉
じる。このため、タービンの出力は減少するが、Ｂ軸お
よびＣ軸のＨＲＳＧの出力圧力は、ほとんど変化せず、
高圧，中圧，低圧の各ドラム２２，２３，２４の水位も
大幅に変更することがなく、安定に運転を続けることが
できる。一般論として、事故が発生すると、各種のは波
及が周囲におよび２次的な事故を引き起こす可能性があ
る。これを防止するには、事故を可能な限り局部範囲に
止め、プラントが制定してから、残りの範囲を生かす処
理が望ましい。タービンのトリップの場合でも、事故が
発生直後は、前記のように、まずＢ軸，Ｃ軸の圧力を制
定させ、その後本来の２軸運転状態である変圧運転にゆ
っくりと移行するのが望ましい。このためには、Ｂ軸，
Ｃ軸の図７の判定部２０８に対応する部分は、事故後の
プラント状態が制定したことを判定するか、あるいはタ
イマ（図示せず）を設けて制定に要する十分な所定時間
経過後に、再びスイッチ２０５およびスイッチ２０７に
対応する部分を元の状態に復帰させるとともに、圧力設
定点を２軸定常運転時に、漸次減少させることによりプ
ラント状態が大きな変動をすることなく、移行できる。
このときのＡ軸，Ｂ軸，Ｃ軸の圧力設定点の変更の状況
を図４に示す。なお、図のＡ点はＡ軸のガスタービンが
トリップを発生した時点，Ｂ点は弁の全閉時点，Ｃ点は
止め弁の全閉時点，Ｄ点はＡ軸を切り離したのちの現象
認識した時点，Ｅ点は正常運転移行完了時点をそれぞれ
示す。同図に示すように、Ａ軸の圧力設定点は、事故発
生直前のコモンヘッダ５１の上流側パイプ内の圧力に保
持される。これは、つぎの再起動時のときには、自然放
熱分しか温度が下がらず、急速起動が可能となるため、
都合が良い。またＢ軸，Ｃ軸は、Ａ軸と同様、トリップ
直後に急上昇し、しばらくその値に保持されるが、プラ
ントに大きな影響を及ぼさない範囲でゆっくりと設定点
を下降させる過程でＣＶ弁を全開にしてゆく、このよう
に、特定の軸系で事故が発生した場合に、他の軸に悪影
響を及ぼさないように調整することが可能である。運用
の立場からも、特定な軸を切り離す場合には、その軸の
ＣＶ弁を強制的に閉止してゆき、残りの軸は、前記のよ
うに切り離し直前の圧力をアナログメモリに蓄え、これ
を設定値として圧力制御視ながら、影響を最小にするこ
とが可能である。また軸を追加する場合でも、既設に１
００％軸出力で運転中のＡ軸に、他のＢ軸を追加してコ
モンヘッダを介してタービンに蒸気を供給するときに
は、Ａ軸の主蒸気の圧力をＢ軸の圧力設定点とした上
で、Ｂ軸ガスタービンを起動し、順次昇圧してゆく、こ
の過程でＢ軸の各バイパス弁の設定点を主蒸気圧より
も、わずかに高く設定し、待機させながら、バイパス蒸
気流量を最小化して、昇圧完了後、Ａ軸の蒸気流と自動
的に合流させることにより燃料経済性も向上する。プラ
ントの起動操作の場合には、大別して同時起動と順次起
動があるが、いずれの場合にも、各軸特有の環境条件下
で、最も好ましい圧力条件を作りながら起動する。すな
わち、同時起動ならば共通の圧力設定値を各軸の高圧，
中圧，低圧のＣＶ弁６９，７０，７１にそれぞれ与え、
余剰蒸気をバイパス弁５４，５５，５６で逃しながら、
スムーズにタービン出力を上昇させる。順次起動なら
ば、最先行軸の高圧，中圧，低圧を後続の軸の圧力設定
目標値として取り込み、これに追従させながら、バイパ
ス弁５４，５５，５６で余剰蒸気を逃がす。最先行軸の
圧力設定値の変更は、あらかじめ設定した計画値に基づ
いて制御する。いずれの場合も、タービン７，８，９に
とっては各軸のバラバラの動きが、コモンヘッダ５１，
５２，５３に入る蒸気の圧力をほぼ一定に制御している
ことで、また、タービン７，８，９を含む外乱の影響は
各軸で独立に圧力を制御することにより、お互いにスム
ーズな運転が可能となる。Next, the operation will be described. During the 100% rated normal operation, the determination unit 208 recognizes from the operation status information 210, 211, and 212 from the general controller 300 that the determination unit 208 is in the normal operation state, the switch 205 is closed, and the switch 207 is connected to the a contact. . Therefore, the pressure measurement value P MS L measured by the pressure sensor 200 is stored in the analog memory 206 passing through the signal delay time element 213 and the switch 205. At the same time, the determination unit 208
The pressure set value P SET L from P is sent to the pressure set point 201 through the switch section 209 and the switch 207. Since the pressure set value P SET L at the pressure set point 201 at this time is smaller than the pressure value P MS L measured by the pressure sensor 200,
The valve 69 is fully open. Similarly, the valves 69B and 69C of the other B and C axes are fully opened. After a while,
If the gas turbine 2 trips only the A-axis during 100% rated normal operation, the determination unit 208 causes the general controller 30 to operate.
This is recognized from the operating status information 210, 211, and 212 from 0, the switch 205 is opened, and the a contact of the switch 207 is switched to the b contact. Therefore, the pressure stored in the analog memory 206 immediately before the trip of the gas turbine 2 is sent to the pressure set point 201 via the switch 207, and the pressure set value is changed to a pressure value P MS L0 larger than that during normal operation. Although the output of the A-axis gas turbine 2 decreases, since the above value is maintained, the valve 6
9 gradually closes, and after fully closed, the above value becomes smaller due to heat radiation. The stop valve 60 is closed after the valve 69 is fully closed. At this time, by adjusting the set pressure of the pressure set point 201 on the B-axis and the C-axis, the same operation as the A-axis is performed to hold the pressure set value immediately before the trip of the gas turbine 2 on the A-axis. 69B and 69C are partially closed. Therefore, the output of the turbine decreases, but the output pressure of the HRSG of the B axis and the C axis hardly changes,
The water level of each of the high-pressure, medium-pressure, and low-pressure drums 22, 23, 24 is not significantly changed, and stable operation can be continued. In general, when an accident occurs, various types of ripples can cause surrounding accidents and secondary accidents. To prevent this, it is desirable to limit the accident to the local area as much as possible, establish the plant, and then utilize the remaining area. Even in the case of a turbine trip, immediately after the accident, as described above, it is desirable to first establish the B-axis and C-axis pressures, and then slowly shift to the original biaxial operation state, which is the variable pressure operation. To do this, the B axis,
The portion of the C-axis corresponding to the determination unit 208 in FIG. 7 determines again that the plant state after the accident has been established, or a timer (not shown) is provided, and after a sufficient predetermined time required for the establishment has elapsed, the portion is restored again. By returning the parts corresponding to the switch 205 and the switch 207 to the original state and gradually decreasing the pressure set point during the two-axis steady operation, the plant state can be shifted without making a large change.
FIG. 4 shows how the pressure set points of the A-axis, B-axis and C-axis are changed at this time. In the figure, point A is the point when the A-axis gas turbine trips, point B is the point when the valve is fully closed, point C is the point when the stop valve is fully closed, and point D is the phenomenon recognition after the axis A is disconnected. The point E and the point E indicate the completion point of normal operation transition. As shown in the figure, the pressure set point of the A-axis is held at the pressure in the upstream pipe of the common header 51 immediately before the accident. This is because at the time of the next restart, the temperature drops only by natural heat dissipation, enabling quick start,
convenient. Similarly to the A-axis, the B-axis and C-axis suddenly rise immediately after the trip and are held at that value for a while, but the CV valve is fully opened in the process of slowly lowering the set point within the range that does not significantly affect the plant. In this way, when an accident occurs in a specific axis system, it is possible to make adjustments so as not to adversely affect other axes. From the standpoint of operation, when disconnecting a specific axis, the CV valve of that axis is forcibly closed, and the remaining axes store the pressure immediately before disconnection in the analog memory as described above, and store it in the analog memory. The effect can be minimized while viewing the pressure control as a set value. Moreover, even when adding an axis, 1
When adding another B-axis to the A-axis operating at 00% shaft output and supplying steam to the turbine via the common header, the main steam pressure of the A-axis is set as the B-axis pressure set point. Then, the B-axis gas turbine is started and the pressure is sequentially increased. In this process, the set point of each bypass valve of the B-axis is set slightly higher than the main steam pressure, and the bypass steam flow rate is minimized while waiting. After the pressurization is completed, the fuel economy is also improved by automatically joining the steam flow of the A-axis. The start-up operation of the plant is roughly divided into simultaneous start-up and sequential start-up. In either case, the start-up operation is started while creating the most preferable pressure condition under the environmental condition peculiar to each axis. That is, if they are started simultaneously, the common pressure setting value is
Apply to medium and low pressure CV valves 69, 70 and 71,
While escaping excess steam with the bypass valves 54, 55, 56,
Increases turbine output smoothly. In the case of sequential activation, the high pressure, the medium pressure, and the low pressure of the most preceding shaft are taken in as the pressure setting target values of the following shafts, and the bypass valves 54, 55, 56 are used to allow the excess steam to escape while following these. The change of the pressure set value of the most advanced axis is controlled based on a preset planned value. In any case, the disparate movements of the respective shafts for the turbines 7, 8 and 9 are caused by the common header 51,
By controlling the pressure of the steam entering 52, 53 to be almost constant, and by controlling the pressure independently on each axis, the influence of disturbances including the turbines 7, 8, 9 can be controlled smoothly. Is possible.

【手続補正６】[Procedure correction 6]

【補正対象書類名】明細書[Document name to be amended] Statement

【補正対象項目名】００２２[Name of item to be corrected] 0022

【補正方法】変更[Correction method] Change

【補正内容】[Correction content]

【００２２】[0022]

【発明の効果】本発明は、以上説明したように構成され
ているので、以下に記載するような効果を奏する。Since the present invention is constructed as described above, it has the following effects.

Claims (8)

【特許請求の範囲】[Claims] 【請求項１】 それぞれ独立して蒸気発生源より発生し
た少なくとも２個以上の蒸気を、共通連絡管で合流さ
せ、少なくとも１台の蒸気タービンに導き、前記蒸気タ
ービンおよび発電機を駆動させる多軸複合サイクル発電
プラントにおいて、前記蒸気タービンへの蒸気圧力を調
整する圧力調整弁を、前記共通連絡管の上流側配管に設
けた、ことを特徴とする多軸複合サイクル発電プラン
ト。1. A multi-spindle that independently combines at least two steams generated from a steam generation source by a common communication pipe and guides them to at least one steam turbine to drive the steam turbine and a generator. In the combined cycle power plant, a pressure adjusting valve for adjusting the steam pressure to the steam turbine is provided in an upstream pipe of the common communication pipe, the multi-shaft combined cycle power plant. 【請求項２】 それぞれ独立して蒸気発生源より発生し
た少なくとも２個以上の蒸気を、共通連絡管で合流さ
せ、少なくとも１台の蒸気タービンに導き、前記蒸気タ
ービンおよび発電機を駆動させる多軸複合サイクル発電
プラントにおいて、前記蒸気タービンへの蒸気圧力を調
整する圧力調整弁を、前記の上流側配管に設け、かつ前
記共通連絡管の上流側配管内の圧力が設定値と等しくな
るように前記蒸気圧力調整弁の開閉量を制御する制御手
段を設けたことを特徴とする多軸複合サイクル発電プラ
ント。2. A multi-spindle which independently combines at least two or more steams generated from a steam generation source by a common communication pipe and guides them to at least one steam turbine to drive the steam turbine and a generator. In the combined cycle power plant, a pressure adjusting valve for adjusting the steam pressure to the steam turbine is provided in the upstream side pipe, and the pressure in the upstream side pipe of the common communication pipe is equal to a set value. A multi-shaft combined cycle power plant, comprising control means for controlling the opening / closing amount of a steam pressure adjusting valve. 【請求項３】 それぞれ独立して蒸気発生源より発生し
た少なくとも２個以上の蒸気を、共通連絡管で合流さ
せ、少なくとも１台の蒸気タービンに導き、前記蒸気タ
ービンおよび発電機を駆動させる多軸複合サイクル発電
プラントにおいて、前記蒸気タービンへの蒸気圧力を調
整する圧力調整弁と、前記蒸気タービンへ流入する蒸気
を遮断する蒸気遮断弁のすべてもしくは一部のいずれか
一方とを前記共通連絡管の上流側配管に設けたことを特
徴とする多軸複合サイクル発電プラント。3. A multi-spindle which independently drives at least two steams generated from a steam generation source through a common communication pipe and leads to at least one steam turbine to drive the steam turbine and a generator. In a combined cycle power plant, a pressure regulating valve that regulates the steam pressure to the steam turbine and either or all of a part of the steam shutoff valve that shuts off the steam flowing into the steam turbine are connected to the common communication pipe. A multi-axis combined cycle power plant characterized by being provided in upstream piping. 【請求項４】 それぞれ独立して蒸気発生源より発生し
た少なくとも２個以上の蒸気を、共通連絡管で合流さ
せ、少なくとも１台の蒸気タービンに導き、前記蒸気タ
ービンおよび発電機を駆動させる多軸複合サイクル発電
プラントにおいて、前記蒸気タービンへの蒸気圧力を調
整する圧力調整弁と、前記蒸気発生源より発生した蒸気
が前記共通連絡管上流側配管への流れを停止するボイラ
止め弁と、前記蒸気タービンへ流入する蒸気を遮断する
蒸気遮断弁のすべてもしくは一部のいずれか一方とを前
記共通連絡管の上流側配管に設けたことを特徴とする多
軸複合サイクル発電プラント。4. A multi-spindle that independently drives at least two steams generated from a steam generation source by a common connecting pipe and leads to at least one steam turbine to drive the steam turbine and a generator. In a combined cycle power plant, a pressure adjusting valve that adjusts the steam pressure to the steam turbine, a steam stop valve that stops the flow of steam generated from the steam generation source to the common communication pipe upstream side pipe, and the steam A multi-shaft combined cycle power plant, characterized in that all or part of a steam shutoff valve for shutting off steam flowing into a turbine is provided in an upstream side pipe of the common communication pipe. 【請求項５】 それぞれ独立して蒸気発生源より発生し
た少なくとも２個以上の蒸気を、共通連絡管で合流さ
せ、少なくとも１台の蒸気タービンに導き、前記蒸気タ
ービンおよび発電機を駆動させる多軸複合サイクル発電
プラントにおいて、前記蒸気タービンへの蒸気圧力を調
整する圧力調整弁と、前記蒸気発生源より発生する蒸気
が前記共通連絡管上流側配管への流れを停止するボイラ
止め弁と、前記蒸気タービンへ流入する蒸気を遮断する
蒸気遮断弁のすべてもしくは一部のいずれか一方とを前
記共通連絡管の上流側配管に設け、かつ前記共通連絡
管，上流側配管内の圧力が設定値となるように前記圧力
調整弁の開閉量を制御する制御手段と、特定軸で停止や
事故が発生したとき、当該軸のボイラ止め弁を前記圧力
調整弁が閉じたのち、閉じさせる制御手段と、特定な軸
で停止や事故が発生したとき、当該軸の蒸気遮断弁を閉
じさせる制御手段を設けたことを特徴とする多軸複合サ
イクル発電プラント。5. A multi-spindle which independently combines at least two or more steams generated from a steam generation source by a common communication pipe and guides them to at least one steam turbine to drive the steam turbine and a generator. In a combined cycle power plant, a pressure adjusting valve that adjusts the steam pressure to the steam turbine, a boiler stop valve that stops the flow of steam generated from the steam generation source to the common communication pipe upstream side pipe, and the steam All or some of the steam shutoff valves that shut off the steam flowing into the turbine are installed in the upstream pipe of the common communication pipe, and the pressure in the common communication pipe and the upstream pipe becomes the set value. Control means for controlling the opening / closing amount of the pressure regulating valve, and when a stop or an accident occurs in a specific axis, the boiler stop valve of the axis is closed after the pressure regulating valve is closed. A multi-shaft combined cycle power plant, which is provided with a control means for controlling the same and a control means for closing the steam cutoff valve of the shaft when a stop or an accident occurs in a specific shaft. 【請求項６】 前記圧力調整弁用制御手段は、前記共通
連絡管上流側にあらたに台数を追加して起動する場合、
追加軸の共通連絡管の上流側配管に設けられるととも
に、その圧力設定値を既に運転中の共通連絡管の上流側
配管のうち最も小さい圧力にしたことを特徴とする請求
項２，４，５のいずれかに記載の多軸複合サイクル発電
プラント。6. When the control means for the pressure regulating valve is newly activated on the upstream side of the common communication pipe and is activated,
6. The additional shaft is provided on the upstream side pipe of the common connecting pipe, and the pressure set value is set to the smallest pressure among the upstream side pipes of the common connecting pipe already in operation. A multi-axis combined cycle power plant according to any one of 1. 【請求項７】 前記圧力調整弁用制御手段は、前記共通
連絡管内の圧力が所定以上の早さで下降あるいは上昇す
る現象を発生したことを検知したとき、検知される直前
の前記共通連絡管内の圧力をもって前記圧力調整弁の設
定値としたことを特徴とする請求項２，４，５，６のい
ずれかに記載の多軸複合サイクル発電プラント。7. The inside of the common communication pipe immediately before being detected, when the pressure control valve control means detects that the pressure in the common communication pipe has decreased or increased at a predetermined speed or more. The multi-shaft combined cycle power plant according to any one of claims 2, 4, 5 and 6, wherein the pressure is set as the set value of the pressure regulating valve. 【請求項８】 前記圧力調整弁用制御手段は、前記現象
が特定の軸に限定してを発生したことを検知したとき、
当該軸以外の前記圧力調整弁の設置値を、前記現象が収
束したのち、変更することを特徴とする請求項７記載の
多軸複合サイクル発電プラント。8. The pressure control valve control means, when it is detected that the phenomenon is limited to a specific axis,
8. The multi-shaft combined cycle power plant according to claim 7, wherein the installation value of the pressure control valve other than the shaft is changed after the phenomenon has converged.
JP21145992A 1992-08-07 1992-08-07 Multi-shaft combined cycle power plant Expired - Fee Related JP3144440B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP21145992A JP3144440B2 (en) 1992-08-07 1992-08-07 Multi-shaft combined cycle power plant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP21145992A JP3144440B2 (en) 1992-08-07 1992-08-07 Multi-shaft combined cycle power plant

Publications (2)

Publication Number Publication Date
JPH0658104A true JPH0658104A (en) 1994-03-01
JP3144440B2 JP3144440B2 (en) 2001-03-12

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ID=16606293

Family Applications (1)

Application Number Title Priority Date Filing Date
JP21145992A Expired - Fee Related JP3144440B2 (en) 1992-08-07 1992-08-07 Multi-shaft combined cycle power plant

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Country Link
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010261444A (en) * 2009-05-05 2010-11-18 General Electric Co <Ge> Steam turbine power generation system and method of assembling the same
JP2016008688A (en) * 2014-06-25 2016-01-18 中国電力株式会社 Syngas supply system
WO2020031716A1 (en) * 2018-08-08 2020-02-13 川崎重工業株式会社 Combined cycle power plant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010261444A (en) * 2009-05-05 2010-11-18 General Electric Co <Ge> Steam turbine power generation system and method of assembling the same
JP2016008688A (en) * 2014-06-25 2016-01-18 中国電力株式会社 Syngas supply system
WO2020031716A1 (en) * 2018-08-08 2020-02-13 川崎重工業株式会社 Combined cycle power plant
JP2020023943A (en) * 2018-08-08 2020-02-13 川崎重工業株式会社 Combined cycle power plant

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