JPH10325337A - Compressor surging preventing device for pressure fluidized bed combined power generational system - Google Patents
Compressor surging preventing device for pressure fluidized bed combined power generational systemInfo
- Publication number
- JPH10325337A JPH10325337A JP13845797A JP13845797A JPH10325337A JP H10325337 A JPH10325337 A JP H10325337A JP 13845797 A JP13845797 A JP 13845797A JP 13845797 A JP13845797 A JP 13845797A JP H10325337 A JPH10325337 A JP H10325337A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- pressure
- surging
- valve
- gas turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は加圧流動層複合発電
システムにおいて負荷変動がある場合の圧縮機サージン
グ防止装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor surging prevention apparatus in a pressurized fluidized-bed combined power generation system when there is a load change.
【０００２】[0002]
【従来の技術】加圧流動層複合発電システムでは流動層
ボイラで石炭等を燃焼させ、発生した蒸気で蒸気タービ
ンを駆動し、更に流動層ボイラの燃焼で得られた高温、
高圧の燃焼ガスでガスタービンを駆動し、高効率で電力
を得るものである。2. Description of the Related Art In a pressurized fluidized-bed combined power generation system, coal and the like are burned in a fluidized-bed boiler, a steam turbine is driven by generated steam, and the high temperature obtained by combustion of the fluidized-bed boiler is further increased.
A gas turbine is driven by high-pressure combustion gas to obtain electric power with high efficiency.
【０００３】図４は上記に説明の加圧流動層複合発電シ
ステムの燃焼装置の代表的な系統図である。図におい
て、１１はガスタービン、１２はガスタービンに結合さ
れた圧縮機、１３は加圧流動層ボイラであり、圧力容器
１３−１内に火炉１３−２、容器１３−３を有し、発生
した蒸気で図示していない蒸気タービンを駆動し、燃焼
したガスはダクト１６，１７を通ってガスタービン１１
に供給され、ガスタービン１１を駆動し、その排気ガス
からは排熱回収ボイラ２０を通して排熱を回収し、煙突
２１から外気へ排出する。FIG. 4 is a typical system diagram of a combustion device of the pressurized fluidized bed combined cycle system described above. In the figure, 11 is a gas turbine, 12 is a compressor coupled to the gas turbine, 13 is a pressurized fluidized bed boiler, which has a furnace 13-2 and a container 13-3 in a pressure vessel 13-1, and generates The steam thus generated drives a steam turbine (not shown), and the combusted gas passes through ducts 16 and 17 to the gas turbine 11.
And drives the gas turbine 11, recovers exhaust heat from the exhaust gas through an exhaust heat recovery boiler 20, and discharges the exhaust heat from a chimney 21 to the outside air.
【０００４】ガスタービン１１で駆動される圧縮機１２
により空気が加圧され、圧縮機出口弁１５を介し、ダク
ト１８により加圧流動層ボイラ１３内の火炉１３−２に
燃焼用空気として供給される。又、起動時には、加圧流
動層ボイラ１３からの燃焼ガスが充分にダクト１６から
供給されないので、起動用燃焼器１４を駆動し、圧縮機
出口弁１５を切換えてダクト１９側に圧縮機１２から空
気を供給し、ガスタービン１１を駆動して立上げを行
う。加圧流動層ボイラ１３が充分に加熱した後は、圧縮
機出口弁１５を切換えてダクト１９の空気を絶ってガス
タービン１１は加圧流動層ボイラ１３からの燃焼ガスで
駆動される。A compressor 12 driven by a gas turbine 11
The air is pressurized and supplied to the furnace 13-2 in the pressurized fluidized bed boiler 13 by the duct 18 through the compressor outlet valve 15 as combustion air. Also, at the time of startup, since the combustion gas from the pressurized fluidized bed boiler 13 is not sufficiently supplied from the duct 16, the startup combustor 14 is driven, the compressor outlet valve 15 is switched, and the compressor 19 is moved to the duct 19 side. Air is supplied and the gas turbine 11 is driven to start up. After the pressurized fluidized bed boiler 13 is sufficiently heated, the compressor outlet valve 15 is switched to cut off the air in the duct 19 and the gas turbine 11 is driven by the combustion gas from the pressurized fluidized bed boiler 13.
【０００５】加圧流動層ボイラ１３の火炉１３−２で
は、負荷変化に対して流動層の高さを変化させる。即
ち、負荷減少時には火炉１３−２内の媒体を容器１３−
３に取り出して移動し、火炉１３−２内の流動層高さを
低くし、逆に負荷が増加する時には容器１３−３から媒
体を火炉１３−２内に戻して流動層高を増加させる。こ
のように加圧流動層ボイラ１３の火炉１３−２では流動
層高の操作によって流動層内の伝熱管の伝熱面積を増減
させ、蒸気の発生量を調節している。[0005] In the furnace 13-2 of the pressurized fluidized bed boiler 13, the height of the fluidized bed is changed in response to a change in load. That is, when the load decreases, the medium in the furnace 13-2 is transferred to the container 13-.
3 and move to lower the height of the fluidized bed in the furnace 13-2. Conversely, when the load increases, the medium is returned from the vessel 13-3 into the furnace 13-2 to increase the height of the fluidized bed. As described above, in the furnace 13-2 of the pressurized fluidized-bed boiler 13, the heat transfer area of the heat transfer tube in the fluidized bed is increased or decreased by operating the fluidized bed height to adjust the amount of generated steam.
【０００６】[0006]
【発明が解決しようとする課題】前述の加圧流動層複合
発電システムにおいては、ガスタービン１１に直結した
圧縮機１２は通常のものと異り、出口側に大容量の圧力
容器１３−１を有しており、吸込風量の変化に対して圧
力比の変化が遅い。負荷が減少した場合には、火炉１３
−２の燃焼用空気流量を給炭量に応じて少くする必要が
ある。そのために圧縮機１２から火炉１３−２に供給さ
れる空気流量を減少させなければならない。この時の風
量減少時には、ある限界圧力値においてサージングを起
すが、この圧縮機のサージング限界圧力比も風量の減少
に伴って同時に低下する。しかし、前述のように空気流
量を減少しても、圧縮機出口側は大容量の圧力容器１３
−１があるため、運転圧力比は低下せず、以前の高い圧
力状態を保持している。その結果、風量を減少していく
と、運転中の圧力はサージング限界圧力ラインに達し、
サージングに至ることになる。In the pressurized fluidized-bed combined power generation system described above, the compressor 12 directly connected to the gas turbine 11 is different from a normal compressor, and a large-capacity pressure vessel 13-1 is provided at the outlet side. And the change in pressure ratio is slow with respect to the change in suction air volume. If the load decreases, the furnace 13
It is necessary to reduce the combustion air flow rate of -2 according to the amount of coal supplied. Therefore, the flow rate of air supplied from the compressor 12 to the furnace 13-2 must be reduced. At this time, when the air volume decreases, surging occurs at a certain limit pressure value, but the surging limit pressure ratio of the compressor also decreases at the same time as the air volume decreases. However, even if the air flow rate is reduced as described above, the compressor outlet side has a large capacity pressure vessel 13.
Since there is -1, the operating pressure ratio does not decrease and maintains the previous high pressure state. As a result, as the air flow decreases, the pressure during operation reaches the surging limit pressure line,
It will lead to surging.
【０００７】そこで、本発明は、前述のように風量減少
時に圧縮機がサージングに至る前に圧縮機出口側圧力が
サージング限界圧力に達しないように圧縮機からの風量
をバイパスさせ、サージングを回避できる加圧流動層複
合発電プラントの圧縮機サージング防止装置を提供する
ことを課題としてなされたものである。Accordingly, the present invention avoids surging by bypassing the air flow from the compressor so that the compressor outlet side pressure does not reach the surging limit pressure before the compressor reaches surging when the air flow is reduced as described above. An object of the present invention is to provide a compressor surging prevention device for a pressurized fluidized bed combined cycle power plant that can be used.
【０００８】[0008]
【課題を解決するための手段】本発明は、上記の課題を
解決するために次の（１）及び（２）の手段を提供す
る。The present invention provides the following means (1) and (2) for solving the above-mentioned problems.
【０００９】（１）加圧流動層ボイラで蒸気系を加熱す
ると共に、その燃焼ガスでガスタービンを駆動し、同ガ
スタービンに直結の圧縮機からの空気を前記加圧流動層
ボイラの燃焼用空気として供給する加圧流動層複合発電
システムにおける圧縮機サージング防止装置であって；
前記圧縮機出口側と前記ガスタービン排気側との間に連
通し、開閉弁を有する第１のバイパス流路と；前記圧縮
機出口側と前記ガスタービン入口側との間を連通し、開
閉弁を有する第２のバイパス流路と；前記圧縮機出口圧
力を検出する圧力検出器と；同圧力検出器の検出圧力値
を入力し、あらかじめ定められた圧縮機入口可変静翼開
度とサージング限界圧力との関係に基づいて前記第１及
び第２のバイパス流路開閉弁を制御する制御装置とを具
備してなることを特徴とする加圧流動層複合発電システ
ムの圧縮機サージング防止装置。(1) A steam system is heated by a pressurized fluidized bed boiler, and a gas turbine is driven by the combustion gas, and air from a compressor directly connected to the gas turbine is used for combustion of the pressurized fluidized bed boiler. A compressor anti-surging device in a pressurized fluidized-bed combined power generation system supplying as air;
A first bypass passage communicating between the compressor outlet side and the gas turbine exhaust side and having an on-off valve; communicating between the compressor outlet side and the gas turbine inlet side; A pressure detector for detecting the compressor outlet pressure, and a predetermined compressor inlet variable stator vane opening and a surging limit by inputting the pressure detected by the pressure detector. A controller for controlling the first and second bypass passage opening / closing valves on the basis of a relationship with pressure; and a compressor surging prevention apparatus for a pressurized fluidized bed combined power generation system.
【００１０】（２）上記の（１）の発明において、前記
制御装置にはあらかじめ２つのサージング限界圧力特性
を定めておき、同制御装置は前記圧力検出器で検出する
運転中の圧力が前記サージング限界圧力の一方の圧力に
達すると入口可変静翼の開度を保持すると共に、第１バ
イパス流路の開閉弁を開放し、更に、他方の限界圧力に
達すると第２のバイパス流路の開閉弁を開放するように
制御することを特徴とする加圧流動層複合発電システム
の圧縮機サージング防止装置。(2) In the invention of the above (1), two surging limit pressure characteristics are determined in advance in the control device, and the control device determines that the operating pressure detected by the pressure detector is the surging. When the pressure reaches one of the limit pressures, the opening degree of the inlet variable stationary blade is maintained, and the on-off valve of the first bypass flow path is opened. When the other limit pressure is reached, the opening and closing of the second bypass flow path is opened and closed. A compressor surging prevention apparatus for a pressurized fluidized-bed combined power generation system, characterized in that control is performed to open a valve.
【００１１】（３）上記の（２）の発明において、あら
かじめ定められた前記２つのサージング限界圧力特性は
前記圧縮機の吸気温度により補正可能としたことを特徴
とする加圧流動層複合発電システムの圧縮機サージング
防止装置。(3) In the invention of the above (2), the two predetermined surging limit pressure characteristics can be corrected by an intake air temperature of the compressor. Compressor surging prevention device.
【００１２】本発明の（１）においては、第１のバイパ
ス流路と第２のバイパス流路とを備えており、これら流
路はそれぞれ開閉弁を有し、圧縮機がサージングを起す
直前にはこれら開閉弁を開放し、圧縮機出口側からの空
気をバイパスさせて流出させ、出口側圧力が上昇しない
ようにしてサージングを防ぐ。In (1) of the present invention, a first bypass flow path and a second bypass flow path are provided, each of which has an on-off valve, and which is provided immediately before the compressor starts surging. Opens these on-off valves to allow air from the compressor outlet side to bypass and flow out, and to prevent surging by preventing the outlet side pressure from rising.
【００１３】即ち、運転中に負荷が減少すると、これに
伴って加圧流動層ボイラに流入する圧縮機からの空気量
も負荷減少に伴って減少させるが、圧縮機出口側には大
きな圧力容器があるので圧縮機入口可変翼開度を小さく
して空気流量を減少させても出口側圧力は低下せず、サ
ージングに至ってしまう。That is, when the load decreases during operation, the amount of air from the compressor flowing into the pressurized fluidized-bed boiler also decreases with the decrease in load. Therefore, even if the opening degree of the variable blades at the compressor inlet is reduced to reduce the air flow rate, the pressure at the outlet side does not decrease, resulting in surging.
【００１４】そこで、本発明の（１）では、制御装置に
はあらかじめサージングに至る直前のサージング限界圧
力を設定し、記憶させておき、圧縮機入口可変静翼開度
を減少させて空気流量を減少させる過程において、圧縮
機出口圧力がこの限界圧力に達すると圧縮機入口可変静
翼開度の減少を制限すると共に第１又は第２、あるいは
両方の開閉弁を開き、圧縮機からの空気をバイパスさせ
て圧縮機出口圧力が上昇しないようにしてサージングに
至らないようにする。この場合の運転中の圧縮機出口圧
力は圧力検出器で検出し、制御装置に入力され、制御装
置では前述のようにあらかじめ設定した圧力限界と比較
し、上記のように第１、第２バイパス流路の開閉弁を制
御する。Therefore, in (1) of the present invention, the surging limit pressure immediately before surging is set in the control device and stored in advance, and the air flow rate is reduced by reducing the opening degree of the variable vanes at the compressor inlet. In the process of reducing, when the compressor outlet pressure reaches this limit pressure, the reduction of the compressor inlet variable vane opening is limited and the first or second or both on-off valves are opened, and air from the compressor is released. By bypassing, the compressor outlet pressure is prevented from rising, so that surging does not occur. In this case, the compressor outlet pressure during operation is detected by the pressure detector and input to the control device. The control device compares the pressure with the preset pressure limit as described above, and performs the first and second bypasses as described above. Controls the open / close valve of the flow path.
【００１５】上記の圧縮機からの空気量をバイパスさせ
る方法としては、（２）の発明のように、制御装置には
限界圧力を２つ定めておき、まず最初に１つの限界圧力
に基づいて第１バイパス流路の開閉弁を開放する。この
場合には圧縮機出口側から空気がバイパスしてガスター
ビン排気側に流出し、圧縮機出口圧力の上昇を抑え、サ
ージングに至らないようにするが、圧縮機の空気に高
温、高圧の蒸気が混入する場合があり、この場合には圧
縮機出口圧力が急激に上昇することがある。このような
場合においては２つ目の限界圧力に基づいて第２のバイ
パス流路の開閉弁を開き、圧縮機出口側から空気をバイ
パス流路を介してガスタービンの入口側へ流出させ、流
動層からの燃焼ガスに混入する。このようにして、圧縮
機出口圧力の上昇を抑え、サージングに至らないように
制御することができる。As a method for bypassing the amount of air from the compressor, as in the invention of (2), two critical pressures are determined in the control device, and first, based on one critical pressure, The on-off valve of the first bypass flow path is opened. In this case, air is bypassed from the compressor outlet side and flows out to the gas turbine exhaust side to suppress the rise in compressor outlet pressure and prevent surging, but high-temperature, high-pressure steam is added to the compressor air. May be mixed, and in this case, the compressor outlet pressure may increase sharply. In such a case, the on-off valve of the second bypass flow path is opened based on the second limit pressure, and air is discharged from the compressor outlet side to the gas turbine inlet side via the bypass flow path, and Mixes into combustion gases from beds. In this way, it is possible to suppress an increase in the compressor outlet pressure and control so as not to cause surging.
【００１６】更に、（３）の発明においては、圧縮機の
吸気温度によりサージラインが変化するが、制御装置に
は吸気温度変化により補正をかける制御が出来るように
しているので、圧縮機の吸気温度変化に対しても補正
し、制御することができる。Further, in the invention of (3), the surge line changes depending on the intake air temperature of the compressor. However, since the control device can perform control to make a correction based on the change in intake air temperature, the intake line of the compressor can be controlled. The temperature can be corrected and controlled.
【００１７】[0017]
【発明の実施の形態】以下、本発明の実施の形態につい
て図面に基づいて具体的に説明する。図１は本発明の実
施の一形態に係る加圧流動層複合発電システムの圧縮機
サージング防止装置の系統図である。図において、符号
１１乃至２１は図４に示す従来のものと同一機能を有す
るので説明は省略するが、本発明の特徴部分は符号２乃
至７で示す部分であり、以下に詳しく説明する。Embodiments of the present invention will be specifically described below with reference to the drawings. FIG. 1 is a system diagram of a compressor surging prevention device of a combined pressurized fluidized bed power generation system according to an embodiment of the present invention. In the figure, reference numerals 11 to 21 have the same functions as those of the conventional device shown in FIG. 4, and therefore description thereof will be omitted.
【００１８】図１において、２は圧縮機出口バイパス弁
で、圧縮機１２の出口側とガスタービン１１の入口側ガ
ス通路に連通するダクト１９との間に配設されたバイパ
ス管６の途中に設けられている。３はサージング防止弁
であり、圧縮機１２の出口側とガスタービン１１の排気
系路とに連通するバイパス管７の途中に設けられてい
る。In FIG. 1, reference numeral 2 denotes a compressor outlet bypass valve, which is provided in the middle of a bypass pipe 6 provided between an outlet side of the compressor 12 and a duct 19 communicating with a gas passage on the inlet side of the gas turbine 11. Is provided. Reference numeral 3 denotes a surging prevention valve, which is provided in the middle of a bypass pipe 7 that communicates with the outlet side of the compressor 12 and the exhaust system of the gas turbine 11.
【００１９】４は圧力検出器であり、圧縮機１２の出口
側の配管に設けられ、圧縮機出口側の圧力を検出する。
５は制御装置であり、圧力検出器４からの圧縮機１２出
口側圧力信号を入力し、後述するように、圧縮機１２の
サージングが起る直前の運転限界圧力比としての制御ラ
インと比較し、圧縮機出口側圧力がサージング直前の値
となるとサージング防止弁３、あるいは圧縮機出口バイ
パス弁２を開放し、サージングを防止するように制御す
るものである。Reference numeral 4 denotes a pressure detector which is provided on a pipe on the outlet side of the compressor 12 and detects a pressure on the compressor outlet side.
Reference numeral 5 denotes a control device which receives a compressor 12 outlet side pressure signal from the pressure detector 4 and compares it with a control line as an operation limit pressure ratio immediately before surging of the compressor 12 as described later. When the pressure on the compressor outlet side becomes a value immediately before surging, the anti-surging valve 3 or the compressor outlet bypass valve 2 is opened to control so as to prevent surging.
【００２０】図２は上記の実施の形態における圧縮機の
入口可変静翼の開度と圧縮機出口圧力との関係を示す図
である。図２において、サージライン（Ｓ）の特性は、
圧縮機においてあらかじめわかっており、このサージラ
イン（Ｓ）の曲線より２５％圧力の減少した特性を運転
限界圧力として制御ライン（Ａ）とする。更に、サージ
ライン（Ｓ）の特性より２０％圧力の減少した特性を制
御ライン（Ｂ）として設定する。これらの制御ライン
（Ａ）、（Ｂ）の特性データは制御装置５にあらかじめ
設定しておくと共に、圧縮機の吸気温度に対しても補正
がかかるように制御可能としておく。即ち図２におい
て、吸気温度が上昇するとサージラインあるいは制御ラ
インが下方に、又吸気温度が下降すると上方に変化する
ので、制御装置でこのような補正ができるようにしてい
る。FIG. 2 is a diagram showing the relationship between the opening degree of the variable inlet vanes of the compressor and the compressor outlet pressure in the above embodiment. In FIG. 2, the characteristics of the surge line (S) are as follows.
The characteristic which is known in advance in the compressor and whose pressure is reduced by 25% from the curve of the surge line (S) is defined as the operation limit pressure as the control line (A). Further, a characteristic in which the pressure is reduced by 20% from the characteristic of the surge line (S) is set as the control line (B). The characteristic data of these control lines (A) and (B) are set in the control device 5 in advance, and can be controlled so that the intake air temperature of the compressor is also corrected. That is, in FIG. 2, the surge line or the control line changes downward when the intake air temperature rises, and changes upward when the intake air temperature falls. Therefore, such a correction can be made by the control device.
【００２１】図２においてＣは運転点であり、その入口
可変静翼開度をα2 として、今負荷が減少して圧縮機の
空気流量を減少する場合に、入口可変静翼開度を減少す
ると、前述のように圧縮機出口側は大きな圧力容器１３
−１に連通しているので圧力は直ちに下降せず、そのま
まの状態を保持して開度α1 でＣ′点の圧力β1 で制御
ライン（Ａ）に達する。[0021] a C is the operating point in FIG. 2, as a inlet variable stator vanes opening the alpha 2, if the current load decreases the air flow rate of the compressor decreases, reducing the inlet variable stator vanes opening Then, as described above, the compressor outlet side is a large pressure vessel 13.
Since communicates -1 pressure does not immediately lowered, reach the control line (A) at a pressure beta 1 of point C 'in opening alpha 1 holds intact.
【００２２】本発明の実施の形態においては、まずこの
Ｃ′点の圧縮機出口圧力β1 を圧力検出器４で検出する
と共に、入口可変静翼８の開度をα1 に保持させて図１
に示すサージング防止弁３を開放し、圧縮機出口側の空
気をバイパス管７から逃して圧縮機出口圧力がこれ以
上、上昇しないようにする。In the embodiment of the present invention, first, the compressor outlet pressure β 1 at the point C ′ is detected by the pressure detector 4, and the opening degree of the inlet variable vane 8 is held at α 1 . 1
The anti-surge valve 3 is opened to release the air on the compressor outlet side from the bypass pipe 7 so that the compressor outlet pressure does not rise any more.
【００２３】上記のＣ′点において圧力はβ1 の点で保
持され、上昇しないが、空気中に高温の蒸気が混入する
場合があり、このような場合には更に、圧縮機出口圧力
は急激に上昇することがある。このような場合には圧力
がｄ点のβ2 まで上昇すると制御ライン（Ｂ）に達し、
本発明の実施の形態においてはこのｄ点の圧力β2 を圧
力検出器４で検出し、図１に示す圧縮機出口バイパス弁
２を開き、圧縮機１２の出口側の空気をバイパス管６か
らガスタービン１１の入口側に逃がし、圧縮機出口圧力
がサージライン（Ｓ）まで上昇しないようにする。At the above-mentioned point C ', the pressure is maintained at the point of β 1 and does not rise, but high-temperature steam may be mixed into the air. In such a case, the compressor outlet pressure further increases rapidly. May rise. In such a case, when the pressure rises to β 2 at the point d, the pressure reaches the control line (B),
In the embodiment of the present invention, the pressure β 2 at the point d is detected by the pressure detector 4, the compressor outlet bypass valve 2 shown in FIG. 1 is opened, and the air on the outlet side of the compressor 12 is discharged from the bypass pipe 6. The gas is released to the inlet side of the gas turbine 11 so that the compressor outlet pressure does not rise to the surge line (S).
【００２４】図３は上記に説明の制御を行う制御装置５
内の制御フローを示す図である。制御装置５内にはあら
かじめ記憶装置５−１内に図２に示すような制御ライン
（Ａ）、（Ｂ）のデータが記憶されている。運転中に負
荷が減少し、圧縮機の空気量を減少させるために入口可
変静翼の開度を減少させる場合に、運転中の圧縮機出口
圧力を圧力検出器４で検出し、この圧力があらかじめ設
定した制御ライン（Ａ）、（Ｂ）の規定値を越えると、
制御装置５は直ちに入口可変静翼８の開度を保持した上
でサージ防止弁３、あるいは圧縮機出口バイパス弁２を
開き、加圧流動層ボイラ１３へ流入する空気量をバイパ
スして圧力上昇を防ぎ、サージングを防止するものであ
る。次にその制御フローについて詳しく説明する。FIG. 3 shows a control unit 5 for performing the control described above.
It is a figure which shows the control flow in FIG. In the control device 5, data of control lines (A) and (B) as shown in FIG. When the load decreases during operation and the opening degree of the inlet variable vane is reduced to reduce the air amount of the compressor, the compressor outlet pressure during operation is detected by the pressure detector 4, and this pressure is detected. Exceeding the prescribed values of the control lines (A) and (B) set in advance
The controller 5 immediately maintains the opening of the inlet variable stator vane 8 and opens the surge prevention valve 3 or the compressor outlet bypass valve 2 to bypass the amount of air flowing into the pressurized fluidized bed boiler 13 and increase the pressure. To prevent surging. Next, the control flow will be described in detail.
【００２５】図３において、まずＳ１で加圧流動層ボイ
ラ１３の負荷が減少すると、圧縮機１２からの空気量も
減少させる必要があるので、Ｓ２において圧縮機の入口
可変静翼の開度を減少させる。その時Ｓ３において圧力
検出器４により圧縮機出口圧力を検出し、記憶装置５−
１から制御ライン（Ａ）のデータを取込み、その検出圧
力値が所定の圧力値以内であるか否かを調べ、検出圧力
値が制御ライン（Ａ）で定める値に等しいか、あるいは
これを越えていると、Ｓ４においてサージング防止弁３
を開き、空気流量をバイパスさせてサージングを防止す
る。検出した出口圧力が制御ライン（Ａ）で定める圧力
値に達していなければ、Ｓ７でそのまま運転を継続す
る。In FIG. 3, when the load of the pressurized fluidized-bed boiler 13 is reduced in S1, the amount of air from the compressor 12 also needs to be reduced. Decrease. At that time, in S3, the compressor outlet pressure is detected by the pressure detector 4, and the storage device 5-
The data of the control line (A) is fetched from 1 and it is checked whether the detected pressure value is within a predetermined pressure value, and the detected pressure value is equal to or exceeds the value determined by the control line (A). The surging prevention valve 3 in S4.
To bypass the air flow to prevent surging. If the detected outlet pressure has not reached the pressure value determined by the control line (A), the operation is continued at S7.
【００２６】Ｓ４でサージング防止弁３を開いた後、Ｓ
５において、記憶装置５−１より制御ライン（Ｂ）のデ
ータを取込み、圧力検出器４で検出した運転中の圧縮機
出口圧力が、この制御ライン（Ｂ）で定める圧力値に達
しているか否かを調べ、達していればＳ６において圧縮
機出口バイパス弁２を開き、空気流量を更にバイパスさ
せてサージングを防止する。制御ライン（Ｂ）で定まる
圧力値に達していなければ、Ｓ７でそのまま運転を継続
する。After opening the anti-surging valve 3 in S4,
At 5, the data of the control line (B) is fetched from the storage device 5-1, and whether or not the operating compressor outlet pressure detected by the pressure detector 4 has reached the pressure value determined by the control line (B) The compressor outlet bypass valve 2 is opened in S6 if it has reached, and the air flow is further bypassed to prevent surging. If the pressure value determined by the control line (B) has not been reached, the operation is continued in S7.
【００２７】Ｓ７ではそれぞれＳ１，Ｓ３，Ｓ５，Ｓ６
での処理後に運転を継続し、Ｓ８で入口可変静翼の開度
調整が必要であればＳ２に戻り、必要なければ終了す
る。制御装置５は、このように入口可変静翼の開度を減
少させる際に、圧縮機出口圧力が減少せずにサージング
ラインに近づき、制御ライン（Ａ）に達した時点で入口
可変静翼８の開度を保持し、サージング防止弁３、ある
いは圧縮機出口バイパス弁２を開放して圧縮機１２出口
側から流出する空気量をバイパスさせ、圧縮機１２のサ
ージングを防止する。In S7, S1, S3, S5, S6
The operation is continued after the processing in step. If it is necessary to adjust the opening degree of the inlet variable stationary blade in step S8, the process returns to step S2, and otherwise ends. When the opening degree of the inlet variable stationary blade is reduced in this way, the control device 5 approaches the surging line without decreasing the compressor outlet pressure and reaches the control line (A) at the time of reaching the control line (A). , The surging prevention valve 3 or the compressor outlet bypass valve 2 is opened to bypass the amount of air flowing out from the compressor 12 outlet side, thereby preventing the compressor 12 from surging.
【００２８】[0028]
【発明の効果】本発明は、（１）は、加圧流動層ボイラ
で蒸気系を加熱すると共に、その燃焼ガスでガスタービ
ンを駆動し、同ガスタービンに直結の圧縮機からの空気
を前記加圧流動層ボイラの燃焼用空気として供給する加
圧流動層複合発電システムにおける圧縮機サージング防
止装置であって；前記圧縮機出口側と前記ガスタービン
排気側との間に連通し、開閉弁を有する第１のバイパス
流路と；前記圧縮機出口側と前記ガスタービン入口側と
の間を連通し、開閉弁を有する第２のバイパス流路と；
前記圧縮機出口圧力を検出する圧力検出器と；同圧力検
出器の検出圧力値を入力し、あらかじめ定められた圧縮
機入口可変静翼開度とサージング限界圧力との関係に基
づいて前記第１及び第２のバイパス流路開閉弁を制御す
る制御装置とを具備してなることを特徴としている。
又、（２）の発明では（１）の発明において、前記制御
装置にはあらかじめ２つのサージング限界圧力特性を定
めておき、同制御装置は前記圧力検出器で検出する運転
中の圧力が前記サージング限界圧力の一方の圧力に達す
ると入口可変静翼の開度を保持すると共に、第１バイパ
ス流路の開閉弁を開放し、更に、他方の限界圧力に達す
ると第２のバイパス流路の開閉弁を開放するように制御
することを特徴としている。更に、（３）の発明では、
上記（２）の発明において、前記２つのサージング限界
圧力特性は前記圧縮機の吸気温度により補正可能とする
ことを特徴としている。According to the present invention, (1) heats a steam system with a pressurized fluidized bed boiler, drives a gas turbine with the combustion gas, and removes air from a compressor directly connected to the gas turbine. A compressor surging prevention device in a pressurized fluidized bed combined power generation system for supplying air for combustion in a pressurized fluidized bed boiler, wherein the device communicates between the compressor outlet side and the gas turbine exhaust side, and includes an on-off valve. A second bypass flow path communicating between the compressor outlet side and the gas turbine inlet side and having an on-off valve;
A pressure detector for detecting the compressor outlet pressure; inputting a detected pressure value of the pressure detector, and detecting the first pressure on the basis of a predetermined relationship between a compressor inlet variable stationary blade opening degree and a surging limit pressure. And a control device for controlling the second bypass passage opening / closing valve.
Further, in the invention of (2), in the invention of (1), two surging limit pressure characteristics are previously defined in the control device, and the control device determines that the operating pressure detected by the pressure detector is the surging. When the pressure reaches one of the limit pressures, the opening degree of the inlet variable stationary blade is maintained, and the on-off valve of the first bypass flow path is opened. When the other limit pressure is reached, the opening and closing of the second bypass flow path is opened and closed. The valve is controlled to be opened. Furthermore, in the invention of (3),
The invention of the above (2) is characterized in that the two surging limit pressure characteristics can be corrected by the intake air temperature of the compressor.
【００２９】上記の構成により、加圧流動層複合発電シ
ステムにおいて、加圧流動層ボイラの負荷が減少し、圧
縮機から加圧流動層へ供給する空気量を減少させる場合
に、圧縮機入口可変静翼開度を減少させても圧縮機がサ
ージングに至る前に圧縮機出口圧力の上昇を抑え、サー
ジングを確実に防止することができる。With the above configuration, in the pressurized fluidized bed combined power generation system, when the load on the pressurized fluidized bed boiler is reduced and the amount of air supplied from the compressor to the pressurized fluidized bed is reduced, the compressor inlet variable Even if the opening degree of the vane is reduced, the rise of the compressor outlet pressure is suppressed before the compressor reaches surging, so that surging can be reliably prevented.
【００３０】更に、第１、第２のバイパス流路を設けた
ことにより、第１のバイパス流路で圧縮機のサージング
を防止でき、この時の圧縮機出口圧力が万一急激に上昇
するようなことがあっても、更に第２のバイパス流路の
開閉弁を開くことによりサージングを確実に防止するこ
とができる。Further, by providing the first and second bypass passages, surging of the compressor can be prevented in the first bypass passage so that the compressor outlet pressure at this time suddenly increases. Even if there is nothing, surging can be reliably prevented by further opening the on-off valve of the second bypass flow path.
【００３１】更に、圧縮機の吸気温度によりサージング
ラインが変化しても、この変化分を補正することができ
るのでサージングの防止が一層確実になる。Furthermore, even if the surging line changes due to the intake air temperature of the compressor, the change can be corrected, so that the surging can be more reliably prevented.
【図１】本発明の実施の一形態に係る加圧流動層複合発
電システムの圧縮機サージング防止装置の系統図であ
る。FIG. 1 is a system diagram of a compressor surging prevention device of a pressurized fluidized bed combined cycle power generation system according to an embodiment of the present invention.
【図２】本発明の実施の一形態に係る加圧流動層複合発
電システムの圧縮機サージング防止装置の入口可変静翼
開度と圧縮機出口圧力との関係を示す図である。FIG. 2 is a diagram illustrating a relationship between an inlet variable vane opening degree and a compressor outlet pressure of a compressor surging prevention device of the pressurized fluidized bed combined power generation system according to one embodiment of the present invention.
【図３】本発明の実施の一形態に係る加圧流動層複合発
電システムの圧縮機サージング防止装置の制御フローチ
ャートである。FIG. 3 is a control flowchart of a compressor surging prevention device of the pressurized fluidized-bed combined power generation system according to one embodiment of the present invention.
【図４】従来の加圧流動層複合発電システムの系統図で
ある。FIG. 4 is a system diagram of a conventional pressurized fluidized bed combined cycle system.
２ 圧縮機出口バイパス弁 ３ サージング防止弁 ４ 圧力検出器 ５ 制御装置 ５−１ 記憶装置 ６，７ バイパス管 ８ 入口可変静翼 １１ ガスタービン １２ 圧縮機 １３ 加圧流動層ボイラ １３−１ 圧力容器 １４ 起動用燃焼器 １６，１７，１８，１９ ダクト ２０ 排熱回収ボイラ ２１ 煙突 2 Compressor outlet bypass valve 3 Surging prevention valve 4 Pressure detector 5 Control device 5-1 Storage device 6, 7 Bypass pipe 8 Inlet variable stator vane 11 Gas turbine 12 Compressor 13 Pressurized fluidized bed boiler 13-1 Pressure vessel 14 Startup combustor 16, 17, 18, 19 Duct 20 Waste heat recovery boiler 21 Chimney
───────────────────────────────────────────────────── フロントページの続き (72)発明者 藤井 文倫 兵庫県高砂市荒井町新浜２丁目１番１号 三菱重工業株式会社高砂製作所内 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Bunrin Fujii 2-1-1, Shinhama, Arai-machi, Takasago-shi, Hyogo Pref. Mitsubishi Heavy Industries, Ltd.
Claims (3)
共に、その燃焼ガスでガスタービンを駆動し、同ガスタ
ービンに直結の圧縮機からの空気を前記加圧流動層ボイ
ラの燃焼用空気として供給する加圧流動層複合発電シス
テムにおける圧縮機サージング防止装置であって；前記
圧縮機出口側と前記ガスタービン排気側との間に連通
し、開閉弁を有する第１のバイパス流路と；前記圧縮機
出口側と前記ガスタービン入口側との間を連通し、開閉
弁を有する第２のバイパス流路と；前記圧縮機出口圧力
を検出する圧力検出器と；同圧力検出器の検出圧力値を
入力し、あらかじめ定められた圧縮機入口可変静翼開度
とサージング限界圧力との関係に基づいて前記第１及び
第２のバイパス流路開閉弁を制御する制御装置とを具備
してなることを特徴とする加圧流動層複合発電システム
の圧縮機サージング防止装置。1. A pressurized fluidized-bed boiler heats a steam system, drives a gas turbine with the combustion gas, and supplies air from a compressor directly connected to the gas turbine to combustion air of the pressurized fluidized-bed boiler. A compressor bypass anti-surging device in a pressurized fluidized bed combined power generation system that supplies as: a first bypass passage communicating between the compressor outlet side and the gas turbine exhaust side and having an on-off valve; A second bypass passage communicating between the compressor outlet side and the gas turbine inlet side and having an on-off valve; a pressure detector for detecting the compressor outlet pressure; and a pressure detected by the pressure detector A control device for inputting a value and controlling the first and second bypass flow passage opening / closing valves based on a predetermined relationship between a compressor inlet variable vane opening and a surging limit pressure. It is characterized by Compressor surging prevention device for pressurized fluidized bed combined power generation system.
ジング限界圧力特性を定めておき、同制御装置は前記圧
力検出器で検出する運転中の圧力が前記サージング限界
圧力の一方の圧力に達すると入口可変静翼の開度を保持
すると共に、第１バイパス流路の開閉弁を開放し、更
に、他方の限界圧力に達すると第２のバイパス流路の開
閉弁を開放するように制御することを特徴とする請求項
１記載の加圧流動層複合発電システムの圧縮機サージン
グ防止装置。2. The control device has two surging limit pressure characteristics determined in advance, and the control device has an inlet when the operating pressure detected by the pressure detector reaches one of the surging limit pressures. Controlling the opening degree of the variable stator vane, opening the on-off valve of the first bypass flow path, and further opening the on-off valve of the second bypass flow path when the other limit pressure is reached. The compressor surging prevention apparatus for a pressurized fluidized-bed combined power generation system according to claim 1, wherein:
ング限界圧力特性は前記圧縮機の吸気温度により補正可
能としたことを特徴とする請求項２記載の加圧流動層複
合発電システムの圧縮機サージング防止装置。3. The compressor according to claim 2, wherein the two predetermined surging limit pressure characteristics can be corrected by an intake air temperature of the compressor. apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13845797A JP3530344B2 (en) | 1997-05-28 | 1997-05-28 | Compressor surging prevention device for pressurized fluidized bed combined cycle system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13845797A JP3530344B2 (en) | 1997-05-28 | 1997-05-28 | Compressor surging prevention device for pressurized fluidized bed combined cycle system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10325337A true JPH10325337A (en) | 1998-12-08 |
| JP3530344B2 JP3530344B2 (en) | 2004-05-24 |
Family
ID=15222475
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13845797A Expired - Fee Related JP3530344B2 (en) | 1997-05-28 | 1997-05-28 | Compressor surging prevention device for pressurized fluidized bed combined cycle system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3530344B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008025965A (en) * | 2006-07-25 | 2008-02-07 | Public Works Research Institute | Pressure incinerator equipment and its operation method |
| JP2008025966A (en) * | 2006-07-25 | 2008-02-07 | Public Works Research Institute | Pressure incinerator equipment and its start-up method |
| WO2008149731A1 (en) * | 2007-05-30 | 2008-12-11 | Mitsubishi Heavy Industries, Ltd. | Integrated gasification combined cycle plant |
| JP2011137576A (en) * | 2009-12-28 | 2011-07-14 | Sanki Eng Co Ltd | Method of operating pressurized-fluidized incinerator and pressurized-fluidized incinerator facility |
| CN107827251A (en) * | 2017-10-31 | 2018-03-23 | 亿昇(天津)科技有限公司 | A kind of centrifugal blower anti-surge control method |
| CN108332055A (en) * | 2018-02-11 | 2018-07-27 | 曹京良 | A kind of distribution point defeated station natural gas compression system |
| JP2020046082A (en) * | 2018-09-14 | 2020-03-26 | 国立研究開発法人産業技術総合研究所 | Method of operating pressurized fluidized circulation furnace system |
-
1997
- 1997-05-28 JP JP13845797A patent/JP3530344B2/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008025965A (en) * | 2006-07-25 | 2008-02-07 | Public Works Research Institute | Pressure incinerator equipment and its operation method |
| JP2008025966A (en) * | 2006-07-25 | 2008-02-07 | Public Works Research Institute | Pressure incinerator equipment and its start-up method |
| WO2008149731A1 (en) * | 2007-05-30 | 2008-12-11 | Mitsubishi Heavy Industries, Ltd. | Integrated gasification combined cycle plant |
| US8028511B2 (en) | 2007-05-30 | 2011-10-04 | Mitsubishi Heavy Industries, Ltd. | Integrated gasification combined cycle power generation plant |
| JP2011137576A (en) * | 2009-12-28 | 2011-07-14 | Sanki Eng Co Ltd | Method of operating pressurized-fluidized incinerator and pressurized-fluidized incinerator facility |
| CN107827251A (en) * | 2017-10-31 | 2018-03-23 | 亿昇(天津)科技有限公司 | A kind of centrifugal blower anti-surge control method |
| CN108332055A (en) * | 2018-02-11 | 2018-07-27 | 曹京良 | A kind of distribution point defeated station natural gas compression system |
| JP2020046082A (en) * | 2018-09-14 | 2020-03-26 | 国立研究開発法人産業技術総合研究所 | Method of operating pressurized fluidized circulation furnace system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3530344B2 (en) | 2004-05-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH10325337A (en) | Compressor surging preventing device for pressure fluidized bed combined power generational system | |
| JP2006118391A (en) | Control device for extracted air boosting facility in integrated gasification combined cycle plant | |
| JP3132834B2 (en) | Gas turbine combustor steam cooling system | |
| EP0933504B1 (en) | Pressurized fluidized-bed combined cycle power generation system | |
| JP4374798B2 (en) | Mill primary air flow controller for pulverized coal fired boiler equipment | |
| JP7168300B2 (en) | Method and device for avoiding surge of supercharger attached to incinerator | |
| JPS6232181A (en) | Device for energy recovery from gas generated in regeneration tower of fluid catalytic cracking equipment | |
| JP6623319B1 (en) | Waste treatment facility and operation method thereof | |
| JP4004499B2 (en) | Overspeed avoidance device for regenerative gas turbine | |
| JP4287940B2 (en) | Pressurized fluidized bed boiler apparatus and control method thereof | |
| JP5711795B2 (en) | Pressurized fluidized incinerator equipment and control method of pressurized fluidized incinerator equipment | |
| JP7246293B2 (en) | Waste treatment equipment and its operation method | |
| JP3700075B2 (en) | Pressurized fluidized bed combined power plant | |
| JP7063971B2 (en) | Pressurized air supply system and how to start the pressurized air supply system | |
| JPH08210601A (en) | Controller for power plant having pressure fluidized bed boiler | |
| JP7289777B2 (en) | Waste treatment equipment and its operation method | |
| JP2000161606A (en) | Steaming prevention control method nd apparatus for coal saving apparatus | |
| JP3845905B2 (en) | Outlet feed water temperature control device for gas high pressure feed water heater in exhaust recombustion combined cycle plant | |
| JP4127911B2 (en) | Steam turbine ground steam pressure controller | |
| JP3199893B2 (en) | Pressurized fluidized bed combustion plant | |
| JP2000345811A (en) | Exhaust heat recovery boiler plant and operating method thereof | |
| JP3649680B2 (en) | Extraction steam pressure control device and control method for main turbine | |
| JP2554492Y2 (en) | Control device for pressurized fluidized bed boiler | |
| JPH09105503A (en) | Method and apparatus for controlling steam temperature of combined cycle plant | |
| JPH05296407A (en) | After burning type combined cyclic power generating facility |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Effective date: 20040210 Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20040227 |
|
| LAPS | Cancellation because of no payment of annual fees |