WO2012133332A1 - 排熱回収ボイラおよび発電プラント - Google Patents
排熱回収ボイラおよび発電プラント Download PDFInfo
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- WO2012133332A1 WO2012133332A1 PCT/JP2012/057784 JP2012057784W WO2012133332A1 WO 2012133332 A1 WO2012133332 A1 WO 2012133332A1 JP 2012057784 W JP2012057784 W JP 2012057784W WO 2012133332 A1 WO2012133332 A1 WO 2012133332A1
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- fuel
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- stage auxiliary
- auxiliary combustion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/103—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with afterburner in exhaust boiler
- F01K23/105—Regulating means specially adapted therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/006—Auxiliaries or details not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
- F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B35/00—Control systems for steam boilers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22G—SUPERHEATING OF STEAM
- F22G1/00—Steam superheating characterised by heating method
- F22G1/16—Steam superheating characterised by heating method by using a separate heat source independent from heat supply of the steam boiler, e.g. by electricity, by auxiliary combustion of fuel oil
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- 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]
Definitions
- Embodiments of the present invention relate to an exhaust heat recovery boiler and a power plant.
- the combined cycle power plant is a power plant in which an exhaust heat recovery boiler is combined with a gas turbine and a steam turbine.
- a high-temperature and high-pressure combustion gas is sent from the combustor to the gas turbine, and the generator is rotated by rotating the gas turbine by the expansion of the combustion gas.
- the exhaust gas is introduced into an exhaust heat recovery boiler, and steam is generated by the heat energy of the exhaust gas in the exhaust heat recovery boiler.
- the steam is sent to the steam turbine and turns the generator with the gas turbine.
- an exhaust heat recovery boiler is a boiler that generates steam according to the heat of exhaust gas discharged from a gas turbine and supplies the steam to the steam turbine.
- an auxiliary combustion device for heating the exhaust gas has been added. Waste heat recovery boilers are increasing. This is because the output of the gas turbine decreases in summer and it is necessary to compensate for the decrease in the amount of steam generated in the exhaust heat recovery boiler as the amount of exhaust gas decreases.
- other than steam turbines such as cogeneration plants and desalination plants This is to supply steam.
- the heat balance inside the exhaust heat recovery boiler differs greatly between when the auxiliary combustion device is ignited and the exhaust gas is heated and when the auxiliary combustion device is extinguished.
- the amount of evaporation may increase too much and the degree of superheating of the steam may decrease, or conversely, the degree of superheating of the steam may increase excessively.
- the object of the present invention is to solve the problems of the prior art and appropriately distribute the amount of fuel input to the auxiliary combustion devices installed at multiple locations in the exhaust heat recovery boiler according to the operation status of the exhaust heat recovery boiler.
- An object is to provide an exhaust heat recovery boiler that can be used.
- Another object of the present invention is to provide an exhaust heat recovery boiler capable of appropriately distributing the amount of fuel input to the auxiliary combustion devices installed at a plurality of locations in the exhaust heat recovery boiler according to the operation status of the exhaust heat recovery boiler. It is to provide a power plant equipped with.
- an exhaust gas recovery boiler includes a plurality of heat exchangers including a superheater, an evaporator, and a economizer along a flow direction of exhaust gas from a gas turbine.
- a first stage auxiliary combustion device for heating the exhaust gas on the upstream side of the superheater, and an upstream side of the evaporator, in an exhaust gas recovery boiler that is disposed inside and generates steam using the exhaust gas of the gas turbine
- a second stage auxiliary combustion device for heating the exhaust gas, a first stage auxiliary combustion apparatus, a fuel supply system for distributing and supplying fuel to the second stage auxiliary combustion apparatus, and the first stage
- the ratio of the fuel to be supplied to each of the auxiliary combustion devices and the second-stage auxiliary combustion device to the total fuel input amount is preset according to the total fuel input amount, and the fuel to be input to each auxiliary fuel device according to the distribution ratio Controlling the distribution of fuel Characterized by comprising a distribution control means.
- a power plant includes a gas turbine that rotationally drives a turbine with high-temperature, high-pressure combustion gas, and a plurality of superheaters, evaporators, and economizers along the flow direction of exhaust gas from the gas turbine.
- An exhaust gas recovery boiler that generates steam using exhaust gas from the gas turbine, a steam turbine driven by the steam generated in the exhaust gas recovery boiler, the gas turbine, and the A generator driven by a steam turbine, wherein the exhaust gas recovery boiler includes a first stage auxiliary combustion device that heats the exhaust gas upstream of the superheater, and the exhaust gas upstream of the evaporator.
- the distribution ratio of the fuel to be supplied to the auxiliary combustion apparatus and the second stage auxiliary combustion apparatus with respect to the total fuel input amount is set in advance according to the total fuel input amount.
- a fuel distribution control means for controlling distribution.
- FIG. 1 is a system diagram of a power plant including an exhaust heat recovery boiler according to an embodiment of the present invention.
- 1 is a schematic view showing an exhaust heat recovery boiler according to an embodiment of the present invention. These are the graphs which show the change of the fuel distribution to the auxiliary combustion apparatus in the waste heat recovery boiler by one Embodiment of this invention.
- FIG. 1 is a system diagram of a combined cycle type power plant to which an exhaust heat recovery boiler according to the present embodiment is applied.
- reference numeral 10 indicates a generator
- 12 indicates a steam turbine
- 14 indicates a gas turbine
- Reference numeral 16 indicates an exhaust heat recovery boiler.
- the generator 10 is connected by the same drive shaft 18 as the steam turbine 12 and the gas turbine 14.
- An air compressor 20 is connected to the drive shaft 18.
- the air compressor 20 compresses air A sucked from the outside into a high temperature and high pressure and supplies the compressed air to the combustor 22.
- the compressed air is mixed with the fuel supplied from the fuel system 24 and burned, and high-temperature and high-pressure combustion gas is sent to the gas turbine 14.
- the turbine of the gas turbine 14 is rotationally driven, and the generator 10 rotates.
- the exhaust gas 25 discharged from the gas turbine 14 is guided to the exhaust heat recovery boiler 16 through the exhaust duct 26.
- a high temperature superheater 28 in order from the upstream side along the flow direction of the exhaust gas 25 discharged from the gas turbine 14,
- Four types of heat exchangers such as an evaporator 32 and a economizer 34 are installed.
- a steam drum 36 is installed in the evaporator 32.
- the economizer 34 heats the boiler feed water with the heat of the exhaust gas 25 and then supplies it to the steam drum 36.
- the steam drum 36 performs gas-liquid separation of the saturated steam generated in the evaporator 32, and maintains a balance with the saturated steam by maintaining the interior at a predetermined water level.
- the water that has been gas-liquid separated by the steam drum 36 is reintroduced into the evaporator 32.
- the saturated steam inside the steam drum 36 is sent to the low-temperature superheater 30 through the saturated steam pipe 38 and superheated here, and further guided to the high-temperature superheater 28 where the steam is further superheated.
- a temperature reducer 40 for adjusting the steam temperature is installed between the low temperature superheater 30 and the high temperature superheater 28.
- An outlet pipe 42 is connected to the boiler outlet of the high-temperature superheater 28, and the superheated steam superheated by the high-temperature superheater 28 is sent to the steam turbine 12 through the outlet pipe 42 and performs expansion work to perform the steam turbine. 12 is rotated.
- the steam that has finished the work is led to the condenser 43 and returned to the water, is pressurized by the feed water pump 46 through the condensate return pipe 45 by the condensate pump 46, and is returned to the economizer 34.
- fuel supply pipes 54 and 55 for supplying fuel to the auxiliary combustion devices 50 and 52, respectively, are branched.
- the auxiliary combustion devices 50 and 52 are installed at two places as follows.
- the first stage auxiliary combustion device 50 is disposed at the most upstream position in the flow direction of the exhaust gas 25, and is installed upstream of the high-temperature superheater 28 in the case of the exhaust heat recovery boiler 16 of this embodiment.
- a plurality of burners 51 are installed toward the high-temperature superheater 28 on the downstream side.
- the first fuel supply pipe 54 is provided with a fuel adjustment valve 56 and a fuel cutoff valve 57, and controls the amount of fuel to be burned by the burner 51 by adjusting the opening of the fuel adjustment valve 56. Yes.
- the second stage auxiliary burner 52 is disposed at a position downstream of the first stage auxiliary burner 50, in the case of this embodiment, upstream of the evaporator 32.
- a plurality of burners 53 are installed toward the evaporator 32 on the downstream side.
- the second fuel supply pipe 55 is provided with a fuel adjustment valve 58 that adjusts the fuel input amount and a fuel cutoff valve 59 that closes when the burner 53 is extinguished.
- reference numeral 60 indicates a control device that controls ignition, extinguishing, and fuel injection amount of the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52.
- the flow rate of the fuel flowing through the fuel system 24 is detected by the flow meter 62 and input to the control device 60.
- the distribution ratio of the fuel input amount is set in advance as shown in FIG. 3, and the controller 60 controls the fuel input amount. Based on the relationship, the opening amounts of the fuel adjustment valves 56 and 58 are respectively adjusted to control the amount of fuel injected into the first stage auxiliary burner 50 and the second stage auxiliary burner 52. Yes.
- the exhaust heat recovery boiler according to the present embodiment is configured as described above. Next, its operation and effects will be described. First, the operation of the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52 in the exhaust heat recovery boiler 16 will be described. Since the second stage auxiliary burner 52 is installed upstream of the evaporator 32, when the exhaust gas 25 is heated by the flame blown from the burner 53, the amount of evaporation in the evaporator 32 is mainly increased. Can be increased.
- the first stage auxiliary combustion device 50 is disposed upstream of the high temperature superheater 28 and the low temperature superheater 30, when the exhaust gas 25 is heated by the flame blown from the burner 51, The superheat degree of the steam generated in the high temperature superheater 28 and the low temperature superheater 30 can be increased.
- the horizontal axis represents the total amount of fuel input to the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52
- the vertical axis represents the amount of fuel input to each auxiliary combustion device 50, 52.
- a broken line A indicates a change in the amount of fuel input to the first-stage auxiliary burner 50
- a broken line B indicates a change in the amount of fuel input to the second-stage auxiliary burner 52. Since the horizontal axis represents the total amount of fuel input, the sum of the slope values of the polygonal line A and the polygonal line B is 1.
- the fuel is distributed to the first-stage auxiliary burner 50 and the second-stage auxiliary burner 52 as follows as the amount of fuel input increases.
- the method of distributing the fuel input amount is changed into three regions of a small input amount region, an intermediate input amount region, and a large input amount region.
- the second stage auxiliary combustion device when the exhaust heat recovery boiler 16 is operated without igniting the auxiliary combustion devices 50 and 52, the amount of steam is insufficient, and when the amount of steam to be supplied to the steam turbine 12 is increased, first, the second stage auxiliary combustion device.
- the burner 53 of 52 is ignited to increase the amount of fuel input to the auxiliary combustion device 52 (straight line b1). From the start-up stage, the second stage auxiliary burner 52 and the first stage auxiliary burner 50 are ignited to increase the fuel at the same time, or the first stage prior to the second stage auxiliary burner 52.
- the auxiliary combustion device 50 is ignited and fuel is increased, the high temperature superheater 28 and the low temperature superheater 30 are overheated with high temperature exhaust gas while the amount of evaporation is not sufficient.
- the steam temperature at the boiler outlet is controlled by a temperature reducer 40 installed between the high-temperature superheater 28 and the low-temperature superheater 30, and by overheating the steam,
- the spray flow rate becomes excessive, and water induction into the high temperature superheater 28 and the low temperature superheater 30 becomes a problem.
- ignition and fuel injection to the second-stage auxiliary combustion device 52 are started first, and the first-stage auxiliary combustion device 50 is stopped in the small injection amount region.
- the control device 60 sets the fuel input amount to the second stage auxiliary combustor 52 at a constant rate in response to a request for increasing the steam flow rate. Increase linearly. As the amount of fuel input increases, the thermal power of the burner 53 increases, so the amount of steam generated in the evaporator 32 by the exhaust gas 25 heated by the burner 53 increases. The steam is sequentially sent from the evaporator 32 to the low temperature superheater 30 and the high temperature superheater 28, where the steam is superheated by the exhaust gas 25 discharged from the gas turbine 14 and sent to the steam turbine 12.
- the first stage auxiliary combustion device 50 since the first stage auxiliary combustion device 50 is stopped, the steam is not overheated by the high temperature superheater 28 and the low temperature superheater 30, and spraying by the temperature reducer 40 that controls the steam temperature is prevented. It is possible to appropriately control the steam temperature without becoming excessive.
- the increase amount of the steam supplied to the steam turbine 12 is not so large, so the first stage auxiliary combustion apparatus 50 is stopped and only the second stage auxiliary combustion apparatus 52 is used. Even when it is in operation, the required amount of steam increase can be sufficiently covered.
- the first stage auxiliary burner 50 is also ignited. However, after the burner 51 is ignited, it is maintained constant after reaching the amount of fuel input necessary for combustion as a seed flame (straight line a1). At the same time, in the second stage auxiliary burner 52, a constant amount of fuel is supplied while the amount of fuel input to the first stage auxiliary burner 50 increases.
- control device 60 linearly increases the amount of fuel input to the second stage auxiliary combustor 52 at a constant rate (straight line b2). During this time, in the first stage auxiliary burner 50, the burner 51 continues to burn as a seed flame.
- the amount of steam evaporated by the evaporator 32 increases, but without the additional cooking by the first stage auxiliary combustion device 50, the high temperature superheater 28, the low temperature superheater. In 30, the steam can be sufficiently heated by the exhaust gas 25.
- the burner 51 of the first stage auxiliary combustion device 50 is in a state of being ignited, so that it is necessary to increase the degree of superheating of the steam. It is possible to respond quickly.
- control device 60 distributes the fuel input amount in the large input amount region. Control will be transferred.
- control device 60 supplies fuel to both the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52. Increase the amount by a certain percentage.
- the amount of steam generated in the evaporator 32 increases due to an increase in the amount of fuel input to the second stage auxiliary burner 52, and the first stage auxiliary burner 50 heats. If the temperature of the exhaust gas 25 is not increased, the steam is not sufficiently heated in the high temperature superheater 28 and the low temperature superheater 30 and the steam temperature at the boiler outlet may be lowered.
- the amount of fuel input is increased to the first stage auxiliary burner 50 at a constant rate as shown by the straight line a2.
- the thermal power of 51 is increased to raise the temperature of the exhaust gas 25.
- the superheat degree of the steam is increased by the temperature high temperature superheater 28 and the low temperature superheater 30.
- the rate of increase of the fuel input to the first stage auxiliary combustor 50 is greater. It is set to be larger than the rate of increase of the fuel to be input to the second stage auxiliary burner 52.
- the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52 are connected to each other. While increasing the amount of fuel input, it is possible to smoothly supply an appropriate amount of steam at an appropriate temperature. Note that the rate of increase in the amount of fuel input to each of the first-stage auxiliary burner 50 and the second-stage auxiliary burner 52 (inclinations of the straight line a2 and the straight line b3) is an example and is not limited to this. Absent.
- the amount of fuel input to the first stage auxiliary combustion device 50 and the second stage auxiliary combustion device 52 is not individually controlled, but the total amount of fuel input is distributed in advance at a certain ratio. Therefore, if the amount of fuel input to the first stage auxiliary combustion device 50 is determined, the fuel injection to the second stage auxiliary combustion device 52 is also controlled in a direction that makes the relationship between the amount of generated steam and the vapor temperature appropriate. It will be. In this way, the control of fuel distribution to the first stage auxiliary combustion apparatus 50 and the second stage auxiliary combustion apparatus 52 can be simplified.
- exhaust heat recovery boiler of the present invention can be applied not only to a steam turbine but also to a plant that supplies steam to, for example, a desalination plant.
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Abstract
Description
図1は、本実施形態による排熱回収ボイラが適用されるコンバインドサイクル型の発電プラントの系統図である。
このうち、第1段目の助燃装置50は、排ガス25の流れ方向において最上流の位置に配置され、この実施形態の排熱回収ボイラ16の場合、高温過熱器28の上流側に設置されている。この第1段目の助燃装置50には、複数のバーナ51が下流側の高温過熱器28に向けて設置されている。第1の燃料供給配管54には、燃料調整弁56と燃料遮断弁57が配設されており、バーナ51で燃焼させる燃料投入量を燃料調整弁56の開度を調整することで制御している。バーナ51を消火するときには燃料遮断弁57が閉じるようになっている。
第2段目の助燃装置52は、第1段目の助燃装置50より下流位置、この実施形態の場合、蒸発器32の上流側に配置されている。この第2段目の助燃装置52には複数のバーナ53が下流側の蒸発器32に向けて設置されている。第2の燃料供給配管55には、燃料投入量を調整する燃料調整弁58とバーナ53を消火するときに閉じる燃料遮断弁59が配設されている。
まず、第1段目の助燃装置50と第2段目の助燃装置52の排熱回収ボイラ16における作用について説明する。
第2段目の助燃装置52は、蒸発器32の上流に設置されていることから、バーナ53から噴き出される火炎で排ガス25が加熱されると、主に、蒸発器32での蒸発量を増大させることができる。
図3において、この実施形態では、小投入量域、中間投入量域、大投入量域の3つの領域に分けてそれぞれ燃料投入量の配分の仕方を変えている。
Claims (6)
- ガスタービンから排出ガスの流れ方向にそって過熱器、蒸発器、節炭器からなる複数の熱交換器がダクト内に配置され、前記ガスタービンの排ガスを利用して蒸気を発生する排ガス回収ボイラにおいて、
前記過熱器の上流側で前記排ガスを加熱する第1段目の助燃装置と、
前記蒸発器の上流側で前記排ガスを加熱する第2段目の助燃装置と、
前記第1段目の助燃装置と前記第2段目の助燃装置に燃料を分配して供給する燃料供給系と、
前記第1段目の助燃装置と前記第2段目の助燃装置にそれぞれ投入する燃料の全燃料投入量に対する配分比が、全燃料投入量に応じてあらかじめ設定され、前記配分比にしたがって各助燃装置に投入する燃料の分配を制御する燃料分配制御手段と、
を具備したことを特徴とする排熱回収ボイラ。 - 前記燃料分配制御手段は、蒸気量増加に従って、まず前記第2段目の助燃装置への燃料投入量を増大させ、その後、前記第1段目の助燃装置への燃料投入量を増大させるように燃料の分配を制御することを特徴とする請求項1に記載の排熱回収ボイラ。
- 前記燃料分配制御手段は、前記過熱器での蒸気過熱度が十分な間、前記第1段目の助燃装置への燃料投入量は一定にして種火の状態を保持したまま、前記第2段目の助燃装置への燃料投入量を増加させることを特徴とする請求項2に記載の排熱回収ボイラ。
- 高温、高圧の燃焼ガスによってタービンを回転駆動するガスタービンと、
前記ガスタービンから排出ガスの流れ方向にそって過熱器、蒸発器、節炭器からなる複数の熱交換器がダクト内に配置され、前記ガスタービンの排ガスを利用して蒸気を発生する排ガス回収ボイラと、
前記排ガス回収ボイラで発生した蒸気により駆動される蒸気タービンと、
前記ガスタービンおよび前記蒸気タービンによって駆動される発電機と、を備え、
前記排ガス回収ボイラは、
前記過熱器の上流側で前記排ガスを加熱する第1段目の助燃装置と、
前記蒸発器の上流側で前記排ガスを加熱する第2段目の助燃装置と、
前記第1段目の助燃装置と前記第2段目の助燃装置に燃料を分配して供給する燃料供給系と、
前記第1段目の助燃装置と前記第2段目の助燃装置にそれぞれ投入する燃料の全燃料投入量に対する配分比が、全燃料投入量に応じてあらかじめ設定され、前記配分比にしたがって各助燃装置に投入する燃料の分配を制御する燃料分配制御手段と、を具備したことを特徴とする発電プラント。 - 前記排ガス回収ボイラの燃料分配制御手段は、蒸気量増加に従って、まず前記第2段目の助燃装置への燃料投入量を直線的に増大させ、その後前記第1段目の助燃装置への燃料投入量を増大させることを特徴とする請求項4に記載の発電プラント。
- 前記排ガス回収ボイラの燃料分配制御手段は、前記過熱器での蒸気過熱度が十分な間、前記第1段目の助燃装置への燃料投入量は一定にして種火の状態を保持したまま、前記第2段目の助燃装置への燃料投入量を増加させることを特徴とする助燃装置を有する請求項5に記載の発電プラント。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/007,141 US20140174053A1 (en) | 2011-03-25 | 2012-03-26 | Heat recovery steam generator and power plant |
DE112012001451.0T DE112012001451T5 (de) | 2011-03-25 | 2012-03-26 | Wärmerückgewinnungsdampferzeuger und Kraftwerk |
KR1020137027752A KR101500895B1 (ko) | 2011-03-25 | 2012-03-26 | 배열 회수 보일러 및 발전 플랜트 |
US15/873,650 US10344627B2 (en) | 2011-03-25 | 2018-01-17 | Heat recovery steam generator and power plant |
Applications Claiming Priority (2)
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JP2011-067530 | 2011-03-25 | ||
JP2011067530A JP5537475B2 (ja) | 2011-03-25 | 2011-03-25 | 排熱回収ボイラおよび発電プラント |
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US14/007,141 A-371-Of-International US20140174053A1 (en) | 2011-03-25 | 2012-03-26 | Heat recovery steam generator and power plant |
US15/873,650 Division US10344627B2 (en) | 2011-03-25 | 2018-01-17 | Heat recovery steam generator and power plant |
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WO2012133332A1 true WO2012133332A1 (ja) | 2012-10-04 |
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PCT/JP2012/057784 WO2012133332A1 (ja) | 2011-03-25 | 2012-03-26 | 排熱回収ボイラおよび発電プラント |
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US (2) | US20140174053A1 (ja) |
JP (1) | JP5537475B2 (ja) |
KR (1) | KR101500895B1 (ja) |
DE (1) | DE112012001451T5 (ja) |
WO (1) | WO2012133332A1 (ja) |
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JP7088812B2 (ja) * | 2018-11-12 | 2022-06-21 | 三菱重工業株式会社 | コンバインドサイクルプラント、その制御装置、及びその運転方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01318802A (ja) * | 1988-06-16 | 1989-12-25 | Hitachi Ltd | 再熱型コンバインドプラントの蒸気温度制御システム |
JP2001108202A (ja) * | 1999-10-05 | 2001-04-20 | Babcock Hitachi Kk | 排熱回収ボイラ |
JP2004068652A (ja) * | 2002-08-02 | 2004-03-04 | Mitsubishi Heavy Ind Ltd | コンバインドサイクル発電プラントおよびその起動方法 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH05203146A (ja) * | 1992-01-29 | 1993-08-10 | Hitachi Ltd | ガスタービン燃焼器及びガスタービン発電装置 |
US6092362A (en) * | 1996-11-27 | 2000-07-25 | Hitachi, Ltd. | Gas-turbine combustor with load-responsive premix burners |
JP3794796B2 (ja) * | 1997-08-29 | 2006-07-12 | 三菱重工業株式会社 | コンバインド発電プラント |
US6092363A (en) * | 1998-06-19 | 2000-07-25 | Siemens Westinghouse Power Corporation | Low Nox combustor having dual fuel injection system |
JP2001116208A (ja) * | 1999-10-14 | 2001-04-27 | Babcock Hitachi Kk | ダクトバーナ付き排熱回収ボイラ |
RU2436969C2 (ru) | 2007-03-02 | 2011-12-20 | Ансальдо Энергия С.П.А. | Электростанция комбинированного цикла и соответствующий способ эксплуатации |
-
2011
- 2011-03-25 JP JP2011067530A patent/JP5537475B2/ja active Active
-
2012
- 2012-03-26 WO PCT/JP2012/057784 patent/WO2012133332A1/ja active Application Filing
- 2012-03-26 KR KR1020137027752A patent/KR101500895B1/ko active IP Right Grant
- 2012-03-26 US US14/007,141 patent/US20140174053A1/en not_active Abandoned
- 2012-03-26 DE DE112012001451.0T patent/DE112012001451T5/de not_active Ceased
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2018
- 2018-01-17 US US15/873,650 patent/US10344627B2/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01318802A (ja) * | 1988-06-16 | 1989-12-25 | Hitachi Ltd | 再熱型コンバインドプラントの蒸気温度制御システム |
JP2001108202A (ja) * | 1999-10-05 | 2001-04-20 | Babcock Hitachi Kk | 排熱回収ボイラ |
JP2004068652A (ja) * | 2002-08-02 | 2004-03-04 | Mitsubishi Heavy Ind Ltd | コンバインドサイクル発電プラントおよびその起動方法 |
Also Published As
Publication number | Publication date |
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JP2012202610A (ja) | 2012-10-22 |
US20180142580A1 (en) | 2018-05-24 |
DE112012001451T5 (de) | 2014-01-09 |
KR101500895B1 (ko) | 2015-03-09 |
KR20140024334A (ko) | 2014-02-28 |
JP5537475B2 (ja) | 2014-07-02 |
US10344627B2 (en) | 2019-07-09 |
US20140174053A1 (en) | 2014-06-26 |
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