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WO2014033837A1 - Chaudière à récupération de chaleur perdue, procédé de commande de ladite chaudière à récupération de chaleur perdue, et centrale électrique à cycle combiné l'employant - Google Patents

Chaudière à récupération de chaleur perdue, procédé de commande de ladite chaudière à récupération de chaleur perdue, et centrale électrique à cycle combiné l'employant Download PDF

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Publication number
WO2014033837A1
WO2014033837A1 PCT/JP2012/071698 JP2012071698W WO2014033837A1 WO 2014033837 A1 WO2014033837 A1 WO 2014033837A1 JP 2012071698 W JP2012071698 W JP 2012071698W WO 2014033837 A1 WO2014033837 A1 WO 2014033837A1
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WIPO (PCT)
Prior art keywords
exhaust gas
steam
heat recovery
recovery boiler
exhaust
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.)
Ceased
Application number
PCT/JP2012/071698
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English (en)
Japanese (ja)
Inventor
恩敬 金
吉田　卓弥
矢敷　達朗
幸徳 片桐
高橋　一雄
小山　一仁
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Hitachi Ltd
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Hitachi Ltd
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Publication date
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Priority to PCT/JP2012/071698 priority Critical patent/WO2014033837A1/fr
Publication of WO2014033837A1 publication Critical patent/WO2014033837A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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

  • the present invention relates to an exhaust heat recovery boiler, an exhaust heat recovery boiler control method, and a combined cycle power plant using the same.
  • the combined cycle power plant includes an exhaust heat recovery boiler that uses hot exhaust gas discharged from a gas turbine as a heat source to boil feed water to obtain steam and supply the steam to the steam turbine.
  • Power generation consisting of multiple gas turbines, exhaust heat boilers (exhaust heat recovery boilers), and steam turbines with the aim of generating steam at an earlier timing from the exhaust heat recovery boiler when the plant is started in order to shorten the startup time
  • warm-up is performed between the main steam pipe connected to the steam turbine from the exhaust heat boiler (exhaust heat recovery boiler) and the main steam pipe of another exhaust heat boiler (exhaust heat recovery boiler) in the same power plant.
  • Some have a connecting pipe see, for example, Patent Document 1).
  • the startup time of the power plant can be shortened.
  • the exhaust heat recovery boiler is designed to have a large heat capacity in order to ensure a heat transfer area. For this reason, a relatively long time is required for temperature rise and steam generation, and it takes time to establish the steam conditions that can be supplied to the steam turbine.
  • exhaust gas having a temperature lower than the temperature of the heat transfer surface of the exhaust heat recovery boiler may flow before and immediately after ignition of the gas turbine. At this time, since the temperature of the exhaust heat recovery boiler is once lowered by the inflowing exhaust gas, steam generation is delayed.
  • the present invention has been made based on the above-described matters, and an object of the present invention is to generate steam at an early timing and supply it to the steam turbine, and to reduce the start-up time of the plant, the exhaust heat recovery boiler, and the exhaust heat recovery boiler And a combined cycle power plant using them.
  • the present application includes a plurality of means for solving the above-described problems. For example, in an exhaust heat recovery boiler that generates steam using exhaust gas supplied from an external heat source and water supplied from the outside.
  • a box-shaped casing provided with openings at both ends, an exhaust gas inflow part provided on one opening side of the casing, an exhaust gas outflow part provided on the other opening side of the casing, and the casing
  • An exhaust gas flow path section provided in the interior of the exhaust gas flow path section, a plurality of steam generation sections arranged in parallel in a direction orthogonal to the flow direction of the exhaust gas in the exhaust gas flow path section, and a partition that divides the plurality of steam generation sections
  • the plate the adjusting means for adjusting the flow of the exhaust gas so that the exhaust gas selectively flows into all or part of the plurality of steam generation units, Serial exhaust gas allowed to flow into the portion of the steam generator, then the exhaust gas sequentially so as to flow into another steam generator, characterized by comprising a control device for operating the adjustment means.
  • the exhaust heat recovery boiler is divided into a plurality of steam generation units arranged in parallel with respect to the inflow direction of the exhaust gas, and at the start of startup, a part of the plurality of steam generation units is heated.
  • the steam temperature can be increased to a predetermined temperature in a short time.
  • the plant start-up time can be shortened.
  • FIG. 1 is a schematic configuration diagram showing an exhaust heat recovery boiler, a control method for an exhaust heat recovery boiler, and a control system for an exhaust heat recovery boiler constituting a first embodiment of a combined cycle power plant using them.
  • FIG. 1 is a system configuration diagram showing an embodiment of an exhaust heat recovery boiler of the present invention, an exhaust heat recovery boiler control method, and a combined cycle power plant using the exhaust heat recovery boiler
  • FIG. 2 is an exhaust heat recovery boiler of the present invention. It is a schematic block diagram which shows the control system of the waste heat recovery boiler which comprises 1st Embodiment of the control method of a waste heat recovery boiler, and the combined cycle power plant using these.
  • FIG. 1 shows a system flow of a combined cycle power plant having a gas turbine 3, an exhaust heat recovery boiler 4, a steam turbine 5, a generator 6, and a condenser 7.
  • the gas turbine 3 includes a compressor 3 a, a turbine 3 b, a combustor 3 c, and a drive shaft 30.
  • the compressor 3a sucks and pressurizes air and supplies it as combustion air to the combustor 3c.
  • the combustor 3c mixes and burns the combustion air with fuel to generate high-temperature combustion gas.
  • the combustion gas drives the turbine 3 b and drives the compressor 3 b, the steam turbine 5 and the generator 6 through the drive shaft 30.
  • the exhaust heat recovery boiler 4 exchanges heat between the exhaust gas 1 from the gas turbine 3 and the feed water 2C to generate steam 2A, and supplies the steam 2A to the steam turbine 5.
  • the feed water 2 ⁇ / b> C supplied to the exhaust heat recovery boiler 4 is stored in the lower part of the condenser 7 and is pumped to the exhaust heat recovery boiler 4 by the feed water pump 8.
  • the exhaust gas 1 from the gas turbine 3 is discharged into the atmosphere from a stack (not shown) after heat exchange with the feed water 2C.
  • the steam turbine 5 is connected to the gas turbine 3 by a drive shaft 30 and is driven by the introduction of the steam 2A generated in the exhaust heat recovery boiler 4.
  • the steam 2 ⁇ / b> B that has performed work in the steam turbine 5 is condensed in the condenser 7, and then returned to the exhaust heat recovery boiler 4 by the feed water pump 8.
  • the generator 6 is connected to the steam turbine 5 by a drive shaft 30, is driven by the gas turbine 3 and the steam turbine 5, and sends the generated power to the system.
  • the exhaust heat recovery boiler 4 includes a box-shaped casing 4A in which the exhaust gas 1 from the gas turbine 3 is introduced and the outer peripheral portion is covered with a heat insulating material, and an exhaust gas flow path portion 4B in the casing 4A.
  • the first and second partition plates 14A and 14B divided into three in the width direction, the first exhaust gas flow path 4Ba formed by the first partition plate 14A and the casing 4A, the first partition plate 14A and the second partition plate 14B.
  • First to third steam generation units 10a to 10c provided respectively, and first to third exhaust gas inflow adjusting means 11a to 11a provided at the respective upstream inlets of the first to third exhaust gas passages 4Ba to 4Bc. 11c , Generated by first to third exhaust gas outflow adjusting means 12a to 12c provided at each outlet on the downstream side of the first to third exhaust gas passages 4Ba to 4Bc, and the first to third steam generators 10a to 10c.
  • the first to third steam control valves 13a to 13c for adjusting the flow rate of the supplied steam to the steam turbine 5 are provided.
  • the casing 4A has openings at both ends, the opening on one side forms an exhaust gas inflow part 18 for introducing the exhaust gas 1 from the gas turbine 3, and the other opening exchanges heat with the steam generating part.
  • the exhaust gas outflow part 19 which discharges the exhaust gas after having been formed is formed.
  • the exhaust heat recovery boiler 4 is configured by the first to third units 40a to 40c divided into three in the width direction in the exhaust gas passage portion 4B in the casing 4A, and the exhaust gas passage portion 4B. From the upstream side toward the downstream side, the first unit 40a is disposed on the leftmost side, the second unit 40b is disposed on the center, and the third unit 40c is disposed on the rightmost side.
  • Each unit includes an independent exhaust gas flow path, a steam generation unit, an exhaust gas inflow adjusting means, an exhaust gas outflow adjusting means, and a steam control valve.
  • the water supply is supplied from the water supply pump 8 through the water supply pipes to the steam generators 10a to 10c of the first to third units 40a to 40c.
  • steam is supplied to the turbine 5 from the steam generators 10a to 10c of the first to third units 40a to 40c via the main steam pipes.
  • the first to third steam control valves 13a to 13c are provided in each main steam pipe.
  • Each main steam pipe is provided with temperature sensors 15a to 15c for detecting the temperature of the steam generated by the steam generators 10a to 10c.
  • the temperature sensors 15a to 15c output the detected temperatures of the steam generated by the respective steam generation units to the control device 20 described later.
  • the exhaust gas inflow part 18 on the upstream side of the exhaust gas flow path part 4B of the exhaust heat recovery boiler 4 is connected to an exhaust gas duct 9 into which the exhaust gas 1 from the gas turbine 3 is introduced.
  • the exhaust gas duct 9 is provided with a temperature sensor 16 that detects the exhaust gas temperature of the gas turbine 3 and a flow rate sensor 17 that detects the flow rate of the exhaust gas 1.
  • the temperature sensor 16 outputs the detected exhaust gas temperature, and the flow sensor 17 outputs the detected exhaust gas flow rate to the control device 20 described later.
  • FIG. 3 is a longitudinal side view showing the exhaust heat recovery boiler according to the present invention, the exhaust heat recovery boiler control method, and the apparatus configuration of the exhaust heat recovery boiler constituting the first embodiment of the combined cycle power plant using these. It is.
  • the second unit 40b and the third unit 40c are configured in the same manner as the first unit 40a, and the same members are designated by subscripts “a” to “b” or the subscripts of the respective members of the first unit 40a. The description will be omitted as it is shown in place of “c”.
  • the first steam generation unit 10a includes, for example, a superheater 101a, an evaporator 102a, and a economizer 103a arranged in order from the upstream side along the flow direction of the exhaust gas 1, and an upper portion of the casing 4A. It is comprised with the natural-circulation boiler horizontally installed in the heat exchanger tube which has arrange
  • the water supply is supplied to the economizer 103a through the water supply pipe 8 by the water supply pump 8, preheated to a predetermined temperature, and then supplied to the steam drum 104a.
  • the feed water supplied to the steam drum 104a is circulated and heated in the order of the evaporator 102a and the steam drum 104a, and separated into water and steam by the steam drum 104a.
  • the water is circulated again in the evaporator 102a and the steam drum 104a, but the steam is sent to the superheater 101a, where it is further heated, and then supplied to the steam turbine 5 from the main steam pipe.
  • the first exhaust gas inflow adjusting means 11a adjusts the flow rate of the exhaust gas 1 flowing from the gas turbine 3 into the first steam generation unit 10a, and is disposed, for example, on the inlet side of the partition plate 14A.
  • the damper 110a and the damper drive unit 115a can adjust the inflow amount of the exhaust gas 1 in the first exhaust gas passage 4Ba by the damper opening. As shown in FIG. 2, when the opening degree of the damper 110 a is controlled at a position parallel to the flow direction of the exhaust gas 1, the exhaust gas inflow amount becomes maximum, and the damper 110 a of the damper 110 a is crossed with the flow direction of the exhaust gas 1. When the opening degree is controlled, the inflow of the exhaust gas 1 is blocked.
  • the first exhaust gas outflow adjusting means 12a adjusts the flow rate of the exhaust gas 1 flowing out from the first steam generation unit 10a.
  • the first exhaust gas outflow adjustment means 12a is disposed on the outlet side of the partition plate 14A and is exhaust gas in the first exhaust gas passage 4Ba. 1 is configured by a damper 120a capable of adjusting the outflow amount of 1 by the damper opening degree and a drive part 125a of the damper. As shown in FIG. 2, when the opening degree of the damper 120 a is controlled at a position parallel to the flow direction of the exhaust gas 1, the exhaust gas outflow amount becomes maximum, and the damper 120 a is positioned at a position intersecting the flow direction of the exhaust gas 1. When the opening degree is controlled, the outflow of the exhaust gas 1 is blocked.
  • the first steam control valve 13a adjusts the supply flow rate of the steam generated by the first steam generation unit 10a to the steam turbine 5, and can adjust the steam flow rate in the main steam pipe by its opening, for example. It is comprised with the adjustment valve and the drive part of the adjustment valve.
  • Openings of the dampers 110a and 120a constituting the first exhaust gas inflow adjusting means 11a and the first exhaust gas outflow adjusting means 12a are driven by the drive portions 115a and 125a of the dampers that receive a command signal from the control device 20.
  • the valve opening degree of the first steam control valve 13a is controlled by a drive unit that receives a command signal from the control device 20.
  • the heat capacity on the heat receiving side is changed in accordance with the amount of supplied heat, so that the generated steam can be quickly brought to a desired temperature. It is characterized by allowing it to rise. That is, the heat receiving volume and the water supply amount in the exhaust heat recovery boiler 4 on the heat receiving side are changed according to the heat amount of the exhaust gas 1 from the gas turbine 3 that is the supply heat amount. Specifically, during the period in which the exhaust gas 1 has a low calorific value in the plant startup process, high-temperature steam can be generated quickly by controlling the flow of the exhaust gas 1 so as to heat only a part of the steam generator. Can do. As a result, the startup time of the combined cycle power plant can be shortened.
  • FIG. 4 is a control block diagram showing the exhaust heat recovery boiler of the present invention, the control method of the exhaust heat recovery boiler, and the control device constituting the first embodiment of the combined cycle power plant using these.
  • the same reference numerals as those shown in FIG. 1 and FIG. 2 are the same parts, and detailed description thereof will be omitted.
  • the exhaust gas inflow adjusting means 11a to 11c and the exhaust gas outflow adjusting means 12a to 12c are heated so that only a part of the steam generating parts are heated.
  • a control device 20 for controlling the valve opening degrees of the steam control valves 13a to 13c for adjusting the supply flow rate of the steam generated in the steam generating section to the steam turbine 5.
  • the control device 20 calculates the heat capacity on the heat receiving side from the supplied heat amount and outputs an exhaust gas flow rate command signal to each unit, and whether there is a ventilation condition of steam generated by the steam generation unit to the turbine 3
  • the steam flow rate calculation unit 22 that outputs a steam flow rate command signal to each unit and the exhaust gas flow rate command signal are input, and the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflows are input.
  • the first to third exhaust gas flow control output units 23a to 23c for outputting the command signals to the adjusting means 12a to 12c and the steam flow rate command signals are input, and the commands to the first to third steam control valves 13a to 13c are input.
  • First to third steam flow rate control output units 24a to 24c for outputting signals.
  • the exhaust gas flow calculation unit 21 detects the temperature sensor 16 that measures the temperature of the exhaust gas 1 of the gas turbine 3 introduced into the casing 4A, and the exhaust gas of the gas turbine 3 that is introduced into the casing 4A.
  • the detection signal of the flow sensor 17 that measures the flow rate of 1 the detection signals of the temperature sensors 15a to 15c that measure the temperature of the steam generated in each steam generator, and the start / stop command signal of the combined cycle power plant are input To do.
  • the start / stop command signal may be a known method such as determining whether or not the signal indicating the operation mode input from the host controller or the like has a value indicating the start of the start mode. good.
  • the exhaust gas flow calculation unit 21 calculates the heat capacity on the heat receiving side from the exhaust gas temperature as the supply heat amount and the start / stop command signal of the combined cycle power plant, so that the calculated heat capacities are obtained. 3. Output command signals to the exhaust gas flow control output units 23a to 23c.
  • the first exhaust gas flow control output unit 23a outputs a drive command corresponding to the command signal to each of the drive units 115a and 125a of the dampers 110a and 120a constituting the first exhaust gas inflow adjustment unit 11a and the first exhaust gas outflow adjustment unit 12a. .
  • the second exhaust gas flow control output unit 23b sends a drive command corresponding to the command signal to each of the drive units 115b and 125b of the dampers 110b and 120b constituting the second exhaust gas inflow adjustment unit 11b and the second exhaust gas outflow adjustment unit 12b.
  • the third exhaust gas flow control output unit 23c sends a drive command corresponding to the command signal to each of the drive units 115c and 125c of the dampers 110c and 120c constituting the third exhaust gas inflow adjustment unit 11c and the third exhaust gas outflow adjustment unit 12c. Output.
  • the opening degrees of the dampers 110a to 110c constituting the first to third exhaust gas inflow adjusting means 11a to 11c and the dampers 120a to 120c constituting the first to third exhaust gas outflow adjusting means 12a to 12c are controlled. Since the unit into which the exhaust gas 1 is introduced is selectively controlled, the heat capacity on the heat receiving side can be controlled.
  • the steam flow rate calculation unit 22 inputs detection signals from the temperature sensors 15a to 15c that measure the temperature of the steam generated by each steam generation unit and a start / stop command signal for the combined cycle power plant, and is generated by the steam generation unit.
  • the presence / absence of a condition for venting the steam to the steam turbine 5 is calculated, and command signals are output to the first to third steam flow rate control output units 24a to 24c so as to vent from the unit that satisfies the ventilation condition.
  • the first steam flow control output unit 24a outputs a drive command corresponding to the command signal to the drive unit of the first steam control valve 13a, and similarly, the second steam flow control output unit 24b and the third steam flow control output unit.
  • 24c outputs the drive command according to a command signal to each drive part of the 2nd and 3rd steam control valves 13b and 13c.
  • the opening degree of each of the first to third steam control valves 13a to 13c is controlled, and the unit for supplying the generated steam is selectively controlled. Therefore, the steam generated at an early timing is supplied to the steam turbine 5. Can supply. As a result, the plant startup time can be shortened.
  • FIG. 5 is a flowchart showing an exhaust heat recovery boiler of the present invention, an exhaust heat recovery boiler control method, and a start-up process flow of the control device constituting the first embodiment of the combined cycle power plant using these. .
  • the control device 20 determines whether or not the plant is in the starting process (step S1). As a determination method, for example, the determination may be made based on whether or not the signal indicating the operation mode input from the host controller or the like has a value indicating the start of the start mode. When it is determined that the plant is in the starting process, the process proceeds to (Step S2), and otherwise, the process returns to (Step S1). Before starting the plant, the dampers 110a to 110c constituting the first to third exhaust gas inflow adjusting means 11a to 11c and the dampers 120a to 120c constituting the first to third exhaust gas outflow adjusting means 12a to 12c shown in FIG. 120c and the first to third steam control valves 13a to 13c are all in a closed state, and the flow path form through which the exhaust gas 1 from the gas turbine 3 flows into each steam generation section can be expressed as 000.
  • Control device 20 determines whether or not the exhaust gas temperature is equal to or higher than a predetermined value (step S2). Specifically, the exhaust gas flow calculation unit 21 of the control device 20 compares and determines the temperature of the exhaust gas 1 of the gas turbine 3 taken from the temperature sensor 1 and a predetermined specified value gt1.
  • the specified value gt1 is a value of the exhaust gas temperature that can raise the temperature of the steam generating unit 10b, and may be set by bias-adding a predetermined temperature based on the temperature of the steam generating unit 10b at this time, for example. good. If the exhaust gas temperature is equal to or higher than the specified value gt1, the process proceeds to (Step S4), and otherwise, the process proceeds to (Step S3).
  • the control device 20 When the exhaust gas temperature is less than the specified value gt1, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to flow into the first steam generation unit 10a and the third steam generation unit 10c, and to the second steam generation unit 10b.
  • a command signal is output to the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so as to obtain a flow path configuration (flow path configuration 101) that does not flow (step 101).
  • the dampers 110a and 110c and the first and third exhaust gas outflow adjusting means 12a and 12c constituting the first and third exhaust gas flow adjusting means 11a and 11c in the closed state are provided so that the flow path form 101 is obtained.
  • a command signal for opening the dampers 120a and 120c constituting the command, and a command signal for maintaining the closed state of the damper 110b constituting the second exhaust gas flow adjusting means 11b and the damper 12b constituting the second exhaust gas outflow adjusting means 12b Is output to the drive units 115a to 115c and 125a to 125c of each damper. This is done in order to prevent the low temperature exhaust gas 1 from lowering the temperature of the second steam generation unit 10b to be heated first. Note that the processing returns to (step S2) after execution of the processing of (step S3).
  • step S2 when the exhaust gas temperature becomes equal to or higher than the specified value gt1, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to flow into the second steam generation unit 10b, and the first steam generation unit 10a and the first steam generation unit 10a.
  • the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so as to have a flow path configuration (flow path configuration 010) that does not flow into the 3 steam generation section 10c.
  • a command signal is output to (step S4).
  • a command signal for closing 120a and 120c, and a command signal for opening the damper 110b constituting the second exhaust gas flow adjusting means 11b and the damper 120b constituting the second exhaust gas outflow adjusting means 12b are provided for each damper.
  • the heat receiving part that receives the heat of the exhaust gas 1 is only the second steam generation part 10b (the heat capacity is reduced), so that high-temperature steam can be generated quickly.
  • the control device 20 determines whether or not the temperature of the steam generated by the second steam generation unit 10b is equal to or higher than a predetermined value st1 (step S5). Specifically, in the exhaust gas flow calculation unit 21 of the control device 20, the temperature of the steam of the second steam generation unit 10b taken from the temperature sensor 15b is compared with a predetermined specified value st1.
  • the prescribed value st1 is, for example, a steam temperature obtained by subtracting a predetermined value from the steam temperature that satisfies the ventilation condition to the steam turbine 5.
  • the process proceeds to (Step S7), and otherwise, the process returns to (Step S5).
  • Step S5 it may be determined whether the exhaust gas 1 is in a state in which the main body temperature (for example, the internal metal temperature) of the second steam generation unit 10b can be raised. For example, the determination may be made based on whether the temperature of the exhaust gas 1 is higher than a predetermined value compared with a temperature (for example, an internal metal temperature) representing the state of the second steam generation unit 10b.
  • the main body temperature for example, the internal metal temperature
  • the determination may be made based on whether the temperature of the exhaust gas 1 is higher than a predetermined value compared with a temperature (for example, an internal metal temperature) representing the state of the second steam generation unit 10b.
  • control device 20 determines whether or not the temperature of the steam generated by the second steam generating unit 10b is equal to or higher than a predetermined specified value st2 (step S6). Specifically, in the steam flow rate calculation unit 22 of the control device 20, the temperature of the steam of the second steam generation unit 10b taken from the temperature sensor 15b is compared with a predetermined specified value st2.
  • the specified value st2 is, for example, a steam temperature that satisfies a ventilation condition to the steam turbine 5. If the steam temperature is equal to or higher than the specified value st2, the process proceeds to (Step S9), and otherwise, the process returns to (Step S6).
  • Step S6 it may be determined whether or not the steam generated by the second steam generation unit 10b has approached a state in which the steam can be vented to the steam turbine 5.
  • this criterion may be configured by the following items or a combination thereof.
  • the generated steam temperature is higher than a predetermined value by comparison with a temperature representing the state of the steam turbine 5 (for example, a metal temperature inside the steam turbine or a main steam temperature).
  • the generated steam pressure is higher than a predetermined specified value as compared with the internal pressure of the steam turbine 5. ⁇
  • the generated steam flow is higher than the specified value.
  • Step S5 when the steam temperature is equal to or higher than the specified value st1, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to flow into the first steam generation unit 10a and the second steam generation unit 10b, and the third The first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c are commanded so as to have a flow path configuration (flow path configuration 110) that does not flow into the steam generation section 10c. A signal is output (step S7).
  • a command signal for closing the damper 110c constituting the third exhaust gas flow adjusting means 11c and the damper 120c constituting the third exhaust gas outflow adjusting means 12c so as to obtain the flow path form 110 and the first And a command signal for opening the dampers 110a, 110b constituting the second exhaust gas flow adjusting means 11a, 11b and the dampers 120a, 120b constituting the first and second exhaust gas outflow adjusting means 12a, 12b.
  • the heat receiving part that receives the heat of the exhaust gas 1 is added with the first steam generating part 10a only from the second steam generating part 10b, and the heat capacity is increased, so that the steam flow supplied to the steam turbine 5 is increased. be able to.
  • the control device 20 determines whether or not the temperature of the steam generated by the first steam generator 10a is equal to or higher than a predetermined value st1 (step S8). Specifically, in the exhaust gas flow calculation unit 21 of the control device 20, the temperature of the steam of the first steam generation unit 10a taken from the temperature sensor 15a is compared with a predetermined specified value st1. Here, the specified value st1 is the same as (step S5). If the steam temperature is equal to or higher than the specified value st1, the process proceeds to (Step S11), and otherwise, the process returns to (Step S7).
  • step S6 when the steam temperature is equal to or higher than the specified value st2, the control device 20 causes only the generated steam from the second steam generation unit 10b to flow into the steam turbine 5, and the first and third steam generation units 10a. , 10c, command signals are output to the first to third steam control valves 13a to 13c so as not to flow into the steam turbine 5 (step S9).
  • step S9 command signals are output to the first to third steam control valves 13a to 13c so as not to flow into the steam turbine 5.
  • the control device 20 determines whether or not the temperature of the steam generated by the first steam generator 10a is equal to or higher than a predetermined value st2 (step S10). Specifically, the steam flow rate calculation unit 22 of the control device 20 compares and determines the steam temperature of the first steam generation unit 10a taken from the temperature sensor 15a and a predetermined specified value st2. Here, the specified value st2 is the same as (Step S6). If the steam temperature is equal to or higher than the specified value st2, the process proceeds to (Step S12), and otherwise, the process returns to (Step S9).
  • step S8 when the steam temperature is equal to or higher than the specified value st1, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to be converted into the first steam generation unit 10a, the second steam generation unit 10b, and the third steam generation unit 10c.
  • Command signals are output to the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so as to be in a flow path form (flow path form 111) flowing into the Step S11).
  • the dampers 110a to 110c constituting the first to third exhaust gas flow adjusting means 11a to 11c and the dampers constituting the first to third exhaust gas outflow adjusting means 12a to 12c so as to obtain the flow path form 111.
  • Command signals for opening 120a to 110c are output to the drive units 115a to 115c and 125a to 125c of the respective dampers.
  • the heat receiving part that receives the heat of the exhaust gas 1 is added with the third steam generating part 10c from the first and second steam generating parts 10a, 10b, and the heat capacity is increased.
  • the flow rate can be increased. Note that after executing the process of (Step S11), the process proceeds to return.
  • step S10 when the steam temperature is equal to or higher than the specified value st2, the control device 20 causes only the steam generated from the first steam generator 10a and the second steam generator 10b to flow into the steam turbine 5, A command signal is output to the first to third steam control valves 13a to 13c so that the steam generated from the third steam generating section 10c does not flow into the steam turbine 5 (step S12).
  • the high-temperature steam generated by the first steam generation unit 10 a and the second steam generation unit 10 b is vented to the steam turbine 5.
  • the control device 20 determines whether or not the temperature of the steam generated by the third steam generator 10c is equal to or higher than a predetermined value st2 (step S13). Specifically, the steam flow rate calculation unit 22 of the control device 20 compares and determines the steam temperature of the third steam generation unit 10c taken from the temperature sensor 15c and a predetermined specified value st2. Here, the specified value st2 is the same as (Step S6). If the steam temperature is equal to or higher than the specified value st2, the process proceeds to (Step S13), and otherwise, the process returns to (Step S12).
  • Step S10 when the steam temperature is equal to or higher than the specified value st2, the control device 20 determines that the steam generated from the first steam generating unit 10a, the second steam generating unit 10b, and the third steam generating unit 10c is a steam turbine.
  • the command signal is output to the first to third steam control valves 13a to 13c so as to flow into the flow (step S14).
  • the high-temperature steam generated by the first steam generation unit 10a, the second steam generation unit 10b, and the third steam generation unit 10c is vented to the steam turbine 5. Note that after executing the processing of (Step S14), the process proceeds to return.
  • FIG. 6 is a flowchart showing a stop processing flow of the control device constituting the first embodiment of the exhaust heat recovery boiler, the exhaust heat recovery boiler control method of the present invention, and the combined cycle power plant using them. .
  • the control device 20 determines whether or not the plant is in a stop process (step S21).
  • the determination method may be a known method such as determination from the operation mode. If it is determined that the plant is in the process of stopping, the process proceeds to (Step S22) and (Step S25), and otherwise, the process returns to (Step S21).
  • the dampers 110a to 110c constituting the first to third exhaust gas inflow adjusting means 11a to 11c and the damper 120a constituting the first to third exhaust gas outflow adjusting means 12a to 12c shown in FIG. ⁇ 120c and the first to third steam control valves 13a to 13c are all open, and the flow path form through which the exhaust gas 1 from the gas turbine 3 flows into each steam generation section can be expressed as 111.
  • Control device 20 determines whether or not the exhaust gas temperature is equal to or lower than a predetermined value (step S22). Specifically, the exhaust gas flow calculation unit 21 of the control device 20 compares and determines the temperature of the exhaust gas 1 of the gas turbine 3 taken from the temperature sensor 1 and a predetermined specified value gt2.
  • the specified value gt2 is a value at which the exhaust gas lowers the main body temperature (for example, internal metal temperature) of the steam generation unit 10b. For example, it may be set by subtracting a predetermined temperature based on the body temperature of the steam generation unit 10b at this time. If the exhaust gas temperature is less than or equal to the specified value gt2, the process proceeds to (Step S24), and otherwise, the process proceeds to (Step S23).
  • the control device 20 When the exhaust gas temperature exceeds the specified value gt2, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to flow into the first steam generation unit 10a, the second steam generation unit 10b, and the third steam generation unit 10c.
  • Command signals are output to the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so as to maintain the state of (flow path form 111) (step S23). . In addition, it returns to (step S22) after execution of the process of (step S23).
  • step S22 when the exhaust gas temperature becomes equal to or lower than the specified value gt2, the control device 20 causes the exhaust gas 1 from the gas turbine 3 to flow into the first and third steam generation units 10a and 10c and the second steam.
  • a command signal is sent to the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so that the flow path form (flow path form 101) does not flow into the generator 10b.
  • Is output step S24.
  • a command signal for opening 120a, 120c and a command signal for closing the damper 110b constituting the second exhaust gas flow adjusting means 11b and the damper 120b constituting the second exhaust gas outflow adjusting means 12b are provided for each damper. Output to the driving units 115a to 115c and 125a to 125c. As a result, the inflow of the exhaust gas 1 to the second steam generation unit 10b is blocked, and the main body temperature of the second steam generation unit 10b is prevented from being lowered. As a result, the activation time at the next activation can be shortened. After executing (Step S24), the process proceeds to (Step S28).
  • the control device 20 determines that the temperature of the steam generated by the first to third steam generation units 10a to 10c is a predetermined specified value st3. It is determined whether it is below (step S25). Specifically, the steam flow rate calculation unit 22 of the control device 20 compares the steam temperatures of the first to third steam generation units 10a to 10c taken from the temperature sensors 15a to 15c with a predetermined specified value st3. to decide.
  • the specified value st3 is, for example, a steam temperature obtained by adding a predetermined value from the steam temperature that satisfies the ventilation condition to the steam turbine 5. If the steam temperature of any of the fetched first to third steam generators 10a to 10c is equal to or lower than the specified value st3, the process proceeds to (Step S26). Otherwise, the process returns to (Step S25).
  • Step S25 When the steam temperature of any of the first to third steam generation units 10a to 10c is equal to or less than the specified value st3 in (Step S25), the control device 20 sends the generated steam from the corresponding steam generation unit to the steam turbine 5. A closing command is output to the steam control valve of the corresponding unit so as not to flow in (step S26). As a result, the supply of the steam whose temperature has decreased in the steam generation section to the steam turbine 5 is stopped.
  • the control device 20 determines whether or not all of the first to third steam control valves 13a to 13c are closed (step S27). If all of the first to third steam control valves 13a to 13c are closed, the process proceeds to return, and otherwise returns to (step S25).
  • Step S24 After execution of the process, the control device 20 determines whether or not the exhaust gas flow rate is equal to or less than a specified value (step S28). Specifically, the exhaust gas flow calculation unit 21 of the control device 20 compares and determines the flow rate of the exhaust gas 1 of the gas turbine 3 taken in from the flow sensor 17 and a predetermined specified value gt3.
  • the specified value gt3 is a value with which it can be determined whether or not the exhaust gas 1 flows into the exhaust heat recovery boiler 4. If the exhaust gas flow rate is less than or equal to the specified value gt3, the process proceeds to (Step S29), and otherwise returns to (Step S24). In (step S28), for example, even if the rotational speed of the gas turbine 3 is detected and is equal to or less than a predetermined value, it is determined that the exhaust gas 1 does not flow into the exhaust heat recovery boiler 4. good.
  • step S28 when the exhaust gas flow rate becomes equal to or less than the specified value gt3, the control device 20 uses the flow path configuration in which the exhaust gas 1 from the gas turbine 3 does not flow into the first to third steam generation units 10a to 10c ( A command signal is output to the first to third exhaust gas inflow adjusting means 11a to 11c and the first to third exhaust gas outflow adjusting means 12a to 12c so as to obtain the flow path form 000) (step S29). Specifically, the dampers 110a to 110c constituting the first to third exhaust gas flow adjusting means 11a to 11c and the dampers constituting the first to third exhaust gas outflow adjusting means 12a to 12c so as to obtain the flow path form 000.
  • Command signals for closing 120a to 120c are output to the drive units 115a to 115c and 125a to 125c of the respective dampers.
  • the inflow and outflow of the exhaust gas 1 to all the steam generation units 10a to 10c are blocked, and the main body temperature of all the steam generation units 10a to 10c is prevented from being lowered.
  • the activation time at the next activation can be shortened.
  • the exhaust heat recovery boiler 4 is moved in the inflow direction of the exhaust gas 1.
  • it is divided into a plurality of steam generators in parallel, and it is configured to heat a part of the plurality of steam generators at the start of startup, so the steam temperature rises to a predetermined temperature in a short time it can.
  • the plant startup time can be shortened.
  • the control method of a waste heat recovery boiler, and the combined cycle power plant using these, heat capacity per steam generation part 1 unit Therefore, the drum can be downsized, and the thermal stress and thermal deformation of the drum can be reduced. As a result, the restriction on the conventional exhaust gas temperature rise rate can be relaxed, so that the plant start-up time can be shortened.
  • the exhaust heat recovery boiler control method of the present invention and the combined cycle power plant using them, the entire exhaust heat recovery boiler 4 is heated in the process of starting the plant.
  • the heat capacity per steam generator is reduced by dividing the exhaust heat recovery boiler 4 into a plurality of parallel steam generators, and limited to a part of the steam generators at the start of startup. Since the heating is performed, the steam temperature can be raised to a predetermined temperature in a short time. As a result, since the steam supply to the steam turbine 5 can be accelerated, the plant startup time is shortened.
  • the control method of a waste heat recovery boiler, and the combined cycle power plant using these, the 2nd steam generation part 10b used at the time of starting is used. Since it is arranged between the other first and third steam generators 10a, 10c to reduce the heat dissipation after the stop, the second steam generator 10b can be maintained at a high temperature in the plant stop state. As a result, it is possible to generate steam earlier than before when starting up next time.
  • the heat insulating material as a constituent member is also included with the steam generating unit.
  • the steam generating part inside the exhaust heat recovery boiler 4 is sequentially heated, so that the heating of the heat insulating material, which is also the object of heating, can be delayed.
  • the control method of a waste heat recovery boiler, and the combined cycle power plant using these it is several in width direction with respect to the flow direction of waste gas. Since the exhaust gas flow path is provided and each flow path is provided with a unit having a steam generation unit, the capacity per unit of the steam generation unit (unit) is reduced compared to the conventional method, and the drum provided in the steam generation unit Can be miniaturized. By reducing the size of the drum, thermal stress and thermal deformation can be reduced, so that the life of the equipment can be extended and the exhaust gas temperature rise rate that has been limited in the past can be increased. As a result, the plant startup time can be further shortened.
  • the order of using the steam generation unit at the time of starting the plant is not limited to the example of the present embodiment.
  • FIG. 7 is a schematic configuration diagram showing an exhaust heat recovery boiler according to the present invention, an exhaust heat recovery boiler control method, and a control system for an exhaust heat recovery boiler constituting a second embodiment of a combined cycle power plant using them. It is.
  • FIG. 7 the same reference numerals as those shown in FIG. 1 to FIG.
  • the exhaust gas flow path of each unit is provided with one damper as exhaust gas inflow means and one damper as exhaust gas outflow means.
  • the second embodiment is different in that two dampers are disposed as exhaust gas inflow means and two dampers are disposed as exhaust gas outflow means in the width direction of the exhaust gas flow path of each unit.
  • the dampers are arranged in a plane perpendicular to the exhaust gas flow so that the direction of each damper intersects the exhaust gas flow at a right angle while the damper is closed.
  • Other waste heat recovery boilers and facilities constituting the combined cycle power plant are the same as those in the first embodiment.
  • each damper when the opening degree of these dampers is controlled to a position parallel to the flow direction of the exhaust gas 1, the exhaust gas inflow amount becomes maximum and intersects the flow direction of the exhaust gas 1.
  • the opening degree of these dampers is controlled to the position, the inflow of the exhaust gas 1 is blocked. Therefore, the length in the width direction of each damper may be about half of the exhaust gas passage width.
  • each damper can be disposed at a location closer to the steam generating section, and therefore the length of the exhaust gas flow path of each unit can be shortened. As a result, the unit can be further downsized.
  • the exhaust heat recovery boiler control method of the present invention and the combined cycle power plant using them, the same effects as those of the first embodiment described above. Can be obtained. Moreover, since the length of the exhaust gas flow path can be shortened, the unit including the steam generation unit and the exhaust heat recovery boiler can be further reduced in size.
  • FIG. 8 is a schematic configuration diagram showing an exhaust heat recovery boiler according to the present invention, an exhaust heat recovery boiler control method, and a control system for an exhaust heat recovery boiler constituting a third embodiment of a combined cycle power plant using these. It is.
  • FIG. 8 the same reference numerals as those shown in FIG. 1 to FIG.
  • the dampers are closed in the width direction of the exhaust gas flow path of each unit.
  • the dampers are arranged in a plane perpendicular to the exhaust gas flow so that the direction of each damper intersects the exhaust gas flow at a right angle.
  • the two dampers as the exhaust gas inflow means in the steam generation units 10a and 10c other than the center are in the state in which the exhaust gas flows while the dampers are closed. It is different in that it is arranged so that it intersects at an angle rather than at right angles.
  • Other waste heat recovery boilers and facilities constituting the combined cycle power plant are the same as those in the second embodiment.
  • the damper 110b located at the center in the width direction of the exhaust gas passage portion 4B is provided. It arrange
  • the exhaust heat recovery boiler control method of the present invention and the combined cycle power plant using them, the same effects as those of the first embodiment described above. Can be obtained.
  • the dampers 110a and 110c constituting the first and third exhaust gas inflow means 11a and 11c are closed and the damper 110b constituting the second exhaust gas inflow means 11b is opened,
  • the pressure loss of the exhaust gas in the heat recovery boiler 4 as a whole can be reduced.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
PCT/JP2012/071698 2012-08-28 2012-08-28 Chaudière à récupération de chaleur perdue, procédé de commande de ladite chaudière à récupération de chaleur perdue, et centrale électrique à cycle combiné l'employant Ceased WO2014033837A1 (fr)

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PCT/JP2012/071698 WO2014033837A1 (fr) 2012-08-28 2012-08-28 Chaudière à récupération de chaleur perdue, procédé de commande de ladite chaudière à récupération de chaleur perdue, et centrale électrique à cycle combiné l'employant

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PCT/JP2012/071698 WO2014033837A1 (fr) 2012-08-28 2012-08-28 Chaudière à récupération de chaleur perdue, procédé de commande de ladite chaudière à récupération de chaleur perdue, et centrale électrique à cycle combiné l'employant

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016050580A (ja) * 2014-08-28 2016-04-11 ゼネラル・エレクトリック・カンパニイ 複合サイクル発電プラントの熱エネルギー節減方法
JP2019011721A (ja) * 2017-06-30 2019-01-24 三菱日立パワーシステムズ株式会社 コンバインドサイクルプラントの制御装置及びコンバインドサイクルプラントの停止方法
EP3551864A4 (fr) * 2016-12-08 2020-08-19 Atlas Copco Comptec, LLC Système de récupération de chaleur perdue
JP2020125736A (ja) * 2019-02-06 2020-08-20 三浦工業株式会社 蒸気システム

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6385207A (ja) * 1986-09-27 1988-04-15 Mitsubishi Heavy Ind Ltd 複合発電システム
JPS63311001A (ja) * 1987-06-12 1988-12-19 株式会社日立製作所 再熱式排熱回収ボイラ
JPH01240707A (ja) * 1988-03-18 1989-09-26 Toshiba Corp コンバインドサイクル発電プラント
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
JPH04366303A (ja) * 1991-06-13 1992-12-18 Toshiba Corp 自然循環形排熱回収ボイラ
JP2001082110A (ja) * 1999-09-16 2001-03-27 Mitsubishi Heavy Ind Ltd コンバインドサイクルプラント
JP2001342848A (ja) * 2000-06-05 2001-12-14 Toyota Motor Corp ガスタービン発電システムの廃熱回収方法
JP2005330866A (ja) * 2004-05-19 2005-12-02 Tokyo Electric Power Co Inc:The 複合発電プラント

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6385207A (ja) * 1986-09-27 1988-04-15 Mitsubishi Heavy Ind Ltd 複合発電システム
JPS63311001A (ja) * 1987-06-12 1988-12-19 株式会社日立製作所 再熱式排熱回収ボイラ
JPH01240707A (ja) * 1988-03-18 1989-09-26 Toshiba Corp コンバインドサイクル発電プラント
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
JPH04366303A (ja) * 1991-06-13 1992-12-18 Toshiba Corp 自然循環形排熱回収ボイラ
JP2001082110A (ja) * 1999-09-16 2001-03-27 Mitsubishi Heavy Ind Ltd コンバインドサイクルプラント
JP2001342848A (ja) * 2000-06-05 2001-12-14 Toyota Motor Corp ガスタービン発電システムの廃熱回収方法
JP2005330866A (ja) * 2004-05-19 2005-12-02 Tokyo Electric Power Co Inc:The 複合発電プラント

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016050580A (ja) * 2014-08-28 2016-04-11 ゼネラル・エレクトリック・カンパニイ 複合サイクル発電プラントの熱エネルギー節減方法
EP3551864A4 (fr) * 2016-12-08 2020-08-19 Atlas Copco Comptec, LLC Système de récupération de chaleur perdue
JP2019011721A (ja) * 2017-06-30 2019-01-24 三菱日立パワーシステムズ株式会社 コンバインドサイクルプラントの制御装置及びコンバインドサイクルプラントの停止方法
JP2020125736A (ja) * 2019-02-06 2020-08-20 三浦工業株式会社 蒸気システム
JP7225867B2 (ja) 2019-02-06 2023-02-21 三浦工業株式会社 蒸気システム

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