WO2021020207A1 - Dispositif de commande de centrale électrique, centrale électrique, et procédé de commande de centrale électrique - Google Patents

Dispositif de commande de centrale électrique, centrale électrique, et procédé de commande de centrale électrique Download PDF

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Publication number
WO2021020207A1
WO2021020207A1 PCT/JP2020/028090 JP2020028090W WO2021020207A1 WO 2021020207 A1 WO2021020207 A1 WO 2021020207A1 JP 2020028090 W JP2020028090 W JP 2020028090W WO 2021020207 A1 WO2021020207 A1 WO 2021020207A1
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Prior art keywords
condensate
control
power plant
valve
steam
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PCT/JP2020/028090
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English (en)
Japanese (ja)
Inventor
和宏 堂本
孝裕 竹友
道男 佐々木
尚 三田
Original Assignee
三菱日立パワーシステムズ株式会社
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Priority to KR1020227001608A priority Critical patent/KR20220019829A/ko
Publication of WO2021020207A1 publication Critical patent/WO2021020207A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • 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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • 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
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/38—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type

Definitions

  • Patent Document 1 discloses a circulation type boiler system that can be used in a thermal power plant, a conventional power plant, and the like.
  • Patent Document 1 when the load demand increases, the turbine bleeding valve and the deaerator water level adjusting valve of the steam generator such as a boiler are narrowed down to a certain opening, so that the generator output can be reduced to a relatively short time. It is disclosed that it will increase in. As a result, it is possible to improve the responsiveness without increasing the strength of the turbine as compared with the case where the increase in the load requirement is dealt with only by increasing the fuel input amount to the steam generator.
  • Patent Document 1 the turbine bleeding valve of the steam generator and the water level adjusting valve of the deaerator are narrowed down to a certain opening degree to cope with an increase in load demand.
  • such narrowing down of the turbine bleeding valve and the deaerator water level adjusting valve causes the generator output to increase sharply, so that the generator output may become excessive with respect to fluctuations in load requirements (that is, the generator output is temporarily increased). There is a risk that the load command value will be exceeded).
  • At least one aspect of the present disclosure has been made in view of the above circumstances, and when the load demand increases, the output of the power plant can be followed with good responsiveness and within an appropriate range with respect to the load command value. It is an object of the present invention to provide a control device for a power plant, a power plant, and a method for controlling the power plant.
  • the control device of the power plant is used to solve the above problems.
  • a steam generator configured to generate steam and A turbine configured to be driveable using the steam
  • a condenser configured to generate condensate by condensing the steam that has finished its work in the turbine
  • a condensate control valve configured to be able to adjust the amount of condensate supplied to the steam generator
  • a heater configured to heat the condensate using the bleed air from the turbine
  • An bleed valve configured to adjust the flow rate of the bleed air
  • It is a control device of a power plant equipped with When the load command value for the power plant increases, the condensate throttle control that narrows the opening degree of the condensate control valve and the load increase control that increases the load of the steam generator are performed.
  • the opening degrees of the condensing control valve and the bleeding valve are controlled by an opening degree change rate set based on the change rate of the load command value.
  • the power plant control method is to solve the above problems.
  • a steam generator configured to generate steam and A turbine configured to be driveable using the steam
  • a condenser configured to generate condensate by condensing the steam that has finished its work in the turbine
  • a condensate control valve configured to be able to adjust the amount of condensate supplied to the steam generator
  • a heater configured to heat the condensate using the bleed air from the turbine
  • An bleed valve configured to adjust the flow rate of the bleed air
  • FIG. 1 is an overall configuration diagram of a power plant 1 according to one aspect of the present disclosure.
  • the power plant 1 includes a steam generator 2 configured to be capable of generating steam.
  • the steam generator 2 is a device capable of generating steam by applying heat to the water supply.
  • the steam generator 2 is a boiler device capable of generating steam from water supply using, for example, the amount of heat generated by burning fuel. More specifically, the boiler device is a conventional boiler capable of generating steam by crushing coal with a pulverized coal machine (not shown) and burning it in a fireplace.
  • the boiler device may be a drum type boiler or a once-through type boiler.
  • the steam generated by the steam generator 2 is supplied to the turbine 6 via the steam supply path 4.
  • the turbine 6 is rotationally driven by high-temperature and high-pressure steam generated by the steam generator 2.
  • the turbine 6 includes a high-pressure turbine 6a arranged on the upstream side and two low-pressure turbines 6b1 and 6b2 arranged on the downstream side.
  • the high-pressure turbine 6a and the two low-pressure turbines 6b1 and 6b2 are connected in series with each other.
  • the two low pressure turbines 6b1 and 6b2 are connected in parallel with each other.
  • the steam generated by the steam generator 2 first drives the high-pressure turbine 6a on the upstream side, and then drives the low-pressure turbines 6b1 and 6b2 on the downstream side.
  • each turbine 6 driven by steam is input to the generator 5 connected to the output shaft 3 of the turbine 6.
  • the kinetic energy input from the turbine 6 is converted into electrical energy.
  • the electric energy generated by the generator 5 is supplied to an electric power system (not shown) via a predetermined path, for example.
  • FIG. 1 illustrates a case where only the output shafts 3 of the low-pressure turbines 6b1 and 6b2 of the turbine 6 are connected to the generator 5, only the output shaft of the high-pressure turbine 6a of the turbine 6 generates power. It may be connected to the machine 5, or may be coaxially connected to the generator 5 with the output shaft of the high-pressure turbine 6a and the output shafts of the low-pressure turbines 6b1 and 6b2 as a common shaft.
  • the steam supply path 4 connecting the steam generator 2 and the turbine 6 is provided with a steam valve 8 (main steam valve) for adjusting the flow rate of steam supplied from the steam generator 2 to the turbine 6.
  • the opening degree of the steam valve 8 can be controlled by a control signal from the control device 100 described later.
  • the steam that has finished work in the turbine 6 is supplied to the condenser 10 arranged on the downstream side.
  • the condenser 10 is configured to be capable of generating condenser by condensing the steam discharged from the turbine 6. Specifically, the condenser 10 condenses steam by exchanging heat with the cooling water to generate condensed water.
  • the condensate generated by the condenser 10 is stored in the first condensate tank 12 of the condenser 10.
  • the second condensate tank 16 is connected to the first condensate tank 12 via the condensate discharge line 14.
  • the condensate generated by the condensate 10 is stored in the first condensate tank 12.
  • An appropriate reference storage level for condensate is set in the first condensate tank 12, and when the condensate storage level exceeds the standard storage level, the condensate is stored in the first condensate tank 12. Is sent to the second condensate tank 16 via the condensate discharge line 14, so that the condensate level of the first condensate tank 12 is properly maintained.
  • the condensate discharge line 14 is provided with a condensate discharge valve 27 configured so that the flow rate of the condensate flowing through the condensate discharge line 14 can be adjusted.
  • the condensate generated by the condenser 10 is returned to the steam generator 2 via the condensate line 22.
  • the condensate line 22 is provided with a condensate control valve 23 for adjusting the flow rate of the condensate flowing through the condensate line 22.
  • the opening degree of the condensate control valve 23 is controlled in order to properly maintain the condensate level in the condenser 10 on the upstream side, but in the condensate throttle control described later, the opening degree is positively adjusted. By squeezing, the flow rate of condensate flowing through the condensate line 22 can be reduced.
  • the condensate line 22 is provided with a plurality of heaters 24 and a deaerator 25.
  • the plurality of heaters 24 are provided in series along the condensate line 22, and are configured to be capable of raising the temperature by exchanging heat with the extracted air from the turbine 6 for the condensate flowing through the condensate line 22.
  • the bleed air from the turbine 6 is supplied to the plurality of heaters 24 and the deaerator 25, respectively, via the bleed air line 26 extending from the turbine 6.
  • the condensate flowing through the condensate line 22 is gradually heated by passing through the plurality of heaters 24 and then supplied to the steam generator 2.
  • the bleed air cooled by exchanging heat with the condensate in the plurality of heaters 24 joins the condensate line 22.
  • the bleed air line 26 is provided with an bleed valve 28 for adjusting the flow rate of the bleed air from the turbine 6.
  • the opening degree of the bleeding valve 28 is configured so that the opening degree can be adjusted based on a control signal from the control device 100 described later.
  • the opening degree of the bleed valve 28 is controlled so that, for example, bleed air corresponding to the flow rate of the condensate of the condensate line 22, which is the heat exchange target, is supplied to the heater 24.
  • the deaerator 25 is a device for removing dissolved oxygen, carbon dioxide, etc. contained in the condensate flowing through the condensate line 22.
  • the control device 100 is a control unit of the power plant 1, and has a hardware configuration including an electronic arithmetic unit such as a computer.
  • the control device 100 functions as a control device according to at least one aspect of the present invention by installing a program for executing the control method according to at least one aspect of the present invention in such a hardware configuration. It is configured to be possible.
  • the control device 100 is configured to be able to comprehensively control the power generation plant 1 by transmitting and receiving control signals to and from each component of the power generation plant 1. Such control of the power plant 1 is performed based on a load command value for the power plant 1 acquired by the control device 100 from the outside.
  • the load command value is a command value related to the load required for the power plant 1, and may be determined according to, for example, the supply and demand state in the power system, or may be determined manually by the operator of the power plant 1. Good.
  • FIG. 2 is a control flow diagram of the control device 100 of FIG.
  • the inside of the control device 100 is shown as a functional block diagram, and the control device 100 includes a steam valve control unit 110 and a steam generator control unit 120.
  • the steam valve control unit 110 is a functional block that outputs an opening command value of the steam valve 8 in response to an input signal
  • the steam generator control unit 120 is a control parameter of the steam generator 2 in response to an input signal. It is a functional block that outputs a water supply demand signal and a fuel demand signal.
  • the generator output L (output of the generator 5), the load command value Ld, the steam pressure set value Ps, and the steam pressure value P are input to the control device 100, respectively.
  • the generator output L can be acquired based on various sensors installed in the generator 5.
  • the load command value Ld is a command value input from the outside to the power plant 1 (for example, received from the central power supply command room according to the power supply / demand state of the power system).
  • the steam pressure set value Ps is a target value of the steam pressure generated by the steam generator 2, and is set by the control device 100.
  • the steam pressure value P can be obtained from a pressure sensor installed in the steam supply path 4.
  • the generator output L and the load command value Ld are input to the deviation calculator 102.
  • the deviation ⁇ L output from the deviation calculator 102 is input to the PI controller 106 via the switch 104.
  • the switch 104 is a switch that can select the first control route C1 or the second control route C2 based on whether or not the condensate throttle control is executed.
  • the first control route C1 is a control route selected at the time of normal control in which the condensate throttle control is not executed, and the deviation ⁇ L is directly input to the PI controller 106.
  • the second control route C2 is a control route selected when the condensate throttle control is executed, and the deviation ⁇ L is input to the PI controller 106 via the filter 108.
  • the filter 108 performs a predetermined filtering process on the deviation ⁇ L which is an input value.
  • FIG. 3 is an example of the characteristic function f of the filtering process applied by the filter 108 to the deviation ⁇ L.
  • the characteristic function f'corresponding to the case where the first control route C1 is selected is shown by a broken line for comparison (in the first control route C1, the deviation ⁇ L is directly input to the PI controller 106). Therefore, it is substantially equivalent to having a characteristic function f'which is a linear linear function with a slope of "1" and an intercept of "0").
  • the characteristic function f is set so that the output value is larger than the characteristic function f'in the negative region (that is, ⁇ L ⁇ 0). More specifically, as shown in FIG. 3, the characteristic function f has a linear characteristic with a slope of “1” in the positive region ( ⁇ L ⁇ 0) and the subthreshold region ( ⁇ L ⁇ L1) in the negative region. In the negative region ( ⁇ L1 ⁇ ⁇ L ⁇ 0) of the predetermined value ⁇ L1 or more, the slope is “0” and the dead band characteristic is obtained.
  • the PI controller 106 feedback-controls the opening degree of the steam valve 8 by outputting a steam valve opening command value corresponding to the deviation ⁇ L input to the PI controller 106.
  • the PI controller 106 outputs the steam valve opening command value corresponding to the deviation ⁇ L calculated by the deviation calculator 102.
  • the PI controller 106 outputs a steam valve command value corresponding to the deviation ⁇ L after the filtering process is performed by the filter 108.
  • the filter 108 as described above with reference to FIG.
  • the steam pressure set value Ps and the steam pressure value P are input to the deviation calculator 122.
  • the deviation ⁇ P output from the deviation calculator 122 is input to the PI controller 124.
  • the PI controller 124 outputs an output signal corresponding to the deviation ⁇ P.
  • the load command value Ld is added as a feedforward component by the adder 126 to the output signal output from the PI controller 124, so that the load followability of the steam generator 2 is improved.
  • Such a control signal of the steam generator 2 is output to the steam generator 2 to be controlled as a water supply demand signal Sw and a fuel demand signal Sf, which are control parameters of the steam generator 2.
  • the condensate throttle control is a control for increasing the output of the generator 5 by reducing the opening degree of the condensate control valve 23 and the bleed air valve 28.
  • FIG. 4 is a flowchart showing the generator output increase mechanism by the condensate throttle control for each process.
  • the opening of the condensate control valve 23 is reduced (step S100).
  • a throttle operation of the condensate control valve 23 may be manually performed by the operator, or the condensate control valve from the control device 100 detects a trigger signal for starting control by the control device 100. It may be carried out automatically by transmitting a control signal to 23.
  • step S101 When the opening degree of the condensate control valve 23 decreases, the flow rate of condensate flowing through the condensate line 22 located on the downstream side of the condensate control valve 23 decreases (step S101).
  • the opening degree of the bleeding valve 28 is controlled so as to correspond to the flow rate of the condensate flowing through the condensate line 22.
  • the flow rate required for heat exchange with condensate is introduced. Therefore, when the flow rate of the condensate in the condensate line 22 decreases as in step S101, the opening degree of the bleeding valve 28 is controlled to decrease accordingly (step S102).
  • the opening degree of the bleed valve 28 decreases, the bleed air supplied to the heater 24 decreases, so that the amount of steam flowing through the turbine 6 increases (step S103) and the generator output L increases (step S104).
  • the output of the generator 5 can be increased.
  • the effect of increasing the generator output by the condensate throttle control is not permanent, but is temporary for a limited period after the condensate throttle control is started. This is because the condensate flow rate is reduced by the condensate throttle control, so that the deaerator level in the deaerator 25 is lowered and the water supply to the steam generator 2 cannot be continued. As a result, the effect of increasing the generator output by the condensate throttle control decreases after a temporary period.
  • the load command value Ld when the load command value Ld increases, the load command value (for example, by manual operation by the operator of the power plant 1) is used to permanently increase the generator output L.
  • the throttle of the steam valve 8 is suppressed during the condensate throttle control, so that the generator output by the condenser throttle control It makes it easier to obtain an increase effect.
  • the deviation ⁇ L is set to be larger in the negative side region than in the first control route C1 by performing the filtering process by the filter 108. As a result, the steam valve 8 is less likely to be throttled when the condensate throttle control is executed, so that the effect of increasing the generator output can be easily obtained.
  • the spillover control is performed by adjusting the opening degree of the condensate control valve 23 as described above in the normal time when the condensate throttle control is not executed. That is, by adjusting the opening degree of the condensate control valve 23 to change the amount of condensate supplied to the condensate line 22, the level of condensate stored in the first condensate tank 12 is appropriately managed. ..
  • the condensate control valve 23 is throttled regardless of the condensate level of the first condensate tank 12 in order to increase the generator output L, so that the first condensate tank 12 and Spillover control is performed by adjusting the opening degree of the condensate discharge valve 27 provided between the second condensate tanks 16.
  • FIG. 5 is a control flow diagram relating to the condensate discharge valve 27 in the spillover control.
  • the condensate discharge valve opening command value corresponding to the deviation ⁇ F is output.
  • feedback control is performed so that the condensate level becomes the condensate level target value F * (that is, the deviation ⁇ F becomes zero).
  • the condensate level target value F * is set by the condensate level target value setting unit 134.
  • the return water level target value F * is set by adding the addition target value F * 2 to the normal target value F * 1 in the adder 136.
  • the switch 138 selects " ⁇ " as the addition target value F * 2.
  • the condensate level target value F * is set larger by ⁇ when the condensate throttle control is not implemented than when the condensate throttle control is implemented.
  • the opening degree of the condensate discharge valve 27 is fixed to be small (preferably set to the fully closed state), and the condensate discharge valve 27 is not involved in the spillover control. become.
  • ⁇ is not added to the condensate level target value F *, so that the opening degree of the condensate discharge valve 27 becomes the condensate level target value F *. Feedback is controlled. As a result, even when the condensate control valve 23 is in a state of being throttled by the condensate throttle control, it is possible to perform spillover control by adjusting the opening degree of the condensate discharge valve 27.
  • FIG. 6 is a flowchart showing the load response control of the power plant 1 for each process
  • FIG. 7 is a timing chart showing the load command value Ld at the time of load response control and the output transition of the power plant 1 in association with each other.
  • FIG. 7 a case where the load command value Ld, which was in the first steady value L1 as an initial state, monotonically increases from time t1 to time t2 and fluctuates so as to increase to the second steady value L2. Let's take an example.
  • the control device 100 monitors the load command value Ld input to the power plant (step S200), and determines whether or not the load command value Ld has increased (step S201).
  • the determination in step S201 is performed based on, for example, whether or not the amount of change in the load command value Ld with respect to the first steady-state value L1 before the time t1 has reached the determination threshold value.
  • the rate of change of the load command value Ld the amount of change of the load command value Ld in a predetermined period
  • the load command value Ld increases. Is determined.
  • step S202 the condensate throttle control is executed (step S202).
  • the condensate throttle control is performed by reducing the opening degree of the condensate control valve 23 and the bleed air valve 28 as described above.
  • Such a throttle operation of the condensate control valve 23 may be manually performed by, for example, an operator, or is automatically performed by transmitting a control signal from the control device 100 to the condensate control valve 23 and the bleeding valve 28. It may be done as a target.
  • the condensate throttle control is performed in step S202, the output of the generator 5 temporarily increases as described above with reference to FIG.
  • the control device 100 performs load increase control of the steam generator 2 (step S203). Since the condensate throttle control is limited to a temporary increase in the output of the generator 5 as described above, the output increase effect of the condensate throttle control is reduced by performing the load increase control of the steam generator 2. It is possible to follow the increase of the load command value Ld.
  • step S203 is performed after step S202 is performed for the sake of formality
  • steps S202 and S203 may be performed at the same time. That is, the condensate throttle control and the load increase control may be performed at the same time.
  • the load increase control is less responsive than the condensate throttle control (because the initial action at the start of the change of the load command value Ld is slow)
  • step S203 is carried out after step S202 and that step S203 is carried out before step S202 as shown in FIG.
  • step S204 YES
  • step S205 YES
  • FIG. 7 as a comparative example, when only the condensate throttle control is performed from time t1 (first comparative example), and the load increase of the steam generator 2 is performed from time t1 without performing the condensate throttle control.
  • first comparative example when only the condensate throttle control is performed from time t1
  • second comparative example The case where only the control is performed.
  • the response is better than that in the second comparative example, and the output of the power plant 1 can be temporarily increased immediately after the time t1.
  • the effect of increasing the output by the condensate throttle control does not last forever.
  • the second comparative example only the load increase control is performed, and the responsiveness is low.
  • the steam generator 2 is a device such as a coal-fired boiler, there is a process of crushing coal with a pulverized coal machine, so there is a time lag until the crushed coal is input to the fireplace and reflected in the output. Is large and the responsiveness is poor.
  • this embodiment by combining the condensate throttle control and the load increase control when the load command value Ld increases, good responsiveness to a change in the load command value Ld can be obtained, and at the same time, good responsiveness can be obtained. It has been shown that the time required for the output of the power plant 1 to converge to the second steady-state value L2 is shortened.
  • the opening degrees of the condensate control valve 23 and the bleeding valve 28 are narrowed as described above, and the opening change rate at that time is the change rate of the load command value Ld acquired in step S200.
  • the amount of change in the generator output L due to the condensate throttle control depends on the rate of change in the opening degree of the condensate control valve 23 and the bleed air valve 28. Therefore, by controlling the rate of change in the opening degree of the condensate control valve 23 and the bleeding valve 28 when the condensate throttle control is executed, the amount of change in the generator output L becomes excessive, which deviates from the load command value Ld. It can be suppressed to be too much.
  • a power plant capable of following the output of the power plant with good responsiveness and within an appropriate range to the load command value when a load increase request is made. It is possible to provide a control device, a power plant, and a control method for the power plant.
  • the control device of the power plant is A steam generator configured to be able to generate steam (for example, the steam generator 2 of the above embodiment) and A turbine configured to be driveable using the steam (for example, the turbine 6 of the above embodiment) and A condenser (for example, the condenser 10 of the above embodiment) configured to be able to generate condensate by condensing the steam that has finished its work in the turbine.
  • a condensate control valve (for example, the condensate control valve 23 of the above embodiment) configured to be able to adjust the supply amount of the condensate to the steam generator.
  • a heater configured to heat the condensate using the bleed air from the turbine (for example, the heater 24 of the above embodiment) and An bleeding valve configured so that the flow rate of the bleeding air can be adjusted (for example, the bleeding valve 28 of the above embodiment) and (For example, the control device (for example, the control device 100 of the above embodiment) of the power plant (for example, the power plant 1 of the above embodiment).
  • the condensate throttle control that narrows the opening degree of the condensate control valve and the load increase control that increases the load of the steam generator are performed.
  • the opening degrees of the condensing control valve and the bleeding valve are controlled by an opening degree change rate set based on the change rate of the load command value.
  • the output of the power plant is increased by performing the condensate throttle control that narrows the opening of the condensate control valve in addition to the load increase control. It can be increased responsively. As a result, better responsiveness can be obtained as compared with the case where only the load increase control, which takes a relatively long time to respond, is performed. Further, by implementing the condensate throttle control and the load increase control, the output of the power plant can be increased until the target load is reached even when the change in the load command value is large. By performing the condensate throttle control and the load increase control in combination in this way, it is possible to follow the output of the power plant with good responsiveness to an increase in the load command value.
  • the opening degree of the condensate control valve and the bleeding valve is controlled based on the opening degree change rate set based on the change rate of the load command value.
  • the power plant further includes a steam valve (for example, the steam valve 8 of the above embodiment) for controlling the amount of steam supplied to the turbine.
  • a steam valve for example, the steam valve 8 of the above embodiment
  • it is configured to suppress a decrease in the opening command value for the steam valve due to the execution of the condensing throttle control (for example, in the above embodiment, the steam valve opening command value is set.
  • the deviation ⁇ L input to the output PI controller 106 is corrected by the filter 108).
  • the condensate throttle control when the condensate throttle control is performed, the decrease in the opening degree of the steam valve is suppressed.
  • the opening of the steam valve is reduced so as to reduce the generator output exceeding the target output, so that the generator output is reduced. Can be suppressed.
  • the effect of increasing the generator output by the condensate throttle control can be obtained more accurately.
  • a steam valve control unit (for example, the steam valve control unit 110 of the above embodiment) configured to be able to control the opening degree of the steam valve based on the deviation between the output of the generator and the load command value is provided.
  • the steam valve control unit is performing the condensate throttle control, the deviation is in the negative side region, and the opening degree of the steam valve with respect to the deviation is the non-execution of the condensate throttle. It is configured to be controlled to be larger than the inside (for example, in the above embodiment, the filter 108 has the characteristics shown in FIG. 3).
  • the opening degree of the steam valve is larger than that when the condensate throttle control is not carried out. It is controlled to be large. As a result, the decrease in the opening degree of the steam valve when the condensate throttle control is performed is suppressed, so that the effect of increasing the generator output by the condensate throttle control can be obtained more accurately.
  • the steam valve control unit sets the opening degree of the steam valve with respect to the deviation to the deviation in the negative region where the deviation is equal to or more than a predetermined value during the execution of the condensate throttle control.
  • the filter 108 is configured to be controlled so as to be constant (for example, in the above embodiment, the filter 108 has the characteristics shown in FIG. 3).
  • the opening degree of the steam valve is suppressed to be constant, so that the effect of increasing the generator output by the condensate throttle control can be obtained. It can be obtained more accurately.
  • the power plant A condensate discharge line configured to be able to discharge the condensate stored in the condensate (for example, the condensate discharge line 14 of the above embodiment) and A condensate discharge valve (for example, the condensate discharge valve 27 of the above embodiment) configured to be able to adjust the flow rate of the condensate in the condensate discharge line.
  • the opening degree of the condensate discharge valve is adjusted to control the level of the condensate in the condenser (for example, the condensate throttle in the above embodiment).
  • the condensate discharge valve 27 is controlled at the time of control to adjust the condensate level).
  • the condensate level can be appropriately managed by controlling the opening degree of the condensate discharge valve while controlling the condensate control valve by the condensate throttle control.
  • the output of the power plant can be followed with good responsiveness by simultaneously performing the condensate throttle control and the load increase control when the load command value fluctuates.
  • the output of the power plant can be responsively and suitably followed with respect to a relatively large fluctuation of the load command value in which the load command value increases by 5% or more.
  • the load command value is input to the power plant from the central power supply control room according to the supply and demand state of the power system.
  • the output of the power plant can be responsively and suitably followed according to the supply and demand state of the electric power system.
  • the steam generator is a coal-fired boiler that uses coal as fuel.
  • the power plant according to one aspect of the present disclosure is The control device according to any one of (1) to (9) above is provided.
  • the output of the power plant can be made to follow the increase of the load command value with good responsiveness. ..
  • the power plant control method is A steam generator configured to be able to generate steam (for example, the steam generator 2 of the above embodiment) and A turbine configured to be driveable using the steam (for example, the turbine 6 of the above embodiment) and A condenser (for example, the condensate control valve 23 of the above embodiment) configured to be able to generate condensate by condensing the steam that has finished work in the turbine.
  • a condensate control valve (for example, the condensate control valve 23 of the above embodiment) configured to be able to adjust the supply amount of the condensate to the steam generator.
  • a heater configured to heat the condensate using the bleed air from the turbine (for example, the heater 24 of the above embodiment) and An bleeding valve configured so that the flow rate of the bleeding air can be adjusted (for example, the bleeding valve 28 of the above embodiment) and A control method for a power plant (for example, the power plant 1 of the above embodiment).
  • the condensate throttle control that narrows the opening degree of the condensate control valve and the load increase control that increases the load of the steam generator are performed.
  • the opening degrees of the condensate control valve and the bleeding valve are controlled by the opening degree change rate set based on the change rate of the load command value.
  • the output of the power plant is increased by performing the condensate throttle control that narrows the opening degree of the condensate control valve in addition to the load increase control. It can be increased responsively. As a result, better responsiveness can be obtained as compared with the case where only the load increase control, which takes a relatively long time to respond, is performed. Further, by implementing the condensate throttle control and the load increase control, the output of the power plant can be increased until the target load is reached even when the change in the load command value is large. By performing the condensate throttle control and the load increase control in combination in this way, it is possible to follow the output of the power plant with good responsiveness to an increase in the load command value.
  • the opening degree of the condensate control valve and the bleeding valve is controlled based on the opening degree change rate set based on the change rate of the load command value.

Abstract

La présente invention concerne un dispositif de commande d'une centrale électrique qui est pourvue d'un générateur de vapeur, d'une turbine, d'un condenseur, d'une vanne de régulation de condensat, d'un dispositif de chauffage et d'une vanne de purge. Lors de l'augmentation de la valeur de commande de charge pour la centrale électrique, le dispositif de commande effectue une commande d'étranglement de condensat, pour réduire le degré d'ouverture de la vanne de régulation de condensat, et une commande d'augmentation de charge, pour augmenter la charge du générateur de vapeur. Dans la commande d'étranglement de condensat, le degré d'ouverture de la vanne d'air de purge et de la vanne de régulation de condensat est commandé avec un taux de changement d'ouverture réglé sur la base du taux de variation de la valeur de commande de charge.
PCT/JP2020/028090 2019-07-26 2020-07-20 Dispositif de commande de centrale électrique, centrale électrique, et procédé de commande de centrale électrique WO2021020207A1 (fr)

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JP2019138072A JP6775070B1 (ja) 2019-07-26 2019-07-26 発電プラントの制御装置、発電プラント、及び、発電プラントの制御方法
JP2019-138072 2019-07-26

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0454204A (ja) * 1990-06-21 1992-02-21 Mitsubishi Heavy Ind Ltd 抽気復水タービンの制御装置
JP2000303803A (ja) * 1999-04-21 2000-10-31 Nippon Steel Corp 発電システム
JP2002129908A (ja) * 2000-10-25 2002-05-09 Kawasaki Steel Corp 蒸気タービン復水器の水位レベル制御方法
WO2012090778A1 (fr) * 2010-12-27 2012-07-05 三菱重工業株式会社 Dispositif de régulation de débit de condensat pour centrale électrique et méthode de régulation
JP2013053531A (ja) * 2011-09-01 2013-03-21 Hitachi Ltd 発電プラント及びその発電出力増加方法
CN107965356A (zh) * 2017-12-25 2018-04-27 东北电力大学 一种火电机组灵活性提升控制方法

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6545737B2 (ja) * 2017-02-23 2019-07-17 三菱重工業株式会社 発電システム及び発電システムの制御方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0454204A (ja) * 1990-06-21 1992-02-21 Mitsubishi Heavy Ind Ltd 抽気復水タービンの制御装置
JP2000303803A (ja) * 1999-04-21 2000-10-31 Nippon Steel Corp 発電システム
JP2002129908A (ja) * 2000-10-25 2002-05-09 Kawasaki Steel Corp 蒸気タービン復水器の水位レベル制御方法
WO2012090778A1 (fr) * 2010-12-27 2012-07-05 三菱重工業株式会社 Dispositif de régulation de débit de condensat pour centrale électrique et méthode de régulation
JP2013053531A (ja) * 2011-09-01 2013-03-21 Hitachi Ltd 発電プラント及びその発電出力増加方法
CN107965356A (zh) * 2017-12-25 2018-04-27 东北电力大学 一种火电机组灵活性提升控制方法

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JP6775070B1 (ja) 2020-10-28

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