WO2014147738A1 - ガスタービン発電システム - Google Patents
ガスタービン発電システム Download PDFInfo
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- WO2014147738A1 WO2014147738A1 PCT/JP2013/057784 JP2013057784W WO2014147738A1 WO 2014147738 A1 WO2014147738 A1 WO 2014147738A1 JP 2013057784 W JP2013057784 W JP 2013057784W WO 2014147738 A1 WO2014147738 A1 WO 2014147738A1
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- power generation
- output
- gas turbine
- turbine
- generator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/26—Control of fuel supply
- F02C9/28—Regulating systems responsive to plant or ambient parameters, e.g. temperature, pressure, rotor speed
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
- F02C9/48—Control of fuel supply conjointly with another control of the plant
- F02C9/50—Control of fuel supply conjointly with another control of the plant with control of working fluid flow
- F02C9/54—Control of fuel supply conjointly with another control of the plant with control of working fluid flow by throttling the working fluid, by adjusting vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/60—Fluid transfer
- F05D2260/602—Drainage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/01—Purpose of the control system
- F05D2270/06—Purpose of the control system to match engine to driven device
- F05D2270/061—Purpose of the control system to match engine to driven device in particular the electrical frequency of driven generator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/304—Spool rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/309—Rate of change of parameters
Definitions
- the present invention relates to a gas turbine power generation system.
- the power generation output is controlled by the turbine output, specifically the fuel flow rate, etc., and there may be a delay in the response of the power generation output to the control of the fuel flow rate.
- the fuel flow rate changes, for example, when controlling the power generation output
- the combustion gas temperature also changes, but if the temperature of the combustion gas changes rapidly, the temperature distribution of the high temperature parts exposed to the combustion gas becomes uneven and thermal stress Will increase. Excessive thermal stress can lead to thermal fatigue and thus failure of the hot parts.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas turbine power generation system capable of contributing to stabilization of the grid frequency by improving the response of the power generation output to the power demand.
- the present invention controls the generation load to change the setting of the turbine rotational speed when the change rate of the fuel flow rate according to the gas turbine output command is out of the limited range, and changes the fuel by the limit value.
- the power generation output is changed at a larger change rate than when the flow rate is changed.
- the responsiveness of the electric power generation output with respect to an electric power demand can be improved, and it can contribute to stabilization of system frequency.
- FIG. 1 is a schematic view of a gas turbine power generation system according to a first embodiment of the present invention. It is a functional block diagram of the gas turbine control device with which the gas turbine power generation system concerning a 1st embodiment of the present invention was equipped. It is a flowchart showing the output control procedure by the gas turbine control system with which the gas turbine power generation system concerning a 1st embodiment of the present invention was equipped. It is a figure showing an example of the behavior of the various outputs to the electric power demand of the gas turbine power generation system concerning a 1st embodiment of the present invention. It is a figure showing an example of the control screen by the output device with which the gas turbine power generation system concerning a 1st embodiment of the present invention was equipped.
- FIG. 1 is a schematic view of a gas turbine power generation system according to a first embodiment of the present invention.
- the gas turbine power generation system 100 illustrated in FIG. 1 includes a gas turbine 17, a generator 5, a generator control device 10, and a gas turbine control device 7.
- the gas turbine 17 is a single-shaft gas turbine, and includes a compressor 1, a combustor 20, and a turbine 2.
- the compressor 1 sucks atmospheric air and compresses it to generate compressed air 21, and supplies the generated compressed air 21 to the combustor 20. Further, an IGV (Inlet Guide Vane) 9 is provided at the air intake of the compressor 1. The IGV 9 changes the amount of air flowing into the compressor 1 by rotating a plurality of vanes (not shown) to change the opening area of the air intake port of the compressor 1.
- IGV Inlet Guide Vane
- the combustor 20 mixes the compressed air 21 from the compressor 1 with the fuel injected from the burner 18 and burns it to generate a combustion gas 22.
- the combustion gas 22 flows into the turbine 2 through the combustor liner 19.
- the flow rate of fuel burned by the burner 18 is adjusted by a fuel flow control valve 8 provided in the fuel pipe.
- the turbine 2 is driven by the combustion gas 22 from the combustor 20 (the rotational power of the turbine shaft 13 is obtained).
- the rotational speed of the turbine shaft 13 is detected by the rotational speed detector 26 and is output to the gas turbine control device 7.
- the combustion gas 22 whose energy is recovered by the turbine 2 is discharged as an exhaust 14. Further, a portion of the compressed air extracted by the compressor 1 is supplied as turbine cooling air 23 to the turbine 2.
- the turbine cooling air 23 bypasses the combustor 20 and is directly supplied from the compressor 1 to the turbine 2 to cool the stationary blades 24 and the moving blades 25 constituting the turbine 2.
- the generator 5 is connected to the turbine shaft 13 of the gas turbine 17 and is driven by the rotational power obtained by the turbine 2 to generate AC power.
- the generator control device 10 is provided between the generator 5 and the electric power system, and includes a load regulator 11 and a frequency regulator 12.
- a load regulator 11 is a mechanism that adjusts the size of the power generation load of the generator 5 (for example, the current or phase to be supplied to the stator).
- the frequency adjuster 12 is a mechanism for adjusting the output frequency of the generator 5, and outputs the alternating current output obtained by the generator 5 as a set frequency (for example, a reference frequency such as 50 Hz or 60 Hz).
- the output of the generator 5 is wave-shaped via the generator controller 10 and sent to the power consumer via the power cable.
- the gas turbine control device 7 receives various input signals and controls a fuel flow rate control (hereinafter referred to as FFD) for controlling the opening degree of the fuel flow control valve 8 and an intake flow rate command for controlling the opening degree of the IGV 9 (hereinafter referred to as CIGV) And outputs various signals including a generator control command (hereinafter referred to as IMWD) for controlling the operation of the generator control device 10.
- FFD fuel flow rate control
- IMWD generator control command
- the input signal of the gas turbine control device 7 includes a gas turbine output command (hereinafter referred to as MWD) according to the power demand, a turbine rotational speed from the rotational speed detector 26, and an actual value measured by a power meter (not shown).
- the amount of generated power (hereinafter referred to as RMW) and other input signals from various detectors (not shown) (hereinafter referred to as state quantity signals) are included.
- FIG. 2 is a functional block diagram of the gas turbine controller 7.
- the gas turbine control device 7 includes a protection limiter 101, a rotation number limiter 102, an output controller 103, an FFD calculator 104, a load limiter 105, an exhaust temperature limiter 106, an output change rate limiter 107, an IGV opening calculator 108, and a comparison.
- the vessel 109 is provided.
- an output device 110 is connected to the gas turbine control device 7 so that trends of power generation output, turbine rotational speed, operation mode and the like can be confirmed (see FIG. 5 described later).
- the output device 110 is, for example, a monitor device such as a maintenance console.
- the FFD calculator 104 receives the MWD, the turbine rotational speed, and the RMW, calculates the necessary amount of increase or decrease in the fuel flow rate from, for example, the difference between RMW and MWD, and compares the fuel flow value taking this into consideration Output to 109.
- the fuel flow rate is controlled according to the MWD so that the RMW approaches the MWD, thereby functioning as a fuel flow control device that adjusts the turbine output, and hence the power generation output.
- the load limiter 105 has a function of limiting the maximum output by the approval output of the power generation facility. Therefore, the fuel flow rate value corresponding to the maximum output limit value (or a value set a little lower in consideration of the margin) is output from the load limiter 105 to the comparator 109.
- Exhaust temperature limiter 106 functions to limit the maximum temperature of exhaust 14. Therefore, the fuel flow rate value corresponding to the maximum temperature limit value (or a value set slightly lower in consideration of the margin) is output from the exhaust temperature limiter 106 to the comparator 109.
- the output change rate limiter 107 functions to limit the maximum value of the change rate of the turbine output (in this case, the change rate of the fuel flow rate) in consideration of the thermal stress and the like generated in the high temperature parts of the gas turbine.
- the rate of change referred to here is the change in turbine output per hour.
- the output change rate limiter 107 controls the fuel flow rate so that the change rate does not exceed the limit value.
- the power change rate limiter 107 outputs a fuel flow value that can be changed at a rate of increase or decrease of the limit with respect to the current value only when the rate of change of the fuel flow rate exceeds the limit value.
- the comparator 109 is a low value selector, and selects and selects the lowest value among the fuel flow rate command values from the FFD calculator 104, the rotation speed limiter 102, the exhaust temperature limiter 106, and the output change rate limiter 107. The obtained value is output to the fuel flow control valve 8 as FFD.
- the IGV opening calculator 108 receives the turbine rotational speed and RMW from the rotational speed detector 26, calculates CIGV based on these values, and outputs the CIGV to the IGV 9. Specifically, the IGV opening calculator 108 performs the function of controlling the intake flow rate of the compressor 1 at a constant level.
- the speed limiter 102 functions to limit the IMWD so that the turbine speed does not deviate from the limit range.
- the upper limit value and the lower limit value of the turbine rotational speed are set in advance in consideration of, for example, resonance of the blades of the compressor 1 and the turbine 2, an allowable value of centrifugal stress, and a rotating stall of the compressor 1.
- the rotation speed limiter 102 outputs an upper limit value of the turbine rotation speed to the output controller 103 when the turbine rotation speed input from the rotation speed detector 26 exceeds the upper limit value, and a lower limit value otherwise.
- the protection limiter 101 is various other limitations, and receives signals (state quantity signals) of temperature sensor, pressure sensor, torque sensor etc. (all not shown) to obtain various values such as surge temperature, surge pressure, shaft torque, etc. Limit the turbine speed so as not to get out of the limit range.
- the output controller 103 determines whether the change rate of the fuel flow rate according to the MWD is a value within the limited range, and changes the setting of the turbine rotational speed according to the determination to set the IMWD.
- the output controller 103 receives the outputs from the FFD calculator 104, the load limiter 105, the exhaust temperature limiter 106, and the output change rate limiter 107, and the output of the FFD calculator 104 is the change rate limiter 107, etc. It is judged whether or not it is within the limit value by. In the case of this example, it can be determined whether or not the fuel flow value output by the FFD calculator 104 is the minimum value.
- the output controller 103 sets the IMWD according to the MWD without changing the setting of the turbine rotational speed. If the fuel flow rate output from the FFD calculator 104 deviates from the limited range, the turbine rotational speed in the case of changing the generator load is calculated following the sudden change of the MWD. At this time, the output controller 103 has a low value selector function, and the predicted value is compared with the limit value of the turbine rotational speed by the protection limiter 101 and the rotational speed limiter 102, and the lowest value among the three.
- the output controller 103 changes the setting of the turbine rotation speed to the predicted value, and then sets IMWD according to the MWD. If the predicted value exceeds any of the limit values, the IMWD is set according to the limit value without changing the setting of the turbine speed. In this case, since the limit value is the set value, IMWD is also the set value (limit value).
- the IMWD set as described above by the output controller 103 is output to the generator control device 10.
- FIG. 3 is a flowchart showing an output control procedure of the gas turbine power generation system by the gas turbine control device 7.
- the gas turbine control device 7 repeatedly executes the procedure of steps S101 to S111 of FIG. 3 during the power generation operation.
- Step S101-S107 When the procedure of FIG. 3 is started, the gas turbine control device 7 first inputs various signals (state quantity signal, rotation speed, MWD, RMW) (step S101). Subsequently, the gas turbine control device 7 performs output control to determine whether the change rate of FFD calculated based on the MWD falls within the limited range (range from the lower limit value to the upper limit value) output from the output change rate limiter 107. The determination is made by the processing unit 103 (step S102). If the rate of change of the FFD deviates from the limit range, the gas turbine control device 7 shifts the procedure to step S 108 (described later), and if it falls within the limit range, the output controller 103 sets IMWD according to the MWD.
- various signals state quantity signal, rotation speed, MWD, RMW
- Step S103 and output to the generator control device 10 (step S104). Subsequently, it is determined whether the deviation between the turbine rotational speed and the set rotational speed is within the allowable value (set value) (step S105). If the deviation is within the allowable value, the gas turbine control device 7 ends the procedure of FIG. If it exceeds the allowable value, the gas turbine control device 7 calculates the FFD and CIGV by the FFD calculator 104 and the IGV opening calculator 108 (step S106), and the fuel flow control valve 8 and the IGV 9 respectively to FFD and CIGV. It outputs and controls the fuel flow rate and the intake flow rate (step S107).
- the gas turbine control device 7 After executing the procedure of steps S106 and S107, the gas turbine control device 7 returns the procedure to step S105, and repeats the procedure of steps S106 and S107 until the deviation between the turbine rotational speed and the set value becomes less than the allowable value.
- the opening degree control of the IGV 9 will be supplemented.
- the turbine rotational speed decreases, the intake flow rate of the compressor 1 decreases, and the fuel / air ratio increases even with the same fuel flow rate, and the temperature of the combustion gas 22 increases. Therefore, it is desirable to control the opening degree of the IGV 9 by the IGV opening degree computing unit 108 so as to suppress the fluctuation of the intake flow rate. This is because the temperature of the combustion gas 22 is kept constant even if the rotation speed (turbine rotation speed) of the compressor 1 changes, and high reliability and output change speed can be ensured.
- the IGV 9 opens (the opening degree increases), and when the rotational speed increases, the IGV 9 closes (the opening degree decreases).
- the efficiency of the compressor 1 improves.
- the turbine rotational speed is decreased at the time of the output increase, the compressor efficiency is improved, the temperature of the discharge air of the compressor 1 is reduced, and the compressor power is also reduced.
- the increase in turbine output due to the reduction in compressor power is added to the increase in turbine output due to the fuel flow rate.
- the temperature of the combustion gas 22 is also lowered due to the decrease of the discharge air temperature, the change of the exhaust temperature accompanying the change of the turbine output is reduced, and the reliability is improved.
- the compressor efficiency increases when the rotational speed decreases with respect to the reference rotational speed, and decreases when the rotational speed increases with respect to the reference rotational speed.
- This may also provide the same beneficial synergy as the IGV control described above.
- Step S108-S111 If it is determined in the previous step S102 that the FFD change rate is out of the limited range, the gas turbine control device 7 calculates the turbine rotational speed when the generator load is controlled according to the MWD with the output controller 103 (Step S108).
- the method of prediction calculation is not limited, for example, the turbine rotational speed after load adjustment in the case where the deviation (difference from the limit value) of the MWD is adjusted by the generator load is calculated.
- the gas turbine control device 7 compares the predicted value of the turbine speed with the limit value of the speed limiter 102 or the protection limiter 101 with the output controller 103 (step S109), and if the predicted value is within the limit value.
- step S110 After changing the setting of the turbine rotational speed from the current value to the predicted value (step S110), the procedure moves to step S103 described above, and the IMWD is set according to the MWD.
- the output controller 103 does not change the setting of the turbine rotational speed, and the protection limiter 101 or the rotational speed limiter
- the IMWD is set in accordance with the limit value of 102 (step S111), and the procedure moves to step S104 described above.
- the fuel flow rate according to the MWD and the rate of change thereof are within the limited range and follow the MWD by fuel flow control. If possible, fuel flow control controls the turbine output according to the MWD.
- the load of the generator is controlled by the load regulator 11 to maintain the turbine rotational speed according to the change of the turbine output, and the fuel flow rate control while maintaining the turbine rotational speed
- the generator output follows the MWD.
- the frequency of the power generation output is controlled by the frequency regulator 12 to a set value (for example, 50 Hz or 60 Hz).
- control of the power generation output is attempted by changing the setting of the turbine speed, and if the predicted value of the turbine speed after changing is within the limit value, the setting of the turbine speed is temporarily predicted. It is changed to a value, and the generation output follows MWD by the change of generation load. For example, when the change rate of FFD according to MWD rises beyond the limit value, the setting of the turbine speed is lowered to increase the generator load, and the increase is larger than when FFD is increased at the limit change rate.
- the power generation output changes at a rate to follow the MWD.
- kinetic energy released as the rotational speed of the turbine shaft 13 changes is added to the energy recovered from the combustion gas 22, and the energy consumed by the generator motive power is temporarily increased.
- the rate of change of FFD according to MWD falls beyond the limit value
- the setting of the turbine speed is increased to reduce the generator load, which causes a larger drop than when FFD is reduced at the limit change rate.
- the power generation output changes at a rate to follow the MWD. In other words, the kinetic energy required to change the rotational speed of the turbine shaft 13 with respect to the energy recovered from the combustion gas 22 is reduced, and the energy consumed by the generator power is temporarily reduced.
- the power generation output follows the MWD at a rate of change that exceeds the maximum rate of change of the power generation output that can be realized only by the fuel flow rate control. While the procedure of FIG. 3 is repeatedly performed, the setting of the turbine rotational speed returns to the original value (a value corresponding to the generated output frequency of the setting). Also during this time, the frequency of the power generation output is controlled by the frequency regulator 12 to the set value.
- FIG. 4 is a diagram showing an example of the behavior of various outputs of the gas turbine power generation system with respect to the power demand. This example illustrates the case where the demand increases.
- the left row shows the case without the generator control unit 10 and the demand fluctuation is small
- the central row shows the case without the generator control unit 10 and the demand fluctuation is large
- the right row shows the present embodiment. It is a case of the form and represents a case where the demand fluctuation is large.
- the demand fluctuation (the change rate of the MWD) is small, it is possible to follow the demand fluctuation by the fuel flow rate while maintaining the turbine rotational speed (left row).
- the rate of change of the fuel flow rate required according to the demand fluctuation exceeds the limit value, the rate of increase of the fuel flow rate is limited, resulting in a shortage of generated output with respect to the power demand.
- the turbine rotational speed can not be maintained due to the lack of the turbine output, and the output frequency also decreases accordingly.
- the setting of the turbine rotational speed is lowered by the output controller 103 in response to the rapid increase of the demand fluctuation, and the generator load is adjusted by the load regulator 11 It is possible to compensate for the shortage of the turbine output due to the limitation and make the power generation output follow the sudden change of the power demand.
- the turbine speed is lower than the reference speed (dotted line), but the output frequency is maintained by the frequency regulator 12.
- the present embodiment can also cope with a sharp decrease in power demand. That is, when controlling the power generation output only by controlling the turbine output, if the reduction rate of the fuel flow rate according to the demand fluctuation exceeds the limit value, the setting of the turbine rotational speed is increased by the output controller 103 and the load regulator 11 As a result, the generator load is reduced, so that the excess of the power generation output is reduced to the kinetic energy of the turbine shaft 13, and the power generation output can be made to follow the rapid decrease of the power demand.
- the turbine speed is higher than the reference speed (dotted line), but the output frequency is maintained by the frequency regulator 12.
- the present embodiment it is possible to improve the response of the generated output to the power demand and contribute to the stabilization of the grid frequency. Further, since the power generation output can be adjusted regardless of the fuel flow rate control with respect to the rapid demand fluctuation, it is possible to suppress the thermal fatigue and the like of the high temperature parts.
- Power storage technology using storage batteries and flywheels is known as equipment that responds to sudden changes in power demand, but when applied to existing gas turbine power generation facilities, large-scale equipment such as flywheels and storage batteries are newly installed. It has to be costed. In addition, the loss is increased due to the bearing loss of the flywheel and the natural discharge of the rechargeable battery. On the other hand, in the case of this embodiment, compared with these cases, it can be applied inexpensively to existing gas turbine power generation equipment, and the merit is large in that the loss is also small.
- FIG. 5 is a view showing an example of a control screen by the output device.
- the control screen in the same figure shows that the operation mode corresponds to the output fluctuation only by the fuel flow control FFD single corresponding display unit 301, the output fluctuation using the setting change of the turbine rotational speed in addition to the fuel flow control
- a rotation speed conversion corresponding display unit 302 is provided to indicate that the operation mode corresponds to.
- the present operation mode can be confirmed by these displays.
- a trend graph display unit 303 is provided on the control screen, and the transition 304 of the power generation output ( ⁇ MWD) in this portion, and the power generation output (when the setting of the turbine rotational speed is not changed) by fuel flow control only
- the transition 305 and the transition 306 of the turbine rotational speed are displayed. Therefore, the manager or the like can grasp the operating state of the gas turbine power generation system by the trend graph display unit 303.
- FIG. 6 is a schematic view of a gas turbine power generation system according to a second embodiment of the present invention.
- the same parts as those in the first embodiment are indicated by the same reference numerals in the drawings and the explanation will be omitted.
- the difference between the gas turbine power generation system 200 of the present embodiment and the gas turbine power generation system 100 of the first embodiment is that the two-shaft gas turbine 27 is applied.
- the gas turbine power generation system 200 includes a two-shaft gas turbine 27, a motor generator 6, a gas turbine control device 7a, a generator control device 10, and the like.
- the two-shaft gas turbine 27 includes a gas generator 15 and a power turbine 16.
- the power turbine 16 has a configuration in which the low pressure turbine 2 b and the generator 5 are connected by a low pressure turbine shaft 13 b.
- the power turbine 16 basically rotates at a constant rotational speed in order to suppress the frequency fluctuation of the power generation output.
- the power generation output of the generator 5 is sent to a power consumer via a power cable.
- a rotation speed detector 26b is provided on the low pressure turbine shaft 13b.
- the gas generator 15 includes a compressor 1, a combustor 20, and a high pressure turbine 2a.
- the high pressure turbine 2a is connected to the compressor 1 via a gas generator shaft 13a. Since the gas generator 15 is mechanically separated from the power turbine 16 by the shaft, the gas generator 15 can be rotationally driven at a rotational speed different from that of the power turbine 16.
- a rotation number detector 26a is provided on the gas generator shaft 13a.
- the high pressure turbine 2 a obtains rotational power by the energy of the high temperature and high pressure combustion gas 22 from the combustor 20.
- the rotational power of the high pressure turbine 2a is transmitted to the compressor 1 via the gas generator shaft 13a to rotationally drive the compressor 1.
- the combustion gas 22 flows into the low pressure turbine 2 b of the power turbine 16 after a part of the energy is converted to the rotational power of the high pressure turbine 2 a.
- the low pressure turbine 2 b obtains rotational power by the energy of the combustion gas 22 which has driven the high pressure turbine 2 a.
- the rotational power of the low pressure turbine 2 b is transmitted to the generator 5 via the low pressure turbine shaft 13 b to rotationally drive the generator 5.
- the combustion gas 22 driving the low pressure turbine 2 b is discharged as the exhaust 14. Further, a part of the air compressed by the compressor 1 is extracted as the turbine cooling air 23, and is supplied to the high pressure turbine 2a and the low pressure turbine 2b without passing through the combustor 20.
- the motor generator 6 is a device that functions as both a motor and a generator, and is connected to the high pressure turbine shaft 13a.
- the motor generator 6 is connected to the power system of the generator 5 via the generator control device 10, and can exchange power with the power system.
- a part of the power generation output of the generator 5 is a high-pressure turbine by supplying a part of the power generation output of the generator 5 to the motor generator 6 by the generator control device 10 and driving the motor generator 6 as a motor.
- the kinetic energy of the shaft 13a is reduced, and the power generation output of the gas turbine power generation system 200 is suppressed.
- the gas turbine control device 7a has essentially the same configuration as the gas turbine control device 7 (see FIG. 2) of the first embodiment, but the limiting values for protection are the same for the high pressure turbine 2a and the low pressure turbine 2b. It may be set in consideration of each. Further, among the procedures described in the following flowchart, the control procedure of the motor generator 6 and the generator control device 10 is assumed to be borne by the output controller 103 (see FIG. 2).
- FIG. 7 is a flowchart showing an output control procedure of the gas turbine power generation system by the gas turbine control device 7a.
- the gas turbine control device 7a repeatedly executes the procedure of steps S201 to S214 of FIG. 7 during the power generation operation.
- Step S201-S210 Steps S201 to S210 are steps for causing the power generation output to follow the MWD without changing the setting of the rotational speed of the high pressure turbine 2a, with the change rate of FFD according to the MWD within the limited range.
- This is a procedure corresponding to steps S101 to S107 (see FIG. 3) of the embodiment. That is, when the procedure of FIG. 7 is started, the gas turbine control device 7a first inputs various signals (state quantity signal, rotational speed, MWD, RMW, etc.) (step S201), and the change rate of FFD according to MWD is It is judged by the output controller 103 whether or not it is within the limit range (step S202).
- the gas turbine control device 7a transfers the procedure to step S211 (described later) if the change rate of the FFD is out of the limited range, and if it is within the limited range, the motor generator 6 need not be driven.
- step S205 it is determined whether the deviation between the rotational speed of the high pressure turbine 2a and the set rotational speed is within the allowable value (set value) (step S205). If the deviation is within the allowable value, the gas turbine control device 7a transfers the procedure to step S206 (described later), and if exceeding the allowable value, the IGV opening calculator 108 calculates CIGV (step S207). The CIGV is output to control the intake flow rate (step S208). After executing the procedure of steps S207 and S208, the gas turbine control device 7a returns the procedure to step S205 and repeats steps S207 and S208 until the deviation between the rotational speed of the high pressure turbine 2a and the set value becomes less than the allowable value.
- the gas turbine control device 7a determines that the deviation between the rotational speed of the low pressure turbine 2b and the set rotational speed is within the allowable value (set value). It is determined whether or not (step S206). If the deviation is within the allowable value, the gas turbine control device 7a ends the procedure of FIG. If the deviation exceeds the allowable value, the gas turbine control device 7a calculates the FFD by the FFD calculator 104 (step S209), and outputs the FFD to the fuel flow control valve 8 to change the fuel flow rate (step S210) .
- the gas turbine control device 7a After executing the procedure of steps S209 and S210, the gas turbine control device 7a returns the procedure to step S206 and repeats steps S209 and S210 until the deviation between the rotational speed of the low pressure turbine 2b and the set value becomes less than the allowable value.
- balance adjustment control is performed so that the rotational power obtained by the high pressure turbine 2a and the consumption power of the compressor 1 become equal.
- This control is generally based on the adjustment of the rotational speed of the gas generator 15 and the intake flow rate of the compressor 1. For example, when the rotation speed of the gas generator 15 is higher than the set value, the consumption power of the compressor 1 is increased and the rotation speed is decreased by increasing the opening of the IGV 9 to increase the intake flow rate. Conversely, the rotation speed of the gas generator 15 can be increased by decreasing the opening degree of the IGV 9.
- the FFD corresponding to the MWD is output to the fuel flow control valve 8, and the rotational power of the low pressure turbine 2 b is adjusted to the power generation output of the generator 5.
- the rotational speed of the power turbine 16 is controlled to be substantially constant.
- the gas turbine control device 7a opens the IGV 9 so that the rotational speed of the gas generator 15 approaches the set value. Control.
- the rotational speed of the gas generator 15 can not be uniquely determined with respect to the power generation output and can be changed.
- Step S211-S214 If it is determined in step S202 that the FFD change rate is out of the limitation range, the gas turbine control device 7a outputs the rotational speed of the high pressure turbine 2a when the motor generator 6 is driven according to the MWD.
- the prediction calculation is performed at 103 (step S211). Although the method of the prediction calculation is not limited, for example, the number of revolutions of the high pressure turbine 2a as a result of generating or consuming the generated output of the deviation (difference from the limit value) of the MWD by the motor generator 6 is calculated.
- the gas turbine control device 7a compares the predicted value of the rotational speed of the high pressure turbine 2a with the limit value of the rotational speed limiter 102 or the protective limiter 101 by the output controller 103 (step S212), and the predicted value is within the limit value. If so, the setting of the number of revolutions of the high pressure turbine 2a is changed from the current value to the predicted value (step S213), and the deviation of the MWD is set to IMWD (step S214). Move. On the other hand, when the predicted value exceeds the limit value in the previous step S212 and the power generation output can not be made to follow the MWD even if the motor generator 6 is driven, the gas turbine control device 7a rotates the high pressure turbine 2a. The procedure moves to step S203 described above without payment of the number setting.
- the motor generator 6 is not driven as a generator or a motor, and the power generation output is generated by the fuel flow rate control Make MWD follow. Since the rotational speed of the low pressure turbine 2b does not change, the output frequency of the generator 5 is also maintained.
- the load controller 11 is controlled by the gas turbine control device 7a to apply a power generation load to the motor generator 6, and the rate of change of FFD is limited.
- the power generation output (the sum of the power generation outputs of the generator 5 and the motor generator 6) is increased at a larger change rate than when the value of.
- the load controller 11 is controlled by the gas turbine control device 7a, and a part of the generator output of the generator 5 is the motor of the motor generator 6.
- the power generation output is reduced at a larger change rate than when the fuel flow rate is reduced at the limited change rate.
- the power generation output changes at a rate of change exceeding the maximum rate of change of the power generation output that can be realized only by the fuel flow rate control, and follows the MWD. While the procedure of FIG. 7 is repeatedly performed, the setting of the rotational speed of the high pressure turbine 2a returns to the original value (a value corresponding to the generated output frequency of the setting).
- the frequency of the output compensated from the motor generator 6 to the power system is controlled by the frequency regulator 12 to a set value (for example, 50 Hz or 60 Hz).
- the power generation output can be controlled by rapidly following a sudden change in the power demand without depending on the fuel flow rate control, so that the same effect as that of the first embodiment can be obtained.
- the generator control device 10 can be smaller in capacity than the first embodiment, and the main part of the invention can be configured at low cost. That is, in the first embodiment, the generator control device 10 needs the same capacity as the total power generation output of the gas turbine 17 in order to process the total power generation output of the gas turbine 17 with the generator control device 10.
- the low pressure turbine 2b which bears most of the output, is driven at a constant speed.
- the generator control device 10 is required only for the motor generator 6 on the side of the high pressure turbine 2a performing variable speed operation, so the capacity of the generator control device 10 can be reduced. For example, when it is desired to change the output corresponding to 10% of the rated power generation output in addition to the output change due to the fuel flow rate, it is sufficient to use the generator control device 10 having a capacity of 10% of the rated power generation output.
- FIG. 8 is a diagram showing an example of the behavior of various outputs of the gas turbine power generation system according to the present embodiment with respect to the power demand. This example illustrates the case where the demand increases.
- This figure corresponds to FIG. 4 of the first embodiment, and the left row shows the case where the motor generator 6 and the generator control device 10 are not present, and when the demand fluctuation is small, the center row shows the motor generator 6 and the case where the generator control apparatus 10 is not present and the demand fluctuation is large, the right column shows the case of the present embodiment and the demand fluctuation is large.
- the power generation output can be made to follow the power demand by the fuel flow rate. As a result, the rotational speed of the low-pressure turbine shaft 13b is reduced and the frequency of the power generation output is also reduced.
- the present embodiment energy is exchanged between the electric power system and the gas generator 15 by driving the motor generator 6 as a generator or a motor by the generator control device 10, in this case
- the power generation output is compensated by driving the motor generator 6 as a generator.
- the power generation output follows the sudden change in the power demand.
- the rotational speed of the high-pressure turbine 2a is reduced because the rotational power is partially converted to electric energy by the motor generator 6, the output frequency of the motor generator 6 is adjusted to the set value by the frequency adjuster 12. Ru.
- the low pressure turbine 2b rotates independently of the high pressure turbine 2a, the rotational speed does not change and the output frequency does not change. Therefore, the grid frequency is also stable.
- FIG. 8 exemplifies the case where the power demand increases, the same is true when it decreases.
- FIG. 9 is a schematic view of a gas turbine power generation system according to a third embodiment of the present invention.
- the same parts as those in the embodiment already described are indicated by the same reference numerals in the drawings and the explanation will be omitted.
- the difference between the gas turbine power generation system 300 of the present embodiment and the gas turbine power generation system 200 of the second embodiment is that the power system is provided with a renewable energy power generation device 30. Since the renewable energy generator 30 is connected to the power system, a larger fluctuation range of the power generation output is required.
- a renewable energy generator 30 is connected to the two-shaft gas turbine 27 through a power system.
- the renewable energy power generation device 30 various power generation devices that generate electric power using renewable energy such as a wind power generation device, a solar power generation device, or a wave power generation device can be applied, for example.
- a power generator is applied in the gas turbine power generation system 300.
- a detector 31 for fluctuation prediction that detects a power fluctuation prediction value of the renewable energy power generation device 30, and a power generation output of the renewable energy power generation device 30 based on a signal of the detector 31.
- a predicted value calculator 32 is provided to calculate a predicted value (variation).
- the detector 31 can use an anemometer provided at the windward point of the wind power generator, a receiver of weather information, or the like. Moreover, when a solar power generation device is used, an illuminance meter or the like installed in the surrounding area can be used for the detector 31 in addition to the weather information receiving device.
- the predicted value calculator 32 outputs the power fluctuation predicted value (hereinafter referred to as PMWD) of the renewable energy power generation device 30 to the gas turbine control device 7b.
- the FFD calculator 104 (see FIG. 2) of the gas turbine control device 7b inputs PMWD together with RMW (actual power generation amount), sets the number of rotations of the high pressure turbine 2a based on PMWD, and sets the number of rotations after setting.
- the fuel flow rate value and the opening degree of the IGV 9 are calculated so that
- FIG. 10 is a flowchart showing an output control procedure of the gas turbine power generation system by the gas turbine control device 7b.
- steps S301, S302 and S307-S318 in the same figure are respectively the same as steps S201-S214 in the second embodiment.
- steps S303 to S306 are added between steps S302 and S307.
- steps S303 to S306 will be described.
- Step S303-S306 This procedure is a procedure of changing the set rotational speed of the high pressure turbine 2a according to the above-mentioned PMWD, and secures an adjustment allowance of the output of the high pressure turbine 2a according to the fluctuation prediction of the power generation output of the renewable energy power generation device 30. It is a procedure. Specifically, the gas turbine control device 7b first inputs PMWD to the FFD calculator 104 (step S303), and analyzes the PMWD by the FFD calculator 104 (step S304). In the analysis of PMWD, calculation of time change (rate of change) of PMWD is performed. Subsequently, the gas turbine control device 7b sets a standby condition by the FFD calculator 104 (step S305).
- the standby condition is an adjustment allowance of the rotational speed of the high pressure turbine 2a to be secured in preparation for the fluctuation of the power generation output of the renewable energy power generation device 30.
- the set rotational speed of the high pressure turbine 2a is set higher than the present to secure a reduction in the turbine output of the high pressure turbine 2a.
- the set rotational speed of the high pressure turbine 2a is set lower than the present to secure an increase in the turbine output of the high pressure turbine 2a.
- the setting rotation speed after a change is called standby value for convenience.
- the gas turbine control device 7b changes the set rotational speed of the high pressure turbine 2a by the FFD calculator 104 to the standby value obtained in step S305 (step S306), and shifts the procedure to step S307 described above.
- the rotational speed of the high pressure turbine 2a is controlled to the rotational speed after the setting change in the subsequent steps S309, S311, and S312. Specifically, by reducing the opening degree of the IGV 9 and reducing the power consumption of the compressor 1, the rotational speed of the high pressure turbine 2a is increased. On the other hand, the rotational speed of the high pressure turbine 2a is lowered by increasing the power consumption of the compressor 1 by increasing the opening degree of the IGV 9.
- the number of revolutions of the turbine shaft can be predicted by a function using an amount of surplus power that is expected to be generated only by the power change due to the fuel flow rate, the moment of inertia of the turbine shaft, and the number of revolutions.
- the convertible amount of the turbine rotational power to the electric power and the convertible amount of the electric power to the turbine rotational power are limited by the upper limit value and the lower limit value of the rotational speed of the turbine shaft.
- the set rotational speed is operated with the reference value by predicting the fluctuation of the power generation output of the renewable energy power generation apparatus 30 and adjusting the set rotational speed of the high pressure turbine 2a in advance. Since the adjustment allowance of the turbine output is wider than in the case, the absorption allowance of the fluctuation of the power generation output of the renewable energy power generation device 30 can be widely secured.
Abstract
Description
1.ガスタービン発電システム
図1は本発明の第1の実施の形態に係るガスタービン発電システムの概略図である。
図2はガスタービン制御装置7の機能ブロック図である。
図3はガスタービン制御装置7によるガスタービン発電システムの出力制御手順を表すフローチャートである。
ガスタービン制御装置7は、図3の手順を開始すると、まず各種信号(状態量信号、回転数、MWD、RMW)を入力する(ステップS101)。ガスタービン制御装置7は、続いてMWDを基に演算したFFDの変化率が出力変化率リミッター107から出力された制限範囲(下限値から上限値までの範囲)に納まっているか否かを出力制御器103で判定する(ステップS102)。ガスタービン制御装置7は、FFDの変化率が制限範囲から逸脱していればステップS108(後述)に手順を移し、制限範囲に納まっていれば、出力制御器103でMWDに応じてIMWDを設定し(ステップS103)、発電機制御装置10に出力する(ステップS104)。続いてタービン回転数と設定回転数との偏差が許容値(設定値)以内であるか否かを判定する(ステップS105)。偏差が許容値以内であれば、ガスタービン制御装置7は同図の手順を終了し、再び開始する。許容値を超えていれば、ガスタービン制御装置7はFFD演算器104及びIGV開度演算器108でFFD及びCIGVを演算し(ステップS106)、燃料流量制御弁8及びIGV9にそれぞれFFD及びCIGVを出力して燃料流量及び吸気流量を制御する(ステップS107)。このとき、FFD演算器104で演算されたFFDがロードリミッター105等による制限値を超えていれば、前述した通りFFDは制限される。ステップS106,S107の手順を実行したら、ガスタービン制御装置7は、ステップS105に手順を戻し、タービン回転数と設定値との偏差が許容値以下になるまでステップS106,S107の手順を繰り返す。
先のステップS102でFFD変化率が制限範囲から外れていると判定した場合、ガスタービン制御装置7は、MWDに応じて発電機負荷を制御した場合のタービン回転数を出力制御器103で予測演算する(ステップS108)。予測演算の方法は限定されないが、例えばMWDの逸脱分(制限値との差分)を発電機負荷で調整した場合における負荷調整後のタービン回転数を演算する。次に、ガスタービン制御装置7は、タービン回転数の予測値を回転数リミッター102や保護リミッター101の制限値と出力制御器103で比較し(ステップS109)、予測値が制限値以内であれば、タービン回転数の設定を現在の値から予測値に変更した上で(ステップS110)、前述したステップS103に手順を移してMWDに応じてIMWDを設定する。一方、予測値が制限値を超えていてMWDに応じた発電機制御が困難である場合には、出力制御器103は、タービン回転数の設定を変更することなく、保護リミッター101又は回転数リミッター102の制限値に応じてIMWDを設定し(ステップS111)、前述したステップS104に手順を移す。
図4は電力需要に対するガスタービン発電システムの各種出力の挙動の一例を表した図である。この例では需要が増大する場合を例示している。同図において、左列は発電機制御装置10がない場合であって需要変動が小さいとき、中央列は発電機制御装置10がない場合であって需要変動が大きいとき、右列は本実施の形態の場合であって需要変動が大きいときを表している。
図5は出力装置による制御画面の一例を表す図である。
図6は本発明の第2の実施の形態に係るガスタービン発電システムの概略図である。第1の実施の形態と同様の部分には同図において既出図面と同符号を付して説明を省略する。
ステップS201-S210は、MWDに応じたFFDの変化率が制限範囲内であって高圧タービン2aの回転数の設定を変更せずに発電出力をMWDに追従させる手順であり、第1の実施の形態のステップS101-S107(図3参照)に相当する手順である。すなわち、ガスタービン制御装置7aは、図7の手順を開始すると、まず各種信号(状態量信号、回転数、MWD、RMW等)を入力し(ステップS201)、MWDに応じたFFDの変化率が制限範囲内であるか否かを出力制御器103で判定する(ステップS202)。ガスタービン制御装置7aは、FFDの変化率が制限範囲から外れていればステップS211(後述)に手順を移し、制限範囲内であれば、電動発電機6を駆動する必要がないので、出力制御器103でIMWDをゼロ(IMWD=0)に設定して(ステップS203)、発電機制御装置10に出力する(ステップS204)。
先のステップS202でFFD変化率が制限範囲から外れていると判定した場合、ガスタービン制御装置7aは、MWDに応じて電動発電機6を駆動した場合の高圧タービン2aの回転数を出力制御器103で予測演算する(ステップS211)。予測演算の方法は限定されないが、例えばMWDの逸脱分(制限値との差分)の発電出力を電動発電機6で発電又は消費した結果の高圧タービン2aの回転数を演算する。次に、ガスタービン制御装置7aは、高圧タービン2aの回転数の予測値を回転数リミッター102や保護リミッター101の制限値と出力制御器103で比較し(ステップS212)、予測値が制限値以内であれば、高圧タービン2aの回転数の設定を現在の値から予測値に変更し(ステップS213)、MWDの逸脱分をIMWDに設定した上で(ステップS214)、前述したステップS204に手順を移す。一方、先のステップS212で予測値が制限値を超えていて電動発電機6を駆動してもMWDに発電出力を追従させられない場合には、ガスタービン制御装置7aは、高圧タービン2aの回転数の設定を経納することなく前述したステップS203に手順を移す。
図9は本発明の第3の実施の形態に係るガスタービン発電システムの概略図である。既に説明した実施の形態と同様の部分には同図において既出図面と同符号を付して説明を省略する。
この手順は、前述したPMWDに応じて高圧タービン2aの設定回転数を変更する手順であり、再生可能エネルギー発電装置30の発電出力の変動予測に応じて高圧タービン2aの出力の調整代を確保する手順である。具体的には、ガスタービン制御装置7bは、まずPMWDをFFD演算器104に入力し(ステップS303)、FFD演算器104でPMWDを分析する(ステップS304)。PMWDの分析では、PMWDの時間変化(変化率)の演算等が行われる。続いて、ガスタービン制御装置7bは、FFD演算器104で待機条件を設定する(ステップS305)。待機条件とは、再生可能エネルギー発電装置30の発電出力の変動に備えて確保すべき高圧タービン2aの回転数の調整代のことである。例えばPMWDの変化率から今後再生可能エネルギー発電装置30の発電出力の増大が見込まれる場合には、高圧タービン2aのタービン出力の下げ代を確保すべく高圧タービン2aの設定回転数を現状よりも高く設定する。反対に、今後再生可能エネルギー発電装置30の発電出力の減少が見込まれる場合には、高圧タービン2aのタービン出力の上げ代を確保すべく高圧タービン2aの設定回転数を現状よりも低く設定する。以降、変更後の設定回転数を便宜的に待機値という。但し、待機値は、リミッターにより制限されるので、許容される高圧タービン回転数の上限及び下限値を逸脱することはない。そして、ガスタービン制御装置7bは、FFD演算器104で高圧タービン2aの設定回転数をステップS305で求めた待機値に変更し(ステップS306)、前述したステップS307に手順を移す。
本発明の技術的範囲は以上の実施の形態の態様に限定されるものではなく、種々の変形例が含まれ得る。例えば、前述した各実施の形態に備わった構成要素は全てが必須のものではなく、発明の要部ではない要素は適宜省略可能である。また、各実施の形態の構成要素は、機能や役割が共通する他の要素で代替することができる。また、各実施の形態は相互に又は部分的に組み合わせ可能である。更には、上記の各構成、機能、処理部、処理手段等は、それらの一部又は全部を、例えば集積回路で設計する等によりハードウェアで実現してもよい。また、上記の各構成、機能等は、プロセッサがそれぞれの機能を実現するプログラムを解釈し、実行することによりソフトウェアで実現してもよい。
2 タービン
2a 高圧タービ
2b 低圧タービン
5 発電機
6 電動発電機
7,7a,7b ガスタービン制御装置
11 負荷調整器
12 周波数調整器
15 ガスジェネレータ
16 パワータービン
20 燃焼器
30 再生可能エネルギー発電装置
32 予測値演算器(予測装置)
100 ガスタービン発電システム
103 出力制御装置
104 FFD演算器(燃料流量制御装置)
107 出力変化率リミッター(変化率制限装置)
108 IGV開度演算器(吸気流量制御装置)
110 出力装置
200 ガスタービン発電システム
300 ガスタービン発電システム
MWD ガスタービン出力指令
Claims (8)
- 連結した圧縮機及び高圧タービン、並びに前記圧縮機からの圧縮空気を燃料とともに燃焼し高圧タービンを駆動する燃焼器を有するガスジェネレータと、
前記ガスジェネレータを駆動した燃焼ガスで駆動する低圧タービン及び前記低圧タービンに連結した発電機を有するパワータービンと、
前記ガスジェネレータにより駆動し前記発電機の電力系統と接続した電動発電機と、
ガスタービン出力指令に応じて前記燃焼器への燃料流量を制御して前記発電機の発電出力を調整する燃料流量制御装置と、
前記燃料流量制御装置による燃料流量の変化率を制限する変化率制限装置と、
前記電動発電機の出力周波数を調整する周波数調整器と、
前記電動発電機の発電負荷を調整する負荷調整器と、
ガスタービン出力指令に応じた前記燃料流量の変化率が制限値を超えて上昇する場合、前記ガスタービン出力指令に応じて前記負荷制御器を制御して前記電動発電機に発電負荷を与え、前記制限値で燃料流量を増加させる場合よりも大きな変化率で発電出力を増加させる出力制御装置と
を備えたことを特徴とするガスタービン発電システム。 - 請求項1のガスタービン発電システムにおいて、
前記出力制御装置は、ガスタービン出力指令に応じた前記燃料流量の変化率が制限値を超えて下降する場合、前記ガスタービン出力指令を基に前記負荷制御器に指令し、前記発電機の一部の発電出力を前記電動発電機の電動機駆動に用いて前記ガスジェネレータの運動エネルギーに変換し、前記制限値で燃料流量を減少させる場合よりも大きな変化率で発電出力を減少させる
ことを特徴とするガスタービン発電システム。 - 請求項1のガスタービン発電システムにおいて、前記圧縮機の吸気流量を維持するように制御する吸気流量制御装置を備えたことを特徴とするガスタービン発電システム。
- 請求項1のガスタービン発電システムにおいて、前記圧縮機が、基準回転数よりも低速で回転する場合に効率が上昇し、基準回転数よりも高速で回転する場合に効率が低下するように設計されていることを特徴とするガスタービン発電システム。
- 吸い込んだ空気を圧縮する圧縮機と、
前記圧縮機からの圧縮空気を燃料とともに燃焼する燃焼器と、
前記燃焼器からの燃焼ガスにより駆動するタービンと、
前記タービンにより駆動する発電機と、
ガスタービン出力指令に応じて前記燃焼器への燃料流量を制御して発電出力を調整する燃料流量制御装置と、
前記燃料流量制御装置による燃料流量の変化率を制限する変化率制限装置と、
前記発電機の出力周波数を調整する周波数調整器と、
前記発電機の発電負荷を調整する負荷調整器と、
ガスタービン出力指令に応じた前記燃料流量の変化率が制限範囲から外れる場合、前記タービンの回転数の設定を変更した上で前記ガスタービン出力指令に応じて前記負荷制御器を制御して発電負荷を制御し、前記制限値で燃料流量を変化させる場合よりも大きな変化率で発電出力を変化させる出力制御装置と
を備えたことを特徴とするガスタービン発電システム。 - 請求項1-5のいずれかのガスタービン発電システムにおいて、
前記電力系統と接続した再生可能エネルギー発電装置と、
前記再生可能エネルギー発電装置の発電出力の変動を予測する予測装置と、
前記予測装置による予測値を基に前記再生可能エネルギー発電装置の発電出力の変動を吸収するタービン出力の調整代を広げるガスタービン制御装置と
を備えたことを特徴とするガスタービン発電システム。 - 請求項1のガスタービン発電システムにおいて、運転モードを表す表示を含む制御画面を表示する出力装置を備えたことを特徴とするガスタービン発電システム。
- ガスタービン出力指令に応じた燃料流量の変化率が制限範囲から外れる場合、タービン回転数の設定を変更して発電負荷を制御し、制限値で燃料流量を変化させる場合よりも大きな変化率で発電出力を変化させることを特徴とするガスタービン発電システムの発電出力制御方法。
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PCT/JP2013/057784 WO2014147738A1 (ja) | 2013-03-19 | 2013-03-19 | ガスタービン発電システム |
DE112013006847.8T DE112013006847T5 (de) | 2013-03-19 | 2013-03-19 | Gasturbinenstromerzeugungssystem |
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JP2017020505A (ja) * | 2015-07-13 | 2017-01-26 | ゼネラル・エレクトリック・カンパニイ | ガスタービン出力増大システム |
JP2018017196A (ja) * | 2016-07-29 | 2018-02-01 | 株式会社日立製作所 | ガスタービン発電装置の制御装置、ガスタービン発電装置の制御方法およびガスタービン発電装置 |
JP2019143563A (ja) * | 2018-02-22 | 2019-08-29 | 三菱日立パワーシステムズ株式会社 | 二軸ガスタービン発電設備、その制御装置、及びその制御方法 |
JP2020165323A (ja) * | 2019-03-28 | 2020-10-08 | 三菱重工業株式会社 | 1軸式ガスタービンの運転制御装置、運転制御方法及びプログラム |
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