JPWO2013080386A1 - Solar thermal combined cycle power plant - Google Patents

Abstract

Solar heat which heats a heat storage medium with a 1st heat collector (1), and heat-exchanges the said heat storage medium and a part of feed water from a feed water pump (8) with a heat exchanger (9), and produces | generates warm water. The hot water generated by the use hot water generation unit (30) and the solar heat use hot water generation unit (30) is pressurized by an intake spray water pump (13), and the pressurized hot water is gasified by an intake spray device (20). The hot water generated by the solar-heated intake spray unit (31) sprayed on the intake air of the turbine (3) and the solar-heated hot water generating unit (30) is evaporated by the second heat collector (2). A solar heat generation steam generation unit (32) for generating steam and supplying the steam to the steam turbine (5).

Description

  The present invention relates to a solar combined cycle power plant, and more particularly to a combined cycle power plant including a heat collector that obtains thermal energy from the sun.

  One of the power generation plants that support industrial power uses a fossil resource such as natural gas, oil, and coal seam gas to drive and generate power from a gas turbine, and to drive and generate power from steam generated by the exhaust heat of the gas turbine. There is a combined cycle power plant.

  In such a combined cycle power plant, a heating facility that heats a heat medium with sunlight, a heat exchanger that heats and evaporates feed water with the heat medium supplied from the heating facility, and steam generated in the heat exchanger It has a pipe that joins the steam obtained by the exhaust heat of the gas turbine and supplies it to the steam turbine, and even if the temperature of the heat medium changes due to fluctuations in sunshine conditions, etc., it has a thermal effect on the heat exchanger. A solar combined power generation facility (solar thermal combined cycle power plant) is disclosed that can be mitigated and that can mitigate the effects of fluctuations in the supply steam flow caused by temperature fluctuations of the heat medium (for example, patents) Reference 1).

JP 2008-121383 A

  In the case of the above-described solar thermal combined cycle power plant, the heat energy that the heat medium brings into the heat exchanger is calculated, and the flow rate of the heat medium flowing from the heating facility to the heat exchanger is controlled according to the heat energy. The thermal influence on the exchanger can be mitigated.

  By the way, the gas turbines that make up a solar thermal combined cycle power plant operate when the atmospheric temperature rises in the summer, or when the atmospheric temperature is high throughout the year, such as low latitudes, or when the atmospheric temperature is low. In comparison, it is known that the air intake amount of the compressor is relatively decreased, and the power generation efficiency and the power generation output are decreased.

  In the solar combined cycle power plant described in Patent Document 1, no mention is made of the power generation efficiency of the gas turbine and the decrease in power generation output when the atmospheric temperature rises. For this reason, when operating in the summer or in low latitude areas, the output of the gas turbine decreases due to an increase in atmospheric temperature, so the solar combined cycle power plant as a whole can sufficiently obtain the effect of increasing the output of the steam turbine due to sunlight. It may not be possible.

  In addition, the effect of increasing the output by sunlight is not obtained when the sunlight is temporarily shielded due to the time when sufficient solar radiation is not obtained (for example, in the evening) or due to an increase in cloud cover. There was a problem that the output and efficiency of the cycle power plant could not be prevented.

  The present invention has been made on the basis of the above-mentioned matters, and the object thereof is to suppress a decrease in power generation efficiency and power generation output of the gas turbine even under a high atmospheric temperature condition, and even if the sunshine condition fluctuates, the entire plant is further A solar combined cycle power plant capable of improving efficiency and increasing output is provided.

  In order to achieve the above object, a first invention includes a gas turbine that is driven using a combustion gas of a gas turbine fuel, an exhaust heat recovery boiler that generates steam by exhaust heat from the gas turbine, and the exhaust gas. A steam turbine driven by steam from a heat recovery boiler, a condenser that cools the steam from the steam turbine to generate feed water, and pumps the feed water stored in the condenser to the exhaust heat recovery boiler A solar combined cycle power plant including a water supply pump, wherein a heat storage medium is heated by a first heat collector, and heat exchange is performed between the heat storage medium and a part of water supplied from the water supply pump by a heat exchanger. The hot water generation unit for generating hot water and the hot water generated by the solar water use hot water generation unit are pressurized by an intake spray water pump, and the pressurized hot water is supplied by an intake spray device. The solar-heated intake spray unit sprayed on the intake air of the gas turbine and the hot water generated by the solar-heated hot water generating unit are evaporated in a second heat collector to generate steam, and the steam is converted into the steam And a solar heat utilization steam generation unit that supplies the turbine.

  Further, the second invention is a gas turbine driven using combustion gas of gas turbine fuel, an exhaust heat recovery boiler that generates steam by exhaust heat from the gas turbine, and steam from the exhaust heat recovery boiler. Solar heat provided with a driving steam turbine, a condenser that cools the steam from the steam turbine to generate feed water, and a feed water pump that pumps the feed water stored in the condenser to the exhaust heat recovery boiler In the combined cycle power plant, the first heat collector that heats the heat storage medium by solar thermal energy, and the heated heat storage medium and a part of the water supplied from the water supply pump are subjected to heat exchange to generate hot water. A heat exchanger to be generated, a heat storage tank for storing the heat storage medium after heat exchange by the heat exchanger, and a circulation pump for pumping the heat storage medium from the heat storage tank to the first heat collector A first hot water supply pipe that branches from an outlet of the heat exchanger and supplies the hot water to the intake spray device, an intake spray water pump that is provided in the first hot water supply pipe and pressurizes the hot water, An intake spray device that sprays hot water pressurized by an intake spray water pump onto the intake air of the gas turbine, and an upstream side of the intake spray device of the first hot water supply pipe, controls the flow rate of the sprayed hot water And a regulating valve to be provided.

  Further, according to a third invention, in the second invention, a second hot water supply pipe branched from an outlet of the heat exchanger and supplying the hot water to the second heat collector, and the hot water by solar thermal energy. A second heat collector that generates steam by evaporating the steam, a steam supply pipe that supplies the steam generated by the second heat collector to the turbine, and a steam supply pipe that is provided in the steam supply pipe and supplies the turbine A first regulating valve that controls the flow rate of the steam, a steam return pipe that supplies the steam generated by the second heat collector to the condenser, and the steam return pipe. And a second regulating valve for controlling the flow rate of the steam returned to the vessel.

  In a fourth aspect based on the third aspect, the turbine includes a high-pressure steam turbine and an intermediate-pressure steam turbine, and the steam supply pipe discharges the steam generated by the second heat collector. It is mixed with the generated steam of the heat recovery boiler and supplied to the inlet of the intermediate pressure steam turbine.

  Furthermore, a fifth invention is the third or fourth invention, provided at the outlet side of the heat exchanger, provided at a temperature detector for measuring the temperature of the hot water, and at the steam supply pipe, A steam temperature detector for measuring the temperature of the steam generated by the heat collector of No. 2, and the measured values of the temperature detector and the steam temperature detector are taken in, and the opening of the regulating valve and the first regulating valve And a control device for controlling the operation.

  Further, a sixth invention according to the fifth invention further includes a water-saving mode selection switch for an operator to specify whether the operation is valid or invalid, and the control device is valid or invalid when the operation is designated by the water-saving mode selection switch. The procedure for capturing the signal of the above, the procedure for comparing the measured value of the steam temperature detector with a predetermined temperature at which the steam supply can be started, and the measured value of the temperature detector and the predetermined hot water spray can be started By comparing the results of the three procedures and the truth of the results of the three procedures, both the increased output of the gas turbine and the increased output of the steam turbine, the increased output of the gas turbine and the increased output of the steam turbine Either one of the operation modes is determined to be one of the denial of the increase output of the gas turbine and the negation of the increase output of the steam turbine, and the opening degrees of the adjustment valve and the first adjustment valve are determined. The And executes the Gosuru procedures.

  According to the present invention, it comprises an intake spray device and a heat storage tank that stores heat energy from the sun via a heat storage medium, and sprays high-pressure hot water obtained from the heat energy of the heat storage tank to the compressor inlet, Since boiling under reduced pressure is performed in the air and inside the compressor, it is possible to suppress a decrease in power generation efficiency and power generation output of the gas turbine even under conditions where the atmospheric temperature is high. Further, the output of the gas turbine can be increased and the efficiency can be improved even during a time period when sufficient solar radiation cannot be obtained (for example, in the evening) or after sunset. As a result, it is possible to provide a solar combined cycle power plant capable of further improving efficiency and increasing output as a whole plant even if the sunshine condition varies.

It is a system configuration figure showing one embodiment of the solar thermal combined cycle power plant of the present invention. It is a characteristic view which shows an example of the load request | requirement instruction | command in one Embodiment of the solar thermal combined cycle power plant of this invention. It is a characteristic view which shows the time change of the retained heat amount of the thermal storage tank which comprises one Embodiment of the solar thermal combined cycle power plant of this invention. It is a characteristic view which shows the time change of the heat collecting amount of the 2nd heat collector which comprises one embodiment of the solar combined cycle power plant of this invention. It is a characteristic view which shows the time change of the power generation output in one Embodiment of the solar combined cycle power plant of this invention. It is a schematic block diagram which shows the control system which comprises one Embodiment of the solar thermal combined cycle power plant of this invention. It is a control block diagram which shows the solar thermal power generation control system which comprises the control system shown in FIG. It is a table | surface figure which shows the operation mode in one embodiment of the solar thermal combined cycle power plant of this invention. It is a flowchart figure which shows the processing content of the operation mode switching in one embodiment of the solar combined cycle power plant of this invention.

Embodiments of a solar combined cycle power plant according to the present invention will be described below with reference to the drawings. FIG. 1 is a system configuration diagram showing an embodiment of a solar combined cycle power plant of the present invention.
FIG. 1 shows a gas turbine 3, an exhaust heat recovery boiler 4, a steam turbine 5, a generator 6, a condenser 7, an intake spray device 20, a first heat collector 1, a second heat collector 2, and a heat exchanger. 9 shows a system flow of a solar combined cycle power plant having 9 and a heat storage tank 10.

  In FIG. 1, the gas turbine 3 includes a compressor 3 a, a turbine 3 b, a combustor 3 c, and a drive shaft 15. The compressor 3a sucks and pressurizes air and supplies it as combustion air to the combustor 3c. The combustor 3c mixes and burns the combustion air with fuel to generate high-temperature combustion gas. The combustion gas drives the turbine 3 b and drives the compressor 3 b, the steam turbine 5, and the generator 6 through the drive shaft 15.

  The exhaust heat recovery boiler 4 generates steam by the exhaust gas from the gas turbine 3 and supplies the steam to the steam turbine 5. The feed water supplied to the exhaust heat recovery boiler 4 is stored in the lower part of the condenser 7 and is pumped to the exhaust heat recovery boiler 4 by the feed water pump 8.

  The steam turbine 5 includes a high-pressure steam turbine 5 a and an intermediate-pressure steam turbine 5 b connected to the gas turbine 3 by a drive shaft 15, and uses the high-pressure steam generated in the exhaust heat recovery boiler 4 to To drive. The steam after working in the high-pressure steam turbine 5a is returned again to the exhaust heat recovery boiler 4 and reheated in a heat exchanger (not shown) in the exhaust heat recovery boiler 4. The intermediate pressure steam turbine 5b is driven using the reheated steam.

  The solar thermal combined cycle power plant 50 according to the present embodiment has a configuration similar to that of the conventional combined cycle plant, and further uses a solar thermal hot water generating unit 30 that generates and stores hot water using solar heat, and compresses the hot water. The solar heat utilization intake spray unit 31 which sprays on the entrance of the machine 3a, and the solar heat utilization steam generation unit 32 which produces | generates a vapor | steam from warm water with a solar heat, and supplies it to a steam turbine are provided.

  The solar heat-use hot water generating unit 30 includes a first heat collector 1 that heats a heat storage medium that is supplied using infrared B contained in sunlight as a heat source, and a heat storage medium that is heated to a high temperature by the first heat collector 1. A heat exchanger 9 that can supply hot water by exchanging heat with the water supplied from the water supply pump 8, a heat storage tank 10 that stores a heat storage medium after the water is heated by the heat exchanger 9, and heat storage An oil circulation pump 11 that pumps the heat storage medium from the tank 10 to the first heat collector 1 is provided. The first heat collector 1 and the heat exchanger 9, the heat exchanger 9 and the heat storage tank 10, and the heat storage tank 10 and the first heat collector 1 are connected by piping. The heat storage medium is circulated between these pipes and each component device by the oil circulation pump 11. In the present embodiment, a trough solar collector is used as the first heat collector 1, and oil having a high flash point is used as the heat storage medium.

  The solar-heated intake spray unit 31 is provided in a first hot water supply pipe 21 that branches from the outlet of the heat exchanger 9 and supplies hot water to the intake spray device 20, and an intake air that pressurizes the hot water. A spray water pump 13, an intake spray device 20 that sprays pressurized hot water on the intake side of the inlet of the compressor 3a, and an intake spray nozzle that is provided upstream of the intake spray device 20 and controls the flow rate of the sprayed warm water And an inlet valve 14. The high-pressure hot water sprayed by the intake spray device 20 is boiled under reduced pressure at the inlet of the compressor 3a and inside the compressor 3a to cool the intake air. Furthermore, moisture is added to the intake air to increase the mass flow rate of the intake air. Cooling of the intake air brings about a reduction in power of the compressor 3a. Further, the increase in the mass flow rate of the intake air causes an increase in combustion air, that is, an increase in the output of the turbine 3b, which contributes to an increase in the output of the gas turbine 3 as a whole.

  The solar heat utilization steam generation unit 32 is supplied with the second hot water supply pipe 22 that branches from the outlet of the heat exchanger 9 and supplies hot water to the second heat collector 2 and infrared B contained in sunlight as a heat source. The second heat collector 2 that generates superheated steam by evaporating the warm water, and the superheated steam generated by the second heat collector 2 is mixed with the generated steam of the exhaust heat recovery boiler 4 to obtain an intermediate pressure steam turbine. A steam supply pipe 23 that is supplied to the inlet of 5b, and a solar heat steam control valve 12 that is provided in the steam supply pipe 23 and controls the flow rate of the superheated steam that is generated by the second heat collector 2 that is supplied to the intermediate pressure steam turbine 5b. When the second heat collector 2 cannot sufficiently obtain solar heat such as at night, the steam return pipe 24 for returning the steam generated by the second heat collector 2 to the condenser 7 and the steam return pipe 24 Solar heat provided to control the flow rate of steam returned to the condenser 7 And a gas-bypass valve 16.

  The reason why the steam supply pipe 23 is connected to the inlet of the intermediate pressure steam turbine 5b is that the merit of increasing the output of the intermediate pressure steam turbine 5b can be obtained without requiring modification of the exhaust heat recovery boiler 4. For example, if the steam supply pipe 23 is connected to the inlet or outlet of the high-pressure steam turbine 5a, the advantage of increasing the output of the high-pressure steam turbine 5a can be obtained. The demerit of the occurrence of remodeling increases.

  Further, an embodiment of the solar combined power generation plant of the present invention includes a control system, which will be described in detail later, and includes the temperature of hot water, the pressure of the intake spray water, the steam temperature at the outlet of the second heat collector 2. The pressure, the temperature of the heat storage medium, and the like are detected and input to a control device described later. The temperature of the hot water is detected by a hot water temperature detector 17 a provided on the outlet side of the heat exchanger 9, and the pressure of the intake spray water is the intake air provided on the outlet side of the intake spray water pump 13 of the first hot water supply pipe 21. It is detected by the spray water pressure detector 17b. The steam temperature and pressure at the outlet of the second heat collector 2 are detected by a steam temperature detector 18 a and a steam pressure detector 18 b provided on the upstream side of the solar steam control valve 12 in the steam supply pipe 23. Further, the temperature of the heat storage medium is detected by an oil temperature detector 19 provided in the heat storage tank 10.

The following three points are mentioned as one feature of the embodiment of the solar combined cycle power plant 50 of the present invention.
(1) The heat storage medium is heated by the first heat collector 1 in the solar-heat-use hot water generation unit 30, and the heat storage medium and the water supply are heat-exchanged by the heat exchanger 9 to generate hot water. Based on the hot water, the hot water is evaporated by the second heat collector 2 in the solar heat utilizing steam generation unit 32 to generate superheated steam, and the superheated steam is supplied to the steam turbine 5.
(2) The hot water generated by the solar heat utilization hot water generation unit 30 is pressurized by the intake spray water pump 13 in the solar heat utilization intake spray unit 31, and the pressurized hot water is supplied to the compressor 3 a of the gas turbine 3 by the intake spray device 20. Spray on the intake side of the inlet.
(3) The solar heat utilization hot water generation unit 30 includes the first heat collector 1, the heat exchanger 9, the heat storage tank 10 that stores the heat storage medium, and the oil circulation pump that circulates the heat storage medium between the components. 11, and the heat medium heated by the first heat collector 1 can be stored in the heat storage tank 10.

  According to the present embodiment, by using the heat storage medium and the heat energy accumulated in the heat storage tank 10 to supply hot water with the heat exchanger 9, the turbine 3b can be used in the evening when the sufficient amount of solar radiation cannot be obtained or after sunset. Output increase and efficiency improvement. In addition, even when sunlight is temporarily shielded due to an increase in the amount of cloud, etc., the temperature of the hot water can be maintained within a certain range with the heat energy accumulated in the heat storage tank 10 and stable against weather fluctuations. Power generation output.

  Next, the operating characteristics of the solar combined cycle power plant 50 of the present invention will be described with reference to FIGS. FIG. 2 is a characteristic diagram showing an example of a load request command in one embodiment of the solar combined cycle power plant of the present invention, and FIG. 3 is a possession of a heat storage tank constituting the embodiment of the solar combined cycle power plant of the present invention. FIG. 4 is a characteristic diagram showing the time variation of the amount of heat, FIG. 4 is a characteristic diagram showing the time variation of the heat collection amount of the second heat collector constituting one embodiment of the solar combined cycle power plant of the present invention, and FIG. It is a characteristic view which shows the time change of the power generation output in one embodiment of the solar thermal combined cycle power plant.

  In FIG. 2, the vertical axis indicates the load request command MWD, and the horizontal axis indicates time T. For example, the power generation command (load request command MWD) sent to the solar thermal combined cycle power plant 50 from the central power supply command station An example of a change characteristic in 24 hours from midnight to midnight on the next day is shown. According to the characteristic line A in the figure, the load request command MWD starts increasing from 6 o'clock to 7 o'clock, reaches a peak around 14:00, and starts decreasing from around 18 o'clock. This reflects the characteristic that energy consumption due to social activities starts to increase from 6:00 to 7:00 and decreases around 18:00 when the factory stops operation.

Next, heat collection characteristics and the like of the solar thermal combined cycle power plant 50 in an area where such a load request command MWD is sent will be described with reference to FIGS. 3 and 4.
In FIG. 3, the vertical axis represents the amount of heat QM of the heat storage medium stored in the heat storage tank 10 according to the present embodiment, the horizontal axis represents time T, and the change characteristics in 24 hours from midnight to midnight the next day. An example is shown. Tw0 in the figure is the set temperature of hot water at the outlet of the heat exchanger 9 that enables the start of hot water spraying to the gas turbine 3, and the broken line in the figure indicates the amount of heat retained corresponding to this set temperature. Yes. As shown in FIG. 3, the amount of heat stored in the heat storage medium stored in the heat storage tank 10 starts to rise from about 6 o'clock when the sun rises due to the heat energy obtained by the first heat collector 1, and the sunset It becomes the characteristic which starts a fall from around 18:00. In addition, after sunset, the amount of heat retained gradually decreases due to heat dissipation.

  In FIG. 3, the time zone indicated by H1 from 9:00 to 23:00 is a time zone in which the temperature of the hot water can be heated to a temperature at which the hot water can be sprayed into the intake air of the gas turbine 3. In the present embodiment, warm water is sprayed on the intake air of the gas turbine 3 during this time period, and the output of the gas turbine 3 can be increased.

  In FIG. 4, the vertical axis indicates the amount of heat collected Q obtained by the second heat collector 2 in the present embodiment, and the horizontal axis indicates time T, and changes in 24 hours from midnight to midnight the next day. An example of a characteristic is shown. Ts0 in the figure is a set temperature of steam at the outlet of the second heat collector 2 that enables the start of steam supply to the steam turbine 5, and a broken line in the figure indicates the amount of heat collected corresponding to this set temperature. Is shown. As shown in FIG. 4, the amount of heat collected in the second heat collector increases rapidly with the solar altitude, and the time zone in which the elevation angle of the trough heat collector can follow the solar altitude (for example, time 9 indicated by H2). In the time zone of 15:00 from the hour), sufficient heat energy can be obtained to turn the hot water into steam. In this time zone, by supplying steam to the steam turbine 5, the output of the steam turbine 5 can be increased, and the output of the entire solar combined cycle power plant 50 can be increased. In addition, the amount of heat collected fluctuates greatly between the time from 8:00 to 9:00 and between the time from 15:00 to 16:00. This is because the elevation angle of the trough heat collector did not follow and the amount of heat collection was insufficient before time 8:00 when the solar altitude was low and after time 16:00.

  In addition, the heat collection area of the 1st heat collector 1 in FIG. 3 can be made small compared with the heat collection area of the 2nd heat collector 2 in FIG. This is because the amount of heat generated by the first heat collector 1 is the amount of heat necessary for heating water from room temperature to a temperature that allows the start of hot water spraying to the gas turbine 3, whereas The amount of heat by the second heat collector 2 is the amount of heat necessary to generate superheated steam that can be supplied to the steam turbine 5, and the amount of heat by the second heat collector 2 is greater than that of the first heat collector 1. It is because it is larger than the amount of heat. In FIG. 4, the amount of heat collection required for the generation of superheated steam changes greatly with time. This is because the heat collection area of the second heat collector 2 is large, and the change in the amount of heat collection from the sun is directly increased. By receiving.

Next, FIG. 5 shows the power generation output characteristics when a solar thermal combined cycle power plant is operated using hot water or steam obtained by the first heat collector 1 and the second heat collector 2 in the present embodiment. Will be described.
In FIG. 5, the vertical axis represents the power generation output P, and the horizontal axis represents time T. An example of the change characteristics of the power generation output of the solar combined cycle power plant in this embodiment over 24 hours from midnight to midnight the next day. Indicates. The characteristic line A in the figure shows the power generation output when the solar combined cycle power plant is controlled to coincide with the load request command MWD from the central power supply command station shown in FIG. In the characteristic line A, the portion indicated by A1 is an increase in output due to the intake spray to the gas turbine 3, and the portion indicated by A2 is an increase in output due to the supply of heating steam to the steam turbine 3. The characteristic line A0 in the figure indicates the power generation output by the gas turbine 3 and the steam turbine 5 excluding the output increase due to solar thermal energy.

According to the characteristic line A0, the power generation output of only the gas turbine 3 and the steam turbine 5 during the daytime is kept low. Therefore, according to this embodiment, as compared with conventional combined cycle power plant, it can be reduced fossil fuel consumption and CO ₂ emissions during the day. Moreover, unlike the conventional solar combined cycle power plant, the output can be increased from evening to night when sufficient heat energy from the sun cannot be obtained.

  In addition, since the heat collector has two stages, the first heat collector 1 preheats the feed water and warms the water, and the second heat collector 2 uses the heated water as superheated steam. Thus, the fluctuation range of the steam temperature when sunlight is temporarily shielded can be suppressed as compared with the configuration in which the heat collector is one stage.

  Next, a control system and a control method constituting one embodiment of the solar combined cycle power plant of the present invention will be described with reference to FIGS. 6 is a schematic configuration diagram showing a control system constituting one embodiment of a solar combined cycle power plant of the present invention, FIG. 7 is a control block diagram showing a solar power generation control system constituting the control system shown in FIG. FIG. 8 is a table showing an operation mode in one embodiment of the solar combined cycle power plant of the present invention, and FIG. 9 is a flowchart showing processing contents of operation mode switching in the embodiment of the solar combined cycle power plant of the present invention. It is. 6 to 9, the same reference numerals as those shown in FIGS. 1 to 5 are the same parts, and detailed description thereof is omitted.

  In FIG. 6, the control system includes a turbine control device 102, an exhaust heat recovery boiler control device 101, and a solar power generation control device 100, each of which measures the gas turbine 3, the exhaust heat recovery boiler 4, and the solar combined cycle power plant 50. The entire plant is controlled by exchanging values (temperature, pressure, etc.), operation amounts (valve opening, pump speed, collector elevation angle, etc.), and operation commands.

  Here, the turbine control device 102 controls the power generation output, the gas turbine rotation speed, the turbine exhaust temperature, the ratio of fuel to combustion air (fuel / air ratio), and the like. The exhaust heat recovery boiler control device 101 controls the rotation speed of the feed water pump 8, the drum water level of the exhaust heat recovery boiler 4, and the opening / closing operation of a turbine bypass valve (not shown) that bypasses the steam supplied to the steam turbine 5. Further, the solar thermal power generation control device 100 controls the heat collection amount in the first heat collector 1 and the second heat collector 2, the intake spray amount to the gas turbine 3, the steam supply amount to the steam turbine 5, and the like. These control devices may be mounted on the same control computer, or may be mounted on different control computers so that each computer controls the plant while synchronizing with each other.

  In the control system in the present embodiment, the turbine control device 102 receives the load request command MWD from the central power supply command station, and controls the output of the gas turbine 3 based on the load request command MWD. Further, in the solar thermal power generation control device 100, the load request command MWD, the weather information CC including, for example, the detection signal of the atmospheric temperature and the solar altitude, the water saving mode specified by the operator operating the water saving mode switch 25 The presence / absence selection signal SW and various measured values of the solar thermal combined cycle power plant 50 are input, and each component device of the solar thermal combined cycle power plant 50 is controlled. Further, the solar thermal power generation control device 100 sends a feed water flow rate command correction value GSAD to the exhaust heat recovery boiler control device 101. The exhaust heat recovery boiler control device 101 controls the exhaust heat recovery boiler 4 based on the feed water flow rate command correction value GSAD and various measured values of the exhaust heat recovery boiler 4.

Next, processing contents of the solar thermal power generation control device 100 and the exhaust heat recovery boiler control device 101 will be described with reference to FIG.
In FIG. 7, the solar thermal power generation control device 100 is calculated by an input unit to which each measurement value is input, a calculation unit that calculates a command value to each component device based on the input value from the input unit, and a calculation unit. Output unit for outputting the command value to each component device.

  The input unit includes a load request command MWD from the central power supply command station, a steam temperature TSA at the outlet of the second heat collector 2 from the steam temperature detector 18a, and a second heat collector from the steam pressure detector 18b. The steam pressure PSA at the outlet 2, the intake spray water temperature TWA from the hot water temperature detector 17 a, the intake spray water pressure PWA from the intake spray water pressure detector 17 b, and the temperature of oil as a heat storage medium from the oil temperature detector 19. The weather information CC including the measured values of the TOIL and the atmospheric temperature and the solar altitude is input.

  From the output section, the opening degree command CSAD to the solar steam control valve 12, the opening degree command CAB to the solar steam bypass valve 16, and the elevation angle command A2D to the second heat collector 2 are opened to the intake spray nozzle inlet valve 14. Degree command CWD, rotation speed command NWD to intake spray water pump 13, rotation speed command NOILD to oil circulation pump 11, elevation angle command A1 to first heat collector 1, and water supply to exhaust heat recovery boiler control device 101 A flow rate command GSAD is output.

  The calculation unit includes a steam pressure calculation unit 100a that calculates the opening commands CSAD, CAB, and CWD of the solar heat steam control valve 12, the solar heat steam bypass valve 16, and the intake spray nozzle inlet valve 14 based on the steam pressure PSA and the like, Steam temperature calculation unit 100b that calculates the elevation angle command A2D of the second heat collector 2 based on the temperature TSA and the like, and hot water that calculates the rotational speed command NWD of the intake spray water pump 13 based on the intake spray water pressure PWA and the like A pressure calculation unit 100c and a hot water temperature calculation unit 100d for calculating the rotation speed command NOILD of the oil circulation pump 11 and the elevation angle command A1 of the first heat collector 1 based on the intake spray water temperature TWA and the like are provided. .

  The steam pressure calculation unit 100a includes output control means 203, steam pressure control means 204, intake spray flow rate control means 205, intake spray nozzle inlet valve opening degree control means 206, and adder 214.

  The output control means 203 inputs the steam pressure PSA, and the opening degree command CSAD of the solar steam control valve 12 and the opening degree command CTAB of the solar steam bypass valve 16 so that the steam pressure PSA matches the preset target pressure. Is calculated. By controlling the steam pressure PSA so as to match the target pressure, the output fluctuation of the steam turbine 3 due to the change in solar thermal energy is suppressed.

  The steam pressure control means 204 receives the steam pressure PSA, and calculates a feed water flow rate command GSAD1 in the second heat collector 2 based on the steam pressure PSA. The calculated feed water flow rate command GSAD1 is output to the adder 214 and the steam temperature control means 207 of the steam pressure calculation unit 100b.

  The intake spray flow rate control means 205 inputs a load request command MWD, and calculates an intake spray flow rate command GWD based on the load request command MWD. In the present embodiment, the feed water at the outlet of the feed water pump 8 is branched and supplied to the second heat collector 2 and the intake spray device 20 via the exhaust heat recovery boiler 4, the heat exchanger 9. The intake spray flow rate control means 205 calculates the flow rate of water supplied to the intake spray device 20.

  The intake spray nozzle inlet valve opening degree control means 206 receives the intake spray flow rate command GWD, and calculates the opening degree command CWD of the intake spray nozzle inlet valve 14 based on the intake spray flow rate command GWD.

  The adder 214 inputs the feed water flow rate command GSAD1 in the second heat collector 2 from the steam pressure control means 204 and the intake spray flow rate command GWD from the intake spray flow rate control means 205, adds them, and calculates the feed water flow rate command. A correction value GSAD is calculated. The feed water flow command correction value GSAD is output to the exhaust heat recovery boiler control device 101. The calculation of the exhaust heat recovery boiler control apparatus 101 will be described later.

The steam temperature calculation unit 100b includes steam temperature control means 207 and second heat collector control means 208.
The steam temperature control means 207 inputs the steam temperature TSA, the weather information CC, and the feed water flow rate command GSAD1 in the second heat collector 2 from the steam pressure control means 204, and sets the steam temperature TSA to a preset target temperature. The heat collection amount command QSD of the second heat collector 2 is calculated so as to match.

  The second heat collector control means 208 inputs the heat collection amount command QSD of the second heat collector 2, and the elevation angle command A2D of the second heat collector 2 for the heat collection amount to follow the heat collection amount command QSD. Is calculated.

  The hot water pressure calculation unit 100 c includes an intake spray water pump control unit 209. In the present embodiment, high-temperature water supply that has been diverted at the outlet of the heat exchanger 9 is pressurized by the intake spray water pump 13 and then sprayed from the intake spray device 20 toward the inlet of the compressor 3a. In order to reliably boil the feed water at the inlet or inside of the compressor 3a, it is necessary to maintain the feed water temperature at a high temperature and a high pressure. The hot water pressure calculator 100c controls the intake spray water pressure PWA in the intake spray device 20, and the hot water temperature calculator 100d controls the intake spray water temperature TWA.

  The intake spray water pump control means 209 inputs the intake spray water pressure PWA and the intake spray flow rate command GWD from the intake spray flow rate control means 205 so that the intake spray water pressure PWA matches the preset target pressure. Then, the rotational speed command NWD of the intake spray water pump 13 is calculated.

  The hot water temperature calculation unit 100d includes an intake spray water temperature control means 210, an oil circulation pump control means 211, an oil temperature control means 212, and a first heat collector control means 213.

  The intake spray water temperature control means 210 receives the intake spray water temperature TWA and the intake spray flow rate command GWD from the intake spray flow rate control means 205, and is an oil for setting the intake spray water temperature TWA to a preset target temperature. A flow rate command GOILD is calculated.

  The oil circulation pump control means 211 inputs the oil flow rate command GOILD, and calculates the rotation speed command NOILD of the oil circulation pump 11 so that the flow rate of the heat storage medium matches the oil flow rate command GOILD.

  The oil temperature control means 212 inputs the oil temperature TOIL, the weather information CC, and the oil flow rate command GOILD from the intake spray water temperature control means 210, and sets the oil temperature TOIL so as to match the preset target temperature. A heat collection amount command QOILD of one heat collector 1 is calculated. It is desirable to maintain the temperature of the oil as the heat storage medium in the present embodiment at a temperature that does not reach the flash point for the purpose of accumulating heat energy. The target temperature is set from this viewpoint.

  The first heat collector control means 213 receives the heat collection amount command QOILD of the first heat collector 1, and the elevation angle command A1D of the first heat collector 1 for the heat collection amount to follow the heat collection amount command QOILD. Is calculated.

  Next, calculation of the exhaust heat recovery boiler control apparatus 101 will be described. The exhaust heat recovery boiler control apparatus 101 includes an adder 201 and a feed water pump control means 202.

  The adder 201 inputs, for example, the feed water flow rate command FWD to the feed water pump 8 calculated by another calculation unit and the feed water flow rate command correction value GSAD from the adder 214, and performs an addition operation to obtain the feed water flow rate correction command FWD1 calculate.

  The feed water pump control means 202 inputs the feed water flow rate correction command FWD1, and calculates the rotation speed command NFWP of the feed water pump 8 so that the feed water flow rate at the outlet of the feed water pump 8 matches the feed water flow rate correction command FWD1. Since the feed water flow rate of the feed water pump 8 is controlled by such feed water flow rate correction command FWD1, appropriate plant control is possible even when the feed water is branched and supplied to each component device as in the present embodiment. Become.

Next, the operation method of one embodiment of the solar combined cycle power plant of the present invention will be described.
As described above, in one embodiment of the solar combined cycle power plant of the present invention, the second collection in the solar heat utilization steam generation unit 32 is based on the hot water generated in the solar heat utilization hot water generation unit 30 shown in FIG. The operation of increasing the output of the steam turbine 5 by evaporating the hot water in the heater 2 to generate superheated steam and supplying the superheated steam to the steam turbine 5 by the solar steam control valve 12; The hot water generated at 30 is pressurized by the intake spray water pump 13 in the solar-heated intake spray unit 31, and the pressurized hot water is sprayed by the intake spray nozzle inlet valve 14 on the intake side of the inlet of the compressor 3 a of the gas turbine 3. By doing so, the operation of increasing the output of the gas turbine 3 is provided.

  Therefore, when one of these operations is used, when both are used, and when neither is used, the operation mode is determined, and these are the opening / closing of the solar steam control valve 12 and the intake spray nozzle inlet valve 14. It depends on the condition. Since the opening degree of the solar steam control valve 12 is controlled by the opening degree command CSAD of the solar thermal power generation control device 100 as shown in FIG. If it exceeds, it can be judged that it is in an open state. Similarly, since the opening degree of the intake spray nozzle inlet valve 14 is controlled by the opening degree command CWD of the solar thermal power generation control device 100, if the opening degree command CWD is 0% or less, the opening degree is closed and exceeds 0%. If it is, it can be judged that it is in an open state.

  FIG. 8 shows an operation mode in one embodiment of the solar combined cycle power plant of the present invention. In FIG. 8, mode 1 is a case where both the solar steam control valve 12 and the intake spray nozzle inlet valve 14 are opened, and the solar thermal combined cycle power plant 50 is configured to perform intake spray and steam on the gas turbine 3. Steam supply to the turbine 3 is performed. This maximizes the power output and plant efficiency of the solar combined cycle power plant 50.

  Mode 2 is a case where the intake spray nozzle inlet valve 14 is closed and the solar steam control valve 12 is opened, and the solar thermal combined cycle power plant 50 stops the intake spray to the gas turbine 3, Since steam is supplied to the turbine 3, moisture released from the gas turbine 3 to the atmosphere can be suppressed. As a result, the amount of plant water used can be reduced.

  Mode 3 is a case where the solar steam control valve 12 is closed and the intake spray nozzle inlet valve 14 is opened, and the solar combined cycle power plant 50 stops supplying steam to the steam turbine 3, Since the intake air spray to the turbine 5 is performed, it is possible to operate while increasing the plant output. Increased output operation is possible in cloudy weather or in the evening when sufficient heat energy from the sun cannot be obtained.

  Mode 4 is a case where both the solar steam control valve 12 and the intake spray nozzle inlet valve 14 are closed, and the solar thermal combined cycle power plant 50 supplies the intake spray to the gas turbine 3 and the steam supply to the steam turbine 3. It becomes the driving | operation which stopped both. Operation as a combined cycle power plant or night operation is possible.

Next, the processing content of the solar thermal power generation control device 100 that switches the above-described four types of operation modes will be described with reference to FIG.
First, in the solar thermal power generation control device 100, the steam temperature TSA at the outlet of the second heat collector 2 from the steam temperature detector 18a is equal to or higher than the steam set temperature Ts0 that enables the steam supply to the steam turbine 5 to start. Is determined (step S1). As shown in FIG. 4, when the steam temperature TSA is equal to or higher than a predetermined set temperature Ts0, steam can be supplied to the steam turbine 5, and the plant can be increased by the steam turbine 5. If the steam temperature TSA is equal to or higher than the set temperature Ts0, the process proceeds to (Step S2). Otherwise, the process proceeds to (Step S6).

  The solar thermal power generation control device 100 determines whether the water-saving mode presence / absence selection signal SW designated by the operator is 1 (valid) or 0 (invalid) (step S2). When the water saving mode is enabled, the spraying of hot water to the intake side of the inlet of the compressor 3a of the gas turbine 3 is limited for the purpose of saving the water supply of the plant, and when it is disabled, this limitation is excluded. . When the water saving mode presence / absence selection signal SW is 0 (invalid), the process proceeds to (step S3), and when it is 1 (valid), the process proceeds to (step S5).

  The solar thermal power generation control device 100 determines whether or not the intake water spray water temperature TWA from the hot water temperature detector 17a is equal to or higher than the set temperature of hot water that allows the hot water spray to be started on the gas turbine 3 (step S3). . As shown in FIG. 3, when the intake spray water temperature TWA is equal to or higher than a predetermined set temperature Tw0, it is possible to start the hot water spray to the gas turbine 3 and increase the output of the plant by the gas turbine 3. . If the intake spray water temperature TWA is equal to or higher than the set temperature Tw0, the process proceeds to (Step S4), and otherwise proceeds to (Step S5).

  The solar thermal power generation control device 100 operates the plant as mode 1 (step S4). Specifically, both the opening degree command CSAD of the solar steam control valve 12 and the opening degree instruction CWD of the intake spray nozzle inlet valve 14 are set to exceed 0%, each valve is opened, and the output of the plant by the gas turbine 3 is increased. And increase the output of the plant by the steam turbine 5.

  On the other hand, when the water-saving mode presence / absence selection signal SW is 1 (valid) in (Step S2) or when the intake spray water temperature TWA is lower than the set temperature Tw0 in (Step S3), the solar thermal power generation control device 100 The plant is operated as mode 2 (step S5). Specifically, the opening degree command CSAD of the solar steam control valve 12 is exceeded by 0% to open the solar steam control valve 12, and the opening degree command CWD of the intake spray nozzle inlet valve 14 is set to 0% or less to the intake spray nozzle inlet. The valve 14 is closed. Thereby, the increase in the output of the plant by the steam turbine 5 and the water saving of the plant are achieved.

  In (Step S1), when the steam temperature TSA is lower than the set temperature Ts0, the solar thermal power generation control device 100 determines that the intake spray water temperature TWA from the hot water temperature detector 17a is the value of hot water spray to the gas turbine 3. It is determined whether or not the temperature is equal to or higher than the set temperature of warm water that can be started (step S6). If the intake spray water temperature TWA is equal to or higher than the set temperature Tw0, the process proceeds to (Step S7), and otherwise proceeds to (Step S9).

  The solar thermal power generation control device 100 determines whether the water-saving mode presence / absence selection signal SW designated by the operator is 1 (valid) or 0 (invalid) (step S7). When the water saving mode is enabled, the spraying of hot water to the intake side of the inlet of the compressor 3a of the gas turbine 3 is limited for the purpose of saving the water supply of the plant, and when it is disabled, this limitation is excluded. . If the water-saving mode presence / absence selection signal SW is 0 (invalid), the process proceeds to (step S8), and if it is 1 (valid), the process proceeds to (step S9).

  The solar thermal power generation control device 100 operates the plant as mode 3 (step S8). Specifically, the opening degree command CSAD of the solar steam control valve 12 is set to 0% or less, the solar steam control valve 12 is closed, and the opening degree command CWD of the intake spray nozzle inlet valve 14 is set to exceed 0%, and the intake spray nozzle inlet valve is set. 14 is opened. As a result, the output of the plant by the gas turbine 3 is increased.

  On the other hand, if the water-saving mode presence / absence selection signal SW is 1 (valid) in (Step S7), or if the intake spray water temperature TWA is lower than the set temperature Tw0 in (Step S6), the solar thermal power generation control device 100 The plant is operated as mode 4 (step S9). Specifically, both the opening degree command CSAD of the solar steam control valve 12 and the opening degree command CWD of the intake spray nozzle inlet valve 14 are set to 0% or less, and each valve is closed to exclude the solar heat energy. Operate as a cycle power plant.

  According to the embodiment of the solar combined cycle power plant of the present invention described above, the intake spray device 20 and the heat storage tank 10 for storing the heat energy from the sun via the heat storage medium are provided, and obtained by this heat energy. The high-pressure hot water thus produced is sprayed at the inlet of the compressor 3a and boiled under reduced pressure in the air and inside the compressor 3a, so that the power generation efficiency and power generation output of the gas turbine 3 can be suppressed even under high atmospheric temperature conditions. . Further, the output of the gas turbine 3 can be increased and the efficiency can be improved even during a time period when sufficient solar radiation cannot be obtained (for example, in the evening) or after sunset. As a result, it is possible to provide the solar combined cycle power plant 50 that can further improve the efficiency and increase the output of the entire plant even if the sunshine condition varies.

  Moreover, according to one embodiment of the solar combined cycle power plant of the present invention described above, the temperature of hot water can be stably maintained even when sunlight is temporarily shielded by an increase in the amount of clouds, etc. As a whole, it is possible to provide a solar combined cycle power plant 50 capable of further improving efficiency and increasing output.

  Further, according to the embodiment of the solar combined cycle power plant of the present invention described above, the temperature fluctuation of the hot water can be minimized, so that the output fluctuation of the gas turbine 3 and the aggregation of the hot water in the intake portion of the gas turbine 3 (drain) ) Can be suppressed. This can prevent the generation of scale on the blade surface due to the adhesion of drain to the moving blade and stationary blade of the compressor 3a of the gas turbine 3. As a result, the safety of the compressor 3a of the gas turbine 3 is maintained. The solar combined cycle power plant 50 that enables high-efficiency operation can be provided.

Moreover, according to one embodiment of the solar combined cycle power plant of the present invention described above, the hot water obtained by the first heat collector 1 is obtained from the sun obtained by the second heat collector 2. Since this steam is supplied to the steam turbine 5 as the steam with the thermal energy of, the effect of increasing the output can be obtained in the steam turbine 5 in addition to the increase in the output of the gas turbine 3 in fine weather. As a result, it is possible to obtain the effect of improving the plant efficiency while suppressing the CO ₂ emission amount.

  Moreover, in one embodiment of the solar combined cycle power plant of the present invention, the existing combined cycle power plant equipment includes a first heat collector 1, a second heat collector 2, a heat exchanger 9, a heat storage tank 10, It can be realized by additionally installing equipment such as an oil circulation pump 11, a solar heat control valve 12, an intake spray water pump 13, an intake spray nozzle inlet valve 14, an intake spray device 20, and the like. Thus, it is possible to provide a solar thermal combined cycle power plant that enables high-efficiency operation.

DESCRIPTION OF SYMBOLS 1 1st heat collector 2 2nd heat collector 3 Gas turbine 4 Exhaust heat recovery boiler 5 Steam turbine 7 Condenser 8 Water supply pump 9 Heat exchanger 10 Heat storage tank 11 Oil circulation pump 12 Solar heat steam control valve 13 Intake Spray water pump 14 Intake spray nozzle inlet valve 16 Solar steam bypass valve 17a Hot water temperature detector 17b Intake spray water pressure detector 18a Steam temperature detector 18b Steam pressure detector 19 Oil temperature detector 20 Intake spray device 21 First warm water supply Pipe 22 Second hot water supply pipe 23 Steam supply pipe 24 Steam return pipe 25 Water-saving mode switch 30 Solar-powered hot water generation unit 31 Solar-powered intake spray unit 32 Solar-powered steam generation unit 50 Solar-heated combined cycle power plant 100 Solar-power generation control device

Claims (6)

Gas turbine (3) driven using combustion gas of gas turbine fuel, exhaust heat recovery boiler (4) generating steam by exhaust heat from the gas turbine (3), and exhaust heat recovery boiler (4) A steam turbine (5) driven by steam from the steam turbine, a condenser (7) for cooling the steam from the steam turbine (5) to generate feed water, and the water supply stored in the condenser (7) A solar heat combined cycle power plant comprising a feed water pump that pumps the waste heat to the exhaust heat recovery boiler (4),
The first heat collector (1) heats the heat storage medium, and the heat exchanger (9) exchanges heat between the heat storage medium and a part of the water supplied from the water supply pump (8) to generate hot water. A solar-heated hot water generating unit (30);
The hot water generated by the solar heat utilization hot water generating unit (30) is pressurized by an intake spray water pump (13), and the pressurized hot water is converted into intake air of the gas turbine (3) by an intake spray device (20). The hot water produced by the solar heat-use intake spray unit (31) to be sprayed and the solar heat-use hot water production unit (30) is evaporated by a second heat collector (2) to produce steam, A solar steam generation unit (32) for supplying to the steam turbine (5);
A solar combined cycle power plant characterized by comprising: Gas turbine (3) driven using combustion gas of gas turbine fuel, exhaust heat recovery boiler (4) generating steam by exhaust heat from the gas turbine (3), and exhaust heat recovery boiler (4) A steam turbine (5) driven by steam from the steam turbine, a condenser (7) for cooling the steam from the steam turbine (5) to generate feed water, and the water supply stored in the condenser (7) A solar heat combined cycle power plant comprising a feed water pump that pumps the waste heat to the exhaust heat recovery boiler (4),
The first heat collector (1) that heats the heat storage medium by solar thermal energy and heat exchange between the heated heat storage medium and a part of the water supplied from the water supply pump (8) generate hot water. A heat exchanger (9), a heat storage tank (10) for storing the heat storage medium after heat exchange with the heat exchanger (9), and the heat storage medium from the heat storage tank (10). A circulation pump (11) for pumping to the heater (1), a first hot water supply pipe (21) for branching from the outlet of the heat exchanger (9) and supplying the hot water to the intake spray device (20), An intake spray water pump (13) provided in the first hot water supply pipe (21) for pressurizing the hot water, and hot water pressurized by the intake spray water pump (13) is taken into the intake of the gas turbine (3). An intake spray device (20) for spraying air, and the first hot water supply pipe ( Upstream is provided on the side of solar thermal combined cycle power plant, characterized in that it comprises control valve which controls the hot water flow rate for spraying and (14) of the intake spray device 1) (20). In the solar combined cycle power plant according to claim 2,
A second hot water supply pipe (22) for branching from the outlet of the heat exchanger (9) to supply the hot water to the second heat collector (2); A second heat collector (2) for generating the steam, a steam supply pipe (23) for supplying the steam generated by the second heat collector (2) to the turbine (5), and the steam supply pipe ( 23), and the steam produced by the first regulating valve (12) for controlling the flow rate of the steam supplied to the turbine (5) and the second heat collector (2) is supplied to the condenser. A steam return pipe (24) supplied to (7), and a second regulating valve (16) provided in the steam return pipe (24) for controlling the flow rate of the steam to be returned to the condenser (7); A solar combined cycle power plant characterized by comprising: In the solar combined cycle power plant according to claim 3,
The turbine (5) includes a high-pressure steam turbine (5a) and an intermediate-pressure steam turbine (5b),
The steam supply pipe (23) mixes the steam generated by the second heat collector (2) with the steam generated by the exhaust heat recovery boiler (4), and enters the inlet of the intermediate pressure steam turbine (5b). A solar combined cycle power plant, characterized by In the solar combined cycle power plant according to claim 3 or 4,
Provided on the outlet side of the heat exchanger (9), a temperature detector (17a) for measuring the temperature of the hot water, and provided in the steam supply pipe (23), the second heat collector (2) A steam temperature detector (18a) for measuring the temperature of the steam generated in step (b), and the measured values of the temperature detector (17a) and the steam temperature detector (18a) are taken in, and the regulating valve (14) and the first And a control device (100) for controlling the opening of one regulating valve (12). In the solar combined cycle power plant according to claim 5,
A water-saving mode selection switch (25) for enabling the operator to specify whether the operation is valid or invalid;
The control device (100) takes a valid or invalid signal that is designated by the water-saving mode selection switch (25),
A procedure for comparing the measured value of the steam temperature detector (18a) with a predetermined temperature at which steam supply can be started;
A procedure for comparing the measured value of the temperature detector (17a) with a temperature at which a predetermined hot water spray can be started;
Depending on the truth of the results of the three procedures, both the increased output of the gas turbine (3) and the increased output of the steam turbine (5), the increased output of the gas turbine (3) and the increased power of the steam turbine (5) Either one of the increased outputs, the negation of the increased output of the gas turbine (3) and the denied of the increased output of the steam turbine (5) are determined, and the adjustment valve ( 14) and a procedure for controlling the opening degree of the first regulating valve (12). A solar thermal combined cycle power plant.

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