JP5384300B2 - Intake air cooling device for gas turbine, gas turbine plant, reconstruction method of existing gas turbine plant, and intake air cooling method of gas turbine - Google Patents

Description

  The present invention relates to an intake air cooling device for a gas turbine capable of performing intake air cooling of a gas turbine, a gas turbine plant, a reconstructing method of an existing gas turbine plant, and an intake air cooling method of a gas turbine.

  2. Description of the Related Art Conventionally, in a power generation gas turbine that basically includes a compressor, a combustor, and a turbine, the output of the turbine is affected by the temperature of intake air that is sucked into the compressor. That is, especially in the summer, the atmospheric temperature rises, so the density of the intake air decreases, the mass flow rate decreases, and the output decreases. In order to suppress such a decrease in output, some have an intake air cooling device that cools the intake air.

  In the intake air cooling device, there is a type that performs refrigeration cooling that cools the intake air by exchanging heat with the refrigerant cooled by the refrigerator, and by humidifying the intake air and evaporating the humidified water There are types that perform humidification cooling that cools the intake air, and there are types that include both refrigeration cooling and humidification cooling. In addition, in the type having refrigeration cooling and humidification cooling, there is a technology that uses refrigeration cooling and humidification cooling separately so that the intake air has a relative humidity of 100% and a temperature close to the maximum efficiency. It has been proposed (see, for example, Patent Document 1).

JP 2001-041049 A

However, in the intake air cooling device of the type by humidification cooling, since the cooling is performed by evaporating the moisture given to the intake air by humidification and taking away the latent heat, the cooling can be performed at a relatively low cost. If the relative humidity becomes 100%, that is, if the temperature falls to the wet bulb temperature, it will not be possible to cool any more. For this reason, there was a problem that the output could not be increased sufficiently, especially under weather conditions where the atmospheric humidity was high.
In addition, in a type of intake air cooling device using refrigeration cooling, cooling with a chiller can cool to a target temperature regardless of the state of the atmosphere, while power for driving the chiller is required. Even if a high output can be obtained by this, there is a problem that the loss of the refrigeration power occurs and the economic efficiency deteriorates.
Even in the intake air cooling apparatus such as Patent Document 1 having both, although it is possible to output with high efficiency by the gas turbine by properly using humidification cooling and refrigeration cooling, in the case of performing refrigeration cooling, it is not necessarily due to the loss of refrigeration power. They were not always driving economically.

  The present invention has been made in view of the above-described circumstances, and is an intake for a gas turbine that can achieve both high output power generation by a gas turbine for power generation and improved economic efficiency by performing intake air cooling. It is an object of the present invention to provide a cooling device, a gas turbine plant, a rebuilding method for an existing gas turbine plant, and a gas turbine intake air cooling method.

In order to solve the above problems, the present invention proposes the following means.
The present invention is a gas turbine intake air cooling device used for intake air cooling of a power generation gas turbine having a compressor, a combustor, and a turbine, and drives air to be drawn into the power generation gas turbine by driving a refrigerator. Each of the first cooling means for cooling, the second cooling means for cooling the air sucked into the power generation gas turbine by humidification, and the first cooling means and the second cooling means are operated. Or a cooling control unit that can be switched to non-operation, wherein the cooling control unit performs intake air cooling with the first cooling means and generates power by the power generation gas turbine with a required output acquired in advance. The difference between the first power generation balance, which is the difference in the balance, and the difference between the power generation balance, which is generated by the gas turbine for power generation at the maximum output possible by performing intake air cooling with the second cooling means. Based on the comparison between certain second power balance difference, it is characterized by determining the respective operating or non-operation of the first cooling means and the second cooling unit.

  Further, the present invention humidifies the intake air of a power generation gas turbine having a compressor, a combustor, and a turbine by driving a refrigerator to cool the air taken into the power generation gas turbine. A gas turbine intake air cooling method in which the air sucked into the power generation gas turbine is cooled by a second cooling means for cooling the intake air by the first cooling means. The first power generation balance difference, which is the difference in power generation balance due to power generation by the power generation gas turbine at the output, and the power generation gas turbine at the maximum output possible by performing intake air cooling with the second cooling means. Based on the magnitude comparison with the second power generation balance difference, which is the difference in power generation balance due to power generation, each of the first cooling means and the second cooling means is operated or not earned. It is characterized by determining the.

  According to this configuration and method, the first power balance difference obtained by performing the intake air cooling with the first cooling means and generating power with the required output, and the maximum output possible by performing the intake air cooling with the second cooling means. Based on the magnitude comparison with the second power generation balance difference generated by the power generation, the operation or non-operation of each of the first cooling means and the second cooling means is determined. For this reason, when the first power generation balance difference is larger than the second power generation balance difference, that is, when the balance is commensurate with the intake air cooling by driving the refrigerator with the first cooling means, the first By performing the intake air cooling by the cooling means, it is possible to output from the power generation turbine with the required output regardless of the atmospheric humidity state. On the other hand, when the first power generation balance difference is smaller than the second power generation balance difference, that is, when the intake and output cooling is not performed when the refrigerator is driven by the first cooling means, the second By performing the intake air cooling by the cooling means, it is possible to make the maximum output from the power generation gas turbine while ensuring the economy.

  In the above-described gas turbine intake air cooling device, the cooling control unit supplies the intake air to the required inlet temperature that is the intake air temperature at which the power generation gas turbine can output with the required output. Necessary refrigeration power calculating means for calculating required refrigeration power that is required for the refrigerator to cool by the cooling means, and the power generation by performing intake air cooling with the required output and the second cooling means. Difference output calculation means for calculating a difference output from the maximum output that can be output by the gas turbine, the required refrigeration power obtained by the required refrigeration power calculation means, and the difference output obtained by the difference output calculation means On the basis of the intake air cooling by the first cooling means and output from the gas turbine for power generation at the required output, and the maximum output by cooling the intake air by the second cooling means Based on the difference output calculated by the difference output calculation means, the difference income calculation means for calculating the difference income that is the difference of the income from the power generation when output from the gas turbine for power generation, the first output When the intake air is cooled by the cooling means and output from the power generation gas turbine at the required output, and when the intake air is cooled by the second cooling means and output from the power generation gas turbine at the maximum output Difference cost calculation means for calculating a difference cost that is a difference in expenditure accompanying power generation, and the difference income and the difference cost are compared, and when the difference income is equal to or less than the difference cost, the first And an operation determining means for operating at least the first cooling means when the cooling means is inactive, the second cooling means is in operation, and the differential income is greater than the differential cost. Rukoto is more preferable.

  In the above-described gas turbine intake air cooling method, the intake air is cooled by the first cooling means to a required inlet temperature that is an intake air temperature at which the power generation gas turbine can output with the required output. The required refrigeration power calculation step for calculating the required refrigeration power, which is the power required by the refrigerator, and the required output and the second cooling means perform intake air cooling, and can be output by the power generation gas turbine A difference output calculation step for calculating a difference output from the maximum output, the required refrigeration power obtained in the required refrigeration power calculation step, and the difference output obtained in the difference output calculation step. Intake air cooling by one cooling means and output from the power generation gas turbine at the required output, and intake power cooling by the second cooling means and the power generation gas turbine at the maximum output Based on the differential income calculation step for calculating the differential income, which is the difference in income from power generation with the output from the bin, and the differential output obtained in the differential output calculation step, the first cooling means takes in the air Expenditure associated with power generation when cooled and output from the power generation gas turbine at the required output, and when cooled by intake air by the second cooling means and output from the power generation gas turbine at the maximum output A difference cost calculation step of calculating a difference cost that is a difference between the difference income and the difference cost, and if the difference income is equal to or less than the difference cost, the first cooling means is not used. It is more preferable to include an operation determining step of operating, when the second cooling means is operating, and when the difference revenue is larger than the difference cost, at least the first cooling means is operating. There.

  According to this configuration and method, the required refrigeration power required for the refrigerator to cool the intake air by the first cooling means can be obtained at the required inlet temperature corresponding to the required output. Further, a differential output between the required output and the maximum output possible by performing the intake air cooling with the second cooling means can be obtained. Based on the required refrigeration power and the differential output, the intake air is cooled by the first cooling means and output from the power generation gas turbine at the required output, and the intake air is cooled by the second cooling means and the maximum The differential income, which is the difference in income from power generation with the output from the gas turbine for power generation, is obtained. Furthermore, based on the obtained differential output, the first cooling means cools the intake air and outputs the required output from the power generation gas turbine, and the second cooling means cools the intake air and generates the maximum power output gas. It is possible to obtain a differential cost that is a difference in expenditure associated with power generation from the case of output from the turbine. And the magnitude comparison of the 1st power generation balance difference and the 2nd power generation balance difference can be performed by performing the size comparison with these calculated | required difference income and difference costs. When the difference revenue is equal to or less than the difference cost, that is, when the first power generation balance difference is smaller than the second power generation balance difference, the first cooling means is not operated, and the second By operating the cooling means, it is possible to make the maximum output from the gas turbine for power generation while ensuring the economy. Further, when the differential revenue is larger than the differential cost, that is, when the first power generation balance difference is larger than the second power generation balance difference, the humidity of the atmosphere is increased by operating at least the first cooling means. Regardless of the state, it can be output from the power generation turbine with the required output.

  Further, in the above-described gas turbine intake air cooling device, the required inlet temperature calculating means for calculating the required inlet temperature based on the required output acquired in advance, and the atmospheric air based on the acquired dry bulb temperature and humidity Temperature calculating means for calculating the dew point temperature and wet bulb temperature of the required refrigeration power, the required refrigeration power calculating means is the required inlet temperature calculated by the required inlet temperature calculating means and the dew point calculated by the temperature calculating means More preferably, the required refrigeration power is calculated based on temperature, and the difference output calculation means calculates the difference output based on the required output and the wet bulb temperature calculated by the temperature calculation means.

  Further, in the above-described gas turbine intake air cooling method, based on the required inlet temperature calculation step of calculating the required inlet temperature based on the required output acquired in advance, and the acquired air dry bulb temperature and atmospheric humidity, A temperature calculation step of calculating the dew point temperature and wet bulb temperature of the atmosphere, and in the required refrigeration power calculation step, the required inlet temperature calculated in the required inlet temperature calculation step and the temperature calculated in the temperature calculation step More preferably, the required refrigeration power is calculated based on a dew point temperature, and in the differential output calculation step, the differential output is calculated based on the required output and the wet bulb temperature calculated in the temperature calculation step.

  According to this configuration and method, the required inlet temperature can be obtained based on the required output. Further, based on the acquired atmospheric temperature and atmospheric humidity, the atmospheric dew point temperature and wet bulb temperature can be obtained. For this reason, required refrigeration power can be calculated | required based on the calculated | required said required inlet_port | entrance temperature and dew point temperature, and also a difference output can be calculated based on a required output and the calculated | required said wet bulb temperature.

  Further, in the above-described gas turbine intake air cooling device, the operation determining means obtains the atmospheric dry bulb temperature and the required inlet temperature and compares them, and the required inlet temperature is equal to or higher than the dry bulb temperature. In this case, it is more preferable that the first cooling unit and the second cooling unit are inoperative regardless of the size of the first power generation balance difference and the second power generation balance difference.

  In the above-described gas turbine intake air cooling method, in the operation determination step, the dry-bulb temperature of the atmosphere and the required inlet temperature are acquired and compared, and the required inlet temperature is equal to or higher than the dry-bulb temperature. In this case, it is more preferable that the first cooling unit and the second cooling unit are inoperative regardless of the size of the first power generation balance difference and the second power generation balance difference.

  According to this configuration and method, by obtaining the dry bulb temperature of the atmosphere and the required inlet temperature corresponding to the required output and comparing the magnitude, the current atmosphere is sucked into the power generation gas turbine for the required output. It can be determined whether cooling is required for output. That is, when the required inlet temperature is equal to or higher than the dry bulb temperature, it can be determined that sufficiently low-temperature air can be sucked without cooling the intake air, and the first cooling means and the second cooling means are As a non-operation, an output corresponding to at least the required output can be obtained from the power generation gas turbine.

  Further, in the above-described gas turbine intake air cooling apparatus, the operation determining means obtains the atmospheric dry bulb temperature and wet bulb temperature, and the required inlet temperature, compares the required magnitude, and the required inlet temperature is the dry bulb temperature. If the temperature is lower than the temperature and not less than the minimum humidification cooling temperature obtained from the wet bulb temperature, the first cooling means is not used regardless of the magnitude of the first power generation balance difference and the second power generation balance difference. More preferably, the second cooling means is in operation.

  Further, in the above-described gas turbine intake air cooling method, in the operation determining step, the dry-bulb temperature and wet-bulb temperature of the atmosphere and the required inlet temperature are acquired and compared in magnitude, and the required inlet temperature is the dry bulb temperature. If the temperature is lower than the temperature and not less than the minimum humidification cooling temperature obtained from the wet bulb temperature, the first cooling means is not used regardless of the magnitude of the first power generation balance difference and the second power generation balance difference. More preferably, the second cooling means is in operation.

  According to this configuration and method, the required dry inlet temperature and the dew point temperature, and the required inlet temperature corresponding to the required output are obtained and compared, so that the required inlet can be obtained only by humidification cooling by the second cooling means. It can be determined whether or not it can be cooled to below the temperature. That is, when the required inlet temperature is less than the dry bulb temperature and is equal to or higher than the minimum humidification cooling temperature obtained from the wet bulb temperature, the humidification cooling only by the second cooling means is used until the required inlet temperature reaches the wet bulb temperature. The first cooling means can be deactivated and the second cooling means can be activated to obtain an output corresponding to the required output from the power generation gas turbine.

  Further, in the above-described gas turbine intake air cooling device, the operation determining means acquires the atmospheric dew point temperature and the required inlet temperature, compares the required magnitude, the required inlet temperature is equal to or lower than the dew point temperature, and When the differential revenue is greater than the differential cost, the second cooling means is deactivated, and when the required inlet temperature is higher than the dew point temperature and the differential revenue is greater than the differential cost, the first More preferably, the second cooling means is also operated together with the cooling means.

  Further, in the above-described gas turbine intake air cooling method, in the operation determining step, the atmospheric dew point temperature and the required inlet temperature are acquired and compared in magnitude, and the required inlet temperature is equal to or lower than the dew point temperature, and When the differential revenue is greater than the differential cost, the second cooling means is deactivated, and when the required inlet temperature is higher than the dew point temperature and the differential revenue is greater than the differential cost, the first More preferably, the second cooling means is also operated together with the cooling means.

  According to this configuration and method, when the atmosphere is cooled to the dew point by the first cooling means by obtaining the dew point temperature of the atmosphere and the required inlet temperature corresponding to the required output and comparing the magnitude, the required inlet port is obtained. It can be determined whether or not the temperature is higher. Here, if the temperature is lower than the required inlet temperature when the first cooling means cools to the dew point, the temperature can be lowered to the required inlet temperature even if part of the cooling is performed by the second cooling means. Means. In such a case, the loss of the refrigeration power caused by operating the first cooling means can be minimized by performing a part of the cooling by the second cooling means, thereby reducing the cost. Further improvement can be achieved.

  A gas turbine plant according to the present invention includes the above-described gas turbine intake air cooling device and the power generation gas turbine.

  According to this configuration, by providing the above-described gas turbine intake air cooling device, the power generation gas turbine can generate power economically and with high output.

  Further, the reconstructing method of an existing gas turbine plant of the present invention is characterized in that the gas turbine plant is constructed by adding the gas turbine intake air cooling device to the existing gas turbine for power generation. It is said.

  According to this method, the power generation by the existing gas turbine for power generation can be made economical and high output only by additionally installing the above-described gas turbine intake air cooling device. Here, the additional installation of the gas turbine intake air cooling device refers to the first cooling means, the second cooling means, and the cooling control unit, which are the configuration of the gas turbine intake air cooling device, in addition to the existing power generation gas turbine. It is not limited to establishing a new. That is, while the power generation gas turbine and one of the first cooling means or the second cooling means are configured as existing equipment, the other of the first cooling means or the second cooling means and the cooling This is a concept that includes a new control unit, and a configuration in which a first cooling unit and a second cooling unit are configured as existing facilities, whereas a new cooling control unit is included.

According to the gas turbine intake air cooling apparatus of the present invention, under the control of the cooling control unit, the intake air cooling is performed by the refrigeration cooling by the first cooling means and the humidification cooling by the second cooling means. It is possible to achieve both high power generation by the gas turbine and improved economic efficiency.
According to the gas turbine intake air cooling method of the present invention, the power generation by the power generation gas turbine is performed by performing the intake air cooling by the refrigeration cooling by the first cooling means and the humidification cooling by the second cooling means in accordance with the above steps. It is possible to achieve both higher output and improved economic efficiency.
In addition, according to the gas turbine plant of the present invention, it is possible to achieve both higher power generation and improved economic efficiency by the gas turbine intake cooling device.
In addition, according to the rebuilding method of the existing gas turbine plant, it is possible to achieve both higher power generation and improved economic efficiency of the existing power gas turbine by additionally installing the gas turbine intake air cooling device. it can.

1 is an overall view of a gas turbine plant according to an embodiment of the present invention. It is a block diagram which shows the detail of a cooling control part in the intake-air-cooling apparatus for gas turbines of embodiment of this invention. In the intake-air-cooling apparatus for gas turbines of embodiment of this invention, it is NC diagram memorize | stored in the memory | storage part. It is a flowchart which shows the judgment flow performed by the operation determination means in the intake-air-cooling apparatus for gas turbines of embodiment of this invention. It is a general view of the gas turbine plant of the 1st modification of embodiment of this invention. It is a general view of the gas turbine plant of the 2nd modification of embodiment of this invention.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings. FIG. 1 is a block diagram illustrating an embodiment of the present invention.
FIG. 1 is a schematic configuration diagram of a gas turbine plant according to an embodiment of the present invention. As shown in FIG. 1, a gas turbine plant 1 includes a power generation gas turbine 2, a generator 3 connected to the power generation gas turbine 2, and a gas turbine intake air cooling device that performs intake air cooling of the power generation gas turbine 2. 10.

The power generation gas turbine 2 generates a combustion gas G by mixing the fuel F with the compressor 2a that generates compressed air A2 by sucking and compressing the air A1 from the atmosphere, and the compressed air A2 generated by the compressor 2a. A combustor 2b, a turbine 2c that is rotationally driven by the combustion gas G generated in the combustor 2b, a rotor 2d that penetrates the compressor 2a and the turbine 2c, and a gas turbine control unit 2e that controls each component are provided. The generator 3 is connected to the rotor 2d. The rotor 2d is provided with blade structures of the compressor 2a and the turbine 2c. Then, under the control of the gas turbine control unit 2e, the compressor 2a compresses the air A1 by the blade structure to generate the compressed air A2, and the combustor 2b generates the combustion gas G and supplies it to the turbine 2c. Thus, in the turbine 2c, it is possible to generate power with the generator 3 by rotating the rotor 2d by the blade structure. The gas turbine control unit 2e, the required output W _PR is input in response to the power demand during operation, as the gas turbine control unit 2e outputs the required output W _PR, compressors 2a, a combustor 2b and the turbine 2c are controlled. Here, the electric power demand includes electric power that can be sold. For example, when electric power can be sold by private power generation, the electric power that can be sold or the rest of the electric power sold to the customer by the electric power company In the case where power can be sold to other electric power companies, the electric power that can be sold to other electric power companies is included.

  The gas turbine intake air cooling device 10 drives the refrigerator 11 to cool the air A1 taken into the power generation gas turbine 2 and the humidification, so that the gas turbine intake air is sucked into the power generation gas turbine 2. A second cooling means 13 for cooling the air A1 and a cooling control unit 20 capable of switching each of the first cooling means 12 and the second cooling means 13 between operation and non-operation. In the present embodiment, the first cooling means 12 and the second cooling means 13 are arranged in this order from the upstream side in the intake passage of the compressor 2a.

  The first cooling means 12 includes a first heat exchanger 12a that exchanges heat with the air A1 that is sucked and cools it, a second heat exchanger 12b that exchanges heat with the outside air and dissipates heat, and It has the refrigerator 11 provided between the 1st heat exchanger 12a and the 2nd heat exchanger 12b, and drives with electric power, and the refrigerator control part 12c which controls the drive of the refrigerator 11. FIG. Between the 1st heat exchanger 12a and the refrigerator 11, the 1st piping 12d which makes | forms a circulation path is distribute | arranged, and cold water circulates inside. Similarly, a second pipe 12e forming a circulation path is also arranged between the second heat exchanger 12b and the refrigerator 11, and cooling water circulates inside. The refrigerator 11 radiates heat from the internal refrigerant to the cooling water circulating through the second pipe 12e under the control of the refrigerator control unit 12c, and absorbs heat between the cooling water circulating through the first pipe 12d. Then, the cold water circulating through the first pipe 12d is cooled. And in the 1st heat exchanger 12a, air A1 is cooled by performing heat exchange between the cold water which circulates through the 1st piping 12d cooled with the refrigerator 11, and the air A1 inhaled. Here, the refrigerator control unit 12c is connected to the cooling control unit 20, and based on the control signal input from the cooling control unit 20, the refrigerator 11 is driven and air A1 is generated by the first heat exchanger 12a. Can be cooled to a desired temperature.

  The second cooling means 13 includes an evaporative cooler 13a through which the inhaled air A1 flows, a storage portion 13b in which humidifying water L is stored, and an evaporative cooler 13a that removes the water L from the storage portion 13b. A humidifying pump 13c to be supplied to the vehicle, and a humidifying control unit 13d for controlling the humidifying pump 13c. The evaporative cooler 13a includes a cooling chamber 13e into which air A1 flows in and out, a porous member 13f provided so as to block the flow path of the air A1 inside the cooling chamber 13e, and water supplied by a humidifying pump 13c. A water spray nozzle 13g for spraying L into the porous member 13f. Further, the humidification control unit 13d is connected to the cooling control unit 20, and on the basis of a control signal input from the cooling control unit 20, the humidification pump 13c is driven to spray water on the porous member 13f and evaporate. By doing so, heat can be taken from the air A1 passing through the porous member 13f by latent heat and cooled to a desired temperature.

As shown in FIG. 2, the gas turbine intake air cooling device 10 includes an atmospheric temperature measurement unit 15 that measures the dry-bulb temperature T _amb of the atmosphere, and an atmospheric humidity measurement unit 16 that measures the absolute humidity φ _amb of the atmosphere. Is provided. The dry bulb temperature T _amb and the absolute humidity φ _amb acquired by the atmospheric temperature measurement unit 15 and the atmospheric humidity measurement unit 16 are output to the cooling control unit 20. The cooling control unit 20 is connected to the gas turbine control unit 2e. The cooling control unit 20 is input from the required output W _PR input from the gas turbine control unit 2e, the atmospheric dry bulb temperature T _amb input from the atmospheric temperature measurement unit 15, and the atmospheric humidity measurement unit 16. Based on the absolute humidity φ _amb , the first cooling means 12 and the second cooling means 13 are operated. Details of the cooling control unit 20 will be described below.

  As shown in FIG. 2, the cooling control unit 20 includes a temperature calculation unit 21, a required inlet temperature calculation unit 22, a necessary refrigeration power calculation unit 23, a difference output calculation unit 24, a difference income calculation unit 25, and a difference. Cost calculating means 26, operation determining means 27, and a storage unit 28 storing various data are provided. And the cooling control part 20 is a temperature calculation process, a required inlet temperature calculation process, a required refrigeration power calculation process, a difference output calculation process, a difference income calculation process, a difference cost calculation process, and an operation | movement by these structures. The determination process is performed, and the first cooling means 12 and the second cooling means 13 are caused to perform intake air cooling.

Temperature calculating means 21, the temperature calculating step calculates the dew point temperature _{T d} and a wet-bulb temperature _{T Wb} of the atmosphere. The temperature calculation means 21 calculates the atmospheric dew point temperature calculation unit 21a for calculating the atmospheric dew point temperature _Td , calculates the atmospheric wet bulb temperature T _Wb , and uses the lowest temperature that can be cooled by humidification cooling from the wet bulb temperature T _Wb. A humidifying and cooling minimum temperature calculating unit 21b for calculating a certain humidifying and cooling minimum temperature _Thmin . The atmospheric dew point temperature calculation unit 21a calculates the atmospheric dew point temperature T _d based on the dry bulb temperature T _amb and the absolute humidity φ _amb input from the atmospheric temperature measurement unit 15 and the atmospheric humidity measurement unit 16, respectively. Specifically, in the present embodiment, the storage unit 28 has an NC diagram (for example, “How to read and use the thorough master air diagram”, edited by the Society for Air Conditioning and Sanitation Engineering, 1998, pp16, etc.). The atmospheric dew point temperature calculation unit 21a refers to the NC diagram ((1) in FIG. 2) stored in the storage unit 28, and determines the dry bulb temperature T _amb and the absolute humidity φ _amb . The dew point temperature _Td is obtained by fitting. Then, the atmospheric dew point temperature calculation unit 21 a outputs the calculated dew point temperature T _d to the necessary refrigeration power calculation means 23. Similarly, the humidification / cooling minimum temperature calculation unit 21b refers to the NC diagram ((1) in FIG. 2) stored in the storage unit 28, and applies the dry bulb temperature T _amb and the absolute humidity φ _amb by fitting. The wet bulb temperature T _Wb is obtained. Further fogging lowest temperature calculating unit 21b obtains the fogging lowest temperature T _hmin is the minimum value of the inlet temperature of the compressor 2c for performing fogging from wet bulb temperature T _Wb. The humidification cooling minimum temperature T _hmin can be calculated by the following < _Equation 1>, for example, by giving the humidification cooling efficiency η _hc obtained from a trial operation or design calculation.

Then, the humidification cooling minimum temperature calculation unit 21 b outputs the calculated humidification cooling minimum temperature _Thmin to the differential output calculation means 24. Although the dew point temperature T _d and the wet bulb temperature T _Wb are obtained from the dry bulb temperature T _amb and the absolute humidity φ _amb in the atmosphere, the dew point thermometer and the wet bulb thermometer are provided, and the dew point temperature T _{d is} directly provided. Alternatively, the wet bulb temperature T _Wb may be measured.

Request inlet temperature calculation means 22, as the required inlet temperature calculating step, based on the required output W _PR inputted from the gas turbine control unit 2e, an inlet air temperature of the power generation gas turbine 2 can be outputted by the required output W _PR A certain required inlet temperature _TPR is calculated. Specifically, in the present embodiment, the storage unit 28 stores in advance the relationship between the intake air temperature T at the inlet of the compressor 2a and the turbine output of the power generation gas turbine of this configuration ((2) in FIG. 2). It is remembered. The request inlet temperature calculation unit 22 refers to the relationship stored intake air temperature T and the turbine output to the storage unit 28, by fitting the required output W _PR as turbine output, the corresponding intake air temperature T The required inlet temperature _TPR can be obtained. Then, the required inlet temperature calculating means 22 outputs the calculated required inlet temperature _TPR to the necessary refrigeration power calculating means 23 described later. The relationship between the intake air temperature T and the turbine output is described in, for example, “Gas Turbine Theory 5th Edition”, Sarabanamuttoo, HIH, et al. , 2001 "etc. can be used.

The necessary refrigeration power calculation means 23 needs to be the power required in the refrigerator 11 to cool the intake air to the required inlet temperature _TPR by the first cooling means 12 as the required refrigeration power calculation process. The refrigeration power _WIN is calculated. More specifically, the necessary refrigeration power calculation means 23 is calculated with a specific enthalpy difference calculation unit 23a that calculates a specific enthalpy difference Δh that needs to be taken to cool to the target temperature by the first cooling means 12. A required refrigeration capacity calculation unit 23b that calculates the required refrigeration capacity ΔH required by the refrigerator 11 of the first cooling means 12 based on the specific enthalpy difference Δh, and the refrigerator 11 based on the calculated required refrigeration capacity ΔH. and a required refrigerating power calculation unit 23c for calculating the necessary refrigeration power W _iN is a power required in.

In the following, for the sake of simplicity, the description will be made _assuming that the humidification cooling efficiency η _hc in < _Equation 1> is 100%, that is, “T _hmin = T _Wb ”.
Specific enthalpy difference calculation unit 23a, a request inlet temperature T _PR inputted from the required inlet temperature calculation means 22, and the dew point temperature Td inputted from the atmospheric dew point temperature calculating section 21a, dry inputted from ambient temperature measuring unit 15 Based on the sphere temperature T _amb ((5) in FIG. 2) and the absolute humidity φ _amb ((4) in FIG. 2) input from the atmospheric humidity measuring unit 16, the current cooling means 12 in to cool to the required inlet temperature T _PR calculates a need certain specific enthalpy difference Δh depriving present air. Specifically, the specific enthalpy difference calculation unit 23a refers to the NC diagram ((1) in FIG. 2) stored in the storage unit 28 shown in FIG. 3, and inputs the dry bulb temperature T _amb and absolute humidity. Input φ _amb and obtain a point B representing the current atmospheric condition. Moreover, the specific enthalpy difference calculation section 23a is required inlet temperature _{T PR} type a, with the inlet air temperature T is required inlet temperature _{T PR} Request A point is a relative humidity of 100%. Next, it is determined whether or not the point B representing the current atmospheric state is on the lower temperature side than the wet bulb temperature constant line La passing through the point A. When it is determined that the point B representing the current atmospheric state is on the lower temperature side than the wet bulb temperature constant line La, the specific enthalpy difference Δh is output as “0”. This is because when the dry bulb temperature T _amb is equal to or lower than the required inlet temperature T _PR , it is not necessary to cool, and even if the dry bulb temperature T _amb is higher than the required inlet temperature T _PR , the wet bulb temperature constant line La This is because when the temperature is lower than that, only humidification cooling is required. Details will be described later. Note that the point B representing the current atmospheric state is at a lower temperature side than the wet bulb temperature constant line La in FIG. 3, the point B representing the atmospheric state in FIG. 3 is that the intake air temperature T is higher than the line where T = _TPR constant. located in a small area X (for example, the point B1) or, or, T _{= T PR} position sandwiched by region Y1 in the wet-bulb temperature constant line La through certain lines and points a (e.g., point B2) to Means that.

Also, the specific enthalpy difference calculation unit 23a, when the B point representing the current state of the atmosphere in the high temperature side than the wet-bulb temperature constant line La is then the dew point temperature T _d and the required inlet temperature T _PR A size comparison is performed, and different calculations are performed when the dew point temperature T _d is lower than the required inlet temperature T _PR and when the dew point temperature T _d is equal to or higher than the required inlet temperature T _PR . Here, the dew point temperature _Td is lower than the required inlet temperature _TPR in FIG. 3 when the point B representing the current atmospheric state is on the higher temperature side than the wet bulb temperature constant line La and The absolute humidity φ _amb is located in a region Y2 where the absolute humidity φ _{A is} less than the absolute humidity φ _{A at the} point A (for example, the point B3). Further, when the dew point temperature _Td becomes _{equal to} or higher than the required inlet temperature TPR, the dew point temperature _Td is positioned in a region Z where the absolute humidity φ _amb of the atmosphere is _equal to or higher than the absolute humidity φ _{A at the} point A in FIG. It is.

First, in case dew point temperature _{T d} is less than required inlet temperature _{T PR} (region Y2), cooled from B3 that it is the current state of the atmosphere, to B3' that points A and wet bulb temperature _{T Wb} are the same The specific enthalpy difference Δh that needs to be taken away is obtained. This is due to, as described later, from the state of point B3' to the required inlet temperature T _PR is possible cooling by the second cooling means 13. Further, in case dew point temperature T _d is higher than the required inlet temperature T _PR (area Z), the B4 that it is the current state of the atmosphere, and cooled to a dew point temperature T _d4, a further request inlet temperature T _PR The specific enthalpy difference Δh that needs to be taken to cool to the point A is obtained. A specific specific enthalpy difference Δh is calculated by the following <Equation 2>. Here, in <Expression 2>, the function f is obtained from the NC diagram. Then, the specific enthalpy difference calculation unit 23a outputs the obtained specific enthalpy difference Δh to the necessary refrigeration capacity calculation unit 23b.

Required cooling capacity calculating unit 23b, based on the specific enthalpy difference calculation section 23a in the calculated specific enthalpy difference Delta] h, required refrigeration required to cool until the required inlet temperature T _PR by the first cooling means 12 The ability ΔH is calculated. Specifically, the required cooling capacity calculation unit 23b, together with the intake air flow rate G _IN is inputted in the compressor 2a of the gas turbine 2c from the gas turbine control section 2e, specific enthalpy difference from the specific enthalpy difference calculation section 23a Delta] h Is entered. The necessary cooling capacity calculating unit 23b, based on the input intake air flow rate G _IN and specific enthalpy difference Delta] h, obtaining the required refrigeration capacity ΔH in the following <Equation 3>. Then, the necessary refrigeration capacity calculation unit 23b inputs the obtained necessary refrigeration capacity ΔH to the necessary refrigeration power calculation unit 23c.

Necessary refrigeration power calculation unit 23c calculates the necessary refrigeration power W _IN needed to output the required refrigeration capacity [Delta] H. Specifically, the necessary refrigeration power calculation unit 23c is input with the necessary refrigeration capacity ΔH from the necessary refrigeration capacity calculation unit 23b, and from the refrigerator control unit 12c, the refrigeration unit 11 specific to the first cooling means 12 The coefficient of performance COP is input. The necessary cooling capacity calculating unit 23b, based on the required refrigeration capacity ΔH and the COP inputted, obtains the necessary refrigeration power W _IN by the following <Equation 4>. Then, the necessary refrigeration power calculation unit 23 c outputs the obtained necessary refrigeration power _WIN to the differential income calculation means 25.

In addition, the differential output calculation means 24, as a differential output calculation step, performs humidification cooling maximum output that is the maximum output that can be output by the power generation gas turbine 2 by performing intake air cooling with the required output _WPR and the second cooling means 13. The difference output ΔW with _respect to W _hmax is calculated. Specifically, the differential output calculation unit 24 includes a humidification cooling maximum output calculation unit 24a that calculates a humidification cooling maximum output W _hmax that is an output of the gas turbine 2 when the intake air temperature T becomes the humidification cooling minimum temperature _Thmin. And a difference output calculation unit 24b for calculating the difference output ΔW. The present humidification cooling minimum temperature _Thmin is input from the humidification cooling minimum temperature calculation unit 21b to the humidification cooling maximum output calculation unit 24a. Then, the humidification / cooling maximum output calculation unit 24a obtains the humidification / cooling maximum output W _hmax with reference to the relationship between the intake air temperature T and the turbine output ((2) of FIG. 2) stored in the storage unit 28 and shown in FIG. . Here, in the humidification cooling, the target air is humidified, and the humidified water evaporates and cools by taking away latent heat. Therefore, in the second cooling means 13 that is humidification cooling, the temperature in the wet state is obtained. _{Is not} less than the minimum humidification cooling temperature T _hmin, which is a temperature obtained by adding the humidification cooling efficiency η _hc to the measured wet bulb temperature T _Wb , in other words, the minimum humidification cooling temperature T _hmin is The minimum temperature that can be cooled by the second cooling means 13 in the state is shown. Therefore, _obtaining the output corresponding to the minimum humidification cooling temperature T _hmin is to obtain the maximum humidification cooling output W _hmax that can be output by the power generation gas turbine 2 by performing the intake air cooling by the second cooling means 13. . Accordingly, the difference output computing unit 24b, by calculating the difference between the required output _{W PR} fogging maximum output _{W hmax,} it is possible to obtain a differential output ΔW between the required output _{W PR} fogging maximum output _{W hmax} . Then, the difference output calculation unit 24b outputs the obtained difference output ΔW to the difference income calculation means 25 and the difference cost calculation means 26, respectively.

Difference income calculation means 25 as a difference income calculation step, and Combined Output power generation gas turbine 2 in the first in the cooling unit 12 air cooled to the required output W _PR, intake air cooling in the second cooling means 13 Then, a differential income INC, which is a difference in income from power generation with _respect to the output from the power generation gas turbine 2 at the humidified cooling maximum output W _hmax , is calculated. More specifically, the difference revenue calculation means 25 need refrigeration power with the required refrigeration power W _IN from necessary refrigeration power calculating unit 23c of the operation unit 23 is inputted, the difference output computing part 24b of the differential output calculation means 24 The differential output ΔW is input. Also, the storage unit 28, the power unit price P _E is stored is the power cost per unit output. Then, the difference income calculating means 25 refers to the power unit price P _E of the storage unit 28 and based on the power unit price P _E , the difference output ΔW and the necessary refrigeration power W _IN , the difference income INC by the following <Equation 5>. Is calculated. That is, the required output _WPR that can be output by the power generation gas turbine 2 by intake air cooling by the first cooling means 12 and the output by the power generation gas turbine 2 by cooling the intake air by the second cooling means 13 from differential output ΔW between fogging maximum output W _hmax, by actually by the intake-air cooling in the first cooling unit 12 to deduct the necessary refrigeration power W _iN fraction as a loss in the actual output difference is calculated is, by multiplying the power unit price P _E to the output difference, power revenue in the case of power generation by the power generation gas turbines 2 of the case of using the case of using a first cooling unit 12 the second cooling unit 13 Can be obtained as the difference income INC. Then, the difference income calculation means 25 outputs the obtained difference income INC to the operation determination means 27. In the above description, the power unit price _PE is stored in the storage unit 28, but may be input from the outside in a timely manner. In this way, it is possible to reflect the electricity unit price P _E in the current performing the calculation of the difference income INC.

Difference cost calculation means 26 as the difference cost calculation step, a Combined Output power generation gas turbine 2 in the first in the cooling unit 12 air cooled to the required output W _PR, intake air cooling in the second cooling means 13 Then, a differential cost Cc, which is a difference in expenditure associated with power generation, from the case of outputting from the gas turbine 2 for power generation with the maximum humidified cooling output W _hmax is calculated. Specifically, the differential cost calculation means 26 receives the differential output ΔW from the differential output calculation means 24 and also generates the power generation efficiency E _G in the generator 3 from the gas turbine control unit 2e, that is, power generation per unit output. The amount is entered. Also, the storage unit 28, the fuel unit price P _F is stored is the fuel price unit calorific value per. Then, the differential cost calculating means 26 refers to the fuel unit price P _F in the storage unit 28, and based on the fuel unit price P _F , the differential output ΔW and the power generation efficiency E _G ((3) in FIG. 2), The differential cost _Cc is calculated by <Equation 6>. That is, the difference output ΔW and the power generation efficiency E _G, it is possible to determine the difference in the power generation amount of the case of using the case of using a first cooling unit 12 the second cooling unit 13, to which the fuel unit price P By multiplying _F , the difference C _F of the fuel cost consumed with power generation can be obtained as the difference cost C _c . Then, the differential cost calculation unit 26 outputs the obtained differential cost _Cc to the operation determination unit 27. Note that the cost associated with power generation is not limited to the actual fuel cost. For example, when the gas turbine 2 for power generation is operated, there is a replacement / repair cost due to the consumption of each member such as a moving blade. Costs may also be considered. However, most of the cost associated with power generation is occupied by the fuel cost. In this embodiment, the differential cost _Cc is calculated in consideration of only the fuel cost. In the above, the fuel unit price P _F is assumed to be stored in the storage unit 28 may be what is timely externally input. By doing so, it is possible to reflect the fuel unit price P _F at the current performing the calculation of the difference cost C _c.

The operation determination unit 27 determines whether the first cooling unit 12 and the second cooling unit 13 are to be operated or not as an operation determination step. In this case, a control signal is sent to the refrigerator 11 through the refrigerator control unit 12c of the first cooling unit 12 and the second cooling unit 13 through the humidification control unit 13d so as to achieve desired intake air cooling. To the humidifying pump 13c. Here, the operation determining means 27 includes the differential income calculating means 25 to the differential income INC, the differential cost calculating means 26 to the differential cost C _c , and the atmospheric temperature measuring unit 15 to the dry bulb temperature T _amb ((5) in FIG. 2). The dew point temperature T _d ((6) in FIG. 2) from the atmospheric dew point temperature calculation unit 21a, the wet bulb temperature T _Wb ((7) in FIG. 2) from the humidification cooling minimum temperature calculation unit 21b, and the required inlet temperature calculation means 22, the required inlet temperature T _PR ((8) in FIG. 2) is inputted. Then, the operation determining means 27 is based on these input differential income INC, differential cost C _c , dry bulb temperature T _amb , dew point temperature T _d , wet bulb temperature T _Wb, and required inlet temperature T _PR in FIG. Based on the determination flow shown, the operation of each of the first cooling means 12 and the second cooling means 13 is determined. Details are shown below.

As shown in FIG. 4, the operation determining means 27 first determines whether or not the dry bulb temperature T _{amb in} the atmosphere is equal to or lower than the required inlet temperature T _PR (step S1). When the dry bulb temperature T _amb is equal to or lower than the required inlet temperature T _PR (YES), that is, the current atmospheric state is the region X shown in FIG. 2 will be able to obtain a required output _{W PR,} operation determining means 27 determines that the first cooling means 12 and the second cooling unit 13 are both inactive (OFF) (step S11). On the other hand, when the dry bulb temperature T _amb is higher than the required inlet temperature T _PR (NO), that is, when it is necessary to perform intake air cooling to obtain the required output W _PR in the power generation gas turbine 2, the following determination is made. Move to the step.

That is, operation determining means 27, then determines whether fogging lowest temperature _{T hmin} of the atmosphere required inlet temperature _{T PR} below (step S2). When the minimum humidification cooling temperature T _hmin is equal to or lower than the required inlet temperature T _PR (YES), that is, the current atmospheric state is more than the wet bulb temperature constant line La passing through the point A in the region Y shown in FIG. In the case of the low temperature side region Y1, the operation determining unit 27 sets the first cooling unit 12 to non-operating (OFF) and sets the second cooling unit 13 to operating (ON) (step S12). . As a result, the intake air of the power generation gas turbine 2 is humidified and cooled only by the second cooling means 13. Here, the atmosphere region Y1, since it is the low temperature side than the wet-bulb temperature constant line La passing through the point A the intake air temperature T becomes the required inlet temperature T _PR, Doing fogging, represented by for example, point B2 from state to B2' point where the request inlet temperature T _PR as a target to reach fogging lowest temperature T _hmin it can be cooled, is possible to output only the required output W _PR minute by a gas turbine for power generation 2 It becomes possible. On the other hand, the humidification when cooled lowest temperature T _hmin is higher than the required inlet temperature T _PR (NO), i.e. if the current state of the air reaches a high temperature side than the wet-bulb temperature constant line La shown in FIG. 3, the following The process proceeds to the determination step.

The operation determining unit 27 determines whether dew point temperature _{T d} of the atmosphere is lower than the required inlet temperature _{T PR} (step S3). When the dew point temperature T _d is equal to or higher than the required inlet temperature T _PR (NO), that is, when the current atmospheric state is the region Z shown in FIG. 3, the process proceeds to step S4, and the dew point temperature T _d Is equal to or lower than the required inlet temperature _TPR (YES), that is, when the current atmospheric state is the region Y2 on the higher temperature side than the wet bulb temperature constant line La passing through the point A in the region Y shown in FIG. In step S5, the process proceeds to step S5. Then, in steps S4, S5, operation determining unit 27 compares the magnitude of the difference revenue INC and the difference cost _{C c.}

Here, the fact that the difference income INC is greater than the difference cost C _c is a power revenue when were generated by first requesting intake air cooling means 12 inlet temperature T _PR until cooled to the required output W _PR No. This means that the difference in power revenue when the second cooling means 13 cools to the extent possible and generates power at the humidified cooling maximum output W _hmax is larger than the difference between the power generation costs. That other words, that the difference income INC is greater than the difference cost C _c, the first power balance difference which is a difference between power balance when were generated by cooling in the first cooling means 12, the second of greater than the second power balance difference which is a difference between power balance when cooled to was generated by the cooling means 13, is better to cool to the required inlet temperature T _PR by the first cooling means 12 second cooling This means that it is more economical than cooling by means 13 as much as possible. On the other hand, the fact that the difference income INC is less than the difference cost C _c is that the first power balance difference by the first cooling means 12 second of power balance difference below by the second cooling means 13, This means that the cooling by the second cooling means 13 as much as possible is more economical than the cooling by the first cooling means 12 to the required inlet temperature _TPR .

That is, in step S4, when the difference income INC is less than the difference cost C _c (NO), as the direction of cooling by the second cooling means 13 is economical, non-operating the first cooling unit 12 (OFF), and the second cooling means 13 is activated (ON) (step S13). As a result, the intake air of the power generation gas turbine 2 is humidified and cooled only by the second cooling means 13. Here, since the atmospheric state in this case is located in the region Z, for example, the atmospheric air located at the point B4 shown in FIG. 3 is humidified along the wet bulb temperature constant line Lb4 passing through the point B4. The air is cooled to the point B4 ′ where the relative humidity becomes 100%, and the power generation gas turbine 2 is driven by the intake air temperature T to obtain the humidified cooling maximum output W _hmax .

On the other hand, in step S4, when the difference income INC is greater than the difference cost C _c (YES), as a direction of cooling by the first cooling means 12 is economical, operation of the first cooling means 12 ( The control signal is output so as to cool to the required inlet temperature _TPR , and the second cooling means 13 is deactivated (OFF) (step S14). As a result, the intake air of the power generation gas turbine 2 is refrigerated and cooled only by the first cooling means 12. For this reason, for example, the air located at the point B4 is lowered until the relative humidity reaches 100% with the absolute humidity φ _amb being constant, and reaches the dew point B4d (dew point temperature T _d4 ), and the temperature is lowered along the relative humidity 100% curve. Then, it is cooled until it reaches the state of point A where the required inlet temperature TPR is _reached . Therefore, it is possible to obtain the required output W _PR by _inhaling at the required inlet temperature _TPR and driving the power generation gas turbine 2.

Further, in step S5, when the difference income INC is less than the difference cost C _c (NO), as the direction of cooling by the second cooling means 13 is economical, non-operating the first cooling unit 12 (OFF), and the second cooling means 13 is activated (ON) (step S15). As a result, the intake air of the power generation gas turbine 2 is humidified and cooled only by the second cooling means 13. Here, since the atmospheric state in this case is located in the region Y1 shown in FIG. 3, for example, the atmospheric air located at the point B3 is humidified along the wet bulb temperature constant line Lb3 passing through the point B by being humidified. The air is cooled to the point B3 ″ where the relative humidity becomes 100%, and the power generation gas turbine 2 is driven by the intake air temperature T to obtain the maximum humidified cooling output W _hmax .

On the other hand, in step S5, when the difference income INC is the difference cost C _c higher (YES), the direction of cooling by the first cooling means 12 is economical, operation of the first cooling means 12 ( Here, the second cooling means 13 is also operated (ON) (step S16). Then, the operation determining means 27, with respect to the first cooling means 12, up to a temperature at which the absolute humidity is the same as the point B3 that is the current atmospheric state and the point B3 ′ is the same as the point A and the wet bulb temperature. A control signal is output so as to cool. In addition, the operation determination unit 27 outputs a control signal to the second cooling unit 13 so as to perform humidification cooling from the point B3 ′ to the point A. As a result, the current atmosphere at the point B3 is first cooled by the first cooling means 12 arranged on the upstream side and moved to the point B3 ′, and further at the second cooling means 13 arranged on the downstream side. After being cooled, it moves to the point A along the wet bulb temperature constant line La and is cooled to the required inlet temperature _TPR . Therefore, it is possible to obtain the required output W _PR by _inhaling at the required inlet temperature _TPR and driving the power generation gas turbine 2.

As described above, the cooling control unit 20 of the present embodiment, by the operation determining unit 27, in step S4, S5 of operation determining step, to generate power at the requested output W _PR performs intake-air cooling in the first cooling means 12 Based on the magnitude comparison between the first power generation balance difference due to the power generation and the second power generation balance difference due to power generation with the maximum humidification cooling output W _hmax possible by performing the intake air cooling with the second cooling means 13, The operation or non-operation of each of the first cooling means 12 and the second cooling means 13 is determined. For this reason, when the first power generation balance difference is large with respect to the second power generation balance difference, that is, when the balance is commensurate with the intake air cooling by driving the refrigerator 11 with the first cooling means 12, by performing the air cooled by the first cooling means 12 can be output from the power generation gas turbine 2 at the required output W _PR regardless of the state of the humidity of the atmosphere. On the other hand, when the first power generation balance difference is smaller than the second power generation balance difference, that is, when the intake air cooling is performed by driving the refrigerator 11 with the first cooling means 12, By performing the intake air cooling by the second cooling means 13, it is possible to output the maximum amount from the power generation gas turbine 2 while ensuring economic efficiency. For this reason, under the control of the cooling control unit 20, the intake air cooling is performed by the refrigeration cooling by the first cooling means 12 and the humidification cooling by the second cooling means 13, thereby increasing the power generation by the power generation gas turbine 2. It is possible to achieve both output and economic efficiency.

Furthermore, the cooling control unit 20 of the present embodiment, the case of step S16 in operation determining step, that is, when the lower than the required inlet temperature T _PR cooled to the dew point in the first cooling means 12, operation determining means 27 A part of the cooling is performed by the second cooling means 13 to cool to the required inlet temperature _TPR . Therefore, the refrigeration power W _IN amount of loss caused by operating the first cooling unit 12 can be minimized, the economy can be further improved. In the present step S16, it is not always necessary to be combined with the first cooling means 12 the second cooling unit 13, may be performed intake air cooling to the required inlet temperature T _PR only the first cooling means 12 .

Furthermore, the cooling control unit 20 of the present embodiment, the operation determination means 27 to implement the step S2 of the operation determining process, when the required inlet temperature _{T PR} is dry-bulb temperature _T below _amb, is fogging lowest temperature _{T hmin} more Thus, the intake air cooling is performed only by the second cooling means 13 without shifting to step S3. In such a case, it is possible to obtain an output corresponding to the required output W _PR from the power generation gas turbine 2 by using the intake air temperature T as the required inlet temperature T _PR even in humidification cooling by the second cooling means 13. Improvement and high output can be achieved. Furthermore, the cooling control unit 20 of the present embodiment, the operation determination means 27 to implement step S1 of operation determining step, if required inlet temperature T _PR is dry-bulb temperature T _amb above, the first cooling means 12 and at least the required output W _PR partial output can be obtained from the power generation gas turbine 2 the second cooling unit 13 as a non-operational, unnecessarily operating the first cooling unit 12 and the second cooling unit 13 You can avoid it.

  In the above embodiment, the first cooling means 12 is arranged on the upstream side and the second cooling means 13 is arranged on the downstream side in the intake path of the power generation gas turbine 2, but this is not limitative. The order of arrangement may be reversed. In this case, the second cooling means 13 for humidifying is arranged on the upstream side, and the humidified air is sucked into the compressor 2 a of the power generation gas turbine 2 after passing through the first cooling means 12. The For this reason, the moisture (mist) supplied by the second cooling means 13 becomes difficult to enter the compressor 2a, and the occurrence of damage such as erosion due to moisture can be more reliably prevented. In addition, when the 2nd cooling means 13 is arrange | positioned upstream, since the cooling by the 2nd cooling means 13 is performed ahead of the cooling by the 1st cooling means 12, in an operation determination process. In step S16, the second cooling means 13 performs humidification cooling along the wet bulb temperature constant line Lb3 from the point B3 to the point B3 ″ where the relative humidity becomes 100% as shown in FIG. The cooling means 12 performs refrigeration cooling from the point B3 ″ to the point A.

  In addition, the second cooling means 13 has a structure in which a porous material is provided in the intake flow path, but is not limited to this, and any structure can be selected as long as the structure can humidify the intake air. You may do it. For example, as in the first modification shown in FIG. 5, a water sprayer 13h is provided in place of the evaporative cooler 13a, and a large number of nozzles 13i of the water sprayer 13h are arranged in the intake flow path, and water is supplied from the nozzles 13i. It is good also as what humidifies intake air by making it spray.

  In the above embodiment, the gas turbine plant 1 includes the power generation gas turbine 2, the power generator 3, and the gas turbine intake air cooling device 10. Further, the exhaust gas using the exhaust gas in the power generation gas turbine 2 is used. You may comprise as a gas turbine combine implant provided with the gas utilization means. FIG. 6 shows a second modification of the gas turbine combine implant. As shown in FIG. 6, the gas turbine plant 30 of this modification includes a power generation gas turbine 2, a generator 3, a gas turbine intake air cooling device 10, a steam generation means 31 that is an exhaust gas utilization means, A high-pressure steam turbine 32 and a low-pressure steam turbine 33 that are driven by steam discharged from the steam generation means 31, and a condenser 34 that generates water from the steam discharged from the low-pressure steam turbine 33.

  In this embodiment, the steam generating means 31 includes a high pressure superheater 31a, a high pressure evaporator 31b, a high pressure economizer 31c, a low pressure superheater 31d, a low pressure evaporator 31e, and a low pressure economizer 31f. The exhaust gas supplied from the power generation gas turbine 2 flows in this order, and receives heat supply from the exhaust gas.

  In the low pressure economizer 31f, water is supplied from the condenser 34 by the pump 34a, and the supplied water is preheated by the heat supplied from the exhaust gas from the turbine 2c, and the low pressure evaporator 31e and the high pressure economizer 31c. To supply. In the low-pressure evaporator 31e, the water preheated in the low-pressure economizer 31f is heated by the heat supplied from the exhaust gas to generate steam, which is supplied to the low-pressure superheater 31d. In the low-pressure superheater 31 d, the supplied steam is heated by the heat supplied from the exhaust gas from the turbine 2 c to generate superheated steam and supply it to the low-pressure steam turbine 33.

  In the high pressure economizer 31c, the water supplied by being pressurized by the pump 31g from the low pressure economizer 31f is further preheated by the heat supplied from the exhaust gas from the turbine 2c and supplied to the high pressure evaporator 31b. The In the high pressure evaporator 31b, the water preheated in the high pressure economizer 31c is heated by the heat supplied from the exhaust gas, and steam is generated and supplied to the high pressure superheater 31a. In the high-pressure superheater 31a, the supplied steam is heated by the heat supplied from the exhaust gas from the turbine 2c, and superheated steam is generated and supplied to the high-pressure steam turbine 32.

  The high-pressure steam turbine 32 can be driven by the steam supplied from the high-pressure superheater 31 a and can generate power with the generator 35. Further, the steam circulated in the high-pressure steam turbine 32 is supplied to the low-pressure steam turbine 33 together with the steam from the low-pressure superheater 31d, so that the low-pressure steam turbine 33 can be driven and the generator 36 can generate power. is there. The steam that has circulated in the low-pressure steam turbine 33 is supplied to the condenser 34 and then supplied to the steam generation means 31 again.

  As described above, in the gas turbine plant 30 provided with the steam generation means 31 as the exhaust gas utilization means, the high-pressure steam turbine 32 and the low-pressure steam turbine 33 can be driven using the exhaust gas to generate electric power. In addition, the economy can be further improved.

  As mentioned above, although embodiment of this invention was explained in full detail with reference to drawings, the concrete structure is not restricted to this embodiment, The design change etc. of the range which does not deviate from the summary of this invention are included.

For example, in each of the above-described embodiments, the first cooling unit 12 and the second cooling unit 13 are connected in series, but a configuration in which one of them is connected in parallel and selectively used may be used.
In addition, the present invention is not a technology that is applied only to a newly installed gas turbine plant, but can also be applied to an existing gas turbine plant. That is, the gas turbine 2 for electric power generation is provided as an existing gas turbine plant, and the intake-air cooling apparatus 10 for gas turbines is installed here. Alternatively, as an existing gas turbine plant, at least one of the power generation gas turbine 2 and the first cooling means 12 or the second cooling means 13 is provided, and the first cooling means 12 or the second cooling is provided here. By installing the other of the means 13 and the cooling control unit 12, the gas turbine intake air cooling device 10 is configured. Furthermore, the first cooling means 12 and the second cooling means 13 may both be provided as existing, and the cooling control unit 12 may be incorporated therein to constitute the gas turbine intake air cooling device 10.
In any pattern, in the gas turbine plants 1 and 30 configured by being reconstructed, the power generation by the existing gas turbine for power generation is economical and high output. be able to.

DESCRIPTION OF SYMBOLS 1, 30 Gas turbine plant 2 Gas turbine for electric power generation 2a Compressor 2b Combustor 2c Turbine 10 Intake cooling device for gas turbine 11 Refrigerator 12 First cooling means 13 Second cooling means 20 Cooling control part 21 Temperature calculating means 22 Required inlet temperature calculating means 23 Required refrigeration power calculating means 24 Differential output calculating means 25 Differential income calculating means 26 Differential cost calculating means 27 Operation determining means C _c Differential cost (≈C _F )
INC differential income T _amb dry bulb temperature T _PR required inlet temperature T _d dew point temperature T _Wb wet bulb temperature W _IN required refrigeration power W _PR required output W _hmax humidification cooling maximum output φ _amb absolute humidity ΔW differential output

Claims (14)

An intake air cooling device for a gas turbine used for intake air cooling of a power generation gas turbine having a compressor, a combustor, and a turbine,
First cooling means for driving a refrigerator to cool the air taken into the power generation gas turbine;
A second cooling means for cooling the air taken into the power generation gas turbine by humidification;
A cooling control unit capable of switching each of the first cooling means and the second cooling means to operation or non-operation;
The cooling control unit is configured to perform a first air generation cooling difference by generating an electric power by the power generation gas turbine with a required output acquired in advance by performing intake air cooling with the first cooling means; and Based on the magnitude comparison with the second power generation balance difference, which is the difference in power generation balance by generating power with the power generation gas turbine at the maximum output possible by performing intake air cooling with the second cooling means, An intake air cooling device for a gas turbine that determines whether each of the cooling means and the second cooling means are in operation or not. The intake-air cooling apparatus for a gas turbine according to claim 1,
The cooling control unit is necessary for the refrigerator to cool the intake air by the first cooling means to a required inlet temperature that is an intake temperature at which the power generation gas turbine can output at the required output. Necessary refrigeration power calculating means for calculating the required refrigeration power that is assumed to be power,
Differential output calculation means for calculating a differential output between the required output and the maximum output that can be output by the power generation gas turbine by performing intake air cooling with the second cooling means;
Based on the required refrigeration power obtained by the necessary refrigeration power calculating means and the difference output obtained by the differential output calculating means, the first cooling means cools the intake air and generates the power generation gas at the required output. Differential income calculation for calculating differential income, which is the difference in income from power generation between when output from a turbine and when the intake air is cooled by the second cooling means and output from the gas turbine for power generation at the maximum output Means,
Based on the differential output obtained by the differential output calculation means, when the intake air is cooled by the first cooling means and output from the gas turbine for power generation at the required output, and the second cooling means Differential cost calculating means for calculating a differential cost, which is a difference in expenditure associated with power generation when the intake gas is cooled and output from the power generation gas turbine at the maximum output;
The difference income and the difference cost are compared, and when the difference income is equal to or less than the difference cost, the first cooling means is inactive, the second cooling means is in operation, and the difference income is The gas turbine intake air cooling device further includes an operation determining unit that operates at least the first cooling unit when the difference is larger than the differential cost. The intake air cooling device for a gas turbine according to claim 2,
Requested inlet temperature calculating means for calculating the required inlet temperature based on the required output acquired in advance;
Temperature calculating means for calculating the dew point temperature and wet bulb temperature of the atmosphere based on the dry bulb temperature and humidity of the atmosphere to be acquired,
The required refrigeration power calculating means calculates the required refrigeration power based on the required inlet temperature calculated by the required inlet temperature calculating means and the dew point temperature calculated by the temperature calculating means,
The difference output calculating means calculates the difference output based on the required output and the wet bulb temperature calculated by the temperature calculating means. In the intake-air cooling apparatus for gas turbines of Claim 2 or Claim 3,
The operation determining means acquires the dry bulb temperature of the atmosphere and the required inlet temperature, compares the magnitude, and if the required inlet temperature is equal to or higher than the dry bulb temperature, the first power generation balance difference and An intake air cooling apparatus for a gas turbine, wherein the first cooling means and the second cooling means are inoperative regardless of the magnitude of the second power generation balance difference. In the intake-air cooling apparatus for gas turbines as described in any one of Claims 2-4,
The operation determining means obtains the atmospheric dry bulb temperature and wet bulb temperature, and the required inlet temperature, compares the magnitude, and the required inlet temperature is less than the dry bulb temperature, humidified cooling obtained from the wet bulb temperature. When the temperature is not less than the minimum temperature, the first cooling means is deactivated regardless of the magnitude of the first power generation balance difference and the second power generation balance difference, and the second cooling means is activated. An intake air cooling device for a gas turbine. In the intake-air cooling apparatus for a gas turbine according to any one of claims 2 to 5,
The operation determining means obtains the atmospheric dew point temperature and the required inlet temperature and compares them, and if the required inlet temperature is equal to or lower than the dew point temperature and the differential income is greater than the differential cost, When the second cooling means is deactivated, the required inlet temperature is higher than the dew point temperature, and the differential income is larger than the differential cost, the second cooling means is also operated together with the first cooling means. An intake air cooling device for a gas turbine, characterized in that An intake air cooling device for a gas turbine according to any one of claims 1 to 6,
A gas turbine plant comprising the gas turbine for power generation.   The reconstructing method for an existing gas turbine plant, wherein the gas turbine plant according to claim 7 is constructed by additionally installing the gas turbine intake air cooling device with respect to the existing power generation gas turbine. A power generation gas turbine having a compressor, a combustor, and a turbine drives the refrigerator to cool the air sucked into the power generation gas turbine and humidifies the power generation gas. A gas turbine intake air cooling method for cooling air taken into the turbine by a second cooling means for cooling,
A first power generation balance difference, which is a difference in power generation balance by performing intake air cooling with the first cooling means and generating power by the power generation gas turbine with a required output acquired in advance, and the second cooling means. Based on the magnitude comparison with a second power generation balance difference that is a difference in power generation balance by generating power with the power generation gas turbine at the maximum output possible by performing intake air cooling, the first cooling means and the first An intake air cooling method for a gas turbine, characterized in that operation or non-operation of each of the second cooling means is determined. The gas turbine intake air cooling method according to claim 9,
Power required by the refrigerator to cool the intake air by the first cooling means to a required inlet temperature that is an intake temperature at which the power generation gas turbine can output at the required output. A required refrigeration power calculation step for calculating the required refrigeration power;
A differential output calculation step of calculating a differential output between the required output and the maximum output that can be output by the power generation gas turbine by performing intake air cooling with the second cooling means;
Based on the required refrigeration power obtained in the necessary refrigeration power calculation step and the difference output obtained in the difference output calculation step, the first cooling means cools the intake air and generates the power generation gas at the required output. Differential income calculation for calculating differential income, which is the difference in income from power generation between when output from a turbine and when the intake air is cooled by the second cooling means and output from the gas turbine for power generation at the maximum output Process,
Based on the differential output obtained in the differential output calculation step, the first cooling means cools the intake air and outputs the required output from the gas turbine for power generation, and the second cooling means A differential cost calculation step of calculating a differential cost that is a difference in expenditure associated with power generation when the intake gas is cooled and output from the power generation gas turbine at the maximum output;
The difference income and the difference cost are compared, and when the difference income is equal to or greater than the difference cost, the first cooling means is inactive, the second cooling means is in operation, and the difference income is And an operation determining step of operating at least the first cooling means when the difference cost is greater than the differential cost. In the gas turbine intake air cooling method according to claim 10,
A required inlet temperature calculating step of calculating the required inlet temperature based on the required output acquired in advance;
A temperature calculation step for calculating the dew point temperature and the wet bulb temperature of the atmosphere based on the dry bulb temperature and the atmospheric humidity of the atmosphere to be acquired;
In the required refrigeration power calculation step, the required refrigeration power is calculated based on the required inlet temperature calculated in the required inlet temperature calculation step and the dew point temperature calculated in the temperature calculation step,
In the differential output calculation step, the differential output is calculated based on the required output and the wet bulb temperature calculated in the temperature calculation step. The gas turbine intake air cooling method according to claim 10 or 11,
In the operation determining step, the dry-bulb temperature of the atmosphere and the required inlet temperature are acquired and compared in magnitude, and when the required inlet temperature is equal to or higher than the dry-bulb temperature, the first power generation balance difference and A gas turbine intake air cooling method, wherein the first cooling means and the second cooling means are deactivated regardless of the magnitude of the second power generation balance difference. In the gas turbine intake air cooling method according to any one of claims 10 to 12,
In the operation determination step, the dry bulb temperature and wet bulb temperature of the atmosphere, and the required inlet temperature are obtained and compared in magnitude, and the required inlet temperature is less than the dry bulb temperature and humidification cooling obtained from the wet bulb temperature. When the temperature is not less than the minimum temperature, the first cooling means is deactivated regardless of the magnitude of the first power generation balance difference and the second power generation balance difference, and the second cooling means is activated. An intake air cooling method for a gas turbine. In the gas turbine intake air cooling method according to any one of claims 10 to 13,
In the operation determination step, when the dew point temperature of the atmosphere and the required inlet temperature are acquired and compared, the required inlet temperature is less than the dew point temperature and the difference income is less than the difference cost. When the second cooling means is deactivated, the required inlet temperature is equal to or higher than the dew point temperature, and the differential income is less than the differential cost, the second cooling means is also used together with the first cooling means. An intake air cooling method for a gas turbine, wherein the gas turbine is operated.

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