Gas turbine intake cooling system and method coupling evaporative refrigeration with compressed refrigeration

Abstract

The application discloses a gas turbine intake cooling system and method coupling evaporation refrigeration and compression refrigeration, and the system comprises: an intake cooling unit, comprising a honeycomb water trap, an intake heat exchanger group and a filter module; a spray evaporation cooling loop, in fluid communication with the honeycomb water trap, for spraying atomized cooling water to the honeycomb water trap; a compression refrigeration indirect cooling loop, in fluid communication with the intake heat exchanger group, for providing chilled water to the intake heat exchanger group; an environmental parameter acquisition unit, for acquiring environmental data in real time; and a controller, in communication connection with the environmental parameter acquisition unit, the spray evaporation cooling loop and the compression refrigeration indirect cooling loop respectively, for controlling the gas turbine intake cooling system to operate in a refrigeration mode, a spray evaporation cooling mode or a compression refrigeration indirect cooling mode according to a pre-acquired power generation plan and environmental data. The application can realize a gas turbine intake cooling effect with good uniformity, high control precision, low operation cost and safety and reliability.

Description

Technical Field

[0001] This invention belongs to the field of gas turbine intake air cooling technology, and particularly relates to a gas turbine intake air cooling system and method that couples evaporative refrigeration and compression storage. Background Technology

[0002] Gas turbines are core power equipment in combined cycle power generation and distributed energy systems. With their characteristics of rapid start-up, strong peak-shaving capability, and clean and efficient operation, they play a crucial role in peak shaving and baseload power generation in power systems. However, the power output and thermal efficiency of gas turbines are highly sensitive to inlet air temperature. Increased ambient temperature leads to a significant decrease in the unit's (gas turbine's) output and efficiency, especially during the high-temperature periods of summer, often failing to meet the peak electricity demand of the grid and severely impacting the reliability of the power supply system.

[0003] To address the issue of insufficient power output from gas turbines during high-temperature seasons, inlet air cooling technology has been widely adopted. Currently, the most common inlet air cooling methods for gas turbines in the industry are mainly divided into two categories: direct spray evaporation cooling and indirect chilled water heat exchange cooling. Both methods have significant limitations. Spray evaporation cooling relies on water mist evaporation to absorb heat and cool the inlet air. While the system structure is simple and the investment and operating energy consumption are relatively low, its cooling effect is severely constrained by ambient temperature and humidity conditions. In high-humidity environments, its cooling capacity is significantly reduced. Furthermore, traditional spray cooling often uses a uniform spray control method, which cannot be differentiated based on differences in wind direction and speed, easily leading to uneven cooling in the inlet area. Indirect chilled water heat exchange cooling is not limited by ambient humidity, provides stable cooling, and can achieve deep cooling. However, conventional refrigeration systems lack cold energy storage, cannot operate in accordance with the fluctuations in electricity spot market prices, and cannot leverage peak-valley electricity price differences to reduce the operating costs of the cooling system.

[0004] Meanwhile, existing gas turbine inlet cooling systems generally employ traditional feedback-based control logic, adjusting the cooling medium flow rate based on the deviation between the actual inlet temperature and the preset target temperature. However, the inlet heat exchange and cooling process exhibits significant lag and large inertia. Traditional control methods suffer from slow response speed and limited adjustment accuracy, making them unsuitable for the rapid load changes of gas turbines. They fail to maintain stable inlet temperature during rapid load fluctuations, negatively impacting the safe, stable, and efficient operation of the unit. Furthermore, most existing coupled inlet cooling systems have simple control logic, unable to flexibly switch between evaporative cooling and direct cooling modes based on actual unit output conditions and environmental meteorological conditions, resulting in low system adaptability and overall utilization efficiency.

[0005] Therefore, there is an urgent need to develop a gas turbine inlet cooling system and method that combines the advantages of evaporative cooling and compression storage cooling, has good cooling uniformity, high control precision, low operating cost, and is safe and reliable, in order to solve many problems existing in the current technology. Summary of the Invention

[0006] The purpose of this invention is to provide a gas turbine intake air cooling system and method that couples evaporative cooling and compression storage cooling, combining the advantages of evaporative cooling and compression storage cooling to achieve a gas turbine intake air cooling effect with good uniformity, high control precision, low operating cost, and safety and reliability.

[0007] To achieve the above objectives, the present invention employs the following technical solution:

[0008] In a first aspect, the present invention provides a gas turbine intake air cooling system that couples evaporative refrigeration and compression refrigeration, comprising:

[0009] The intake cooling unit includes a honeycomb water separator, an intake heat exchanger group, and a filter module arranged sequentially along the gas turbine intake direction;

[0010] A spray evaporative cooling circuit, fluidly connected to the honeycomb water separator, is used to spray atomized cooling water onto the honeycomb water separator. The spray evaporative cooling circuit includes a buffer water tank, a booster pump, a solenoid valve group, and a spray cooler group connected in sequence. The outlet of the buffer water tank is connected to the input end of the solenoid valve group through the booster pump. The multiple output ends of the solenoid valve group are respectively connected to each spray cooler in the spray cooler group. The spray cooler group includes multiple spray coolers arranged in sections along different directions of the air intake cooling unit, and the spray cooler group is arranged upstream of the honeycomb water separator along the air intake direction.

[0011] A compressed cold storage indirect cooling circuit is fluidly connected to the intake air heat exchanger group and is used to supply chilled water to the intake air heat exchanger group;

[0012] Environmental parameter acquisition unit, used to collect environmental data in real time;

[0013] The controller is communicatively connected to the environmental parameter acquisition unit, the spray evaporation cooling circuit, and the compression storage indirect cooling circuit, and is used to control the gas turbine intake cooling system to operate in storage mode, spray evaporation cooling mode, or compression storage indirect cooling mode according to the pre-acquired power generation plan and environmental data.

[0014] Optionally, the compression cold storage indirect cooling circuit includes a refrigeration unit, a cold water pump, a cold storage tank, a cold release pump, and a first valve, a second valve, a third valve, a fourth valve group, a fifth valve, a sixth valve, and a seventh valve; the fourth valve group includes multiple electrically adjustable valves, each of which corresponds to a heat exchange zone of the intake air heat exchanger group, with its inlet connected in parallel to the cold source water supply main pipe and its outlet connected to the water inlet of the corresponding heat exchange zone respectively;

[0015] The outlet of the refrigeration unit is connected to the first side of the third valve via a cold water pump. The outlet of the third valve is connected to the main cold water supply pipe of the fourth valve group and the first side of the seventh valve. The second side of the seventh valve is connected to the first side of the sixth valve and the first side of the cold release pump. The second side of the sixth valve and the second side of the cold release pump are both connected to the cold storage tank.

[0016] The return water inlet of the refrigeration unit is connected to the first side of the second valve, and the second side of the second valve is connected to the first side of the first valve and the first side of the fifth valve respectively; the second side of the first valve is connected to the outlet of each heat exchange zone of the air inlet heat exchanger group; the second side of the fifth valve is connected to the cold storage tank.

[0017] Optionally, the gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage further includes:

[0018] A cold source temperature sensor is installed on the cold source water supply main pipe of the fourth valve group and is connected in communication with the controller to measure the current cold source outlet water temperature in real time.

[0019] Multiple zone flow sensors are installed on the air inlet side of each heat exchange zone of the air inlet heat exchanger group and are connected in communication with the controller to measure the air inlet flow of each heat exchange zone in real time.

[0020] Optionally, the controller is electrically connected to the booster pump, solenoid valve group, chilled water pump, cold release pump, refrigeration unit, and the first, second, third, fourth valve group, fifth, sixth, and seventh valves, respectively, for outputting control commands to adjust the operating status of each actuator; the controller is embedded with a trained spray cooling feedforward model and a cold storage cooling feedforward model. The spray cooling feedforward model is used to calculate the optimal spray water distribution coefficient of each direction of the intake cooling unit based on the input environmental data, theoretical unit volume spray water volume, and equipment operating status of the gas turbine intake cooling system; the cold storage cooling feedforward model is used to output the optimal opening command of each electric regulating valve in the fourth valve group based on the input current cold source outlet water temperature, intake air flow rate of each heat exchange zone, target intake air temperature, and environmental data.

[0021] In a second aspect, the present invention provides a gas turbine intake air cooling method that couples evaporative refrigeration and compression cold storage, applied to a controller in a gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage as described in the first aspect, characterized in that it includes:

[0022] Acquire real-time environmental data; the environmental data includes: wind direction, wind speed, temperature, humidity, and atmospheric pressure data;

[0023] Based on the pre-acquired functional relationship between the maximum power output of the gas turbine and the inlet air temperature, environmental data, and power generation plan, it is determined whether the gas turbine is in the maximum power output state;

[0024] If it is determined that the gas turbine is not at its maximum power output, then it is further determined whether the cold storage tank contains chilled water to meet the cooling requirements. If so, the gas turbine intake cooling system is shut down; otherwise, the gas turbine intake cooling system is put into cold storage mode.

[0025] If it is determined that the gas turbine is in the maximum power generation state, the inverse function of the above functional relationship is used to calculate the inlet temperature required to achieve the target power generation, and this temperature is used as the target inlet temperature.

[0026] Determine whether the target intake air temperature is less than or equal to the average value of the evaporative cooling limit temperature in each direction calculated based on the environmental data. If so, the gas turbine intake air cooling system is operated in spray evaporative cooling mode; otherwise, the intake air cooling system is operated in compression storage indirect cooling mode.

[0027] Optionally, determining whether the gas turbine is in its maximum power generation output state includes:

[0028] Real-time acquisition of the opening degree of the gas turbine inlet adjustable guide vanes, the target power output given in the power generation plan, and the actual power output;

[0029] Based on the environmental data, the theoretical maximum power output of the gas turbine under the current environmental conditions is calculated using the functional relationship between the maximum power output of the gas turbine and the inlet air temperature.

[0030] When the target power generation output is not less than the theoretical maximum power generation output, and the opening degree of the inlet adjustable guide vane reaches the preset maximum opening degree threshold, and the absolute value of the deviation between the actual power generation output and the theoretical maximum power generation output is less than the preset output deviation threshold, the gas turbine is judged to be in the maximum power generation output state.

[0031] Optionally, operating the gas turbine intake cooling system in a cold storage mode includes:

[0032] Close all valves and booster pumps in the spray evaporation cooling circuit;

[0033] Close the first valve, the fourth valve group, and the cold release pump in the compression cold storage indirect cooling circuit;

[0034] Start the refrigeration unit and chilled water pump;

[0035] Open the second, third, fifth, sixth, and seventh valves;

[0036] The chilled water produced by the refrigeration unit is successively sent to the bottom of the cold storage tank through the cold water pump, the third valve, the seventh valve, and the sixth valve for storage. The chilled water at the top of the cold storage tank is then successively sent to the return water port of the refrigeration unit through the fifth valve and the second valve.

[0037] Optionally, operating the gas turbine intake air cooling system in spray evaporative cooling mode includes:

[0038] Start the booster pump and close all valves, chilled water pump, cold release pump and refrigeration unit of the compression cold storage indirect cooling circuit;

[0039] The initial moisture content of the air is calculated based on temperature, atmospheric pressure and humidity data, and the evaporative cooling limit temperature is iteratively calculated based on the initial moisture content of the air, and the theoretical water spray volume per unit volume is calculated based on the evaporative cooling limit temperature.

[0040] The theoretical unit volume water spray volume, wind direction and wind speed data, as well as the equipment operating status of the gas turbine intake cooling system, are input into the spray cooling feedforward model to obtain the optimal water spray volume distribution coefficients for each direction of the intake cooling unit.

[0041] Calculate the actual required water spray volume in each direction of the intake cooling unit based on the optimal water spray volume distribution coefficient;

[0042] Based on the actual required water spray volume in each direction, the single valve flow characteristics of the solenoid valve group are matched, and the optimal switching combination and timing control of each solenoid valve are output so that the intake temperature of the intake cooling unit in each direction after cooling approaches the evaporative cooling limit temperature.

[0043] Optionally, operating the intake cooling system in a compression-storage indirect cooling mode includes:

[0044] Close all valves and booster pumps in the spray evaporation cooling circuit;

[0045] Determine whether the cold storage tank contains enough chilled water to meet the cooling requirements;

[0046] If so, construct a cold storage and release loop; otherwise, construct a direct cooling loop.

[0047] The current cold source outlet water temperature, the air flow rate of each heat exchange zone of the gas turbine, and the target air inlet temperature are obtained in real time. The current cold source outlet water temperature is the outlet water temperature of the cold source in the current operating loop.

[0048] Input the current cold source outlet water temperature, the air flow rate of each heat exchange zone, the target air inlet temperature, and environmental data into the cold storage cooling feedforward model to obtain the optimal opening command for each electric regulating valve in the fourth valve group.

[0049] According to the optimal opening command, the opening degree of each electric regulating valve in the fourth valve group is dynamically adjusted to match the chilled water flow rate of each heat exchange zone with the air intake flow rate of the corresponding zone, to compensate for the influence of uneven airflow distribution in the intake duct on the cooling effect, so that the intake air temperature of each zone after cooling can stably reach the target intake air temperature.

[0050] Optionally, the construction of the cold storage and release circulation loop includes: starting the cold release pump; opening the first valve, the fourth valve group, the fifth valve, and the seventh valve; closing the second valve, the third valve, and the sixth valve; the chilled water at the bottom of the cold storage tank is sequentially transferred to the inlet of the air intake heat exchanger group for cooling through the cold release pump, the seventh valve, and the fourth valve group; the returned water after cooling enters the return water port of the refrigeration unit from the outlet of the air intake heat exchanger group through the first valve and the second valve.

[0051] The direct cooling cycle includes: starting the refrigeration unit and the chilled water pump, opening the first valve, the second valve, the third valve and the fourth valve group, and closing the fifth valve, the sixth valve, the seventh valve and the release pump; the chilled water produced by the refrigeration unit is successively sent to the inlet of the air intake heat exchanger group for cooling through the chilled water pump, the third valve and the fourth valve group, and the return water after cooling enters the return water port of the refrigeration unit from the outlet of the air intake heat exchanger group through the first valve and the second valve in sequence.

[0052] Compared with the prior art, the beneficial effects achieved by the present invention are as follows:

[0053] The present invention provides a gas turbine intake air cooling system and method that couples evaporative cooling and compression storage cooling. The system sets up an intake air cooling unit including a honeycomb evaporative cooling device and an intake air heat exchanger group, and builds a dual cooling structure of a spray evaporative cooling loop and a compression storage indirect cooling loop. An environmental parameter acquisition unit is configured to collect real-time environmental data, and the controller communicates with each unit and loop to achieve coordinated control of each actuator. It fully integrates the advantages of spray evaporative cooling and compression storage indirect cooling to achieve uniform, precise, economical and safe cooling of the gas turbine intake air, and can reduce operating costs and improve operational stability.

[0054] The present invention provides a gas turbine intake air cooling system and method that couples evaporative refrigeration and compression cold storage. This method achieves intelligent start-up and shutdown and adaptive mode switching of the cooling system by clarifying the judgment logic of the gas turbine's maximum power generation output state and the switching mechanism of cooling mode and cold storage mode. The cooling mode is activated only when the unit is in the maximum power generation output state. When it is not in the maximum power generation output state, cold storage or shutdown is selected according to the cold storage tank's cooling capacity. This avoids unnecessary energy waste and makes full use of the unit's idle time for cold storage, which is in line with the peak and valley electricity price rules of the spot electricity market, effectively reducing system operating costs. At the same time, it ensures that the operation of the cooling system is precisely matched with the unit's output demand, thereby improving the system's operating economy. Attached Figure Description

[0055] Figure 1 The diagram shown is a process flow chart of a gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage in one embodiment of the present invention.

[0056] Figure 2 The figure shown is a cross-sectional view of the air intake cooling unit duct in one embodiment of the present invention;

[0057] Figure 3 The figure shown is a graph illustrating the functional relationship between the maximum power output of the gas turbine and the inlet air temperature in one embodiment of the present invention.

[0058] Figure 4 The diagram shown is a flow chart of a gas turbine intake air cooling method that couples evaporative refrigeration and compression cold storage in one embodiment of the present invention.

[0059] In the diagram: 1. Gas turbine; 2. Honeycomb precipitator; 3. Inlet heat exchanger assembly; 4. Filter module; 5. Buffer water tank; 6. Booster pump; 7. Solenoid valve assembly; 8. Spray cooler assembly; 9. Refrigeration unit; 10. Cold water pump; 11. Cold storage tank; 12. Cold release pump; 131. First valve; 132. Second valve; 133. Third valve; 134. Fourth valve assembly; 135. Fifth valve; 136. Sixth valve; 137. Seventh valve. Detailed Implementation

[0060] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0061] Example 1

[0062] like Figure 1-2 As shown in the figure, this embodiment of the invention introduces a gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage, including: an intake air cooling unit, a spray evaporative cooling circuit, a compression cold storage indirect cooling circuit, an environmental parameter acquisition unit, and a controller;

[0063] In this embodiment, the intake cooling unit includes a honeycomb water separator 2, an intake heat exchanger group 3, and a filter module 4 arranged sequentially along the gas turbine intake direction.

[0064] Among them, the honeycomb water eliminator 2 has an internal honeycomb structure, which can efficiently remove free water droplets carried in the air after spray cooling, and prevent droplets from entering downstream equipment and causing wet compression; the intake heat exchanger group 3 is arranged between the honeycomb water eliminator 2 and the filter module 4, dividing the entire air duct cross section into multiple independent heat exchange zones. Each zone is equipped with an independent chilled water supply branch pipe and an electric regulating valve, which can independently adjust the chilled water flow according to the intake air flow of the zone to compensate for the influence of uneven airflow distribution in the intake duct; the filter module 4 is arranged at the downstream end of the intake treatment unit. As the primary air filtration device of the gas turbine 1, it can further remove impurities in the air, prevent pollutants from entering the gas turbine compressor, and ensure the safe operation of the unit.

[0065] The components are detachably connected by flanges or clamps, which facilitates inspection and maintenance. At the same time, the overall structure of the air intake treatment unit is compatible with the original air intake duct of the gas turbine 1, which does not require large-scale modification of the unit body, making construction easy and highly adaptable.

[0066] In this embodiment, the spray evaporation cooling circuit is in fluid communication with the honeycomb water separator 2 and is used to spray atomized cooling water into the honeycomb water separator 2. The spray evaporation cooling circuit includes a buffer water tank 5, a booster pump 6, a solenoid valve group 7, and a spray cooler group 8 connected in sequence. The outlet of the buffer water tank 5 is connected to the input end of the solenoid valve group 7 through the booster pump 6. The multiple output ends of the solenoid valve group 7 are respectively connected to each spray cooler in the spray cooler group 8. The spray cooler group 8 is arranged upstream of the honeycomb water separator along the air inlet direction and is arranged in sections along different directions of the air duct cross-section, such as... Figure 2 As shown, multiple spray coolers are set in each of the three directions corresponding to the left, right and down of the air intake duct. The spray volume can be independently controlled according to the wind direction and wind speed to achieve precise spraying. In this embodiment, the compression cold storage indirect cooling circuit is fluidly connected to the air intake heat exchanger group 3 and is used to provide chilled water to the air intake heat exchanger group 3.

[0067] The compression cold storage indirect cooling circuit includes a refrigeration unit 9, a cold water pump 10, a cold storage tank 11, a cold release pump 12, and a first valve 131, a second valve 132, a third valve 133, a fourth valve group 134, a fifth valve 135, a sixth valve 136, and a seventh valve 137; the fourth valve group 134 includes multiple electrically adjustable valves, each of which corresponds to a heat exchange zone of the air intake heat exchanger group 3, with its inlet connected in parallel to the cold source water supply main pipe, and its outlet connected to the water inlet of the corresponding heat exchange zone;

[0068] The outlet of the refrigeration unit 9 is connected to the first side of the third valve 133 via the cold water pump 10. The outlet of the third valve 133 is connected to the cold source water supply main pipe of the fourth valve group 134 and the first side of the seventh valve. The second side of the seventh valve 137 is connected to the first side of the sixth valve 136 and the first side of the cold release pump 12. The second side of the sixth valve 136 and the second side of the cold release pump 12 are both connected to the cold storage tank 11.

[0069] The return water inlet of the refrigeration unit 9 is connected to the first side of the second valve 132, and the second side of the second valve 132 is connected to the first side of the first valve and the first side of the fifth valve 135 respectively; the second side of the first valve 131 is connected to the outlet of each heat exchange zone of the air inlet heat exchanger group 3; the second side of the fifth valve 135 is connected to the cold storage tank 11.

[0070] Specifically, refrigeration unit 9 is an electric compressor refrigeration unit, equipped with a matching power tower and a circulating pump. The power tower is located outdoors and forms a closed cooling water circulation loop with the condenser side of the electric compressor refrigeration unit through the circulating pump. It is used to provide cooling medium for the condenser of the electric compressor refrigeration unit, remove the condensation heat released during the refrigeration process, and ensure that the unit operates stably under rated conditions.

[0071] The refrigeration unit 9 can be flexibly started and stopped according to the system operation mode. In the cooling mode, it directly provides chilled water to the air intake heat exchanger group 3; in the cold storage mode, it sends the produced low-temperature chilled water to the cold storage tank 11 for storage, so as to realize the off-peak distribution of cooling capacity.

[0072] In this embodiment, the environmental parameter acquisition unit includes a wind direction and speed meter, a temperature sensor, a humidity sensor, and an atmospheric pressure sensor arranged at the inlet of the gas turbine 1 air intake duct. Each sensor is electrically connected to the controller and is used to collect environmental data at the inlet of the air intake duct in real time, specifically including: wind direction data, wind speed data, temperature data, humidity data, and atmospheric pressure data.

[0073] An anemometer is installed in an open area on the windward side of the air intake duct. It can continuously measure the direction and speed distribution of incoming airflow from different directions, providing multi-directional airflow parameter input for the spray cooling feedforward model to achieve optimized allocation of water spray volume for each spray cooler. Temperature, humidity and atmospheric pressure sensors are integrated at the same acquisition point, which can simultaneously acquire the current ambient temperature, humidity and atmospheric pressure values. These values ​​are used to calculate the evaporative cooling limit temperature, initial air humidity and theoretical water spray volume per unit volume, providing basic data support for the operation condition judgment and control logic of the spray evaporative cooling mode.

[0074] In this embodiment, the gas turbine intake cooling system further includes: a cold source temperature sensor, installed on the cold source water supply main pipe of the fourth valve group and connected in communication with the controller, for real-time measurement of the current cold source outlet water temperature; and multiple zone flow sensors, respectively installed on the intake side of each heat exchange zone of the intake heat exchanger group 3 and connected in communication with the controller, for real-time measurement of the intake air flow of each heat exchange zone.

[0075] Specifically, those skilled in the art will understand that the above-mentioned sensor is only a preferred embodiment, and other measuring devices that can achieve the same function can also be used, such as using a differential pressure flow meter to measure the air inlet flow, or using the built-in temperature sensor of the chiller or cold storage tank 11 to obtain the cold source outlet water temperature, etc. These modifications should all fall within the protection scope of this invention.

[0076] In this embodiment, the controller is communicatively connected to the environmental parameter acquisition unit, the spray evaporation cooling circuit, and the compression cold storage indirect cooling circuit, respectively, and is used to control the gas turbine intake cooling system to operate in cold storage mode, spray evaporation cooling mode, or compression cold storage indirect cooling mode according to the pre-acquired power generation plan and environmental data.

[0077] Specifically, the controller is electrically connected to the booster pump 6, solenoid valve group 7, chilled water pump 10, cold release pump 12, refrigeration unit 9, and first valve 131, second valve 132, third valve 133, fourth valve group 134, fifth valve 135, sixth valve 136, and seventh valve 137, respectively, and is used to output control commands to adjust the operating status of each actuator. The controller is embedded with a trained spray cooling feedforward model and a cold storage cooling feedforward model. The spray cooling feedforward model is used to calculate the optimal spray water distribution coefficient of each direction of the intake cooling unit based on the input environmental data, theoretical unit volume spray water volume, and equipment operating status of the gas turbine intake cooling system. The cold storage cooling feedforward model is used to output the optimal opening command of each electric regulating valve in the fourth valve group based on the input current cold source outlet water temperature, intake air flow rate of each heat exchange zone, target intake air temperature, and environmental data.

[0078] Specifically, the equipment operating status includes the start-stop status, open / closed status and operating parameters of the booster pump, solenoid valve group and spray cooler group, as well as the current operating mode of the gas turbine intake cooling system.

[0079] Specifically, in this embodiment, two units of each of the booster pump 6, chilled water pump 10, and cooling pump 12 are configured, and the two pumps of the same type are connected in parallel via pipelines. This parallel structure, with one in operation and one on standby, allows for seamless switching to the other unit in case of failure or maintenance of a single device, ensuring continuous and stable delivery of the cooling circuit medium and improving the overall system reliability.

[0080] Specifically, both the spray cooling feedforward model and the cold storage cooling feedforward model are built into the controller. They are both constructed using a lightweight BP backpropagation neural network. They are trained offline and optimized using data from multiple operating conditions in the field. After training, the weight parameters are embedded into the control program. The overall computation is small and the response speed is fast, which is suitable for the real-time computing needs of embedded controllers in industrial fields.

[0081] The spray cooling feedforward model uses temperature, humidity, atmospheric pressure, wind direction, wind speed data, and a preset theoretical water volume per unit volume as multi-dimensional input features. It combines the actual operating conditions of the equipment in the spray evaporative cooling loop to complete feature fitting. Relying on the nonlinear fitting capability of neural networks, it accurately infers the temperature difference in different directions (regions) and quickly solves the optimal water volume distribution coefficient corresponding to each layout direction of the air intake cooling unit. Based on this, it matches the working logic of the solenoid valve group 7 to achieve a balanced and reasonable distribution of spray water volume across the entire area, effectively mitigating the adverse effects of external meteorological fluctuations on the spray cooling effect.

[0082] The cold storage cooling feedforward model uses the actual outlet water temperature of the cold source, the real-time air flow rate of each heat exchange zone, the preset target air inlet temperature, and environmental data as input samples. Based on the trained neural network model, it establishes a precise mapping relationship between the cooling medium flow rate and the air inlet cooling effect. It can predict the trend of air inlet temperature change in advance, avoid the control deviation caused by traditional lag regulation, and stably output the optimal opening adjustment command corresponding to each electric regulating valve in the fourth valve group. By relying on the independent control method of zone flow, it balances the cooling capacity of different air duct areas, so that the gas turbine air inlet temperature after heat exchange and cooling can quickly meet the set target, and adapt to the stable operation requirements of the unit under different loads and operating conditions throughout the process.

[0083] In this embodiment, by rationally configuring the piping, valves, and valve group structure of the compression-storage indirect cooling loop, the intake heat exchanger group 3 is divided into multiple independent heat exchange zones. Cold source temperature sensors and zone flow sensors are configured, and spray cooling feedforward models and storage cooling feedforward models are embedded in the controller. This not only enables independent and precise control of the chilled water flow rate in each heat exchange zone, but also allows for real-time acquisition of operating parameters through sensors and advance prediction and control based on the feedforward model. This effectively overcomes the lag and large inertia drawbacks of traditional feedback control, significantly improves the accuracy of intake temperature control, compensates for the impact of uneven airflow distribution in the intake duct on the cooling effect, improves the uniformity of intake cooling, avoids problems such as local overcooling and insufficient cooling, ensures stable combustion conditions of the gas turbine, and extends the service life of the unit's core components.

[0084] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

[0085] Example 2

[0086] like Figure 4 As shown, this embodiment of the invention provides a gas turbine intake air cooling method that couples evaporative refrigeration and compression cold storage, applied to the controller in the gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage as described in Embodiment 1, comprising:

[0087] S1: Acquire real-time environmental data;

[0088] The environmental data includes: wind direction, wind speed, temperature, humidity, and atmospheric pressure data;

[0089] S2: Based on the pre-acquired functional relationship between the maximum power output of the gas turbine and the inlet air temperature, environmental data, and power generation plan, determine whether the gas turbine is in the maximum power output state;

[0090] S3: If it is determined that the gas turbine is not in the maximum power generation state, then it is further determined whether the cold storage tank 11 contains chilled water that meets the cooling requirements. If so, the gas turbine intake cooling system is put into a shutdown state; otherwise, the gas turbine intake cooling system is put into cold storage mode.

[0091] S4: If it is determined that the gas turbine is in the maximum power generation state, the inverse function of the above functional relationship is used to calculate the intake temperature required to achieve the target power generation, and this temperature is used as the target intake temperature.

[0092] S5: Determine whether the target intake air temperature is less than or equal to the average value of the evaporative cooling limit temperature in each direction calculated based on the environmental data. If so, the gas turbine intake air cooling system is set to spray evaporative cooling mode; otherwise, the intake air cooling system is set to compression storage indirect cooling mode.

[0093] In this embodiment, in step S2, the pre-obtained functional relationship between the maximum power output of the gas turbine and the inlet air temperature is provided by the gas turbine manufacturer. In this embodiment, the functional relationship is as follows: Figure 3 As shown.

[0094] In this embodiment, step S2, determining whether the gas turbine is in its maximum power generation output state, includes:

[0095] S21: Real-time acquisition of the opening degree of the gas turbine inlet adjustable guide vanes, the target power output given in the power generation plan, and the actual power output;

[0096] S22: Based on the environmental data, the theoretical maximum power output of the gas turbine under the current environmental conditions is calculated using the functional relationship between the maximum power output of the gas turbine and the intake air temperature.

[0097] Specifically, the theoretical maximum power output of a gas turbine is calculated using a functional relationship provided by the gas turbine manufacturer. This calculation method is a technical means commonly used by those skilled in the art and will not be described in detail here.

[0098] S23: When the target power generation output is not less than the theoretical maximum power generation output, and the opening degree of the inlet adjustable guide vane reaches the preset maximum opening degree threshold, and the absolute value of the deviation between the actual power generation output and the theoretical maximum power generation output is less than the preset output deviation threshold, it is determined that the gas turbine is in the maximum power generation output state.

[0099] Specifically, in this embodiment, the preset maximum opening threshold is provided by the gas turbine manufacturer, and the preset output deviation threshold is 1%.

[0100] Specifically, this embodiment refines the judgment conditions for the maximum power output state of the gas turbine, and combines the comprehensive judgment of the inlet adjustable guide vane opening, target power output, actual power output and theoretical maximum power output to ensure the accuracy of the judgment of the maximum power output state of the unit. This avoids the cooling system from being falsely started or not started due to judgment deviation, ensuring that the unit can obtain stable intake cooling when needed, further reducing ineffective energy consumption, and improving the accuracy and reliability of system operation.

[0101] In this embodiment, step S3, determining whether the cold storage tank 11 contains chilled water sufficient to meet cooling requirements, includes:

[0102] The internal medium liquid (chilled water) level of the cold storage tank 11 is collected. If the internal medium liquid (chilled water) level meets the cooling capacity threshold, then there is enough chilled water to meet the cooling requirements; otherwise, there is not enough chilled water to meet the cooling requirements.

[0103] In this embodiment, step S3, which involves operating the gas turbine intake cooling system in cold storage mode, includes:

[0104] Close all valves and booster pump 6 in the spray evaporation cooling circuit;

[0105] Close the first valve 131, the fourth valve group 134, and the cold release pump 12 in the compression cold storage indirect cooling circuit;

[0106] Start the refrigeration unit 9 and the chilled water pump 10;

[0107] Open the second valve 132, the third valve 133, the fifth valve 135, the sixth valve 136, and the seventh valve 137;

[0108] The chilled water produced by the refrigeration unit 9 is successively sent to the bottom of the cold storage tank 11 through the cold water pump 10, the third valve 133, the seventh valve 137, and the sixth valve 136 for storage. The chilled water at the top of the cold storage tank 11 is then successively sent to the return water port of the refrigeration unit 9 through the fifth valve 135 and the second valve 132.

[0109] Specifically, this embodiment achieves efficient storage of cold energy by clearly defining the valve opening and closing, equipment start-up and shutdown logic, and chilled water circulation path in the cold storage mode. The chilled water produced by the refrigeration unit 9 can be orderly sent into the cold storage tank 11 for storage. Furthermore, through precise pipeline control, the connection with the heat exchange zone is cut off to avoid cold energy loss, ensuring a stable and efficient cold storage process. This provides reliable cold source support for subsequent peak-hour cold release and cooling, further leveraging the economic advantages of off-peak electricity cold storage and reducing the energy consumption and electricity costs of the cooling system.

[0110] In this embodiment, step S4: calculate the intake temperature required to achieve the target power generation output using the inverse function of the aforementioned functional relationship, and use it as the target intake temperature. The calculation of the intake temperature required to achieve the target power generation output is a technical method commonly used by those skilled in the art, and will not be described in detail here.

[0111] In this embodiment, the average value of the evaporative cooling limit temperature in each direction calculated based on the environmental data in step S5 includes:

[0112] Acquire current environmental data; current environmental data includes the ambient temperature T measured using a temperature sensor. db The ambient relative humidity X is measured using a humidity sensor. rh ;

[0113] Based on current environmental data, calculate the saturated water vapor pressure e under the current operating conditions. s The formula is expressed as follows: (This is related to the actual water vapor pressure e.)

[0114] e s =0.611exp(T db (18.678-T db / 234.5) / (T db +257.14));

[0115] e=e s ×X rh / 100;

[0116] Where exp represents an exponential function with the natural constant as the base, and lg represents a common logarithmic function with the base 10.

[0117] The average value T of the evaporative cooling limit temperature in all directions was calculated using the adiabatic saturation relation. wb,avg The formula is expressed as follows:

[0118] T wb,avg =1.05×(237.3lg(e / 0.61078)) / (7.5-lg(e / 0.61078)).

[0119] In this embodiment, step S5, which involves operating the gas turbine intake cooling system in spray evaporative cooling mode, includes:

[0120] Start booster pump 6 and close all valves, chilled water pump, cold release pump and refrigeration unit of the compression cold storage indirect cooling circuit;

[0121] The initial moisture content of the air is calculated based on temperature, atmospheric pressure and humidity data, and the evaporative cooling limit temperature is iteratively calculated based on the initial moisture content of the air, and the theoretical water spray volume per unit volume is calculated based on the evaporative cooling limit temperature.

[0122] The theoretical unit volume water spray volume, wind direction and wind speed data, as well as the equipment operating status of the gas turbine intake cooling system, are input into the spray cooling feedforward model to obtain the optimal water spray volume distribution coefficients for each direction of the intake cooling unit.

[0123] Calculate the actual required water spray volume in each direction of the intake cooling unit based on the optimal water spray volume distribution coefficient;

[0124] Match the single-valve flow characteristics of the solenoid valve group 7 according to the actual required water spray volume in each direction, and output the optimal switching combination and timing control of each solenoid valve so that the intake temperature of the intake cooling unit in each direction after cooling approaches the evaporative cooling limit temperature.

[0125] Specifically, this embodiment clarifies the specific operation process of the spray evaporative cooling mode, calculates the evaporative cooling limit temperature and theoretical unit volume water spray volume based on environmental parameters, and achieves the optimal allocation of water spray volume in each direction by relying on the spray cooling feedforward model. It matches the flow characteristic output switch combination and control timing of the solenoid valve group 7, which not only fully leverages the advantages of simple structure and low operating cost of spray evaporative cooling, but also adapts to differences in wind direction and wind speed, achieves precise spraying in multiple directions, further improves the uniformity and cooling effect of spray cooling, and meets the low-cost cooling needs under suitable low humidity conditions.

[0126] In this embodiment, step S5, which involves operating the intake cooling system in a compression-storage indirect cooling mode, includes:

[0127] Close all valves and booster pump 6 in the spray evaporation cooling circuit;

[0128] Determine whether the cold storage tank 11 contains enough chilled water to meet the cooling requirements;

[0129] If so, construct a cold storage and release loop; otherwise, construct a direct cooling loop.

[0130] The current cold source outlet water temperature, the air flow rate of each heat exchange zone of the gas turbine, and the target air inlet temperature are obtained in real time. The current cold source outlet water temperature is the outlet water temperature of the cold source in the current operating loop.

[0131] Input the current cold source outlet water temperature, the air flow rate of each heat exchange zone, the target air inlet temperature, and environmental data into the cold storage cooling feedforward model to obtain the optimal opening command for each electric regulating valve in the fourth valve group.

[0132] According to the optimal opening command, the opening degree of each electric regulating valve in the fourth valve group is dynamically adjusted to match the chilled water flow rate of each heat exchange zone with the air intake flow rate of the corresponding zone, to compensate for the influence of uneven airflow distribution in the intake duct on the cooling effect, so that the intake air temperature of each zone after cooling can stably reach the target intake air temperature.

[0133] The construction of the cold storage and release circulation loop includes: starting the cold release pump 12; opening the first valve 131, the fourth valve group 134, the fifth valve 135 and the seventh valve 137; closing the second valve 132, the third valve 133 and the sixth valve 136; the chilled water at the bottom of the cold storage tank 11 is sequentially transferred to the inlet of the air intake heat exchanger group 3 through the cold release pump 12, the seventh valve 137 and the fourth valve group 134 for cooling, and the return water after cooling enters the return water port of the refrigeration unit 9 from the outlet of the air intake heat exchanger group 3 through the first valve 131 and the second valve 132.

[0134] The direct cooling cycle includes: starting the refrigeration unit 9 and the chilled water pump 10, opening the first valve 131, the second valve 132, the third valve 133 and the fourth valve group 134, and closing the fifth valve 135, the sixth valve 136, the seventh valve 137 and the cold release pump 12; the chilled water produced by the refrigeration unit 9 is successively sent to the inlet of the air intake heat exchanger group 3 through the chilled water pump 10, the third valve 133 and the fourth valve group for cooling, and the return water after cooling enters the return water port of the refrigeration unit 9 from the outlet of the air intake heat exchanger group 3 through the first valve 131 and the second valve 132 in sequence.

[0135] Specifically, this embodiment clarifies the construction logic, valve actions, and chilled water circulation path of the cold storage and release loop and the direct cooling loop under the compression cold storage indirect cooling mode, thereby achieving flexible switching of the cold source. When the cold storage tank 11 has sufficient cold capacity, the cold storage and release loop is used first to make full use of the stored cold capacity and reduce operating costs. When the cold storage is insufficient, the direct cooling loop of the refrigeration unit 9 is started to ensure that the deep cooling demand is met. At the same time, the opening of the electric regulating valve of each heat exchange zone is controlled by the cold storage cooling feedforward model to achieve precise matching of chilled water flow and air intake flow, further improving cooling uniformity and control accuracy, avoiding equipment failure caused by mixing different cooling modes, and ensuring safe and reliable system operation.

[0136] Example 3

[0137] This embodiment provides a computer-readable storage medium storing a computer program that, when executed, implements the gas turbine intake air cooling method of coupled evaporative refrigeration and compression cold storage as described in Embodiment 2.

[0138] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0139] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0140] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0141] The embodiments of the present invention have been described above with reference to the accompanying drawings. However, the present invention is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of the present invention without departing from the spirit and scope of the claims. All of these forms are within the protection scope of the present invention.

Claims

1. A gas turbine intake air cooling system that couples evaporative refrigeration and compression cold storage, characterized in that, include: The intake cooling unit includes a honeycomb water separator, an intake heat exchanger group, and a filter module arranged sequentially along the gas turbine intake direction; A spray evaporative cooling circuit, fluidly connected to the honeycomb water separator, is used to spray atomized cooling water onto the honeycomb water separator. The spray evaporative cooling circuit includes a buffer water tank, a booster pump, a solenoid valve group, and a spray cooler group connected in sequence. The outlet of the buffer water tank is connected to the input end of the solenoid valve group through the booster pump. The multiple output ends of the solenoid valve group are respectively connected to each spray cooler in the spray cooler group. The spray cooler group includes multiple spray coolers arranged in sections along different directions of the air intake cooling unit, and the spray cooler group is arranged upstream of the honeycomb water separator along the air intake direction. A compressed cold storage indirect cooling circuit is fluidly connected to the intake air heat exchanger group and is used to supply chilled water to the intake air heat exchanger group; Environmental parameter acquisition unit, used to collect environmental data in real time; The controller is communicatively connected to the environmental parameter acquisition unit, the spray evaporation cooling circuit, and the compression storage indirect cooling circuit, and is used to control the gas turbine intake cooling system to operate in storage mode, spray evaporation cooling mode, or compression storage indirect cooling mode according to the pre-acquired power generation plan and environmental data.

2. The gas turbine intake air cooling system with coupled evaporative refrigeration and compression cold storage as described in claim 1, characterized in that, The compression cold storage indirect cooling circuit includes a refrigeration unit, a cold water pump, a cold storage tank, a cold release pump, and a first valve, a second valve, a third valve, a fourth valve group, a fifth valve, a sixth valve, and a seventh valve. The fourth valve group includes multiple electrically adjustable valves, each of which corresponds to a heat exchange zone of the air intake heat exchanger group. Its inlet is connected in parallel to the cold source water supply main pipe, and its outlet is connected to the water inlet of the corresponding heat exchange zone. The outlet of the refrigeration unit is connected to the first side of the third valve via a cold water pump. The outlet of the third valve is connected to the main cold water supply pipe of the fourth valve group and the first side of the seventh valve. The second side of the seventh valve is connected to the first side of the sixth valve and the first side of the cold release pump. The second side of the sixth valve and the second side of the cold release pump are both connected to the cold storage tank. The return water inlet of the refrigeration unit is connected to the first side of the second valve, and the second side of the second valve is connected to the first side of the first valve and the first side of the fifth valve respectively; the second side of the first valve is connected to the outlet of each heat exchange zone of the air inlet heat exchanger group; the second side of the fifth valve is connected to the cold storage tank.

3. The gas turbine intake air cooling system with coupled evaporative refrigeration and compression cold storage according to claim 2, characterized in that, Also includes: A cold source temperature sensor is installed on the cold source water supply main pipe of the fourth valve group and is connected in communication with the controller to measure the current cold source outlet water temperature in real time. Multiple zone flow sensors are installed on the air inlet side of each heat exchange zone of the air inlet heat exchanger group and are connected in communication with the controller to measure the air inlet flow of each heat exchange zone in real time.

4. The gas turbine intake air cooling system with coupled evaporative refrigeration and compression cold storage according to claim 3, characterized in that, The controller is electrically connected to the booster pump, solenoid valve group, chilled water pump, cold release pump, refrigeration unit, and the first, second, third, fourth valve group, fifth, sixth, and seventh valves, respectively, and is used to output control commands to adjust the operating status of each actuator. The controller is embedded with a trained spray cooling feedforward model and a cold storage cooling feedforward model. The spray cooling feedforward model is used to calculate the optimal spray water distribution coefficient of each direction of the intake cooling unit based on the input environmental data, theoretical unit volume spray water volume, and equipment operating status of the gas turbine intake cooling system. The cold storage cooling feedforward model is used to output the optimal opening command of each electric regulating valve in the fourth valve group based on the input current cold source outlet water temperature, intake air flow rate of each heat exchange zone, target intake air temperature, and environmental data.

5. A gas turbine intake air cooling method coupling evaporative refrigeration and compression cold storage, applied to a controller in the gas turbine intake air cooling system coupling evaporative refrigeration and compression cold storage as described in any one of claims 1-4, characterized in that, include: Acquire real-time environmental data; the environmental data includes: wind direction, wind speed, temperature, humidity, and atmospheric pressure data; Based on the pre-acquired functional relationship between the maximum power output of the gas turbine and the inlet air temperature, environmental data, and power generation plan, it is determined whether the gas turbine is in the maximum power output state; If it is determined that the gas turbine is not at its maximum power output, then it is further determined whether the cold storage tank contains chilled water to meet the cooling requirements. If so, the gas turbine intake cooling system is shut down; otherwise, the gas turbine intake cooling system is put into cold storage mode. If it is determined that the gas turbine is in the maximum power generation state, the inverse function of the above functional relationship is used to calculate the inlet temperature required to achieve the target power generation, and this temperature is used as the target inlet temperature. Determine whether the target intake air temperature is less than or equal to the average value of the evaporative cooling limit temperature in each direction calculated based on the environmental data. If so, the gas turbine intake air cooling system is operated in spray evaporative cooling mode; otherwise, the intake air cooling system is operated in compression storage indirect cooling mode.

6. The gas turbine intake air cooling method coupled with evaporative refrigeration and compression storage according to claim 5, characterized in that, The determination of whether the gas turbine is in maximum power generation output state includes: Real-time acquisition of the opening degree of the gas turbine inlet adjustable guide vanes, the target power output given in the power generation plan, and the actual power output; Based on the environmental data, the theoretical maximum power output of the gas turbine under the current environmental conditions is calculated using the functional relationship between the maximum power output of the gas turbine and the inlet air temperature. When the target power generation output is not less than the theoretical maximum power generation output, and the opening degree of the inlet adjustable guide vane reaches the preset maximum opening degree threshold, and the absolute value of the deviation between the actual power generation output and the theoretical maximum power generation output is less than the preset output deviation threshold, the gas turbine is judged to be in the maximum power generation output state.

7. The gas turbine intake air cooling method coupled with evaporative refrigeration and compression storage as described in claim 6, characterized in that, The method of operating the gas turbine intake air cooling system in cold storage mode includes: Close all valves and booster pumps in the spray evaporation cooling circuit; Close the first valve, the fourth valve group, and the cold release pump in the compression cold storage indirect cooling circuit; Start the refrigeration unit and chilled water pump; Open the second, third, fifth, sixth, and seventh valves; The chilled water produced by the refrigeration unit is successively sent to the bottom of the cold storage tank through the cold water pump, the third valve, the seventh valve, and the sixth valve for storage. The chilled water at the top of the cold storage tank is then successively sent to the return water port of the refrigeration unit through the fifth valve and the second valve.

8. The gas turbine intake air cooling method coupled with evaporative refrigeration and compression storage according to claim 7, characterized in that, The method of operating the gas turbine intake air cooling system in spray evaporative cooling mode includes: Start the booster pump and close all valves, chilled water pump, cold release pump and refrigeration unit of the compression cold storage indirect cooling circuit; The initial moisture content of the air is calculated based on temperature, atmospheric pressure and humidity data, and the evaporative cooling limit temperature is iteratively calculated based on the initial moisture content of the air, and the theoretical water spray volume per unit volume is calculated based on the evaporative cooling limit temperature. The theoretical unit volume water spray volume, wind direction and wind speed data, as well as the equipment operating status of the gas turbine intake cooling system, are input into the spray cooling feedforward model to obtain the optimal water spray volume distribution coefficients for each direction of the intake cooling unit. Calculate the actual required water spray volume in each direction of the intake cooling unit based on the optimal water spray volume distribution coefficient; Based on the actual required water spray volume in each direction, the single valve flow characteristics of the solenoid valve group are matched, and the optimal switching combination and timing control of each solenoid valve are output so that the intake temperature of the intake cooling unit in each direction after cooling approaches the evaporative cooling limit temperature.

9. The gas turbine intake air cooling method coupled with evaporative refrigeration and compression storage according to claim 8, characterized in that, The method of operating the intake air cooling system in compression storage indirect cooling mode includes: Close all valves and booster pumps in the spray evaporation cooling circuit; Determine whether the cold storage tank contains enough chilled water to meet the cooling requirements; If so, construct a cold storage and release loop; otherwise, construct a direct cooling loop. The current cold source outlet water temperature, the air flow rate of each heat exchange zone of the gas turbine, and the target air inlet temperature are obtained in real time. The current cold source outlet water temperature is the outlet water temperature of the cold source in the current operating loop. Input the current cold source outlet water temperature, the air flow rate of each heat exchange zone, the target air inlet temperature, and environmental data into the cold storage cooling feedforward model to obtain the optimal opening command for each electric regulating valve in the fourth valve group. According to the optimal opening command, the opening degree of each electric regulating valve in the fourth valve group is dynamically adjusted to match the chilled water flow rate of each heat exchange zone with the air intake flow rate of the corresponding zone, to compensate for the influence of uneven airflow distribution in the intake duct on the cooling effect, so that the intake air temperature of each zone after cooling can stably reach the target intake air temperature.

10. The gas turbine intake air cooling method coupled with evaporative refrigeration and compression storage according to claim 9, characterized in that, The construction of the cold storage and release circulation loop includes: starting the cold release pump; opening the first valve, the fourth valve group, the fifth valve, and the seventh valve; closing the second valve, the third valve, and the sixth valve; the chilled water at the bottom of the cold storage tank is sequentially transferred to the inlet of the air intake heat exchanger group for cooling through the cold release pump, the seventh valve, and the fourth valve group; the returned water after cooling enters the return water port of the refrigeration unit from the outlet of the air intake heat exchanger group through the first valve and the second valve. The direct cooling cycle includes: starting the refrigeration unit and the chilled water pump, opening the first valve, the second valve, the third valve and the fourth valve group, and closing the fifth valve, the sixth valve, the seventh valve and the release pump; the chilled water produced by the refrigeration unit is successively sent to the inlet of the air intake heat exchanger group for cooling through the chilled water pump, the third valve and the fourth valve group, and the return water after cooling enters the return water port of the refrigeration unit from the outlet of the air intake heat exchanger group through the first valve and the second valve in sequence.

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