Intelligent air volume control method of composite flow closed cooling tower and cooling tower thereof

Abstract

The application discloses an intelligent air volume control method of a composite flow closed cooling tower and the cooling tower, relates to the technical field of energy-saving refrigeration and air conditioning equipment, and the composite flow closed cooling tower comprises heat exchange coils and an air inlet bin arranged on the windward side of the heat exchange coils. The air inlet bin is divided into a plurality of independent air inlet channels which are not communicated with each other. Each independent air inlet channel is provided with an air volume adjusting component and an air speed detecting component. The method comprises the following steps: constructing a digital mapping model of a three-dimensional flow field inside the composite flow closed cooling tower and heat exchange load based on operating parameters; identifying an abnormal flow field area; determining corresponding weak air inlet channels in combination with air speed data; calculating and implementing directional air volume compensation; and simultaneously, feeding forward adjusting each channel according to the air volume demand predicted according to the heat exchange load change trend. The application optimizes the heat exchange efficiency of the composite flow closed cooling tower.

Description

Technical Field

[0001] This application relates to the field of energy-saving refrigeration and air conditioning equipment technology, and in particular to an intelligent airflow control method for a composite flow closed-loop cooling tower and the cooling tower thereof. Background Technology

[0002] Cooling towers are core heat dissipation equipment in industrial waste heat and refrigeration systems. Among them, the heat exchange coils of the composite flow closed-loop cooling tower form a closed independent circulation loop, isolating the medium to be cooled from the atmosphere throughout the process. The sprayed water only evaporates and dissipates heat on the outer surface of the coil, which has the advantages of clean medium, low water drift, and water saving. It is widely used in scenarios such as precision equipment cooling, clean production, and continuous operation in extremely cold regions.

[0003] The heat exchange efficiency of a compound flow closed-circuit cooling tower largely depends on the uniformity of airflow distribution on the windward side of the heat exchange coil. In actual operation, due to the influence of tower structure, spray disturbance, and air intake conditions, local abnormal flow fields such as vortex zones, airflow short-circuit zones, and weak wind zones are easily formed on the windward side of the coil. This causes differences in windward wind speed in different sections of the coil, resulting in local overheating or undercooling of the coil and a decrease in overall heat exchange efficiency.

[0004] However, existing closed-loop cooling towers typically rely on fixed-speed fans or simple frequency conversion feedback control based on outlet water temperature for airflow regulation. This approach uses a single temperature parameter to uniformly adjust the airflow across the entire tower, failing to identify the location and intensity of localized abnormal flow fields in different sections of the coil, and also lacking the ability to provide zoned compensation for the airflow demands of different sections. Therefore, existing airflow regulation methods struggle to eliminate localized flow field inhomogeneities on the windward side of the coil, preventing the surface airflow velocity from becoming uniform and hindering further improvements in the heat exchange efficiency of closed-loop cooling towers. Summary of the Invention

[0005] In order to overcome the shortcomings of the existing technology, optimize the air volume regulation method of the composite flow closed cooling tower, and further optimize the heat exchange efficiency of the composite flow closed cooling tower, this application provides an intelligent air volume control method for the composite flow closed cooling tower and the cooling tower thereof.

[0006] Firstly, the objective of this invention is achieved through the following technical solution: A method for intelligent airflow control in a compound flow closed-loop cooling tower, the compound flow closed-loop cooling tower including heat exchange coils and an air inlet chamber disposed on the windward side of the heat exchange coils, the air inlet chamber being divided into several independent air inlet channels that are not interconnected, each independent air inlet channel being equipped with an airflow regulating component and an air velocity detection component, the method comprising: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat transfer load inside the composite flow closed cooling tower is calculated. Based on the digital mapping model, the abnormal flow field region inside the composite flow closed cooling tower is determined; Based on the wind speed data collected by the wind speed detection component, the weak wind inlet channel corresponding to the abnormal flow field region is determined among the several independent inlet channels. Based on the weak wind inlet channel, the target compensation amount of the weak wind inlet channel is calculated, and the air volume adjustment component of the weak wind inlet channel is adjusted according to the target compensation amount to obtain directional air volume compensation for the weak wind inlet channel. Based on the changing trend of the heat exchange load, the predicted air volume demand is calculated, and the several independent air inlet channels are adjusted in advance according to the predicted air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

[0007] By adopting the above technical solution, this application sets up an air inlet chamber on the windward side of the heat exchange coil, which is divided into several independent air inlet channels that are not interconnected. This is combined with a digital mapping model, airflow regulation components, and wind speed detection components, along with directional airflow compensation and feedforward regulation. Specifically, by constructing a three-dimensional flow field and heat exchange load digital mapping model based on operating parameters, and determining abnormal flow field regions within the tower accordingly, the airflow regulation is transformed from a passive feedback mechanism relying on a single outlet water temperature to an active identification based on the actual flow field within the tower. This solves the problem that existing control methods cannot detect local flow field unevenness. By dividing the air inlet chamber into independent, non-interconnected air inlet channels, and determining the weak-wind air inlet channel corresponding to the abnormal flow field area based on wind speed data, and performing directional airflow compensation on it, the airflow in each independent air inlet channel does not interfere with each other. This achieves precise and independent airflow compensation for the local weak-wind section of the coil, avoiding the defect of the whole tower uniform adjustment that cannot take into account the differences between each section. At the same time, the predicted value of airflow demand is calculated based on the heat exchange load change trend and feedforward adjustment is performed, so that the airflow output leads the load change, overcoming the problem of temperature feedback adjustment lag, and further making the surface wind speed of the heat exchange coil tend to be uniform. This application eliminates the local flow field non-uniformity on the windward side of the coil as a whole, making the surface wind speed of the heat exchange coil uniform, and significantly improving the heat exchange efficiency of the composite flow closed cooling tower.

[0008] In a preferred embodiment of this application: the composite flow closed-circuit cooling tower is one of several towers in a multi-tower parallel system, the multi-tower parallel system comprising several towers, each tower being equipped with a fan and an air inlet valve; the method further includes: Based on the wind pressure distribution on the air inlet side of each of the towers, the system-level wind pressure balance model of the multi-tower parallel system is calculated. Based on the system-level wind pressure balance model, the coordinated adjustment amount of the fan speed and air inlet valve opening of each of the towers is determined, and the towers are coordinated and adjusted according to the coordinated adjustment amount to obtain the heat dissipation distribution of the towers with equal load and equal air volume.

[0009] By adopting the above technical solution, a system-level wind pressure balance model is constructed based on the wind pressure distribution on the air inlet side of each tower. Based on this model, the coordinated adjustment amount of the fan speed and air inlet valve opening of each tower is determined, so that the air volume adjustment is upgraded from independent adjustment of a single tower to coordinated adjustment of multiple towers. This avoids air volume competition between towers and backflow of airflow, and realizes heat dissipation distribution with equal load and equal air volume for several towers. From the system level, the overall heat dissipation balance and operational stability of the multi-tower parallel system are improved.

[0010] In a preferred embodiment of this application: the airflow regulating component includes a servo-driven electric louvered damper and an independent makeup air fan; the wind speed detection component includes a pressure stabilizing chamber and a wind speed sensing assembly located at the end of the independent air inlet channel; the method further includes: Based on the coupling relationship between air volume, spray water flow rate, and heat exchange load, the optimal air volume ratio with minimum energy consumption is calculated, and the several independent air inlet channels are controlled according to the optimal air volume ratio, including: The spray water flow rate and heat exchange load of each of the several independent air inlet channels are obtained, and the energy consumption coefficient of each independent air inlet channel under unit heat exchange is determined based on the coupling relationship. Based on the energy consumption coefficient, with the goal of minimizing the total energy consumption of the several independent air intake channels, the optimal air volume ratio among the several independent air intake channels is calculated; Based on the optimal air volume ratio, the opening degree of the servo-driven electric louver damper and the rotation speed of the independent make-up air fan are controlled.

[0011] By adopting the above technical solution, directional air volume compensation has a precise and controllable actuator and stable and accurate wind speed acquisition conditions. At the same time, by establishing the coupling relationship between air volume, spray water flow rate and heat exchange load, the energy consumption coefficient under unit heat exchange is determined and the optimal air volume ratio is solved with the goal of minimizing total energy consumption. This enables air volume regulation to further achieve optimal energy consumption while ensuring heat exchange, overcoming the shortcomings of existing control systems that only focus on heat exchange and do not consider energy consumption.

[0012] In a preferred embodiment of this application: determining the abnormal flow field region inside the composite flow closed-loop cooling tower based on the digital mapping model includes: Based on the digital mapping model, the heat exchange coil region where the heat exchange coil is located is obtained, and the heat exchange coil region is divided to obtain the first heat dissipation coil region and the second heat dissipation coil region. Based on the first heat dissipation coil area and the second heat dissipation coil area, obtain the heat dissipation influencing factors related to airflow distribution; Based on the aforementioned heat dissipation influencing factors, obtain the air volume demand influencing factor, which represents the degree of air volume demand. Based on the air volume demand influencing factor, the first heat dissipation coil area and the second heat dissipation coil area are divided to obtain the division result, and the abnormal flow field area is determined based on the division result.

[0013] By adopting the above technical solution, the influencing factors and progressive process of abnormal flow field areas were determined and refined. This makes the identification of abnormal flow field areas no longer rely on a single, general judgment of the entire tower, but rather on the quantitative differentiation of heat dissipation differences in different sections of the coil, thereby more accurately locating the weak wind sections that need compensation.

[0014] In a preferred embodiment of this application: the heat exchange coil region is a wet heat exchange region; the first heat exchange coil region is a stable heat exchange region with stable spray distribution within the wet heat exchange region; and the second heat exchange coil region is a disturbed heat exchange region within the wet heat exchange region adjacent to the airflow short-circuit region and where the spray is disturbed. The step of dividing the heat exchange coil region to obtain the first heat exchange coil region and the second heat exchange coil region specifically includes: Based on the spray distribution in the heat exchange coil area, the stable spray region and the spray disturbance region are obtained; Based on the spray stability region and the spray disturbance region, the airflow short-circuit region is obtained; Based on the airflow short-circuit region and the heat exchange coil region, the first heat dissipation coil region and the second heat dissipation coil region are obtained.

[0015] By adopting the above technical solution, and considering that the entire composite flow closed cooling tower is mainly wet heat exchanged and that different coil sections are not affected by the spray disturbance, the coil area is clearly divided into a stable heat exchange zone with stable spray distribution and a disturbed heat exchange zone with adjacent airflow short-circuit zone and spray disturbance. The stable / disturbed spray zone is first identified by spray distribution, and then the airflow short-circuit zone is obtained accordingly, finally resulting in two types of coil areas. This helps to improve the accuracy of the identification results of abnormal flow field areas.

[0016] In a preferred embodiment of this application, the step of calculating the target compensation amount for the weak wind inlet channel based on the weak wind inlet channel includes: Based on the division results, heat dissipation demand information is obtained, and based on the heat dissipation demand information, overall heat dissipation numerical information is obtained. The heat dissipation demand information includes the target outlet water temperature and heat dissipation duration, and the overall heat dissipation numerical information includes pre-cooling air volume, pre-cooling duration, steady-state air volume, and steady-state heat dissipation duration. Obtain the compensation distance, and based on the compensation distance and the overall heat dissipation value information, obtain the air supply parameters. The compensation distance refers to the distance between the heat dissipation coil area and the several independent air inlet channels. The air supply parameters include the zoned air supply pre-cooling air volume and the zoned air supply steady-state air volume of each independent air inlet channel. Based on the air supply parameters, the target compensation amount of the weak wind intake channel is determined.

[0017] By adopting the above technical solution, numerical values ​​such as pre-cooling air volume, pre-cooling duration, steady-state air volume, and steady-state heat dissipation duration are introduced to quantify the heat dissipation process in stages. Furthermore, the spatial relationship between the coil area and each independent air intake channel is incorporated into the calculation through compensation distance. This ensures that the target compensation amount for each independent air intake channel matches both the time process and spatial location of the heat dissipation demand, improving the accuracy of directional air volume compensation.

[0018] In a preferred embodiment of this application, obtaining the overall heat dissipation value information based on the heat dissipation requirement information specifically includes: The target outlet water temperature is extracted from the heat dissipation demand information, and the air volume corresponding to the target outlet water temperature is taken as the steady-state air volume. Based on the heat dissipation duration and the target outlet water temperature, the pre-cooling duration, the steady-state heat dissipation duration, and the pre-cooling air volume are obtained; the pre-cooling air volume includes the pre-cooling boost air volume and the pre-cooling drop air volume, and the pre-cooling duration includes the pre-cooling boost duration and the pre-cooling drop duration. By associating the steady-state airflow, the pre-cooling duration, the steady-state heat dissipation duration, and the pre-cooling airflow, the overall heat dissipation numerical information is obtained; And / or, The air volume demand influencing factors include a first air volume demand influencing factor and a second air volume demand influencing factor; the zoned air supply pre-cooling air volume includes zoned boost air supply pre-cooling air volume and zoned fall-down air supply pre-cooling air volume; obtaining the air supply parameters based on the compensation distance and the overall heat dissipation value information specifically includes: Based on the first air volume demand influence factor, the second air volume demand influence factor, the pre-cooling air volume, and the compensation distance, obtain the pre-cooling air volume of the zone's boost air supply and the pre-cooling air volume of the zone's fallback air supply. The steady-state air volume of the zoned air supply is obtained based on the first air volume demand influence factor, the second air volume demand influence factor, the steady-state air volume, and the compensation distance.

[0019] By adopting the above technical solution, the determination of air supply parameters is further refined in two aspects: First, the pre-cooling stage is subdivided into pre-cooling boost and pre-cooling fall, and the pre-cooling boost / fall air volume and duration are distinguished accordingly. This allows the overall heat dissipation numerical information to depict the dynamic changes in air volume during the heat dissipation process, avoiding overshoot and fluctuations caused by sudden changes in air volume. Second, the air volume demand influencing factors are divided into first and second air volume demand influencing factors. Combined with the compensation distance, the pre-cooling air volume of the zoned boost air supply, the pre-cooling air volume of the zoned fall air supply, and the steady-state air volume of the zoned air supply are calculated for each independent air intake channel. This allows the differentiated air volume demand of different coil sections and the spatial compensation distance to jointly determine the actual air volume of each channel. This achieves stable air volume compensation in the time dimension and accurate air volume compensation in the spatial dimension for each independent air intake channel.

[0020] Secondly, the objective of this invention is achieved through the following technical solution: A composite flow closed-loop cooling tower includes a heat exchange coil, an air inlet chamber disposed on the windward side of the heat exchange coil, and a controller. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is equipped with an air volume regulating component and an air speed detection component. The controller is configured to perform the following operations: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat exchange load inside the composite flow closed cooling tower is calculated. Based on the digital mapping model, the abnormal flow field region inside the composite flow closed cooling tower is determined; Based on the wind speed data collected by the wind speed detection component, the weak wind inlet channel corresponding to the abnormal flow field region is determined among the several independent inlet channels. Based on the weak wind inlet channel, the target compensation amount of the weak wind inlet channel is calculated, and the air volume adjustment component of the weak wind inlet channel is adjusted according to the target compensation amount to obtain directional air volume compensation for the weak wind inlet channel. Based on the changing trend of the heat exchange load, the predicted air volume demand is calculated, and the several independent air inlet channels are adjusted in advance according to the predicted air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

[0021] Thirdly, the objective of this invention is achieved through the following technical solution: A computer device includes a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the steps of the intelligent airflow control method for a composite flow closed-loop cooling tower described above.

[0022] Fourthly, the objective of this invention is achieved through the following technical solution: A computer-readable storage medium storing a computer program that, when executed by a processor, implements the steps of the intelligent airflow control method for a composite flow closed-loop cooling tower described above.

[0023] In summary, this application includes at least one of the following beneficial technical effects: 1. An air inlet chamber, divided into several independent air inlet channels with no communication, is set up on the windward side of the heat exchange coil. A three-dimensional digital mapping model of the flow field and heat exchange load is constructed by the controller. This application transforms the airflow regulation from passive feedback relying on a single outlet water temperature to active identification based on the actual flow field inside the tower, solving the problem that existing control methods cannot detect local flow field unevenness inside the tower. By identifying the weak wind inlet channel corresponding to the abnormal flow field area and performing directional airflow compensation on it, and ensuring that the airflow in each independent inlet channel does not interfere with each other, accurate and independent airflow compensation for local weak wind sections of the coil is achieved. By using feedforward regulation based on the heat exchange load change trend, the airflow output leads the load change, overcoming the lag of temperature feedback regulation. This eliminates the local flow field unevenness on the windward side of the coil, making the air velocity on the surface of the heat exchange coil uniform and significantly improving the heat exchange efficiency of the composite flow closed cooling tower. 2. To address the issues of mutual wind pressure interference and air volume competition among towers in a multi-tower parallel system, a system-level wind pressure balance model is constructed based on the wind pressure distribution on the air inlet side of each tower. Based on this model, the coordinated adjustment amount of the fan speed and air inlet valve opening of each tower is determined, thereby transforming air volume regulation from independent regulation of a single tower to coordinated regulation of multiple towers, thus avoiding air volume competition and backflow between towers. Attached Figure Description

[0024] Figure 1 This is a flowchart of an intelligent airflow control method for a composite flow closed-loop cooling tower according to an embodiment of this application; Figure 2 This is an embodiment of the overall structure of a composite flow closed-loop cooling tower. Figure 1 ; Figure 3 This is an embodiment of the overall structure of a composite flow closed-loop cooling tower. Figure 2 (Remove part of the outer shell); Figure 4 This is a schematic diagram of a device according to one embodiment of this application. Detailed Implementation

[0025] The present application will be further described in detail below with reference to the accompanying drawings.

[0026] In one embodiment, such as Figure 1As shown, this application discloses an intelligent airflow control method for a composite flow closed-loop cooling tower. The composite flow closed-loop cooling tower includes a heat exchange coil and an air inlet chamber disposed on the windward side of the heat exchange coil. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is equipped with an airflow adjustment component and an air speed detection component.

[0027] A compound flow closed-loop cooling tower refers to a closed-loop cooling tower that simultaneously houses a spray heat exchange section with heat exchange coils and a packing evaporation heat exchange section located below it, with air flowing through both heat exchange sections in a compound flow. It includes heat exchange coils and an air inlet chamber located on the windward side of the heat exchange coils. The heat exchange coils are closed-loop coils that allow the process medium to be cooled to circulate internally and receive heat exchange between air and spray water on their outer surface. The air inlet chamber is a cavity located on the windward side of the heat exchange coils, used to guide outside air into the tower and flow through the heat exchange coils. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is a parallel air duct formed by partitions separating the air inlet chambers in the width and / or height direction of the windward side, with airflow not interconnected between them. Airflow regulating components are actuators that can change the airflow volume of the corresponding independent air inlet channel, and wind speed detection components are sensors that can detect the airflow speed within the corresponding independent air inlet channel.

[0028] Specifically, the number and separation method of the independent air inlet channels can be determined according to the tower size and coil arrangement. For example, it can be divided into 3 to 12 independent air inlet channels along the length of the heat exchange coil. Solid partitions are set between adjacent independent air inlet channels to ensure that they are not interconnected, so that the air volume adjustment of any independent air inlet channel will not affect the adjacent channels through airflow. The air volume adjustment component can be one or more of the following combinations: servo electric louvered damper, electric regulating damper, and independent makeup air fan. The wind speed detection component can be conventional wind speed detection devices in the art, such as thermal wind speed sensor, Pitot tube anemometer, and ultrasonic wind speed sensor. Any component that can adjust and detect the air volume and wind speed of each independent air inlet channel can be used in this embodiment, and will not be listed here.

[0029] The intelligent airflow control method for a compound flow closed-circuit cooling tower specifically includes the following steps: S1: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat exchange load inside the composite flow closed cooling tower is calculated.

[0030] In this embodiment, operating parameters are physical quantities that characterize the current operating state of the composite flow closed-circuit cooling tower, including but not limited to inlet water temperature, outlet water temperature, circulating water flow rate, spray water flow rate, inlet dry-bulb temperature, inlet wet-bulb temperature, wind speed in each independent inlet channel, and fan speed. The three-dimensional flow field refers to the velocity and pressure distribution of air within the tower in three-dimensional space; the heat transfer load refers to the heat that the heat exchange coils need to dissipate or actually dissipate under current operating conditions; the digital mapping model refers to a mathematical mapping relationship that takes operating parameters as input and the three-dimensional flow field distribution and heat transfer load distribution within the tower as output, reflecting the correspondence between operating parameters and the flow field and heat transfer load within the tower.

[0031] Specifically, temperature sensors, flow meters, wind speed sensors, and speed sensors can be installed at the inlet pipe, outlet pipe, spray pipe, each independent air inlet channel, and fan of the composite flow closed-loop cooling tower to collect the aforementioned operating parameters in real time. The establishment of the digital mapping model includes, but is not limited to: first, simulating the tower's geometric model under different combinations of operating parameters using computational fluid dynamics (CFD) to obtain the three-dimensional flow field and heat transfer load distribution under each operating condition, and using the sample pairs formed by the operating parameters and simulation results for fitting or training to obtain the digital mapping model; second, using measured data from sensors arranged inside the tower, employing machine learning methods such as neural networks and support vector regression, with operating parameters as input and the flow field and heat transfer load reconstructed from measured data as output, to train the digital mapping model; third, establishing a reduced-order mechanism model based on the mass, momentum, and energy conservation equations and identifying parameters using measured data. All of the above modeling methods are conventional means feasible in this field.

[0032] The digital mapping model uses a BP neural network that includes an input layer, several fully connected hidden layers, and an output layer. The number of nodes in the input layer is equal to the dimension of the input parameters (running parameter vector), and the number of nodes in the output layer is equal to the sum of the number of nodes in the flow field grid and the number of heat transfer loads. The activation function of the hidden layer is ReLU.

[0033] S2: Based on the digital mapping model, determine the abnormal flow field region inside the composite flow closed cooling tower.

[0034] In this embodiment, the abnormal flow field region refers to the spatial region in the three-dimensional flow field within the tower where the wind speed deviates from the wind speed required for heat dissipation in the coil section, resulting in insufficient or uneven heat exchange in that section. Typical manifestations include weak wind zones with excessively low local wind speeds, short-circuit zones where airflow short-circuits, or turbulent zones with severely uneven airflow distribution. Based on the digital mapping model obtained in step S1, the actual wind speed distribution corresponding to each section of the heat exchange coil within the tower under the current operating parameters and the target wind speed distribution required for heat dissipation in that section can be calculated. The actual wind speed distribution and the target wind speed distribution are compared section by section. When the actual wind speed in a certain spatial region is lower than the target wind speed in that region by a preset deviation, that spatial region is identified as an abnormal flow field region. For example, the preset deviation is taken as 10% to 20% of the target wind speed.

[0035] S3: Based on the wind speed data collected by the wind speed detection component, determine the weak wind inlet channel corresponding to the abnormal flow field region among several independent inlet channels.

[0036] In this embodiment, the weak wind inlet channel refers to an independent inlet channel among several independent inlet channels whose transported airflow passes through an abnormal flow field area and whose measured wind speed is lower than a set threshold, i.e., an inlet channel that causes insufficient heat exchange in the corresponding coil section.

[0037] Specifically, since the air inlet chamber is divided into several independent air inlet channels that are not interconnected, each independent air inlet channel corresponds one-to-one with a specific section of the heat exchange coil in space. Therefore, based on the spatial location of the determined abnormal flow field area, the independent air inlet channel corresponding to the abnormal flow field area in the windward direction can be determined. Then, the wind speed data collected by the wind speed detection component in the independent air inlet channel is read. When the wind speed data is lower than a set threshold, the independent air inlet channel is determined as a weak wind air inlet channel. The set threshold can be a preset proportion of the target wind speed required for heat dissipation of the coil section corresponding to the independent air inlet channel, for example, 80% to 90% of the target wind speed.

[0038] S4: Based on the weak wind intake channel, calculate the target compensation amount of the weak wind intake channel, and adjust the air volume adjustment component of the weak wind intake channel according to the target compensation amount to obtain directional air volume compensation for the weak wind intake channel.

[0039] In this embodiment, the target compensation amount refers to the amount of air volume that needs to be added to the weak wind intake channel in order to make the wind speed of the weak wind intake channel reach the target wind speed required for heat dissipation of its corresponding coil section; directional air volume compensation refers to increasing the air volume of the independent intake channel that is determined to be weak wind only.

[0040] Specifically, the target compensation amount can be determined by the difference between the current measured air volume of the weak wind intake channel and its target air volume, that is, the difference between the target air volume and the current measured air volume is used as the target compensation amount; after obtaining the target compensation amount, an adjustment command is sent to the air volume adjustment component of the weak wind intake channel, such as increasing the opening of the servo electric louver damper and / or increasing the speed of the independent make-up air fan, so that the air volume of the weak wind intake channel increases to the target air volume.

[0041] S5: Based on the changing trend of heat exchange load, the predicted value of air volume demand is calculated, and the air volume demand is adjusted in advance for several independent air inlet channels according to the predicted value of air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

[0042] In this embodiment, the trend of heat exchange load change refers to the direction and rate of change of heat exchange load over time, such as whether the load increases, decreases, or remains stable, and how quickly it changes. The predicted air volume demand refers to the air volume value required by each independent air inlet channel in the future period, predicted based on the trend of heat exchange load change; feedforward regulation refers to the control of adjusting the air volume in advance before the outlet water temperature deviates due to changes in heat exchange load.

[0043] Specifically, taking a certain composite flow closed-loop cooling tower as an example, its air inlet chamber is divided into 6 independent air inlet channels (numbered 1# to 6#) along the length of the heat exchange coil. The system collects the heat exchange load every 30 seconds. Assume the heat exchange load collected at the current time t0 is 1200kW, and the heat exchange loads collected at 30-second intervals for the three most recent times are t_0, ... -2 1080kW, t -1 If the load is 1140kW at time t0 and 1200kW at time t0, the rate of change of the heat exchange load can be obtained by linear extrapolation: the load increment at adjacent times is 60kW / 10s, that is, the load increases at a rate of 6kW / s. Therefore, the next time step (t0) can be predicted. +1 (That is, after 30 seconds) the heat exchange load will rise to 1200 + 60 = 1260 kW, meaning the heat exchange load trend is a continuous increase, with the predicted air volume demand corresponding to a load of 1260 kW. Furthermore, based on the pre-calibrated load-air volume correspondence (in this example, it is calibrated so that every 1 kW of heat exchange load corresponds to a total air volume of 0.05 m³ / s, i.e., the load-air volume ratio coefficient is 0.05), t can be calculated. +1The total air volume required at time t0 is 1260 × 0.05 = 63 m³ / s. Assuming the heat dissipation load is evenly distributed across all independent air intake channels, the predicted air volume requirement for each independent air intake channel is 63 ÷ 6 = 10.5 m³ / s. However, the actual air volume for each independent air intake channel at time t0 is 1200 × 0.05 ÷ 6 = 10 m³ / s. Therefore, at time t0, feedforward adjustment is performed on the six independent air intake channels in advance, pre-adjusting the air volume of each channel from 10 m³ / s to 10.5 m³ / s. For example, the opening of the servo-driven electric louvered dampers in each channel is synchronously increased from 60% to 63%.

[0044] In one embodiment, a multi-tower parallel system refers to a system in which several composite flow closed-circuit cooling towers are connected in parallel on the water path and jointly undertake the same heat dissipation task. The composite flow closed-circuit cooling tower is one of the multiple towers in the system. The multiple towers in parallel system include several towers, and each tower is equipped with a fan and an air inlet valve. The air inlet valve is a valve installed on the air inlet side of the corresponding tower and used to adjust the total air intake.

[0045] In one embodiment, a smart airflow control method for a composite flow closed-circuit cooling tower further includes: S10: Based on the wind pressure distribution on the air intake side of each of the towers, the system-level wind pressure balance model of the multi-tower parallel system is calculated.

[0046] In this embodiment, the air pressure distribution on the inlet side refers to the static air pressure distribution at each position on the windward side of the air inlet side of each tower; the mutual interference relationship of air pressure refers to the interaction relationship in which the air pressure generated by the operation of the fan of any tower is affected by the operation of the fans of the adjacent towers when multiple towers are arranged in parallel, that is, the air pressure on the inlet side of a tower changes with the operating state of the adjacent towers; the system-level air pressure balance model refers to a mathematical model that takes the fan speed and air inlet valve opening of each of the towers as inputs, and takes the air pressure on the inlet side of each of the towers after considering the mutual interference of air pressure between towers as output.

[0047] Specifically, wind pressure sensors are arranged on the air inlet side of each tower to collect the wind pressure distribution on the air inlet side of each tower in real time. The methods for obtaining the mutual interference relationship of wind pressure include, but are not limited to: performing overall CFD simulation on the multi-tower parallel system, observing the response changes of the wind pressure on the air inlet side of the other towers when the fan speed or air inlet valve opening of a certain tower is changed, thereby calibrating the wind pressure influence coefficient between towers, and characterizing the mutual interference relationship between the wind pressure of each tower in the form of an influence coefficient matrix.

[0048] For example, the system-level wind pressure balance model can be expressed as P = A·U + P_0, where P = [P_1, P_2, ..., P_s]^T is the wind pressure vector on the inlet side of each of the s towers, U = [N_1, α_1, N_2, α_2, ..., N_s, α_s]^T is the input vector composed of the fan speed N and the inlet valve opening α of each tower, P_0 is the wind pressure vector on the inlet side of each tower when it operates independently, and A is the wind pressure influence coefficient matrix between towers, where the element A_ij represents the degree of influence of the j-th input variable on the wind pressure on the inlet side of the i-th tower. The influence coefficient matrix A is obtained by calibrating the overall CFD simulation of the multi-tower parallel system: each time the fan speed or inlet valve opening of a certain tower is changed individually, the response change of the wind pressure on the inlet side of the other towers is observed, and the ratio of the wind pressure change to the input change is used as the corresponding influence coefficient A_ij. By calibrating them one by one, the complete influence coefficient matrix A is obtained. Therefore, given the fan speed and inlet valve opening of each tower, the model can calculate the inlet air pressure of each tower after considering the mutual interference between towers, thus providing a basis for step S20 to solve the coordinated adjustment amount with the goal of making the air pressure of each tower tend to be consistent.

[0049] S20: Based on the system-level wind pressure balance model, determine the coordinated adjustment amount of the fan speed and air inlet valve opening of each of the several towers, and adjust the several towers in a coordinated manner according to the coordinated adjustment amount to obtain the heat dissipation distribution of the several towers with equal load and equal air volume.

[0050] In this embodiment, the internal allocation within a single tower is still differentiated according to S1~S5 and S100, while S10~S20 only achieves overall airflow balance between towers, and the two are at different levels. The coordinated adjustment amount refers to the adjustment amount required to simultaneously adjust the fan speed and inlet valve opening of each tower to eliminate the air pressure imbalance between towers. Specifically, with the goal of minimizing the air pressure difference on the air inlet side of each tower, the coordinated adjustment amount of the fan speed and inlet valve opening of each tower is obtained by using the system-level air pressure balance model as a constraint. The solution can employ conventional optimization algorithms in the field, such as using the minimum variance of the air pressure on the air inlet side of each tower as the objective function and the fan speed and inlet valve opening as decision variables for optimization. Any solution method that can make the air pressure of each tower tend to balance under the constraint of the system-level air pressure balance model is applicable and is not limited here.

[0051] In one embodiment, an intelligent airflow control method for a composite flow closed-loop cooling tower further includes: an airflow adjustment component comprising a servo-electric louvered damper and an independent makeup air fan; an airflow detection component comprising a pressure stabilizing chamber and an airflow sensing component located at the end of an independent air inlet channel; the servo-electric louvered damper adjusts the air inlet resistance by changing the blade angle, achieving continuous airflow adjustment under the condition where the fan is the primary exhaust fan; the independent makeup air fan is activated when the airflow demand of a certain channel cannot be met even when the servo-electric louvered damper is fully open, forcibly making air into that channel. Based on the coupling relationship between airflow, spray water flow rate, and heat exchange load, the optimal airflow ratio under minimum energy consumption is calculated, and several independent air inlet channels are controlled according to the optimal airflow ratio, including: S100: Obtain the spray water flow rate and heat exchange load of each of the several independent air inlet channels, and determine the energy consumption coefficient of each independent air inlet channel under unit heat exchange based on the coupling relationship.

[0052] In this embodiment, the coupling relationship refers to the relationship between air volume, spray water flow rate and heat exchange load, which mutually restrict each other and jointly determine the heat exchange effect. That is, the same heat exchange load can be achieved by different combinations of air volume and spray water flow rate, while the air volume is borne by the energy consumption of the fan and the make-up air fan, and the spray water flow rate is borne by the energy consumption of the spray pump.

[0053] Specifically, taking the aforementioned six independent air intake channels as an example, the spray water flow rate and heat exchange load of the corresponding coil section for each channel are obtained. For example, the spray water flow rate of channel #1 is 8 m³ / h, the heat exchange load is 200 kW, and its current air volume is 10 m³ / s. The coupling relationship can be expressed as the heat exchange load Q being a function of air volume G and spray water flow rate W, Q=f(G,W), which can be obtained from field tests or calibration using the aforementioned digital mapping model. The energy consumption coefficient is calculated as follows: the air-side energy consumption of channel #1 includes its allocated main fan power and independent makeup air fan power, set at 5.5 kW; the water-side energy consumption is the spray pump power allocated to this channel, set at 1.5 kW; therefore, the total energy consumption of channel #1 is 5.5 + 1.5 = 7 kW, corresponding to a heat exchange of 200 kW. Thus, the energy consumption coefficient of channel #1 under a unit heat exchange is 7 ÷ 200 = 0.035 kW / kW. The energy consumption coefficients of channels 2 to 6 were calculated in the same way. For example, due to the different spray water flow and airflow conditions in each channel, the energy consumption coefficients of channels 2 to 6 were 0.032, 0.038, 0.040, 0.034, and 0.036 kW / kW, respectively.

[0054] S200: Based on the energy consumption coefficient, with the goal of minimizing the total energy consumption of several independent air intake channels, the optimal air volume ratio among several independent air intake channels is calculated.

[0055] In this embodiment, the optimal air volume ratio refers to the air volume distribution ratio among several independent air inlet channels when the total energy consumption of several independent air inlet channels is minimized under the premise of meeting the total heat exchange load requirements.

[0056] Specifically, under the constraint that the total heat exchange load of the tower is 1200kW and needs to be shared by 6 independent air inlet channels, the optimization is performed with the objective function of minimizing the sum of the total energy consumption of each channel. The solution can be obtained using the Lagrange multiplier method or linear, quadratic programming, and other optimization methods.

[0057] S300: Based on the optimal airflow ratio, it controls the opening of the servo-driven electric louver damper and the speed of the independent makeup air fan.

[0058] In this embodiment, following step S200, taking channel #4 as an example, its target air volume is reduced from 10 m³ / s to 8.3 m³ / s. Then, the opening of the servo electric louver damper of channel #4 is reduced from 60% to about 50%. For example, according to the opening-air volume relationship in this example, every 1% reduction in opening reduces the air volume by about 0.175 m³ / s. A reduction of 1.7 m³ / s corresponds to a reduction of about 10% in opening. The independent make-up air fan is then slowed down or stopped. Taking channel #2 as an example, its target air volume is increased from 10 m³ / s to 11.2 m³ / s. Then, the opening of its servo electric louver damper is first increased from 60% to fully open (100%). If the air volume still does not reach 11.2 m³ / s after being fully opened, its independent make-up air fan is started and the speed is adjusted to make up the difference.

[0059] In one embodiment, in step S2, the abnormal flow field region inside the composite flow closed cooling tower is determined according to the digital mapping model, including: S21: Based on the digital mapping model, obtain the heat exchange coil area where the heat exchange coil is located, and divide the heat exchange coil area to obtain the first heat dissipation coil area and the second heat dissipation coil area.

[0060] In this embodiment, the heat exchange coil area refers to the space occupied by the heat exchange coil in the tower; the first heat dissipation coil area and the second heat dissipation coil area refer to two sub-areas obtained by dividing the heat exchange coil area according to the difference in heat dissipation conditions.

[0061] Specifically, the heat exchange coil area is a wet heat exchange area. The first heat exchange coil area is a stable heat exchange zone within the wet heat exchange area, characterized by a stable spray distribution. A stable heat exchange zone refers to a coil section where the spray water is evenly covered and the heat exchange conditions are stable. The second heat exchange coil area is a disturbed heat exchange zone within the wet heat exchange area, adjacent to an airflow short-circuit area and where the spray is disturbed. An airflow short-circuit area refers to a region where some airflow is drawn away before passing through the main heat exchange surface of the coil, forming a local short circuit. A disturbed heat exchange zone refers to a coil section where the heat exchange conditions are unstable due to proximity to short-circuit areas and disturbances in the spray distribution and airflow. Different coil sections within the wet heat exchange area exhibit variations in spray uniformity and airflow short-circuit conditions due to their different distances from the tower inlet, fan, and spray pipes, thus distinguishing between stable and disturbed heat exchange zones.

[0062] The heat exchange coil area is divided into a first heat dissipation coil area and a second heat dissipation coil area, specifically including: S211: Based on the spray distribution in the heat exchange coil area, obtain the stable spray region and the spray disturbance region.

[0063] Specifically, the spray water coverage density of each section along the length of the heat exchange coil area can be obtained using a digital mapping model or a spray density sensor. The rated spray density is set at 100%. The spray density is set at 95%–105% in the stable spray region and at 70%–94% in the disturbed spray region.

[0064] S212: Obtain the airflow short-circuit region based on the spray stability region and the spray disturbance region.

[0065] In this embodiment, the airflow short-circuit region refers to the area in the heat exchange coil region where part of the incoming air is not fully drawn through the coil's heat exchange surface before being drawn away by the fan. The spray disturbance is caused by the local high-speed lateral airflow resulting from the airflow short-circuit. Therefore, the airflow short-circuit region can be deduced from the spray disturbance region: the area adjacent to the spray disturbance region (sections 1# and 6#) that, according to the digital mapping model, shows airflow bypassing the main heat exchange surface of the coil and the local wind speed direction deviating from the normal windward direction, is identified as the airflow short-circuit region.

[0066] S213: Based on the airflow short-circuit region and the heat exchange coil region, obtain the first heat dissipation coil region and the second heat dissipation coil region.

[0067] For example, a short circuit is formed at the corners of the air inlets at both ends of the tower due to the abrupt change in airflow, creating an airflow short-circuit region. The coil section in the heat exchange coil region adjacent to the airflow short-circuit region is designated as the second heat dissipation coil region, and the remaining coil sections in the heat exchange coil region that are far from the airflow short-circuit region and have stable spray are designated as the first heat dissipation coil region.

[0068] S22: Based on the first and second heat dissipation coil areas, obtain the heat dissipation influencing factors related to airflow distribution.

[0069] In this embodiment, heat dissipation influencing factors refer to various factors that affect the heat dissipation effect of the corresponding coil area and are related to the air volume distribution of that area; wherein the first heat dissipation influencing factors are obtained from the first heat dissipation coil area, including the first load factor and the first environmental factor; the second heat dissipation influencing factors are obtained from the second heat dissipation coil area, including the second load factor, the second spray factor and the second environmental factor.

[0070] For example, for the first radiator coil area: the first load factor is the heat dissipation load represented by the product of the inlet and outlet water temperature difference and the circulating water flow rate of the coil in this area; the first environmental factor is the dry-bulb temperature and wet-bulb temperature of the air inlet on the windward side of this area, in this example the dry-bulb temperature is 32℃ and the wet-bulb temperature is 26℃. For the second radiator coil area: the second load factor is the heat dissipation load of this area; the second spray factor is the spray water flow rate and spray uniformity of this area, in this example the spray water flow rate is lower than the rated value due to airflow short-circuit disturbance and the spray uniformity is worse; the second environmental factor is the dry-bulb and wet-bulb temperature of the air inlet in this area, because the actual air inlet temperature of the adjacent short-circuit area is higher than that of the first radiator coil area, in this example the dry-bulb temperature is 35℃ and the wet-bulb temperature is 28℃.

[0071] S23: Based on the factors affecting heat dissipation, obtain the air volume demand influencing factor, which represents the degree of air volume demand.

[0072] In this embodiment, the airflow demand influencing factor is a quantitative indicator derived from heat dissipation influencing factors and used to characterize the airflow demand level of the corresponding coil area. The larger the value, the more airflow is needed in that area. The airflow demand influencing factor includes a first airflow demand influencing factor and a second airflow demand influencing factor. The first airflow demand influencing factor includes a first intrinsic influencing factor and a first extrinsic influencing factor; the second airflow demand influencing factor includes a second intrinsic influencing factor and a second extrinsic influencing factor.

[0073] For example, taking the aforementioned tower with six independent air inlet channels arranged along the length of the coil as an example, the section in the middle of the coil corresponding to channels 3 and 4 has good heat dissipation conditions and is classified as the first heat dissipation coil area, according to the digital mapping model calculation. The sections at both ends of the coil corresponding to channels 1 and 6, and the sections near the corners of the tower's air inlets that are prone to airflow short circuits, have poor heat dissipation conditions and are classified as the second heat dissipation coil area. In this example, the load of the channel 3 and 4 section is 400kW, and the load of the channel 1 and 6 section is 350kW.

[0074] First, obtain the preset heat dissipation related factors. The preset heat dissipation related factors refer to the set of factors that are pre-determined and significantly related to the air volume demand. For the first heat dissipation coil area: use the preset heat dissipation related factors to screen the first heat dissipation influencing factors to obtain the first heat dissipation screening factors, including the first load influencing factors and the first environmental influencing factors; among them, obtain the first intrinsic influencing factor based on the first load influencing factor. For example, normalize the heat dissipation load: if the rated load is 500kW, then the first intrinsic influencing factor = 400 / 500 = 0.80; obtain the first extrinsic influencing factor based on the first environmental influencing factor. For example, normalize the influence of the inlet wet-bulb temperature on heat exchange: if the reference wet-bulb temperature is 24℃, and the extrinsic factor increases by 0.05 for every 1℃ increase, then the first extrinsic influencing factor = 1 + (26-24) × 0.05 = 1.10. For the second heat dissipation coil area: the second heat dissipation screening factors are obtained, including the second load influencing factor (350kW), the second spray influencing factor (spray uniformity, such as 0.7, 1 for complete uniformity) and the second environmental influencing factor (wet bulb temperature 28℃); the second intrinsic influencing factor is obtained based on the second load influencing factor and the second spray influencing factor, for example, the second intrinsic influencing factor = (350 / 500) ÷ 0.7 ≈ 1.00; the second extrinsic influencing factor is obtained based on the second environmental influencing factor, for example, the second extrinsic influencing factor = 1 + (28-24) × 0.05 = 1.20.

[0075] S24: Based on the air volume demand influencing factors, divide the first heat dissipation coil area and the second heat dissipation coil area, obtain the division results, and determine the abnormal flow field area based on the division results.

[0076] Specifically, the division result refers to the result obtained after further distinguishing the first heat dissipation coil area and the second heat dissipation coil area based on the air volume demand influencing factor, indicating the degree of air volume demand in each coil section.

[0077] Specifically, the first and second airflow demand influencing factors are combined, and the product of the internal and external influencing factors is taken as the comprehensive airflow demand influencing factor for this area: Comprehensive airflow demand influencing factor for the first radiator coil area = 0.80 × 1.10 = 0.88; Comprehensive airflow demand influencing factor for the second radiator coil area = 1.00 × 1.20 = 1.20. A comparison shows that the airflow demand in the second radiator coil area is significantly higher than that in the first radiator coil area. Coil sections whose comprehensive airflow demand influencing factor exceeds a preset threshold (e.g., 1.0) are marked as high-demand sections, resulting in the following division: In this example, the sections corresponding to channels 1# and 6# are high-demand sections. Then, considering the actual air supply situation in this section: If the actual wind speed corresponding to the high-demand section is lower than the target wind speed increased due to high demand, the flow field area corresponding to the high-demand section is determined as an abnormal flow field area. In this example, the sections of channels 1# and 6# are determined as abnormal flow field areas.

[0078] In one embodiment, the overall heat dissipation numerical information in this step is a specific embodiment of the predicted airflow demand value described in step S5 under the scenario where the outlet water temperature needs to be rapidly adjusted, that is, the feedforward adjustment is subdivided into a pre-cooling stage and a steady-state stage. In step S4, based on the weak airflow inlet channel, the target compensation amount of the weak airflow inlet channel is calculated, including: S41: Based on the division results, obtain heat dissipation demand information, and based on the heat dissipation demand information, obtain overall heat dissipation numerical information. The heat dissipation demand information includes the target outlet water temperature and heat dissipation duration, and the overall heat dissipation numerical information includes pre-cooling air volume, pre-cooling duration, steady-state air volume, and steady-state heat dissipation duration.

[0079] In this embodiment, heat dissipation requirement information refers to the conditions required to achieve a predetermined heat dissipation target, including the target outlet water temperature and heat dissipation duration: the target outlet water temperature refers to the set temperature that the heat exchange coil outlet side needs to reach, and the heat dissipation duration refers to the time required for the current outlet water temperature to drop to the target outlet water temperature and maintain it. Overall heat dissipation numerical information refers to the airflow and time values ​​calculated from the overall tower level to meet the above heat dissipation requirements, including pre-cooling airflow, pre-cooling duration, steady-state airflow, and steady-state heat dissipation duration: steady-state airflow refers to the constant airflow required to reach and maintain the target outlet water temperature; steady-state heat dissipation duration refers to the duration of operation after the outlet water temperature stabilizes at the target outlet water temperature; pre-cooling airflow refers to the airflow, different from the steady-state airflow, applied during the pre-cooling stage before steady-state to accelerate the drop in outlet water temperature; and pre-cooling duration refers to the duration of the pre-cooling stage.

[0080] Specifically, step S41 includes: S411: Extract the target outlet water temperature from the heat dissipation demand information and use the air volume corresponding to the target outlet water temperature as the steady-state air volume.

[0081] In this embodiment, the air volume corresponding to the target outlet water temperature refers to the air volume required to maintain the outlet water temperature at the target outlet water temperature under the current inlet water temperature, circulating water flow rate and inlet air temperature and humidity conditions. This air volume is referred to as the steady-state air volume.

[0082] For example, continuing from the previous example, the target outlet water temperature is 32℃. This can be found from the digital mapping model or the pre-calibrated "outlet water temperature and air volume" relationship table: under the current conditions of inlet water temperature of 37℃, rated circulating water flow rate, and inlet air wet-bulb temperature of 26℃, the total air volume required to maintain an outlet water temperature of 32℃ is 60m³ / s. Therefore, 60m³ / s is taken as the steady-state air volume.

[0083] S412: Based on the heat dissipation time and target outlet water temperature, obtain the pre-cooling time, steady-state heat dissipation time, and pre-cooling air volume; the pre-cooling air volume includes the pre-cooling boost air volume and the pre-cooling drop air volume, and the pre-cooling time includes the pre-cooling boost time and the pre-cooling drop time.

[0084] In this embodiment, the pre-cooling boost air volume refers to the air volume applied in the early stage of the pre-cooling phase to quickly lower the outlet water temperature, which is higher than the steady-state air volume; the pre-cooling drop air volume refers to the transition air volume that drops from the boost air volume to near the steady state in the later stage of the pre-cooling phase, when the outlet water temperature is close to the target value, in order to avoid overshoot; the pre-cooling boost duration and the pre-cooling drop duration are the durations for applying the pre-cooling boost air volume and the pre-cooling drop air volume, respectively; the steady-state heat dissipation duration is the remaining duration after deducting the pre-cooling duration from the heat dissipation duration.

[0085] Continuing from the previous example (heat dissipation time 600s, target outlet water temperature 32℃, steady-state airflow 60m³ / s). The current outlet water temperature is 37℃, a 5℃ difference from the target 32℃. To rapidly lower the temperature within the limited heat dissipation time, the pre-cooling airflow is set to 1.2 times the steady-state airflow, i.e., 72m³ / s, with a pre-cooling duration of 120s. This allows the outlet water temperature to rapidly drop from 37℃ to approximately 33℃ within the first 120s. Subsequently, to prevent a sudden decrease in airflow causing a temperature rebound, and also to prevent continued high airflow leading to overcooling and energy waste, the pre-cooling airflow is set to 1.05 times the steady-state airflow, i.e., 63m³ / s, with a pre-cooling duration of 60s. This allows the outlet water temperature to smoothly transition to 32℃. The total pre-cooling time is 120 + 60 = 180s, and the steady-state heat dissipation time is 600 − 180 = 420s. The boost and pullback ratios and durations of precooling can be determined by the heat dissipation time, temperature difference, and thermal inertia of the tower. The greater the temperature difference, the higher the boost ratio and the longer the boost duration.

[0086] S413: Correlates steady-state airflow, pre-cooling duration, steady-state heat dissipation duration, and pre-cooling airflow to obtain overall heat dissipation data.

[0087] In this embodiment, association refers to organizing the above air volume values ​​and duration values ​​in chronological order to form a complete "air volume-time" control sequence, which is the overall heat dissipation numerical information.

[0088] S42: Obtain compensation distance. Based on the compensation distance and overall heat dissipation data, obtain the air supply parameters. The compensation distance refers to the distance between the heat dissipation coil area and several independent air intake channels. The air supply parameters include the zoned air supply pre-cooling air volume and the zoned air supply steady-state air volume for each independent air intake channel.

[0089] In this embodiment, the air volume demand influencing factors include the first air volume demand influencing factor and the second air volume demand influencing factor; the zoned air supply pre-cooling air volume includes the zoned boost air supply pre-cooling air volume and the zoned drop air supply pre-cooling air volume.

[0090] Specifically, step S42 includes: S421: Based on the first air volume demand influence factor, the second air volume demand influence factor, the pre-cooling air volume, and the compensation distance, obtain the pre-cooling air volume of the zone's boost supply air and the pre-cooling air volume of the zone's drop supply air.

[0091] In this embodiment, the zoned air supply precooling air volume includes the zoned boost air supply precooling air volume and the zoned fall air supply precooling air volume: the zoned boost air supply precooling air volume refers to the air volume that should be delivered at the air supply end of each independent air inlet channel during the precooling boosting stage; the zoned fall air supply precooling air volume refers to the air volume that should be delivered at the air supply end of each independent air inlet channel during the precooling fall stage.

[0092] Specifically, the precooling air volume in the overall heat dissipation data is the overall value of the tower. It needs to be allocated to each zone according to the air volume demand influence factor of each coil zone, and then converted to the air supply end according to the compensation distance. Continuing the previous example, the overall precooling boost air volume is 72m³ / s, the comprehensive air volume demand influence factor of the first heat dissipation coil zone is 0.88, and that of the second heat dissipation coil zone is 1.20. The 72 m³ / s airflow is weighted according to the influence factor and allocated to each zone. Taking a zone with 6 channels, the second heat dissipation coil zone containing channels 1 and 6, and the first heat dissipation coil zone containing channels 3 and 4 (channels 2 and 5 are assigned to the stable side) as an example, the second heat dissipation coil zone has a high single-channel factor and receives more airflow. In this example, the airflow required at the coil of channel 6 (second heat dissipation coil zone) during the pre-cooling boosting stage is 12 m³ / s after factor weighting. Then, it is converted to the air supply end according to its compensation distance of 1.2m: zone boosting air supply pre-cooling airflow = 12 ÷ (1 − 0.08 × 1.2) ≈ 13.3 m³ / s. Similarly, the coil of channel 3 (first heat dissipation coil zone, compensation distance 0.5m) requires 10 m³ / s, and the zone boosting air supply pre-cooling airflow = 10 ÷ (1 − 0.08 × 0.5) ≈ 10.4 m³ / s. The pre-cooling air volume for the zoned return air supply is calculated using the same method based on a pre-cooling return air volume of 63 m³ / s. In this example, channel #6 yields approximately 11.6 m³ / s and channel #3 yields approximately 10.9 m³ / s.

[0093] S422: Obtain the steady-state air volume for zoned air supply based on the first air volume demand influence factor, the second air volume demand influence factor, the steady-state air volume, and the compensation distance.

[0094] In this embodiment, the steady-state air volume of zoned air supply refers to the air volume that should be delivered by the air supply end of each independent air inlet channel during the steady-state stage.

[0095] Specifically, the overall steady-state airflow of 60 m³ / s is weighted and allocated to the corresponding channels of each coil area according to the first and second airflow demand influence factors, and then converted to the air supply end according to the compensation distance of each channel. Continuing the previous example, the steady-state demand at the coil of channel #6 (second heat dissipation coil area, second airflow demand influence factor 1.20, compensation distance 1.2m) is 10 m³ / s, and the steady-state airflow of the zoned air supply is 10 ÷ (1 − 0.08 × 1.2) ≈ 11.1 m³ / s; the steady-state demand at the coil of channel #3 (located in the first heat dissipation coil area, first airflow demand influence factor 0.88, compensation distance 0.5m) is 10 m³ / s, and the steady-state airflow of the zoned air supply is 10 ÷ (1 − 0.08 × 0.5) ≈ 10.4 m³ / s. This yields the airflow at the air supply end of each independent air intake channel in the steady-state phase.

[0096] S43: Determine the target compensation amount for the weak wind intake channel based on the air supply parameters.

[0097] In this embodiment, the target compensation amount is the difference between the air volume that the weak wind inlet channel should deliver according to the air supply parameters and the current actual air volume of the channel. The target compensation amount is taken at different times during the pre-cooling / steady-state stages, which is the air volume value that needs to be compensated for the weak wind inlet channel.

[0098] For example, following step S42. Taking channel #6 (belonging to the second heat dissipation coil area, with a compensation distance of 1.2m), which is determined to be a weak wind intake channel, as an example: its zoned air supply steady-state air volume is 11.1m³ / s, while the current actual air volume of this channel is 10m³ / s. Therefore, the target compensation amount in the steady-state stage is 11.1−10=1.1m³ / s; in the pre-cooling enhancement stage, its zoned enhanced air supply pre-cooling air volume is calculated to be 13.3m³ / s (corresponding to 12m³ / s at the coil). Therefore, the target compensation amount in the pre-cooling enhancement stage is 13.3−10=3.3m³ / s. After obtaining the phased target compensation amount, the airflow adjustment component of channel #6 is adjusted according to step S4: During the pre-cooling boost phase, the servo-electric louver damper is opened to full and the independent makeup air fan is started to supplement 3.3 m³ / s, which is maintained for 120s; during the pre-cooling fall phase, the compensation amount is reduced to the corresponding value and maintained for 60s; then, it enters the steady-state phase, compensating only 1.1 m³ / s and maintaining it for 420s. In this way, phased and quantitative directional airflow compensation is achieved for the weak wind intake channel.

[0099] In one embodiment, after step S5, a method for intelligent airflow control of a composite flow closed-loop cooling tower further includes: S501: Obtain zone wind speed detection information, compare the zone wind speed detection information with the corresponding air volume value in the overall heat dissipation numerical information to obtain the zone difference value, compare the zone difference value with the preset change threshold range, and if the zone difference value is outside the preset change threshold range, trigger the zone wind speed change information collection command.

[0100] In this embodiment, the zone wind speed detection information refers to the actual air volume converted from the wind speed of each independent air intake channel (after rectification by the terminal pressure stabilizing chamber) measured by the wind speed detection component of each independent air intake channel; the zone difference value refers to the difference between the actual air volume of an independent air intake channel and the air volume value corresponding to the current stage of the channel in the overall heat dissipation numerical information; the preset change threshold refers to the allowable difference range. Differences within this range are considered to be adequately compensated, while differences outside the range are considered to be excessively large and require further processing.

[0101] For example, the target airflow for channel #6 in the steady-state phase is 11.1 m³ / s. The actual airflow, calculated from the measured wind speed of the wind speed sensor in the pressure-stabilizing chamber at the end of channel #6 and converted using the cross-sectional area of ​​the pressure-stabilizing chamber, is 10.3 m³ / s. Therefore, the zone difference value is 11.1 - 10.3 = 0.8 m³ / s. Assuming a preset change threshold of ±0.5 m³ / s, the zone difference value of 0.8 m³ / s in this example exceeds this threshold, indicating that the actual airflow in this channel is significantly lower than the target value (possibly due to dust accumulation on the damper, performance degradation of the make-up air fan, or greater-than-expected airflow attenuation along the path). This triggers the zone wind speed change information collection command for channel #6. If the measured airflow for a channel (such as #3) is 10.2 m³ / s and the target is 10.4 m³ / s, the difference of 0.2 m³ / s is within the ±0.5 m³ / s threshold, and the compensation is considered adequate, no collection command is triggered.

[0102] S502: Obtain adjustment parameter information based on the command to collect information on wind speed changes in different zones.

[0103] In this embodiment, the adjustment parameter information refers to the parameters that need to be adjusted for the air volume adjustment component of the channel in order to eliminate the difference value between zones, such as the additional increment of the opening of the servo electric louver damper, the additional increment of the speed of the independent make-up air fan, etc.

[0104] Specifically, following the previous example, after channel #6 triggers the collection command, it collects the current status and operating environment information of the airflow regulation components in that channel: the current servo-driven electric louver damper is fully open (100%), and the independent makeup air fan speed is 80% of its rated speed. The required additional adjustment is calculated from the zone difference value of 0.8 m³ / s: since the damper has no upward adjustment margin, the entire adjustment is borne by the makeup air fan. Based on the fan speed-airflow relationship (rated speed corresponds to an airflow increment of 5 m³ / s, approximately linear), the required additional speed increment is calculated as 0.8 / 5 × 100% = 16%, resulting in the adjustment parameter information: "Independent makeup air fan speed increased from 80% to 96%". If the difference is due to excessive airflow (actually higher than the target), the corresponding adjustment parameter information is to reduce the damper opening or decrease the fan speed.

[0105] S503: Trigger adjustment command based on adjustment parameter information.

[0106] In this embodiment, the adjustment command refers to the execution command issued to the airflow adjustment component of the channel based on the adjustment parameter information. After the adjustment command is executed, the process can return to step S501 to detect the zone wind speed again and verify the difference value. This cycle continues until the difference value of each channel zone falls within the preset change threshold range, forming a closed-loop control mode.

[0107] It should be understood that the sequence number of each step in the above embodiments does not imply the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of this application.

[0108] In one embodiment, such as Figure 2 and Figure 3 As shown, a composite flow closed-loop cooling tower is provided, including a heat exchange coil, an air inlet chamber disposed on the windward side of the heat exchange coil, and a controller. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is equipped with an air volume regulating component and an air speed detection component.

[0109] The controller is configured to perform the following operations: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat transfer load inside the composite flow closed cooling tower is calculated. Based on the digital mapping model, the abnormal flow field region inside the composite flow closed cooling tower was determined; Based on the wind speed data collected by the wind speed detection component, the weak wind inlet channel corresponding to the abnormal flow field region is identified among several independent inlet channels. Based on the weak wind intake channel, the target compensation amount of the weak wind intake channel is calculated, and the air volume adjustment component of the weak wind intake channel is adjusted according to the target compensation amount to obtain directional air volume compensation for the weak wind intake channel. Based on the changing trend of heat exchange load, the predicted value of air volume demand is calculated, and feedforward adjustment is performed on several independent air inlet channels according to the predicted value of air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

[0110] Optionally, the composite flow closed cooling tower of this embodiment is a closed mixed flow (composite flow) structure, mainly including a tower body, a heat exchange coil installed in the tower body, a spray system installed above the heat exchange coil, a packing installed below the heat exchange coil, a water tank installed at the bottom of the tower body, a circulating water pump, and an air inlet chamber and a fan installed on the windward side of the heat exchange coil. The air inlet chamber is not shown in the figure.

[0111] The heat exchange coil is a closed serpentine tube assembly, consisting of several parallel heat exchange tubes connected in series and / or in parallel via connecting elbows. Its inlet and outlet are respectively connected to the process medium to be cooled (i.e., equipment water) pipeline. The process medium flows in a closed loop inside the heat exchange coil and does not come into direct contact with the spray water and air outside the coil.

[0112] The spray system is located above the heat exchange coils and includes a main water distribution pipe, spray branch pipes, and spray heads (not shown in the figure) installed on the spray branch pipes. The packing material is located below the heat exchange coils and is used for secondary evaporation and heat dissipation of the spray water flowing over its surface. The water tank (not shown in the figure) is located at the bottom of the tower and is used to collect the falling spray water; the inlet of the circulating water pump is connected to the water tank, and the outlet is connected to the main water distribution pipe at the top of the tower via a vertical water pipe.

[0113] After the treated spray circulating water is returned, it enters the water tank at the bottom of the tower through the inlet (also known as the equipment water inlet). The circulating water pump draws the spray water out of the tank and transports it upwards to the top of the tower through vertical water pipes. See also Figure 2 and Figure 3 Spray water enters the main water distribution pipe from the middle through an elbow and flows axially from the middle to both ends. The side wall of the main water distribution pipe has several distribution holes along its length, through which the spray water is distributed to the spray branch pipes on both sides. This distribution method from the middle to both ends ensures a relatively even water supply pressure throughout the main water distribution pipe. The spray branch pipes have several mounting holes spaced along their length, with a corresponding spray head installed at each hole. Spray water is transported through the spray branch pipes and sprayed by the spray heads onto the heat exchange coils below.

[0114] The sprinkler head includes an upper insertion section for sealing with the mounting hole of the sprinkler branch pipe and a lower water distribution structure. The water distribution structure adopts a double-layer water distribution plate structure, including a first water distribution plate on top and a second water distribution plate on the bottom. After the sprinkler water flows out of the sprinkler head, part of it diffuses outward through the first water distribution plate and falls into the outer area of ​​the sprinkler head's coverage area, while the other part diffuses outward through the second water distribution plate into the area directly below and adjacent to the sprinkler head and falls into the inner area of ​​the coverage area.

[0115] The heat exchange cycle process of the composite flow closed-loop cooling tower in this embodiment is as follows: The water (process medium) to be cooled enters through the lower inlet of the heat exchange coil and flows from bottom to top inside the heat exchange coil. The circulating water pump pumps the spray water (approximately 32°C) from the water tank to the top spray system through the water pipe. The spray head sprays the spray water onto the outer surface of the heat exchange coil, where it exchanges heat with the water flowing from bottom to top inside the coil, thus lowering the temperature of the water and causing the spray water to absorb heat and rise.

[0116] The heated spray water flows downwards and over the packing material below the heat exchange coils, where it comes into contact with the air, evaporates and dissipates heat, and falls into the water tank at the bottom of the tower after cooling. It is then pumped back to the top of the tower by the circulating water pump, and the cycle continues. Air is drawn into the tower by the fan through the independent air inlet channels of the air inlet chamber, flows through the heat exchange sections of the coils and the packing material, forming a composite flow (mixed flow) for heat exchange.

[0117] For specific limitations regarding the controller of a composite flow closed-circuit cooling tower, please refer to the limitations of the intelligent airflow control method for a composite flow closed-circuit cooling tower mentioned above, which will not be repeated here. Each module in the controller can be implemented entirely or partially through software, hardware, or a combination thereof. Each module can be embedded in the processor of a computer device in hardware form or independent of the processor, or it can be stored in the memory of a computer device in software form, so that the processor can call and execute the corresponding operations of each module.

[0118] In one embodiment, a computer device is provided, which may be a server, and its internal structure diagram may be as follows: Figure 4 As shown, the computer device includes a processor, memory, network interface, and database connected via a system bus. The processor provides computing and control capabilities. The memory includes non-volatile storage media and internal memory. The non-volatile storage media stores the operating system, computer programs, and database. The internal memory provides an environment for the operation of the operating system and computer programs stored in the non-volatile storage media. The database stores digital mapping models, etc. The network interface is used for communication with external terminals via a network connection. When the computer program is executed by the processor, it implements an intelligent airflow control method for a composite flow closed-loop cooling tower.

[0119] In one embodiment, a computer device is provided, including a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, it implements the steps of the intelligent airflow control method for a composite flow closed cooling tower as described above.

[0120] In one embodiment, a computer-readable storage medium is provided having a computer program stored thereon, which, when executed by a processor, implements the steps of the intelligent airflow control method for a composite flow closed-loop cooling tower as described above.

[0121] Those skilled in the art will understand that all or part of the processes in the above embodiments can be implemented by a computer program instructing related hardware. The computer program can be stored in a non-volatile computer-readable storage medium, and when executed, it can include the processes of the embodiments of the above methods. Furthermore, any references to memory, storage, databases, or other media used in the embodiments provided in this application can include non-volatile and / or volatile memory.

[0122] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the above-described division of functional units and modules is used as an example. In practical applications, the above functions can be assigned to different functional units and modules as needed, that is, the internal structure of the device can be divided into different functional units or modules to complete all or part of the functions described above.

[0123] The above-described embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be included within the protection scope of this application.

Claims

1. A method for intelligent airflow control in a composite flow closed-loop cooling tower, characterized in that, The composite flow closed-loop cooling tower includes heat exchange coils and an air inlet chamber located on the windward side of the heat exchange coils. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is equipped with an airflow regulating component and an air velocity detection component. The method includes: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat transfer load inside the composite flow closed cooling tower is calculated. Based on the digital mapping model, the abnormal flow field region inside the composite flow closed cooling tower is determined; Based on the wind speed data collected by the wind speed detection component, the weak wind inlet channel corresponding to the abnormal flow field region is determined among the several independent inlet channels. Based on the weak wind inlet channel, the target compensation amount of the weak wind inlet channel is calculated, and the air volume adjustment component of the weak wind inlet channel is adjusted according to the target compensation amount to obtain directional air volume compensation for the weak wind inlet channel. Based on the changing trend of the heat exchange load, the predicted air volume demand is calculated, and the several independent air inlet channels are adjusted in advance according to the predicted air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

2. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 1, characterized in that, The composite flow closed-loop cooling tower is one of several towers in a multi-tower parallel system, each tower being equipped with a fan and an air inlet valve. The method further includes: Based on the wind pressure distribution on the air inlet side of each of the towers, the system-level wind pressure balance model of the multi-tower parallel system is calculated. Based on the system-level wind pressure balance model, the coordinated adjustment amount of the fan speed and air inlet valve opening of each of the towers is determined, and the towers are coordinated and adjusted according to the coordinated adjustment amount to obtain the heat dissipation distribution of the towers with equal load and equal air volume.

3. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 1, characterized in that, The airflow regulating component includes a servo-driven electric louvered damper and an independent makeup air fan; the wind speed detection component includes a pressure stabilizing chamber and a wind speed sensing assembly located at the end of the independent air inlet channel; the method further includes: Based on the coupling relationship between air volume, spray water flow rate, and heat exchange load, the optimal air volume ratio with minimum energy consumption is calculated, and the several independent air inlet channels are controlled according to the optimal air volume ratio, including: The spray water flow rate and heat exchange load of each of the several independent air inlet channels are obtained, and the energy consumption coefficient of each independent air inlet channel under unit heat exchange is determined based on the coupling relationship. Based on the energy consumption coefficient, with the goal of minimizing the total energy consumption of the independent air intake channels, the optimal air volume ratio among the independent air intake channels is calculated. Based on the optimal air volume ratio, the opening degree of the servo-driven electric louver damper and the rotation speed of the independent make-up air fan are controlled.

4. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 1, characterized in that, The determination of the abnormal flow field region inside the composite flow closed cooling tower based on the digital mapping model includes: Based on the digital mapping model, the heat exchange coil region where the heat exchange coil is located is obtained, and the heat exchange coil region is divided to obtain the first heat dissipation coil region and the second heat dissipation coil region. Based on the first heat dissipation coil area and the second heat dissipation coil area, obtain the heat dissipation influencing factors related to airflow distribution; Based on the aforementioned heat dissipation influencing factors, obtain the air volume demand influencing factor, which represents the degree of air volume demand. Based on the air volume demand influencing factor, the first heat dissipation coil area and the second heat dissipation coil area are divided to obtain the division result, and the abnormal flow field area is determined based on the division result.

5. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 4, characterized in that, The heat exchange coil area is a wet heat exchange area. The first heat exchange coil area is a stable heat exchange area with stable spray distribution within the wet heat exchange area. The second heat exchange coil area is a disturbed heat exchange area within the wet heat exchange area adjacent to the airflow short-circuit area and where the spray is disturbed. The division of the heat exchange coil area to obtain the first heat exchange coil area and the second heat exchange coil area specifically includes: Based on the spray distribution in the heat exchange coil area, the stable spray region and the spray disturbance region are obtained; Based on the spray stability region and the spray disturbance region, the airflow short-circuit region is obtained; Based on the airflow short-circuit region and the heat exchange coil region, the first heat dissipation coil region and the second heat dissipation coil region are obtained.

6. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 4, characterized in that, The step of calculating the target compensation amount for the weak wind intake channel based on the weak wind intake channel includes: Based on the division results, heat dissipation demand information is obtained, and based on the heat dissipation demand information, overall heat dissipation numerical information is obtained. The heat dissipation demand information includes the target outlet water temperature and heat dissipation duration, and the overall heat dissipation numerical information includes pre-cooling air volume, pre-cooling duration, steady-state air volume, and steady-state heat dissipation duration. Obtain the compensation distance, and based on the compensation distance and the overall heat dissipation value information, obtain the air supply parameters. The compensation distance refers to the distance between the heat dissipation coil area and the several independent air inlet channels. The air supply parameters include the zoned air supply pre-cooling air volume and the zoned air supply steady-state air volume of each independent air inlet channel. Based on the air supply parameters, the target compensation amount of the weak wind intake channel is determined.

7. The intelligent airflow control method for a composite flow closed-loop cooling tower according to claim 6, characterized in that, The step of obtaining overall heat dissipation value information based on the heat dissipation demand information specifically includes: The target outlet water temperature is extracted from the heat dissipation demand information, and the air volume corresponding to the target outlet water temperature is taken as the steady-state air volume. Based on the heat dissipation duration and the target outlet water temperature, the pre-cooling duration, the steady-state heat dissipation duration, and the pre-cooling air volume are obtained; the pre-cooling air volume includes the pre-cooling boost air volume and the pre-cooling drop air volume, and the pre-cooling duration includes the pre-cooling boost duration and the pre-cooling drop duration. By associating the steady-state airflow, the pre-cooling duration, the steady-state heat dissipation duration, and the pre-cooling airflow, the overall heat dissipation numerical information is obtained; And / or, The air volume demand influencing factors include a first air volume demand influencing factor and a second air volume demand influencing factor; the zoned air supply pre-cooling air volume includes zoned boost air supply pre-cooling air volume and zoned fall-down air supply pre-cooling air volume; obtaining the air supply parameters based on the compensation distance and the overall heat dissipation value information specifically includes: Based on the first air volume demand influence factor, the second air volume demand influence factor, the pre-cooling air volume, and the compensation distance, obtain the pre-cooling air volume of the zone's boost air supply and the pre-cooling air volume of the zone's fallback air supply. The steady-state air volume of the zoned air supply is obtained based on the first air volume demand influence factor, the second air volume demand influence factor, the steady-state air volume, and the compensation distance.

8. A composite flow closed-loop cooling tower, characterized in that, It includes a heat exchange coil, an air inlet chamber located on the windward side of the heat exchange coil, and a controller. The air inlet chamber is divided into several independent air inlet channels that are not interconnected. Each independent air inlet channel is equipped with an air volume regulating component and an air speed detection component. The controller is configured to perform the following operations: Based on the collected operating parameters of the composite flow closed cooling tower, a digital mapping model of the three-dimensional flow field and heat exchange load inside the composite flow closed cooling tower is calculated. Based on the digital mapping model, the abnormal flow field region inside the composite flow closed cooling tower is determined; Based on the wind speed data collected by the wind speed detection component, the weak wind inlet channel corresponding to the abnormal flow field region is determined among the several independent inlet channels. Based on the weak wind inlet channel, the target compensation amount of the weak wind inlet channel is calculated, and the air volume adjustment component of the weak wind inlet channel is adjusted according to the target compensation amount to obtain directional air volume compensation for the weak wind inlet channel. Based on the changing trend of the heat exchange load, the predicted air volume demand is calculated, and the several independent air inlet channels are adjusted in advance according to the predicted air volume demand to make the air velocity on the surface of the heat exchange coil uniform.

9. A computer device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the intelligent airflow control method for a composite flow closed cooling tower as described in any one of claims 1 to 7.

10. A computer-readable storage medium storing a computer program, characterized in that, When the computer program is executed by the processor, it implements the steps of the intelligent airflow control method for a composite flow closed cooling tower as described in any one of claims 1 to 7.

Images