Air treatment device, and control method and control device therefor

Abstract

This application provides an air handling equipment and its control method and device. The air handling equipment includes a main duct, an isolation and distribution component, and a regulating component. The main duct is connected to multiple heat exchange tubes. The isolation and distribution component isolates the main duct into a first passage and a second passage, and can regulate the number of heat exchange tubes connected to the first and second passages. The regulating component includes a first regulating valve located at the water inlet end of the first passage and a second regulating valve located at the water inlet end of the second passage. The method includes: determining the target outlet air temperature of the second passage and the first passage based on the total air volume, the target total air temperature, and the target total air humidity; adjusting the first regulating valve and the second regulating valve to make the outlet air temperature of the first passage and the second passage reach the corresponding target outlet air temperature; and increasing the number of heat exchange tubes connected to the second passage when the second regulating valve reaches a first preset opening degree and the actual total air humidity is still higher than the target total air humidity. This application can broaden the effective temperature and humidity regulation range.

Description

Technical Field

[0001] This application relates to the field of air treatment technology, and in particular to an air treatment device and its control method and control apparatus. Background Technology

[0002] Air handling equipment (such as air conditioners) is widely used in various building environments such as clean rooms, large venues and operating rooms. Air handling equipment can partially or completely regulate the temperature, humidity, flow rate and cleanliness of the air, so that the air parameters of the target environment meet the needs of different application scenarios.

[0003] However, the air handling equipment in related technologies has a limited capacity to handle heat and humidity loads and cannot stably maintain the temperature and humidity setpoints in the target environment. Summary of the Invention

[0004] The main objective of this application is to provide an air handling equipment and its control method and device, which aims to broaden the capacity range of the air handling equipment for handling heat and humidity loads.

[0005] To achieve the above objectives, a first aspect of this application provides a control method for an air handling equipment. The air handling equipment includes a main pipeline, an isolation and distribution assembly, a regulating assembly, and multiple independent heat exchange tubes. The main pipeline has multiple water outlets connected to it, and each of the multiple water outlets is connected one-to-one to the water inlet of one of the multiple heat exchange tubes. The isolation and distribution assembly is disposed within the main pipeline to isolate the main pipeline into a first passage and a second passage. The isolation and distribution assembly is capable of adjusting the number of heat exchange tubes connected to the first passage and the second passage. The regulating assembly includes a first regulating valve and a second regulating valve. The first regulating valve is disposed at the water inlet of the first passage, and the second regulating valve is disposed at the water inlet of the second passage. The method includes: Obtain the target total supply air temperature and target total supply air humidity of the air handling unit; The second target outlet temperature of the second passage is determined based on the preset total air volume, the target total air temperature, and the target total air humidity, and the first target outlet temperature of the first passage is determined based on the target total air temperature and the second target outlet temperature. Adjust the opening of the first regulating valve to make the outlet air temperature of the first passage reach the first target outlet air temperature, and adjust the opening of the second regulating valve to make the outlet air temperature of the second passage reach the second target outlet air temperature. When the opening degree of the second regulating valve reaches the first preset opening degree, and the actual total supply air humidity of the air handling equipment is higher than the target total supply air humidity, the isolation distribution component is controlled to increase the number of heat exchange tubes connected to the second passage.

[0006] To achieve the above objectives, a second aspect of the present application provides a control device for implementing the control method of the air handling equipment as described in the first aspect.

[0007] To achieve the above objectives, a third aspect of this application provides an air handling device, the air handling device comprising: The control device as described in the second aspect; The main pipeline has multiple outlets connected to its conduit. An isolation distribution component is disposed within the main pipeline to isolate the main pipeline into a first path and a second path. The regulating component includes a first regulating valve and a second regulating valve, wherein the first regulating valve is disposed at the water inlet end of the first passage and the second regulating valve is disposed at the water inlet end of the second passage; Multiple independent heat exchange tubes are provided, and the multiple outlets of the main pipe are connected one-to-one to the inlet of the multiple heat exchange tubes. The isolation distribution component can adjust the number of heat exchange tubes connected to the first passage and the second passage.

[0008] The air handling equipment, control method, and control device proposed in this application divide the main pipeline into a first passage and a second passage through an isolation distribution component. Combined with a first regulating valve and a second regulating valve respectively located at the water inlet of the two passages, independent regulation of the chilled water flow rate in the heat exchange tubes connected to different passages is achieved to meet basic temperature and humidity control requirements. Furthermore, when the opening degree of the second regulating valve reaches a first preset opening degree and the actual total supply air humidity is still higher than the target total supply air humidity, the isolation distribution component actively increases the number of heat exchange tubes connected to the second passage. Thus, when flow regulation reaches a bottleneck, this application can further enhance dehumidification or cooling capacity by dynamically expanding the physical heat exchange area of ​​the passage. Compared to the fixed-structure coils in related technologies, which can only rely on flow regulation and have a limited adjustment range, this application achieves dual control of chilled water flow rate regulation and heat exchange area regulation, thereby broadening the effective temperature and humidity regulation range of the air handling equipment. Attached Figure Description

[0009] Figure 1 This is a schematic diagram of the air handling equipment provided in an embodiment of this application; Figure 2 This is a flowchart of the control method for the air handling equipment provided in the embodiments of this application; Figure 3 This is provided by the embodiments of this application. Figure 2 The flowchart of step S201 in the text; Figure 4 This is another structural schematic diagram of the air handling equipment provided in the embodiments of this application; Figure 5 This is provided by the embodiments of this application. Figure 2 Flowchart of step S202; Figure 6 This is another flowchart of the control method for the air handling equipment provided in the embodiments of this application; Figure 7 This is provided by the embodiments of this application. Figure 2 Another flowchart for step S202.

[0010] Reference numerals in the attached drawings: Air handling unit 100, main pipe 110, water outlet 111, isolation distribution assembly 120, first regulating valve 131, second regulating valve 132, heat exchange tube 140, first passage 141, second passage 142, fins 150, baffle plate 160, water collection assembly 170, condensate collection pan 180, air inlet 410, return air outlet 420, air outlet 430, fan assembly 440. Detailed Implementation

[0011] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application.

[0012] It should be noted that although functional modules are divided in the device schematic diagram and a logical order is shown in the flowchart, in some cases, the steps shown or described may be performed in a different order than the module division in the device or the order in the flowchart. The terms "first," "second," etc., in the specification, claims, and the aforementioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0013] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing embodiments of this application only and is not intended to limit this application.

[0014] Air handling equipment (such as air conditioners and dehumidifiers) is widely used in various building environments such as clean rooms, large venues and operating rooms. Air handling equipment can partially or completely regulate the temperature, humidity, flow rate and cleanliness of the air, so that the air parameters of the target environment meet the needs of different application scenarios.

[0015] In related technologies, air handling units typically adopt the following structural forms for air temperature and humidity control in different application scenarios: The first is a single-coil system, which uses a single chilled water coil to handle both sensible heat load (cooling) and latent heat load (dehumidification). The airflow is changed by adjusting the flow rate of chilled water through the coil. However, in order to improve the energy efficiency ratio of the central computer room, the chilled water supply temperature tends to be increased. However, excessively high supply water temperature will reduce the dehumidification capacity of the coil, resulting in excessively high indoor humidity. The second is a dual-coil (or dual-duct) system, which sets up two independent ducts in the air handling unit. The two ducts are equipped with cooling coils for dry operation (mainly responsible for cooling) and cooling coils for wet operation (mainly responsible for dehumidification), respectively. Decoupled control of temperature and humidity is achieved by adjusting the air volume of each duct and the water flow rate of the coil. However, this type of equipment is complex in structure, bulky, and requires high initial investment. The ductwork layout occupies a lot of space, and because the size and heat exchange area of ​​the wet coil are fixed during manufacturing, the fixed-ratio hardware structure cannot flexibly adapt when the latent heat load (dehumidification demand) fluctuates drastically in actual operating conditions, resulting in a limited dehumidification adjustment range. The third type is the secondary return air system. This system is mostly used in applications with large-scale air supply demands. Air is cooled and dehumidified by a single cooling coil and then mixed with some indoor return air (secondary return air) to increase the supply air temperature. To achieve secondary return air mixing, the unit needs to add an additional mixing mechanism, resulting in a complex and bulky equipment structure. Furthermore, the state of the mixed air is highly dependent on the precise control of the return air state and the return air mixing ratio. When the indoor heat and humidity load changes rapidly (large fluctuations in operating conditions), the equipment struggles to adapt to load changes, exhibiting delayed response to changing load conditions and poor control accuracy. The fourth type is the single-coil reheat system. This system uses a single cooling coil to cool and dehumidify the air. In order to reach the target supply air temperature, it is often necessary to reheat the dehumidified low-temperature air. This structure has a cooling and heating cancellation phenomenon, resulting in low energy utilization efficiency and high operating energy consumption.

[0016] In summary, air handling equipment in related technologies has significant limitations in terms of temperature and humidity regulation range.

[0017] Based on this, embodiments of this application provide an air handling equipment and its control method and control device, aiming to broaden the adaptability of the air handling equipment to the magnitude of heat and humidity load.

[0018] The air handling equipment and its control method and control device provided in the embodiments of this application are specifically described through the following embodiments. First, the control method of the air handling equipment in the embodiments of this application is described.

[0019] The control method for an air handling device provided in this application relates to the field of air handling technology. The control method for an air handling device provided in this application can be applied to a terminal, a server, or software running on either a terminal or a server. In some embodiments, the terminal can be a smartphone, tablet, laptop, desktop computer, etc.; the server can be configured as an independent physical server, a server cluster or distributed system composed of multiple physical servers, or a cloud server providing basic cloud computing services such as cloud services, cloud databases, cloud computing, cloud functions, cloud storage, network services, cloud communication, middleware services, domain name services, security services, CDN, and big data and artificial intelligence platforms; the software can be an application implementing the control method for the air handling device, but is not limited to the above forms.

[0020] This application can be used in a wide variety of general-purpose or special-purpose computer system environments or configurations. Examples include: personal computers, server computers, handheld or portable devices, tablet devices, multiprocessor systems, microprocessor-based systems, set-top boxes, programmable consumer electronics, network PCs, minicomputers, mainframe computers, and distributed computing environments including any of the above systems or devices. This application can be described in the general context of computer-executable instructions executed by a computer, such as program modules. Generally, program modules include routines, programs, objects, components, data structures, etc., that perform specific tasks or implement specific abstract data types. This application can also be practiced in distributed computing environments where tasks are performed by remote processing devices connected via a communication network. In distributed computing environments, program modules can reside in local and remote computer storage media, including storage devices.

[0021] The control method for the air handling equipment in this application embodiment is applied to the air handling equipment, which includes a main pipeline, an isolation and distribution component, a regulating component, and multiple independent heat exchange tubes. The main pipeline is a conduit for transporting fluid media such as chilled water, and has multiple outlets connected to it. These outlets are used to distribute the fluid in the main pipeline to each heat exchange tube.

[0022] An isolation distribution component is located inside the main pipeline and can isolate the main pipeline into a first passage and a second passage in the water flow direction. The isolation distribution component can slide or be fixed within the main pipeline according to control commands, dynamically adjusting the number of heat exchange tubes connected to the first and second passages, thereby changing the effective heat exchange area of ​​the first and second passages. Simultaneously, it adjusts the water flow rate distributed to different passages within the main pipeline. The isolation distribution component can be a piston mechanism, which can be manually or electrically adjusted in position within the main pipeline. For example, it can move towards the first passage to increase the number of heat exchange tubes connected to the first passage, naturally reducing the number of heat exchange tubes connected to the second passage. Conversely, when the piston mechanism moves towards the second passage, it reduces the number of heat exchange tubes connected to the first passage and relatively increases the number of heat exchange tubes connected to the second passage. In this embodiment, one passage is primarily responsible for cooling, and the other for dehumidification. The first passage is configured to primarily cool, and the second passage is configured to primarily dehumidify.

[0023] The regulating assembly includes a first regulating valve and a second regulating valve. The first regulating valve is located at the water inlet of the first passage, and the second regulating valve is located at the water inlet of the second passage. The first and second regulating valves control the water flow rate through each passage, thereby affecting the heat exchange effect and outlet air temperature of the corresponding passage. The first and second regulating valves can be electrically operated or pneumatically operated, changing their opening degree by receiving temperature control signals from sensors, thus controlling the chilled water flow rate through their respective passages. Alternatively, in other embodiments, other structures can replace the regulating valves, such as variable frequency water pumps installed on the pipelines of each passage, directly changing the chilled water flow rate through that passage by adjusting the motor speed of the water pump.

[0024] Heat exchange tubes are components in air handling equipment that enable heat and moisture exchange between air and a fluid medium (such as chilled water). Each heat exchange tube can include several independent tubular heat exchange units arranged in parallel within the airflow channel, such as a serpentine coil or U-shaped tube loop composed of multiple copper tubes connected by bends. Each heat exchange tube has an independent inlet and outlet. The multiple outlets of the main pipe are connected one-to-one with the inlets of the multiple heat exchange tubes, forming a heat exchange loop. Optionally, heat transfer is isolated between each pair of adjacent heat exchange tubes by a partition, effectively preventing thermal crosstalk between the first and second flow paths during heat exchange, ensuring that the airflow responsible for deep dehumidification and the airflow responsible for sensible heat cooling remain independent, and guaranteeing the dehumidification efficiency of the second flow path.

[0025] In some embodiments, please refer to Figure 1 , Figure 1 This is a schematic diagram of the air handling equipment provided in an embodiment of this application, as shown below. Figure 1As shown, the air handling unit 100 includes a main pipe 110, an isolation and distribution assembly 120, and multiple independent heat exchange tubes 140. The main pipe 110 has multiple water outlets 111 communicating with its interior. The multiple water outlets 111 of the main pipe 110 are connected one-to-one to the water inlet 143 of the multiple heat exchange tubes 140. The isolation and distribution assembly 120 is located on the main pipe 110 to isolate the main pipe 110 into a first passage 141 and a second passage 142. The isolation and distribution assembly 120 can adjust the number of heat exchange tubes 140 communicating with the first passage 141 and the second passage 142. The adjustment assembly includes a first regulating valve 131 and a second regulating valve 132. The first regulating valve 131 is located at the water inlet of the first passage 141 (i.e., the water inlet 143 of the heat exchange tube 140 communicated by the first passage 141), and the second regulating valve 132 is located at the water inlet of the second passage 142 (i.e., the water inlet 143 of the heat exchange tube 140 communicated by the second passage 142). Among them, the heat exchange tube 140 adopts a coil structure with 4 to 6 rows. Figure 1 There are 4 rows in the middle. Figure 1 The air handling unit 100 is equipped with five heat exchange tubes 140. An isolation and distribution assembly 120 divides the five heat exchange tubes 140 into two pathways: the upper pathway is the first pathway 141, and the lower pathway is the second pathway 142. The chilled water inlet flow rates of the first pathway 141 and the second pathway 142 can be automatically adjusted by the controller based on temperature sensor signals from the corresponding first regulating valve 131 and second regulating valve 132. Each heat exchange tube 140 has multiple fins 150 inserted into it. The number of fins 150 on the multiple heat exchange tubes 140 is the same and they are aligned. The fins 150 of any two heat exchange tubes 140 can be connected or disconnected; when disconnected, they can be separated by a partition 160. A condensate collection tray 180 is also provided at the bottom of the air handling unit 100 to collect condensate generated during the dehumidification process.

[0026] Please refer to Figure 2 , Figure 2 This is an optional flowchart of the control method for the air handling equipment provided in the embodiments of this application. Figure 2 The method may include, but is not limited to, steps S201 to S204.

[0027] Step S201: Obtain the target total supply air temperature and target total supply air humidity of the air handling unit; Step S202: Determine the second target air outlet temperature of the second passage based on the preset total air volume, target total air temperature and target total air humidity, and determine the first target air outlet temperature of the first passage based on the target total air temperature and the second target air outlet temperature. Step S203: Adjust the opening of the first regulating valve so that the outlet air temperature of the first passage reaches the first target outlet air temperature, and adjust the opening of the second regulating valve so that the outlet air temperature of the second passage reaches the second target outlet air temperature. In step S204, when the opening degree of the second regulating valve reaches the first preset opening degree and the actual total supply air humidity of the air handling equipment is higher than the target total supply air humidity, the control isolation distribution component increases the number of heat exchange tubes connected to the second passage.

[0028] Steps S201 to S204 of this application embodiment divide the main pipeline into a first passage and a second passage through an isolation distribution component. Combined with a first regulating valve and a second regulating valve respectively installed at the water inlet of the two passages, independent regulation of the chilled water flow rate in the heat exchange tubes connected to different passages is achieved to meet basic temperature and humidity control requirements. Furthermore, when the opening degree of the second regulating valve reaches the first preset opening degree and the actual total supply air humidity is still higher than the target total supply air humidity, the isolation distribution component actively increases the number of heat exchange tubes connected to the second passage. In this way, when the flow regulation reaches a bottleneck, this application can further improve the dehumidification or cooling capacity by dynamically expanding the physical heat exchange area of ​​the passage. Compared with the fixed structure coil in the related technology, which can only rely on flow regulation and has a limited regulation range, this application realizes dual control of chilled water flow regulation and heat exchange area regulation, thereby broadening the effective regulation range of temperature and humidity of the air handling equipment.

[0029] In step S201 of some embodiments, the target total supply air temperature and target total supply air humidity represent the final supply air state parameters that the mixed air state parameters output from the total outlet of the air handling unit need to achieve in order to make the controlled environment (such as an indoor room) reach the expected comfort or process requirements. That is, the supply air state parameters that the first and second paths need to work together to achieve. The target total supply air temperature and target total supply air humidity under the current operating conditions of the air handling unit can be obtained first. These can be obtained by receiving values ​​set by the user on the control panel, or by the host computer system calculating them using a built-in PID algorithm or fuzzy control algorithm based on the deviation between the actual return air temperature and humidity in the room and the set values. The target total supply air temperature and target total supply air humidity can refer to the target total supply air temperature and target total supply air humidity of the airflow output after passing through multiple heat exchange tubes.

[0030] In some embodiments, please refer to Figure 3 Obtaining the target total supply air temperature and target total supply air humidity of the air handling unit includes the following steps S301 to S304: Step S301: Obtain the return air temperature and the target temperature, and calculate the temperature deviation between the return air temperature and the target temperature; Step S302: Correct the total supply air temperature set in the previous round according to the temperature deviation to obtain the target total supply air temperature; Step S303: Obtain the return air humidity and the target humidity, and calculate the humidity deviation between the return air humidity and the target humidity; Step S304: Correct the total supply air humidity set in the previous round according to the humidity deviation to obtain the target total supply air humidity.

[0031] Before introducing this embodiment, please refer to Figure 4 , Figure 4 This is another structural schematic diagram of the air handling equipment provided in the embodiments of this application, such as... Figure 4 As shown, the left side is the air intake side (mixing fresh and return air), the middle is the processing section, and the right side is the air supply side. Air enters from the left, passes through the heat exchange tube in the middle, mixes, and is then sent into the room through the air outlet 430 on the right. Fresh outdoor air enters through the air inlet 410 (i.e., the fresh air inlet), and indoor recirculated air enters through the return air inlet 420. The two mix to form humid air to be processed. The return air temperature sensor and return air humidity sensor are located at the leftmost return air inlet 420 to collect the current actual state of the room.

[0032] In step S301 of some embodiments, the return air temperature and the target temperature can be obtained, and the temperature deviation between the return air temperature and the target temperature can be calculated. As described above, Figure 4 The return air temperature can be obtained in real time by a return air temperature sensor installed at the return air vent 420 of the air handling unit or in the return air duct. The target temperature can be set by the user according to actual needs, and the temperature deviation is usually calculated as the difference between the return air temperature and the target temperature.

[0033] In step S302 of some embodiments, the target total supply air temperature can be adjusted according to a preset time frequency, such as updating it every half hour or hour, to ensure that the air handling equipment has sufficient reaction time to achieve the target total supply air temperature. Therefore, the total supply air temperature set in the previous round can be corrected according to the temperature deviation calculated in the aforementioned steps to obtain the target total supply air temperature. Specifically, a return air temperature higher than the target temperature indicates that there is residual heat in the room, so the total supply air temperature set in the previous round can be reduced to control the air handling equipment to deliver colder air to offset the heat load. For example, if the measured room temperature is 30°C, the target room temperature is 24°C, and the supply air temperature is 22°C, since the room temperature is higher than the target temperature, it means that the supply air temperature is still too high. At this time, either the supply air volume should be increased or the supply air temperature should be reduced. This application assumes that the supply air volume remains unchanged, so the supply air temperature needs to be reduced. A return air temperature lower than the target temperature indicates that the room is too cold, so the total supply air temperature set in the previous round can be increased to reduce the cooling output of the air handling equipment. The adjustment range of the target total supply air temperature is positively correlated with the absolute value of the temperature deviation. That is, when the indoor temperature deviates significantly from the set value (large absolute value of temperature deviation), the supply air temperature can be adjusted significantly to quickly approach the target value; while when the indoor temperature is close to the set value (small absolute value of temperature deviation), a small adjustment can be made to achieve fine control.

[0034] In step S303 of some embodiments, the return air humidity and the target humidity can be acquired, and the humidity deviation between the return air humidity and the target humidity can be calculated. As described above, the return air humidity can be acquired in real time by a return air humidity sensor installed in the return air vent or return air duct of the air handling unit. The target humidity can be an ideal indoor humidity value set by the user according to actual needs, and the humidity deviation is usually calculated as the difference between the return air humidity and the target humidity.

[0035] In step S304 of some embodiments, the total supply air humidity set in the previous round can be corrected based on the humidity deviation to obtain the target total supply air humidity. Specifically, if the return air humidity is higher than the target humidity, it indicates that the indoor environment is too humid, so the total supply air humidity set in the previous round can be reduced (i.e., a lower moisture content target can be set) to accelerate the convergence of the ambient humidity to the target value; if the return air humidity is lower than the target humidity, the total supply air humidity set in the previous round can be increased. The adjustment range of the target total supply air humidity is positively correlated with the absolute value of the humidity deviation, thus ensuring that the air handling equipment can dynamically match the optimal dehumidification or humidification intensity according to the actual fluctuation of the moisture load.

[0036] This application embodiment calculates the deviation between the return air parameters and the target temperature and humidity, and dynamically corrects the previously set total supply air temperature and humidity based on the deviation to generate a new total supply air temperature and humidity. In this way, the air handling equipment can quickly respond to changes in environmental load and adjust the supply air parameters in a timely manner.

[0037] In step S202 of some embodiments, the second target outlet air temperature of the second passage can then be determined based on the preset total air volume, target total air volume temperature, and target total air volume humidity. Cleanrooms and similar applications typically require a large air volume to remove dust particles through HEPA filters; in this case, a fixed preset total air volume value can be used. For other applications, such as variable air volume systems, the total air volume can be obtained through real-time measurement. The second passage is responsible for latent heat treatment (dehumidification), so the required second target outlet air temperature for the second passage to achieve the target dehumidification effect can be calculated based on the target total air volume humidity. While ensuring the dehumidification capacity of the second passage, since the second passage cools down while dehumidifying, some of the cold energy generated by the second passage can be removed through the first passage. The second target outlet air temperature represents the required outlet air temperature setpoint for the second passage, which is typically lower than the dew point temperature to facilitate moisture condensation.

[0038] After determining the second target air outlet temperature of the second passage, the first target air outlet temperature of the first passage (responsible for sensible heat treatment (cooling)) can be calculated according to the thermodynamic balance principle of air mixing. The first target air outlet temperature represents the set value of the air outlet temperature that the first passage needs to achieve. It is used as a supplementary adjustment variable to maintain the balance of the total supply air temperature, thereby ensuring that the state of the air after mixing in the first and second passages can accurately meet the requirements of the target total supply air temperature.

[0039] In some embodiments, please refer to Figure 5 The second target outlet air temperature of the second passage is determined based on the preset total supply air volume, target total supply air temperature, and target total supply air humidity, including the following steps S501 to S504: Step S501: Calculate the second flow rate corresponding to the second passage based on the preset total air volume, the number of first heat exchange tubes corresponding to the first passage, and the number of second heat exchange tubes corresponding to the second passage. Step S502: Calculate the moisture content of the second outlet air corresponding to the second passage based on the target total dehumidification capacity, the moisture content of the mixed air after the intake and return air are mixed, and the second flow volume. Step S503: Determine the corresponding second target outlet dry bulb temperature based on the preset outlet relative humidity and the second outlet moisture content of the second passage. Step S504: Obtain the chilled water inlet temperature and the preset minimum heat transfer temperature difference at the water inlet end, and calculate the second target outlet temperature of the second passage based on the chilled water inlet temperature, the minimum heat transfer temperature difference, the second target outlet dry bulb temperature, and the target total supply air temperature.

[0040] In step S501 of some embodiments, as described above, the air handling equipment provided in this application dynamically divides multiple parallel heat exchange tubes into two paths based on an isolation distribution component. All heat exchange tubes share the same air duct cross-section, so the airflow through each heat exchange tube can be considered uniform. Furthermore, since the flow resistance characteristics of each heat exchange tube are similar, the airflow through each path can be distributed according to the proportion of the number of heat exchange tubes it connects to to the total number of heat exchange tubes. Specifically, the position of the isolation distribution component in the main duct can be obtained first to determine the number of second heat exchange tubes in the second path and the number of first heat exchange tubes in the first path. Then, the proportion of the number of second heat exchange tubes to the total number of heat exchange tubes is calculated. Based on the calculated proportion and the preset total airflow, the airflow through the second path, i.e., the second airflow, can be calculated. The expression for calculating the second airflow is as follows: (1) in, This indicates the total air volume supplied by the air handling unit. Indicates the number of the second heat exchange tubes. Indicates the number of the first heat exchange tubes. This indicates the second flow rate through the second passage.

[0041] In step S502 of some embodiments, the second outlet air humidity corresponding to the second passage can be calculated based on the target total dehumidification capacity, the humidity of the mixed air after the intake and return air are mixed, and the second flow rate. The target total dehumidification capacity is the total mass of moisture that the air handling equipment needs to remove from the air in the target environment, calculated based on the indoor return air status and the target humidity. The mixed air humidity refers to the initial moisture content before the fresh air and return air enter the heat exchange coil after being mixed. Combining the two with the second flow rate of the second passage, the outlet air humidity required by the second passage can be calculated, i.e., the second outlet air humidity. This ensures that the air handling equipment can meet the set target total dehumidification capacity. The calculation method of the target total dehumidification capacity will be introduced next.

[0042] In some embodiments, please refer to Figure 6 Before calculating the moisture content of the second outlet air corresponding to the second passage based on the target total dehumidification capacity, the moisture content of the mixed air after the intake and return air are mixed, and the second flow rate, the control method of the air handling equipment provided in this application embodiment further includes the following steps S601 to S604: Step S601: Obtain the intake air volume and calculate the intake air volume ratio based on the intake air volume and the preset total air supply volume; Step S602: Obtain the return air humidity determined by the return air temperature and return air humidity, and obtain the inlet air humidity determined by the inlet air temperature and inlet air humidity. Step S603: Calculate the moisture content of the mixed air after the intake and return air are mixed based on the intake air volume ratio, return air moisture content, and intake air moisture content. Step S604: Calculate the target total dehumidification capacity based on the intake air moisture content, total supply air volume, and the target air moisture content determined by the target total supply air temperature and target total supply air humidity.

[0043] In step S601 of some embodiments, during actual operation, the air handling equipment usually needs to introduce fresh air to ensure indoor air quality. At this time, accurately determining the moisture content of the mixed air after the intake and return air are mixed and the target total dehumidification is crucial for achieving precise temperature and humidity control.

[0044] Before introducing this embodiment, the structure of the air handling equipment provided in this application will be further described. Please refer to... Figure 4 The air handling equipment 100 provided in this application also includes a housing, which provides structural support and protection for the equipment and defines the space for airflow. The housing has an air inlet 410 and an air outlet 430, and a heat exchange duct is formed between the air inlet 410 and the air outlet 430. Multiple heat exchange tubes 140 are disposed in the heat exchange duct. The air inlet 410 is used to draw in air to be conditioned, and the air outlet 430 is used to discharge the conditioned air from the air handling equipment. The heat exchange duct is the area where air flows through the heat exchange tubes for heat and humidity exchange. Multiple heat exchange tubes are disposed at corresponding positions in the heat exchange duct of the housing, usually arranged in an array to maximize the contact area with the air and achieve efficient energy transfer. An air inlet temperature sensor and an air inlet humidity sensor are respectively disposed near the air inlet 410 for measuring the air inlet temperature and air inlet humidity, and an air supply temperature sensor and an air supply humidity sensor are respectively disposed near the air outlet 430 for measuring the total supply air temperature and total supply air humidity.

[0045] Alternatively, please refer to Figure 4 The casing contains a fan assembly 440. The air inlet of the fan assembly 440 faces multiple heat exchange tubes 140, and the air outlet of the fan assembly 440 faces the air outlet of the casing. This allows the air, after heat / moisture exchange through the multiple heat exchange tubes 140, to be delivered from the air outlet 430 via the fan assembly 440. The target total supply air temperature and target total dehumidification capacity refer to the temperature and humidity of the air output from the air outlet 430 of the casing.

[0046] Specifically, the intake air volume can be obtained first. The intake air volume can be measured in real time by an air volume sensor installed at the air inlet. Then, the intake air volume ratio can be calculated based on the intake air volume and the preset total air supply volume.

[0047] In step S602 of some embodiments, since the sensor typically reads relative humidity directly, the measured return air temperature and humidity and inlet air temperature and humidity can be converted into corresponding moisture content values ​​using an air enthalpy-humidity chart. This allows the acquisition of the absolute moisture content for both return and inlet air. Specifically, the return air moisture content determined by the return air temperature and humidity can be obtained. The return air temperature and humidity can be collected in real-time by the aforementioned sensor, and the corresponding return air moisture content can be found using an air enthalpy-humidity chart. Similarly, the inlet air moisture content determined by the inlet air temperature and humidity can be obtained. The inlet air temperature and humidity can be collected in real-time by the aforementioned sensor, and the corresponding inlet air moisture content can be converted using an air enthalpy-humidity chart. In step S603 of some embodiments, the moisture content of the mixed air after the intake and return air are mixed can be calculated based on the inlet air volume ratio, return air moisture content, and inlet air moisture content. This allows for the simulation and calculation of the physical mixing process of the air before it enters the heat exchange duct. As described above, the airflows from the inlet and outlet converge before entering the heat exchange duct containing the heat exchange tubes. According to the law of conservation of mass, the state of the mixed air depends on the mixing ratio of the two airflows. Therefore, the moisture content of the mixed air can be calculated using the weighted average formula based on the proportion of the inlet and outlet airflows obtained in the aforementioned steps. The moisture content of the mixed air characterizes the initial moisture state of the air before it flows through the heat exchange tubes. In this way, this application can combine the actual proportions and moisture contents of air from different sources to ensure the accuracy of the obtained mixed air state. The expression for calculating the moisture content of the mixed air is as follows: (2) in, This indicates the moisture content of the mixed air after the intake and return air are combined. Indicated by return air temperature and return air humidity The determined moisture content of the return air. Indicates the intake air temperature and intake air humidity Determined intake air moisture content. This indicates the percentage of incoming air volume.

[0048] In step S604 of some embodiments, the target total dehumidification capacity can be calculated based on the inlet air moisture content, the total supply air volume, and the target air moisture content determined by the target total supply air temperature and target total supply air humidity. Specifically, the target air moisture content that the airflow of the air handling unit should achieve can first be determined based on the target total supply air temperature and target total supply air humidity in an enthalpy-humidity diagram. Then, the total mass of water removed from the air required to change the air from a mixed state to the target state, i.e., the target total dehumidification capacity, is calculated by combining the air density and the total supply air volume. The expression for calculating the target total dehumidification capacity is as follows: (3) in, This indicates the target total dehumidification capacity. This represents the density of air, approximately 1.2 kg / m³. This indicates the moisture content of the mixed air after the intake and return air are combined. Indicates the total supply air temperature as a result and target total supply air humidity The target air humidity level is determined.

[0049] This application's embodiments can accurately acquire the proportion of intake air volume, return air humidity, and intake air humidity when fresh air is introduced into the air handling unit. Based on this real-time data, the humidity of the mixed air after the intake and return air are mixed is accurately calculated. Furthermore, combined with the target total air supply status, the target total dehumidification capacity is accurately calculated, effectively solving the problem of difficulty in accurately determining the mixed air state and required dehumidification capacity when fresh air is introduced. Thus, the air handling unit of this application can more accurately adjust the operating parameters of each channel according to the actual air mixing state and precise target dehumidification requirements, thereby achieving precise control of the total supply air temperature and humidity. This avoids over-dehumidification or under-dehumidification due to inaccurate parameter calculations, especially in scenarios requiring frequent fresh air introduction to meet indoor air quality requirements, where the control effect of this application is even more significant.

[0050] In some embodiments, the calculation of the second outlet air humidity corresponding to the second passage based on the target total dehumidification capacity, the moisture content of the mixed air after the intake and return air are mixed, and the second flow rate includes the following steps: Calculate the product of the second flow rate and the air density, and calculate the ratio between the target total dehumidification capacity and the product; Determine the difference between the moisture content and ratio of the mixed air after the intake and return air are mixed, and determine the moisture content of the second outlet air corresponding to the second passage based on the difference.

[0051] In this embodiment, the product of the second flow rate and the air density can be calculated first, where the air density can be taken as 1.2 kg / m³. The product of the two can represent the mass flow rate of dry air flowing through the second passage per unit time. In this way, the total dehumidification capacity required by the air handling equipment can be converted into the amount of moisture that needs to be removed from the heat exchange tubes corresponding to the second passage per unit mass of air.

[0052] Then, the ratio between the target total dehumidification capacity and the above product can be calculated. This ratio reflects the moisture content reduction that the air passing through the heat exchange tubes of the second path needs to achieve in order to complete the total dehumidification task. Further, this can be achieved by determining the intake air (i.e., from...) Figure 4 The air entering the air handling unit through the air inlet 410 and the return air (i.e., from the air inlet 410) Figure 4 The difference between the moisture content of the mixed air (air entering the air handling unit through the return air inlet 420) and the aforementioned ratio is used to determine the moisture content of the second outlet air corresponding to the second passage. The second outlet air moisture content represents the moisture content that the outlet air of the second passage should reach after completing its dehumidification task. The calculation expression for the second outlet air moisture content is as follows: (4) in, This indicates the target total dehumidification capacity of the air handling unit. This indicates the second flow rate corresponding to the second passage. Indicates air density, This indicates the moisture content of the mixed air after the intake and return air are combined. This indicates the moisture content of the second outlet air corresponding to the second passage.

[0053] This application embodiment calculates the ratio of the target total dehumidification capacity to the mass flow rate of air in the second passage, quantifying the overall dehumidification demand into a dehumidification load per unit mass of air. Based on this, the moisture content of the mixed air after the intake and return air are subtracted from this ratio to determine the moisture content of the second outlet air corresponding to the second passage. This calculation method avoids complex iterations or empirical estimations, ensuring that the outlet air moisture content of the second passage accurately matches the actual dehumidification demand, thereby improving the control accuracy and response speed of the air handling equipment when achieving the target total supply air humidity. Thus, this application embodiment can stably and efficiently provide the required supply air humidity, especially when handling different intake conditions and target humidity requirements, providing a more reliable dehumidification control strategy.

[0054] In step S503 of some embodiments, in practical applications, after the air is cooled and dehumidified by the cooling coil, it is usually in a near-saturated state. To ensure the comfort of the outlet air and avoid excessive dehumidification, a preset outlet relative humidity value (e.g., 95%) can be used as a benchmark. Based on the physical properties of humid air, given the absolute moisture content and outlet relative humidity, the corresponding dry-bulb temperature can be uniquely determined through an air enthalpy-humidity chart. Therefore, by combining the preset outlet relative humidity and the absolute moisture content calculated in the aforementioned steps (i.e., the second outlet moisture content), the second target outlet dry-bulb temperature corresponding to the second passage can be found on the humid air enthalpy-humidity chart. The second target outlet dry-bulb temperature represents the temperature value to which the air must be cooled to achieve the target moisture content. In this way, it can be ensured that the outlet air of the second passage meets the dehumidification requirements while also conforming to the preset air comfort standard.

[0055] In step S504 of some embodiments, the chilled water inlet temperature and the preset minimum heat transfer temperature difference can be obtained, and the second target outlet air temperature of the second passage can be calculated based on the chilled water inlet temperature, the minimum heat transfer temperature difference, and the target total supply air humidity. The minimum heat transfer temperature difference can characterize the minimum temperature difference between the second target outlet air temperature of the second passage and the chilled water temperature. The minimum heat transfer temperature difference can be set to 2°C, and is not limited here.

[0056] The chilled water inlet temperature limits the lowest temperature that the heat exchange tube surface can reach. Therefore, the outlet air temperature cannot be reduced indefinitely, affecting the actual heat exchange effect. This embodiment introduces the chilled water inlet temperature and the minimum heat transfer temperature difference as the physical lower limit of the outlet air temperature of the second path. This allows for the verification and correction of the previously determined second target outlet dry-bulb temperature, resulting in a second target outlet air temperature achievable under actual heat exchange capacity, ensuring that the set second target outlet air temperature is reasonable and attainable. Specifically, the calculated outlet air temperature corresponding to the second path can be compared with a preset lower limit, and the final second target outlet air temperature is determined based on the larger of the two. Thus, this embodiment satisfies dehumidification requirements as much as possible without being unable to achieve the desired temperature due to setting an outlet air temperature target lower than the chilled water temperature. The calculation expression for the second target outlet air temperature is as follows: (5) in, This indicates the real-time measured temperature of the chilled water inlet. Indicates the minimum heat transfer temperature difference. This indicates the dry bulb temperature of the second target air outlet. This indicates the target total supply air temperature of the air handling unit.

[0057] This application embodiment precisely quantifies the dehumidification task into corresponding temperature and humidity indicators, and combines this with the actual physical operating boundaries of the air handling equipment (such as airflow distribution ratio and chilled water temperature limits) to verify and optimize the second target outlet air temperature. This calculates a feasible temperature control target for the second path, ensuring that the set second target outlet air temperature is achievable within the actual heat exchange capacity range. Thus, the air handling equipment of this application can more accurately control the total supply air temperature and humidity, avoiding insufficient or excessive dehumidification due to inaccurate target outlet air temperature settings, and preventing energy waste caused by setting values ​​exceeding physical limits.

[0058] In some embodiments, please refer to Figure 7 The first target outlet air temperature of the first passage is determined based on the target total supply air temperature and the second target outlet air temperature, including the following steps S701 to S703: Step S701: Calculate the first flow rate corresponding to the first passage based on the preset total air volume, the number of first heat exchange tubes corresponding to the first passage, and the number of second heat exchange tubes corresponding to the second passage. Step S702: Calculate the first target outlet dry bulb temperature corresponding to the first passage based on the first flow volume, the second flow volume, the second target outlet air temperature, and the target total supply air temperature. Step S703: Calculate the first target outlet air temperature corresponding to the first passage based on the chilled water inlet temperature, minimum heat transfer temperature difference, first target outlet dry bulb temperature, and target total supply air temperature.

[0059] In step S701 of some embodiments, the first flow rate corresponding to the first passage is calculated based on the preset total air volume, the number of first heat exchange tubes corresponding to the first passage, and the number of second heat exchange tubes corresponding to the second passage. As described above, the first and second passages share the same air inlet cross-section, and the air handling equipment assumes that the air volume is uniformly distributed across the coil cross-section. Therefore, the first flow rate can be obtained by multiplying the ratio of the number of first heat exchange tubes to the total number of heat exchange tubes in the first and second passages by the preset total air volume. The expression for calculating the first flow rate is as follows: (6) in, This indicates the first airflow volume corresponding to the first passage. This indicates the preset total air volume. Indicates the number of the first heat exchange tubes. This indicates the number of the second heat exchange tubes.

[0060] In step S702 of some embodiments, since the total air volume is the sum of the air volumes flowing through the first and second passages, and the total air supply temperature is the result of mixing the outlet temperatures of the two passages, the first target outlet dry-bulb temperature corresponding to the first passage can be calculated through the reverse solution process of the energy balance principle. Because the second passage has already processed some air to a lower second target outlet temperature for dehumidification, to prevent the total air supply temperature from being too low, the first passage needs to provide relatively high-temperature air for thermal neutralization (or temperature compensation) so that the two airflows mix to precisely reach the set target total air supply temperature.

[0061] In step S703 of some embodiments, the first target outlet air temperature corresponding to the first passage can be calculated based on the chilled water inlet temperature, the minimum heat transfer temperature difference, the first target outlet dry-bulb temperature, and the target total supply air temperature. The chilled water inlet temperature is the lowest cooling temperature that the heat exchanger tube can provide, while the minimum heat transfer temperature difference reflects the minimum temperature difference that can be achieved between the chilled water and air during actual operation. Although the previous step calculates the theoretical temperature, actual control needs to consider the hardware limits of the air handling equipment. Specifically, the chilled water inlet temperature and a preset minimum heat transfer temperature difference (e.g., 2°C) can be obtained to determine the lowest physically achievable cooling temperature of the first passage. Then, the theoretically calculated first target dry-bulb temperature can be compared with this physical lower limit (usually taking the larger value), and combined with the constraints of the target supply air state (e.g., the upper limit does not exceed the total supply air temperature setting), to finally determine the executable first target outlet air temperature. Thus, the embodiments of this application can ensure that the issued control commands meet both the mixed temperature and humidity requirements and are within the actual operating capacity range of the heat exchanger.

[0062] This application, based on the overall target supply air temperature and the operating parameters of the second path, determines the first target outlet dry-bulb temperature required by the first path through energy balance calculations, ensuring the synergy of temperature control between the first and second paths. Then, considering actual heat exchange conditions such as chilled water inlet temperature, minimum heat transfer temperature difference, and target total supply air humidity, the first target outlet dry-bulb temperature is corrected and optimized to calculate the actually achievable first target outlet temperature. Thus, this application can fully consider the overall supply air target and equipment physical limitations when controlling the supply air temperature of the first path, avoiding overall supply air temperature deviations or low equipment operating efficiency caused by improper temperature settings in a single path. Ultimately, the embodiments of this application can ensure that the air handling equipment accurately and stably outputs air that meets the target total supply air temperature and target total supply air humidity, improving control accuracy and energy utilization efficiency, and ensuring indoor environmental comfort.

[0063] In step S203 of some embodiments, after calculating the first target air outlet temperature corresponding to the first passage and the second target air outlet temperature corresponding to the second passage through the aforementioned steps, the opening of the first regulating valve can be adjusted to make the air outlet temperature of the first passage reach the first target air outlet temperature, and the opening of the second regulating valve can be adjusted to make the air outlet temperature of the second passage reach the second target air outlet temperature. The opening of the regulating valve can be controlled by a PID controller, which outputs a corresponding control signal to adjust the valve opening based on the deviation between the actual air outlet temperature and the target air outlet temperature. Alternatively, a simple open-loop control can be used, that is, the valve opening can be directly set according to a preset correspondence between the valve opening and the air outlet temperature. Specifically, increasing the opening of the first regulating valve can decrease the air outlet temperature of the first passage, and decreasing the opening of the first regulating valve can increase the air outlet temperature of the first passage. Increasing the opening of the second regulating valve can decrease the air outlet temperature of the second passage, and decreasing the opening of the second regulating valve can increase the air outlet temperature of the second passage. The two regulating valves are independent of each other, ensuring that the chilled water flow rate through the first passage only needs to meet the sensible heat cooling requirement, while the chilled water flow rate through the second passage can meet the deep dehumidification requirement, thus avoiding the cooling and heating cancellation phenomenon caused by excessive dehumidification and reheating in traditional single-coil systems.

[0064] In step S204 of some embodiments, when the opening degree of the second regulating valve reaches the first preset opening degree and the actual total supply air humidity of the air handling unit is higher than the target total supply air humidity, the isolation distribution component is controlled to increase the number of heat exchange tubes connected to the second passage. For example, if the opening degree of the second regulating valve has reached its maximum opening degree or is close to its maximum opening degree (assuming the first preset opening degree is 95%), it indicates that the second target outlet air temperature corresponding to the second passage has reached the lower limit. If the actual total supply air humidity output by the air handling unit still fails to meet the target requirement at this time, it indicates that the current dehumidification capacity of the second passage is insufficient. At this time, the control system can send a command to the isolation distribution component to switch some of the heat exchange tubes originally allocated to the first passage to the second passage, thereby increasing the heat exchange area and dehumidification capacity of the second passage, thereby improving the ability to cope with extreme humidity loads without changing the total hardware resources.

[0065] This application achieves dynamic allocation of the number of heat exchange tubes in the first and second passages by moving the isolation distribution component within the main pipeline. This allocation essentially restructures the physical architecture of the air handling equipment, representing a coarse adjustment of its air handling capacity. When faced with significant changes in latent and sensible heat loads, such as a substantial increase in latent heat load and a decrease in sensible heat load, traditional fixed-structure coils, limited by their fixed heat exchange area, cannot achieve the target dehumidification effect even with maximum chilled water flow; that is, there is a physical upper limit to dehumidification capacity. This application, by controlling the isolation distribution component to change the ratio of the number of heat exchange tubes in the first and second passages, increases the heat exchange area of ​​the second passage responsible for dehumidification. Thus, the embodiments of this application can alter the basic heat exchange characteristics of the air handling equipment, adjusting the baseline range of its sensible and latent heat handling capacity, thereby covering extreme load conditions that traditional fixed structures cannot reach. Therefore, the heat exchange area adjustment function of the isolation distribution component provides the equipment with an operating range that matches the current load characteristics, solving the problem that a single structure cannot simultaneously adapt to large-scale changes in sensible heat ratio.

[0066] Based on the heat exchange area allocation of the first and second passages by the isolation distribution component, the first and second regulating valves continuously adjust the chilled water flow rate through their respective passages to achieve fine-tuning of the supply air temperature. Since the isolation distribution component has already adjusted the heat exchange area to match the current load characteristics, the regulating valves do not need to operate in extreme states such as fully open or slightly open. The first regulating valve precisely meets the cooling requirement of the first passage by controlling the flow rate, and the second regulating valve precisely meets the dehumidification requirement of the second passage by controlling the flow rate. The continuous variability of the flow rate fills the capacity gap between discrete changes in the number of heat exchange tubes, ensuring that the output supply air parameters can be accurately and stably maintained at the set value under the selected heat exchange area ratio.

[0067] Thus, this embodiment of the application uses the isolation distribution component to adjust the heat exchange area, thereby coarsely adjusting the temperature and humidity range of the air handling unit. This overcomes the physical limitations of a fixed coil structure, allowing the effective working area of ​​the air handling unit to flexibly switch between sensible heat treatment and latent heat treatment. Simultaneously, it combines this with the regulating valve to adjust the chilled water flow rate for precise temperature and humidity adjustment within each working area. In this way, the air handling unit can adapt to a wide range of temperature and humidity settings by changing its hardware configuration, while maintaining control precision through flow rate fine-tuning. Even under extreme and complex conditions such as high airflow or high humidity and low heat in cleanrooms, it can maintain independent and decoupled temperature and humidity control without introducing reheat energy, thus broadening the effective temperature and humidity adjustment range and applicable scenarios of the air handling unit.

[0068] In some embodiments, the method provided in this application further includes the following steps: When the actual supply air temperature corresponding to the second passage is higher than the return air dew point temperature, and the opening degree of the second regulating valve is greater than the second preset opening degree, the control isolation distribution component reduces the number of heat exchange tubes connected to the second passage.

[0069] In this embodiment, it can be detected whether the actual supply air temperature corresponding to the second passage is higher than the return air dew point temperature, and whether the opening degree of the second regulating valve is greater than the second preset opening degree. The return air dew point temperature represents the critical temperature at which moisture begins to precipitate from the air. If the actual supply air temperature of the second passage is higher than the return air dew point temperature, ensuring the surface temperature of the heat exchange tubes is not low enough, water vapor in the air cannot condense. At this time, the heat exchange tubes corresponding to the second passage are not dehumidifying at all, but only performing sensible heat cooling. If the opening degree of the second regulating valve has exceeded the second preset opening degree (e.g., 95% or close to fully open), it indicates that the chilled water flow rate has reached its upper limit, and increasing the chilled water flow rate will no longer improve the dehumidification effect. The reason for the above detection results may be that the second passage is allocated too many heat exchange tubes, the heat exchange area is too large, and the airflow is too large, causing the heat load to exceed the maximum cooling capacity that the chilled water can provide; that is, the existing chilled water flow rate cannot drive the excessive number of heat exchange tubes.

[0070] Since the actual outlet air temperature in the second passage cannot be lower than the dew point temperature, the large-area heat exchange tubes are only performing sensible heat exchange. In this case, redistributing the number of heat exchange tubes to optimize the overall energy efficiency ratio is a better choice. Therefore, when the actual supply air temperature corresponding to the second passage is detected to be higher than the return air dew point temperature, and the opening of the second regulating valve is greater than the second preset opening, the isolation distribution component can be controlled to reduce the number of heat exchange tubes connected to the second passage. In this way, the limited low-temperature cold source can be concentrated on fewer heat exchange tubes. When it is detected that the second passage still cannot establish a dehumidification environment below the dew point temperature even when the water flow is saturated (the second valve opening reaches the threshold), its heat exchange area is automatically reduced to restore the dehumidification capacity of the second passage. The regulation strategy of this application can avoid the continuous waste of pumping energy under ineffective dehumidification conditions, and by rebalancing the processing capacity of sensible heat and latent heat, it ensures that each part of the heat exchange coil can work in the state most suitable for the current physical conditions, thereby improving the overall operating energy efficiency under complex and variable operating conditions.

[0071] This application further proposes a control device for implementing the control method of the above-mentioned air handling equipment.

[0072] The specific implementation of this control device is basically the same as the specific embodiment of the control method of the air handling equipment described above, and will not be repeated here.

[0073] A control device is a hardware and / or software entity used to execute control methods for air handling equipment. It may include, but is not limited to, microcontrollers, programmable logic controllers, industrial computers, or application-specific integrated circuits (ASICs). This device typically includes a processor, memory, input / output interfaces, and a communication module. The processor is responsible for executing control algorithms and logical judgments; the memory stores program code, configuration parameters, and real-time data; the input / output interfaces receive signals from sensors (such as temperature sensors, humidity sensors, and flow sensors) and output control commands to actuators (such as the drive mechanism of regulating valves and isolation distribution components); the communication module can be used for data interaction with other systems or for remote monitoring.

[0074] This application also proposes an air handling device, which includes the aforementioned control device, main pipeline, isolation and distribution component, regulating component, and multiple independent heat exchange tubes. The main pipeline has multiple water outlets connected to it, and the multiple water outlets of the main pipeline are connected one-to-one to the water inlet of the multiple heat exchange tubes. The isolation and distribution component is disposed inside the main pipeline to isolate the pipeline into a first passage and a second passage. The isolation and distribution component can adjust the number of heat exchange tubes connected to the first passage and the second passage. The regulating component includes a first regulating valve and a second regulating valve. The first regulating valve is disposed at the water inlet of the first passage, and the second regulating valve is disposed at the water inlet of the second passage.

[0075] The specific implementation method of this air handling equipment is basically the same as the specific embodiment of the control device described above, and will not be repeated here.

[0076] In some embodiments, the air handling equipment further includes a housing and a fan assembly; the housing has an air inlet and an air outlet, a heat exchange duct is formed between the air inlet and the air outlet of the housing, and a plurality of heat exchange tubes are disposed in the heat exchange duct; the fan assembly is disposed in the heat exchange duct, the inlet of the fan assembly faces the plurality of heat exchange tubes, the outlet of the fan assembly faces the air outlet of the housing, and the fan assembly is used to output air with a target total supply air temperature and a target total supply air humidity through the air outlet of the housing.

[0077] The air handling unit comprises a housing and multiple heat exchange tubes located inside the housing. The housing forms the enclosure of the air handling unit, with an air inlet and an air outlet. The internal space between the two forms a heat exchange duct. The heat exchange duct is the channel for airflow and the site of heat and moisture exchange. Optionally, the housing may have a support frame to support the fan assembly and multiple heat exchange tubes. Based on the above structure, the fan assembly serves as the power source of the system, driving air to flow within the heat exchange duct through suction. During this process, the airflow passes through multiple heat exchange tubes, exchanging heat and moisture with the chilled water flowing inside the tubes via the tube surfaces (and fins). This reduces the air temperature and removes moisture from the air, enabling the air to be treated to the target total supply air temperature and humidity, and finally delivered to the target environment through the air outlet.

[0078] Optionally, the air handling equipment further includes a water collection assembly located in the heat exchange duct. The water collection assembly has a pipe structure and a water collection tank. The pipe structure has an outlet end and multiple inlets. The multiple inlets of the water collection assembly are connected one-to-one with the outlet ends of multiple heat exchange tubes. The outlet end of the water collection assembly can be connected to a first passage and a second passage for water circulation. The water collection assembly is located in the heat exchange duct.

[0079] The embodiments described in this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided by the embodiments of this application. As those skilled in the art will know, with the evolution of technology and the emergence of new application scenarios, the technical solutions provided by the embodiments of this application are also applicable to similar technical problems.

[0080] Those skilled in the art will understand that the technical solutions shown in the figures do not constitute a limitation on the embodiments of this application, and may include more or fewer steps than shown, or combine certain steps, or different steps.

[0081] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs.

[0082] Those skilled in the art will understand that all or some of the steps in the methods disclosed above, as well as the functional modules / units in the systems and devices, can be implemented as software, firmware, hardware, or suitable combinations thereof.

[0083] The terms “first,” “second,” “third,” “fourth,” etc. (if present) in the specification and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms “comprising” and “having,” and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0084] It should be understood that in this application, "at least one (item)" means one or more, and "more than" means two or more. "And / or" is used to describe the relationship between related objects, indicating that three relationships can exist. For example, "A and / or B" can represent three cases: only A exists, only B exists, and both A and B exist simultaneously, where A and B can be singular or plural. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "At least one (item) of the following" or similar expressions refer to any combination of these items, including any combination of single or plural items. For example, at least one (item) of a, b, or c can represent: a, b, c, "a and b", "a and c", "b and c", or "a and b and c", where a, b, and c can be single or multiple.

[0085] In the several embodiments provided in this application, it should be understood that the disclosed apparatus and methods can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative; for instance, the division of the units described above is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be through some interfaces; the indirect coupling or communication connection between apparatuses or units may be electrical, mechanical, or other forms.

[0086] The units described above as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of this embodiment according to actual needs.

[0087] Furthermore, the functional units in the various embodiments of this application can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit. The integrated unit can be implemented in hardware or as a software functional unit.

[0088] If the integrated unit is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of this application, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes multiple instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods of the various embodiments of this application. The aforementioned storage medium includes various media capable of storing programs, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0089] The preferred embodiments of the present application have been described above with reference to the accompanying drawings, but this does not limit the scope of the claims of the present application. Any modifications, equivalent substitutions, and improvements made by those skilled in the art without departing from the scope and substance of the embodiments of the present application shall be within the scope of the claims of the present application.

Claims

1. A control method for an air handling equipment, characterized in that, The air handling equipment includes a main pipeline, an isolation and distribution assembly, a regulating assembly, and multiple independent heat exchange tubes. The main pipeline has multiple water outlets connected to it, and each of the multiple water outlets of the main pipeline is connected one-to-one to the water inlet of a plurality of heat exchange tubes. The isolation and distribution assembly is disposed within the main pipeline to isolate the main pipeline into a first passage and a second passage. The isolation and distribution assembly can adjust the number of heat exchange tubes connected to the first passage and the second passage. The regulating assembly includes a first regulating valve and a second regulating valve. The first regulating valve is disposed at the water inlet of the first passage, and the second regulating valve is disposed at the water inlet of the second passage. The method includes: Obtain the target total supply air temperature and target total supply air humidity of the air handling unit; The second target outlet temperature of the second passage is determined based on the preset total air volume, the target total air temperature, and the target total air humidity, and the first target outlet temperature of the first passage is determined based on the target total air temperature and the second target outlet temperature. Adjust the opening of the first regulating valve to make the outlet air temperature of the first passage reach the first target outlet air temperature, and adjust the opening of the second regulating valve to make the outlet air temperature of the second passage reach the second target outlet air temperature. When the opening degree of the second regulating valve reaches the first preset opening degree, and the actual total supply air humidity of the air handling equipment is higher than the target total supply air humidity, the isolation distribution component is controlled to increase the number of heat exchange tubes connected to the second passage.

2. The method according to claim 1, characterized in that, The method further includes: When the actual supply air temperature corresponding to the second passage is higher than the return air dew point temperature, and the opening degree of the second regulating valve is greater than the second preset opening degree, the isolation distribution component is controlled to reduce the number of heat exchange tubes connected to the second passage.

3. The method according to claim 1, characterized in that, The step of determining the second target outlet air temperature of the second passage based on the preset total air volume, the target total air temperature, and the target total air humidity includes: The second flow rate of the second passage is calculated based on the preset total air supply volume, the number of first heat exchange tubes corresponding to the first passage, and the number of second heat exchange tubes corresponding to the second passage. The second outlet air humidity content corresponding to the second passage is calculated based on the target total dehumidification capacity, the moisture content of the mixed air after the intake and return air are mixed, and the second flow volume. The corresponding second target outlet dry bulb temperature is determined based on the preset outlet relative humidity of the second channel and the moisture content of the second outlet air. The chilled water inlet temperature and the preset minimum heat transfer temperature difference are obtained, and the second target outlet air temperature of the second passage is calculated based on the chilled water inlet temperature, the minimum heat transfer temperature difference, the second target outlet dry bulb temperature, and the target total supply air temperature.

4. The method according to claim 3, characterized in that, The air handling equipment further includes a housing having an air inlet and an air outlet, with a heat exchange duct formed between the air inlet and the air outlet, and a plurality of heat exchange tubes disposed in the heat exchange duct. Before calculating the moisture content of the second outlet air corresponding to the second passage based on the target total dehumidification capacity, the moisture content of the mixed air after mixing the inlet and return air, and the second flow rate, the method further includes: Obtain the intake air volume and calculate the intake air volume ratio based on the intake air volume and the preset total air supply volume; Obtain the return air moisture content determined by the return air temperature and return air humidity, and obtain the inlet air moisture content determined by the inlet air temperature and inlet air humidity; The moisture content of the mixed air after the intake and return air are mixed is calculated based on the intake air volume ratio, the return air moisture content, and the intake air moisture content. The target total dehumidification capacity is calculated based on the intake air moisture content, the total supply air volume, and the target air moisture content determined by the target total supply air temperature and the target total supply air humidity.

5. The method according to claim 3, characterized in that, The calculation of the second outlet air humidity corresponding to the second passage based on the target total dehumidification capacity, the moisture content of the mixed air after the intake and return air are combined, and the second flow rate includes: Calculate the product of the second flow rate and the air density, and calculate the ratio between the target total dehumidification capacity and the product; Determine the difference between the moisture content of the mixed air after the intake and return air are mixed and the ratio, and determine the moisture content of the second outlet air corresponding to the second passage based on the difference.

6. The method according to claim 3, characterized in that, Determining the first target outlet temperature of the first passage based on the target total supply air temperature and the second target outlet temperature includes: The first flow rate of the first passage is calculated based on the preset total air volume, the number of first heat exchange tubes corresponding to the first passage, and the number of second heat exchange tubes corresponding to the second passage. The first target outlet dry bulb temperature corresponding to the first passage is calculated based on the first flow volume, the second flow volume, the second target outlet air temperature, and the target total supply air temperature. The first target outlet temperature corresponding to the first passage is calculated based on the chilled water inlet temperature, the minimum heat transfer temperature difference, the first target outlet dry bulb temperature, and the target total supply air temperature.

7. The method according to claim 1, characterized in that, The process of obtaining the target total supply air temperature and target total supply air humidity of the air handling unit includes: Obtain the return air temperature and the target temperature, and calculate the temperature deviation between the return air temperature and the target temperature; The total supply air temperature set in the previous round is corrected based on the temperature deviation to obtain the target total supply air temperature; wherein, if the return air temperature is higher than the target temperature, the total supply air temperature set in the previous round is reduced, and if the return air temperature is lower than the target temperature, the total supply air temperature set in the previous round is increased, and the adjustment range of the target total supply air temperature is positively correlated with the absolute value of the temperature deviation. Obtain the return air humidity and the target humidity, and calculate the humidity deviation between the return air humidity and the target humidity; The total supply air humidity set in the previous round is corrected based on the humidity deviation to obtain the target total supply air humidity; wherein, if the return air humidity is higher than the target humidity, the total supply air humidity set in the previous round is reduced, and if the return air humidity is lower than the target humidity, the total supply air humidity set in the previous round is increased, and the adjustment range of the target total supply air humidity is positively correlated with the absolute value of the humidity deviation.

8. A control device, characterized in that, The control device is used to implement the control method of the air handling equipment as described in any one of claims 1 to 7.

9. An air handling device, characterized in that, The air handling equipment includes: The control device as described in claim 8; The main pipeline has multiple outlets connected to its conduit. An isolation distribution component is disposed within the main pipeline to isolate the main pipeline into a first path and a second path. The regulating component includes a first regulating valve and a second regulating valve, wherein the first regulating valve is disposed at the water inlet end of the first passage and the second regulating valve is disposed at the water inlet end of the second passage; Multiple independent heat exchange tubes are provided, and the multiple outlets of the main pipe are connected one-to-one to the inlet of the multiple heat exchange tubes. The isolation distribution component can adjust the number of heat exchange tubes connected to the first passage and the second passage.

10. The air handling equipment according to claim 9, characterized in that, The air handling equipment also includes: The outer casing has an air inlet and an air outlet, and a heat exchange duct is formed between the air inlet and the air outlet of the outer casing, and a plurality of heat exchange tubes are disposed in the heat exchange duct. A fan assembly is disposed in the heat exchange duct, the inlet of the fan assembly faces the plurality of heat exchange tubes, and the outlet of the fan assembly faces the air outlet of the housing. The fan assembly is used to output air with a target total supply air temperature and a target total supply air humidity through the air outlet of the housing.

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