A control method, device, equipment and medium of an air treatment system

Abstract

The application provides a control method, device, equipment and medium of an air treatment system, the control method comprising: calculating the current moisture content of air in the current state according to the temperature and relative humidity of the air; calculating the first minimum indoor temperature when the wet balance state is met according to different first indoor temperatures, the upper limit value of the design humidity, and the supply air moisture content being the saturated moisture content at the supply air temperature; calculating the second minimum indoor temperature when the wet balance state is met according to different second indoor temperatures, the upper limit value of the design humidity, and the first supply air moisture content; and determining the working mode of the cooling module and the heating module according to the comparison result of the first minimum indoor temperature, the second minimum indoor temperature, and the upper limit value of the preset design temperature. The control method, device, equipment and medium of the air treatment system provided by the application can quickly determine the operating conditions of the cooling module and the heating module.

Description

Technical Field

[0001] This invention relates to the field of nuclear power, and more particularly to a control method, apparatus, equipment and medium for an air handling system. Background Technology

[0002] In nuclear facility environments, condensation prevention control of the HVAC system in the spent fuel pool lobby is a critical technical aspect for ensuring the safe operation of equipment and the health of personnel. Due to the continuous evaporation and moisture dissipation characteristics of the pool, there is a high risk of condensation indoors, which not only accelerates equipment corrosion but may also trigger the spread of radioactive materials.

[0003] Traditional HVAC system anti-condensation design mainly relies on manual calculations and static condition analysis: designers need to initially determine the system capacity based on the temperature limits required by specifications, and then repeatedly check enthalpy-humidity charts or professional software to verify whether the humidity anti-condensation conditions are met, thereby determining the operating conditions of the cooling and heating modules in the HVAC system. Therefore, how to automatically determine the operating conditions of the cooling and heating modules in an HVAC system through trial calculations is a technical problem that urgently needs to be solved. Summary of the Invention

[0004] This invention provides a control method, apparatus, equipment, and medium for an air handling system, which can quickly determine the operating conditions of the cooling and heating modules in an HVAC system.

[0005] This invention provides a control method for an air handling system, applied to an air handling system in a nuclear power plant. The air handling system includes a cooling module and a heating module. The control method includes:

[0006] Calculate the current state of the indoor air based on the current indoor temperature and relative humidity.

[0007] According to different preset first indoor temperatures, when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature, the lowest first indoor temperature when the indoor air meets the moisture balance state is calculated and recorded as the first lowest indoor temperature; wherein, the different preset first indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature.

[0008] According to different preset second indoor temperatures, when the relative humidity of the indoor air is at the upper limit of the design humidity, the lowest second indoor temperature when the indoor air meets the humidity balance state is calculated based on the first supply air moisture content of the cooling module at each second indoor temperature, and is recorded as the second lowest indoor temperature; wherein, the different preset second indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature; the first supply air moisture content is calculated based on the current moisture content;

[0009] The operating modes of the cooling module and the heating module are determined based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit.

[0010] In one embodiment of the present invention, calculating the current humidity content of the indoor air under the current state based on the current indoor temperature and current relative humidity includes:

[0011] In a preset water vapor partial pressure mapping table, the saturated water vapor partial pressure of indoor air in a saturated state is obtained based on the current indoor temperature of the indoor air; wherein, the water vapor partial pressure mapping table represents the mapping relationship between the current indoor temperature of indoor air and the saturated water vapor partial pressure of indoor air in a saturated state.

[0012] Calculate the current water vapor partial pressure based on the saturated water vapor partial pressure and the current relative humidity of the indoor air;

[0013] Calculate the current humidity content of the indoor air under the current conditions based on the current water vapor partial pressure and atmospheric pressure.

[0014] In one embodiment of the present invention, the calculation of the lowest first indoor temperature when the indoor air meets the humidity balance state, denoted as the first lowest indoor temperature, includes:

[0015] When the relative humidity of the indoor air is at the preset upper limit of the design humidity, the corresponding first indoor moisture content, first waste tank wet load, and first personnel wet load are calculated according to the preset different first indoor temperatures.

[0016] The first supply air wet load is obtained by multiplying the saturated moisture content by the supply air volume of the air supply module in the air handling system.

[0017] The first exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the humidity of each of the first indoor spaces; wherein, the first exhaust moisture load = first indoor humidity × exhaust volume;

[0018] At each first indoor temperature, the difference between the first exhaust moisture load and the first supply air moisture load is calculated to obtain the corresponding first exhaust moisture load;

[0019] The first generated wet load is obtained by acquiring and calculating the sum of other indoor wet loads, the first wastewater pool wet load, and the first personnel wet load;

[0020] The first indoor temperature that is greater than or equal to the first generated wet load is retained, and the lowest value of the retained first indoor temperature is selected and recorded as the first lowest indoor temperature.

[0021] In one embodiment of the present invention, the calculation of the lowest second indoor temperature when the indoor air meets the humidity balance state, denoted as the second lowest indoor temperature, includes:

[0022] When the relative humidity of the indoor air is at the upper limit of the design humidity, the corresponding second indoor humidity, second waste pool wet load, second personnel wet load, and first supply air humidity are calculated according to the preset second indoor temperature.

[0023] The corresponding second supply air wet load is obtained by multiplying the supply air volume of the air supply module in the air handling system with the moisture content of each first supply air.

[0024] The corresponding second exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the humidity of each second indoor unit; wherein, the second exhaust moisture load = second indoor humidity × exhaust volume;

[0025] At each second indoor temperature, the difference between the second exhaust moisture load and the second supply air moisture load is calculated to obtain the corresponding second exhaust moisture load;

[0026] The second generated wet load is obtained by summing the other indoor wet loads, the second wastewater wet load, and the second personnel wet load;

[0027] The second indoor temperature that is greater than or equal to the second generated wet load is retained, and the lowest value of the retained second indoor temperature is selected and recorded as the second lowest indoor temperature.

[0028] In one embodiment of the present invention, the step of determining the operating modes of the cooling module and the heating module based on the comparison result of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit value includes:

[0029] Determine the first minimum indoor temperature, the second minimum indoor temperature, and the preset upper limit of the design temperature:

[0030] When both the first minimum indoor temperature and the second minimum indoor temperature are greater than the upper limit of the design temperature, it is determined that the non-condensation requirement is not met.

[0031] When the first minimum indoor temperature is greater than the second minimum indoor temperature, and the second minimum indoor temperature is less than or equal to the upper limit of the design temperature, the cooling module is determined to be in dry operating mode or shutdown mode.

[0032] When the first minimum indoor temperature is less than or equal to the second minimum indoor temperature, and the first minimum indoor temperature is less than or equal to the upper limit of the design temperature, the cooling module is determined to be in wet operating mode.

[0033] In one embodiment of the present invention, determining whether the cooling module is in a dry operating mode or a shutdown mode includes:

[0034] At the second lowest indoor temperature, the first heat transfer load of the building envelope is calculated based on the obtained outdoor temperature and thermal performance parameters of the building envelope.

[0035] Based on the other sensible heat loads in the room, the first sensible heat load of occupants at the second lowest indoor temperature, and the first heat transfer load, determine whether the indoor air meets the thermal equilibrium state:

[0036] When the indoor air meets the thermal equilibrium state, it is determined that both the cooling module and the heating module are in shutdown mode.

[0037] Otherwise, the cooling module is determined to be in dry operating mode or shutdown mode.

[0038] In one embodiment of the present invention, determining whether the cooling module is in a dry operating mode or a shutdown mode further includes:

[0039] When the cooling module is in dry operating mode, the first target indoor temperature when the indoor air meets the thermal equilibrium state is calculated according to different preset third indoor temperatures; wherein, the different preset third indoor temperatures are obtained by gradually adjusting the second minimum indoor temperature according to preset values.

[0040] At the first target indoor temperature, the first target relative humidity when the indoor air meets the humidity balance state is calculated according to different preset first relative humidity; wherein, the different preset first relative humidity is obtained by gradually adjusting according to the preset value based on the design humidity lower limit value.

[0041] The operating parameters of the cooling module are set according to the first target indoor temperature and the first target relative humidity.

[0042] In one embodiment of the present invention, calculating the first target indoor temperature when the indoor air meets the thermal equilibrium state according to different preset third indoor temperatures includes:

[0043] Based on the preset different third indoor temperatures, and according to the outdoor temperature and the thermal performance parameters of the building envelope, the second heat transfer load corresponding to the building envelope is calculated.

[0044] At each of the third indoor temperatures, the corresponding first sensible cooling load is calculated based on the air supply volume of the air supply module in the air handling system and the design air supply temperature of the cooling module; wherein, the first sensible cooling load = air supply volume × specific heat of air × (third indoor temperature - design air supply temperature).

[0045] At each of the third indoor temperatures, the sum of the other indoor sensible heat loads and the second sensible heat load of the occupants at the third indoor temperature is used to obtain the first sensible heat load. The sum of the second heat transfer load and the first air supply sensible cooling load is used to obtain the first sensible cooling load.

[0046] The third indoor temperature is retained when the first sensible cooling load is greater than or equal to the corresponding first sensible heat load. The lowest value of the retained third indoor temperature between the lower limit of the design temperature and the upper limit of the design temperature is selected and denoted as the first target indoor temperature.

[0047] In one embodiment of the present invention, the step of calculating the first target relative humidity when the indoor air meets the humidity balance state according to preset different first relative humidityes at the first target indoor temperature includes:

[0048] At the first target indoor temperature, the third indoor humidity content corresponding to the indoor air is calculated according to different preset first relative humidities;

[0049] Under each of the first relative humidities, the product of the air supply volume of the air supply module in the air handling system and the second supply air moisture content of the air supply module is calculated to obtain the corresponding third supply air wet load.

[0050] Under each of the first relative humidity conditions, the corresponding third exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the corresponding third indoor humidity; wherein, the third exhaust moisture load = exhaust volume × third indoor humidity.

[0051] Under each of the first relative humidities, the corresponding third wet load of the waste tank is calculated based on the first target indoor temperature and the corresponding third indoor moisture content;

[0052] At each of the first relative humidities, the difference between the third supply air wet load and the third exhaust wet load is calculated to obtain the third exhaust wet load. The third waste pool wet load, the third personnel wet load at the first target indoor temperature, and other indoor wet loads are calculated to obtain the third generation wet load.

[0053] The first relative humidity is retained when the third discharge moisture load is greater than or equal to the corresponding third generation moisture load. The lowest value of the retained first relative humidity is selected and recorded as the first target relative humidity.

[0054] In one embodiment of the present invention, the step of calculating the first target indoor temperature when the indoor air meets the thermal equilibrium state according to different preset third indoor temperatures when the cooling module is in dry operating mode further includes:

[0055] At the first target indoor temperature, the first inner wall temperature and the first indoor dew point temperature of the building envelope are calculated based on the outdoor temperature and the thermal performance parameters of the building envelope.

[0056] Determine the temperature of the first inner wall surface and the temperature of the first indoor dew point:

[0057] If the temperature of the first inner wall surface is less than or equal to the first indoor dew point temperature, it is determined that the requirement of no condensation is not met.

[0058] In one embodiment of the present invention, determining whether the cooling module is in a dry operating mode or a shutdown mode further includes:

[0059] When the cooling module is in shutdown mode, at the second lowest indoor temperature, the second inner wall temperature and the second indoor dew point temperature of the building envelope are calculated based on the outdoor temperature and the thermal performance parameters of the building envelope.

[0060] Determine the temperature of the second inner wall surface and the temperature of the second indoor dew point:

[0061] When the temperature of the second inner wall surface is less than or equal to the temperature of the second indoor dew point, it is determined that the non-condensation requirement is not met.

[0062] Otherwise, the total sensible heat load is obtained by calculating the sum of the first sensible heat load and the other sensible heat loads in the room, and the difference between the total sensible heat load and the first heat transfer load is determined: when the difference is equal to 0, the heating module is determined to be in shutdown mode; otherwise, the operating parameters of the heating module are set according to the difference.

[0063] In one embodiment of the present invention, determining that the cooling module is in a wet operating mode includes:

[0064] At the first lowest indoor temperature, based on the outdoor temperature and the thermal performance parameters of the building envelope, the third heat transfer load of the building envelope, the third inner wall surface temperature of the building envelope, and the third indoor dew point temperature are calculated.

[0065] Determine the temperature of the third inner wall surface and the temperature of the third indoor dew point:

[0066] When the temperature of the third inner wall surface is less than or equal to the dew point temperature of the third room, it is determined that the requirement of no condensation is not met.

[0067] Otherwise, the second air supply sensible cooling load is calculated based on the air supply volume of the air supply module in the air handling system, the current indoor temperature, and the first lowest indoor temperature;

[0068] Obtain the sensible heat load of the fourth person at the first lowest indoor temperature, calculate the sum of the sensible heat load of the fourth person and the other sensible heat loads in the room to obtain the second sensible heat load, and calculate the sum of the second supply air sensible cooling load and the third heat transfer load to obtain the second sensible cooling load.

[0069] Determine the second sensible heat load and the second sensible cold load:

[0070] When the second sensible cooling load is greater than the second sensible heat load, it is determined that the cooling module is in wet operating mode and the heating module is in heating mode.

[0071] Otherwise, the cooling module is determined to be in wet operating mode and the heating module is in shutdown mode.

[0072] In one embodiment of the present invention, after determining that the cooling module is in a wet operating mode and the heating module is in a heating mode, the method further includes:

[0073] The operating parameters of the cooling module are set according to the upper limit of the designed humidity and the first minimum indoor temperature.

[0074] The operating parameters of the heating module are set based on the difference between the second sensible cold load and the second sensible heat load.

[0075] In one embodiment of the present invention, after determining that the cooling module is in a wet operating mode and the heating module is in a shutdown mode, the method further includes:

[0076] Determine the second sensible heat load and the second sensible cold load:

[0077] When the second sensible heat load equals the second sensible cold load, the operating parameters of the cooling module are set according to the upper limit of the design humidity and the first minimum indoor temperature.

[0078] When the second sensible heat load is greater than the second sensible cold load, the second target indoor temperature when the indoor air meets the thermal equilibrium state is calculated according to different preset fourth indoor temperatures; at the second target indoor temperature, the second target relative humidity when the indoor air meets the humidity equilibrium state is calculated according to different preset second relative humidity; the operating parameters of the cooling module are set according to the second target indoor temperature and the second target relative humidity; wherein, the different preset fourth indoor temperatures are obtained by gradually adjusting the preset values ​​based on the first minimum indoor temperature; the different preset second relative humidity are obtained by gradually adjusting the preset values ​​based on the design humidity lower limit.

[0079] The present invention also provides a control device for an air handling system, which applies the control method for the air handling system described above. The control device includes:

[0080] The moisture content calculation module is used to calculate the current moisture content of indoor air under the current conditions based on the current indoor temperature and current relative humidity.

[0081] The first temperature calculation module is used to calculate the lowest first indoor temperature when the indoor air meets the humidity balance state, based on different preset first indoor temperatures, and when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature. This lowest first indoor temperature is denoted as the first minimum indoor temperature. The different preset first indoor temperatures are obtained by gradually adjusting the preset lower limit of the design temperature according to the preset value.

[0082] The second temperature calculation module is used to calculate the lowest second indoor temperature when the indoor air meets the humidity balance state, based on the first supply air moisture content of the cooling module at each second indoor temperature, and when the relative humidity of the indoor air is at the upper limit of the design humidity, according to different preset second indoor temperatures. This lowest second indoor temperature is denoted as the second minimum indoor temperature. The different preset second indoor temperatures are obtained by gradually adjusting the preset lower limit of the design temperature. The first supply air moisture content is calculated based on the current moisture content.

[0083] The operating condition judgment module is used to determine the operating mode of the cooling module and the heating module based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit value.

[0084] The present invention also provides an electronic device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the steps of the control method of the air handling system.

[0085] The present invention also provides a computer-readable storage medium storing a computer program, which, when executed by a processor, implements the steps of the control method for the air handling system.

[0086] The beneficial effects of this invention are: It effectively solves the problem of low efficiency caused by traditional manual iterative calculations through a systematic and automated calculation process. Based on design temperature / humidity limits, and by gradually adjusting preset temperature values, it calculates the first and second minimum indoor temperatures that meet the humidity balance conditions, and determines the operating modes of the cooling and heating modules accordingly. This structured calculation method avoids the manual operation of repeatedly querying enthalpy-humidity charts required in traditional methods, significantly improving the accuracy and efficiency of operating condition determination. Attached Figure Description

[0087] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. It is obvious that the drawings described below are merely some embodiments of this application, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort.

[0088] In the attached diagram:

[0089] Figure 1 This is a schematic diagram of an air handling system provided in an embodiment of the present invention;

[0090] Figure 2 This is a flowchart of a control method for an air handling system provided in one embodiment of the present invention;

[0091] Figure 3 This is a flowchart of the control device of an air handling system provided in one embodiment of the present invention;

[0092] Figure 4 This is a schematic diagram of an electronic device provided in one embodiment of the present invention.

[0093] The attached figures are labeled as follows:

[0094] 110. Fresh air module; 120. Exhaust air module; 130. Return air module; 140. Cooling module; 150. Heating module; 160. Blower module; 170. Air supply module; 210. Moisture content calculation module; 220. First temperature calculation module; 230. Second temperature calculation module; 240. Operating condition judgment module; 10. Electronic equipment; 11. Memory; 12. Processor. Detailed Implementation

[0095] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments. Various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. In the absence of conflict, the following embodiments and features in the embodiments can be combined with each other.

[0096] It should be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of the present invention. The drawings only show the components related to the present invention and are not drawn according to the actual number, shape and size of the components in the actual implementation. In the actual implementation, the form, quantity and proportion of each component can be arbitrarily changed, and the layout of the components may also be more complex.

[0097] In the following description, numerous details are explored to provide a more thorough explanation of embodiments of the invention. However, it will be apparent to those skilled in the art that embodiments of the invention may be practiced without these specific details. In other embodiments, well-known structures and devices are shown in block diagram form rather than in detail to avoid obscuring embodiments of the invention.

[0098] Please see Figure 1 This invention discloses an air handling system (HVAC) that can be applied to the lobby of a spent fuel pool in a nuclear power plant to prevent indoor condensation through automated control methods, ensuring equipment safety and personnel comfort. The HVAC system achieves precise control of indoor air temperature and humidity by coordinating various functional modules. The HVAC system may include a fresh air module 110, an exhaust air module 120, a return air module 130, a cooling module 140, a heating module 150, a blower module 160, and a supply air module 170.

[0099] In some embodiments, the fresh air module 110 serves as the inlet for air exchange between the air handling system and the outdoor environment. The fresh air module 110 can adjust the opening of the air valve according to control commands, introducing a certain amount of outdoor fresh air into the air handling system. The introduction of fresh air can dilute the concentration of potentially present radioactive pollutants indoors and provide necessary ventilation. The state parameters of the fresh air, especially temperature and relative humidity, are among the input parameters for the air handling system to perform heat and humidity load calculations and determine its operating mode.

[0100] In some embodiments, the exhaust module 120 can be responsible for forcibly exhausting indoor air to the outside to maintain a safe indoor pressure level and refresh the air. The exhaust module 120 can be linked with the fresh air module 110 for control, ensuring that the exhaust volume matches the fresh air volume and indoor infiltration volume, thereby stabilizing the indoor pressure in the lobby within the design requirements and preventing uncontrolled leakage of radioactive aerosols. Before being discharged, the exhaust air undergoes treatment equipment such as high-efficiency filtration to meet environmental regulations requiring controlled emissions of radioactive pollutants.

[0101] In some embodiments, the return air module 130 can reintroduce a portion of the air in the lobby into the air handling process, mixing it with fresh air. Using return air can significantly reduce the energy consumption of the air handling system because, in winter and summer, the temperature and humidity of indoor air are typically closer to the control target values, requiring far less cooling or heating to process the return air compared to a 100% fresh air mode. The return air module 130 guides indoor air to the mixing section with fresh air via dampers and ducts.

[0102] In some embodiments, the cooling module 140 is a key device in the air handling system for cooling and dehumidification, and it can be an air cooler or cooling coil using chilled water or refrigerant as the refrigerant. The cooling module 140 operates in multiple modes: in wet operating mode, its coil surface temperature is lower than the air dew point temperature, simultaneously cooling and dehumidifying the air; in dry operating mode, its coil surface temperature is higher than the air dew point temperature but lower than the air temperature, only providing isohumid cooling; in shutdown mode, refrigerant circulation is cut off, and air passes directly through the coil without heat exchange. The cooling module 140 can maintain its outlet air temperature stably at a preset design value by adjusting the refrigerant flow rate or inlet water temperature.

[0103] In some embodiments, the heating module 150 can be used for isothermal heating of air, and its heat source can be hot water, steam, or electricity, with corresponding devices being hot water heating coils, steam heaters, or electric heaters. When the indoor sensible heat load is insufficient or the subcooling effect caused by the dehumidification process of the cooling module 140 results in a low indoor temperature, the heating module 150 will be activated to heat the air to the required supply air temperature to maintain indoor thermal balance. The heating module 150 is flexible in its arrangement; it can be integrated into the air handling unit, or it can be set up separately as a reheat unit in the supply air duct, or it can be directly arranged indoors. This arrangement does not affect the overall thermal balance calculation of the air handling system.

[0104] In some embodiments, the blower module 160 can be a fan, which provides power for the flow of air throughout the treatment process. The fan pressurizes the air processed by the cooling module 140 and heating module 150, overcoming the resistance of components such as air ducts, valves, and air outlets, ensuring sufficient airflow to be stably delivered to all required areas indoors. The fan's airflow and pressure head must be rigorously calculated and selected to meet the design requirements of the air handling system.

[0105] In some embodiments, the air supply module 170 is the final outlet for the air processed by the air handling system. The air supply module 170 can evenly distribute the pressurized air from the blower module 160 into the spent fuel water tank hall through the duct system and air outlets. The air supply parameters, including temperature, humidity, and air velocity, directly determine the thermal comfort and anti-condensation effect of the indoor environment. The design of the air supply module 170 must avoid airflow short-circuiting and ensure thorough mixing of air within the room to prevent localized temperature and humidity dead zones, thereby ensuring the uniformity and stability of the environmental parameters throughout the hall.

[0106] Please see Figure 2The present invention also discloses a control method for an air handling system, which can be applied to the air handling system of a nuclear power plant. The control method may include the following steps: Step S10, calculating the current humidity content of the indoor air under the current conditions based on the current indoor temperature and current relative humidity.

[0107] In some embodiments, step S10 includes the following steps: Step S11: In a preset water vapor partial pressure mapping table, obtain the saturated water vapor partial pressure of indoor air in a saturated state according to the current indoor temperature of indoor air; wherein, the water vapor partial pressure mapping table represents the mapping relationship between the current indoor temperature of indoor air and the saturated water vapor partial pressure of indoor air in a saturated state.

[0108] In some embodiments, the water vapor partial pressure mapping table contains a mapping relationship between the current indoor temperature and the saturated water vapor partial pressure of the indoor air when it is saturated, with a temperature range covering 0~100°C. The saturated water vapor partial pressure is obtained by comparing the read current indoor temperature with the temperature data in the mapping table.

[0109] In some embodiments, since the current indoor temperature may be an arbitrary value not located at a temperature node in the mapping table, interpolation is required to calculate the accurate saturated water vapor partial pressure corresponding to that temperature. Specifically, firstly, the position of the current indoor temperature within the water vapor partial pressure mapping table is determined, i.e., two adjacent temperature nodes are found such that the current indoor temperature lies between these two node temperatures. Subsequently, based on these two adjacent temperature nodes and their corresponding known saturated water vapor partial pressure values, a linear interpolation formula is used to calculate the accurate saturated water vapor partial pressure value when the indoor air is saturated at the current indoor temperature.

[0110] In some embodiments, the water vapor partial pressure mapping table in the saturated state of air at 0 - 100°C can be set as a matrix Ps with 2 rows and 61 columns. The value of Ps(0,0) can be obtained and compared with the current indoor temperature T. If Ps(0,0) ≥ T, then the saturated water vapor partial pressure at temperature T = Ps(1,1) - (Ps(1,1) - Ps(1,0)) × (Ps(0,1) - T) / (Ps(0,1) - Ps(0,0)). If Ps(0,0) < T, then i = 0, the values of Ps(0,i) and Ps(0,i + 1) are obtained, and the value corresponding to Ps(0,i + 1) is compared with T. If Ps(0,i + 1) ≥ T > Ps(0,i), then the saturated water vapor partial pressure at temperature T = Ps(1,i + 1) - (Ps(1,i + 1) - Ps(1,i)) × (Ps(0,i + 1) - T) / (Ps(0,i + 1) - Ps(0,i)). If Ps(0,i + 1) < T, then i = i + 1, and the calculation is looped until when i = 60, the saturated water vapor partial pressure at temperature T = Ps(1,60) - (Ps(1,60) - Ps(1,59)) × (Ps(0,60) - T) / (Ps(0,60) - Ps(0,59)).

[0111] In some embodiments, step S10 further includes the following steps: step S12, calculating the current water vapor partial pressure according to the saturated water vapor partial pressure and the current relative humidity of the indoor air.

[0112] In some embodiments, the current water vapor partial pressure is calculated according to the calculated saturated water vapor partial pressure and the current relative humidity of the indoor air monitored in real time. The current relative humidity reflects the ratio of the actual content of water vapor in the air to the saturated content at the current indoor temperature.

[0113] In some embodiments, the saturated water vapor partial pressure of air at a certain temperature represents the maximum capacity of the air to hold water vapor at that temperature, and the current relative humidity characterizes the percentage of the actual water vapor content in this maximum capacity. Therefore, multiplying the saturated water vapor partial pressure by the current relative humidity and then dividing by one hundred can obtain the actual partial pressure of water vapor in the air, that is, the current water vapor partial pressure. The current water vapor partial pressure directly reflects the absolute content of water vapor in the air.

[0114] In some embodiments, the calculation formula of the current water vapor partial pressure is as follows: ; where is the current relative humidity, in units of %; is the saturated water vapor partial pressure at temperature T, in units of Pa; is at temperature T, relative humidity The current partial pressure of water vapor at that time is expressed in Pa; the temperature T can be the current indoor temperature.

[0115] In some embodiments, step S10 further includes the following step: Step S13, calculate the current humidity of indoor air under the current state based on the current water vapor partial pressure and atmospheric pressure.

[0116] In some embodiments, atmospheric pressure is an environmental parameter that needs to be input, and can be standard atmospheric pressure or a value corrected for the local altitude of the nuclear power plant. Moisture content is defined as the mass of water vapor contained in one kilogram of dry air, and its calculation is based on the total air pressure and the partial pressure of water vapor. Moisture content is directly proportional to the current partial pressure of water vapor and inversely proportional to the partial pressure of dry air obtained by subtracting the current partial pressure of water vapor from the atmospheric pressure.

[0117] In some embodiments, the formula for calculating the current moisture content is as follows: ;in, Atmospheric pressure, unit: Pa; This represents the current moisture content. The formula for calculating enthalpy is as follows: ;in, This is the enthalpy value, expressed in kJ / kg.

[0118] In some embodiments, the control method further includes the following steps: Step S20: According to different preset first indoor temperatures, when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature, calculate the lowest first indoor temperature when the indoor air meets the humidity balance state, and record it as the first lowest indoor temperature; wherein, the different preset first indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature.

[0119] In some embodiments, step S20 includes the following steps: Step S21, when the relative humidity of the indoor air is the preset upper limit of the design humidity, calculate the corresponding first indoor moisture content, first waste pool wet load, and first personnel wet load according to the preset different first indoor temperatures.

[0120] In some embodiments, under wet operating conditions, the cooling module 140 is simulated. When the relative humidity of the indoor air is constant at a preset upper limit of the design humidity, the first indoor moisture content, the first waste tank wet load, and the first personnel wet load are calculated at each preset first indoor temperature according to a series of different first indoor temperatures. The preset different first indoor temperatures are a series of temperature values ​​generated by gradually increasing the lower limit of the design temperature in a fixed step size, used to explore the possibility of maintaining moisture balance under different indoor temperature conditions.

[0121] In some embodiments, for each assumed first indoor temperature, the air state parameters of the room, i.e., the first indoor humidity, are first determined using the humidity calculation formula described above, based on the first indoor temperature and a fixed upper limit of design humidity. Next, the amount of water evaporation from the surface of the spent fuel tank is calculated using a given evaporation formula, based on fixed parameters such as the water temperature, surface area, and surface wind speed of the spent fuel tank. This is the first wet load of the spent fuel tank. Simultaneously, based on the assumed first indoor temperature, the amount of moisture emitted by personnel at the first indoor temperature is obtained by querying a pre-stored table of personnel moisture emission data. This is the first personnel wet load.

[0122] In some embodiments, the wet load of the wastewater tank The calculation formula is as follows: ;in, The wet load of the wastewater is expressed in kg / h. The wind speed over the wastewater pool is expressed in m / s. The partial pressure of saturated air water vapor at the water temperature in the pool, in Pa; The area of ​​the wastewater pool is expressed in meters (m²). 2 ; The latent heat of vaporization of water vapor is taken as 2500 kJ / kg; since the wastewater pool is equipped with a cooling system to maintain the pool water temperature no higher than 50℃, therefore... Take the partial pressure of water vapor in saturated air at 50℃.

[0123] In some embodiments, step S20 further includes the following step: step S22, calculating the product of saturated moisture content and air supply volume of the air supply module in the air handling system to obtain the first air supply wet load.

[0124] In some embodiments, the corresponding first supply air wet load can be calculated based on the calculated saturated moisture content and the preset supply air volume of the air supply module 170 in the air handling system. Under the simulated premise that the cooling module 140 is in a wet operating mode, its supply air moisture content is set as the saturated moisture content of the supply air at the supply air temperature of the cooling module 140. The supply air temperature is a set constant value; therefore, the corresponding saturated moisture content can be calculated based on this supply air temperature and the aforementioned calculation formula for moisture content. The first supply air wet load characterizes the impact of the moisture content of the supplied air on the indoor humidity environment after it enters the room. Its calculation method is: First supply air wet load = Supply air volume × Saturated moisture content.

[0125] In some embodiments, step S20 further includes the following step: step S23, calculating the corresponding first exhaust moisture load based on the exhaust volume of the return / exhaust air module in the air handling system and the moisture content of each first indoor unit.

[0126] In some embodiments, a first removal moisture load is calculated based on the preset exhaust volume of the return air module or exhaust air module in the air handling system and the first indoor moisture content calculated for each first indoor temperature. The exhaust process directly discharges the air in the current indoor state to the outside, thereby removing the moisture in it. The first removal moisture load refers to the rate at which moisture is removed from the indoor environment through exhaust, and it is calculated by directly multiplying the preset exhaust volume by the corresponding first indoor moisture content.

[0127] In some embodiments, step S20 further includes the following step: Step S24, at each first indoor temperature, calculate the difference between the first exhaust moisture load and the first supply air moisture load to obtain the corresponding first exhaust moisture load.

[0128] In some embodiments, for each preset first indoor temperature, the calculated first exhaust moisture load at that temperature is subtracted from the calculated first supply air moisture load at the same temperature to obtain the first exhaust moisture load at that first indoor temperature. The first exhaust moisture load represents the total rate at which moisture is removed from the indoor space by the air handling system.

[0129] In some embodiments, step S20 further includes the following step: step S25, obtaining and calculating the sum of other indoor wet loads, the first waste pool wet load, and the first personnel wet load to obtain the first generated wet load.

[0130] In some embodiments, the other indoor moisture load is a fixed input parameter derived from building envelope infiltration, moisture dissipation from other equipment, moisture dissipation from the wastewater pool, etc. This other indoor moisture load is then added to the first wastewater pool moisture load and the first occupant moisture load calculated for each first indoor temperature to obtain the first generated moisture load at the first indoor temperature. The first generated moisture load represents the total rate at which moisture is added to the indoor air environment under the combined action of all indoor moisture sources.

[0131] In some embodiments, step S20 further includes the following step: step S26, retaining a first indoor temperature that is greater than or equal to the corresponding first generated wet load, and selecting the lowest value of the retained first indoor temperature, which is recorded as the first lowest indoor temperature.

[0132] In some embodiments, all preset first indoor temperatures are iterated, and the calculated first discharge moisture load is compared with the first generation moisture load at each first indoor temperature. First indoor temperatures whose first discharge moisture load is greater than or equal to their corresponding first generation moisture load are selected and retained. A moisture balance state requires that the rate of moisture removal is at least equal to the rate of moisture generation to prevent an increase in indoor humidity. From all first indoor temperatures that meet this condition, the lowest value is selected and recorded as the first lowest indoor temperature. This first minimum indoor temperature is the lowest indoor temperature that can be maintained to maintain indoor humidity balance (relative humidity not exceeding the design limit) when the cooling module 140 is operating in wet mode and the supply air humidity is set to saturation.

[0133] In some embodiments, the control method further includes the following steps: Step S30: According to different preset second indoor temperatures, when the relative humidity of the indoor air is the upper limit of the design humidity, calculate the lowest second indoor temperature when the indoor air meets the humidity balance state based on the first supply air moisture content of the cooling module at each second indoor temperature, and record it as the second lowest indoor temperature; wherein, the different preset second indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature.

[0134] In some embodiments, step S30 includes the following steps: Step S31, when the relative humidity of the indoor air is the upper limit of the design humidity, calculate the corresponding second indoor humidity, second waste pool wet load, second personnel wet load, and first supply air humidity according to different preset second indoor temperatures.

[0135] In some embodiments, a dry operating condition simulation is performed on the cooling module 140. With the relative humidity of the indoor air constant at the upper limit of the design humidity, the second indoor humidity content, the second wastewater wet load, the second personnel wet load, and the first supply air humidity content are calculated at each temperature point based on a series of preset second indoor temperatures. The preset second indoor temperatures are a series of temperature values ​​generated by gradually increasing the lower limit of the design temperature in a fixed step size, used to explore the possibility of maintaining humidity balance under different indoor temperature conditions. The first supply air humidity content is calculated based on the current humidity content.

[0136] In some embodiments, for each assumed second indoor temperature, the indoor air state parameters, i.e., the second indoor humidity, are first determined using the humidity calculation formula described above, based on the second indoor temperature and a fixed upper limit of design humidity. Next, the water evaporation rate from the spent fuel tank surface, i.e., the second spent fuel tank wet load, is calculated using the evaporation rate formula described above, based on fixed parameters such as the spent fuel tank's water temperature, surface area, and surface wind speed. Simultaneously, based on this assumed indoor environmental state, the personnel moisture dissipation rate under this environment is obtained by querying a pre-stored personnel moisture dissipation data table.

[0137] In some embodiments, during the dry operating condition simulation of the cooling module, the first supply air moisture content is not the current moisture content, but depends on the operating mode of the air handling system. When the air handling system operates in full return air mode, the first supply air moisture content is equal to the current moisture content; when the air handling system operates in mixed air mode, the formula for calculating the first supply air moisture content is: ,in, The first supply air moisture content, For the fresh air flow, The humidity content of the fresh air. For the return air flow rate, The moisture content of the return air (i.e., the current moisture content).

[0138] In some embodiments, step S30 further includes the following step: step S32, calculating the corresponding second supply air wet load based on the product of the supply air volume of the air supply module in the air handling system and the moisture content of each first supply air.

[0139] In some embodiments, a second supply air wet load is calculated based on the preset supply air volume of the air supply module 170 in the air handling system and the first supply air moisture content calculated for each second indoor temperature. The second supply air wet load characterizes the impact of the moisture content of the supplied air on the indoor humidity environment after it enters the room. The calculation method for the second supply air wet load is: supply air volume × first supply air moisture content.

[0140] In some embodiments, step S30 further includes the following step: step S33, calculating the corresponding second exhaust moisture load based on the exhaust volume of the return / exhaust air module in the air handling system and the humidity of each second room; wherein, the second exhaust moisture load = second room humidity × exhaust volume.

[0141] In some embodiments, a second removal moisture load is calculated based on the preset exhaust volume of the return air module or exhaust air module in the air handling system and the second indoor humidity content calculated for each second indoor temperature. The exhaust process directly discharges the air currently in the room to the outside, thereby continuously removing moisture. The second removal moisture load refers to the rate at which moisture is removed from the room through this physical displacement method of exhaust air. The second removal moisture load is calculated by directly multiplying the preset exhaust volume by the corresponding second indoor humidity content.

[0142] In some embodiments, step S30 further includes the following step: Step S34, at each second indoor temperature, calculate the difference between the second exhaust moisture load and the second supply air moisture load to obtain the corresponding second exhaust moisture load.

[0143] In some embodiments, for each preset second indoor temperature, the calculated second exhaust moisture load at that temperature is subtracted from the calculated second supply air moisture load at the same temperature to obtain the second exhaust moisture load at that temperature. The second exhaust moisture load represents the total rate at which moisture is removed from the indoor environment by the air handling system.

[0144] In some embodiments, step S30 further includes the following step: step S35, obtaining and calculating the sum of other indoor wet loads, second waste pool wet load, and second personnel wet load to obtain the second generated wet load.

[0145] In some embodiments, the other indoor moisture loads are added to the second wastewater moisture load and the second occupant moisture load calculated for each second indoor temperature to obtain the second generated moisture load at that temperature. The second generated moisture load represents the total rate at which moisture is added to the indoor air environment under the combined effect of all indoor moisture sources at the assumed second indoor temperature.

[0146] In some embodiments, step S30 further includes the following step: step S36, retaining the second indoor temperature that is greater than or equal to the corresponding second generated wet load, and selecting the lowest value of the retained second indoor temperature, which is recorded as the second lowest indoor temperature.

[0147] In some embodiments, all preset second indoor temperatures are iterated, and the calculated second moisture discharge load is compared with the second moisture generation load for each second indoor temperature. Second indoor temperatures whose second moisture discharge load is greater than or equal to their corresponding second moisture generation load are selected and retained. A moisture balance state requires that the rate of moisture removal is at least equal to the rate of moisture generation to prevent indoor humidity from rising and maintain it at a set upper limit. From all second indoor temperatures that meet this condition, the second indoor temperature with the lowest value is selected and recorded as the second lowest indoor temperature. This second minimum indoor temperature is the lowest indoor temperature allowed to maintain indoor humidity balance (relative humidity not exceeding the design limit) when the cooling module 140 is operating in dry mode and the humidity of the first supply air is determined by the operating mode.

[0148] In some embodiments, the control method further includes the following steps: Step S40, determining the working mode of the cooling module and the heating module based on the comparison result of the first minimum indoor temperature, the second minimum indoor temperature and the preset design temperature upper limit value.

[0149] In some embodiments, step S40 includes the following steps: step S41, determining the first minimum indoor temperature, the second minimum indoor temperature, and the preset upper limit of the design temperature.

[0150] In some embodiments, the first minimum indoor temperature represents the lowest temperature permissible for maintaining indoor humidity balance when the cooling module 140 is operating in a wet operating mode. The second minimum indoor temperature represents the lowest temperature permissible for maintaining indoor humidity balance when the cooling module 140 is operating in a dry operating mode. The upper limit of the design temperature is the highest permissible indoor temperature set by the ventilation and air conditioning system of a nuclear power plant to ensure the safety of personnel and equipment.

[0151] In some embodiments, step S40 further includes the following step: step S42, when both the first minimum indoor temperature and the second minimum indoor temperature are greater than the upper limit of the design temperature, it is determined that the non-condensation requirement is not met.

[0152] In some embodiments, when the calculated results of both the first minimum indoor temperature and the second minimum indoor temperature are greater than the preset upper limit of the design temperature, it is ultimately determined that the non-condensation requirement is not met. The first minimum indoor temperature and the second minimum indoor temperature are the theoretical minimum temperature requirements derived from the perspective of moisture load balance. If both the first minimum indoor temperature and the second minimum indoor temperature exceed the upper limit of the design temperature, it indicates that even if the indoor temperature is controlled at the maximum allowable value, the moisture load that the air handling system can remove through supply and exhaust air is still insufficient to offset the moisture load generated indoors, and moisture balance cannot be maintained. In this case, regardless of whether the cooling module operates in wet or dry operating mode, it cannot solve the problem of excessive humidity within the allowable temperature range. Therefore, continuing to operate the cooling module or heating module is ineffective for humidity control, and it can be determined that the non-condensation requirement is not met. At this time, the cooling module and heating module can maintain their current operating mode or be in shutdown mode.

[0153] In some embodiments, step S40 further includes the following step: step S43, when the first minimum indoor temperature is greater than the second minimum indoor temperature and the second minimum indoor temperature is less than or equal to the upper limit of the design temperature, it is determined that the cooling module is in a dry operating mode or a shutdown mode.

[0154] In some embodiments, step S43 includes the following steps: Step S431, at the second lowest indoor temperature, calculate the first heat transfer load of the building envelope based on the obtained outdoor temperature and thermal performance parameters of the building envelope.

[0155] In some embodiments, a second lowest indoor temperature is first selected as the currently assumed indoor temperature. Then, the current outdoor temperature and various thermal performance parameters of the building envelope are obtained. These parameters include the heat transfer coefficient of the outer surface, the outer surface area, the thermal resistance of the envelope, the equivalent heat transfer area, the structural thickness, the heat transfer coefficient of the inner surface, and the inner surface area for different orientations or structural parts. Since the building envelope is typically composed of different parts, it needs to be divided into multiple calculation units, and a set of heat balance equations is established and solved for each unit. The heat balance equations describe the heat transfer process from outdoor air to the outer wall of the building envelope, through the building envelope itself, to the inner wall of the building envelope, and finally to the indoor air. By simultaneously solving the heat balance equations for each unit, the heat transfer through that unit's building envelope can be calculated. The heat transfer from all calculation units is summed to obtain the total heat transfer load through the entire building envelope under the current indoor-outdoor temperature difference, i.e., the first heat transfer load. A positive value of this first heat transfer load indicates heat loss from indoors to outdoors, while a negative value indicates heat gain from outdoors to indoors.

[0156] In some embodiments, the heat balance equations can be expressed as: , , ;in, The heat load of the building envelope is expressed in W. Expressed as the convective heat transfer coefficient between outdoor or adjacent room air and the exterior wall of the building envelope, with units of W / (m²). 2 ·℃); This refers to the temperature of the outer wall surface of the building envelope, expressed in °C. This indicates the outdoor or adjacent room air temperature, in °C. It is expressed as the outer surface area of ​​the building envelope, in m². 2 ; This refers to the temperature of the inner wall surface of the building envelope, expressed in °C. Expressed as the equivalent heat transfer area of ​​the building envelope, in m². 2 ; It is expressed as the thermal resistance of the building envelope, with units of (m·℃) / W; The thickness of the building envelope is expressed in meters (m). Expressed as the convective heat transfer coefficient between indoor air and the inner wall surface of the building envelope, with units of W / (m²). 2 ·℃); Indoor air temperature, expressed in °C; It is expressed as the inner surface area of ​​the building envelope, in m². 2 .

[0157] In some embodiments, step S43 further includes the following step: step S432, obtaining and determining whether the indoor air meets the thermal balance state based on other indoor sensible heat loads, the first sensible heat load of personnel at the second lowest indoor temperature, and the first heat transfer load.

[0158] In some embodiments, based on the calculated first heat transfer load, other known indoor sensible heat loads are obtained, along with the sensible heat load of occupants obtained by looking up a table at the second lowest indoor temperature. The indoor sensible heat load refers to the fixed load formed by heat dissipation from indoor equipment, lighting, etc., excluding heat transfer from the building envelope and heat dissipation from occupants. The sensible heat load of occupants is the heat load obtained by looking up a data table based on the number of occupants and their activity status under the assumed second lowest indoor temperature environment. Summing the first heat transfer load, other indoor sensible heat loads, and the first sensible heat load of occupants yields the change in the total indoor sensible heat load under the current second lowest indoor temperature setting. By analyzing the sign and magnitude of the total sensible heat load, it is determined whether the indoor air meets the thermal equilibrium state. The thermal equilibrium state refers to the state where, without activating the cooling or heating modules, the heat gain and heat loss are equal, and the temperature remains stable; that is, the total sensible heat load is 0.

[0159] In some embodiments, step S43 further includes the following steps: Step S433: When the indoor air meets the thermal equilibrium state, it is determined that both the cooling module and the heating module are in shutdown mode; otherwise, it is determined that the cooling module is in dry operating mode or shutdown mode.

[0160] In some embodiments, when the indoor air can achieve thermal equilibrium at the second lowest indoor temperature, it can be determined that both the cooling module and the heating module are in shutdown mode. Specifically, it can be ensured that at the second lowest indoor temperature, no additional cooling or heating is needed to compensate for the sensible heat load, and the heat gain and loss in the room naturally reach equilibrium. Therefore, both the cooling module and the heating module are in shutdown mode, and there is no need to start them.

[0161] In some embodiments, after step S433, step S434 is further included: when it is determined that the cooling module is in dry operating mode, the first target indoor temperature when the indoor air meets the thermal balance state is calculated according to different preset third indoor temperatures; wherein, the different preset third indoor temperatures are obtained by gradually adjusting according to the second lowest indoor temperature according to the preset value.

[0162] In some embodiments, after determining that the cooling module is in dry operating mode, it is necessary to find a better and more energy-efficient indoor temperature setpoint, i.e., a first target indoor temperature, while satisfying thermal balance. The thermal balance point is found by iteratively calculating a series of preset third indoor temperatures. The different preset third indoor temperatures are a series of temperature values ​​generated by gradually adjusting upwards from a second minimum indoor temperature according to a preset step size (e.g., 0.1℃ or 0.5℃).

[0163] In some embodiments, step S434 includes: calculating the second heat transfer load corresponding to the building envelope based on the outdoor temperature and the thermal performance parameters of the building envelope, according to different preset third indoor temperatures.

[0164] In some embodiments, based on different preset third indoor temperatures, and according to the current outdoor temperature and various known thermal performance parameters of the building envelope (including external surface heat transfer coefficient, external surface area, thermal resistance of the envelope, equivalent heat transfer area, structural thickness, internal surface heat transfer coefficient, internal surface area, etc.), the same simultaneous equation solution method as described above is used to calculate the total heat transfer through the building envelope, i.e., the second heat transfer load. The second heat transfer load reflects the net heat gain or net heat loss through the building envelope under different indoor and outdoor temperature differences.

[0165] In some embodiments, step S434 further includes the following step: at each third indoor temperature, calculate the corresponding first sensible cooling load based on the air supply volume of the air supply module in the air handling system and the design air supply temperature of the cooling module. First sensible cooling load = air supply volume × specific heat of air × (third indoor temperature - design air supply temperature).

[0166] In some embodiments, at each third indoor temperature, a corresponding first sensible cooling load is calculated based on the preset air volume of the air supply module in the air handling system, the specific heat capacity of the air at constant pressure, and the design air supply temperature of the cooling module (a preset fixed parameter). The first sensible cooling load represents the amount of sensible heat required to heat the air supply from the design air supply temperature to the currently assumed third indoor temperature. A positive value indicates that the air supply has a cooling effect on the room, while a negative value indicates that the air supply has a heating effect on the room.

[0167] In some embodiments, step S434 further includes the following steps: at each third indoor temperature, calculate the sum of other indoor sensible heat loads and the second sensible heat load of the second person at the third indoor temperature to obtain a first sensible heat load, and calculate the sum of the second heat transfer load and the first air supply sensible cooling load to obtain a first sensible cooling load.

[0168] In some embodiments, firstly, the known other indoor sensible heat loads are added to the second sensible heat load for personnel obtained by looking up a table at the current third indoor temperature to obtain the total sensible heat load generated indoors, i.e., the first sensible heat load. Secondly, the calculated second heat transfer load is added to the calculated first supply air sensible cooling load to obtain the total sensible cooling capacity that the air handling system can provide under the current conditions, i.e., the first sensible cooling load.

[0169] In some embodiments, step S434 further includes the following steps: retaining a third indoor temperature where the first sensible cooling load is greater than or equal to the corresponding first sensible heat load, and selecting the lowest value of the retained third indoor temperature between the lower limit of the design temperature and the upper limit of the design temperature, and recording it as the first target indoor temperature.

[0170] In some embodiments, all preset third indoor temperatures are iterated, and the calculated first sensible cooling load and first sensible heat load are compared at each third indoor temperature. Third indoor temperatures whose first sensible cooling load is greater than or equal to their corresponding first sensible heat load are selected and retained. This indicates that at this third indoor temperature, the cooling capacity of the cooling module can offset the heat gain in the room, achieving a precise thermal balance. From all temperature values ​​that meet this balance condition, those temperatures falling between the preset lower and upper design temperature limits are further selected. The third indoor temperature with the lowest value is then chosen and recorded as the first target indoor temperature. Selecting the lowest value is based on a conservative principle, ensuring that the indoor temperature is as close as possible to the lower limit of the allowable range, allowing for greater flexibility in humidity control while also considering energy efficiency.

[0171] In some embodiments, step S434 further includes the following steps: at the first target indoor temperature, calculate the first inner wall surface temperature and the first indoor dew point temperature of the building envelope based on the outdoor temperature and the thermal performance parameters of the building envelope; determine the first inner wall surface temperature and the first indoor dew point temperature: if the first inner wall surface temperature is less than or equal to the first indoor dew point temperature, determine that the non-condensation requirement is not met.

[0172] In some embodiments, the risk of condensation on the inner surface of the building envelope can be assessed and relevant parameters calculated under a specific condition of a first target indoor temperature. First, the calculated first target indoor temperature can be used as the currently assumed indoor air temperature. Then, the current outdoor temperature and various known thermal performance parameters of the building envelope are obtained. Since the building envelope typically consists of multiple different parts, it needs to be divided into multiple calculation units. For each unit, a set of heat balance equations describing the heat transfer process from outdoor air to the outer wall of the building envelope, through the building envelope itself, to the inner wall of the building envelope, and finally to the indoor air is established and solved simultaneously. By solving these equations, the inner wall temperature of each unit's building envelope can be calculated. After the inner wall temperatures of all units have been calculated, the inner wall temperature with the lowest value among all units is selected and recorded as the first inner wall temperature.

[0173] In some embodiments, the partial pressure of water vapor in the air at a first target indoor temperature is calculated by consulting a saturated vapor pressure table or using a given empirical formula. This partial pressure of water vapor in the air is then substituted into the provided dew point temperature. The calculation is performed using the formula to obtain the critical temperature at which water vapor begins to condense into dew under the current indoor air conditions, i.e., the first indoor dew point temperature. The calculation formula is as follows: ,in, The partial pressure of water vapor in the air at the second lowest indoor temperature and when the relative humidity is the preset upper limit of the design humidity.

[0174] In some embodiments, if the temperature of the first inner wall surface is less than or equal to the first indoor dew point temperature, meaning the temperature of the coldest point on the inner surface of the building envelope has reached or fallen below the current indoor dew point temperature, there is a substantial risk of condensation on the inner wall surface. Condensation produces moisture, which can not only damage the building structure but also increase the indoor moisture load. In this case, activating the heating module to raise the indoor temperature does not directly solve the problem of the excessively low inner wall surface temperature; instead, it may exacerbate the risk of condensation by increasing the moisture content of the indoor air, or at least constitute an ineffective waste of energy. Therefore, the non-condensation requirement is ultimately determined not to be met.

[0175] In some embodiments, after step S433, step S435 is further included: at the first target indoor temperature, the first target relative humidity when the indoor air meets the humidity balance state is calculated according to different preset first relative humidity; wherein, the different preset first relative humidity is obtained by gradually adjusting according to the preset value based on the design humidity lower limit value.

[0176] In some embodiments, after determining the first target indoor temperature, it is necessary to find the lowest relative humidity setpoint that can maintain humidity balance at this temperature, i.e., the first target relative humidity. The humidity balance point is found by iteratively calculating a series of preset first relative humidities. The different preset first relative humidities are a series of humidity values ​​generated by gradually adjusting upwards according to a preset step size (e.g., 1%) based on the design humidity lower limit.

[0177] In some embodiments, step S435 includes the following steps: at a first target indoor temperature, calculate the third indoor humidity corresponding to the indoor air in a saturated state according to different preset first relative humidities.

[0178] In some embodiments, at a fixed first target indoor temperature, a third indoor moisture content is calculated based on different preset first relative humidities, representing the corresponding humidity levels in the indoor air. For each assumed first relative humidity, combined with the known first target indoor temperature, the corresponding air moisture content can be determined using the moisture content calculation formula described above.

[0179] In some embodiments, step S435 further includes the following steps: at each first relative humidity, calculate the product of the air supply volume of the air supply module in the air handling system and the second supply air moisture content of the air supply module to obtain the corresponding third supply air wet load; the third supply air wet load = air supply volume × second supply air moisture content.

[0180] In some embodiments, at each first relative humidity, a third supply air wet load is calculated based on the preset supply air volume of the air supply module in the air handling system and the second supply air moisture content of the supply air provided by the cooling module under dry conditions. The third supply air wet load represents the rate at which moisture is removed from the indoor air after the supply air enters the room because its moisture content is lower than that of the indoor air. The calculation process for the second supply air moisture content is the same as that for the first supply air moisture content, and will not be repeated here.

[0181] In some embodiments, step S435 further includes the following steps: at each first relative humidity, calculate the corresponding third exhaust moisture load based on the exhaust volume of the return / exhaust air module in the air handling system and the corresponding third indoor humidity; the third exhaust moisture load = exhaust volume × third indoor humidity.

[0182] In some embodiments, at each first relative humidity, a third exhaust moisture load is calculated based on the preset exhaust volume of the return air module or exhaust air module in the air handling system and the calculated corresponding third indoor moisture content. The third exhaust moisture load represents the rate at which moisture is removed by directly exhausting humid indoor air to the outside through exhaust ventilation.

[0183] In some embodiments, step S435 further includes the following step: at each first relative humidity, calculate the corresponding third wet load of the waste tank based on the first target indoor temperature and the corresponding third indoor humidity.

[0184] In some embodiments, under each first relative humidity, based on the determined first target indoor temperature and the calculated corresponding third indoor moisture content (this moisture content implies the currently assumed relative humidity information, used to correct the partial pressure difference in the water tank evaporation calculation), combined with the fixed parameters of the waste tank (water temperature, area, wind speed, etc.), the amount of water evaporation on the surface of the water tank, i.e. the third waste tank wet load, is calculated using the given evaporation formula.

[0185] In some embodiments, step S435 further includes the following steps: at each first relative humidity, calculating the difference between the third supply air wet load and the third exhaust wet load to obtain the third exhaust wet load, and calculating the third waste pool wet load, the third personnel wet load at the first target indoor temperature, and other indoor wet loads to obtain the third generation wet load.

[0186] In some embodiments, two types of calculations are performed at each first relative humidity. First, the calculated third supply air moisture load is subtracted from the calculated third exhaust moisture load to obtain the total dehumidification capacity that the air handling system can provide through supply and exhaust air, i.e., the third exhaust moisture load. Second, the calculated third wastewater moisture load, the third occupant moisture load obtained by looking up a table at the first target indoor temperature, and other known indoor moisture loads are added to obtain the total moisture load generated by all indoor moisture sources, i.e., the third generation moisture load.

[0187] In some embodiments, step S435 further includes the following steps: retaining a first relative humidity that is greater than or equal to the corresponding third generating wet load, and selecting the lowest value of the retained first relative humidity as the first target relative humidity.

[0188] In some embodiments, all preset first relative humidity levels are iterated, and the calculated third exhaust moisture load and third generation moisture load are compared at each humidity level. First relative humidity levels where the third exhaust moisture load is greater than or equal to the corresponding third generation moisture load are selected and retained. This means that at the first relative humidity level, the dehumidification capacity of the air handling system can offset the indoor moisture generation, achieving a moisture balance. From all humidity values ​​that meet this balance condition, the lowest first relative humidity value is selected and recorded as the first target relative humidity. Selecting the lowest value aims to reduce the indoor relative humidity as much as possible while meeting process requirements (humidity not lower than the design lower limit).

[0189] In some embodiments, after step S433, step S436 is further included: setting the operating parameters of the cooling module according to the first target indoor temperature and the first target relative humidity.

[0190] In some embodiments, specific operating parameters of the cooling module can be set based on a first target indoor temperature and a first target relative humidity. The first target indoor temperature represents the setpoint indoor temperature that the air handling system should maintain while satisfying thermal balance, energy saving, and controllability. The first target relative humidity represents the setpoint indoor humidity that the air handling system should maintain while satisfying humidity balance at a given temperature and maximizing energy efficiency. These two parameters together constitute the control objectives of the air handling system. The setting of the cooling module's operating parameters will revolve around achieving these two objectives, mainly including the generation and issuance of control commands such as supply air temperature, supply air volume (if variable), chilled water valve opening, and fan speed, ensuring that the air handling system can stably maintain the indoor environment near the calculated first target indoor temperature and first target relative humidity.

[0191] In some embodiments, after step S433, step S437 is further included: when the cooling module is in shutdown mode, at the second lowest indoor temperature, the second inner wall temperature and the second indoor dew point temperature of the building envelope are calculated based on the outdoor temperature and the thermal performance parameters of the building envelope.

[0192] In some embodiments, the calculation process for the second inner wall surface temperature is the same as that for the first inner wall surface temperature, and the calculation process for the second indoor dew point temperature is also the same as that for the first indoor dew point temperature, which will not be elaborated here.

[0193] In some embodiments, after step S437, step S438 is further included: determining the second inner wall surface temperature and the second indoor dew point temperature: when the second inner wall surface temperature is less than or equal to the second indoor dew point temperature, it is determined that the non-condensation requirement is not met; otherwise, the total sensible heat load is obtained by calculating the sum of the first sensible heat load and other sensible heat loads in the room, and the difference between the total sensible heat load and the first heat transfer load is determined: when the difference is equal to 0, it is determined that the heating module is in shutdown mode; otherwise, the operating parameters of the heating module are set according to the difference.

[0194] In some embodiments, if the temperature of the second inner wall surface is less than or equal to the second indoor dew point temperature, meaning the temperature of the coldest point on the inner surface of the building envelope has reached or fallen below the current indoor dew point temperature, there is a risk of condensation on the inner wall surface. Condensation produces moisture, which can not only damage the building structure but also increase the indoor moisture load. In this case, activating the heating module to raise the indoor temperature does not directly solve the problem of the excessively low inner wall surface temperature; instead, it may exacerbate the risk of condensation by increasing the moisture content of the indoor air, or at least constitute an ineffective waste of energy. Therefore, the final determination is that the non-condensation requirement is not met.

[0195] In some embodiments, if the temperature of the second inner wall surface is greater than the second indoor dew point temperature, it indicates that there is no risk of condensation on the inner wall surface. In this case, it is necessary to calculate the indoor heat load. The first sensible heat load obtained at the second lowest indoor temperature is added to the known sensible heat loads of other people in the room to obtain the total sensible heat load. Then, the difference between this total sensible heat load and the first heat transfer load is calculated. This difference reflects the net amount of heat generated by the indoor sensible heat source and the heat lost (or gained) through the building envelope at the second lowest indoor temperature. If the difference is zero, it indicates that the indoor heat gain and loss are naturally balanced, and no additional heating is needed to compensate; therefore, the heating module is determined to be in shutdown mode. Otherwise, if the difference is not zero, i.e., the difference is negative (i.e., the total sensible heat load is less than the first heat transfer load, and the net effect is indoor heat loss), the operating parameters of the heating module need to be set according to the magnitude of this difference. For example, the required heating amount should be calculated and the power of the heater or the opening of the hot water valve should be adjusted accordingly to compensate for heat loss, maintain the indoor temperature at a level not lower than the second lowest indoor temperature, and ensure that the inner wall surface temperature is always higher than the dew point temperature.

[0196] In some embodiments, step S40 further includes the following step: step S44, when the first lowest indoor temperature is less than or equal to the second lowest indoor temperature and the first lowest indoor temperature is less than or equal to the upper limit of the design temperature, it is determined that the cooling module is in a wet operating mode.

[0197] In some embodiments, step S44 includes the following steps: Step S441, at the first lowest indoor temperature, calculate the third heat transfer load of the building envelope, the third inner wall temperature of the building envelope, and the third indoor dew point temperature based on the outdoor temperature and the thermal performance parameters of the building envelope.

[0198] In some embodiments, the calculation process for the third inner wall surface temperature is the same as that for the first inner wall surface temperature, and the calculation process for the third indoor dew point temperature is also the same as that for the first indoor dew point temperature, which will not be elaborated here.

[0199] In some embodiments, step S44 further includes the following step: step S442, determining the temperature of the third inner wall surface and the temperature of the third indoor dew point.

[0200] In some embodiments, the risk of condensation on the inner surface of the building envelope is assessed by comparing the third inner wall surface temperature and the third indoor dew point temperature under a preset first minimum indoor temperature operating condition.

[0201] In some embodiments, step S44 further includes the following step: step S443, when the temperature of the third inner wall surface is less than or equal to the temperature of the third indoor dew point, it is determined that the non-condensation requirement is not met.

[0202] In some embodiments, when the temperature of the third inner wall surface is less than or equal to the third indoor dew point temperature, it indicates that even if the air handling system controls the indoor temperature to the lowest theoretical value allowed for wet operation (the first minimum indoor temperature), the coldest point temperature of the inner surface of the building envelope is still lower than or equal to the dew point temperature of the indoor air, posing a clear risk of condensation. In this case, activating the heating module cannot directly solve the problem of the excessively low inner wall surface temperature. Therefore, the non-condensation requirement is ultimately determined not to be met.

[0203] In some embodiments, step S44 further includes the following step: Step S444, otherwise, calculate the second air supply sensible cooling load based on the air supply volume of the air supply module in the air handling system, the current indoor temperature, and the first minimum indoor temperature.

[0204] In some embodiments, when the temperature of the third inner wall surface is greater than the third indoor dew point temperature, i.e., at the first lowest indoor temperature, the inner surface of the building envelope is safe and there is no risk of condensation. In this case, it is necessary to calculate the sensible heat cooling capacity that the cooling module can provide under wet conditions. Based on the preset airflow rate of the air supply module in the air handling system, the specific heat capacity of the air at constant pressure, the current indoor temperature, and the first lowest indoor temperature, the second air supply sensible cooling load is calculated. The formula for calculating the second air supply sensible cooling load can be the same as described above and will not be repeated here. The second air supply sensible cooling load represents the sensible heat cooling capacity required to process the supply air from the current indoor temperature to the target temperature; a positive value indicates that cooling is required, and a negative value indicates that heating is required.

[0205] In some embodiments, step S44 further includes the following steps: step S445, obtaining the sensible heat load of the fourth person at the first lowest indoor temperature, calculating the sum of the sensible heat load of the fourth person and the other sensible heat loads in the room to obtain the second sensible heat load, and calculating the sum of the second supply air sensible cooling load and the third heat transfer load to obtain the second sensible cooling load.

[0206] In some embodiments, firstly, a fourth sensible heat load for occupants is obtained by looking up a table under a specific environment of a first minimum indoor temperature. Then, this fourth sensible heat load is added to other known, fixed sensible heat loads in the room (such as equipment, lighting heat dissipation, etc.) to obtain the total heat generated by all sensible heat sources in the room at the current target temperature, i.e., the second sensible heat load. Simultaneously, the second supply air sensible cooling load is added to the third heat transfer load (i.e., the net heat transfer through the building envelope) to obtain the total sensible cooling capacity that the air handling system is expected to provide under the current conditions, i.e., the second sensible cooling load.

[0207] In some embodiments, step S44 further includes the following step: step S446, determining the second sensible heat load and the second sensible cold load.

[0208] In some embodiments, by comparing the second sensible heat load and the second sensible cold load, it is possible to assess whether the cooling capacity provided by the air handling system under wet conditions matches the cooling demand required to maintain the first minimum indoor temperature, or whether there is excess capacity.

[0209] In some embodiments, step S44 further includes the following step: step S447, when the second sensible cold load is greater than the second sensible heat load, it is determined that the cooling module is in wet operating mode and the heating module is in heating mode.

[0210] In some embodiments, when the second sensible cooling load is greater than the second sensible heat load, it indicates that the total cooling capacity provided by the cooling module in wet operating mode exceeds the total heat gain required to maintain the indoor environment at the first minimum indoor temperature. If only the cooling module is operated, the indoor temperature will be over-cooled, potentially falling below the set first minimum indoor temperature target value. To stabilize the indoor temperature at the preset target value and fully utilize the dehumidification capacity of the cooling module, the air handling system needs to simultaneously activate the heating module. The heating module will provide an appropriate amount of compensating heat to offset the excess cooling capacity, thereby achieving temperature control. Therefore, the air handling system ultimately determines that the cooling module is in wet operating mode (responsible for dehumidification) and the heating module is in heating mode (responsible for providing compensating heating).

[0211] In some embodiments, after step S447, step S44 further includes the following steps: setting the operating parameters of the cooling module according to the design humidity upper limit and the first minimum indoor temperature; setting the operating parameters of the heating module according to the difference between the second sensible cooling load and the second sensible heat load.

[0212] In some embodiments, after determining that the cooling module is in wet operating mode and the heating module is in heating mode, specific parameters of the cooling module need to be set to ensure that it can effectively control indoor humidity and maintain it below the allowable design humidity upper limit, while taking into account that the indoor temperature has been set to the first minimum indoor temperature. The main function of the cooling module in wet operating mode is to cool and dehumidify the supply air through its surface cooler. The supply air temperature is usually low so that the air reaches a near-saturated state, thereby condensing moisture.

[0213] In some embodiments, provided that the indoor humidity does not exceed the design humidity limit and the indoor temperature is maintained at a first minimum indoor temperature, the moisture content corresponding to the indoor air state point can be calculated based on the design humidity limit and the first minimum indoor temperature. Subsequently, the operating parameters of the cooling module can be set using this moisture content to ensure control of the relative humidity in the spent fuel water tank hall.

[0214] In some embodiments, the difference between the second sensible cooling load and the second sensible heating load can be calculated. This difference represents the amount of compensating heating that the heating module needs to provide to prevent the indoor temperature from falling below a set value. The difference quantifies the net cooling effect generated by the cooling module beyond what is required by the indoor heat load. Without compensation, this net cooling effect will cause the indoor temperature to continue to drop. To maintain thermal balance, heat equal to this difference must be injected into the indoor environment. The operating parameters of the heating module are set based on this calculated compensating heat value. The air handling system calculates and sets specific operating parameters according to the performance characteristics of the heating equipment to ensure that its output heat equals the compensating heat.

[0215] In some embodiments, step S44 further includes the following step: step S448, otherwise, determine that the cooling module is in wet operating mode and the heating module is in shutdown mode.

[0216] In some embodiments, when the second sensible cooling load is less than or equal to the second sensible heat load, it indicates that the total cooling capacity provided by the cooling module in wet operating mode is just sufficient or insufficient to offset the total heat gain in the room. In the case of "equal to," the capacity and demand are perfectly balanced, requiring no additional heating. In the case of "less than," although the capacity is slightly insufficient, the air handling system may allow for a very small range of temperature fluctuations, or prioritize achieving the dehumidification target without activating the heating module (because heating increases energy consumption and contradicts the cooling target). Therefore, in both cases, the cooling module is determined to be in wet operating mode (responsible for dehumidification and all necessary cooling), and the heating module is in shutdown mode (no compensatory heating is required).

[0217] In some embodiments, after step S448, step S44 further includes the following steps: determining the second sensible heat load and the second sensible cold load; when the second sensible heat load equals the second sensible cold load, setting the operating parameters of the cooling module according to the upper limit of the design humidity and the first minimum indoor temperature; when the second sensible heat load is greater than the second sensible cold load, calculating the second target indoor temperature when the indoor air meets the thermal equilibrium state according to preset different fourth indoor temperatures; at the second target indoor temperature, calculating the second target relative humidity when the indoor air meets the humidity equilibrium state according to preset different second relative humidity; setting the operating parameters of the cooling module according to the second target indoor temperature and the second target relative humidity; wherein, the preset different fourth indoor temperatures are obtained by gradually adjusting the preset value based on the first minimum indoor temperature; the preset different second relative humidity are obtained by gradually adjusting the preset value based on the lower limit of the design humidity.

[0218] In some embodiments, when the second sensible heat load equals the second sensible cold load, this indicates that the cooling capacity of the cooling module and the sensible heat gain in the room can be balanced, and the indoor temperature can be stabilized at a preset first minimum indoor temperature without additional adjustments. The air handling system will set the operating parameters of the cooling module based on the design humidity upper limit and the first minimum indoor temperature.

[0219] In some embodiments, when the second sensible heat load is greater than the second sensible cooling load, it indicates that at the currently set first minimum indoor temperature, the sensible heat gain in the room exceeds the maximum sensible cooling capacity that the cooling module can provide under humid conditions, resulting in insufficient cooling capacity. If the first minimum indoor temperature is forcibly maintained, thermal balance cannot be achieved, and the temperature will rise uncontrollably. Therefore, a new, higher indoor temperature setpoint must be found so that the cooling capacity of the air handling system can balance the indoor heat gain at that temperature.

[0220] In some embodiments, this new equilibrium point can be found through iterative calculations. Based on a first minimum indoor temperature, the temperature is gradually adjusted upwards in a preset step size (e.g., 0.1°C or 0.5°C) to generate a series of preset fourth indoor temperatures. For each fourth indoor temperature, a series of calculations can be performed: First, based on this temperature, the current outdoor temperature, and the thermal performance parameters of the building envelope, the heat transfer through the building envelope is calculated using a predetermined heat transfer model. Next, based on the supply air volume, air specific heat capacity, and the difference between the current indoor temperature and the fourth indoor temperature, the sensible cooling load that the supply air can provide is calculated. Then, the sensible heat load of occupants corresponding to this fourth indoor temperature is obtained and added to other sensible heat loads in the room to obtain the total heat gain. Finally, the calculated total heat gain is compared with the total sensible cooling load provided by the air handling system. By iterating through all the preset fourth indoor temperatures, those temperature values ​​that make the total sensible cooling load of the air handling system equal to the total sensible heat load in the room are selected, and a suitable value is chosen from these temperatures that satisfy the heat balance condition as the second target indoor temperature.

[0221] In some embodiments, after determining the second target indoor temperature, it is necessary to find a relative humidity setpoint that can maintain humidity balance based on this new temperature. The humidity can be gradually adjusted upwards according to a preset step size (e.g., 1%) based on the design humidity lower limit, generating a series of preset second relative humidity levels. For each second relative humidity, a humidity balance calculation can be performed: First, at a fixed second target indoor temperature, the corresponding indoor air moisture content is calculated based on the currently assumed second relative humidity. Then, the dehumidification capacity under this condition is calculated, including supply air dehumidification (based on supply air volume and the supply air moisture content provided by the cooling module under wet conditions) and exhaust air dehumidification (based on exhaust air volume and indoor moisture content), and these two parts are added together to obtain the total dehumidification capacity. Next, the total indoor moisture production is calculated, including the water tank evaporation moisture load (calculated based on the second target indoor temperature, the calculated moisture content, and the waste tank parameters), the corresponding personnel moisture load at this temperature and humidity, and other known indoor moisture loads. Finally, the total dehumidification capacity is compared with the total indoor moisture production. All preset second relative humidity levels are iterated through to obtain the second target relative humidity. The screening process for the second target relative humidity is the same as that for the first target relative humidity, and will not be repeated here.

[0222] In some embodiments, finally, all necessary operating parameters of the cooling module, such as the opening degree of the chilled water valve, the chilled water temperature, and the fan speed, can be set based on the second target indoor temperature and the second target relative humidity to ensure that the indoor environment can be stabilized at the same time near the second target indoor temperature and the second target relative humidity in the wet operating mode, so as to achieve a new thermal and humidity balance.

[0223] As can be seen, the above solution effectively solves the problem of low efficiency caused by traditional manual iterative calculations through a systematic automated trial-and-error process. Based on design temperature / humidity limits, and by gradually adjusting preset temperature values, the first and second minimum indoor temperatures that meet the humidity balance conditions are calculated respectively, and the operating modes of the cooling and heating modules are determined accordingly. This structured calculation method avoids the manual operation of repeatedly consulting enthalpy-humidity charts required in traditional methods, significantly improving the accuracy and efficiency of operating condition determination. Simultaneously, by automatically optimizing the lowest feasible temperature point, the energy consumption of the air handling system is optimized while ensuring anti-condensation requirements, providing a safe and economical operating solution for nuclear power plant HVAC systems.

[0224] Please see Figure 3 The present invention also discloses a control device for an air handling system, and the above-described control method can be applied to the control device. The control device may include a moisture content calculation module 210, a first temperature calculation module 220, a second temperature calculation module 230, and an operating condition judgment module 240.

[0225] In some embodiments, the moisture content calculation module 210 can be used to calculate the current moisture content of indoor air in the current state based on the current indoor temperature and current relative humidity.

[0226] In some embodiments, the first temperature calculation module 220 can be used to calculate the lowest first indoor temperature when the indoor air satisfies the humidity balance state, and is recorded as the first lowest indoor temperature, according to different preset first indoor temperatures, when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature; wherein, the different preset first indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature.

[0227] In some embodiments, the second temperature calculation module 230 can be used to calculate the lowest second indoor temperature when the indoor air meets the humidity balance state, based on the first supply air moisture content of the cooling module at each second indoor temperature, according to different preset second indoor temperatures and when the relative humidity of the indoor air is at the upper limit of the design humidity, and denoted as the second lowest indoor temperature; wherein, the different preset second indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature; the first supply air moisture content is calculated based on the current moisture content.

[0228] In some embodiments, the operating condition judgment module 240 can be used to determine the operating mode of the cooling module and the heating module based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature and the preset design temperature upper limit value.

[0229] For specific limitations regarding the control device, please refer to the limitations of the control method above, which will not be repeated here. Each module in the aforementioned control device can be implemented entirely or partially through software, hardware, or a combination thereof. These modules can be embedded in hardware or independently of the memory in the electronic device, or stored in software form in the memory of the electronic device, so that the memory can call and execute the operations corresponding to each module.

[0230] Please see Figure 4 In some embodiments, the electronic device 10 may include a memory 11, a processor 12, and a bus, and may also include a computer program stored in the memory 11 and executable on the processor 12, such as a program for a control method of an air handling system.

[0231] In some embodiments, the memory 11 includes at least one type of readable storage medium, including flash memory, portable hard drive, multimedia card, card-type memory (e.g., SD or DX memory), magnetic memory, magnetic disk, optical disk, etc. In some embodiments, the memory 11 can be an internal storage unit of the electronic device 10, such as the portable hard drive of the electronic device 10. In other embodiments, the memory 11 can also be an external storage device of the electronic device 10, such as a plug-in portable hard drive, smart media card (SMC), secure digital card (SD), flash card, etc., equipped on the electronic device 10. Furthermore, the memory 11 can include both internal storage units and external storage devices of the electronic device 10. The memory 11 can be used not only to store application software and various types of data installed on the electronic device 10, such as the code of control methods for air handling systems, but also to temporarily store data that has been output or will be output.

[0232] In some embodiments, the processor 12 may be composed of integrated circuits, such as a single packaged integrated circuit or multiple integrated circuits packaged with the same or different functions, including combinations of one or more central processing units (CPUs), microprocessors, digital processing chips, graphics processors, and various control chips. The processor 12 is the control unit of the electronic device 10, connecting various components of the electronic device 10 via various interfaces and lines. It executes programs or modules stored in the memory 11 (e.g., programs for control methods of an air handling system) and calls data stored in the memory 11 to perform various functions and process data of the electronic device 10.

[0233] In some embodiments, the processor 12 executes the operating system of the electronic device 10 and various installed applications. The processor 12 executes the applications to implement the steps in the control method of the air handling system described above.

[0234] In some embodiments, the computer program may be divided into one or more modules, one or more of which are stored in the memory 11 and executed by the processor 12 to complete the present application. One or more modules may be a series of computer program instruction segments capable of performing specific functions, which describe the execution process of the computer program in the electronic device 10. For example, the computer program may be divided into a moisture content calculation module 210, a first temperature calculation module 220, a second temperature calculation module 230, a working condition judgment module 240, etc.

[0235] The above embodiments are merely illustrative of the principles and effects of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should still be covered by the claims of the present invention.

Claims

1. A control method for an air handling system, characterized in that, An air handling system applied in a nuclear power plant, the air handling system including a cooling module and a heating module, the control method including: Calculate the current moisture content of the indoor air under the current conditions based on the current indoor temperature and current relative humidity. According to different preset first indoor temperatures, when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature, the lowest first indoor temperature when the indoor air meets the moisture balance state is calculated and recorded as the first lowest indoor temperature; wherein, the different preset first indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature. According to different preset second indoor temperatures, when the relative humidity of the indoor air is at the upper limit of the design humidity, the lowest second indoor temperature when the indoor air meets the humidity balance state is calculated based on the first supply air moisture content of the cooling module at each second indoor temperature, and is recorded as the second lowest indoor temperature; wherein, the different preset second indoor temperatures are obtained by gradually adjusting according to the preset lower limit of the design temperature; the first supply air moisture content is calculated based on the current moisture content; The operating modes of the cooling module and the heating module are determined based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit.

2. The control method for the air handling system according to claim 1, characterized in that, The calculation of the current humidity content of the indoor air under the current conditions, based on the current indoor temperature and current relative humidity, includes: In a preset water vapor partial pressure mapping table, the saturated water vapor partial pressure of indoor air in a saturated state is obtained based on the current indoor temperature of the indoor air; wherein, the water vapor partial pressure mapping table represents the mapping relationship between the current indoor temperature of indoor air and the saturated water vapor partial pressure of indoor air in a saturated state. Calculate the current water vapor partial pressure based on the saturated water vapor partial pressure and the current relative humidity of the indoor air; Calculate the current humidity content of the indoor air under the current conditions based on the current water vapor partial pressure and atmospheric pressure.

3. The control method for the air handling system according to claim 1, characterized in that, The calculation of the lowest first indoor temperature when the indoor air meets the humidity balance state, denoted as the first lowest indoor temperature, includes: When the relative humidity of the indoor air is at the preset upper limit of the design humidity, the corresponding first indoor moisture content, first waste tank wet load, and first personnel wet load are calculated according to the preset different first indoor temperatures. The first supply air wet load is obtained by multiplying the saturated moisture content by the supply air volume of the air supply module in the air handling system. The first exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the humidity of each of the first indoor spaces; wherein, the first exhaust moisture load = first indoor humidity × exhaust volume; At each first indoor temperature, the difference between the first exhaust moisture load and the first supply air moisture load is calculated to obtain the corresponding first exhaust moisture load; The first generated wet load is obtained by acquiring and calculating the sum of other indoor wet loads, the first wastewater pool wet load, and the first personnel wet load; The first indoor temperature that is greater than or equal to the first generated wet load is retained, and the lowest value of the retained first indoor temperature is selected and recorded as the first lowest indoor temperature.

4. The control method for the air handling system according to claim 1, characterized in that, The lowest second indoor temperature at which the indoor air meets the humidity balance state is denoted as the second lowest indoor temperature, including: When the relative humidity of the indoor air is at the upper limit of the design humidity, the corresponding second indoor humidity, second waste pool wet load, second personnel wet load, and first supply air humidity are calculated according to the preset second indoor temperature. The corresponding second supply air wet load is obtained by multiplying the supply air volume of the air supply module in the air handling system with the moisture content of each first supply air. The corresponding second exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the humidity of each second indoor unit; wherein, the second exhaust moisture load = second indoor humidity × exhaust volume; At each second indoor temperature, the difference between the second exhaust moisture load and the second supply air moisture load is calculated to obtain the corresponding second exhaust moisture load; The second generated wet load is obtained by summing the other indoor wet loads, the second wastewater wet load, and the second personnel wet load; The second indoor temperature that is greater than or equal to the second generated wet load is retained, and the lowest value of the retained second indoor temperature is selected and recorded as the second lowest indoor temperature.

5. The control method for the air handling system according to claim 1, characterized in that, The step of determining the operating modes of the cooling module and the heating module based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit includes: Determine the first minimum indoor temperature, the second minimum indoor temperature, and the preset upper limit of the design temperature: When both the first minimum indoor temperature and the second minimum indoor temperature are greater than the upper limit of the design temperature, it is determined that the non-condensation requirement is not met. When the first minimum indoor temperature is greater than the second minimum indoor temperature, and the second minimum indoor temperature is less than or equal to the upper limit of the design temperature, the cooling module is determined to be in dry operating mode or shutdown mode. When the first minimum indoor temperature is less than or equal to the second minimum indoor temperature, and the first minimum indoor temperature is less than or equal to the upper limit of the design temperature, the cooling module is determined to be in wet operating mode.

6. The control method for the air handling system according to claim 5, characterized in that, The determination of whether the cooling module is in dry operating mode or shutdown mode includes: At the second lowest indoor temperature, the first heat transfer load of the building envelope is calculated based on the obtained outdoor temperature and thermal performance parameters of the building envelope. Based on the other sensible heat loads in the room, the first sensible heat load of occupants at the second lowest indoor temperature, and the first heat transfer load, determine whether the indoor air meets the thermal equilibrium state: When the indoor air meets the thermal equilibrium state, it is determined that both the cooling module and the heating module are in shutdown mode. Otherwise, the cooling module is determined to be in dry operating mode or shutdown mode.

7. The control method for the air handling system according to claim 6, characterized in that, The determination of whether the cooling module is in dry operating mode or shutdown mode also includes: When the cooling module is in dry operating mode, the first target indoor temperature when the indoor air meets the thermal equilibrium state is calculated according to different preset third indoor temperatures; wherein, the different preset third indoor temperatures are obtained by gradually adjusting the second minimum indoor temperature according to preset values. At the first target indoor temperature, the first target relative humidity when the indoor air meets the humidity balance state is calculated according to different preset first relative humidity; wherein, the different preset first relative humidity is obtained by gradually adjusting according to the preset value based on the design humidity lower limit value. The operating parameters of the cooling module are set according to the first target indoor temperature and the first target relative humidity.

8. The control method for the air handling system according to claim 7, characterized in that, The step of calculating the first target indoor temperature when the indoor air meets the thermal equilibrium state according to different preset third indoor temperatures includes: Based on the preset different third indoor temperatures, and according to the outdoor temperature and the thermal performance parameters of the building envelope, the second heat transfer load corresponding to the building envelope is calculated. At each of the third indoor temperatures, the corresponding first sensible cooling load is calculated based on the air supply volume of the air supply module in the air handling system and the design air supply temperature of the cooling module; wherein, the first sensible cooling load = air supply volume × specific heat of air × (third indoor temperature - design air supply temperature). At each of the third indoor temperatures, the sum of the other indoor sensible heat loads and the second sensible heat load of the occupants at the third indoor temperature is used to obtain the first sensible heat load. The sum of the second heat transfer load and the first air supply sensible cooling load is used to obtain the first sensible cooling load. The third indoor temperature is retained when the first sensible cooling load is greater than or equal to the corresponding first sensible heat load. The lowest value of the retained third indoor temperature between the lower limit of the design temperature and the upper limit of the design temperature is selected and denoted as the first target indoor temperature.

9. The control method for the air handling system according to claim 7, characterized in that, The step of calculating the first target relative humidity when the indoor air meets the humidity balance state according to different preset first relative humidityes at the first target indoor temperature includes: At the first target indoor temperature, the third indoor humidity content corresponding to the indoor air is calculated according to different preset first relative humidities; Under each of the first relative humidities, the product of the air supply volume of the air supply module in the air handling system and the second supply air moisture content of the air supply module is calculated to obtain the corresponding third supply air wet load. Under each of the first relative humidity conditions, the corresponding third exhaust moisture load is calculated based on the exhaust volume of the return / exhaust air module in the air handling system and the corresponding third indoor humidity; wherein, the third exhaust moisture load = exhaust volume × third indoor humidity. Under each of the first relative humidities, the corresponding third wet load of the waste tank is calculated based on the first target indoor temperature and the corresponding third indoor moisture content; At each of the first relative humidities, the difference between the third supply air wet load and the third exhaust wet load is calculated to obtain the third exhaust wet load. The third waste pool wet load, the third personnel wet load at the first target indoor temperature, and other indoor wet loads are calculated to obtain the third generation wet load. The first relative humidity is retained when the third discharge moisture load is greater than or equal to the corresponding third generation moisture load. The lowest value of the retained first relative humidity is selected and recorded as the first target relative humidity.

10. The control method for the air handling system according to claim 7, characterized in that, The step of calculating the first target indoor temperature when the indoor air meets the thermal equilibrium state according to preset different third indoor temperatures when the cooling module is in dry operating mode further includes: At the first target indoor temperature, the first inner wall temperature and the first indoor dew point temperature of the building envelope are calculated based on the outdoor temperature and the thermal performance parameters of the building envelope. Determine the temperature of the first inner wall surface and the temperature of the first indoor dew point: If the temperature of the first inner wall surface is less than or equal to the first indoor dew point temperature, it is determined that the requirement of no condensation is not met.

11. The control method for the air handling system according to claim 6, characterized in that, The determination of whether the cooling module is in dry operating mode or shutdown mode also includes: When the cooling module is in shutdown mode, at the second lowest indoor temperature, the second inner wall temperature and the second indoor dew point temperature of the building envelope are calculated based on the outdoor temperature and the thermal performance parameters of the building envelope. Determine the temperature of the second inner wall surface and the temperature of the second indoor dew point: When the temperature of the second inner wall surface is less than or equal to the temperature of the second indoor dew point, it is determined that the non-condensation requirement is not met. Otherwise, the total sensible heat load is obtained by calculating the sum of the first sensible heat load and the other sensible heat loads in the room, and the difference between the total sensible heat load and the first heat transfer load is determined: when the difference is equal to 0, the heating module is determined to be in shutdown mode; otherwise, the operating parameters of the heating module are set according to the difference.

12. The control method for the air handling system according to claim 5, characterized in that, The determination that the cooling module is in a wet operating mode includes: At the first lowest indoor temperature, based on the outdoor temperature and the thermal performance parameters of the building envelope, the third heat transfer load of the building envelope, the third inner wall surface temperature of the building envelope, and the third indoor dew point temperature are calculated. Determine the temperature of the third inner wall surface and the temperature of the third indoor dew point: When the temperature of the third inner wall surface is less than or equal to the dew point temperature of the third room, it is determined that the requirement of no condensation is not met. Otherwise, the second air supply sensible cooling load is calculated based on the air supply volume of the air supply module in the air handling system, the current indoor temperature, and the first lowest indoor temperature; Obtain the sensible heat load of the fourth person at the first lowest indoor temperature, calculate the sum of the sensible heat load of the fourth person and the other sensible heat loads in the room to obtain the second sensible heat load, and calculate the sum of the second supply air sensible cooling load and the third heat transfer load to obtain the second sensible cooling load. Determine the second sensible heat load and the second sensible cold load: When the second sensible cooling load is greater than the second sensible heat load, it is determined that the cooling module is in wet operating mode and the heating module is in heating mode. Otherwise, the cooling module is determined to be in wet operating mode and the heating module is in shutdown mode.

13. The control method for the air handling system according to claim 12, characterized in that, After determining that the cooling module is in wet operating mode and the heating module is in heating mode, the method further includes: The operating parameters of the cooling module are set according to the upper limit of the designed humidity and the first minimum indoor temperature. The operating parameters of the heating module are set based on the difference between the second sensible cold load and the second sensible heat load.

14. The control method for the air handling system according to claim 12, characterized in that, After determining that the cooling module is in wet operating mode and the heating module is in shutdown mode, the method further includes: Determine the second sensible heat load and the second sensible cold load: When the second sensible heat load equals the second sensible cold load, the operating parameters of the cooling module are set according to the upper limit of the design humidity and the first minimum indoor temperature. When the second sensible heat load is greater than the second sensible cold load, the second target indoor temperature when the indoor air meets the thermal equilibrium state is calculated according to different preset fourth indoor temperatures; at the second target indoor temperature, the second target relative humidity when the indoor air meets the humidity equilibrium state is calculated according to different preset second relative humidity; the operating parameters of the cooling module are set according to the second target indoor temperature and the second target relative humidity; wherein, the different preset fourth indoor temperatures are obtained by gradually adjusting the preset values ​​based on the first minimum indoor temperature; the different preset second relative humidity are obtained by gradually adjusting the preset values ​​based on the design humidity lower limit.

15. A control device for an air handling system, characterized in that, The control method for the air handling system as described in any one of claims 1 to 14, wherein the control device comprises: The moisture content calculation module is used to calculate the current moisture content of indoor air under the current conditions based on the current indoor temperature and current relative humidity. The first temperature calculation module is used to calculate the lowest first indoor temperature when the indoor air meets the humidity balance state, based on different preset first indoor temperatures, and when the relative humidity of the indoor air is the preset upper limit of the design humidity and the moisture content of the supply air of the cooling module is the saturated moisture content at the supply air temperature. This lowest first indoor temperature is denoted as the first minimum indoor temperature. The different preset first indoor temperatures are obtained by gradually adjusting the preset lower limit of the design temperature according to the preset value. The second temperature calculation module is used to calculate the lowest second indoor temperature when the indoor air meets the humidity balance state, based on the first supply air moisture content of the cooling module at each second indoor temperature, and when the relative humidity of the indoor air is at the upper limit of the design humidity, according to different preset second indoor temperatures. This lowest second indoor temperature is denoted as the second minimum indoor temperature. The different preset second indoor temperatures are obtained by gradually adjusting the preset lower limit of the design temperature. The first supply air moisture content is calculated based on the current moisture content. The operating condition judgment module is used to determine the operating mode of the cooling module and the heating module based on the comparison results of the first minimum indoor temperature, the second minimum indoor temperature, and the preset design temperature upper limit value.

16. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, The steps of the control method for the air handling system as described in any one of claims 1 to 14 are implemented when the processor executes the computer program.

17. A computer-readable storage medium storing a computer program, characterized in that, When the computer program is executed by the processor, it implements the steps of the control method for the air handling system as described in any one of claims 1 to 14.

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