Air energy-carrying air conditioning system and energy transfer and complementary thermal comfort regulation and control method thereof

Abstract

The invention provides an air energy-carrying air conditioning system and an energy transfer and complementary thermal comfort regulation and control method thereof, and belongs to the technical field of temperature regulation and control. Comprising the steps of 1, calculating the radiation heat exchange amount of a pore plate; 2, the natural convection heat exchange amount is calculated; 3, the permeation heat exchange amount is calculated according to the air supply amount sent to the indoor air conditioner area through the pore plate micropores; 4, according to the material characteristics, the thickness and the surface heat exchange characteristics of the enclosure structure, the heat transfer amount of the enclosure structure is calculated; 5, an energy balance model based on space coupling is constructed, and the average indoor air temperature is calculated; and 6, obtaining a complementary relationship among the surface temperature of the enclosure structure, the average air temperature and the PMV, and obtaining a complementary prediction model of the average indoor air temperature and the PMV. According to the method, an average air temperature prediction model is provided and established, and fine description of radiation, convection, permeation and heat transfer of the enclosure structure is realized by dividing a buffer energy storage area and an air conditioning area.

Description

Technical Field

[0001] This invention belongs to the field of indoor temperature prediction technology, and particularly relates to an air-powered air conditioning system and its energy transfer and complementary thermal comfort control method, which is applicable to thermal comfort prediction and system optimization design. Background Technology

[0002] The heat exchange between an air-source heat pump system and the indoor environment can be divided into three main mechanisms: first, the radiative energy transfer between the perforated plate and various indoor surfaces; second, the natural convection energy transfer between the perforated plate surface and the indoor air; and third, the energy transfer generated by the airflow permeating through the micropores during diffusion. If the radiative heat transfer in the system exceeds half of the total energy transfer, this terminal can be classified as a radiation-dominated heat exchange terminal, which can significantly improve the thermal comfort of the residents.

[0003] Existing technologies already include models for predicting average air temperature, such as the air-powered system and its dynamic control method disclosed in CN118896347A, which calculates the equivalent thermal resistance by real-time detection of physical parameters (such as heat flux density and air volume). and heat capacity Predict system startup response time This method enables dynamic start-stop control. However, it has the following limitations: 1) It relies on real-time detection: multiple sets of sensors need to be deployed, which is costly and complex to maintain; 2) It is only applicable to control scenarios: the energy allocation accuracy problem in the system design stage is not solved; 3) It ignores thermal comfort weights: the differential impact of the building envelope on the thermal comfort evaluation PMV and its complementary factors is not quantified. Summary of the Invention

[0004] This invention provides an air-powered air conditioning system and its energy transfer and complementary thermal comfort control method, which trains thermal comfort contribution weights using historical data to achieve high-precision thermal environment prediction.

[0005] To achieve the above objectives, the technical solution of the present invention is: an air-source heat pump air conditioning system and its energy transfer and complementary thermal comfort control method, used for predicting the energy transfer of a building's air-source heat pump system, comprising the following steps: Step 1: Collect the surface area and average absolute temperature of the radiant perforated plate, as well as the surface area and average absolute temperature of the four walls and floor enclosure structures that make up the building space. By unifying and simplifying the five enclosure structure surfaces of the building space into a hypothetical wall, the radiative heat transfer between the surface of the radiant perforated plate and the entire space is equivalent to the radiative energy exchange between the perforated plate and the hypothetical wall, and calculate the radiative heat transfer of the perforated plate. Step 2: Calculate the natural convection heat transfer based on the surface area of ​​the radiant perforated plate, the average temperature of the surface of the radiant perforated plate, and the average temperature of the indoor air. Step 3: Calculate the infiltration heat transfer based on the air volume supplied to the indoor air-conditioned area through the micropores of the perforated plate; Step 4: Calculate the heat transfer of the enclosure structure based on its material properties, thickness, and surface heat transfer characteristics. Step 5: Construct an energy balance model based on spatial coupling. In this model, the total energy provided by the air conditioning system includes the energy of the buffer storage area, the energy of the indoor air conditioning area, and the heat transfer of the building envelope. The energy of the indoor air conditioning area consists of perforated plate radiation heat transfer, natural convection heat transfer, and infiltration heat transfer, thereby calculating the average indoor air temperature. Step 6: Based on the average indoor air temperature, historical operating data analysis is performed by linear regression of different building envelope surface temperatures on the average indoor air temperature, and linear regression of different building envelope surface temperatures and average air temperatures on the thermal comfort evaluation index (PMV, Predicted Mean Vote). This yields a complementary predictive model for the average indoor air temperature and PMV, demonstrating the complementary relationship between building envelope surface temperature, average air temperature, and PMV.

[0006] Furthermore, the formula for calculating the radiative heat transfer of the orifice plate is as follows: ; ; ; ; ; in, The heat transfer rate of the orifice plate is measured in W. The radiative heat transfer per unit area of ​​the orifice plate is expressed in W / m². 2 ; The radiative heat transfer coefficient is expressed in W / (m²). 2 ·K); The surface area of ​​the perforated plate, in meters. 2 ; It is the Stefan-Boltzmann constant. =5.67×10 -8 W / (m 2 ·K 4 ), is the dimensionless radiation angle coefficient between the hypothetical wall and the orifice plate surface; The average absolute temperature of the orifice plate surface, in K; The mean absolute temperature of the hypothetical wall, in Kelvin (K). The unit is the surface area of ​​all surfaces of the enclosure structure (four walls and floor) excluding the perforated plate, expressed in m². 2 ; Emissivity is the dimensionless emissivity of each surface of the enclosure structure (four walls and floor) excluding the perforated plate. The average absolute temperature of all surfaces of the building envelope (four walls and floor) excluding the perforated plate, in K; The equivalent radiation angle coefficient of the hypothetical wall and ceiling surfaces is dimensionless. Let be the emissivity of the orifice plate surface, which is dimensionless.

[0007] Furthermore, the formula for calculating the natural convection heat transfer is as follows: ; ; ; ; ; in, Heat exchanged via natural convection, measured in W. For Nusselt numbers; For Grashof numbers; It is a Prandtl number; The natural convection heat transfer coefficient is expressed in W / (m²). 2 K); C and n are dimensionless constants determined experimentally; The average surface temperature of the top plate is expressed in °C. The average indoor air temperature is expressed in °C. is the thermal conductivity of the fluid, expressed in W / (m·K); Characteristic length, in meters; Acceleration due to gravity, unit m / s² 2 ; The coefficient of volume expansion is expressed in units of 1 / K. Kinematic viscosity, unit: m 2 / s; Thermal diffusivity, in meters (m) 2 / s.

[0008] Furthermore, the operating conditions of perforated plate heating: Orifice plate cooling operation: .

[0009] Furthermore, the formula for calculating the heat transfer rate is as follows: ,in The heat transfer through the perforated plate micropores into the indoor air-conditioned area is expressed in W. Air density, unit: kg / m³ 3 ; Specific heat capacity of air at constant pressure, in J / kg·℃; V represents the temperature of the air entering the indoor air-conditioned zone through the orifice plate for heat exchange, in °C; V represents the amount of infiltrated energy-carrying air entering the indoor air-conditioned zone through the orifice plate, in m³. 3 / s.

[0010] Furthermore, the formula for calculating the heat transfer of the building envelope is as follows: ; ,in, The total heat transfer on surface i of the building envelope, in W; The heat transfer area of ​​surface i of the building envelope, in meters. 2 ; The inner surface temperature of surface i of the building envelope, in °C; The outer surface temperature of the enclosure structure surface i, in °C; The overall heat transfer coefficient of the building envelope i is given by W / (m²). 2 ·K), where δi is the thickness of surface i of the enclosure structure, in meters; Let i be the thermal conductivity of the building envelope, expressed in W / (m·K). , Here, i represents the heat transfer coefficients of the inner and outer surfaces of the building envelope, respectively, in W / (m²). 2 ·K).

[0011] Furthermore, based on a spatially coupled energy balance model, the average indoor air temperature is calculated: ; = ; = ; ; ; ; Based on the energy balance equation above, the formula for calculating the average indoor air temperature is given under two operating conditions: During heating season, , When cooling is provided, ; in, The total energy provided to the air conditioning system To buffer the energy in the energy storage area, The energy for the indoor air-conditioned area (radiative heat transfer calculated in step 1) Step 2 calculates the natural convection heat transfer. Step 3 calculates the osmotic heat transfer. composition), For the heat transfer of the building envelope (calculated in step 4); The system's supply air temperature is expressed in °C. The return air temperature of the energy storage area is expressed in °C. The weighted average temperature of the non-radiative wall surface is expressed in °C.

[0012] Furthermore, the algorithm for the complementary model of indoor average air temperature and PMV uses univariate linear regression analysis to intuitively determine the degree of direct influence of different wall temperatures on the average air temperature. , , b is the correlation coefficient, c is a constant, and the regression coefficient R0 satisfies the condition. 2 A regression coefficient greater than 0.85 indicates a stronger response of the average air temperature to changes in the corresponding wall surface temperature, higher sensitivity, and a faster rate of increase in the average air temperature. Principal component analysis was used to determine the relationship between each wall surface temperature and the average air temperature. The weights are used to obtain the average indoor air temperature. and Complementary model of thermal comfort evaluation indices , .

[0013] Furthermore, in step 6, the historical data includes the building envelope temperature, air supply parameters, and thermal comfort feedback data under typical winter and summer operating conditions.

[0014] The beneficial effects of this invention are: This invention proposes and establishes an average air temperature prediction model. By dividing the area into a buffer energy storage zone and an air-conditioning zone, it achieves a refined description of radiation, convection, infiltration, and heat transfer through the building envelope. The established energy transfer calculation method can calculate the heat transfer through air infiltration between the energy storage zone and the air-conditioning zone. Furthermore, the energy balance model comprehensively considers multiple energy transfer modes, including radiative heat transfer, convective heat transfer, perforated plate infiltration heat transfer, and heat transfer through the building envelope, making it a more accurate and convenient method for predicting average indoor air temperature.

[0015] Furthermore, the complementary relationship model between the building envelope, indoor average air temperature, and human thermal comfort PMV proposed in this invention determines the comprehensive influence weights of each wall surface temperature and the average air temperature, providing theoretical support for building design optimization. This facilitates accurate regulation and control of the indoor environment to optimize indoor thermal comfort and reduce energy consumption. By deepening the understanding of the complementary relationship between radiant terminals and the building envelope, this research provides theoretical support and practical guidance for energy-saving building design and indoor environment optimization, promoting the development and application of green building technologies. Attached Figure Description

[0016] Figure 1 Schematic diagram of spatial division of air-based energy-carrying radiation system; Figure 2 Average indoor air temperature at 1.1m under typical operating conditions with ceiling-mounted radiant terminals. Detailed Implementation

[0017] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0018] Furthermore, the technical solutions of the various embodiments of the present invention can be combined with each other, but only if they are feasible for those skilled in the art. If the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such combination of technical solutions does not exist and is not within the scope of protection claimed by the present invention.

[0019] Step 1: Collect the surface area and average absolute temperature of the radiant perforated plate, as well as the surface area and average absolute temperature of the four walls and floor enclosure of the building space. By simplifying the five enclosure surfaces of the building space into a single imaginary wall, the radiative heat transfer between the surface of the radiant perforated plate and the entire space is equivalent to the radiative energy exchange between the perforated plate and this imaginary wall. Calculate the radiative heat transfer of the perforated plate, which is used to form the energy of the indoor air-conditioned zone. The formula for calculating the radiative heat transfer of the perforated plate is as follows: ; ; ; ; ; in, The heat transfer rate of the orifice plate is measured in W. The radiative heat transfer per unit area of ​​the orifice plate is expressed in W / m². 2 ; The radiative heat transfer coefficient is expressed in W / (m²). 2 ·K); The surface area of ​​the perforated plate, in meters. 2 ; It is the Stefan-Boltzmann constant. =5.67×10 -8 W / (m 2 ·K 4 ), is the dimensionless radiation angle coefficient between the hypothetical wall and the orifice plate surface; The average absolute temperature of the orifice plate surface, in K; The mean absolute temperature of the hypothetical wall, in Kelvin (K). The unit is the surface area of ​​all surfaces of the enclosure structure (four walls and floor) excluding the perforated plate, expressed in m². 2 ; Emissivity is the dimensionless emissivity of each surface of the enclosure structure (four walls and floor) excluding the perforated plate. The average absolute temperature of all surfaces of the building envelope (four walls and floor) excluding the perforated plate, in K; The equivalent radiation angle coefficient of the hypothetical wall and ceiling surfaces is dimensionless. The emissivity of the orifice plate surface is dimensionless. Step 2: Calculate the natural convection heat transfer based on the surface area of ​​the radiant perforated plate, the average temperature of the radiant perforated plate surface, and the average indoor air temperature. This heat transfer is used to form the energy for the indoor air-conditioned area. The formula for calculating the natural convection heat transfer is: ; ; ; ; ; in, This refers to heat transfer via natural convection, measured in W / m³. 2 ; For Nusselt numbers; For Grashof numbers; It is a Prandtl number; The natural convection heat transfer coefficient is expressed in W / (m²). 2 K); C and n are dimensionless constants determined experimentally; The average surface temperature of the top plate is expressed in °C. The average indoor air temperature is expressed in °C. is the thermal conductivity of the fluid, expressed in W / (m·K); Characteristic length, in meters; Acceleration due to gravity, unit m / s² 2 ; The coefficient of volume expansion is expressed in units of 1 / K. Kinematic viscosity, unit: m 2 / s; Thermal diffusivity, in meters (m) 2 / s; Orifice plate heating operation: Orifice plate cooling operation: .

[0020] Step 3: The infiltration heat transfer calculated based on the air volume supplied to the indoor air-conditioned zone through the micropores of the perforated plate is also used to constitute the energy of the indoor air-conditioned zone. The calculation formula for the infiltration heat transfer is: ,in The heat transfer through the perforated plate micropores into the indoor air-conditioned area is expressed in W. Air density, unit: kg / m³ 3 ; Specific heat capacity of air at constant pressure, in J / kg·℃; V represents the temperature of the air entering the indoor air-conditioned zone through the orifice plate for heat exchange, in °C; V represents the amount of infiltrated energy-carrying air entering the indoor air-conditioned zone through the orifice plate, in m³. 3 / s; Step 4: Calculate the heat transfer of the enclosure structure based on its material properties, thickness, and surface heat transfer characteristics. The formula for calculating the heat transfer of the enclosure structure is as follows: ; ,in, The total heat transfer on surface i of the building envelope, in W; The heat transfer area of ​​surface i of the building envelope, in meters. 2 ; The inner surface temperature of surface i of the building envelope, in °C; The outer surface temperature of the enclosure structure surface i, in °C; The overall heat transfer coefficient of the building envelope i is given by W / (m²). 2 ·K), where δi is the thickness of surface i of the enclosure structure, in meters; Let i be the thermal conductivity of the building envelope, expressed in W / (m·K). , Here, i represents the heat transfer coefficients of the inner and outer surfaces of the building envelope, respectively, in W / (m²). 2 ·K); Step 5: Construct an energy balance model based on spatial coupling. (See [link]) Figure 1 The indoor space to be predicted is divided into buffer energy storage area 1 and air-conditioning area 2. The total energy provided by the air-conditioning system in this model includes the energy of the buffer energy storage area, the energy of the indoor air-conditioning area and the heat transfer of the building envelope. The energy of the indoor air-conditioning area consists of perforated plate radiation heat transfer, natural convection heat transfer and infiltration heat transfer, so as to calculate the average indoor air temperature. Calculate the average indoor air temperature: ; = ; = ; ; ; ; Based on the energy balance equation for the average indoor air temperature constructed above, the calculation formula is for temperatures under two operating conditions: during heating: , When cooling is provided, ; in, The total energy provided to the air conditioning system To buffer the energy in the energy storage area, The energy for the indoor air-conditioned area (radiative heat transfer calculated in step 1) Step 2 calculates the natural convection heat transfer. Step 3 calculates the osmotic heat transfer. composition), The heat transfer of the building envelope is calculated in step 4. Since the buffer energy storage area is equipped with a thermal insulation layer, its heat loss can be effectively reduced. Therefore, the heat transfer of the building envelope is negligible compared to other forms of heat exchange. Mainly from air-conditioned areas; The system's supply air temperature is expressed in °C. The return air temperature of the energy storage area is expressed in °C. The weighted average temperature of the non-radiative wall surface, in °C; Step 6: Based on the indoor average air temperature, historical operational data analysis is performed by linear regression of different building envelope surface temperatures on the indoor average air temperature, and linear regression of different building envelope surface temperatures and the average air temperature on PMV. Historical data includes building envelope temperatures, air supply parameters, and thermal comfort feedback data under typical winter and summer conditions. This yields a complementary relationship between building envelope surface temperature, average air temperature, and PMV, resulting in a complementary prediction model for indoor average air temperature and PMV. The algorithm for this complementary model uses univariate linear regression analysis to intuitively determine the direct impact of different wall surface temperatures on the average air temperature. , , b is the correlation coefficient, c is a constant, and the regression coefficient R0 satisfies the condition. 2 A regression coefficient greater than 0.85 indicates a stronger response of the average air temperature to changes in the corresponding wall surface temperature, higher sensitivity, and a faster rate of increase in the average air temperature. Principal component analysis was used to determine the relationship between each wall surface temperature and the average air temperature. The weights are used to obtain the average indoor air temperature. and Complementary model of thermal comfort evaluation indices , k and m are correlation coefficients, and c is a constant, satisfying the regression coefficient R0. 2 Greater than 0.9. Walls with smaller k values ​​have a lower weight in influencing the average air temperature, and respond faster to heat transfer and temperature changes in the indoor environment, quickly transferring heat to the average air temperature. Walls with larger m values ​​have a greater weight in influencing PMV, and respond more significantly to human thermal comfort.

[0021] The method of this invention is applied to an office in Changsha City for demonstration purposes.

[0022] The office measures 4.14m × 3.8m × 2.4m (length × width × height); the ceiling is a perforated aluminum alloy panel with a 9% opening ratio and a diameter of 2mm. The calculated heat transfer coefficients for each wall surface are as follows: South wall 0.8 W / (m²). 2 ·K), West wall 0.68W / (m 2 ·K), the remaining enclosure structure is 0.69W / (m 2 ·K). The heat exchange calculation results of each part of the ceiling-mounted air-carrying radiant terminal are calculated by combining the energy transfer calculation formula of each part and the energy balance formula of the average indoor air temperature, as shown in Table 1.

[0023] Table 1 Summary of heat exchange results for ceiling-mounted air-cooled radiant terminals

[0024] By comparing theoretically calculated temperatures with experimentally measured data, the accuracy of the energy balance model under two typical operating conditions—winter and summer—was verified. The sensitivity of key parameters was identified to guide model simplification, providing theoretical support for subsequent dynamic control strategies. The transient temperature results within one hour were predicted and compared with experimental results. Figure 2 As shown.

[0025] It can be seen that the theoretically calculated average air temperature derived from the indoor energy balance shows good agreement with the experimentally measured value, with the deviation within the allowable range (±0.5°C), verifying the accuracy and applicability of the energy balance model under the ceiling-mounted air-based radiant terminal. Further calculations yielded a complementary relationship model: Winter heating: ,

[0026] Summer cooling: ,

[0027] In the application scenarios of the control method of the present invention, both the circulating energy storage area and the personnel use area can be circulated with air cooling / heating, such as in common civil building scenarios; or only the circulating energy storage area can be circulated with air cooling / heating, and the air in the personnel use area can be directly discharged, such as in operating rooms, clean rooms and other scenarios where indoor air quality is high.

[0028] This invention proposes a complementary relationship model between the building envelope, average indoor air temperature, and physical thermal comfort (PMV). This model determines the comprehensive influence weights of each wall surface temperature and the average air temperature, providing theoretical support for building design optimization. It facilitates accurate regulation and control of the indoor environment to optimize indoor thermal comfort and reduce energy consumption. By deepening the understanding of the complementary relationship between radiant terminals and the building envelope, this research provides theoretical support and practical guidance for energy-efficient building design and indoor environment optimization, promoting the development and application of green building technologies.

[0029] The above description is merely an embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural or procedural transformations made based on the content of the present invention specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of the present invention.

Claims

1. An air-powered air conditioning system and its energy transfer and complementary thermal comfort control method, characterized in that, The steps for establishing a prediction of energy transfer from a building's air-source radiation system include: Step 1: Collect the surface area and average absolute temperature of the radiant perforated plate, as well as the surface area and average absolute temperature of the four walls and floor enclosure structures that make up the building space. By unifying and simplifying the five enclosure structure surfaces of the building space into a hypothetical wall, the radiative heat transfer between the surface of the radiant perforated plate and the entire space is equivalent to the radiative energy exchange between the perforated plate and the hypothetical wall, and calculate the radiative heat transfer of the perforated plate. Step 2: Calculate the natural convection heat transfer based on the surface area of ​​the radiant perforated plate, the average temperature of the surface of the radiant perforated plate, and the average temperature of the indoor air. Step 3: Calculate the infiltration heat transfer based on the air volume supplied to the indoor air-conditioned area through the micropores of the perforated plate; Step 4: Calculate the heat transfer of the enclosure structure based on its material properties, thickness, and surface heat transfer characteristics. Step 5: Construct an energy balance model based on spatial coupling. In this model, the total energy provided by the air conditioning system includes the energy of the buffer storage area, the energy of the indoor air conditioning area, and the heat transfer of the building envelope. The energy of the indoor air conditioning area consists of perforated plate radiation heat transfer, natural convection heat transfer, and infiltration heat transfer. Finally, the average indoor air temperature is calculated. Step 6: Based on the indoor average air temperature, historical operating data analysis is performed by linear regression of different building envelope surface temperatures on the indoor average air temperature and linear regression of different building envelope surface temperatures and air average temperatures on PMV. The complementary relationship between building envelope surface temperature, indoor average air temperature and PMV is obtained, and a complementary prediction model of indoor average air temperature and PMV is obtained.

2. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, The formula for calculating the radiative heat transfer of the perforated plate is as follows: ; ； ； ； ； in, The heat transfer rate of the orifice plate is measured in W. The radiative heat transfer per unit area of ​​the orifice plate is expressed in W / m². 2 ; The radiative heat transfer coefficient is expressed in W / (m²). 2 ·K); The surface area of ​​the perforated plate, in meters. 2 ; It is the Stefan-Boltzmann constant. =5.67×10 -8 W / (m 2 ·K 4 ), is the dimensionless radiation angle coefficient between the hypothetical wall and the orifice plate surface; The average absolute temperature of the orifice plate surface, in K; The mean absolute temperature of the hypothetical wall, in Kelvin (K). The area of ​​the enclosure structure excluding the perforated plate, including the surface of the four walls and the floor, is expressed in meters (m²). 2 ; Emissivity of all surfaces of the enclosure structure except the perforated plate, dimensionless; The average absolute temperature of all surfaces of the enclosure structure, excluding the perforated plate, is expressed in K. The equivalent radiation angle coefficient of the hypothetical wall and ceiling surfaces is dimensionless. Let be the emissivity of the orifice plate surface, which is dimensionless.

3. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 2, characterized in that, The formula for calculating the natural convection heat transfer is as follows: ; ； ； ； ； in, Heat exchanged via natural convection, measured in W. For Nusselt numbers; For Grashof numbers; It is a Prandtl number; The natural convection heat transfer coefficient is expressed in W / (m²). 2 K); C and n are dimensionless constants determined experimentally; The average surface temperature of the top plate is expressed in °C. The average indoor air temperature is expressed in °C. is the thermal conductivity of the fluid, expressed in W / (m·K); Characteristic length, in meters; Acceleration due to gravity, unit m / s² 2 ; The volumetric expansion coefficient is expressed in units of 1 / K. Kinematic viscosity, unit: m 2 / s; Thermal diffusivity, in meters (m) 2 / s.

4. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 3, characterized in that, Orifice plate heating conditions Orifice plate cooling operation .

5. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, The formula for calculating the heat transfer rate is as follows: ,in The heat transfer through the perforated plate micropores into the indoor air-conditioned area is expressed in W. Air density, unit: kg / m³ 3 ; Specific heat capacity of air at constant pressure, in J / kg·℃; V represents the temperature of the air entering the indoor air-conditioned zone through the orifice plate for heat exchange, in °C; V represents the amount of infiltrated energy-carrying air entering the indoor air-conditioned zone through the orifice plate, in m³. 3 / s.

6. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, The formula for calculating the heat transfer of the building envelope is as follows: ; ,in, The total heat transfer on surface i of the building envelope, in W; The heat transfer area of ​​surface i of the building envelope, in meters. 2 ; The inner surface temperature of surface i of the building envelope, in °C; The outer surface temperature of the enclosure structure surface i, in °C; The overall heat transfer coefficient of the building envelope i is given by W / (m²). 2 ·K), where δi is the thickness of surface i of the enclosure structure, in meters; Let i be the thermal conductivity of the building envelope, expressed in W / (m·K). , Here, i represents the heat transfer coefficients of the inner and outer surfaces of the building envelope, respectively, in W / (m²). 2 ·K).

7. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, Construct an energy balance model based on spatial coupling to calculate the average indoor air temperature: ； = ； = ； ； ； ； Based on the energy balance equation above, the formula for calculating the average indoor air temperature is given under two operating conditions: During heating season, ; When cooling is provided, ; in, The total energy provided to the air conditioning system To buffer the energy in the energy storage area, The energy for the indoor air-conditioned area is obtained through radiative heat exchange. Natural convection heat transfer and osmotic heat exchange composition, For heat transfer in the building envelope; The system's supply air temperature is expressed in °C. The return air temperature of the energy storage area is expressed in °C. The weighted average temperature of the non-radiative wall surface is expressed in °C.

8. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, The algorithm for the complementary model of indoor average air temperature and PMV is as follows: It uses univariate linear regression analysis to determine the degree of direct influence of different wall temperatures on the average air temperature. , , b is the correlation coefficient, and c is a constant; principal component analysis is used to determine the correlation between wall temperature and average air temperature and the correlation coefficient. The weights are used to obtain the average indoor air temperature. and Complementary model of thermal comfort evaluation indices: ； 。 9. The air-powered air conditioning system and its energy transfer and complementary thermal comfort control method according to claim 1, characterized in that, In step 6, the historical data includes the building envelope temperature, air supply parameters, and thermal comfort feedback data under typical winter and summer operating conditions.

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