Air energy carrier air conditioning system and its energy transmission and complementary thermal comfort control method

Abstract

The application provides an air energy-carrying air conditioning system and an energy transmission and complementary thermal comfort regulation method thereof, and belongs to the technical field of temperature regulation. The method comprises the following steps: step 1, calculating the radiation heat exchange amount of a hole plate; step 2, calculating the natural convection heat exchange amount; step 3, calculating the permeation heat exchange amount according to the air supply amount of the hole plate micro-holes sent to an indoor air conditioning area; step 4, calculating the heat transfer amount of a building envelope according to the material properties, thickness and surface heat exchange properties of the building envelope; step 5, constructing an energy balance model based on space coupling to calculate the indoor air average temperature; and step 6, obtaining the complementary relationship between the building envelope surface temperature, the air average temperature and PMV, and obtaining the complementary prediction model of the indoor air average temperature and PMV. The application proposes and establishes an air average temperature prediction model, and realizes the fine description of radiation, convection, permeation and building envelope heat transfer 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:

[0006] 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.

[0007] Step 2, calculate the natural convection heat transfer according to the surface area of the radiation hole plate and the average temperature of the radiation hole plate surface and the average temperature of the indoor air;

[0008] Step 3, calculate the permeation heat transfer according to the amount of air supplied to the indoor air conditioning area by the micro-holes of the hole plate;

[0009] Step 4, calculate the heat transfer of the envelope according to the material properties, thickness and surface heat transfer properties of the envelope;

[0010] Step 5, build an energy balance model based on space coupling, wherein the total energy provided by the air conditioning supply system includes the energy of the buffer storage area, the energy of the indoor air conditioning area and the heat transfer of the envelope, the energy of the indoor air conditioning area is composed of the radiation heat transfer of the hole plate, the natural convection heat transfer and the permeation heat transfer, thereby calculating the average temperature of the indoor air;

[0011] Step 6, based on the average temperature of the indoor air, the linear regression of the average temperature of the indoor air with respect to different envelope surface temperatures and the linear regression of the thermal comfort evaluation index (PMV, Predicted Mean Vote) with respect to different envelope surface temperatures and air average temperature are analyzed based on historical operation data, thereby obtaining a complementary relationship between the envelope surface temperature, the air average temperature and the PMV, and obtaining a complementary prediction model of the indoor air average temperature and the PMV.

[0012] Further, the formula for calculating the radiation heat transfer of the hole plate is: ;

[0013] ;

[0014] ;

[0015] ;

[0016] ;

[0017] wherein, is the radiation heat transfer of the hole plate, unit: W; is the radiation heat transfer per unit area of the hole plate, unit: W / m 2 ; is the radiation heat transfer coefficient, unit: W / (m 2 ·K); is the surface area of the hole plate surface, unit: m 2 ; is the Stefan-Boltzmann constant, =5.67×10 -8 W / (m 2 ·K4 ), is the dimensionless radiation angle coefficient between the imaginary wall and the surface of the hole plate; is the average absolute temperature of the surface of the hole plate, in units of K; is the average absolute temperature of the imaginary wall, in units of K; is the surface area of each surface of the envelope surface (four walls and floor) other than the hole plate, in units of m 2 ; is the emissivity of each surface of the envelope surface (four walls and floor) other than the hole plate, dimensionless; is the average absolute temperature of each surface of the envelope surface (four walls and floor) other than the hole plate, in units of K; is the equivalent radiation angle coefficient between the imaginary wall and the surface of the ceiling, dimensionless; is the emissivity of the surface of the hole plate, dimensionless.

[0018] Further, the calculation formula of the natural convection heat exchange amount is: ;

[0019] ;

[0020] ;

[0021] ;

[0022] ;

[0023] wherein, is the natural convection heat exchange amount, in units of W; is the Nusselt number; is the Grashof number; is the Prandtl number; is the natural convection heat exchange coefficient, in units of W / (m 2 ·K); C and n are dimensionless constants determined by experiments; is the average temperature of the surface of the ceiling, in units of ℃; is the average temperature of the indoor air, in units of ℃; is the thermal conductivity of the fluid, in units of W / (m·K); is the characteristic length, in units of m; is the gravitational acceleration, in units of m / s 2 ; is the volumetric expansion coefficient, in units of 1 / K; is the kinematic viscosity, in units of m 2 / s; is the thermal diffusivity, in units of m 2 / s.

[0024] Further, the perforated plate heating condition: ; the perforated plate cooling condition: .

[0025] Further, the calculation formula of the permeation heat exchange amount is: , wherein is the permeation heat exchange amount sent to the indoor air conditioning area by the perforated plate micro-holes, unit: W; is the air density, unit: kg / m 3 ; is the specific heat capacity of air at constant pressure, unit: J / kg·℃; is the air temperature entering the indoor air conditioning area for heat exchange through the perforated plate, unit: ℃; V is the permeation load energy air amount entering the indoor air conditioning area through the perforated plate, unit: m 3 / s.

[0026] Further, the calculation formula of the building envelope heat transfer amount is: ;

[0027] , wherein is the total heat transfer amount of the building envelope surface i, unit: W; is the heat transfer area of the building envelope surface i, unit: m 2 ; is the inner surface temperature of the building envelope surface i, unit: ℃; is the outer surface temperature of the building envelope surface i, unit: ℃; is the comprehensive heat transfer coefficient of the building envelope i, unit: W / (m 2 ·K), δi is the thickness of the building envelope surface i, unit: m; is the thermal conductivity of the building envelope surface i, unit: W / (m·K); , are the heat transfer coefficients of the inner and outer surfaces of the building envelope surface i, respectively, unit: W / (m 2 ·K).

[0028] Further, based on the energy balance model of space coupling, the average temperature of indoor air is calculated:

[0029] ;

[0030] = ;

[0031] = ;

[0032] ;

[0033] ;

[0034] ;

[0035] According to the above energy balance equation, the calculation formula of the indoor air average temperature is the temperature under two working conditions:

[0036] When heating, ,

[0037] When cooling, ;

[0038] Wherein, is the total energy provided by the air conditioning supply system, is the energy of the buffer energy storage area, is the energy of the indoor air conditioning area (the radiation heat transfer calculated in step 1 , the natural convection heat transfer calculated in step 2 , the permeation heat transfer calculated in step 3 ), is the heat transfer of the envelope structure (calculated in step 4); is the supply air temperature of the system, unit ℃; is the return air temperature of the energy storage area, unit ℃; is the weighted average temperature of the non-radiation wall, unit ℃.

[0039] Further, the algorithm of the indoor air average temperature and the PMV complementary model: through a linear regression analysis, the direct influence degree of different wall surface temperatures on the air average temperature is directly judged, , , , b is the correlation coefficient, c is the constant, and the regression coefficient R 2 is greater than 0.85, and the greater the regression coefficient is, the stronger the response of the air average temperature to the change of the corresponding wall surface temperature is, the higher the sensitivity is, and the faster the air average temperature rising rate is; the weight of each wall surface temperature and the air average temperature on is determined by using a principal component analysis method, so that the indoor air average temperature and the complementary model of the thermal comfort evaluation index is obtained, , .

[0040] Further, in step 6, the historical data includes the envelope structure temperature, the supply air parameter and the thermal comfort feedback data under the typical working conditions in winter and summer.

[0041] The beneficial effects of the present application are:

[0042] The application proposes and establishes an air average temperature prediction model, realizes fine description of radiation, convection, penetration and heat transfer of the envelope structure by dividing the buffer energy storage area and the air conditioning area. The energy transfer calculation method can calculate the air penetration heat transfer between the energy storage area and the air conditioning area, and the energy balance model comprehensively considers various energy transfer modes such as radiation heat transfer, convection heat transfer, hole plate penetration heat transfer and envelope structure heat transfer, which is a more accurate and convenient indoor air average temperature prediction method.

[0043] In addition, the complementary relationship model of the envelope structure and the indoor air average temperature and the human thermal comfort PMV proposed by the application determines the comprehensive influence weight of each wall temperature and air average temperature, provides theoretical support for building design optimization, is beneficial to accurate adjustment and control of the indoor environment, optimizes the indoor thermal comfort and reduces energy consumption. Through research, the understanding of the complementary relationship between the radiation terminal and the envelope structure is deepened, theoretical support and practical guidance are provided for building energy saving design and indoor environment optimization, and the development and application of green building technology are promoted. BRIEF DESCRIPTION OF DRAWINGS

[0044] Figure 1 : Space area division schematic diagram of the air energy carrying radiation system;

[0045] Figure 2 : Indoor 1.1m air average temperature under the condition of a typical working condition of a ceiling type radiation terminal. DETAILED DESCRIPTION

[0046] The technical solutions in the embodiments of the application will be clearly and completely described below with reference to the drawings in the embodiments of the application. Obviously, the described embodiments are only part of the embodiments of the application, rather than all the embodiments. Based on the embodiments in the application, all other embodiments obtained by those skilled in the art without creative labor fall within the protection scope of the application.

[0047] In addition, the technical solutions of the various embodiments of the application can be combined with each other, but it must be based on the fact that a person skilled in the art can realize it, and when the combination of technical solutions appears to be contradictory or unachievable, it should be considered that the combination of technical solutions does not exist and is not within the protection scope required by the application.

[0048] Step 1, the surface area and the average absolute temperature of the radiation hole plate are collected, and the surface area and the average absolute temperature of the four walls and the floor envelope structure constituting the building space are collected, the five envelope structure surfaces of the building space are unified and simplified into an imaginary wall surface, the radiation heat exchange between the radiation hole plate surface and the whole space is equivalent to the radiation energy exchange between the hole plate and the imaginary wall surface, the radiation heat exchange of the hole plate is calculated, and the energy of the indoor air conditioning area is calculated. The calculation formula of the radiation heat exchange of the hole plate is: ;

[0049] ;

[0050] ;

[0051] ;

[0052] ;

[0053] wherein, is the radiation heat transfer amount of the perforated plate, unit: W; is the radiation heat transfer amount per unit area of the perforated plate, unit: W / m 2 ; is the radiation heat transfer coefficient, unit: W / (m 2 ·K); is the surface area of the perforated plate surface, unit: m 2 ; is the Stefan-Boltzmann constant, = 5.67 x 10 -8 W / (m 2 ·K 4 ), is the dimensionless radiation angle coefficient between the imaginary wall surface and the perforated plate surface; is the average absolute temperature of the perforated plate surface, unit: K; is the average absolute temperature of the imaginary wall surface, unit: K; is the surface area of each surface of the envelope structure surface (four walls and floor) except the perforated plate, unit: m 2 ; is the emissivity of each surface of the envelope structure surface (four walls and floor) except the perforated plate, dimensionless; is the average absolute temperature of each surface of the envelope structure surface (four walls and floor) except the perforated plate, unit: K; is the equivalent radiation angle coefficient between the imaginary wall surface and the ceiling surface, dimensionless; is the emissivity of the perforated plate surface, dimensionless;

[0054] Step 2, calculate the natural convection heat transfer amount according to the surface area of the radiation perforated plate, and the average temperature of the radiation perforated plate surface and the average temperature of the indoor air, which is used to form the energy of the indoor air conditioning area, and the calculation formula of the natural convection heat transfer amount is: ;

[0055] ;

[0056] ;

[0057] ;

[0058] ;

[0059] in, This refers to natural convection heat transfer, 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: .

[0060] 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;

[0061] 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: ;

[0062] ,in, The total heat transfer on surface i of the building envelope, in W; is the heat transfer area of the building envelope surface i, unit: m 2 ; is the inner surface temperature of the building envelope surface i, unit: ℃; is the outer surface temperature of the building envelope surface i, unit: ℃; is the overall heat transfer coefficient of the building envelope i, unit: W / (m 2 ·K), δi is the thickness of the building envelope surface i, unit: m; is the thermal conductivity of the building envelope surface i, unit: W / (m·K); 、 are the heat transfer coefficients of the inner and outer surfaces of the building envelope surface i, respectively, unit: W / (m 2 ·K);

[0063] Step 5, construct an energy balance model based on space coupling, see Figure 1 , divide the space to be predicted into a buffer energy storage area 1 and an air conditioning area 2, the total energy provided by the air conditioning supply 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 amount of the building envelope, the energy of the indoor air conditioning area is composed of the radiation heat transfer amount of the orifice plate, the natural convection heat transfer amount and the permeation heat transfer amount, so as to calculate the average temperature of indoor air;

[0064] Calculate the average temperature of indoor air:

[0065] ;

[0066] = ;

[0067] = ;

[0068] ;

[0069] ;

[0070] ;

[0071] According to the energy balance equation of the average temperature of indoor air constructed above, the calculation formula is the temperature under two working conditions, when heating: ,

[0072] When cooling, ;

[0073] Among them, is the total energy provided by the air conditioning supply system, is the energy of the buffer 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;

[0074] 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.

[0075] The method of this invention is applied to an office in Changsha City for demonstration purposes.

[0076] The office size is 4.14m*3.8m*2.4m (length* width* height); the ceiling is an aluminum alloy radiation hole plate with an opening rate of 9% and a diameter of 2mm. The heat transfer coefficients of each wall surface are calculated as follows: 0.8 W / (m 2 ·K) for the south wall, 0.68 W / (m 2 ·K) for the west wall, and 0.69 W / (m 2 ·K) for the remaining envelope. The heat exchange calculation results of the suspended air energy radiation terminal are shown in Table 1 by combining the energy transfer calculation formula of each part and the energy balance formula of the indoor air average temperature.

[0077] Table 1: Heat exchange results of suspended air energy radiation terminal

[0078]

[0079] By comparing the theoretical calculation temperature with the experimental measurement data, the accuracy of the energy balance model under two typical working conditions of winter and summer is verified, the key parameter sensitivity is identified to guide the model simplification, and the theoretical support is provided for the subsequent dynamic control strategy. The transient temperature results within 1 hour are predicted and calculated, and the results are shown in Figure 2 .

[0080] It can be seen that the indoor energy balance derived air average temperature theoretical calculation value and the experimental measurement value show good consistency, and the deviation is within the allowable range (±0.5°C), which verifies the accuracy and applicability of the energy balance model under the suspended air energy radiation terminal. Further calculation obtains the complementary relationship model:

[0081] Winter heating:

[0082] ,

[0083]

[0084] Summer cooling:

[0085] ,

[0086]

[0087] In the application scenario of the regulation method, the circulating energy storage area and the personnel use area can be air cooling / heating circulation, such as common civil building scenarios; or only the circulating energy storage area can be air cooling / heating circulation, and the air of the personnel use area is directly discharged, such as operating room, clean room and other scenarios with high indoor air quality.

[0088] The complementary relationship model between the envelope and the average indoor air temperature and the human thermal comfort PMV is provided, the comprehensive influence weight of each wall temperature and the average air temperature is determined, theoretical support is provided for building design optimization, accurate adjustment and control are facilitated on the indoor environment, indoor thermal comfort is optimized, and energy consumption is reduced. Through research, the understanding of the complementary relationship between the radiation terminal and the envelope is deepened, theoretical support and practical guidance are provided for building energy-saving design and indoor environment optimization, and the development and application of green building technology are promoted.

[0089] The above is only an embodiment of the present application, and does not limit the patent range of the present application, and any equivalent structure or equivalent process transformation using the content of the present application specification and drawings, or direct or indirect application in other related technical fields, is also included in the patent protection range of the present application.

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. 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: ； , where k and m are the correlation coefficients.

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 coefficient of volume expansion 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 transferred 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, 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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