# Effects of Supply Parameters of Stratum Ventilation on Energy Utilization Efficiency and Indoor Thermal Comfort: A Computational Approach

Authors: Lina Zhang; Yanhui Mao; Qiu Tu; Xiaogang Wu; Lingyu Tan
Journal: Mathematical Problems in Engineering
 (2021)

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## Abstract

Stratum ventilation shows the significant potential on energy conservation and indoor thermal comfort under cooling applications. Yet, only limited researches focus on the thermal performance of stratum ventilation under heating condition. The heating and cooling operation characteristic of stratum ventilation is different due to the distinct airflow characteristics. Therefore, this paper investigated the parameters that affect energy utilization efficiency and indoor thermal comfort under heating condition served by stratum ventilation via CFD simulations approach. The supply air parameters included temperature, airflow rate, angle, and return air outlet positions. The evaluation indicators adopt ventilation effectiveness and effective draft temperature (EDT) for assessing the energy utilization efficiency and indoor thermal comfort served by stratum ventilation under heating condition. The results demonstrated that, under the heating mode of stratum ventilation, different effects on the thermal performance were made by the mentioned parameters. The ventilation effectiveness was higher when the air supply temperature is 26°C, airflow rate is 7 air change per hour (ACH), and the air supply angle is 45°. The EDT range of the occupied zone is closest to zero K when the air supply temperature is 28°C, airflow rate is 12 (ACH), and the air supply angle is 60°. The related conclusions obtained from this study provide the theoretical basis for the stratum ventilation design and promote its heating application.


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## Body

## 1. Introduction

Energy utilization efficiency and indoor thermal comfort are the main evaluation indicators for the Heating Ventilation and Air Conditioning (HVAC) system. Up to now, 40% of the world energy consumption has been consumed by building energy consumption [1]. And air conditioning accounts for around 40% of the total building energy consumption [2, 3]. Therefore, energy consumption reduction for air conditioning has become an extremely urgent task. It is reported that elevating indoor temperature in summer and decreasing indoor temperature in winter are a necessary mean in reducing the energy consumption of air conditioners. Hence, 195 countries agreed to enhance the indoor temperature by 1.5°C for air conditioner energy reduction in the Paris Agreement [2]. Moreover, most people are recorded to spend the most time (>85%) in the enclosed space with air conditioning, so poor indoor air quality can significantly decrease the life quality and work efficiency of building occupants [4]. It demonstrates that improving indoor air quality is another significant task for the HVAC systems. As the recently proposed mechanical ventilation method, stratum ventilation can be seen as a potential solution for these two problems [5].The fresh air of stratum ventilation is supplied through the inlets installed at the midlevel of the walls. Hence, it can make the fresh air directly reach the breathing zone. Hence, the air supply path can be greatly shortened. According to the related studies, relative to mixing ventilation and displacement ventilation, the stratum ventilation thermal neutral temperature can be increased 2.5°C and 2.0°C, respectively [6]. Therefore, stratum ventilation performs better in thermal comfort and healthy environment. Stratum ventilation used for space cooling applications is widely researched in the existing studies due to its air distribution advantages [7]. The research results pointed out that stratum ventilation can provide higher thermal comfort and lower contaminant concentrations in the breathing zone with lower system energy consumption [8, 9]. Stratum ventilation control method and optimization design in the cooling condition are also the research focus for energy conservation [10].In the actual application, there are various factors that influence the thermal performance of stratum ventilation, such as temperature, airflow rate, the air inlet angle, and the return air outlet positions [6, 11–13]. In the cooling condition, the angle of 0° is generally suggested for preventing the cold air subsidence caused by thermal buoyancy [14]. As for the heating applications, the warm air will rise under the impact of thermal buoyancy. Therefore, there will be an obvious difference on the operation parameters for stratum ventilation between heating and cooling conditions, causing the air supply angle to become a vital factor impacting the ventilation thermal performance for space heating [13]. Hence, the existing researches on optimal parameters of stratum ventilation under cooling condition cannot be used in space heating.For the southern region of China with heating requirement, it is most suitable to employ efficient mechanical ventilation in space heating. As for stratum ventilation, the warm air can be directly supplied into the occupied zone to reduce the vertical temperature gradient [15, 16]. Stratum ventilation as a recently proposed ventilation method is relatively new. And there are only a few studies on its heating application. The current related studies mainly focus on multicriteria performance optimization [17], the effects of operation parameters on the performance indices [18], and the performance comparison of stratum ventilation with other ventilation methods under heating mode [19]. However, researching the impact of supply parameters on ventilation effectiveness (Et) and effective draft temperature (EDT) to propose the optimal supply air parameters for stratum ventilation under heating mode is scarce, which will be the a strong supplement to the current research for the better application of stratum ventilation in the future. Hence, in this paper, a typical office is used to study the optimal parameters based on the flow characteristics under heating condition. Through the combination of experiment and numerical simulation, the impacts of supply air parameters including temperature, airflow rate, angle, and return air outlet position on the stratum ventilation thermal performance under heating condition are assessed by Et and EDT. The related conclusions obtained from this research provide the theoretical basis for the stratum ventilation design and promote its heating application.


## 2. Methodology

### 2.1. Experimental Setup

#### 2.1.1. Test Procedure

The experiment was conducted in a test chamber measuring 6 m × 4 m × 3.5 m under a variation from −10 to −3°C of the ambient air temperature. The treated air was supplied by the air inlets (S1–S4) with a size of 0.3 m × 0.3 m. The air inlets were installed at 1.2 m height of the wall. During the experiment, only S1 and S3 were opened. And the return air outlets were located on the ceiling. Variable speed fans were employed to vary the supply air volume.The internal load of this chamber is set as six occupants and two incandescent lamps. The sedentary occupant was simulated by a cuboid thermal manikin whose size is 0.4 m × 0.25 m × 1.2 m. And a 100 W light bulb was set in the cuboid to represent the occupant’s thermal radiation and convection effects. The method has been commonly used to consider the occupant impact on the indoor thermal environment [20]. The power of the two incandescent lamps installed on one side of the wall is also 100 W. Supply air temperature and velocity were measured by dry bulb temperature and velocity sensors installed on the measurement plumb lines at the heights of 0.1 m, 0.6 m, 1.1 m, 1.4 m, 2.1 m, and 2.8 m, respectively.


#### 2.1.2. Measurement Instrumentation

In this study, T-thermocouple (±0.3°C accuracy) was used to measure the temperature, and hot-wire anemometer (Testo-480) (±0.05 m/s accuracy) was used to measure the velocity. Kline and McClintock are introduced to conduct the error analysis [21]. The relative uncertainty equation is provided as follows:(1)ΔRR=∑i=1nΔXiXi21/2,where X is the independent variant. Through calculation, the temperature and velocity measurement accuracy are calculated as 0.08% and 0.25%, respectively.


### 2.2. CFD Simulation

With the characteristics of less cost and time consuming, computational fluid dynamics (CFD) is commonly employed to simulate indoor thermal environment [22]. Through years of development, CFD simulation can predict indoor velocity distribution, indoor temperature distribution, and indoor air quality accurately [23–25].Based on the related study [26], a typical size of an office model can be used to investigate the airflow characteristics under various ventilation methods. The related research [27] indicates that it is suitable to simulate the air temperature and airflow by using the standard k-ε two-equation model. Hence, considering the higher accuracy and calculation efficiency, the standard k-ε model was introduced in this study. Discrete ordinates radiation model was introduced to consider the radiative heat transfer between surfaces. Boussinesq model was used to compute the buoyancy effect [28]. The air in the calculation area was assumed to be incompressible Newtonian fluid acting as a constant flow. To consider the ambient temperature impacts on the indoor environment, the exterior walls were set as constant temperature [29]. The 3D model is presented in Figure 1, and the detailed boundary conditions of experimental and numerical are shown in Table 1.Figure 1
CFD 3D model (a) and mesh ofZ = 2.0 m (b).
(a)(b)Table 1
Detailed information of the boundary conditions.
Boundary conditionExperimental parameterSimulated parameterSupply air inletUniform velocity27.0°C, 1.30 m/s26-29°C, 0.63–1.30 m/sReturn air outletFree pressure——Exterior wallConstant temperature13.0°C10.0–17.0°CFloor and ceilingAdiabatic——OccupantsConstant heat flux100 W/person100 W/personLightsConstant heat flux100 W/one lamp100 W/one lampTo obtain the results accurately and in time-saving manner, the grid independence test based on the sufficient number of elements was performed. The average temperature at the height of 1.1 m calculated by coarse grid, moderate grid, and fine grid was compared and presented in Table2. Finally, Mesh 2 was selected due to less than 5% of the maximum relative error compared to Mesh 3. Moreover, the girds used in this study are all hexahedral and the mesh quality is one.Table 2
Gird independence test for selection of three densities of mesh.
MeshNumber of gird nodesSimulated temperature (°C)Maximum relative error in computing values of temperature compared to the previous mesh values (%)1165461019.65—2240432421.258.143392675121.110.66


### 2.3. Cases Studied

The purpose of cases is to explore the effects of supply air parameters including temperature, airflow rate, angle, and return air outlet locations on the stratum ventilation thermal performance, respectively. To conduct the univariate analysis, the control variable method was adopted in this study. When discussing the effect of one of the variables, the others are left unchanged. Each parameter with four variations was discussed in the simulation, i.e., 26.0–29.0°C for the supply air temperature (cases 1–4); 7–15 ACH for the supply airflow rate (cases 5–8); 15°∼60° for the supply air angle (cases 9–12). And four return air outlet positions are studies in cases 13–16: on the ceiling, at the same level opposite to the supply air inlets, on the opposite wall of the supply air inlets with 0.5 m height above the floor, and on the same wall of the supply air inlets with 0.5 m height above the floor. The detailed input parameters of the studied case are presented in Table3.Table 3
Studied cases of parameters.
CaseACHTs (°C)Supply air angle (°)Air outlet locationQ (m3/s)Tn (°C)11526.00Ceiling-counted0.46821.0227.0328.0429.05727.00Ceiling-counted0.22021.06100.3137120.3748150.46891027.015Ceiling-counted0.31321.0103011451260131027.00Ceiling-counted0.31321.014The same level in the opposite direction of the air inlet15The bottom level in the opposite direction of the air inlet16The bottom level in the opposite direction of the air inletQ: air supply volume;Ts: supply air temperature; Tn: nominal room temperature; ACH: air change rate per hour.


### 2.4. Ventilation Performance Evaluation Index

Ventilation effectiveness and effective draft temperature are employed in this study to appraise stratum ventilation on the performance of thermal characteristics.


#### 2.4.1. Ventilation Effectiveness

A largerEt indicates a higher energy utilization efficiency. Less warm supply air is needed to achieve the target temperature in the occupied zone. It is calculated through the following equation [30]:(2)Et=Te−TsToz−Ts,where Et is the ventilation effectiveness; Te is the exhaust air temperature, °C; Ts is the supply air temperature, °C; and Toz is the average occupied zone temperature, °C.


#### 2.4.2. Effective Draft Temperature (EDT)

Lin recently put forward a new calculation formula of EDT for stratum ventilation, which has been confirmed to be reliable and straightforward to assess the thermal comfort performance [31]. Similar to the calculation parameters of PMV, EDT can comprehensively consider the effect of indoor air temperature, radiant temperature, velocity, humidity, and human activity on the thermal comfort. The corresponding calculation equation is shown as [32](3)EDT=Toz−Tc−vx−1.1,where Tc is the mean dry-bulb temperature of the space, °C; vx is the local velocity, m/s. The thermal environment is deemed to be satisfactory when EDT value is within the range of −1.2 K and +1.2 K.


## 2.1. Experimental Setup

### 2.1.1. Test Procedure

The experiment was conducted in a test chamber measuring 6 m × 4 m × 3.5 m under a variation from −10 to −3°C of the ambient air temperature. The treated air was supplied by the air inlets (S1–S4) with a size of 0.3 m × 0.3 m. The air inlets were installed at 1.2 m height of the wall. During the experiment, only S1 and S3 were opened. And the return air outlets were located on the ceiling. Variable speed fans were employed to vary the supply air volume.The internal load of this chamber is set as six occupants and two incandescent lamps. The sedentary occupant was simulated by a cuboid thermal manikin whose size is 0.4 m × 0.25 m × 1.2 m. And a 100 W light bulb was set in the cuboid to represent the occupant’s thermal radiation and convection effects. The method has been commonly used to consider the occupant impact on the indoor thermal environment [20]. The power of the two incandescent lamps installed on one side of the wall is also 100 W. Supply air temperature and velocity were measured by dry bulb temperature and velocity sensors installed on the measurement plumb lines at the heights of 0.1 m, 0.6 m, 1.1 m, 1.4 m, 2.1 m, and 2.8 m, respectively.


### 2.1.2. Measurement Instrumentation

In this study, T-thermocouple (±0.3°C accuracy) was used to measure the temperature, and hot-wire anemometer (Testo-480) (±0.05 m/s accuracy) was used to measure the velocity. Kline and McClintock are introduced to conduct the error analysis [21]. The relative uncertainty equation is provided as follows:(1)ΔRR=∑i=1nΔXiXi21/2,where X is the independent variant. Through calculation, the temperature and velocity measurement accuracy are calculated as 0.08% and 0.25%, respectively.


## 2.1.1. Test Procedure

The experiment was conducted in a test chamber measuring 6 m × 4 m × 3.5 m under a variation from −10 to −3°C of the ambient air temperature. The treated air was supplied by the air inlets (S1–S4) with a size of 0.3 m × 0.3 m. The air inlets were installed at 1.2 m height of the wall. During the experiment, only S1 and S3 were opened. And the return air outlets were located on the ceiling. Variable speed fans were employed to vary the supply air volume.The internal load of this chamber is set as six occupants and two incandescent lamps. The sedentary occupant was simulated by a cuboid thermal manikin whose size is 0.4 m × 0.25 m × 1.2 m. And a 100 W light bulb was set in the cuboid to represent the occupant’s thermal radiation and convection effects. The method has been commonly used to consider the occupant impact on the indoor thermal environment [20]. The power of the two incandescent lamps installed on one side of the wall is also 100 W. Supply air temperature and velocity were measured by dry bulb temperature and velocity sensors installed on the measurement plumb lines at the heights of 0.1 m, 0.6 m, 1.1 m, 1.4 m, 2.1 m, and 2.8 m, respectively.


## 2.1.2. Measurement Instrumentation

In this study, T-thermocouple (±0.3°C accuracy) was used to measure the temperature, and hot-wire anemometer (Testo-480) (±0.05 m/s accuracy) was used to measure the velocity. Kline and McClintock are introduced to conduct the error analysis [21]. The relative uncertainty equation is provided as follows:(1)ΔRR=∑i=1nΔXiXi21/2,where X is the independent variant. Through calculation, the temperature and velocity measurement accuracy are calculated as 0.08% and 0.25%, respectively.


## 2.2. CFD Simulation

With the characteristics of less cost and time consuming, computational fluid dynamics (CFD) is commonly employed to simulate indoor thermal environment [22]. Through years of development, CFD simulation can predict indoor velocity distribution, indoor temperature distribution, and indoor air quality accurately [23–25].Based on the related study [26], a typical size of an office model can be used to investigate the airflow characteristics under various ventilation methods. The related research [27] indicates that it is suitable to simulate the air temperature and airflow by using the standard k-ε two-equation model. Hence, considering the higher accuracy and calculation efficiency, the standard k-ε model was introduced in this study. Discrete ordinates radiation model was introduced to consider the radiative heat transfer between surfaces. Boussinesq model was used to compute the buoyancy effect [28]. The air in the calculation area was assumed to be incompressible Newtonian fluid acting as a constant flow. To consider the ambient temperature impacts on the indoor environment, the exterior walls were set as constant temperature [29]. The 3D model is presented in Figure 1, and the detailed boundary conditions of experimental and numerical are shown in Table 1.Figure 1
CFD 3D model (a) and mesh ofZ = 2.0 m (b).
(a)(b)Table 1
Detailed information of the boundary conditions.
Boundary conditionExperimental parameterSimulated parameterSupply air inletUniform velocity27.0°C, 1.30 m/s26-29°C, 0.63–1.30 m/sReturn air outletFree pressure——Exterior wallConstant temperature13.0°C10.0–17.0°CFloor and ceilingAdiabatic——OccupantsConstant heat flux100 W/person100 W/personLightsConstant heat flux100 W/one lamp100 W/one lampTo obtain the results accurately and in time-saving manner, the grid independence test based on the sufficient number of elements was performed. The average temperature at the height of 1.1 m calculated by coarse grid, moderate grid, and fine grid was compared and presented in Table2. Finally, Mesh 2 was selected due to less than 5% of the maximum relative error compared to Mesh 3. Moreover, the girds used in this study are all hexahedral and the mesh quality is one.Table 2
Gird independence test for selection of three densities of mesh.
MeshNumber of gird nodesSimulated temperature (°C)Maximum relative error in computing values of temperature compared to the previous mesh values (%)1165461019.65—2240432421.258.143392675121.110.66


## 2.3. Cases Studied

The purpose of cases is to explore the effects of supply air parameters including temperature, airflow rate, angle, and return air outlet locations on the stratum ventilation thermal performance, respectively. To conduct the univariate analysis, the control variable method was adopted in this study. When discussing the effect of one of the variables, the others are left unchanged. Each parameter with four variations was discussed in the simulation, i.e., 26.0–29.0°C for the supply air temperature (cases 1–4); 7–15 ACH for the supply airflow rate (cases 5–8); 15°∼60° for the supply air angle (cases 9–12). And four return air outlet positions are studies in cases 13–16: on the ceiling, at the same level opposite to the supply air inlets, on the opposite wall of the supply air inlets with 0.5 m height above the floor, and on the same wall of the supply air inlets with 0.5 m height above the floor. The detailed input parameters of the studied case are presented in Table3.Table 3
Studied cases of parameters.
CaseACHTs (°C)Supply air angle (°)Air outlet locationQ (m3/s)Tn (°C)11526.00Ceiling-counted0.46821.0227.0328.0429.05727.00Ceiling-counted0.22021.06100.3137120.3748150.46891027.015Ceiling-counted0.31321.0103011451260131027.00Ceiling-counted0.31321.014The same level in the opposite direction of the air inlet15The bottom level in the opposite direction of the air inlet16The bottom level in the opposite direction of the air inletQ: air supply volume;Ts: supply air temperature; Tn: nominal room temperature; ACH: air change rate per hour.


## 2.4. Ventilation Performance Evaluation Index

Ventilation effectiveness and effective draft temperature are employed in this study to appraise stratum ventilation on the performance of thermal characteristics.


### 2.4.1. Ventilation Effectiveness

A largerEt indicates a higher energy utilization efficiency. Less warm supply air is needed to achieve the target temperature in the occupied zone. It is calculated through the following equation [30]:(2)Et=Te−TsToz−Ts,where Et is the ventilation effectiveness; Te is the exhaust air temperature, °C; Ts is the supply air temperature, °C; and Toz is the average occupied zone temperature, °C.


### 2.4.2. Effective Draft Temperature (EDT)

Lin recently put forward a new calculation formula of EDT for stratum ventilation, which has been confirmed to be reliable and straightforward to assess the thermal comfort performance [31]. Similar to the calculation parameters of PMV, EDT can comprehensively consider the effect of indoor air temperature, radiant temperature, velocity, humidity, and human activity on the thermal comfort. The corresponding calculation equation is shown as [32](3)EDT=Toz−Tc−vx−1.1,where Tc is the mean dry-bulb temperature of the space, °C; vx is the local velocity, m/s. The thermal environment is deemed to be satisfactory when EDT value is within the range of −1.2 K and +1.2 K.


## 2.4.1. Ventilation Effectiveness

A largerEt indicates a higher energy utilization efficiency. Less warm supply air is needed to achieve the target temperature in the occupied zone. It is calculated through the following equation [30]:(2)Et=Te−TsToz−Ts,where Et is the ventilation effectiveness; Te is the exhaust air temperature, °C; Ts is the supply air temperature, °C; and Toz is the average occupied zone temperature, °C.


## 2.4.2. Effective Draft Temperature (EDT)

Lin recently put forward a new calculation formula of EDT for stratum ventilation, which has been confirmed to be reliable and straightforward to assess the thermal comfort performance [31]. Similar to the calculation parameters of PMV, EDT can comprehensively consider the effect of indoor air temperature, radiant temperature, velocity, humidity, and human activity on the thermal comfort. The corresponding calculation equation is shown as [32](3)EDT=Toz−Tc−vx−1.1,where Tc is the mean dry-bulb temperature of the space, °C; vx is the local velocity, m/s. The thermal environment is deemed to be satisfactory when EDT value is within the range of −1.2 K and +1.2 K.


## 3. Results

### 3.1. Model Validation

Once the Airpak model built, a validation is also necessary to investigate the simulation accuracy. The simulation of the airflow and temperature distribution for a typical thermal scenario was conducted, and the results were compared with the experimental results. In the model validation, the supply air temperature was selected to be 27.0°C and the air change per hour was set as 15ACH (c.f. case 2 in Table3). The boundary conditions that are employed in this numerical model are set as same as those in the experiment. The heat sources consisted of occupants and lamps. Velocities and temperatures of five typical positions at 1.1 m were calculated and measured. Differences between the numerical and experimental values are shown in Figure 2. It can be seen that the simulated values (both velocity and temperature) mostly match the measured ones. Maximum, minimum, and average temperature difference values were 0.4, −0.2, and 0.1°C, respectively. And those between the experimental and simulated velocities were 0.07, −0.01, and 0.02 m/s, respectively.Figure 2
Dissimilarities between temperature and velocity experimental and numerical results.To quantitatively describe the model performance, four statistical methods were introduced here as well [33, 34]. Among them, the mean absolute error (MAE) can be defined as follows:(4)MAE=1p∑i=1pxi−yi,where xi represents the measurements, yi represents the numerical values, and p is the total experimental test points.Equation (5) shows the definition of the mean absolute percentage error (MAPE):(5)MAPE=1p∑i=1pxi−yixi×100%.The root-mean-square error (RMSE) is as(6)RMSE=1p∑i=1pxi−yi2.For the index of agreement (IA), it is calculated as follows:(7)IA=1−∑i=1pxi−yi2∑i=1pyi−xm+xi−xm2.When the result value is 0 for the MAE, MAPE, and RMSE and 1 for IA, it shows that the simulation results agree well with the measurements. Table 4 provides the calculation results for the temperature and velocity. MAE, MAPE, and RMSE values of velocity are 0.023 m/s, 0.097%, and 0.001 m/s, respectively, and those of temperature are 0.05°C, 0.01%, and 0.05°C, respectively, which are close to 0. The IA value of temperature is 0.97 and that of velocity is 0.876; both are close to unity. The simulation results are basically consistent with the experimental results, which indicates that the numerical model is reliable to calculate different air parameters of stratum ventilation in various cases.Table 4
The detailed information of model performance.
MetricTemperatureVelocityMAE0.05°C0.023 m/sMAPE0.01%0.097%RMSE0.05°C0.001 m/sIA0.970.876


### 3.2. Effect of Supply Air Parameters on Ventilation Effectiveness

#### 3.2.1. Supply Air Temperature

In this study, ventilation effectiveness is applied as an index to access the energy utilization efficiency. As known to all, the higher the ventilation effectiveness, the better the energy efficiency. Figure3 shows the calculation and fitting curves of the average ventilation effectiveness among the occupied zones at different supply air temperatures. According to the related research [18], polynomial can be applied to the fitting in the study on stratum ventilation. Based on this, the fitting formulae are as follows:(8)Et26=1.005+0.236h−0.06h2,Et27=0.81+0.186h−0.05h2,Et28=0.825+0.187h−0.05h2,Et29=0.913+0.213h−0.05h2,where Et26 is the ventilation effectiveness at supply air temperature of 26°C; Et27 is the ventilation effectiveness at the supply air temperature of 27°C; Et28 is the ventilation effectiveness at the supply air temperature of 28°C; Et29 is the ventilation effectiveness at the supply air temperature of 29°C; h is the height, m.Figure 3
Average ventilation effectiveness at different supply air temperatures.γ is introduced for the propose of comparing the performance under the four supply air temperatures, which is defined as follows:(9)γ=Etx¯Et¯=∫0h0Etx/h0∫0h0Et/h0,where Etx¯ is the mean ventilation effectiveness in any case among the breathing zones; Et¯ is the mean ventilation effectiveness in benchmark case among the breathing zones; h0 is the height of the breathing level, m. In this study, h0 is set as 1.1 m. γ is the ratio of Etx¯ to Et¯. Setting Et26¯ as the base value, it is calculated that Et26¯ is 1.11, Et27¯ is 0.892, Et28¯ is 0.908, and Et29¯ is 1.01. Hence, γ27-26 is 0.804, γ28-26 is 0.818, and γ29-26 is 0.918.The ventilation effectiveness is affected synthetically by the thermal buoyancy and average temperature among the occupied zones. When the supply air temperature is 26°C, more heat would stay in the occupied zone contributing by less thermal buoyancy, thus leading to higher ventilation effectiveness. Since the air inlet of the stratum ventilation is located at the middle level of the side wall, the supply air temperature of 29°C leads the temperature near the supply air inlet to become higher and then resulting in a higher average temperature among the occupied zones compared with that under 27°C and 28°C. However, thermal buoyancy plays a dominant role in these two mechanisms. Hence, the ventilation effectiveness under 26°C of the supply air temperature is the highest. And the ventilation effectiveness under 26°C of the supply air temperatures being 27°C, 28°C, and 29°C is lower.


#### 3.2.2. Airflow Rate

Similarly, to compare the ventilation efficiency at different airflow rates, Figure4 fits the ventilation efficiency at different heights. The formulae are as follows:(10)Et7=0.955+0.097h−0.026h2,Et10=0.879+0.176h−0.05h2,Et12=0.911+0.158h−0.04h2,Et15=0.912+0.128h−0.03h2,where Et7 is the ventilation effectiveness for the 7ACH case; Et10 is the ventilation effectiveness of 10ACH; Et12 is the ventilation effectiveness of 12ACH; Et15 is the ventilation effectiveness of 15ACH. Et7¯ is set as the base value. It can be calculated that Et7¯ is 0.998, Et10¯ is 0.956, Et12¯ is 0.982, Et15¯ is 0.970, γ10-7 is 0.958, γ12-7 is 0.984, and γ15-7 is 0.972. It indicates that the ventilation effectiveness is the highest at 7ACH.Figure 4
Average ventilation effectiveness at different airflow rates (ACH).


#### 3.2.3. Supply Air Angle

The schematic diagram of supply vane angle discussed in this study is provided as Figure5.Figure 5
The supply vane angle schematic diagram.
(a)(b)(c)(d)Using the same method, as shown in Figure6, the fitted formulae of the ventilation effectiveness for different angles are given as follows:(11)Et15=0.932+0.131h−0.035h2,Et30=0.869+0.109h−0.03h2,Et45=0.976+0.119h−0.03h2,Et60=0.997+0.073h−0.02h2,where Et15 is the ventilation effectiveness for the supply air angle of 15°; Et30 is the ventilation effectiveness of supply air angle of 30°; Et45 is the ventilation effectiveness of supply air angle of 45°; Et60 is the ventilation effectiveness of supply air angle of 60°. Et15¯ is selected as the base value. It is calculated that Et15¯ is 0.990, Et30¯ is 0.917, Et45¯ is 1.03, Et60¯ is 1.03, γ30-15 is 0.926, γ45-15 is 1.04, and γ60-15 is 1.04. It depicts that, with a supply air angel of 45°, the ventilation effectiveness can achieve the highest value.Figure 6
Average ventilation effectiveness at different supply air angles.


#### 3.2.4. Return Air Outlet Position

The fitting formulae of the average ventilation effectiveness under different air outlet positions are as follows:(12)Etc=0.932+0.133h−0.035h2,Etoo=0.96+0.142h−0.04h2,Etuo=1.004+0.149h−0.04h2,Etus=0.947+0.135h−0.04h2,where Etc is the ventilation effectiveness for the case of air outlet installed on the ceiling; Etoo is the ventilation effectiveness of the outlet installed at the same level on the wall opposite to the supply air inlet; Etuo is the ventilation effectiveness for the air outlet located at the bottom of the wall opposite to the inlet; Etus is the ventilation effectiveness for the outlet located at the bottom of the same wall as the inlet. As shown in Figure 7, the change trends of Etc, Etoo, Etuo, and Etus are approximately consistent. And Etc¯ is 0.991, Etoo¯ is 1.02, Etuo¯ is 1.07, Etus¯ is 1.01, γoo-c is 1.03, γuo-c is 1.08, and γus-c is 1.02 by calculation. The ventilation effectiveness can be obtained as the highest when the outlet is located under the opposite side.Figure 7
Average ventilation effectiveness at different air outlet positions.


### 3.3. Effect of Supply Air Parameters on Effective Draft Temperature (EDT)

#### 3.3.1. Supply Air Temperature

Besides the ventilation effectiveness, effective draft temperature (EDT) is also a crucial factor for the thermal comfort evaluation. EDTs at three typical heights, namely, 0.1 m, 0.6 m, and 1.1 m, are calculated by (3) to obtain the frequency distribution under different supply air temperatures, as shown in Figure 8. It indicates that when the supply air temperature is 26.0°C, 62% of EDT is 0.4 K at the 0.1 m level, 78% of EDT is 0.5 K on the 0.6 m plane, and 68% of EDT is 1.1 K on the 1.1 m plane. When the supply air temperature is 27.0°C, 67% of EDT is 0K on the 0.1 m plane, 76% of EDT is 0.8 K on the 0.6 m plane, and 65% of EDT is 0.9 K on the 1.1 m plane. When the temperature is 28.0°C, 71% of EDT is 0K on the 0.1 m plane, 72% EDT is 0.8 K on the 0.6 m plane, and 62% EDT is 0.9 K on the 1.1 m plane. When the air supply temperature is 29.0°C, the 0.1 m plane has 74% EDT of −0.09 K, the 0.6 m plane has 63% EDT of 0.8 K, and the 1.1 m plane has 59% EDT of 0.9 K. It indicates that the EDT on the 0.1 m plane is closer to the neutral temperature when the supply air temperature is 27.0°C and 28.0°C. And the percentage around the neutral temperature is higher when the supply air temperature is 28.0°C. Hence, for the perspective of the EDT, the supply air temperature of 28.0°C shows the best effect.Figure 8
EDT frequency at different supply air temperatures.
(a)(b)(c)(d)It is reported that the EDT range that satisfies the occupant is between −1.2 K and 1.2 K. The average EDTs at four supply air temperatures are presented in Figure9. It can be seen that the EDTs at 26–29°C are all within the satisfaction range. And the average EDTs among the occupied zone are 0.82 K (26°C), 0.68 K (27°C), 0.52 K (28°C), and 0.37 K (29°C), respectively. Combining with the EDT frequency discussed results, 28.0°C is optimum under considering the impact of supply air temperature on EDT.Figure 9
Average EDT at different supply air temperatures.


#### 3.3.2. Airflow Rate

The frequency distributions of EDT at different airflow rates are shown in Figure10. It indicates that 85.3% EDT is 0 K at the height of 0.1 m, 56.8% EDT is 0.8 K at the height of 0.6 m, and 65.5% EDT is 1K at the height of 1.1 m in the case of 10ACH. 61.45% EDT is 0.8 K on the 0.1 m plane, 82.2% EDT is 0 K on the 0.6 m plane, and 49.9% EDT is 1 K on the 1.1 m plane in the case of 15ACH. As for the case of 12ACH, the highest frequency at 0.1 m, 0.6 m, and 1.1 m is 71.6, 67.8, and 67.9% with EDT being 1K. Compared with other ACHs, the EDT frequency distribution close to 0K at 0.1 m, 0.6 m, and 1.1 m is relatively high when the airflow is 12ACH. Therefore, the EDT at 12ACH has the highest percentage located in the comfort range among the occupied zones.Figure 10
EDT frequency at different airflow rates (ACH).
(a)(b)(c)(d)Meanwhile, Figure11 shows that the EDTs among the occupied zones with airflow of 7–15ACH are all within the satisfaction range. However, the EDT of 10ACH is close to the upper limit of the satisfaction range. The average EDTs under different airflows among the occupied zones are 0.87 K (7ACH), 0.87 K (10ACH), 0.61 K (12ACH), and 0.58 K (15ACH), respectively. Hence, 12ACH is optimum under considering the impact of airflow on EDT combining with the EDT frequency.Figure 11
Average EDT at different airflow rates (ACH).


#### 3.3.3. Air Supply Angle

Similarly, to evaluate the impact of the air supply angle on the EDT, the frequency distribution at different supply air angles is presented in Figure12. It can be seen that most of the EDTs at four air supply angles are within the comfort interval. When the air supply angle is 60°, the proportions located in comfort zone at 0.1 m, 0.6 m, and 1.1 m are 95%, 97%, and 90%, respectively, which gets the highest among the four air supply angles. Therefore, from the viewpoint of the EDT frequency distribution, it is optimal when the supply air angle is 60°.Figure 12
EDT frequency at different supply air angles.
(a)(b)(c)(d)In Figure13, the EDTs of the occupied area with supply angles of 45° and 60° are within the satisfaction range while those of 15° and 30° are beyond the upper limit of the satisfaction range. Meanwhile, the average EDTs under different angles among the occupied zones are 1.88 K (15°), 1.44 K (30°), 0.67 K (45°), and −0.91 K (60°), respectively. Although the average EDT at the supply angle of 45° is closer to 0 K relative to 60°, the proportions located within the comfort zone at 60° is the highest according to the frequency distribution. Hence, 60° is optimum under considering the impact of supply angle on EDT.Figure 13
Average EDT at different supply air angles.


#### 3.3.4. Return Air Outlet Position

The frequency statistics of the EDTs in the occupied zone are calculated under discussed return air outlet positions. Figure14 demonstrates that more than 86% of the EDTs under the four return air outlets are within the comfort range. And the proportions within the comfort range of the three return air outlet layouts, namely, on the ceiling, right on the opposite wall, and at the lower level on the opposite wall, are the same. When the position of the return air outlet is at the lower level on the same wall, 95% of the EDTs belong to the comfort range, so the effect of EDT is the best when the return air outlet is on the same wall beneath the air supply inlet.Figure 14
EDT frequency for different air outlet positions.
(a)(b)(c)(d)As presented in Figure15, it can be seen that the EDTs among the occupied zones under four outlet locations are all within the satisfaction range. Nevertheless, the EDT with the outlet under the opposite side is close to the upper limit of the satisfaction range. Meanwhile, the average EDTs under different return air outlets among the occupied zones are 0.62 K (on the ceiling), 0.74 K (on the opposite side), 0.89 K (under the opposite side), and 0.72 K (under the same side), respectively. Because the EDT located in the comfort zone is the highest when the outlets are installed under the same side with the inlets, the position of the return air outlet is located at the same wall but at a lower level as the air supply inlet can reach the best performance.Figure 15
Average EDT at different air outlet positions.


## 3.1. Model Validation

Once the Airpak model built, a validation is also necessary to investigate the simulation accuracy. The simulation of the airflow and temperature distribution for a typical thermal scenario was conducted, and the results were compared with the experimental results. In the model validation, the supply air temperature was selected to be 27.0°C and the air change per hour was set as 15ACH (c.f. case 2 in Table3). The boundary conditions that are employed in this numerical model are set as same as those in the experiment. The heat sources consisted of occupants and lamps. Velocities and temperatures of five typical positions at 1.1 m were calculated and measured. Differences between the numerical and experimental values are shown in Figure 2. It can be seen that the simulated values (both velocity and temperature) mostly match the measured ones. Maximum, minimum, and average temperature difference values were 0.4, −0.2, and 0.1°C, respectively. And those between the experimental and simulated velocities were 0.07, −0.01, and 0.02 m/s, respectively.Figure 2
Dissimilarities between temperature and velocity experimental and numerical results.To quantitatively describe the model performance, four statistical methods were introduced here as well [33, 34]. Among them, the mean absolute error (MAE) can be defined as follows:(4)MAE=1p∑i=1pxi−yi,where xi represents the measurements, yi represents the numerical values, and p is the total experimental test points.Equation (5) shows the definition of the mean absolute percentage error (MAPE):(5)MAPE=1p∑i=1pxi−yixi×100%.The root-mean-square error (RMSE) is as(6)RMSE=1p∑i=1pxi−yi2.For the index of agreement (IA), it is calculated as follows:(7)IA=1−∑i=1pxi−yi2∑i=1pyi−xm+xi−xm2.When the result value is 0 for the MAE, MAPE, and RMSE and 1 for IA, it shows that the simulation results agree well with the measurements. Table 4 provides the calculation results for the temperature and velocity. MAE, MAPE, and RMSE values of velocity are 0.023 m/s, 0.097%, and 0.001 m/s, respectively, and those of temperature are 0.05°C, 0.01%, and 0.05°C, respectively, which are close to 0. The IA value of temperature is 0.97 and that of velocity is 0.876; both are close to unity. The simulation results are basically consistent with the experimental results, which indicates that the numerical model is reliable to calculate different air parameters of stratum ventilation in various cases.Table 4
The detailed information of model performance.
MetricTemperatureVelocityMAE0.05°C0.023 m/sMAPE0.01%0.097%RMSE0.05°C0.001 m/sIA0.970.876


## 3.2. Effect of Supply Air Parameters on Ventilation Effectiveness

### 3.2.1. Supply Air Temperature

In this study, ventilation effectiveness is applied as an index to access the energy utilization efficiency. As known to all, the higher the ventilation effectiveness, the better the energy efficiency. Figure3 shows the calculation and fitting curves of the average ventilation effectiveness among the occupied zones at different supply air temperatures. According to the related research [18], polynomial can be applied to the fitting in the study on stratum ventilation. Based on this, the fitting formulae are as follows:(8)Et26=1.005+0.236h−0.06h2,Et27=0.81+0.186h−0.05h2,Et28=0.825+0.187h−0.05h2,Et29=0.913+0.213h−0.05h2,where Et26 is the ventilation effectiveness at supply air temperature of 26°C; Et27 is the ventilation effectiveness at the supply air temperature of 27°C; Et28 is the ventilation effectiveness at the supply air temperature of 28°C; Et29 is the ventilation effectiveness at the supply air temperature of 29°C; h is the height, m.Figure 3
Average ventilation effectiveness at different supply air temperatures.γ is introduced for the propose of comparing the performance under the four supply air temperatures, which is defined as follows:(9)γ=Etx¯Et¯=∫0h0Etx/h0∫0h0Et/h0,where Etx¯ is the mean ventilation effectiveness in any case among the breathing zones; Et¯ is the mean ventilation effectiveness in benchmark case among the breathing zones; h0 is the height of the breathing level, m. In this study, h0 is set as 1.1 m. γ is the ratio of Etx¯ to Et¯. Setting Et26¯ as the base value, it is calculated that Et26¯ is 1.11, Et27¯ is 0.892, Et28¯ is 0.908, and Et29¯ is 1.01. Hence, γ27-26 is 0.804, γ28-26 is 0.818, and γ29-26 is 0.918.The ventilation effectiveness is affected synthetically by the thermal buoyancy and average temperature among the occupied zones. When the supply air temperature is 26°C, more heat would stay in the occupied zone contributing by less thermal buoyancy, thus leading to higher ventilation effectiveness. Since the air inlet of the stratum ventilation is located at the middle level of the side wall, the supply air temperature of 29°C leads the temperature near the supply air inlet to become higher and then resulting in a higher average temperature among the occupied zones compared with that under 27°C and 28°C. However, thermal buoyancy plays a dominant role in these two mechanisms. Hence, the ventilation effectiveness under 26°C of the supply air temperature is the highest. And the ventilation effectiveness under 26°C of the supply air temperatures being 27°C, 28°C, and 29°C is lower.


### 3.2.2. Airflow Rate

Similarly, to compare the ventilation efficiency at different airflow rates, Figure4 fits the ventilation efficiency at different heights. The formulae are as follows:(10)Et7=0.955+0.097h−0.026h2,Et10=0.879+0.176h−0.05h2,Et12=0.911+0.158h−0.04h2,Et15=0.912+0.128h−0.03h2,where Et7 is the ventilation effectiveness for the 7ACH case; Et10 is the ventilation effectiveness of 10ACH; Et12 is the ventilation effectiveness of 12ACH; Et15 is the ventilation effectiveness of 15ACH. Et7¯ is set as the base value. It can be calculated that Et7¯ is 0.998, Et10¯ is 0.956, Et12¯ is 0.982, Et15¯ is 0.970, γ10-7 is 0.958, γ12-7 is 0.984, and γ15-7 is 0.972. It indicates that the ventilation effectiveness is the highest at 7ACH.Figure 4
Average ventilation effectiveness at different airflow rates (ACH).


### 3.2.3. Supply Air Angle

The schematic diagram of supply vane angle discussed in this study is provided as Figure5.Figure 5
The supply vane angle schematic diagram.
(a)(b)(c)(d)Using the same method, as shown in Figure6, the fitted formulae of the ventilation effectiveness for different angles are given as follows:(11)Et15=0.932+0.131h−0.035h2,Et30=0.869+0.109h−0.03h2,Et45=0.976+0.119h−0.03h2,Et60=0.997+0.073h−0.02h2,where Et15 is the ventilation effectiveness for the supply air angle of 15°; Et30 is the ventilation effectiveness of supply air angle of 30°; Et45 is the ventilation effectiveness of supply air angle of 45°; Et60 is the ventilation effectiveness of supply air angle of 60°. Et15¯ is selected as the base value. It is calculated that Et15¯ is 0.990, Et30¯ is 0.917, Et45¯ is 1.03, Et60¯ is 1.03, γ30-15 is 0.926, γ45-15 is 1.04, and γ60-15 is 1.04. It depicts that, with a supply air angel of 45°, the ventilation effectiveness can achieve the highest value.Figure 6
Average ventilation effectiveness at different supply air angles.


### 3.2.4. Return Air Outlet Position

The fitting formulae of the average ventilation effectiveness under different air outlet positions are as follows:(12)Etc=0.932+0.133h−0.035h2,Etoo=0.96+0.142h−0.04h2,Etuo=1.004+0.149h−0.04h2,Etus=0.947+0.135h−0.04h2,where Etc is the ventilation effectiveness for the case of air outlet installed on the ceiling; Etoo is the ventilation effectiveness of the outlet installed at the same level on the wall opposite to the supply air inlet; Etuo is the ventilation effectiveness for the air outlet located at the bottom of the wall opposite to the inlet; Etus is the ventilation effectiveness for the outlet located at the bottom of the same wall as the inlet. As shown in Figure 7, the change trends of Etc, Etoo, Etuo, and Etus are approximately consistent. And Etc¯ is 0.991, Etoo¯ is 1.02, Etuo¯ is 1.07, Etus¯ is 1.01, γoo-c is 1.03, γuo-c is 1.08, and γus-c is 1.02 by calculation. The ventilation effectiveness can be obtained as the highest when the outlet is located under the opposite side.Figure 7
Average ventilation effectiveness at different air outlet positions.


## 3.2.1. Supply Air Temperature

In this study, ventilation effectiveness is applied as an index to access the energy utilization efficiency. As known to all, the higher the ventilation effectiveness, the better the energy efficiency. Figure3 shows the calculation and fitting curves of the average ventilation effectiveness among the occupied zones at different supply air temperatures. According to the related research [18], polynomial can be applied to the fitting in the study on stratum ventilation. Based on this, the fitting formulae are as follows:(8)Et26=1.005+0.236h−0.06h2,Et27=0.81+0.186h−0.05h2,Et28=0.825+0.187h−0.05h2,Et29=0.913+0.213h−0.05h2,where Et26 is the ventilation effectiveness at supply air temperature of 26°C; Et27 is the ventilation effectiveness at the supply air temperature of 27°C; Et28 is the ventilation effectiveness at the supply air temperature of 28°C; Et29 is the ventilation effectiveness at the supply air temperature of 29°C; h is the height, m.Figure 3
Average ventilation effectiveness at different supply air temperatures.γ is introduced for the propose of comparing the performance under the four supply air temperatures, which is defined as follows:(9)γ=Etx¯Et¯=∫0h0Etx/h0∫0h0Et/h0,where Etx¯ is the mean ventilation effectiveness in any case among the breathing zones; Et¯ is the mean ventilation effectiveness in benchmark case among the breathing zones; h0 is the height of the breathing level, m. In this study, h0 is set as 1.1 m. γ is the ratio of Etx¯ to Et¯. Setting Et26¯ as the base value, it is calculated that Et26¯ is 1.11, Et27¯ is 0.892, Et28¯ is 0.908, and Et29¯ is 1.01. Hence, γ27-26 is 0.804, γ28-26 is 0.818, and γ29-26 is 0.918.The ventilation effectiveness is affected synthetically by the thermal buoyancy and average temperature among the occupied zones. When the supply air temperature is 26°C, more heat would stay in the occupied zone contributing by less thermal buoyancy, thus leading to higher ventilation effectiveness. Since the air inlet of the stratum ventilation is located at the middle level of the side wall, the supply air temperature of 29°C leads the temperature near the supply air inlet to become higher and then resulting in a higher average temperature among the occupied zones compared with that under 27°C and 28°C. However, thermal buoyancy plays a dominant role in these two mechanisms. Hence, the ventilation effectiveness under 26°C of the supply air temperature is the highest. And the ventilation effectiveness under 26°C of the supply air temperatures being 27°C, 28°C, and 29°C is lower.


## 3.2.2. Airflow Rate

Similarly, to compare the ventilation efficiency at different airflow rates, Figure4 fits the ventilation efficiency at different heights. The formulae are as follows:(10)Et7=0.955+0.097h−0.026h2,Et10=0.879+0.176h−0.05h2,Et12=0.911+0.158h−0.04h2,Et15=0.912+0.128h−0.03h2,where Et7 is the ventilation effectiveness for the 7ACH case; Et10 is the ventilation effectiveness of 10ACH; Et12 is the ventilation effectiveness of 12ACH; Et15 is the ventilation effectiveness of 15ACH. Et7¯ is set as the base value. It can be calculated that Et7¯ is 0.998, Et10¯ is 0.956, Et12¯ is 0.982, Et15¯ is 0.970, γ10-7 is 0.958, γ12-7 is 0.984, and γ15-7 is 0.972. It indicates that the ventilation effectiveness is the highest at 7ACH.Figure 4
Average ventilation effectiveness at different airflow rates (ACH).


## 3.2.3. Supply Air Angle

The schematic diagram of supply vane angle discussed in this study is provided as Figure5.Figure 5
The supply vane angle schematic diagram.
(a)(b)(c)(d)Using the same method, as shown in Figure6, the fitted formulae of the ventilation effectiveness for different angles are given as follows:(11)Et15=0.932+0.131h−0.035h2,Et30=0.869+0.109h−0.03h2,Et45=0.976+0.119h−0.03h2,Et60=0.997+0.073h−0.02h2,where Et15 is the ventilation effectiveness for the supply air angle of 15°; Et30 is the ventilation effectiveness of supply air angle of 30°; Et45 is the ventilation effectiveness of supply air angle of 45°; Et60 is the ventilation effectiveness of supply air angle of 60°. Et15¯ is selected as the base value. It is calculated that Et15¯ is 0.990, Et30¯ is 0.917, Et45¯ is 1.03, Et60¯ is 1.03, γ30-15 is 0.926, γ45-15 is 1.04, and γ60-15 is 1.04. It depicts that, with a supply air angel of 45°, the ventilation effectiveness can achieve the highest value.Figure 6
Average ventilation effectiveness at different supply air angles.


## 3.2.4. Return Air Outlet Position

The fitting formulae of the average ventilation effectiveness under different air outlet positions are as follows:(12)Etc=0.932+0.133h−0.035h2,Etoo=0.96+0.142h−0.04h2,Etuo=1.004+0.149h−0.04h2,Etus=0.947+0.135h−0.04h2,where Etc is the ventilation effectiveness for the case of air outlet installed on the ceiling; Etoo is the ventilation effectiveness of the outlet installed at the same level on the wall opposite to the supply air inlet; Etuo is the ventilation effectiveness for the air outlet located at the bottom of the wall opposite to the inlet; Etus is the ventilation effectiveness for the outlet located at the bottom of the same wall as the inlet. As shown in Figure 7, the change trends of Etc, Etoo, Etuo, and Etus are approximately consistent. And Etc¯ is 0.991, Etoo¯ is 1.02, Etuo¯ is 1.07, Etus¯ is 1.01, γoo-c is 1.03, γuo-c is 1.08, and γus-c is 1.02 by calculation. The ventilation effectiveness can be obtained as the highest when the outlet is located under the opposite side.Figure 7
Average ventilation effectiveness at different air outlet positions.


## 3.3. Effect of Supply Air Parameters on Effective Draft Temperature (EDT)

### 3.3.1. Supply Air Temperature

Besides the ventilation effectiveness, effective draft temperature (EDT) is also a crucial factor for the thermal comfort evaluation. EDTs at three typical heights, namely, 0.1 m, 0.6 m, and 1.1 m, are calculated by (3) to obtain the frequency distribution under different supply air temperatures, as shown in Figure 8. It indicates that when the supply air temperature is 26.0°C, 62% of EDT is 0.4 K at the 0.1 m level, 78% of EDT is 0.5 K on the 0.6 m plane, and 68% of EDT is 1.1 K on the 1.1 m plane. When the supply air temperature is 27.0°C, 67% of EDT is 0K on the 0.1 m plane, 76% of EDT is 0.8 K on the 0.6 m plane, and 65% of EDT is 0.9 K on the 1.1 m plane. When the temperature is 28.0°C, 71% of EDT is 0K on the 0.1 m plane, 72% EDT is 0.8 K on the 0.6 m plane, and 62% EDT is 0.9 K on the 1.1 m plane. When the air supply temperature is 29.0°C, the 0.1 m plane has 74% EDT of −0.09 K, the 0.6 m plane has 63% EDT of 0.8 K, and the 1.1 m plane has 59% EDT of 0.9 K. It indicates that the EDT on the 0.1 m plane is closer to the neutral temperature when the supply air temperature is 27.0°C and 28.0°C. And the percentage around the neutral temperature is higher when the supply air temperature is 28.0°C. Hence, for the perspective of the EDT, the supply air temperature of 28.0°C shows the best effect.Figure 8
EDT frequency at different supply air temperatures.
(a)(b)(c)(d)It is reported that the EDT range that satisfies the occupant is between −1.2 K and 1.2 K. The average EDTs at four supply air temperatures are presented in Figure9. It can be seen that the EDTs at 26–29°C are all within the satisfaction range. And the average EDTs among the occupied zone are 0.82 K (26°C), 0.68 K (27°C), 0.52 K (28°C), and 0.37 K (29°C), respectively. Combining with the EDT frequency discussed results, 28.0°C is optimum under considering the impact of supply air temperature on EDT.Figure 9
Average EDT at different supply air temperatures.


### 3.3.2. Airflow Rate

The frequency distributions of EDT at different airflow rates are shown in Figure10. It indicates that 85.3% EDT is 0 K at the height of 0.1 m, 56.8% EDT is 0.8 K at the height of 0.6 m, and 65.5% EDT is 1K at the height of 1.1 m in the case of 10ACH. 61.45% EDT is 0.8 K on the 0.1 m plane, 82.2% EDT is 0 K on the 0.6 m plane, and 49.9% EDT is 1 K on the 1.1 m plane in the case of 15ACH. As for the case of 12ACH, the highest frequency at 0.1 m, 0.6 m, and 1.1 m is 71.6, 67.8, and 67.9% with EDT being 1K. Compared with other ACHs, the EDT frequency distribution close to 0K at 0.1 m, 0.6 m, and 1.1 m is relatively high when the airflow is 12ACH. Therefore, the EDT at 12ACH has the highest percentage located in the comfort range among the occupied zones.Figure 10
EDT frequency at different airflow rates (ACH).
(a)(b)(c)(d)Meanwhile, Figure11 shows that the EDTs among the occupied zones with airflow of 7–15ACH are all within the satisfaction range. However, the EDT of 10ACH is close to the upper limit of the satisfaction range. The average EDTs under different airflows among the occupied zones are 0.87 K (7ACH), 0.87 K (10ACH), 0.61 K (12ACH), and 0.58 K (15ACH), respectively. Hence, 12ACH is optimum under considering the impact of airflow on EDT combining with the EDT frequency.Figure 11
Average EDT at different airflow rates (ACH).


### 3.3.3. Air Supply Angle

Similarly, to evaluate the impact of the air supply angle on the EDT, the frequency distribution at different supply air angles is presented in Figure12. It can be seen that most of the EDTs at four air supply angles are within the comfort interval. When the air supply angle is 60°, the proportions located in comfort zone at 0.1 m, 0.6 m, and 1.1 m are 95%, 97%, and 90%, respectively, which gets the highest among the four air supply angles. Therefore, from the viewpoint of the EDT frequency distribution, it is optimal when the supply air angle is 60°.Figure 12
EDT frequency at different supply air angles.
(a)(b)(c)(d)In Figure13, the EDTs of the occupied area with supply angles of 45° and 60° are within the satisfaction range while those of 15° and 30° are beyond the upper limit of the satisfaction range. Meanwhile, the average EDTs under different angles among the occupied zones are 1.88 K (15°), 1.44 K (30°), 0.67 K (45°), and −0.91 K (60°), respectively. Although the average EDT at the supply angle of 45° is closer to 0 K relative to 60°, the proportions located within the comfort zone at 60° is the highest according to the frequency distribution. Hence, 60° is optimum under considering the impact of supply angle on EDT.Figure 13
Average EDT at different supply air angles.


### 3.3.4. Return Air Outlet Position

The frequency statistics of the EDTs in the occupied zone are calculated under discussed return air outlet positions. Figure14 demonstrates that more than 86% of the EDTs under the four return air outlets are within the comfort range. And the proportions within the comfort range of the three return air outlet layouts, namely, on the ceiling, right on the opposite wall, and at the lower level on the opposite wall, are the same. When the position of the return air outlet is at the lower level on the same wall, 95% of the EDTs belong to the comfort range, so the effect of EDT is the best when the return air outlet is on the same wall beneath the air supply inlet.Figure 14
EDT frequency for different air outlet positions.
(a)(b)(c)(d)As presented in Figure15, it can be seen that the EDTs among the occupied zones under four outlet locations are all within the satisfaction range. Nevertheless, the EDT with the outlet under the opposite side is close to the upper limit of the satisfaction range. Meanwhile, the average EDTs under different return air outlets among the occupied zones are 0.62 K (on the ceiling), 0.74 K (on the opposite side), 0.89 K (under the opposite side), and 0.72 K (under the same side), respectively. Because the EDT located in the comfort zone is the highest when the outlets are installed under the same side with the inlets, the position of the return air outlet is located at the same wall but at a lower level as the air supply inlet can reach the best performance.Figure 15
Average EDT at different air outlet positions.


## 3.3.1. Supply Air Temperature

Besides the ventilation effectiveness, effective draft temperature (EDT) is also a crucial factor for the thermal comfort evaluation. EDTs at three typical heights, namely, 0.1 m, 0.6 m, and 1.1 m, are calculated by (3) to obtain the frequency distribution under different supply air temperatures, as shown in Figure 8. It indicates that when the supply air temperature is 26.0°C, 62% of EDT is 0.4 K at the 0.1 m level, 78% of EDT is 0.5 K on the 0.6 m plane, and 68% of EDT is 1.1 K on the 1.1 m plane. When the supply air temperature is 27.0°C, 67% of EDT is 0K on the 0.1 m plane, 76% of EDT is 0.8 K on the 0.6 m plane, and 65% of EDT is 0.9 K on the 1.1 m plane. When the temperature is 28.0°C, 71% of EDT is 0K on the 0.1 m plane, 72% EDT is 0.8 K on the 0.6 m plane, and 62% EDT is 0.9 K on the 1.1 m plane. When the air supply temperature is 29.0°C, the 0.1 m plane has 74% EDT of −0.09 K, the 0.6 m plane has 63% EDT of 0.8 K, and the 1.1 m plane has 59% EDT of 0.9 K. It indicates that the EDT on the 0.1 m plane is closer to the neutral temperature when the supply air temperature is 27.0°C and 28.0°C. And the percentage around the neutral temperature is higher when the supply air temperature is 28.0°C. Hence, for the perspective of the EDT, the supply air temperature of 28.0°C shows the best effect.Figure 8
EDT frequency at different supply air temperatures.
(a)(b)(c)(d)It is reported that the EDT range that satisfies the occupant is between −1.2 K and 1.2 K. The average EDTs at four supply air temperatures are presented in Figure9. It can be seen that the EDTs at 26–29°C are all within the satisfaction range. And the average EDTs among the occupied zone are 0.82 K (26°C), 0.68 K (27°C), 0.52 K (28°C), and 0.37 K (29°C), respectively. Combining with the EDT frequency discussed results, 28.0°C is optimum under considering the impact of supply air temperature on EDT.Figure 9
Average EDT at different supply air temperatures.


## 3.3.2. Airflow Rate

The frequency distributions of EDT at different airflow rates are shown in Figure10. It indicates that 85.3% EDT is 0 K at the height of 0.1 m, 56.8% EDT is 0.8 K at the height of 0.6 m, and 65.5% EDT is 1K at the height of 1.1 m in the case of 10ACH. 61.45% EDT is 0.8 K on the 0.1 m plane, 82.2% EDT is 0 K on the 0.6 m plane, and 49.9% EDT is 1 K on the 1.1 m plane in the case of 15ACH. As for the case of 12ACH, the highest frequency at 0.1 m, 0.6 m, and 1.1 m is 71.6, 67.8, and 67.9% with EDT being 1K. Compared with other ACHs, the EDT frequency distribution close to 0K at 0.1 m, 0.6 m, and 1.1 m is relatively high when the airflow is 12ACH. Therefore, the EDT at 12ACH has the highest percentage located in the comfort range among the occupied zones.Figure 10
EDT frequency at different airflow rates (ACH).
(a)(b)(c)(d)Meanwhile, Figure11 shows that the EDTs among the occupied zones with airflow of 7–15ACH are all within the satisfaction range. However, the EDT of 10ACH is close to the upper limit of the satisfaction range. The average EDTs under different airflows among the occupied zones are 0.87 K (7ACH), 0.87 K (10ACH), 0.61 K (12ACH), and 0.58 K (15ACH), respectively. Hence, 12ACH is optimum under considering the impact of airflow on EDT combining with the EDT frequency.Figure 11
Average EDT at different airflow rates (ACH).


## 3.3.3. Air Supply Angle

Similarly, to evaluate the impact of the air supply angle on the EDT, the frequency distribution at different supply air angles is presented in Figure12. It can be seen that most of the EDTs at four air supply angles are within the comfort interval. When the air supply angle is 60°, the proportions located in comfort zone at 0.1 m, 0.6 m, and 1.1 m are 95%, 97%, and 90%, respectively, which gets the highest among the four air supply angles. Therefore, from the viewpoint of the EDT frequency distribution, it is optimal when the supply air angle is 60°.Figure 12
EDT frequency at different supply air angles.
(a)(b)(c)(d)In Figure13, the EDTs of the occupied area with supply angles of 45° and 60° are within the satisfaction range while those of 15° and 30° are beyond the upper limit of the satisfaction range. Meanwhile, the average EDTs under different angles among the occupied zones are 1.88 K (15°), 1.44 K (30°), 0.67 K (45°), and −0.91 K (60°), respectively. Although the average EDT at the supply angle of 45° is closer to 0 K relative to 60°, the proportions located within the comfort zone at 60° is the highest according to the frequency distribution. Hence, 60° is optimum under considering the impact of supply angle on EDT.Figure 13
Average EDT at different supply air angles.


## 3.3.4. Return Air Outlet Position

The frequency statistics of the EDTs in the occupied zone are calculated under discussed return air outlet positions. Figure14 demonstrates that more than 86% of the EDTs under the four return air outlets are within the comfort range. And the proportions within the comfort range of the three return air outlet layouts, namely, on the ceiling, right on the opposite wall, and at the lower level on the opposite wall, are the same. When the position of the return air outlet is at the lower level on the same wall, 95% of the EDTs belong to the comfort range, so the effect of EDT is the best when the return air outlet is on the same wall beneath the air supply inlet.Figure 14
EDT frequency for different air outlet positions.
(a)(b)(c)(d)As presented in Figure15, it can be seen that the EDTs among the occupied zones under four outlet locations are all within the satisfaction range. Nevertheless, the EDT with the outlet under the opposite side is close to the upper limit of the satisfaction range. Meanwhile, the average EDTs under different return air outlets among the occupied zones are 0.62 K (on the ceiling), 0.74 K (on the opposite side), 0.89 K (under the opposite side), and 0.72 K (under the same side), respectively. Because the EDT located in the comfort zone is the highest when the outlets are installed under the same side with the inlets, the position of the return air outlet is located at the same wall but at a lower level as the air supply inlet can reach the best performance.Figure 15
Average EDT at different air outlet positions.


## 4. Conclusion

The optimal heating parameters of stratum ventilation were explored through experimental and numerical approaches by comparing the differences of impacts among various parameters on the aspects of ventilation performance and thermal comfort. The main conclusions are presented as below:(1)
The ventilation effectiveness was higher with 26°C of the supply air temperature, 7ACH of the airflow rate, and 45° of the air supply angle. The energy utilization can achieve the highest with the above supply air parameters. Moreover, by calculating and comparing the ventilation effectiveness under various return air outlets, it indicated that the value of ventilation effectiveness reached its highest when the return air outlet is located at 0.5 m above the floor on the wall opposite to the air inlet.(2)
The EDT range among the occupied zones was between 0.65 and 1.02 K at the supply air temperature of 28°C, which is the closest to 0 K compared with that at other supply air temperatures. Meanwhile, the EDTs with the air supply angle of 60° and airflow of 12ACH are closer to the neutral temperature. The EDT under the return air outlet at the bottom of the same wall as the air supply inlet was in the range of 0.53–0.75 K, which is the closest to the comfort temperature. Hence, the best supply air parameters are 28°C, 12ACH, 60° and return air outlet at the bottom of the same wall as the air supply inlet under stratum ventilation for obtaining the best thermal comfort.The related conclusions obtained from this research provide the theoretical basis for stratum ventilation design and promote its heating application in Southern China.



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*Source: 6615148-2021-04-08.xml*