# Optimization of Indoor Thermal Comfort Parameters with the Adaptive Network-Based Fuzzy Inference System and Particle Swarm Optimization Algorithm

Authors: Jing Li; Shao-Wu Yin; Guang-Si Shi; Li Wang
Journal: Mathematical Problems in Engineering
 (2017)

---

## Abstract

The goal of this study is to improve thermal comfort and indoor air quality with the adaptive network-based fuzzy inference system (ANFIS) model and improved particle swarm optimization (PSO) algorithm. A method to optimize air conditioning parameters and installation distance is proposed. The methodology is demonstrated through a prototype case, which corresponds to a typical laboratory in colleges and universities. A laboratory model is established, and simulated flow field information is obtained with the CFD software. Subsequently, the ANFIS model is employed instead of the CFD model to predict indoor flow parameters, and the CFD database is utilized to train ANN input-output “metamodels” for the subsequent optimization. With the improved PSO algorithm and the stratified sequence method, the objective functions are optimized. The functions comprise PMV, PPD, and mean age of air. The optimal installation distance is determined with the hemisphere model. Results show that most of the staff obtain a satisfactory degree of thermal comfort and that the proposed method can significantly reduce the cost of building an experimental device. The proposed methodology can be used to determine appropriate air supply parameters and air conditioner installation position for a pleasant and healthy indoor environment.


---

## Body

## 1. Introduction

The quality of the indoor air environment in offices is related to the comfort and health of people and affects the work efficiency of people. Strong local blowing, poor air circulation, and odors exist in an air-conditioned room. Furthermore, the long-term existence of air pollutants in the human body exerts a pernicious effect on people’s health. According to the definition of “healthy” by the World Health Organization, mental and physical aspects should be promoted by having healthy indoor air and a safe, healthy, comfortable indoor environment; these two are the fundamental purposes of modern architecture [1]. Therefore, the problem of evaluating and improving indoor environment quality should be solved immediately.The heating ventilation air conditioning (HVAC) design for modern indoor settings is based only on temperature, air velocity, and relative humidity. However, an individual’s perceptions of the environment cannot be exactly reflected by these three indicators. Predicted mean vote (PMV), predicted percentage of dissatisfied people (PPD), and mean age of air are generally utilized as evaluation indicators in the design of HVAC, but they are not used as design indicators to guide the design process of HVAC. The installation location of an air conditioner and air supply parameters are designed based on experience and can be amended according to evaluation indicators. However, this method involves much workload and is suboptimal. These controllable parameters required to achieve optimal results were directly considered in this study.The most common and accurate means to predict indoor air movement is the use of computational fluid dynamics (CFD) models [2]. Many studies have investigated CFD applications, particularly the flow and heat transfer. The lattice Boltzmann method, which is utilized for the numerical simulation of flow and heat transfer, was used to study the convection heat transfer of nanofluids in an enclosure by Karimipour et al. [3–7]. The CFD model was used by Skovgaard and Nielsen [8] to simulate indoor air flow, and CFD technology was adopted in air conditioning engineering. However, the model grid was divided into thousands of millions. Therefore, this method is highly complicated in terms of calculation, and the real-time capability is insufficient. To solve this problem, several simplified models [9–11] have been proposed, but the accuracy of these simplified models is worse than that of the CFD model; furthermore, making a dynamic prediction of the thermal environment is difficult [12]. Although the analysis of CFD provides a near-optimal solution, the analysis of CFD parameters is not continuous.As practical tools, mathematical metamodels can convert the discretized domain into a continuous one, and this conversion improves the accuracy of the near-optimal solution without the need for excessive computational power. Artificial neural networks (ANN) have been successfully used to develop such metamodeling relationships between design and objective variables. For example, Krauss et al. [13] used the velocity coefficient as the thermal comfort indicator and discussed the influence of CFD-ANN coupling on the interior design; the computation time was reduced considerably. The backpropagation (BP) neural network model was used by Xu et al. [14] to replace the CFD model in the simulation of indoor air flow. Generally, ANN cannot directly deal with the knowledge structure, although it has a strong self-learning ability. Stvrakakis et al. [15] presented a novel CFD-ANN computational method to optimize window sizes for thermal comfort in ventilated buildings; the novel method uses the radial basis function (RBF) architecture. Although the methodology is useful for architects, the algorithm has its limitations. By referring to previous studies, the fuzzy system and ANN were combined in this study, and an adaptive neural fuzzy inference system (ANFIS) [16] was established. The proposed methodology adopts a CFD-ANFIS coupling procedure to correlate the input and output variables. The simulation results showed that the fitting accuracy and training speed of the metamodel improved significantly.To optimize the solution function, Sun et al. [17] used the genetic algorithm to develop indoor thermal comfort parameters and found that the indoor air quality improved after optimization. Luan and Lu [18], who used the adaptive genetic algorithm to optimize the neural network, also obtained a good experimental result. However, the genetic algorithm cannot solve the problem of large-scale computation because of its complex calculation method and low rate of convergence. Therefore, the algorithm is inclined to result in premature convergence. To improve optimization speed without any loss in precision, the improved particle swarm optimization (PSO) algorithm was employed in this study. The global searching strategy of the population was retained in the improved PSO algorithm to avoid complex genetic operations, such as coding, crossover, and mutation. Thus, the algorithm is simplified and easy to implement.In previous research on indoor environment indicators, PMV [19], PPD [20], and age of air [21] were widely used as thermal comfort indicators. In this study, a physical laboratory model was established with the CFD software. Indoor air temperature, air velocity, radiation temperature, and relative humidity as well as the distance between the air supply outlet and the sampling point were obtained through a CFD simulation. The database in CFD was adopted to train ANN. Subsequently, the objective functions of the PSO algorithm were established; these functions comprised PMV, PPD, and age of air [22–24]. Optimization of the objective functions was then conducted with the stratified sequence method [25, 26], and the optimal values of the parameters were obtained. Overall, the proposed methodology meets the requirements of indoor thermal comfort and provides a reference for the design and improvement of indoor air conditioning systems [27].


## 2. Evaluation Indicators for the Indoor Thermal Comfort Environment

### 2.1. Age of Air

The mean age of air refers to the amount of time air has been in a room; it involves the ability to exclude pollutants. Generally, when indoor pollutant sources are distributed uniformly and a room receives fresh air, the mean age of air is small, the air quality is good, and the ability to remove pollutants is strong. As indicated by its physical meaning, the mean age of air is a significant indicator to measure the freshness degree of air and the exchange of air in an air-conditioned room.


### 2.2. Thermal Comfort Indices

The PMV indicator was developed by Professor P. O. Fanger. PMV indicates the thermal response of humans. The PMV indicator adopts seven degrees [29], as shown in Table 1.Table 1
PMV indicator values.
Thermalsensation
Hot
Warm
Microwarm
Moderate
Microcool
Cool
Cold
PMV
+3
+2
+1
0
−1
−2
−3The feelings of most people in the same environment can be represented by the PMV indicator. Thus, the indicator is utilized to evaluate whether a thermal environment is comfortable or not. However, due to individual differences, the PMV indicator cannot represent all personal feelings. Therefore, PPD was proposed to indicate the percentage of people who are dissatisfied with a given thermal environment.


### 2.3. Indoor Air Parameters

#### 2.3.1. Air Velocity

In a thermal environment, air flow provides fresh air to humans and speeds up the human body’s convective heat and evaporative cooling to a certain extent [30].


#### 2.3.2. Body Temperature

Temperature is the main factor that affects thermal comfort because it affects the human body directly through convection and radiation heat exchange. In this study, body temperature was used as an indicator. Bedford [31] found that the human body is highly sensitive to temperature, and the ability to reproduce the sensation of cold and hot is not lower than the reproducibility of the physiological reaction of the organism.


#### 2.3.3. Radiation Temperature

Average radiation temperature is influenced by surface temperature. Generally, the average radiation temperature is not always uniform in the actual production and living environment. Moreover, people often feel cold or hot in a certain part of the body. Thus, studying the influence of the deviation of the average radiation temperature from the air temperature and the effect of the asymmetry of heating or cooling on the physiological or sensory responses of the human body is important.


#### 2.3.4. Relative Humidity

The influence of environmental humidity on the thermal comfort of the human body is mainly manifested in the effect of heat loss from the skin to the environment. Research shows that less than 30% humidity causes an unsatisfactory thermal sensation and affects indoor air quality [32].


## 2.1. Age of Air

The mean age of air refers to the amount of time air has been in a room; it involves the ability to exclude pollutants. Generally, when indoor pollutant sources are distributed uniformly and a room receives fresh air, the mean age of air is small, the air quality is good, and the ability to remove pollutants is strong. As indicated by its physical meaning, the mean age of air is a significant indicator to measure the freshness degree of air and the exchange of air in an air-conditioned room.


## 2.2. Thermal Comfort Indices

The PMV indicator was developed by Professor P. O. Fanger. PMV indicates the thermal response of humans. The PMV indicator adopts seven degrees [29], as shown in Table 1.Table 1
PMV indicator values.
Thermalsensation
Hot
Warm
Microwarm
Moderate
Microcool
Cool
Cold
PMV
+3
+2
+1
0
−1
−2
−3The feelings of most people in the same environment can be represented by the PMV indicator. Thus, the indicator is utilized to evaluate whether a thermal environment is comfortable or not. However, due to individual differences, the PMV indicator cannot represent all personal feelings. Therefore, PPD was proposed to indicate the percentage of people who are dissatisfied with a given thermal environment.


## 2.3. Indoor Air Parameters

### 2.3.1. Air Velocity

In a thermal environment, air flow provides fresh air to humans and speeds up the human body’s convective heat and evaporative cooling to a certain extent [30].


### 2.3.2. Body Temperature

Temperature is the main factor that affects thermal comfort because it affects the human body directly through convection and radiation heat exchange. In this study, body temperature was used as an indicator. Bedford [31] found that the human body is highly sensitive to temperature, and the ability to reproduce the sensation of cold and hot is not lower than the reproducibility of the physiological reaction of the organism.


### 2.3.3. Radiation Temperature

Average radiation temperature is influenced by surface temperature. Generally, the average radiation temperature is not always uniform in the actual production and living environment. Moreover, people often feel cold or hot in a certain part of the body. Thus, studying the influence of the deviation of the average radiation temperature from the air temperature and the effect of the asymmetry of heating or cooling on the physiological or sensory responses of the human body is important.


### 2.3.4. Relative Humidity

The influence of environmental humidity on the thermal comfort of the human body is mainly manifested in the effect of heat loss from the skin to the environment. Research shows that less than 30% humidity causes an unsatisfactory thermal sensation and affects indoor air quality [32].


## 2.3.1. Air Velocity

In a thermal environment, air flow provides fresh air to humans and speeds up the human body’s convective heat and evaporative cooling to a certain extent [30].


## 2.3.2. Body Temperature

Temperature is the main factor that affects thermal comfort because it affects the human body directly through convection and radiation heat exchange. In this study, body temperature was used as an indicator. Bedford [31] found that the human body is highly sensitive to temperature, and the ability to reproduce the sensation of cold and hot is not lower than the reproducibility of the physiological reaction of the organism.


## 2.3.3. Radiation Temperature

Average radiation temperature is influenced by surface temperature. Generally, the average radiation temperature is not always uniform in the actual production and living environment. Moreover, people often feel cold or hot in a certain part of the body. Thus, studying the influence of the deviation of the average radiation temperature from the air temperature and the effect of the asymmetry of heating or cooling on the physiological or sensory responses of the human body is important.


## 2.3.4. Relative Humidity

The influence of environmental humidity on the thermal comfort of the human body is mainly manifested in the effect of heat loss from the skin to the environment. Research shows that less than 30% humidity causes an unsatisfactory thermal sensation and affects indoor air quality [32].


## 3. Modeling

### 3.1. CFD Modeling

With previous models as a basis, a typical laboratory model was established according to the characteristics of a university laboratory. The physical model is shown in Figure1. The size of the model was 8.2 m × 5.4 m × 3.8 m, and the laboratory was enclosed in a stand-alone building complex that included 14 seated people and typical equipment, such as a window (4.4 m × 1.5 m), a file cabinet (1.8 m × 0.4 m × 3.5 m), 8 lamps (50 W), and 14 desks. In addition, a computer emitting 200 W of heat was placed on each desk. People with an average height of 1.73 m were assumed to remain seated in front of the computers and release heat of 58.2 W/m2.Figure 1
Physical laboratory model.The air supply outlet of the model (size of 0.9 m × 0.5 m) was above the window on the rear wall, and the return air vent was on the opposite wall. The air supply’s temperature and velocity were 19°C and 0.75 m/s, respectively. The initial relative humidity in the room was 60%.To simplify the research problem, several assumptions were adopted [33]. First, indoor air cannot be compressed and is in line with the Boussinesq hypothesis. Second, indoor air exhibits a steady flow. Third, the thermal radiation between the solid walls and objects is disregarded. Fourth, indoor air is conducive for transparent radiation media. Lastly, the influence of air leakage is disregarded.Under these assumptions, the governing equations are satisfied in general form as follows:(1)∂ρϕ∂t+divρuϕ=divΓgradϕ+s,where ϕ is a general variable, Γ is the generalized diffusion coefficient, and s is the generalized source term.The CFD software was used to establish the laboratory model. A hexahedral mesh grid was utilized, and the CFD model was simulated. A total of 1000 datasets from the model were obtained when the CFD model was calculated to converge. The data were obtained from the height of the human chest (XZ section of Y = 1.1 m height), and D represents the distance from the sampling point to the air supply outlet. Some of the data are illustrated in Table 2.Table 2
Indoor parameters.
Code
Indoor temperatureT (°C)
Current SpeedV  (m/s)
DistanceD (m)
Radiant temperatureTr (°C)
Relative humidityw (%)
PMV
PPD
Age of air(s)
1
22.98
0.26
2.21
20.32
49.93
-
0.84
20.04
128.97
2
23.01
0.32
2.33
20.18
50.19
-
0.95
24.06
122.98
3
22.38
0
2.51
21.14
51.05
-
0.38
8.07
137.11
4
23.14
0.16
2.60
20.43
51.38
-
0.60
12.67
137.37
5
22.71
0.22
2.76
20.28
51.29
-
0.79
18.30
124.19
⋯
⋯
⋯
⋯
⋯
⋯
⋯
⋯
⋯
997
22.63
0.22
6.50
21.62
53.91
-
0.41
8.59
189.68
998
24.92
0.12
7.81
22.72
56.06
-
0.10
7.12
186.41
999
24.91
0.09
8.62
20.76
57.48
-
0.13
5.38
137.34
1000
24.15
0
8.82
22.47
53.23
0.01
5.00
161.24The distributions of indoor thermal comfort indicators PMV, PPD, and mean age of air were obtained with a postprocessing software and are shown in Figures2–4, respectively.Figure 2
Distribution of PMV.Figure 3
Distribution of PPD.Figure 4
Distribution of the mean air age.The smallest values of PMV were around −1.5 in the seat near the air supply outlet of the air conditioner, as depicted in Figure2. The largest PMV values were about 0.6 in the upper left corner of Figure 2. With regard to people’s comfort, the values of PMV were between −1.5 and −1 in the seat near the air supply outlet, and people in this indoor setting have an obvious feeling of coldness. The values of PMV were between −0.5 and 0.5 in the seat near the return air vent, and people here have a feeling of “moderate” hotness and coldness. In the middle seats of the room, the values of PMV were between −1 and 0.2, and the feeling of thermal discomfort was obvious. Overall, the distribution of PMV values was uneven. The farther a location was from the air supply outlet, the greater the values of PMV were. The largest difference in the distribution of PMV values was obtained in the middle seats.As shown in Figure3, the largest values of PPD were around 80% in the seat near the air supply outlet of the air conditioner. The smallest PPD values were about 10% in the upper left corner of Figure 3. In terms of the degree of people’s satisfaction, the distribution of PPD values was uneven around the seat near the air supply outlet. The PPD values in the lower right corner of Figure 3 range from 50% to 75. Several indoor persons exhibited symptoms of maladjustment, and the rate of dissatisfaction was high. The PPD values were between 10% and 15% (upper right corner of Figure 3), which means that most indoor persons felt good and were highly satisfied with the environment. The PPD values were between 15% and 25% in the seat near the return air vent; most persons felt generally satisfied. The PPD values were around 10% in the upper left corner of Figure 3, which indicates that the persons indoors were highly satisfied with the environment. The PPD values were between 10% and 20% in the middle seats of the room, and people here felt generally satisfied with the environment. In sum, the distribution of PPD values was uneven. In the seat near the air supply outlet, people demonstrated highest satisfaction with the environment, as shown in the upper left corner of Figure 3 where the PPD values are the largest; this location did not meet people’s requirements for a thermally comfortable environment. The PPD values ranged from 10% to 15% in the middle part of the room, and these values produced satisfactory thermal sensations.The distribution of the mean age of air in the room is presented in Figure4. The values of air age were between 20 and 60 s in the seat near the air supply outlet of the air conditioner. The values of air age are 220 s in the upper left corner of Figure 4 and are the largest values of air age. The analysis of the people’s feelings toward the freshness degree of indoor air showed that people felt more comfortable with the air flow in the seat near the air supply outlet of the air conditioner. In the seat near the return air vent, the values of mean air age were around 220 s, which indicate poor air circulation. The distribution of the mean age of air values was between 60 and 180 s in the middle seats of the room; here, people felt good air circulation. The greater the distance is from the air supply outlet to people, the greater the values of air age are. Overall, the whole tendency is gradually increasing.As described in Table2 and Figures 2–4, when the air supply outlet was arranged in accordance with the model above, the comfort requirements were not met. The distribution of the values of PMV, PPD, and age of air was uneven. The PPD values (Figure 3) were higher than the recommended upper limit (10%) in space, which illustrated that people normally felt uncomfortable with the thermal environment. Therefore, optimizing the control parameters of the indoor air condition is necessary.


### 3.2. ANFIS Modeling

Both fuzzy logic and ANN were utilized in the architecture of ANFIS. ANFIS consisted of if-then rules and input-output pairs. ANFIS training was used to learn the algorithms of the neural network [34]. For simplicity, we assumed that the fuzzy inference system has five inputs (x1,x2,x3,x4,andx5) and one output (f) under consideration. A typical rule set with base fuzzy if-then rules for a first-order Sugeno fuzzy model is presented in Figure 5.Figure 5
Block diagram of ANFIS used in this study.The network structure consisted of three layers, namely, input, hidden, and output. The output data were PMV, PPD, and mean age of air. The number of neurons of the first hidden layer was 10, and that in the second one was 32. One thousand sets of input and output data were trained. The principles of the system are as follows.The fuzzy rule according to Takagi–Sugeno is the linear combination of input variables.Rj: if x1 is A1j and x2 is A2j… and xn is Anj,then yj=pj0+pj1x1+···+pjnxn, where j=1,2,…,m, m≤∏i=1nmi.For a given inputx, the degree of adaptation to each rule can be obtained by using the fuzzy method of the single-point fuzzy set as follows:(2)αj=μA1jx1μA2jx2···μAnjxn,where α¯j=αj/∑i=1mαi.The architecture of the ANFIS used in this study is shown in Figure5. The ANFIS architecture has five inputs and one output. This architecture is formed by using 5 layers and 75 if-then rules as follows.Layer 1. Every node in this layer represents a linguistic variable with a node function as(3)μij=μAijxi,where i=1,2,…,n,j=1,2,…,mi and N is the dimension of the input quantity. mi is the fuzzy partition number of xi. n=5 and mi=3, such that(4)μij=exp-xi-cijσij2,where cij and σij comprise the parameter set and are referred to as premise parameters.Layer 2. Each node in this layer is a circular node represented by II and multiplies the incoming signals and then sends the product out. For instance,(5)αj=μ1i1μ2i2···μnin,where i1∈1,2,…,m1,i2∈1,2,…,m2,…,in∈1,2,…,mn,j=1,2,…,m,m=∏i=1nmi.Layer 3. Every node in this layer is a circular node expressed by N. The itch node calculates the ratio of the itch rules’ firing strength to the sum of all rules’ firing strengths as follows:(6)α¯j=αj∑i=1mαi.Layer 4. Each nodei in this layer is a square node with node function:(7)yij=pj0i+pj1ix1+···+pjnixn=∑l=0npjixlj=1,2,…,m;i=1,2,…,r.Layer 5. The single node in this layer is a circular node shown by P that calculates the overall output as the summation of all incoming signals as follows:(8)yi=∑j=1mα¯jyij.


### 3.3. Results and Discussion

In this study, ANFIS method was used to predict the temperature and flow field in a laboratory. The flow field showed good agreement between CFD and ANFIS results. Additionally, the difference between the values of the stream function of ANFIS and CFD was extremely small. Comparison of the calculated values with the predicted values showed that the mean variance and mean absolute error of the PMV indicator were3.89×10-5 and 0.012, respectively. The mean variance and mean absolute error of the PPD indicator were 6.23×10-5 and 0.89, respectively. The mean variance and mean absolute error of the mean age of air indicator were 8.26×10-3 and 0.15, respectively. Almost similar values of minimum and maximum stream functions in the CFD results were obtained. The fitting curves of the calculated and predicted values are shown in Figures 6–8.Figure 6
Fitting curve of PMV.Figure 7
Fitting curve of PPD.Figure 8
Fitting curve of the mean age of air.Figures6–8 and the error analysis showed that the calculated CFD values of PMV, PPD, and the mean age of air were in agreement with the predicted values of ANFIS. Furthermore, the error was very small. The average convergence time was 15 min. Therefore, the model established by ANFIS has high precision and good coincidence and could be a good substitute for the CFD model.


## 3.1. CFD Modeling

With previous models as a basis, a typical laboratory model was established according to the characteristics of a university laboratory. The physical model is shown in Figure1. The size of the model was 8.2 m × 5.4 m × 3.8 m, and the laboratory was enclosed in a stand-alone building complex that included 14 seated people and typical equipment, such as a window (4.4 m × 1.5 m), a file cabinet (1.8 m × 0.4 m × 3.5 m), 8 lamps (50 W), and 14 desks. In addition, a computer emitting 200 W of heat was placed on each desk. People with an average height of 1.73 m were assumed to remain seated in front of the computers and release heat of 58.2 W/m2.Figure 1
Physical laboratory model.The air supply outlet of the model (size of 0.9 m × 0.5 m) was above the window on the rear wall, and the return air vent was on the opposite wall. The air supply’s temperature and velocity were 19°C and 0.75 m/s, respectively. The initial relative humidity in the room was 60%.To simplify the research problem, several assumptions were adopted [33]. First, indoor air cannot be compressed and is in line with the Boussinesq hypothesis. Second, indoor air exhibits a steady flow. Third, the thermal radiation between the solid walls and objects is disregarded. Fourth, indoor air is conducive for transparent radiation media. Lastly, the influence of air leakage is disregarded.Under these assumptions, the governing equations are satisfied in general form as follows:(1)∂ρϕ∂t+divρuϕ=divΓgradϕ+s,where ϕ is a general variable, Γ is the generalized diffusion coefficient, and s is the generalized source term.The CFD software was used to establish the laboratory model. A hexahedral mesh grid was utilized, and the CFD model was simulated. A total of 1000 datasets from the model were obtained when the CFD model was calculated to converge. The data were obtained from the height of the human chest (XZ section of Y = 1.1 m height), and D represents the distance from the sampling point to the air supply outlet. Some of the data are illustrated in Table 2.Table 2
Indoor parameters.
Code
Indoor temperatureT (°C)
Current SpeedV  (m/s)
DistanceD (m)
Radiant temperatureTr (°C)
Relative humidityw (%)
PMV
PPD
Age of air(s)
1
22.98
0.26
2.21
20.32
49.93
-
0.84
20.04
128.97
2
23.01
0.32
2.33
20.18
50.19
-
0.95
24.06
122.98
3
22.38
0
2.51
21.14
51.05
-
0.38
8.07
137.11
4
23.14
0.16
2.60
20.43
51.38
-
0.60
12.67
137.37
5
22.71
0.22
2.76
20.28
51.29
-
0.79
18.30
124.19
⋯
⋯
⋯
⋯
⋯
⋯
⋯
⋯
⋯
997
22.63
0.22
6.50
21.62
53.91
-
0.41
8.59
189.68
998
24.92
0.12
7.81
22.72
56.06
-
0.10
7.12
186.41
999
24.91
0.09
8.62
20.76
57.48
-
0.13
5.38
137.34
1000
24.15
0
8.82
22.47
53.23
0.01
5.00
161.24The distributions of indoor thermal comfort indicators PMV, PPD, and mean age of air were obtained with a postprocessing software and are shown in Figures2–4, respectively.Figure 2
Distribution of PMV.Figure 3
Distribution of PPD.Figure 4
Distribution of the mean air age.The smallest values of PMV were around −1.5 in the seat near the air supply outlet of the air conditioner, as depicted in Figure2. The largest PMV values were about 0.6 in the upper left corner of Figure 2. With regard to people’s comfort, the values of PMV were between −1.5 and −1 in the seat near the air supply outlet, and people in this indoor setting have an obvious feeling of coldness. The values of PMV were between −0.5 and 0.5 in the seat near the return air vent, and people here have a feeling of “moderate” hotness and coldness. In the middle seats of the room, the values of PMV were between −1 and 0.2, and the feeling of thermal discomfort was obvious. Overall, the distribution of PMV values was uneven. The farther a location was from the air supply outlet, the greater the values of PMV were. The largest difference in the distribution of PMV values was obtained in the middle seats.As shown in Figure3, the largest values of PPD were around 80% in the seat near the air supply outlet of the air conditioner. The smallest PPD values were about 10% in the upper left corner of Figure 3. In terms of the degree of people’s satisfaction, the distribution of PPD values was uneven around the seat near the air supply outlet. The PPD values in the lower right corner of Figure 3 range from 50% to 75. Several indoor persons exhibited symptoms of maladjustment, and the rate of dissatisfaction was high. The PPD values were between 10% and 15% (upper right corner of Figure 3), which means that most indoor persons felt good and were highly satisfied with the environment. The PPD values were between 15% and 25% in the seat near the return air vent; most persons felt generally satisfied. The PPD values were around 10% in the upper left corner of Figure 3, which indicates that the persons indoors were highly satisfied with the environment. The PPD values were between 10% and 20% in the middle seats of the room, and people here felt generally satisfied with the environment. In sum, the distribution of PPD values was uneven. In the seat near the air supply outlet, people demonstrated highest satisfaction with the environment, as shown in the upper left corner of Figure 3 where the PPD values are the largest; this location did not meet people’s requirements for a thermally comfortable environment. The PPD values ranged from 10% to 15% in the middle part of the room, and these values produced satisfactory thermal sensations.The distribution of the mean age of air in the room is presented in Figure4. The values of air age were between 20 and 60 s in the seat near the air supply outlet of the air conditioner. The values of air age are 220 s in the upper left corner of Figure 4 and are the largest values of air age. The analysis of the people’s feelings toward the freshness degree of indoor air showed that people felt more comfortable with the air flow in the seat near the air supply outlet of the air conditioner. In the seat near the return air vent, the values of mean air age were around 220 s, which indicate poor air circulation. The distribution of the mean age of air values was between 60 and 180 s in the middle seats of the room; here, people felt good air circulation. The greater the distance is from the air supply outlet to people, the greater the values of air age are. Overall, the whole tendency is gradually increasing.As described in Table2 and Figures 2–4, when the air supply outlet was arranged in accordance with the model above, the comfort requirements were not met. The distribution of the values of PMV, PPD, and age of air was uneven. The PPD values (Figure 3) were higher than the recommended upper limit (10%) in space, which illustrated that people normally felt uncomfortable with the thermal environment. Therefore, optimizing the control parameters of the indoor air condition is necessary.


## 3.2. ANFIS Modeling

Both fuzzy logic and ANN were utilized in the architecture of ANFIS. ANFIS consisted of if-then rules and input-output pairs. ANFIS training was used to learn the algorithms of the neural network [34]. For simplicity, we assumed that the fuzzy inference system has five inputs (x1,x2,x3,x4,andx5) and one output (f) under consideration. A typical rule set with base fuzzy if-then rules for a first-order Sugeno fuzzy model is presented in Figure 5.Figure 5
Block diagram of ANFIS used in this study.The network structure consisted of three layers, namely, input, hidden, and output. The output data were PMV, PPD, and mean age of air. The number of neurons of the first hidden layer was 10, and that in the second one was 32. One thousand sets of input and output data were trained. The principles of the system are as follows.The fuzzy rule according to Takagi–Sugeno is the linear combination of input variables.Rj: if x1 is A1j and x2 is A2j… and xn is Anj,then yj=pj0+pj1x1+···+pjnxn, where j=1,2,…,m, m≤∏i=1nmi.For a given inputx, the degree of adaptation to each rule can be obtained by using the fuzzy method of the single-point fuzzy set as follows:(2)αj=μA1jx1μA2jx2···μAnjxn,where α¯j=αj/∑i=1mαi.The architecture of the ANFIS used in this study is shown in Figure5. The ANFIS architecture has five inputs and one output. This architecture is formed by using 5 layers and 75 if-then rules as follows.Layer 1. Every node in this layer represents a linguistic variable with a node function as(3)μij=μAijxi,where i=1,2,…,n,j=1,2,…,mi and N is the dimension of the input quantity. mi is the fuzzy partition number of xi. n=5 and mi=3, such that(4)μij=exp-xi-cijσij2,where cij and σij comprise the parameter set and are referred to as premise parameters.Layer 2. Each node in this layer is a circular node represented by II and multiplies the incoming signals and then sends the product out. For instance,(5)αj=μ1i1μ2i2···μnin,where i1∈1,2,…,m1,i2∈1,2,…,m2,…,in∈1,2,…,mn,j=1,2,…,m,m=∏i=1nmi.Layer 3. Every node in this layer is a circular node expressed by N. The itch node calculates the ratio of the itch rules’ firing strength to the sum of all rules’ firing strengths as follows:(6)α¯j=αj∑i=1mαi.Layer 4. Each nodei in this layer is a square node with node function:(7)yij=pj0i+pj1ix1+···+pjnixn=∑l=0npjixlj=1,2,…,m;i=1,2,…,r.Layer 5. The single node in this layer is a circular node shown by P that calculates the overall output as the summation of all incoming signals as follows:(8)yi=∑j=1mα¯jyij.


## 3.3. Results and Discussion

In this study, ANFIS method was used to predict the temperature and flow field in a laboratory. The flow field showed good agreement between CFD and ANFIS results. Additionally, the difference between the values of the stream function of ANFIS and CFD was extremely small. Comparison of the calculated values with the predicted values showed that the mean variance and mean absolute error of the PMV indicator were3.89×10-5 and 0.012, respectively. The mean variance and mean absolute error of the PPD indicator were 6.23×10-5 and 0.89, respectively. The mean variance and mean absolute error of the mean age of air indicator were 8.26×10-3 and 0.15, respectively. Almost similar values of minimum and maximum stream functions in the CFD results were obtained. The fitting curves of the calculated and predicted values are shown in Figures 6–8.Figure 6
Fitting curve of PMV.Figure 7
Fitting curve of PPD.Figure 8
Fitting curve of the mean age of air.Figures6–8 and the error analysis showed that the calculated CFD values of PMV, PPD, and the mean age of air were in agreement with the predicted values of ANFIS. Furthermore, the error was very small. The average convergence time was 15 min. Therefore, the model established by ANFIS has high precision and good coincidence and could be a good substitute for the CFD model.


## 4. Improved PSO Algorithm

### 4.1. Objective Function

The main idea behind the stratified sequence method is to sort the multiobjective function according to the level of importance and then obtain the optimal solution of each single objective function. Notably, the aim of the next solution is to search within the optimal solution set obtained from the last time in the process of solving the stratified sequence method. To guarantee the existence of feasible solutions in the next solving process, the tolerance stratification sequence method is applied to broaden the feasible region by means of a tolerance value; namely, the function searches within a certain range near the optimal solution obtained in the last time, rather than being strictly restricted to the last set of optimal solutions. The specific implementation of the tolerance stratification sequence method is defined as follows.We assume that[f1(x),f2(x),…,fp(x)] is a multiple objective function sorted in accordance with the degree of importance. The first objective function f1(x) is solved as follows:(9)minf1xs.t.x∈S.The optimal target valuef1∗ from the first objective function is added with a tolerance value ε1, which is used to optimize the second objective functionf2(x) in the broadened field of the optimal solution set. We let S1=x∣f1≤f1∗+ε1∩S. The first objective function is transformed into the constraint condition(10)minf2xs.t.x∈S1.Likewise(11)minfpxs.t.x∈Sp-1.Therefore, Sp=x∣fp(x)≤fp∗+εp∩Sp-1 is a set of optimal solutions in the sense of the hierarchical sequence. The tolerance stratification sequence method is introduced into the multiobjective optimization model of cutting parameters. Not only does the linear weighting method avoid determining the weight of the difficulty, but it also adds a degree of freedom in the design of the tolerance value, such that the optimization process becomes more in line with the actual production requirements. In this study, the values of PMV, PPD, and mean age of air were utilized to measure indoor thermal comfort and air quality. Thus, the objective function of PSO can be defined as(12)minfpx=GjxGjxmaxs.t.aij≤xij≤biji=1,2,3,4,5;j=1,2,3;p=1,2,3,where Gj(x) is the output; subscript j pertains to different outputs that are the numerical values of PMV, PPD, and mean age of air; xij is the input of the neural network; subscript i pertains to different outputs; aij and bij represent the upper and lower bounds of the input variables, respectively; and the inputs are T,V,Tr,D, and w. We let ε1=1/3·maxi-mini and ε2=1/3·ε1.


### 4.2. Optimization

Kennedy and Eberhart (1995) introduced PSO in 1995 [35]. PSO mimics the social behavior of bird flocks or fish schools. Each time, each particle in the swarm flies to its next position at a specific speed by relying on its achieved best position and the global best position reached by any particle in the swarm. The flowchart of the PSO algorithm is illustrated in Figure 9, and the update rule of particle positions in every iteration is shown in the following two equations:(13)vidk+1=wvidk+c1rand1kpbestidk-xidk+c2rand2kgbestidk-xidk,xidk+1=xidk+1+Krand-Kvidk+1+10-6rand,where w is called inertia weight and is introduced to speed up the convergence of PSO; it usually has a value between (0,1). vidk represents the velocity of particles. k is the iteration number, which ranges within (1:kmax). i is the particle number, which ranges within (1:M). d is the dimension number, which ranges within (1:D). rand1 and rand2 are random numbers between (0,1), and c1 and c2 are called accelerating coefficients. Usually, c1=c2=2. xidk is introduced to store the current positions of every dimension of all particles. pbest (particle best) is a matrix with the same size as x that stores the best position every particle reached from iteration (1: t-1). gbest (global best) with size (1,D) stores the best N-dimensional positions that give the best score by any particle from iterations (1:t-1).Figure 9
Flowchart of the PSO algorithm.In this study, adaptive variation of inertia weight was employed. With the increase in the number of iterations, the inertia weight decreases, and the accuracy of the algorithm improves. The specific change formula is as follows:(14)w=wmax-iter·wmax-wminitermax,where wmax and wmin are the maximum and minimum inertia weights, respectively; iter is the current particle number of iterations; and itermax is the maximum number of iterations for the PSO algorithm.The air supply parameters after optimization are illustrated in Table3.Table 3
Three different evaluation indicators to achieve optimal air conditioning parameters.
Evaluation indicators
Velocity (m/s)
Temperature (°C)
Relative humidity (%)
Distance (m)
PMV
0.42
23.48
49.39
5.70
PPD
0.42
21.69
58.48
4.20
Mean age of air
0.43
19.87
63.19
3.60


## 4.1. Objective Function

The main idea behind the stratified sequence method is to sort the multiobjective function according to the level of importance and then obtain the optimal solution of each single objective function. Notably, the aim of the next solution is to search within the optimal solution set obtained from the last time in the process of solving the stratified sequence method. To guarantee the existence of feasible solutions in the next solving process, the tolerance stratification sequence method is applied to broaden the feasible region by means of a tolerance value; namely, the function searches within a certain range near the optimal solution obtained in the last time, rather than being strictly restricted to the last set of optimal solutions. The specific implementation of the tolerance stratification sequence method is defined as follows.We assume that[f1(x),f2(x),…,fp(x)] is a multiple objective function sorted in accordance with the degree of importance. The first objective function f1(x) is solved as follows:(9)minf1xs.t.x∈S.The optimal target valuef1∗ from the first objective function is added with a tolerance value ε1, which is used to optimize the second objective functionf2(x) in the broadened field of the optimal solution set. We let S1=x∣f1≤f1∗+ε1∩S. The first objective function is transformed into the constraint condition(10)minf2xs.t.x∈S1.Likewise(11)minfpxs.t.x∈Sp-1.Therefore, Sp=x∣fp(x)≤fp∗+εp∩Sp-1 is a set of optimal solutions in the sense of the hierarchical sequence. The tolerance stratification sequence method is introduced into the multiobjective optimization model of cutting parameters. Not only does the linear weighting method avoid determining the weight of the difficulty, but it also adds a degree of freedom in the design of the tolerance value, such that the optimization process becomes more in line with the actual production requirements. In this study, the values of PMV, PPD, and mean age of air were utilized to measure indoor thermal comfort and air quality. Thus, the objective function of PSO can be defined as(12)minfpx=GjxGjxmaxs.t.aij≤xij≤biji=1,2,3,4,5;j=1,2,3;p=1,2,3,where Gj(x) is the output; subscript j pertains to different outputs that are the numerical values of PMV, PPD, and mean age of air; xij is the input of the neural network; subscript i pertains to different outputs; aij and bij represent the upper and lower bounds of the input variables, respectively; and the inputs are T,V,Tr,D, and w. We let ε1=1/3·maxi-mini and ε2=1/3·ε1.


## 4.2. Optimization

Kennedy and Eberhart (1995) introduced PSO in 1995 [35]. PSO mimics the social behavior of bird flocks or fish schools. Each time, each particle in the swarm flies to its next position at a specific speed by relying on its achieved best position and the global best position reached by any particle in the swarm. The flowchart of the PSO algorithm is illustrated in Figure 9, and the update rule of particle positions in every iteration is shown in the following two equations:(13)vidk+1=wvidk+c1rand1kpbestidk-xidk+c2rand2kgbestidk-xidk,xidk+1=xidk+1+Krand-Kvidk+1+10-6rand,where w is called inertia weight and is introduced to speed up the convergence of PSO; it usually has a value between (0,1). vidk represents the velocity of particles. k is the iteration number, which ranges within (1:kmax). i is the particle number, which ranges within (1:M). d is the dimension number, which ranges within (1:D). rand1 and rand2 are random numbers between (0,1), and c1 and c2 are called accelerating coefficients. Usually, c1=c2=2. xidk is introduced to store the current positions of every dimension of all particles. pbest (particle best) is a matrix with the same size as x that stores the best position every particle reached from iteration (1: t-1). gbest (global best) with size (1,D) stores the best N-dimensional positions that give the best score by any particle from iterations (1:t-1).Figure 9
Flowchart of the PSO algorithm.In this study, adaptive variation of inertia weight was employed. With the increase in the number of iterations, the inertia weight decreases, and the accuracy of the algorithm improves. The specific change formula is as follows:(14)w=wmax-iter·wmax-wminitermax,where wmax and wmin are the maximum and minimum inertia weights, respectively; iter is the current particle number of iterations; and itermax is the maximum number of iterations for the PSO algorithm.The air supply parameters after optimization are illustrated in Table3.Table 3
Three different evaluation indicators to achieve optimal air conditioning parameters.
Evaluation indicators
Velocity (m/s)
Temperature (°C)
Relative humidity (%)
Distance (m)
PMV
0.42
23.48
49.39
5.70
PPD
0.42
21.69
58.48
4.20
Mean age of air
0.43
19.87
63.19
3.60


## 5. Layout Design of the Air Conditioner and Analysis of Simulation Results

### 5.1. Layout Design of the Air Conditioner

According to the optimized parameters, the optimal distance from the seats to the air supply outlet is 3.6 m. Thus, the following method was adopted to determine the size and location of the air conditioner. First, the structure of the air supply was set to the shape of a cube, as shown in Figure11. Second, the sphere centers Ri(i=1,2,…,14) were set to the height of the human chest (XZ section of Y = 1.1 m height). Third, a hemisphere with the radius of 3.6 m was drawn, and the location and size of the air conditioner were defined at the intersection of adjacent hemispheres. The location of the air conditioner is shown in Figure 10. The final size of the air conditioner was 1.2 m × 1.2 m × 0.5 m (length × width × height).Figure 10
Location of the air conditioner.Figure 11
Optimized physical model.


### 5.2. Analysis of CFD Simulation

The optimized results showed that the air supply’s position in the model needs to be rearranged. The top distribution of the four cube air supply outlets was adopted in place of the original one. Then, the optimal distance from each air supply outlet to the surrounding seats and the optimized indoor control parameters were employed. For example, the temperature of the air supply outlet of the air conditioner was 19.67°C, indoor relative humidity was adjusted to 63.19%, and the air velocity was 0.43 m/s. The redesigned distribution of the indoor air conditioning is shown in Figure11, and the distribution of PMV, PPD, and mean age of air was obtained when the indoor condition was stabilized, as presented in Figures 12–14.Figure 12
Distribution of the optimized PMV values.Figure 13
Distribution of the optimized PPD values.Figure 14
Distribution of the optimized values of air age.The distribution of the PMV values was even, as depicted in Figure12. In this condition, people normally experience thermal comfort. When the PMV values ranged from −0.5 to 0, the evaluation of thermal comfort was “moderate.” In the seat near the return air vent, the PMV values were around −1.5, and the evaluation of thermal comfort was “slightly cold.” In short, when the evaluation of the indoor environment’s comfort is “moderate,” people experience good thermal comfort. Compared with that in Figure 2, the optimized value of PMV is 0 near the seats around people, which represents a “moderate” feeling of comfort.The distribution of the PPD values was even, as shown in Figure13. In this condition, people normally have a satisfactory sense of thermal comfort because the PPD values are about 10%. In the seat near the return air vent, the PPD values were between 30% and 55%, which shows that the evaluation of thermal comfort is rather low. Overall, people are satisfied with the thermal environment. Compared with those in Figure 3, the optimized values of PPD are about 10%, which means that the satisfaction degree of people is high.The values of air age in the room ranged from 50 to 95 s, and the distribution was balanced as shown in Figure14. The values of air age were between 50 and 70 s, which shows that the effect of ventilation was good. Compared with those in Figure 4, the values of air age inside the room were smaller, and air circulation was better.Overall, as the distribution of PMV, PPD, and air age becomes increasingly balanced, the feeling of thermal comfort and the satisfaction degree of persons indoors obviously improve. The optimized values of air age were smaller than those before, and indoor air circulation was enhanced. Compared with the original data and contour images, we conclude that the optimized indoor air quality was significantly enhanced, and people in the laboratory can enjoy a comfortable environment, which in turn can improve their learning efficiency. Compared with the local air supply structure in the study of Skovgaard and Nielsen [8], the structure of air supply in the current study has a shape of a cube, and the values of PMV range from −0.5 to 0 with an even distribution near the seats. The evaluation of thermal comfort in the room is “moderate.” Compared with structure of the upper air supply and downside air outlet of the air conditioning system employed by Riederer et al. [9], the structure in the present work can provide improved ventilation with the values of air age ranging from 50 to 70 s.


### 5.3. Validation of Optimal Solutions

Based on the above optimization work, the method of combining ANFIS with PSO was applied to verify the accuracy and preponderance of the optimal solutions. For validation purposes, we first used the office model obtained by Xu et al. [28] to simulate the indoor thermal environment via CFD. Second, the approach of ANFIS-PSO was used to optimize the indoor control variables. Finally, the index of thermal comfort obtained by the present work was compared with the experimental data obtained by Xu et al. [28].The control variables after optimization are illustrated in Table4.Table 4
Comparison of the optimal variables in the present work with those in Xu et al. [28].
Controlvariables
Velocity(m/s)
Temperature(°C)
Relative humidity(%)
Distance(m)
Present work
0.42
23
63
3.2
Xu et al. [28]
0.26
22
67
2.9In the present study, several samples were obtained after the indoor climate condition stabilized. Figure15 shows that the temperature ranged between 26°C and 27.3°C. The indoor thermal parameters in the office were in rough agreement with the experimental data obtained by Xu et al. [28] shown in Figure 15. Furthermore, compared with the optimal results of Xu et al. [28], the thermal state of the office is improved, and the distribution of temperature in corners is more uniform (Figure 16).Figure 15
Comparisons ofT,V, and relative humidity between the method of ANFIS-PSO and that in Xu et al. [28].
(a)
Comparison of temperature
(b)
Comparison of velocity
(c)
Comparison of relative humidityFigure 16
Comparison of the index of PMV between the method of ANFIS-PSO and that in Xu et al. [28].Accordingly, we conclude that the presented numerical procedure is a reliable method of predicting the flow and heat transfer in an air-conditioned room.


## 5.1. Layout Design of the Air Conditioner

According to the optimized parameters, the optimal distance from the seats to the air supply outlet is 3.6 m. Thus, the following method was adopted to determine the size and location of the air conditioner. First, the structure of the air supply was set to the shape of a cube, as shown in Figure11. Second, the sphere centers Ri(i=1,2,…,14) were set to the height of the human chest (XZ section of Y = 1.1 m height). Third, a hemisphere with the radius of 3.6 m was drawn, and the location and size of the air conditioner were defined at the intersection of adjacent hemispheres. The location of the air conditioner is shown in Figure 10. The final size of the air conditioner was 1.2 m × 1.2 m × 0.5 m (length × width × height).Figure 10
Location of the air conditioner.Figure 11
Optimized physical model.


## 5.2. Analysis of CFD Simulation

The optimized results showed that the air supply’s position in the model needs to be rearranged. The top distribution of the four cube air supply outlets was adopted in place of the original one. Then, the optimal distance from each air supply outlet to the surrounding seats and the optimized indoor control parameters were employed. For example, the temperature of the air supply outlet of the air conditioner was 19.67°C, indoor relative humidity was adjusted to 63.19%, and the air velocity was 0.43 m/s. The redesigned distribution of the indoor air conditioning is shown in Figure11, and the distribution of PMV, PPD, and mean age of air was obtained when the indoor condition was stabilized, as presented in Figures 12–14.Figure 12
Distribution of the optimized PMV values.Figure 13
Distribution of the optimized PPD values.Figure 14
Distribution of the optimized values of air age.The distribution of the PMV values was even, as depicted in Figure12. In this condition, people normally experience thermal comfort. When the PMV values ranged from −0.5 to 0, the evaluation of thermal comfort was “moderate.” In the seat near the return air vent, the PMV values were around −1.5, and the evaluation of thermal comfort was “slightly cold.” In short, when the evaluation of the indoor environment’s comfort is “moderate,” people experience good thermal comfort. Compared with that in Figure 2, the optimized value of PMV is 0 near the seats around people, which represents a “moderate” feeling of comfort.The distribution of the PPD values was even, as shown in Figure13. In this condition, people normally have a satisfactory sense of thermal comfort because the PPD values are about 10%. In the seat near the return air vent, the PPD values were between 30% and 55%, which shows that the evaluation of thermal comfort is rather low. Overall, people are satisfied with the thermal environment. Compared with those in Figure 3, the optimized values of PPD are about 10%, which means that the satisfaction degree of people is high.The values of air age in the room ranged from 50 to 95 s, and the distribution was balanced as shown in Figure14. The values of air age were between 50 and 70 s, which shows that the effect of ventilation was good. Compared with those in Figure 4, the values of air age inside the room were smaller, and air circulation was better.Overall, as the distribution of PMV, PPD, and air age becomes increasingly balanced, the feeling of thermal comfort and the satisfaction degree of persons indoors obviously improve. The optimized values of air age were smaller than those before, and indoor air circulation was enhanced. Compared with the original data and contour images, we conclude that the optimized indoor air quality was significantly enhanced, and people in the laboratory can enjoy a comfortable environment, which in turn can improve their learning efficiency. Compared with the local air supply structure in the study of Skovgaard and Nielsen [8], the structure of air supply in the current study has a shape of a cube, and the values of PMV range from −0.5 to 0 with an even distribution near the seats. The evaluation of thermal comfort in the room is “moderate.” Compared with structure of the upper air supply and downside air outlet of the air conditioning system employed by Riederer et al. [9], the structure in the present work can provide improved ventilation with the values of air age ranging from 50 to 70 s.


## 5.3. Validation of Optimal Solutions

Based on the above optimization work, the method of combining ANFIS with PSO was applied to verify the accuracy and preponderance of the optimal solutions. For validation purposes, we first used the office model obtained by Xu et al. [28] to simulate the indoor thermal environment via CFD. Second, the approach of ANFIS-PSO was used to optimize the indoor control variables. Finally, the index of thermal comfort obtained by the present work was compared with the experimental data obtained by Xu et al. [28].The control variables after optimization are illustrated in Table4.Table 4
Comparison of the optimal variables in the present work with those in Xu et al. [28].
Controlvariables
Velocity(m/s)
Temperature(°C)
Relative humidity(%)
Distance(m)
Present work
0.42
23
63
3.2
Xu et al. [28]
0.26
22
67
2.9In the present study, several samples were obtained after the indoor climate condition stabilized. Figure15 shows that the temperature ranged between 26°C and 27.3°C. The indoor thermal parameters in the office were in rough agreement with the experimental data obtained by Xu et al. [28] shown in Figure 15. Furthermore, compared with the optimal results of Xu et al. [28], the thermal state of the office is improved, and the distribution of temperature in corners is more uniform (Figure 16).Figure 15
Comparisons ofT,V, and relative humidity between the method of ANFIS-PSO and that in Xu et al. [28].
(a)
Comparison of temperature
(b)
Comparison of velocity
(c)
Comparison of relative humidityFigure 16
Comparison of the index of PMV between the method of ANFIS-PSO and that in Xu et al. [28].Accordingly, we conclude that the presented numerical procedure is a reliable method of predicting the flow and heat transfer in an air-conditioned room.


## 6. Conclusions

In this study, ANFIS modeling and the improved PSO algorithm were combined to improve indoor thermal comfort parameters. The following conclusions were obtained.(
1
) The proposed methodology is an integrated ANFIS-PSO approach developed to optimize air conditioner design in terms of thermal comfort and indoor air quality. The advantage of this integration relies on the reliability of the prediction of indoor thermal and environmental conditions provided by the CFD model. Effect evaluation of the ANFIS model indicated that the ANFIS model can exactly describe the relationship between indoor thermal comfort indicators (PMV, PPD, and age of air) and several factors pertaining to air conditioning (air temperature, relative humidity, indoor radiation temperature, air velocity, and distance from the air supply outlet to people). The ANFIS model can optimize the mathematical model, and the convergence time is about 40 min. Hence, the ANFIS model can replace the CFD model, whose convergence time reaches 12 h. The former can significantly increase the convergence speed under the premise of ensuring accuracy.(
2
) With the improved PSO algorithm and the stratified sequence method, thermal comfort indicators PMV, PPD, and age of air were optimized layer by layer to obtain the optimal air conditioning parameters and installation distance. For example, air temperature was 19.87°C, air velocity was 0.43 m/s, and the optimal distance from the air supply outlet to people was 3.60 m.(
3
) The air conditioning arrangement of the cube air supply mode can be utilized to solve the problems of high temperature and poor ventilation in the local area. The distribution of PMV in the room was optimized from −1.5 to 1.5 to −0.5 to 0. The PPD values were optimized from 60% to 80% to about 10% and the age of air from 60 s to 120 s to 50 s to 70 s. The optimized results showed that the level of thermal comfort was “moderate,” and the effectiveness of ventilation was good. This condition means that people are highly satisfied with the indoor thermal environment.This study focused only on one room in the university, and several factors, such as noise and pollution, were not examined. In the future, other factors should be considered through experimentation.



---

*Source: 3075432-2017-03-22.xml*