# Independent Control of Temperature and Humidity in Air Conditioners by Using Fuzzy Sliding Mode Approach

Authors: Lijian Yang; Ziyang Li; Zhengtian Wu; Mingyang Xie; Baoping Jiang; Baochuan Fu
Journal: Complexity
 (2020)

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## Abstract

This paper proposes a sliding mode control (SMC) strategy to solve the problem of independent control of temperature and humidity in air conditioners; the complexity increases due to the need to make full use of the wind side for cooling. First, dynamics of indoor temperature and humidity are determined based on mathematical models. Second, in order to reduce the chattering effect of SMC and coordinate indoor conditions to satisfy people’s needs, the independent control of temperature and humidity is realized via a novel fuzzy sliding mode control strategy based on reaching laws. Finally, simulation results are provided to verify the effectiveness of the proposed method.


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## Body

## 1. Introduction

In traditional central air-conditioning control systems, temperature is typically the controlled parameter and multiloop PID control method is commonly adopted. However, achieving desired control performance is difficult with the aid of traditional PID controllers due to a variety of reasons, for instance, nonlinearity and time-varying effects in temperature variation and complexity in establishing mathematical models [1]. In addition to the complexity of parameter setting methods, conventional PID controller parameters often have poor system performance and poor adaptability to the controlled process. Therefore, ordinary PID control is difficult to meet the control requirements in the central air-conditioning system.Compared with the conventional air-conditioning system, the temperature- and humidity-independent control system uses high-temperature cold source, solution humidity control, and other technologies to ensure energy saving. Lazzarin and Castellotti studied a self-regenerating solution dehumidification system driven by a heat pump, which was applied to supermarket to verify its energy efficiency by simulating year-round outdoor working conditions [2]. Hao designed a cooling radiant roof, rotary dehumidification, and displacement ventilation air conditioner system. The system can effectively save electrical energy, significantly improve the indoor environment quality, and increase comfort [3]. Although the advantages of independent temperature and humidity controlled air-conditioning systems are obvious, there are still some problems in the actual operation process. For example, if the temperature- and humidity-independent control system needs to make full use of the free cooling on the wind side during the transition season, the exhaust fan needs to be configured, which increases the complexity of the system [4]. Compared with traditional air-conditioning systems, the installation of temperature- and humidity-independent control air-conditioning is more stringent, complicated, and costly.During air-conditioning control, the fuzzy control strategy is more efficient than the PID control because the former can adjust the room temperature under partial load operation and flow rate of cooling water in cooling coil shows satisfactory oscillation response; however, given that the fuzzy approach lacks systemicity, the disadvantages of using fuzzy control method alone in air-conditioning systems are instability and poor robustness in the fuzzy process [5, 6]. In [7–9], a genetic algorithm-based PID controller and self-tuning PID-type fuzzy adaptive controller were designed to simulate the temperature of central air-conditioning systems. These two methods can meet the needs of central air-conditioning temperature control system; the experimental results show that the cooling effect is better. For the problem of parameter/structure uncertainty and input dead zone of nonlinear system, an adaptive control method based on neural network is designed to ensure the stability and robustness of the system [10, 11]. The articles [12–15] study the feedback control problem of stochastic nonlinear systems and have made a lot of contributions to the backstepping between controllers and the system stability proof. In order to compensate the interference or unmeasured state of the system, the articles [16, 17] give a new form of reduced-order K-filters. These control methods and anti-interference methods are also applicable to air-conditioning systems with large lags and numerous interference.Sliding mode control (SMC) was proposed by Emelyanov et al. in the 1950s. Itkin et al. subsequently summarized and developed SMC theory [18]. Later, sliding mode control was widely used in robotics and aviation [19]. Given that the sliding motion is designed to be independent of system parameters and disturbances, therefore, SMC models have the good properties of strong robustness, fast response, and easy implementation. These characteristics can be optimized in the central air-conditioning system and compensate for the shortcomings of conventional PID controllers. In addition, it has witnessed many researches in the related field; for example, a class of discrete-time interval type-2 fuzzy systems were studied in [20]. In [21], the problem of sliding mode control for semi-Markov switching systems with quantized measurement in finite-time level was investigated. When system state trajectory reached the sliding mode surface, the exclusive occurrence of sliding motion on the sliding surface toward the equilibrium point is impossible due to switching signals. Several studies have shown that the fuzzy SMC can suppress chattering effect by linearizing discontinuous signals. The fuzzy sliding mode approach reduces the influence of switching control and remarkably reduces the chattering effect [22]. In terms of application, the fuzzy SMC approach was applied to stochastic systems with (semi)Markov switching parameters which have been developed in [23–25]. In [26, 27], the fuzzy SMC was proposed for nonlinear descriptor systems. Therefore, this paper proposes fuzzy rules in the design of sliding mode parameters and reduction of chattering phenomenon of SMC to ensure the accurate control of indoor temperature and humidity.Different from the traditional control method, the robust and fast response characteristics of the fuzzy sliding mode control adopted in this paper are more suitable for the air-conditioning system with large lags and numerous interference. Meanwhile, the contribution of this study is to propose fuzzy rules in the design of sliding mode controller for independent control of indoor temperature and humidity to solve the problem of increased complexity due to the configuration of the exhaust fan. Compared with the conventional PID control and fuzzy PID control methods, the proposed fuzzy SMC strategy achieves faster adjustment response, smaller overshoot, higher accuracy, and better control effect. At the same time, it ensures that the indoor carbon dioxide concentration is at a normal level. However, this air-conditioning system is mainly suitable for the case where the room model data is known. The design method of the stochastic delay feedback control and the stability controller for the discrete-time half-Markov jump linear system with bounded residence time used in [28–30] will be of a great help for the future work of expanding to random cases.


## 2. Mathematical Modeling of Indoor Environment

The independent control of temperature and humidity in the air-conditioning system adjusts the volume of fresh air supply of the dehumidification system and the volume of return air supply of the temperature control system to meet people’s requirements for indoor environment comfort [31]. The system is illustrated in Figure 1.Figure 1
Air-conditioning system diagram.This study considers an office building environment with the following assumptions [32]: (1) the office building is considered as a closed-loop system. (2) The air pressure in the building remains unchanged. (3) The indoor air diffusion is good and the room temperature can be measured using a temperature sensor. (4) The effect of humidity on room temperature is unclear.


### 2.1. Dynamic Response of Temperature

Given that the independent control of temperature and humidity in the air-conditioning system uses fresh air in the dehumidification system to remove indoor residual humidity, CO2, and odors such that to ensure indoor air quality, the dynamic response modeling of room temperature must only consider the room’s sensible heat [33].The heat energy balance in an air-conditioning system is expressed as follows [34, 35]:(1)Q˙st=Qrt+Qwt−Qdt,where Qrt is the heat provided by the air-conditioning supply air; Qst is the sensible heat; Qdt is the outflow heat; and Qwt is the heat dissipation.The room sensible heat change can be described as follows [28]:(2)Q˙st=ρVC1Ti,where ρ is the indoor air density,kg/m3; V is the room volume, m3; C1 is the specific heat capacity of indoor air, J/(Kg ∗ K); and Ti is the room temperature.The relationship between the sensible heat provided by the air-conditioning system to the room and the air output can be expressed as follows [28]:(3)Qrt=ρC1GstTst,where Gst is the volume of air supplied,m3, and Tst is the air temperature of the sensible heat dry fan coil, °C.For rooms that use temperature and humidity as variables to control the air-conditioning system independently, the main factors that affect the indoor temperature response are listed as follows: sensible heat flowing out of the room and heat dissipation of the room [36]. Heat dissipation of the room includes the following parts: (1) instantaneous sensible cooling load due to the indoor and outdoor temperature difference and direct heat dissipation from the indoor heat source. (2) Heat dissipation caused by the radiation of sunlight through the window.Heat dissipation of the roomQwt is expressed as follows [37]:(4)Qwt=FλδTot−Tit+αiTot−Tit+σ,where F is the wall area,m2; λ is the thermal conductivity of the wall material layer; δ is the thickness of the wall material layer, m; To is the outdoor ambient temperature; αi is the heat transfer coefficient of composite heat transfer surface of the inner wall of the glass window; and σ is the heat generated by the solar radiation of the glass window in the room.The sensible heat flowing out of the room is primarily the heat taken away by return air. Given that the office building is assumed to be a closed-loop system, the return air volume can be calculated according to the supply air volume of the temperature control system as follows [29]:(5)Qdt=ρC1GstTit.Substituting (2)–(5) into (1), (6)ρVC1Ti⋅=ρC1GstTst+FλδTot−Tit+αiTot−Tit+σ−ρC1GstTit.


### 2.2. Dynamic Response of Humidity

The dehumidification system of the air conditioner with independent control of temperature and humidity adopts the full fresh air system. The humidity control system bears all the latent heat load of the building by sending dry fresh air with moisture content lower than the interior designed state. Under the assumptions that the office building is a closed-loop system and the pressure in the building remains unchanged, mass conservation of air humidity can be calculated as follows [38]:(7)Mndn⋅t=Gotdst−dnt+Wht,where Mn is the total mass of air in the building, g; dnt is the moisture content of the air in the building, g/kg; dst is the moisture content of the air supply of the air conditioner, g/kg; Got is the exhaust volume of the dehumidification system, g/h; and Wht is the indoor humidity load, g/h.Hence, determining the total indoor wet loadWh is important. The building’s moisture production primarily comes from people indoors, water surface, plants, and the amount of moisture from infiltrating air [39]. Given that this paper considers an office place, the main indoor moisture load involves the number of people that dissipates moisture and the amount of moisture dissipated by fresh air penetration [40].The wet load of personnel in the office building based on the adults is calculated as follows [32]:(8)Wt1t=0.278n∅g∗10−6,where n is the number of indoor personnel, ∅ is the personnel cluster coefficient, and g is the amount of moisture dissipated by the adults, g/h.Conventional air-conditioning systems only considered the wet load caused by fresh air penetration in winter but ignored the insignificant wet load generated by fresh air penetration in summer. By comparison, dry air is responsible for dehumidification in air-conditioning systems with independent temperature and humidity control although its dehumidification capacity is limited. Therefore, large humidity load caused by outdoor fresh air penetration must be considered. The wet load due to fresh air penetration can be calculated as follows [33]:(9)Wt2t=Lρdot−dnt,where L is the infiltration air volumem3 and do is the outdoor air moisture content.Substituting (8) and (9) into (7) leads to(10)Mndn⋅t=Gotdst−dnt+0.278n∅g∗10−6+Lρdot−dnt.


### 2.3. Estimate of IndoorCO2 Concentration

The latent heat control system in the air conditioner with independent control of temperature and humidity uses full fresh air input to ensure that the predicted air concentration in the office space will remain fresh. The relationship between the indoor concentration and the air volume of the air conditioner in the absence of people is expressed as follows:(11)VC˙=CoutVvt+Qp−Vvt+LC,where C is the indoor CO2 concentration; Qp is the pollutant emission rate; and Vv is the room mechanical ventilation m3/h. Given that the room is considered a closed-loop system, the mechanical ventilation volume is equal to the input air volume of the latent heat control system, that is, Vvt=Got/ρ.According to the actual situation of the office building, the amount of indoorCO2 concentration is calculated from 8 am to 6 pm. Indoor persons are in the normal office state. The extremely light activity state estimates that the average amount of CO2 concentration is 18 L/(person ∗ h).Therefore, the indoorCO2 concentration prediction model is expressed as follows:(12)VC˙=CoutVvt+Qp+18n−Vvt+LC,where n is the number of people in the office.


## 2.1. Dynamic Response of Temperature

Given that the independent control of temperature and humidity in the air-conditioning system uses fresh air in the dehumidification system to remove indoor residual humidity, CO2, and odors such that to ensure indoor air quality, the dynamic response modeling of room temperature must only consider the room’s sensible heat [33].The heat energy balance in an air-conditioning system is expressed as follows [34, 35]:(1)Q˙st=Qrt+Qwt−Qdt,where Qrt is the heat provided by the air-conditioning supply air; Qst is the sensible heat; Qdt is the outflow heat; and Qwt is the heat dissipation.The room sensible heat change can be described as follows [28]:(2)Q˙st=ρVC1Ti,where ρ is the indoor air density,kg/m3; V is the room volume, m3; C1 is the specific heat capacity of indoor air, J/(Kg ∗ K); and Ti is the room temperature.The relationship between the sensible heat provided by the air-conditioning system to the room and the air output can be expressed as follows [28]:(3)Qrt=ρC1GstTst,where Gst is the volume of air supplied,m3, and Tst is the air temperature of the sensible heat dry fan coil, °C.For rooms that use temperature and humidity as variables to control the air-conditioning system independently, the main factors that affect the indoor temperature response are listed as follows: sensible heat flowing out of the room and heat dissipation of the room [36]. Heat dissipation of the room includes the following parts: (1) instantaneous sensible cooling load due to the indoor and outdoor temperature difference and direct heat dissipation from the indoor heat source. (2) Heat dissipation caused by the radiation of sunlight through the window.Heat dissipation of the roomQwt is expressed as follows [37]:(4)Qwt=FλδTot−Tit+αiTot−Tit+σ,where F is the wall area,m2; λ is the thermal conductivity of the wall material layer; δ is the thickness of the wall material layer, m; To is the outdoor ambient temperature; αi is the heat transfer coefficient of composite heat transfer surface of the inner wall of the glass window; and σ is the heat generated by the solar radiation of the glass window in the room.The sensible heat flowing out of the room is primarily the heat taken away by return air. Given that the office building is assumed to be a closed-loop system, the return air volume can be calculated according to the supply air volume of the temperature control system as follows [29]:(5)Qdt=ρC1GstTit.Substituting (2)–(5) into (1), (6)ρVC1Ti⋅=ρC1GstTst+FλδTot−Tit+αiTot−Tit+σ−ρC1GstTit.


## 2.2. Dynamic Response of Humidity

The dehumidification system of the air conditioner with independent control of temperature and humidity adopts the full fresh air system. The humidity control system bears all the latent heat load of the building by sending dry fresh air with moisture content lower than the interior designed state. Under the assumptions that the office building is a closed-loop system and the pressure in the building remains unchanged, mass conservation of air humidity can be calculated as follows [38]:(7)Mndn⋅t=Gotdst−dnt+Wht,where Mn is the total mass of air in the building, g; dnt is the moisture content of the air in the building, g/kg; dst is the moisture content of the air supply of the air conditioner, g/kg; Got is the exhaust volume of the dehumidification system, g/h; and Wht is the indoor humidity load, g/h.Hence, determining the total indoor wet loadWh is important. The building’s moisture production primarily comes from people indoors, water surface, plants, and the amount of moisture from infiltrating air [39]. Given that this paper considers an office place, the main indoor moisture load involves the number of people that dissipates moisture and the amount of moisture dissipated by fresh air penetration [40].The wet load of personnel in the office building based on the adults is calculated as follows [32]:(8)Wt1t=0.278n∅g∗10−6,where n is the number of indoor personnel, ∅ is the personnel cluster coefficient, and g is the amount of moisture dissipated by the adults, g/h.Conventional air-conditioning systems only considered the wet load caused by fresh air penetration in winter but ignored the insignificant wet load generated by fresh air penetration in summer. By comparison, dry air is responsible for dehumidification in air-conditioning systems with independent temperature and humidity control although its dehumidification capacity is limited. Therefore, large humidity load caused by outdoor fresh air penetration must be considered. The wet load due to fresh air penetration can be calculated as follows [33]:(9)Wt2t=Lρdot−dnt,where L is the infiltration air volumem3 and do is the outdoor air moisture content.Substituting (8) and (9) into (7) leads to(10)Mndn⋅t=Gotdst−dnt+0.278n∅g∗10−6+Lρdot−dnt.


## 2.3. Estimate of IndoorCO2 Concentration

The latent heat control system in the air conditioner with independent control of temperature and humidity uses full fresh air input to ensure that the predicted air concentration in the office space will remain fresh. The relationship between the indoor concentration and the air volume of the air conditioner in the absence of people is expressed as follows:(11)VC˙=CoutVvt+Qp−Vvt+LC,where C is the indoor CO2 concentration; Qp is the pollutant emission rate; and Vv is the room mechanical ventilation m3/h. Given that the room is considered a closed-loop system, the mechanical ventilation volume is equal to the input air volume of the latent heat control system, that is, Vvt=Got/ρ.According to the actual situation of the office building, the amount of indoorCO2 concentration is calculated from 8 am to 6 pm. Indoor persons are in the normal office state. The extremely light activity state estimates that the average amount of CO2 concentration is 18 L/(person ∗ h).Therefore, the indoorCO2 concentration prediction model is expressed as follows:(12)VC˙=CoutVvt+Qp+18n−Vvt+LC,where n is the number of people in the office.


## 3. Design of Sliding Mode Controller

Define thatx1=Ts−Ti，u1=GsTs−Ti=Gsx1, and x2=ds−dn,u2=Gods−dn are the state variables. Given that the supplied air temperature Ts and the supplied air moisture content ds are unchanged, Ti⋅=−x1⋅ and dn⋅=−x2⋅.


### 3.1. Temperature Controller

The state equation of the temperature response in the room can be expressed as follows:(13)ρVC1x1⋅=−ρC1u1−FλδTo−Ts+x1−αiTo−Ts+x1−σ.Definexd1 as the error between the supplied air temperature of the terminal device and the ideal indoor temperature Td; that is, if xd1=Ts−Td, then e1=x1−xd1.The integral sliding surface can reduce the steady-state error of the system, weaken the chattering, and enhance the stability of the temperature controller. Therefore, the integral sliding mode surface function is defined as follows:Ifs=e1+k∫e1dt, then(14)s˙=e1⋅+ke1=x1⋅+ke1=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρVC1+ke.When the system state trajectories reached onto the sliding surface,s˙=0 is satisfied and the sliding mode accessibility condition ensures that the motion point at any position in the state space reaches the switching surface within a limited time and the trajectory of approaching movement is unlimited. Therefore, the approach law can effectively improve the dynamic quality of the approach movement. Therefore, the following reaching law of the power function is selected:(15)s˙=−k1sasgns,k>0,0<a<1.Given thatlims⟶0+s˙=lims⟶0+=k1sasgns<0 and lims⟶0−s˙=lims⟶0−=k1sasgns>0, the power reaching law guarantees the existence of the sliding mode and the global arrival condition.Therefore, we can obtain the following formula based on (14) and (15):(16)s˙=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρVC1+ke1=−k1sasgns.Thus, the following sliding mode controller based on the power reaching law is obtained:(17)u1=−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρC1+ke1+k1sasgnsV.Define the following Lyapunov function,Vs=1/2s2:(18)Vs⋅=ss⋅=e⋅+ke1s=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρC1+ke1s.Substituting that (17) is substituted into the available Vs⋅=−k1sasgnss since k1>0 and 0<a<1, it obtains Vs⋅<0. Therefore, the dehumidification system is stable.


### 3.2. Humidity Controller

Equation (10) presents that the state equation of the temperature response in the room can be expressed as follows:(19)Mnx2⋅=−u2−0.278n∅g∗10−6−Lρdo−ds+x2.Definexd2 as the error between the supplied air humidity of the latent heat removal terminal device and the ideal indoor humidity dl; that is, xd2=ds−dl and e2=x2−xd2.Selecting sliding surface function which iss=e2+k3∫e2dt, then(20)s˙=e2⋅+k3e2=−−u2−0.278n∅g∗10−6−Lρdo−ds+x2Mn+k3e2.The selected exponential approach law is(21)s˙=−k2s−εsgns,k2>0,ε>0.Iflims⟶0+s˙=lims⟶0+=−k2s−εsgns<0 and lims⟶0−s˙=lims⟶0−=−k2s−εsgns>0, then power reaching law achieves the condition of sliding motion and global reachability.Furthermore we can obtain the following formula based on (20) and (21):(22)s˙=−u2−0.278n∅g∗10−6−Lρdo−ds+x2Mn+k3e2=−k2s−εsgns.Hence,u2=−Mn−k2s−εsgns−k3e2−Lρdo−ds+x2−0.278n∅g∗10−6.Select the following Lyapunov function:Vs=1/2s2.Then,Vs⋅=ss⋅=−u2−0.278n∅g∗10−6−Lρdo−ds+x2/Mn+k3e2s=s−k2s−εsgns=−k2s2−sεsgns.Becausek2>0,ε>0, Vs⋅<0, the system is stable.


## 3.1. Temperature Controller

The state equation of the temperature response in the room can be expressed as follows:(13)ρVC1x1⋅=−ρC1u1−FλδTo−Ts+x1−αiTo−Ts+x1−σ.Definexd1 as the error between the supplied air temperature of the terminal device and the ideal indoor temperature Td; that is, if xd1=Ts−Td, then e1=x1−xd1.The integral sliding surface can reduce the steady-state error of the system, weaken the chattering, and enhance the stability of the temperature controller. Therefore, the integral sliding mode surface function is defined as follows:Ifs=e1+k∫e1dt, then(14)s˙=e1⋅+ke1=x1⋅+ke1=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρVC1+ke.When the system state trajectories reached onto the sliding surface,s˙=0 is satisfied and the sliding mode accessibility condition ensures that the motion point at any position in the state space reaches the switching surface within a limited time and the trajectory of approaching movement is unlimited. Therefore, the approach law can effectively improve the dynamic quality of the approach movement. Therefore, the following reaching law of the power function is selected:(15)s˙=−k1sasgns,k>0,0<a<1.Given thatlims⟶0+s˙=lims⟶0+=k1sasgns<0 and lims⟶0−s˙=lims⟶0−=k1sasgns>0, the power reaching law guarantees the existence of the sliding mode and the global arrival condition.Therefore, we can obtain the following formula based on (14) and (15):(16)s˙=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρVC1+ke1=−k1sasgns.Thus, the following sliding mode controller based on the power reaching law is obtained:(17)u1=−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρC1+ke1+k1sasgnsV.Define the following Lyapunov function,Vs=1/2s2:(18)Vs⋅=ss⋅=e⋅+ke1s=−u1V−Fλ+αiδx1ρVC1δ−Fλ+αiδTo−TsρVC1δ−σρC1+ke1s.Substituting that (17) is substituted into the available Vs⋅=−k1sasgnss since k1>0 and 0<a<1, it obtains Vs⋅<0. Therefore, the dehumidification system is stable.


## 3.2. Humidity Controller

Equation (10) presents that the state equation of the temperature response in the room can be expressed as follows:(19)Mnx2⋅=−u2−0.278n∅g∗10−6−Lρdo−ds+x2.Definexd2 as the error between the supplied air humidity of the latent heat removal terminal device and the ideal indoor humidity dl; that is, xd2=ds−dl and e2=x2−xd2.Selecting sliding surface function which iss=e2+k3∫e2dt, then(20)s˙=e2⋅+k3e2=−−u2−0.278n∅g∗10−6−Lρdo−ds+x2Mn+k3e2.The selected exponential approach law is(21)s˙=−k2s−εsgns,k2>0,ε>0.Iflims⟶0+s˙=lims⟶0+=−k2s−εsgns<0 and lims⟶0−s˙=lims⟶0−=−k2s−εsgns>0, then power reaching law achieves the condition of sliding motion and global reachability.Furthermore we can obtain the following formula based on (20) and (21):(22)s˙=−u2−0.278n∅g∗10−6−Lρdo−ds+x2Mn+k3e2=−k2s−εsgns.Hence,u2=−Mn−k2s−εsgns−k3e2−Lρdo−ds+x2−0.278n∅g∗10−6.Select the following Lyapunov function:Vs=1/2s2.Then,Vs⋅=ss⋅=−u2−0.278n∅g∗10−6−Lρdo−ds+x2/Mn+k3e2s=s−k2s−εsgns=−k2s2−sεsgns.Becausek2>0,ε>0, Vs⋅<0, the system is stable.


## 4. Design of Fuzzy Sliding Mode Controller

In this paper, approach lawss˙=−k1sasgns and s˙=−k2s−εsgns are selected, in which k1, k2, and ε are appropriate parameters to be selected to ensure that the system state trajectories reach to sliding surface rapidly and suppress chattering. Thus, this paper proposes fuzzy SMC based on reaching laws. The use of fuzzy control instead of traditional control solves the chattering problem of the air-conditioning system while improving the dynamic quality of the system and ensuring the good robustness of the system.


### 4.1. Parameter Fuzzification

This study designs a two-dimensional fuzzy controller to meet the requirements for a stable air-conditioning system under the conditions of temperature parameter changes and interference effects during the operation of the air conditioner. The input signal of fuzzy law is the temperature errore and its derivative de/dt. The output signal is the reaching law parameters ε, k1, and k2. The fuzzy subsets of input and output variables are {NB, NM, NS, ZO, PS, PM, PB} and quantified in the (−1, 1) area. The membership function is selected as a symmetric triangular function, and each value of the fuzzy subset has the same range width [41].


### 4.2. Fuzzy Rules

According to the principle of SMC, the parameters of the reaching lawk1, k2, and ε determine the fuzzy rules, as shown in Tables 1–3, respectively.Table 1
Fuzzy rule with parameterk1.
e1e⋅1NBNMNSZOPSPMPBNBPBPBPMPSPSZOZONMPBPBPMPSPSZONSNSPMPMPMZOZONSNSZOPMPMPSNSNSNMNMPSPSPSZONSNSNMNMPMPSZONSNMNMNMNBPBZOZONMNMNMNBNBTable 2
Fuzzy rule with parameterk2.
e2e⋅2NBNMNSZOPSPMPBNBNBNBNMNMNSZOZONMNBNBNMNSNSZOZONSNBNMNSNSZOPSPSZONMNMNSZOPSPMPMPSNMNSZOPSPSPMPBPMZOZOPSPSPMPBPBPBZOZOPSPMPMPBPBTable 3
Fuzzy rule with parameterε.
e2e⋅2NBNMNSZOPSPMPBNBNBNBNMNMNSZOZONMNBNBNMNSNSZOPSNSNBNMNSNSZOPSPSZONMNSNSZOPSPMPMPSNMNSZOPSPMPMPBPMNSZOPSPSPMPBPBPBZOZOPSPMPMPBPB


### 4.3. Fuzzy Reasoning

This paper uses the center of gravity method to complete deblurring. The output result after deblurring is presented as follows:(23)x0=∑i=1nxiucxi∑i=1nxi,where x0 is the output result after defuzzification, xi is the output variable, and ucxi is the membership function corresponding to xi.


## 4.1. Parameter Fuzzification

This study designs a two-dimensional fuzzy controller to meet the requirements for a stable air-conditioning system under the conditions of temperature parameter changes and interference effects during the operation of the air conditioner. The input signal of fuzzy law is the temperature errore and its derivative de/dt. The output signal is the reaching law parameters ε, k1, and k2. The fuzzy subsets of input and output variables are {NB, NM, NS, ZO, PS, PM, PB} and quantified in the (−1, 1) area. The membership function is selected as a symmetric triangular function, and each value of the fuzzy subset has the same range width [41].


## 4.2. Fuzzy Rules

According to the principle of SMC, the parameters of the reaching lawk1, k2, and ε determine the fuzzy rules, as shown in Tables 1–3, respectively.Table 1
Fuzzy rule with parameterk1.
e1e⋅1NBNMNSZOPSPMPBNBPBPBPMPSPSZOZONMPBPBPMPSPSZONSNSPMPMPMZOZONSNSZOPMPMPSNSNSNMNMPSPSPSZONSNSNMNMPMPSZONSNMNMNMNBPBZOZONMNMNMNBNBTable 2
Fuzzy rule with parameterk2.
e2e⋅2NBNMNSZOPSPMPBNBNBNBNMNMNSZOZONMNBNBNMNSNSZOZONSNBNMNSNSZOPSPSZONMNMNSZOPSPMPMPSNMNSZOPSPSPMPBPMZOZOPSPSPMPBPBPBZOZOPSPMPMPBPBTable 3
Fuzzy rule with parameterε.
e2e⋅2NBNMNSZOPSPMPBNBNBNBNMNMNSZOZONMNBNBNMNSNSZOPSNSNBNMNSNSZOPSPSZONMNSNSZOPSPMPMPSNMNSZOPSPMPMPBPMNSZOPSPSPMPBPBPBZOZOPSPMPMPBPB


## 4.3. Fuzzy Reasoning

This paper uses the center of gravity method to complete deblurring. The output result after deblurring is presented as follows:(23)x0=∑i=1nxiucxi∑i=1nxi,where x0 is the output result after defuzzification, xi is the output variable, and ucxi is the membership function corresponding to xi.


## 5. Simulation Analysis

This study uses MATLAB/Simulink to establish the simulation model of the central air-conditioning system. Fuzzy sliding mode control and traditional PID control methods are used to compare and verify the correctness and feasibility of the proposed strategy.Assuming that the room has a length, width, and height of 16, 10, and 4 m, respectively, the indoor air density, indoor air specific heat capacity, coefficient of thermal conductivity of wall materials, and thickness of the wall material areρ = 1.204 kg/m3, C = 1.003 J/(Kg ∗ K), λ = 0.58 W/(mK), and δ=0.5 m, respectively. Figure 2 illustrates the heat generated by sunlight radiating through the glass in the room.Figure 2
Heat from solar radiation.The indoor temperature is set to 25°C, and the input of outdoor temperature and humidity changes according to the data collected in Suzhou in July, as shown in Figures3 and 4.Figure 3
Outdoor temperature change.Figure 4
Outdoor humidity change.Assuming that the initial indoor ambient temperature is 26°C and the moisture content is 13 g/kg, the enthalpy chart demonstrates that the air moisture content is 12 g/kg when the temperature is set to 25°C and the optimum indoor relative humidity is 60%. Therefore, the ideal air moisture content is 12 g/kg.The comparison of indoor temperature and humidity responses under the sliding mode and the PID control strategies are illustrated in Figures5 and 6, respectively.Figure 5
Indoor temperature response.Figure 6
Indoor humidity response.The air volume input of indoor temperature and humidity control under the sliding mode and PID control strategies is compared and illustrated in Figures7 and 8, respectively.Figure 7
Temperature control input air volume.Figure 8
Humidity control input air volume.Figures5–8 demonstrate that the air conditioner system with independent control of temperature and humidity using the fuzzy SMC strategy can achieve the set temperature and humidity faster when the input air volume is only slightly different compared with the PID control. Meanwhile, it can be seen in Figures 5 and 6 that, compared with the air-conditioning system under PID control, the fuzzy sliding mode control strategy has minimal vibration at the preset humidity and temperature. From the data derived from the figure, it can be seen that the indoor temperature reaches the expected temperature time under fuzzy sliding mode control, fuzzy PID, and PID strategies: 7.668 min, 9.630 min, and 11.256 min, and the temperature overshoots are 0.0939, 0.3095, and 0.3789. The time for indoor humidity to reach the expected humidity is 11.256 min, 17.148 min, and 18.954 min. The humidity overshoot is 0.1145, 0.2284, and 0.3272.So, you can get the following result.Theorem 1.
The temperature error of the fuzzy sliding mode control strategy is only 30% and 24% of the other two methods.Theorem 2.
The humidity error of the fuzzy sliding mode control strategy is 50% and 35% of the other two methods.Theorem 3.
Compared with the traditional PID control technique, the higher accuracy of the SMC strategy ensures that the indoor environment is maintained at the desired level and meets the comfort requirements of the human body.Under the above circumstances, assuming that 10 people are inside the office, the fresh air input can be used to estimate theCO2 concentration in the indoor air within a day with the office CO2 concentration accounting for 0.045% of the air at 8:00. The simulation results are illustrated in Figure 9.Figure9 shows that the air conditioner with independent control of temperature and humidity using the fuzzy SMC can ensure a maximum indoor CO2 concentration of 0.1% [42], which belongs to fresh air and meets the requirements of human comfort.Figure 9
CO2 content assessment.


## 6. Conclusion

This paper proposes a fuzzy sliding mode approach for the independent control of temperature and humidity in air-conditioning systems. By analyzing the indoor environmental effect, mathematical models for room temperature, humidity, andCO2 concentration are developed. Compared with the traditional PID method, the simulation results show that the fuzzy-rules-based SMC achieves better dynamic performance. However, the proposed method is only applicable to the temperature- and humidity-independent control air-conditioning system in solution dehumidification mode. If the rotor dehumidification is used, it may lead to a large deviation in temperature control due to the coupling of heat and humidity. It is expected that the following research can overcome the temperature and humidity coupling of the air conditioner happening. The results of this study can provide practical guidance for engineering applications.



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*Source: 1976584-2020-08-04.xml*