## 4 Results and Discussion  
### Temperature and Humidity  
The temperature indicated in Figure 5a is the most important thermal environmental factor, as it is the dry-bulb temperature. Accordingly, it displayed a distribution of 26.2-26.8 \({}^{\circ}\)C in the air-conditioned space. The temperature was not high for the kitchen, where the cooling flow was not supplied smoothly. However, a high temperature was observed around the corner of the living room. (Air flow distribution will be described later in Section 4.3.)  
The thermal comfort evaluation via ASHRAE comfort zone, shown in Figure 3c, was based on the dry-bulb temperature, and the effect of solar radiation was not considered. Unlike the constant temperature and humidity chamber in which the performance of the refrigerator is mainly evaluated, the actual living space is affected by solar radiation owing to the presence of windows. Because of the direct sunlight that enters the living room through the window, the distribution of the black bulb's temperature measured at the radiation equilibrium state of the black body was different from that of the dry-bulb temperature.  
As seen in Figure 2a, the windows of the cooling space can be found in the west and south of the living room. In particular, there are partial windows in the west and full windows in the south. The experiment was conducted around 1 p.m., with the south set as the direction of the solar radiation. Because of the solar radiation, a region with a high average radiant temperature appeared in the area  
Figure 5: Temperature distribution at a height of 1.1 m from the ground in a residential space with hybrid desiccant cooling: (**a**) dry bulb temperature; (**b**) globe (black bulb) temperature.  
around the southern window. In the absence of sunlight, the radiant temperature was reported to be approximately 1 \({}^{\circ}\)C higher than the dry-bulb temperature [29].  
It should be noted that at the time of measurement, the average radiant temperature was measured without a shade. Therefore, there is a significant difference of 3.4 \({}^{\circ}\)C between the black bulb temperature distribution (shown in Figure 5b) and the dry-bulb temperature distribution (shown in Figure 5a). The globe temperature was clearly higher near the southern window, but was also higher than the dry-bulb temperature in other areas where direct sunlight was not shining. Overall, it showed a distribution of 28.8-29.8 \({}^{\circ}\)C, which is at least 2 \({}^{\circ}\)C higher than the dry-bulb temperature.  
Figure 6 presents the distribution of humidity at the height of 1.1 m from the ground in the cooling space. As depicted in Figure 6a, the overall distribution of relative humidity fell between 44% and 50%; thus, the indoor environment could be located in the upper right part of the ASHRAE comfort zone (as shown in Figure 3). In the case of the local humidity, the saturated water vapor pressure tended to increase with a rise in temperature; thus, the humidity distribution showed similarity with the inversion of the temperature distribution shown in Figure 5a. That is, the relative humidity was lowest in the left corner of the living room where the dry-bulb temperature is high, whereas it was high in the kitchen corner and near the wall opposite the outlet, where the cooling effect was likewise high.  
The standard ASHRAE comfort zone is dictated by the dry-bulb temperature and relative humidity; however, in the PMV calculation, humidity is considered as the partial pressure of water vapor, which is known to be directly related to the humidity ratio. Figure 6b shows the humidity ratio obtained from the dry-bulb temperature in Figure 5a and the relative humidity in Figure 6a. Based on the figure, the humidity ratio ranged between 10.0 and 10.6 g/kg, while the shape of the overall spatial distribution was similar to that of the relative humidity depicted in Figure 6a.