Experimental Investigation of the Potential of a New Fabric-Based Evaporative Cooling Pad

Abstract

Direct evaporative coolers are energy-efficient, economic solutions to supplying cooling demand for space conditioning. Since their potential strongly depends on air hygrothermal conditions, they are traditionally used in dry and hot climates, though they can be used in many applications and climates. This work proposes a new direct evaporative cooling system with a fabric-based pad. Its design enables maximum wetted surface with minimum pressure drop. Its performance has been experimentally characterized in terms of saturation efficiency, air humidification, pressure drop, and level of particles, based on a full factorial Design of Experiments. Factors studied are air dry bulb temperature, specific humidity, and airflow. Saturation efficiencies obtained for a 25 cm pad are above the values achieved by other alternative evaporative cooling (EC) pads proposed in the literature, with lower pressure drops.

1. Introduction

Evaporative cooling is a phenomenon that occurs in nature when water comes into contact with unsaturated air, hence its occurrence near water bodies like waterfalls or the sea, after a storm, or due to sweat evaporation from skin. Its applicability for human comfort dates back to ancient Egypt [1]. The consequent simplicity of evaporative cooling systems makes them cost-effective, energy-efficient, and environmentally friendly solutions for a wide range applications and climates [2]. They permit achieving appropriate indoor conditions in otherwise non-conditioned indoor spaces such as greenhouses, storehouses, factories, and farms, where ventilation during the cooling season is insufficient, and mechanical cooling is unfeasible. However, their use for indoor comfort is also crucial. On the path to Net Zero Energy Buildings, they can either substitute, improve the performance of, or complement conventional mechanical compression cooling systems.

Direct Evaporative Coolers (DEC) enable air cooling as it passes through wetted pads or sprayed water. As water evaporates in air, heat and mass transfer transforms the sensible heat of air into latent heat in an adiabatic process, lowering the air Dry Bulb Temperature (DBT) of treated air towards its Wet Bulb Temperature (WBT), while its specific humidity increases. Materials of commercialized pads range from aspen wood or absorbent plastic foams to “rigid-media” pads made of corrugated materials including cellulose, plastic, and fiberglass [3].

Cellulose commercialized pads are extensively studied in the literature, both experimentally and theoretically, through mathematical models. Sheng & Nanna [4] characterize the saturation efficiency and humidity increase in the treated air of a cellulose corrugated panel in terms of inlet air DBT, air velocity and pad thickness. Besides saturation efficiency and humidification increase, Malli et al. [5], Franco et al. [6] and Warke & Deshmukh [7] characterize the pressure drop generated.

Barzegar et al. [8] compare the performance of cellulose pads from two different manufacturers, though only in terms of air velocity. Al-Badri & Al-Waaly [9] compare the saturation efficiency of three different cellulose pads in terms of inlet air DTB, air WBT and water temperature and ratio. He et al. [10] compare the performance of a Munters CELdek® cellulose pad to a PVC fibre pad, while Franco et al. [11] compares a cellulose pad to a plastic mesh-based pad. The latter also approaches the study of heat and mass coefficients, and so do Al-Badri and AlWaaly [9]. To the knowledge of the authors, only He et al. [10] provide detailed observations on water entrainment.

There exists wide research on the use of alternative materials for DEC media. Most works focus on pads made of locally available vegetable fibres such as coconut [12,13,14,15,16], jute [12,17,18], luffa [17,19] and palash [13,14], as well as wood fibres [17,20].

Some research also considers the use of porous stones [20,21] and ceramics [22] as DEC media. More unusual EC medias are made of bulk charcoal [18,23], sliced wood [24], perforated bamboo [25], composite material with rice byproducts [26] or shredded latex foam, palm fruit fibre, etc. [18].

However, existing literature barely approaches the use of textiles for evaporative cooling, despite the advantage of their wicking ability, as studied by Xu et al. [27] for indirect evaporative cooling systems. They analysed six different fabrics compared to Kraft paper, with favourable results, but nonetheless observed that the use of fabrics may cause mechanical problems, as wet surfaces distort if adhered to a support sheet.

Liao et al. [28] studied nonwoven fabric and coir as alternatives to EC pads, providing correlations for saturation efficiency and pressure drop in terms of pad thickness. Alam et al. [12] also studied coir, together with sackcloth, with the former performing better due to a maximum temperature drop of 4 °C. Both studies highlight the energy efficiency and low cost of the solution proposed. Liao and Chiu [29] experimentally studied a new pad made of coarse and fine fabric PVC sponge mesh, obtaining efficiencies of up to 86.32% and 85.5% for 15 cm thickness pads, respectively.

Fabrics have occasionally been considered in combination with passive cooling solutions for buildings. Ghosal et al. [30] studied the cooling effect of a wetted shade fabric installed in a green house, achieving up to 6 °C temperature drop. Esparza et al. [31] designed a fabric-based evaporative cooling system with a 3 mm thick wool and polyester membrane as an alternative to water roof ponds. Their solution achieved the lowest temperatures under the three climate conditions studied: hot sub-humid, warm sub-humid and hot humid.

Together with capillary diffusion and wicking ability, the main assets of the use of fabrics relies on their low cost, it being possible to reuse discarded clothes. Microbial growth is the main concern shared by all evaporative cooling equipment but specially noticed for pads based on organic materials, both conventional and alternative. Proper maintenance based on bleedoff, makeup water quality and complete emptying of the sump during non-operating periods would avoid this issue [32,33]. As usually found in commercial systems, fabric-based EC can also include ozonisers or UV lamps for pathogen inactivation in working water. Moreover, simple pad configurations made with fabrics can be easily disassembled and washed, facilitating the maintenance of the media.

Organic fibres may also be disregarded due to concerns about system durability. For instance, Jute, Luffa, Comm and Palm show cooling efficiency degradation with time. Deterioration is mainly due to bio-degradation, and among the previous materials, jute fibres show the worst performance [17]. Nonetheless, replacement of media in non-elaborated pads made of organic, widely available materials would be cost-effective.

The aim of this work is to design, build and experimentally characterize a new Evaporative Cooling Pad made of cotton fabric as an alternative to conventional pads, which is different from the proposals already studied in the literature. Saturation efficiency, air humidification, pressure drop and particles are presented and contrasted with results obtained in existing research.

2. Materials and Methods

This section describes the design, construction and experimental characterization of the target evaporative cooling system.

2.1. Design and Construction of the Fabric EC System

A fabric-based evaporative cooling (EC) pad has been designed and built with a 25 x 1600 cm² piece of cotton fabric. It was obtained from a 200 x 200 cm² cloth cut into eight pieces, then sewed. The cloth has been arranged and stretched on a wire structure, creating a 25 cm thick hexagonal pad with homogeneous air paths separated with the aid of spacers (Figure 1). The cross section is 0.18 m². This design aims at avoiding any mechanical issues related to problems observed in the literature [27]. Since the cloth does not excessively tighten, in case of slight deterioration of the cotton fibres the system would not dismantle.

The pad is installed within a methacrylate case 45 cm wide, 45 cm high and 25 cm deep. Since the pad is hexagonal, non-useful areas are blocked with additional methacrylate plates to avoid air bypass. Water is pumped from a lower deposit to an upper distributor. The water pump provides 9.5 l/min and requires 9 W. The whole system is connected to air inlet and outlet plenums. These plenums are pyramidal shaped and 60 cm long to favour uniform airflow through the pad. (Figure 2).

2.2. Experimental Setup

The system is connected through flexible ducts to an Air Handling Unit (AHU) that provides the desired conditions of air Dry Bulb Temperature (DBT), Relative Humidity (RH) and volume flow (Figure 3). DBT and RH sensors at the outlet enable control of the AHU. The Airflow is measured with an orifice plate, by differential pressure measurements in the nozzle and six diameters far upstream. Pressure drop is also measured in the fabric EC system.

DBT and RH are measured in triplicate at the fabric EC system inlet and outlet with 4-wire Pt100 and capacity sensors. The system characterization is based on the average measurements of these three-sensor measuring points. This triple measurement at each section also enables the checking of any possible stratification. At the air inlet, DBT standard deviation ranges from 0.52 to 0.57 °C, while RH standard deviation ranges from 0 to 2.4%. At the air outlet, DBT standard deviation ranges from 0.12 to 0.54 °C, and RH standard deviation ranges from 2.5 to 5.3%. Comparing these values to the uncertainty of the measurement given later (Section 3), it demonstrates that no representative stratification occurs.

Water temperature in both the lower tank and the upper distributor is measured in duplicate with ceramic Pt100 sensors. Temperature Pt100 sensors’ accuracy is ± 0.1 °C, and they are calibrated with a Fluke 9103 dry well, while RH capacity sensors’ accuracy is ± 2%, and they are calibrated with a Vaisala Humidity Calibrator HMK15. Pressure drop was measured with a Honeywell 163PC01D75 (160 PC series). The orifice plate was previously calibrated with a nozzle, using a Testo 435-4 for pressure drop measuring. Temperature, RH and differential pressure sensors are connected to an Agilent 34972A data acquisition system.

Additionally, airborne particles at the system outlet are characterized with a Lasair II Air particle counter. Measurements have been performed in duplicate at the three airflow levels and for the media wetted and dry (total of 12 tests).

2.3. Design of Experiments

To characterize the behaviour of the system, this work proposes a full factorial design of experiments. Target factors are three-level air volume flow (V), six-level DBT (T) and three-level specific humidity (w), the latter in kilograms of vapor to kilograms of dry air (kg_v / kg_da). Air DBT ranges from 25 to 50 °C to cover the most common summer conditions worldwide. Airflow and specific humidity are limited by the experimental setup: the air volume flow rate studied ranges from the lowest limit of the orifice plate accuracy and the maximum airflow provided by the AHU, while the minimum and maximum specific humidity considered are the air specific humidity at the laboratory and the maximum humidity achievable with the humidifier at 25 °C.

Tests are performed in Valladolid, Spain (approximately 700 m.a.s.l.). The experimental runs are performed once, randomized. Tests that did not reach a steady state were disregarded and repeated.

Table 1. Factors, levels, and test code. Order of the test run is in parenthesis.

Airflow [m3/h]	Specific Humidity [kgv/kgda]	DBT [°C]
		T1 25 °C	T2 30 °C	T3 35 °C	T4 40 °C	T5 45 °C	T6 50 °C
V1 210	W1 0.0115	V1T1W1 (1)	V1T2W1 (8)	V1T3W1 (16)	V1T4W1 (10)	V1T5W1 (6)	V1T6W1 (13)
	W2 0.0150	V1T1W2 (9)	V1T2W2 (3)	V1T3W2 (5)	V1T4W2 (12)	V1T5W2 (14)	V1T6W2 (17)
	W3 0.0195	V1T1W3 (11)	V1T2W3 (7)	V1T3W3 (2)	V1T4W3 (4)	V1T5W3 (15)	V1T6W3 (18)
V2 300	W1 0.0115	V2T1W1 (43)	V2T2W1 (49)	V2T3W1 (37)	V2T4W1 (47)	V2T5W1 (52)	V2T6W1 (40)
	W2 0.0150	V2T1W2 (42)	V2T2W2 (39)	V2T3W2 (46)	V2T4W2 (50)	V2T5W2 (45)	V2T6W2 (53)
	W3 0.0195	V2T1W3 (54)	V2T2W3 (48)	V2T3W3 (51)	V2T4W3 (38)	V2T5W3 (44)	V2T6W3 (41)
V3 450	W1 0.0115	V3T1W1 (32)	V3T2W1 (22)	V3T3W1 (19)	V3T4W1 (27)	V3T5W1 (24)	V3T6W1 (30)
	W2 0.0150	V3T1W2 (36)	V3T2W2 (34)	V3T3W2 (21)	V3T4W2 (31)	V3T5W2 (26)	V3T6W2 (28)
	W3 0.0195	V3T1W3 (23)	V3T2W3 (33)	V3T3W3 (35)	V3T4W3 (20)	V3T5W3 (29)	V3T6W3 (25)

gathers the levels of the factors studied, tests performed, and their order.

3. Results

Actual DBT and RH conditions of inlet air achieved in the AHU for the Design of Experiments shown in Table 1 are gathered in

Table 2. Measured inlet conditions for each test.

Airflow [m3/h]	Specific Humidity [kgv/kgda]	DBT [°C]
		T1 25 °C	T2 30 °C	T3 35 °C	T4 40 °C	T5 45 °C	T6 50 °C
V1 210	W1 0.0115	25.2 °C 55.0%	29.6 °C 45.3%	36.4 °C 30.6%	39.7 °C 30.3%	46.5 °C 17.7%	48.5 °C 15.4%
	W2 0.0150	24.6 °C 84.8%	30.5 °C 55.9%	35.9 °C 43.0%	40.0 °C 32.3%	46.0 °C 21.9%	48.5 °C 17.1%
	W3 0.0195	25.2 °C 100 %	29.2 °C 71.4%	36.3 °C 55.0%	39.6 °C 48.8%	46.6 °C 29.2%	50.2 °C 22.3%
V2 300	W1 0.0115	25.8 °C 55.8%	30.0 °C 44.8%	34.6 °C 33.7%	39.9 °C 27.4%	45.3 °C 22.0%	51.5 °C 14.6%
	W2 0.0150	25.2 °C 71.7%	30.3 °C 60.2%	34.9 °C 45.5%	40.0 °C 39.5%	45.2 °C 29.8%	50.9 °C 20.2%
	W3 0.0195	25.3 °C 81.4%	30.0 °C 72.5%	34.9 °C 63.1%	40.8 °C 48.6%	45.9 °C 36.1%	51.6 °C 28.5%
V3 450	W1 0.0115	25.2 °C 58.0%	30.4 °C 43.9%	35.9 °C 31.5%	41.5 °C 30.6%	45.9 °C 16.9%	52.0 °C 18.6%
	W2 0.0150	25.0 °C 69.7%	30.0 °C 61.6%	35.7 °C 45.3%	41.5 °C 31.6%	46.8 °C 28.8%	48.0 °C 20.8%
	W3 0.0195	25.2 °C 93.0%	30.0 °C 69.2%	35.0 °C 58.7%	41.4 °C 47.4%	43.2 °C 39.3%	51.1 °C 23.3%

.

Outlet conditions and water temperatures are given in

Table 3. Measured air outlet conditions for each test.

Airflow [m3/h]	Specific Humidity [kgv/kgda]	DBT [°C]
		T1 25 °C	T2 30 °C	T3 35 °C	T4 40 °C	T5 45 °C	T6 50 °C
V1 210	W1 0.0115	20.1 °C 86.0%	20.5 °C 87.9%	23.7 °C 77.0%	25.2 °C 83.8%	27.0 °C 87.7%	29.3 °C 83.1%
	W2 0.0150	20.1 °C 100%	23.4 °C 97.8%	26.0 °C 95.7%	26.0 °C 91.1%	28.2 °C 88.7%	29.8 °C 74.4%
	W3 0.0195	22.7 °C 100%	23.6 °C 100%	26.6 °C 94.0%	27.7 °C 94.1%	30.2 °C 94.5%	32.0 °C 93.4%
V2 300	W1 0.0115	18.8 °C 91.9%	21.4 °C 87.3%	23.5 °C 85.8%	25.9 °C 80.1%	28.2 °C 76.6%	30.3 °C 74.0%
	W2 0.0150	20.9 °C 100%	22.9 °C 100%	25.3 °C 92.8%	27.8 °C 88.2%	29.4 °C 81.8%	31.3 °C 74.0%
	W3 0.0195	21.6 °C 100%	24.3 °C 100%	27.1 °C 100%	29.0 °C 100%	31.2 °C 90.8%	32.8 °C 84.7%
V3 450	W1 0.0115	19.6 °C 90.0%	22.2 °C 87.6%	25.9 °C 70.5 %	29.1 °C 72.8 %	29.5 °C 71.7 %	34.2 °C 69.5%
	W2 0.0150	21.0 °C 100%	23.8 °C 95.8 %	26.3 °C 89.7 %	29.5 °C 74.4 %	32.8 °C 73.5 %	32.1 °C 74.4%
	W3 0.0195	23.1 °C 99%	25.7 °C 100%	27.0 °C 98.1 %	30.7 °C 92.1 %	32.0 °C 89.0 %	37.4 °C 68.9%

and

Table 4. Measured water temperatures for each test.

Airflow [m3/h]	Specific Humidity [kgv/kgda]	DBT [°C]
		T1 25 °C	T2 30 °C	T3 35 °C	T4 40 °C	T5 45 °C	T6 50 °C
V1 210	W1 0.0115	17.1 °C	17.7 °C	20.0 °C	20.9 °C	21.6 °C	22.1 °C
	W2 0.0150	19.9 °C	21.3 °C	22.0 °C	22.6 °C	23.5 °C	23.7 °C
	W3 0.0195	22.2 °C	22.7 °C	23.0 °C	24.4 °C	26.0 °C	26.7 °C
V2 300	W1 0.0115	16.7 °C	18.0 °C	19.2 °C	20.4 °C	21.8 °C	22.4 °C
	W2 0.0150	20.0 °C	20.4 °C	21.6 °C	22.9 °C	22.7 °C	24.3 °C
	W3 0.0195	21.1 °C	21.8 °C	23.8 °C	24.6 °C	24.5 °C	25.6 °C
V3 450	W1 0.0115	16.9 °C	19.3 °C	19.6 °C	20.7 °C	21.4 °C	23.5 °C
	W2 0.0150	19.5 °C	20.7 °C	22.1 °C	22.3 °C	23.7 °C	23.7 °C
	W3 0.0195	21.1 °C	22.7 °C	22.9 °C	25.9 °C	24.9 °C	25.4 °C

, respectively.

Values provided in Table 2, Table 3 and Table 4 are the average values measured during the steady state periods for each test. The uncertainty of these values can be determined as the sum of the sensor accuracy (Section 2.2) and the standard deviation of the measured value along the period considered. The standard deviation of the DBT and RH measurements during steady state conditions is below ± 0.2 °C and ± 3% at the system inlet, respectively. These are larger than the DBT and RH standard deviations at the system outlet (± 0.1 °C and ± 1%, respectively), which is due to the effect of the AHU control. Consequently, uncertainty would be ± 0.3 °C for the DBT and ± 5% for the RH.

Next, the results of the obtained target parameters are described and discussed within existing research.

3.1. Saturation Efficiency

Saturation efficiency, ε, relates the temperature drop achieved in the air between the inlet (T_in) and outlet (T_out) to the maximum temperature drop achievable, the latter being considered in terms of the adiabatic saturation temperature of inlet air (T_{as in}), as expressed in Equation (1):

$$\epsilon =\frac{T_{in}-T_{out}}{T_{in}-T_{asin}}$$

(1)

Results obtained for the saturation efficiency are shown in Figure 4.

Saturation efficiency is almost constant with the inlet air DBT, though for extreme temperatures (over 40 °C) it decreases. Inlet air humidity level has also a minor effect. Saturation efficiency can be expected to be almost constant for the common range of inlet air hygrometric conditions. Nonetheless, the effect of the airflow level is more noticeable, as larger airflows incur into lower saturation efficiencies. A more detailed analysis of this dependency is approached in the discussion section in comparison to existing research.

3.2. Air Humidification

Air humidification is studied through the increment of the specific humidity, w, as demonstrated in Equation (2):

$$\Delta w=w_{out}-w_{in}$$

(2)

Results shown in Figure 5 illustrate how the increment of the specific humidity strongly depends on the inlet air DBT. Higher inlet specific humidity slightly conditions a lower increment. Both results are due to the larger Wet Bulb Depression (WBD), this being the difference between the DBT and the Wet Bulb Temperature (WBT). Since saturation efficiency is fairly maintained for a particular design operating at a particular airflow, larger WBD also involves larger humidity increments.

Some tests (V1T1W2, V1T1W3, V2T1W3, V2T2W3 and V3T1W3) showed air slight dehumidification. This is because water temperatures (Table 2) did not reach the air saturation temperature of inlet air. Consequently, under inlet air conditions corresponding to high relative humidity, when adiabatic saturation and dew point (DPT) temperatures were similar, water temperature was slightly below air DPT. Tests V1T3W3 and V1T4W4 show the same behaviour, though inlet air relative humidity is low. In this case, water temperature remained far from the target adiabatic saturation temperature due to the thermal inertia of the 50 l water tank, thus not being representative.

3.3. Pressure Drop

Pressure drop in the fabric EC pad has been calculated through the experimental procedure shown in Figure 3, varying the potentiometer of the fan in four positions. Measurement of the pressure drop in the calibrated orifice plate enables determination of the air volume flow through the system (

Table 5. Airflow and pressure drop registered in the system.

Pressure Drop in the Orifice Plate (Pa)	Air volume Flow (m3/h)	Pressure Drop in the Fabric EC System (Pa)
766	543	9
531	451	6
179	261	3
95	190	2

). Pressure drops obtained are low, as expected due to the design of the system and the low Reynolds numbers achievable under the air velocities tested for the airpath between wetted surfaces. Comparison to values obtained in the literature for conventional and other alternative pads is discussed in the next section.

3.4. Airborne Particles

DEC systems are known to perform some cleaning of treated air [2]. The study of particles airborne through the system provide insight into this issue and also into the water entrainment that can involve risk of dispersion of Legionella bacteria. To analyse the latter issue, special attention must be paid to 5 µm aerosols. This sizing is determinant because they are breathable aerosols of enough size to contain rod shaped 1 x 3 µm size bacteria [33].

Table 6. Airborne particles counted at the fabric EC pad outlet.

Media	Airflow (m3/h)	Test No.	Particle Size
			0.3 µm	0.5 µm	1 µm	5 µm	10 µm	25 µm	Total
Dry	V1	1	300493	137149	58035	1704	290	18	497689
		6	304787	128504	53955	1694	229	7	489176
	V2	2	297348	129643	50795	1227	197	6	479216
		4	294970	122589	45750	1054	140	3	464506
	V3	3	298592	133134	52997	1010	103	9	485845
		5	294268	121133	44317	783	88	7	460596
Wet	V1	7	330227	112532	42305	1111	124	6	486305
		8	332127	111734	42688	1209	134	7	487899
	V2	9	327564	101634	33258	658	70	4	463188
		12	346768	106485	34215	598	72	2	488140
	V3	10	333924	110254	40466	798	86	4	485532
		11	334664	105435	35631	553	57	2	476342

gathers the number of particles registered for all tests performed at each airflow level, with the dry and then wetted media.

The smallest registered particles of 0.3 µm account for 60 to 70% of the total number of particles counted. As well as this, almost all particles registered (99.6 to 99.9%) are equal to or smaller than 1 µm and therefore cannot contain Legionella bacteria.

Concerning air cleaning, the number of particles decreases through the wetted media in about 15–17% for 0.5 µm, 22–30% for 1 µm, 25–45% for 5 µm, and above 60% for the largest particles. However, the number of the smallest 0.3 µm particles increases in 9 to 14%. This demonstrates that wetted media actually performs air cleaning of particles equal to or above 0.5 µm. Water entrainment may also be restricted to small aerosols that cannot contain Legionella, though this needs further study using other measuring methods that distinguish between particles and aerosols. Nonetheless, proper maintenance of the system is strictly necessary to avoid proliferation of Legionella.

4. Discussion

Results for the air specific humidity increase correspond to those in existing research. Sheng & Nnanna [4] registered increments of the air specific humidity from 3. 4 g_v/kg_da at 25.5 °C to 7.4 g_v/kg_da at 45 °C, thus being of the same order of magnitude than the ones obtained in the present work.

Figure 6 shows the saturation efficiencies in terms of air velocity in comparison to previous results in existing literature on alternative pads [21,28,29]. For clarity and correspondence to the air hygrothermal conditions studied in the referred works, it only presents results obtained for the first three levels of temperature (T1, T2 and T3) at the intermediate humidity level (W2). Corresponding relative humidity is 70%, 50% and 40%, approximately. Only results for the largest thicknesses studied in the referred works are considered (15 cm). No information was given in the referred works as to the errors expected.

Comparison to results obtained by Jain and Hindoliya [14] is given in Figure 7. To compare results obtained under the closest air conditions to the referred work, Figure 7 shows results from the present work obtained only at temperature levels T4 and T5, at the lowest humidity level (W1). No information was given in the referred work as to the errors expected. It can be observed that the proposed system using woven fabric can achieve larger saturation efficiencies than using other alternative materials made from vegetable fibres.

Regarding the results compared in Figure 6 and Figure 7, the new fabric-based EC cooling pad can achieve larger saturation efficiencies. This could be due to the larger thickness (25 cm) compared with the commonly largest thickness studied (15 cm) but also because of the wicking and capillary diffusion properties of the fabric used.

Taking a look at the results compared in Figure 8, larger thicknesses, in this case, does not incur excessive pressure drops. Pressure drops obtained by the new fabric 25 cm thick EC pad is of the same order of magnitude as that expected for conventional 15 cm cellulose pads [21] and other fabric-type pads in the literature [28]. This fact would be due to clearer air paths through the proposed pad compared with the compacity of the commercial CELdek® and configurations with coir and nonwoven fabric 15 cm pads.

Indeed, pressure drop is much lower than that obtained for alternative pads made of different stones [21] or fabric PVC sponge mesh [29]. Much larger pressure drops can be expected in pads made of different available fibres, such as khus, palash, coconut or aspen involve [13], and thus are not represented in Figure 8.

Concerning results for airborne particles, and to the knowledge of the authors, no previous research has approached this issue. Water entrainment is analysed in terms of the air velocity of cellulose and PVC pads by He et al. [10] by means of water-sensitive papers. They concluded that cellulose pads and low air velocities avoided risk of water entrainment.

5. Conclusions

Existing literature on the use of wetted fabrics for Evaporative Cooling purposes is scarce, despite demonstrated interest in these materials in terms of capillary diffusion and wicking ability. Related previous research has focused on its combination with passive architecture, and fabric-based EC pads are anecdotic among the large number of new pads built with alternative materials that can be found in the literature.

The present work designed and built an alternative EC pad using cotton fabric. The detailed description given of the system construction permits its reproduction.

The saturation efficiency registered is barely affected by air inlet hygrometric conditions, though larger airflows involve lower efficiencies. The values obtained are above those for other alternative pads studied in the literature. This could be due to both the pad design and the cotton fabric wicking ability and capillary diffusion.

Air humidification increases notably with inlet air DBT, slightly affecting specific humidity. This is due to larger Wet Bulb Depressions and stable saturation efficiencies in the same airflow.

The pressure drop generated for the 25 cm pad is of the same order of magnitude as results in existing research found for 15 cm conventional cellulose pads and 15 cm fabric-based pads, and much lower than other alternative pads made of vegetable fibres and different stones. Further research on the aerodynamic resistance of the pads could illustrate the optimum configuration.

Particle counting demonstrates that the wetted media performs air cleaning for particles above 0.3 µm. As well as this, more than 99.6% of the airborne particles counted cannot contain the Legionella bacteria, both for dry and wet media. However, proper maintenance of the system is strictly necessary to avoid microbial growth, as well as any risk of Legionella dispersion. In this sense, fabrics used as wetting media in simple configurations can be easily dismantled and washed for maintenance. Replacement of the media would be cost-effective. Further research on the durability of organic-based EC media would be necessary to enhance the use of these alternative systems.

The better performance obtained for the cotton fabric in this particular design, compared with other materials, can enhance the use, or reuse, of common fabrics for EC purposes.