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U.S.- India Joint
Center for Building Energy Research and Development
(CBERD)
Multi Utility Evaporative Cooler with Diabatic
Contacting Device
Milind V Rane, Narendra Singh
IIT Bombay, Mechanical Engineering Department
ASHRAE Hot Climates Conference
Millennium Hotel, Doha, Qatar
February 24 to 26, 2014
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Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
Acknowledgements
The authors acknowledge the assistance and thank all the reviewers, in particular, the following
organisations, for their advice and continued support.
The U.S. Department of Energy (DOE) and the Department of Science and Technology (DST),
Government of India (GOI) provided joint funding for work under the U.S.–India Partnership to
Advance Clean Energy Research (PACE-R) program’s “U.S.–India Joint Center for Building Energy
Research and Development” (CBERD) project. The Assistant Secretary for Energy Efficiency and
Renewable Energy, Office of Building Technology, State and Community Programs, of the U.S. DOE
under Contract No. DE-AC02-05CH11231 supports the U.S. CBERD activity. The DST, GOI,
administered by Indo-U.S. Science and Technology Forum, supports the Indian CBERD activity.
Please cite this document as:
Rane M V, Singh N, “Indirect Evaporative Precooling of Fresh Air Using Heat Exchangers with
Enhanced Flow Passages”, Proceedings of ASHRAE Hot Climates Conference, Millennium Hotel,
Doha, Qatar, February 24 to 26, 2014, Paper # 12605
Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
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Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
Heat Pump Laboratory at Indian Institute of Technology Bombay
Document No.- Task 3.1/04/13-14
Multi Utility Evaporative Cooler with Diabatic Contacting
Device
Author
Milind V Rane, PhD; Narendra Singh
April, 2014
Team Member
Milind V Rane, Darren I Pinto, Deepa M Vedartham,
Shreyas A Chavan, Narendra Singh, Prathamesh T Manave, Mukesh Bharadwaj
Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
ABSTRACT
Experimental and theoretical investigation of an evaporative cooler using patented diabatic
contacting device with high surface density, 410 to 550 m2 / m3, will be presented in this paper.
Heat and mass transfer coefficients have been reported. High surface density of the heat and
mass transfer surface helps keep the unit compact and air flow parallel the wavy surface of the
rotating disks helps achieve high heat and mass transfer coefficients while keeping the pressure
drops low. Carryover of liquid in to the air stream is also avoided in this design.
The diabatic contacting device involves multiple disks assembled on a non-circular shaft
rotated at 5 to 40 rpm using a low speed low wattage rotor motor. Multi stage contacting is
possible with several diabatic contacting devices assembled in series. Cooling capacity of the
assembly can be increased by increasing the number of parallel trays or increasing the length
of each contacting tray. Assembly of the rotating disks dips in the water in the trough as it
rotates and then comes in contact with the air passing perpendicular to the shaft. Evaporation
of water cools the remaining water in the trough and this in turn cools the fluid being passed
through the passages of the diabatic contacting device. This cooling effect has been used to
cool liquids, condense refrigerant or process vapours which simultaneously aerating and / or
evaporating effluent streams in a once through flow arrangement.
The system is economically viable and involves less maintenance cost. The analysis presented
in the paper confirms the benefit of indirect evaporative coolers for hot and humid climate
conditions.
Keywords: Multi utility evaporative cooler, diabatic contacting device, rotating disks
Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
CONTENT
ABSTRACT
vi
CONTENT
vii
NOMENCLATURE
viii
1. INTRODUCTION
1
2. DESIGN CONSIDERATIONS
2
2.1 Experimental Set Up
2
2.2 Instrumentation
5
3. THEORETICAL INVESTIGATION
4.2 Assumptions
5
6
5. RESULTS AND DISCUSSION
7
6. CONCLUSION
9
REFERENCES
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U.S.-India joint Center for Building Energy Research and Development (CBERD)
10
NOMENCLATURE
A
area, m2
BICL
building integrated closed loop
cp
specific heat capacity at constant pressure, kJ/kg.K
d
diameter, m
EWC
evaporative water cooler
G
mass of water transferred, kg/s (lb/h)
h
enthalpy, kJ/kg, (BTU/lb)
KD
mass transfer coefficient, kg/m2s (lb/ft2h)
lmtd
log mean temperature difference
lmwd
log mean humidity difference
m
mass flow rate, kg/s
n
number
P
power, W
p
pressure, Pa
Q
heat transfer rate, kW
t
temperature, oC
U
heat transfer coefficient, kW/m2.K
u
velocity, m/s
w
specific humidity, g H2O/kg.da
Greek Letters
Ø
relative humidity, %
Suffixes
a
cw
da
db
ewc
hme
thk
tot
tr
w
wb
air
cooling water
dry air
dry bulb
evaporative water cooler
heat and mass exchange
thickness
total
tray/trough
water/moisture
wet bulb
Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
1. INTRODUCTION
Evaporative cooling is an energy efficient alternative, which can be successfully employed in
hot and dry regions where difference between dry bulb temperature and wet bulb temperature
is significant. In addition to difference between DBT and WBT, thermal comfort for
occupants can be achieved where WBT is less than required temperature for thermal
conditions. The numerous advantages of evaporative cooling over the mechanical vapor
compressions systems such as low cost, fresh air supply, less power consumption make it a
viable option (Heidarinejad, G et al., 2008, 2009) for achieving the goal of thermal comfort.
It is also an environmental friendly approach of conditioning the air. Ideally, if no heat is lost
to the surroundings, air can be sensibly cooled, although it absorbs latent energy of water
vapor being picked up.
Many researchers have investigated evaporative cooling and a variety of designs have been
proposed. Aluminum plate-type heat exchanger was proposed by Watt and Brown (1997).
Scofield and DesChamps (1984) investigated the dry surface plate heat exchanger to be used
for direct/indirect evaporative cooling and showed 30% saving in the energy cost. AlJuwayhel et al. (1997) showed that the thermal effectiveness of two-stage evaporative cooler
was high with cooling tower. Thermal performance was shown to improve with increase in
packing thickness and mass flow rate in air pre-cooler. Many researchers have proposed
mathematical models by theoretically investigating different systems. In case of direct
evaporative cooling, air gets contaminated with impurities. Some of these models include
finite difference method based analysis by Baker and Shryock (1961), Kettleborough and
Hieh (1983) model using enthalpy potential, Dai and Samathy (2002) model for predicting
liquid gas interface temperature and correlations of heat transfer coefficients of wet and dry
surfaces by Maclaine-cross and Banks (1981).
Most of the designs and models proposed in literature have low packing efficiencies, thus
have lesser area for heat and mass exchange per unit volume. In the current paper we present
experimental and theoretical investigation of Diabatic Contacting device as an evaporative
cooler having high surface density, 410 to 550 m2 / m3 which is 120 to 185% higher than
conventional ones (Reddy 2003). Note that diabatic device refers to the device allowing heat
exchange with the surroundings contrary to adiabatic device where no heat transfer to or from
surrounding is allowed. High surface density of the heat and mass transfer surface helps keep
the unit compact. Air flow parallel to the wavy surface of the rotating disks helps achieve
high heat and mass transfer coefficients while keeping the pressure drops low 50 to100 kPa.
The system offers multiple benefits such as co-generation of cold water suitable for drinking
in air conditioning applications. In another application, circulation of sewage water in the
troughs will help reuse the waste water avoiding the need for fresh water. The remaining
waste water in the trough having high organic matter can be treated separately to reduce
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U.S.-India joint Center for Building Energy Research and Development (CBERD)
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Biochemical Oxygen Demands, BODs and Chemical Oxygen Demands, CODs, thus
reducing the cost of further water treatment while the same unit serves as an evaporative
cooler or evaporative condenser. The cold water can be utilized for providing the cooling
effect to structure thus reducing load on AC resulting in less power consumption and
operating cost. In addition to this, the design can find application with sea water for
desalination as well. Suitable plastic coatings can ensure reasonable life of various
components of the contacting device.
Multi stage contacting is possible with several diabatic contacting devices assembled in
series. Cooling capacity of the system can be increased by increasing the number of parallel
trays or increasing the length of each contacting tray. Assembly of the rotating disks dips in
the water in the trough as it rotates and then comes in contact with the air passing
perpendicular to the shaft. Evaporation of water cools the remaining water in the trough and
this in turn cools the fluid being passed through the cooling passages of the diabatic
contacting device. This cooling effect can be used to cool liquids, condense refrigerant,
building or process vapors.
Buildings consume 24% to 40% energy of the total energy consumption in a country (PerezLombard et al. 2008). Of this nearly half is consumed in meeting the thermal comfort. Most
of the cooling load that needs to be taken care by HVAC is the consequence of solar energy
gain. Readers can refer to Islam et al. (2009) for radiation data in middle-east countries.
This system can be integrated well with buildings reducing the cooling load without requiring
any blower or fan.
The system is economically viable and involves less maintenance cost. The analysis
presented in the paper confirms the benefit of indirect evaporative coolers for hot and humid
climate conditions.
2. DESIGN CONSIDERATIONS
2.1 Experimental Set-up
Rane et al, 2002 developed and tested the novel contacting device as an absorber and
regenerator of liquid desiccant bed dryer. In the current paper the design has been improved.
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U.S.-India joint Center for Building Energy Research and Development (CBERD)
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The EWC prototype used for the experiment has rotating disks of 142 mm diameter mounted
on a square shaft. The shafts rotate at 5 to 40 rpm using a low speed low wattage of 10 W
rotor motor. Aluminium troughs have water filled in with disks dipped typically 1/3rd of
height of water in trough as shown in Figure 1. The remaining portion is exposed to
incoming air for heat and mass exchange. Three passages are provided under the Aluminium
trough to uniformly circulate hot water running in building integrated closed loop. Water to
be cooled, transfers heat to the water in the trough. This circulated water cools down as it
flows through the passages and is obtained as chilled water which can be used for various
utilities. The water in the trough in turn transfers heat to the ambient air coming in contact
with the disk. Auxiliary power consumption is minimized as no blowers are used to circulate
the air. Figure 1 shows rotating disk mounted on a shaft. As the disk rotates, it picks up
water from the trough and brings it in contact with incoming hot and dry air. The injection
molded disks prevent any carryover of the liquid. Figure 3 is the set up used for carrying out
experiments with five trays in parallel.
Figure 1: Schematic of Rotating Disk in Trough
Design specifications of the experimental set up have been listed in Table 1.
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Table 1. Specifications of Indirect Evaporative Cooler
Parameter
Symbol
Unit
Description/Value
Trough length
Pitch circle diameter of trough
Inner hydraulic diameter of
trough channel
ltr
dtr.i
mm
mm
2133
150
dcp.i
mm
8.6
Number of trays in system
Type of contacting disk (CD)
Diameter of CD
Thickness of CD
Number of Contacting disk per
tray
Speed of contacting disk
ntr.dh
_
1
_
ddisk
thkdisk
_
mm
mm
plastic
142
1
ndisk.tr
_
500
rpmdisk
rpm
40
The schematic of the setup is shown in Figure 2. The BICL in the schematic represents the
closed loop which is extracting solar thermal load from structures. The figure shows an
arrangement of five troughs placed in parallel. Note that authors have presented analysis with
only one trough in the entire paper.
Figure 2: Schematic of Indirect Evaporative Cooler
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2.2 Instrumentation
a) One 24 DC motor with rated power of 36 W were used to rotate the shaft having
perforated disks mounted.
b) In order drive one DC motor, DC power supply with following specification was used:
TRIO PS/1AC/24DC/10
Order No : 2866323
Input 100-240 V ~ 3 to 1.5 A/50-60Hz
Operational voltage: 85 to 264 V D rating: <90V~2.5%/V
Output: 24V DC /10 A
Sno: 3012923231
Rev: 04
c) RTDs with an accuracy of ± 0.3 ºC have been used to measure the temperature of water
in trough, tw.tr and cooling water at IEC inlet, tcw1 and outlet, tcw2. For evaluating log
mean temperature/humidity difference, temperature of water at the sides, tw.tr.1 and tw.tr.2
have also been measured using RTDs.
d) A rotameter with an accuracy of ±2% of reading has been used to measure flow rate of
water. The range and resolution of the instrument is 0 to10 lpm and 0.1 lpm,
respectively.
e) An anemometer with an accuracy of ±2% of reading was used to measure the velocity
of the air at inlet and outlet to EWC. The range and resolution of the instrument are 0.4
to 30m/s and 0.1m/s respectively.
f) For pressure measurement, manometer is utilized with a resolution 1mm of water
column.
3. THEORETICAL INVESTIGATION
Heat transfer coefficient of the system has been evaluated based on the heat exchange area
provided by cooling passage. As mass transfer is taking place over the mass exchange area
provided by disks, the total area provided by the disks has been used to evaluate mass transfer
coefficient. Temperature and humidity obtained during the experimental investigation have
been utilized for evaluation.
m.w.disk.tot = rpm mw.disk ndisk.tr
lmtd = [(t1 – tw.tr.1) – (t2 – tw.tr.2)]/ [ln (t1 – tw.tr.1)/(t2 – tw.tr.2)]
Q = mcw cp.cw (tcw1- tcw2)
U = Q/ (Acp * lmtd)
lmwd = [(w1 – wtr.1) – (w2 – wtr.2)]/ [ln (w1 – wtr.1)/ (w2 – wtr.2)]
G = ma (w2 – w1)
KD = G/ ( Ahme lmwd)
1
2
3
4
5
6
7
.
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3.1 Assumptions
For analysis of the experimental results obtained, following assumptions have been made:
a) Injection molded disks providing heat and mass exchange area are acting as plain
disks.
b) The heat loss to surroundings from cooling water from back side to environment
is negligible.
Under the assumptions stated, energy released by cooling water should be equal to the energy
gained by water rotating with disks. This can be expressed in following manner:
Q = mw.disk.tot cp.w ( tw.tr.1- tw.tr.2)
8
Note that water holding capacity of single contacting disk is 1.2g. This together with rpm of
rotating disk can be utilized to evaluate the total mass of water rotating in a contacting
trough, using geometry presented in Figure 1. This analysis is omitted for the sake of brevity.
Under the above mentioned assumptions, theoretical value of heat and mass transfer
coefficient was estimated with different conditions. Average overall heat transfer coefficient
was obtained to be 8 kW/m2K and mass transfer coefficient to be 150 g/m2s based on the area
of the cooling passages.
Figure 3: Picture of Indirect Evaporative Cooler
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U.S.-India joint Center for Building Energy Research and Development (CBERD)
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4. RESULTS AND DISCUSSION
One trough was used in the system for experimentation as this was sufficient to take care of
the cooling requirement. Flow rate of the cooling water was kept at 5 lpm. As the tap water
was sufficient to provide required head, no pump was used. Natural wind at an average speed
of 1 to 4 m/s provided the required flux of air to draw heat and mass from the disks dipped in
water inside trough. Heat duty of 0.38 kW was observed to be removed from cooling water
at a pressure drop of 2.0 m of water column. Heat transfer coefficient Ui, 4.8 kW/m2K and
mass transfer coefficient, 16.5 g/m2s were evaluated based on the temperatures and humidity
obtained during experimentation. A typical result of experimentation is presented in Table 1
Table 1 a: Experimental results
t1
ºC
tw2
ºC
Ø1
%
w1
g/kg
h1
J/kg
t2
ºC
tw2
ºC
Ø2
%
w2
g/kg
h2
kJ/kg
tcw1
ºC
tcw2
ºC
tw.tr.1
ºC
tw.tr.2
ºC
ua
m/s
28.3
36.8
38.1
32.3
31.6
24.8
25.1
25.7
24.3
25.2
76
39.5
38
52.8
60.3
18.5
15.4
15.9
16.1
17.7
75.6
76.6
79.3
73.7
77.1
26.5
34.1
36.0
30.1
30.2
25.2
24.9
25.2
23.8
24.6
90
45
43
69
64
19.7
15.9
16.1
16.2
17.9
76.9
76.1
77.5
71.6
76.1
28.2
31.2
31.4
31.1
31
27.1
29.3
29.0
29.2
29.1
26.4
28.4
28.5
28.2
28.1
26.1
28.2
28.2
27.9
27.6
2.3
1.3
2
1.8
3
Table 1 b: Experimental results
lmtd
lmwd
mcw
Q
Ui
KD.
2
ºC
g/kg
kg/s
kW
kW/m K
g/m2s
0.96
2.52
0.08
0.38
4.8
16.5
1.7
8.98
0.05
0.63
4.1
33.7
1.45
9.47
0.12
0.72
5.9
100
1.89
8.33
0.15
1.1
1.1
59.8
2.12
6.51
0.18
1.4
12
29.0
Table 1 a: Experimental results (in Imperial Units)
t1
ºF
tw2
ºF
Ø1
%
w1
lb/ lbda
h1
BTU/ lb
t2
ºF
tw2
ºF
Ø2
%
w2
lb/ lbda
h2
BTU/ lb
82.9
98.2
100.6
90
88.9
76.4
76.6
78.3
75.7
77.4
76
39.5
38
52.8
60.3
0.0185
0.0154
0.0159
0.0161
0.0177
0.0325
0.0330
0.0341
0.0317
0.0331
79.7
93.4
96.8
86.2
86.4
77.4
76.8
77.4
74.8
76.3
90
45
43
69
64
0.0197
0.0159
0.0161
0.0162
0.0179
0.0331
0.0327
0.0333
0.308
0.0327
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tcw1
ºF
tcw2
ºF
tw.tr.1
ºF
82.8
88.2
88.5
88
87.8
80.8
80.8
83.3
82.8
82.6
79.5
83.1
83.3
82.8
82.6
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tw.tr.2 ua
ºF
ft/h
79
82.8
82.8
82.2
81.7
27165
15354
23622
21259
35433
Table 1 b: Experimental results (in Imperial Units)
lmtd
lmwd
mcw
Q
Ui
KD.
2
ºF
lb/ lbda
lb/h
BTU/h
BTU(th)/h ft ºF
lb /ft2h
1.7
0.003
635
1296.6
845
12.2
12.7
0.009
397
2150.0
722
24.8
15.6
0.009
952
2456.7
1039
73.7
5.4
0.008
1190
3753
194
44.1
5.5
0.007
1429
4776
211
21.8
The analysis can be confirmed by employing the energy equation, Eq 8.
rotating with disk was found out to be 362.7 g/s.
The total mass
On an average, solar insolation of 650 W/m2 falling on building of say 12 m2 area can easily
be met by the presented evaporative cooler with three trays in parallel, assuming a reflection
coefficient of 0.8. The heat transfer coefficients reported are based on the area of cooling
passage having hydraulic diameter of 8.61 mm.
Based on experimentally obtained mass transfer coefficient and heat transfer coefficient, the
potential of the system can easily be realized in different countries. Table 2 shows the monthly
averaged solar insolation for various cities.
Table 2. Climatic conditions in different cities
City
t1
ºC
tw1
ºC
Ø1
%
w1
g/kg
h1
kJ/kg
*I
MJ/m2/day
Bahrain
Riyadh
AbuDhabi
Doha
Baghdad
41.4
43.4
40.4
41.5
44.0
28.7
20.1
33.4
31.2
25.1
40.0
10.0
63.0
49.0
22.0
20.16
5.47
30.6
25.0
12.5
93.54
57.7
119
106
91.5
35.2
35.2
36.2
35.2
36.1
Wind
speed
ft/h
5.07
5.17
4.78
4.91
5.07
Note: * Have been taken from Islam et al., 2009.
Table 2. Climatic conditions in different cities (in Imperial units)
City
t1
ºF
tw1
ºF
Ø1
%
w1
lbm/lbm
h1
BTU/lbm
*I
BTU/ft2/day
Bahrain
Riyadh
AbuDhabi
Doha
Baghdad
106.5
110.1
104.7
106.7
111.2
83.7
68.2
92.1
88.2
77.2
40.0
10.0
63.0
49.0
22.0
0.0202
0.0055
0.0306
0.0250
0.0125
40.2
24.8
51.2
45.6
39.4
3101
3101
3190
3101
3181
For cities such as Doha, monthly average insolation is around 35.2 MJ/m2/day. Even after
considering a reflection coefficient of 0.8 from exposed surface of buildings, 7.04 MJ/m2/day
gets trapped in structures. This incurs huge cost in maintaining thermal comfort inside
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U.S.-India joint Center for Building Energy Research and Development (CBERD)
Page 8 of 10
Wind
speed
m/s
59882
61063
56457
57992
59882
buildings. Indirect evaporative cooler can remove the part or whole of that load.
Authors have also presented wind speed in Table 2. The system requires no fan or blower and
can easily run on natural winds. The obtained heat and mass transfer coefficients are with wind
speed of 0 to 4 m/s. As the wind data shows higher wind velocities in cities presented, higher
heat and mass transfer coefficients can be obtained. This makes the system an ideal choice for
cities such as Doha.
5. CONCLUSIONS
The paper presents experimental investigation of a novel indirect evaporative cooler which can
be integrated in buildings to meet the solar thermal load. Evaporative cooler can successfully
be employed to maintain thermal comfort in structures in various cities presented. The system
offers several benefits which can be enlisted as follows:
a) System has high mass transfer coefficient of average 47.8 g/m2s and heat transfer
coefficient of 5.58 kW/m2K
b) Pressure drop across the evaporative cooler in cooling water line can be used by
using multiple shorter trays in parallel.
c) System requires no fan or blower and can easily run on natural winds. This reduces
the energy throughput of the system making it cost effective.
d) It is easily scalable. Number of troughs can be increased or decreased depending
upon the requirements.
e) Carryover of water in the air stream is avoided by keeping gap between the rotating
disk assembly and the bottom of the tray mounted above.
The above mentioned advantages coupled with ease of fabrication make it a viable option for
cooling the structures simultaneously deriving multiple benefits in many parts of the world.
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Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
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15. Watt J R, Brown W K, 1997. Evaporative air conditioning handbook. Fairmont Press.
.
Annexure_051_March 2014
U.S.-India joint Center for Building Energy Research and Development (CBERD)
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