Teknomekanik, Vol. 6, No. 2, pp. 67-81, December 2023
e-ISSN: 2621-8720 p-ISSN: 2621-9980

Experimental investigation of effect of extent and position of bypass
openings on performance of a single unit liquid desiccant based indirect
evaporative cooler
Pamu Raja Naveen1,2*, Srinivas Kishore Pisipaty2 and Siva Subramanyam Mendu3
Department of Mechanical Engineering, Raghu Engineering College(A), Visakhapatnam, INDIA
Department of Mechanical Engineering, Andhra University College of Engineering, Andhra
University, Visakhapatnam, INDIA
3
Department of Mechanical Engineering, MVGR College of Engineering (A), Vizianagaram,
Andhra Pradesh, INDIA
1
2

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Published by Universitas Negeri Padang.
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* Corresponding Author: rjnvn15@gmail.com
Received Sep 02nd 2023; Revised Oct 21st 2023; Accepted Nov 03rd 2023
Cite this

https://doi.org/10.24036/teknomekanik.v6i2.25172

Abstract: In high temperature and high humidity zones, evaporative cooling is ineffective and
vapour compression systems are less energy efficient. Therefore, an alternative system is highly
desirable which is effective, energy efficient and enables the use of cheap and sustainable energy
sources. Indirect evaporative cooling helps in retaining humidity level of air, but is less effective in
attaining lower air temperatures. To mitigate this challenge, M-cycle indirect evaporative cooling
system helps in achieving sub-wet bulb temperatures. In this work, performance of a novel modified
indirect evaporative M-cycle cooling system assisted by 40% aqueous Li-Cl liquid desiccant is
experimentally investigated against various parameters. The cooling system used in this study is a
single unit system which can perform indirect evaporative cooling, liquid desiccant
dehumidification and internal cooling to the liquid desiccant. With an air velocity of 1 m/s at the
inlet, the introduction of openings in between inlet and exit of the cooling system has shown a
maximum improvement of 19.2% in its dew point effectiveness, with unaffected dehumidification
effectiveness. Furthermore, it is observed that the dew point effectiveness is decreased with the
increasing distance of openings from the inlet. The investigated cooling and dehumidification system
is useful as a pre-air-conditioner to conventional air-conditioning systems and also as a stand-alone
air-conditioning system.
Keywords: Liquid desiccant dehumidification; M-cycle; dew point evaporative cooler
1.

Introduction

Air conditioning is an essential requirement these days rather than a luxury. Apart from the
industrial purposes, it can be treated as a major energy consumption in domestic applications.
Conventional Vapour compression systems (VCR) are highly energy consuming and researchers are
trying to replace it with a less energy consuming alternative. In high temperature and low humidity
climates evaporative cooling is useful to some extent with reasonable comfort. Evaporative cooling
raises humidity of air which causes discomfort to the people in high temperature and high humidity
climates. To compensate for this drawback indirect evaporative cooling is an alternative method.
Although indirect evaporative cooling does not increase humidity of the air, however, this method
is not as efficient as direct evaporative systems in cooling the air. In this regard, Hafiz M.U. Raza et
al [1] fabricated 3 types of evaporative cooling systems viz., direct evaporative cooling (DEC),
indirect evaporative cooling (IEC) and regenerative cycle (M Cycle) evaporative cooling for testing
lab testing in an experimental work in Pakistan. Performances were compared and assessed. Direct
evaporative cooling can achieve a lowest temperature of wet bulb temperature (WBT) of air.
Temperatures achieved by indirect evaporative cooling are higher than those achieved by direct
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evaporative cooling. Many researchers worked on the practicability of indirect evaporative cooling
in varied climatic conditions. A research done by Yang Y et al. [2] fully analyzes and compares
indirect evaporative coolers with various designs and inlet air conditions. According to a review by
Uzair Sajjad [3], The mechanical vapor compression technology that is now used in the air
conditioning business can potentially be replaced with an M cycle cooling system.
An improvement of the indirect evaporative cooler is Maisotsenko cycle (M-cycle) that works on
latent heat of vaporization of water and combines heat transfer with evaporative cooling. While
with an indirect evaporative cooler, temperatures higher than wet bulb temperature are achieved,
M-cycle can produce sub-wet bulb temperatures near to dew point temperature. Like in an indirect
evaporative cooler, there are two channels, product air channel and working air channel, separated
by a good heat conducting wall. In M-cycle systems, a part of the product air is diverted into the
working air channel where it undergoes evaporative cooling, absorbing heat from air flowing
through the product air channel. Sub-wet bulb temperatures near to dew point temperature are
achieved due to the reason that the air is precooled before it enters the working channel. M-cycle
systems find applications in HVAC, cooling towers, gas turbines and cooling of electronic
equipment. In their study, Ragheb Raad et al. [4] simulated and evaluated the use of a back-worn
cooling dress which employs regenerative evaporative cooling technique and discovered this
method managed to dry air from this cloth than the single-channel design, resulting in a lower fabric
temperature. Ali Mohammad Ez Abadi et al. [5] modeled and experimentally validated five different
configurations of cooling systems based on regenerative cycle and concluded that these variations
may be useful in different climatic conditions in order to achieve comfort conditions. In their work,
Rubeena Kousar et al. [6] used experimentation to examine how a wide range of operational factors
might affect the efficiency of counter flow and cross flow M cycle designs in view of all aspects.
Imtiyaz Hussain et al [7] proposed a standby system in examining the effects of various climatic and
method related factors on the working of direct, indirect, and Maisotsenko systems for temperature
control in a variety of uses, including cultivation, animal care, electronic appliances, biotech, and
agri-business. With a recommendation for vertical tube arrangement over horizontal arrangement,
Xuchen Fan et al [8] constructed an innovative M-cycle based cooling tower and experimentally
investigated its cooling efficiency. Sergey Anisimov et al [9] conducted a theoretical simulation on
different variations in M-cycle cooling systems. Out of the variations, variation 2 - regenerative Mcycle showed lower outlet temperatures compared variation 3 – regenerative cooling system with
perforations. In the perforated system, small multiple holes are made in the wall separating the
product air and working air channels.
In high temperature and high humidity areas, dehumidifying the air is necessary to meet the comfort
needs of the occupants. Liquid desiccants (LD) are promising alternatives to conventional Vapour
compression systems in dehumidifying the air. Complete wetting of the surfaces has been a problem
in liquid desiccant systems. In their study, Ronghui Qi et al. [10] proposed a silica super-hydrophilic
blanket by the sol-gel method on pre-etched plastic surfaces to improve wetting performance, and
they observed that this innovative coating could significantly improve the wetting performance on
plastic surfaces. Because the way liquid flows, influences heat and mass transfer, Ronghui Qi et al.
[11] suggested a mathematical model to assess the disperse patterns of air-liquid flow down
convective absorption, for dehumidification, and they addressed the issue of completely wetting
the surfaces.
Hybrid systems that combine Liquid desiccant systems with conventional VCR systems are also
feasible and their performance evaluation is found in the literature. Experimental research has been
done by Kumar S et al.[12] on a liquid desiccant dehumidifier coupled with a vapour compression
refrigeration system. When compared to VCR alone, the highest gains of the system in COP and
MRR are 8.09% and 26.75%, respectively. Kashish Kumar and Alok Singh [13] suggest a
coalescence of a liquid desiccant air-conditioning system with a VCR machine as a good alternative,
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in hot and humid areas. Using an absorption system and vapor compression refrigeration system
with subcooling and a cascade mode for downsizing, Erjian Chen et al. [14] suggested a solarpowered hybrid system with air cooling in their work.
A different category of hybrid systems that combine direct and indirect evaporative cooling with
liquid desiccant dehumidification systems offer significant energy savings. Rubeena Kousar et al.
[15] conducted a thorough analysis on economics and effectiveness of different configurations of a
multistage dew point indirect evaporative cooler with solar desiccant system. Yanling Zhang et al.
[16] prepared and tested a theoretical heat and mass transfer model and performed a thorough
parametric analysis on an indirect evaporative cooled liquid desiccant air conditioning system with
a hexagonal plate heat exchanger that features both counter flow and cross flow. Some researchers
focused on environmental issues raised in air-conditioning. Reza Andika Setyadi and Rudy Setia
budy [17] addressed practical issues in using variable frequency drives of heating, ventilating and
air-conditioning in medical equipped health care centers. Fadhillah Ikhsan Dinul et al [18]
investigated the effectiveness of using NaOH and Na2CO3 solutions as CO2 absorbents.
One of the factors that deteriorates the cooling and dehumidification performance of liquid
desiccant systems is rise of liquid temperature due to latent heat effects. Internal cooling is often
provided by some means to overcome this problem. One of the arrangements for providing internal
cooling to liquid desiccant is to use cooling water tubes over which liquid desiccant flows. Richard
Jayson Varela et al. [19] analyzed the working of a novel adiabatic packed bed 3 fluid system with
fins, employing a unique ionic liquid desiccant solution. Cui et al. [20] designed and simulated a
system that integrates evaporative and desiccant systems. It combines the benefits of M-cycle
systems and desiccant liquid systems.
All the above research was carried-out with a common aim of replacing the conventional vapour
compression systems with low energy consuming systems, for air-conditioning applications. Most
of the work was done on evaporative cooling and liquid desiccant dehumidification systems owing
to their dependence on cheap and sustainable energy sources. Out of them, the systems which
incorporated evaporative cooling and liquid desiccant dehumidification in a single unit are attractive
because of their compact design. These systems suffer from inferior performance. Moreover, most
of the work done on such systems is theoretical and limited experimental research was carried out.
This shows the necessity of exploring and examining possible ways and modifications that can
improve the performance of liquid desiccant assisted M-cycle cooling systems. Furthermore,
experimental studies are much more needed to support the findings of theoretical and numerical
studies. To fill this gap, experimental investigation was carried out on such a system in the present
work. Many modifications in the previous designs were attempted to improve the cooling
performance and the results are presented. The effects of various parameters on the cooling and
dehumidification performance were observed and presented. It is possible to design liquid desiccant
dehumidification systems in such a manner that the liquid desiccant used can be provided internal
cooling with the help of an evaporative cooling in a regenerative way which is a more effective way
of evaporative cooling. Such a system is designed, fabricated and tested for its performance under
the effects of various parameters. Investigations were carried out by some researchers to assess the
performance of M-cycle systems by providing multiple holes in the wall separating the two channels
[9] . As a modification to these provisions, the influence of an intermediate opening provided at
various locations and with various dimensions, is experimentally observed along with many other
parameters that influenced its performance.

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e-ISSN: 2621-8720 p-ISSN: 2621-9980

2.

Material dan methods

2.1 Experimental setup

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The experimental setup for the present investigation is basically an M-cycle based parallel plate
evaporative cooling system assisted by liquid desiccant dehumidification showcased by the schematic
diagram (Figure.1&2). Figures depict the whole experimental setup, which includes an air
conditioning system and a liquid desiccant assisted indirect evaporative cooling system. The cooling
system for the current study is fabricated by stacking together thin rectangular aluminium sheets of
dimensions 1m X 0.2m, parallel to each other and 5mm apart, thereby making a number of parallel
channels meant for flow of air through them. Aluminium sheets are chosen because they are good
conductors of heat, available in very thin sheets and less costly. Alternate channels are meant for
the flow of product air and working air.

Figure 1 : Schematic representation of experimental unit
Air enters the product air channels at the front end of the setup and passes through the product air
channels. The air that enters the cooling system at the entrance is controlled by a fan speed
regulator. At the other end of the setup, by placing a partial restriction to the flow of air, a part of
the air leaves the system as product (supply) air and the remaining air enters the adjacent working
air channels. Air after flowing through the working air channels, leaves the cooling system at the
front end through the openings provided at the top cover as exhaust air. The portion of the air
diverted into the working channels is controlled by the sliding plate opening at the rear end. As the
aluminium sheets are very thin, there is a very little resistance to heat transfer across them [21] . In
the aluminium sheets, bypass openings are cut in various sizes and at various locations. Part of
product air passes into working air channels through these intermediate openings before reaching
the rear end. The effectiveness of the cooling system in reducing the temperature and humidity is
examined in relation to the size and location of these intermediate bypass openings.
The walls of the working air channels are maintained wet by pasting filter paper on the walls and a
continuous supply of water. Liquid desiccant is made to flow on the walls of the product air channels
as a thin film, over a part of the total length of the cooling system. Two containers are arranged at
an elevation to hold liquid desiccant and water from where these liquids flow into the cooling system
by gravity. Ball valves are provided to regulate the flow in the pipelines that carry liquids into the
system. Water flow is kept very low just to compensate for the evaporative loss. Water flow is kept
very low just to compensate for the evaporative loss. The desiccant liquid, after flowing through
the cooling system, is collected at the bottom which can be regenerated by some means and reused.
The air flowing through product air channels undergoes dehumidification by coming into contact
with the liquid desiccant flowing down over the walls by gravity. A 40% Lithium chloride aqueous
solution is used as liquid desiccant solution. The air flowing through the working channels
undergoes evaporative cooling, thus taking the heat of condensation of dehumidification and cools
the product air [22].
For measuring air flow rates, a fan type anemometer is used. To keep track of the condition of the
air, temperature and humidity monitoring equipment are kept at the entrance and exit of the
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cooling system. A vapor compression system-based air conditioner is used to maintain different
entry air conditions to the cooling system. The air-conditioning unit consists of refrigerant
evaporator coils, heaters, steam injector and a blower. The ambient air first enters the air
conditioner. Its condition is altered to the desired inlet condition by changing its temperature and
humidity ratio with the aid of the heater regulator, steam

Figure 2 : Experimental setup
2.2 Calculations involved
Performance is evaluated in terms of air exit temperature, air exit humidity ratio, Dew point
effectiveness and Dehumidification effectiveness. Dew point effectiveness and dehumidification
effectiveness given by the following equations 1 [23] & 2 [24] .
𝑇 −𝑇

𝐷𝑒𝑤 𝑝𝑜𝑖𝑛𝑡 𝑒𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒𝑛𝑒𝑠𝑠 𝜀𝑑𝑒𝑤 = 𝑇 𝑖𝑛−𝑇 𝑜𝑢𝑡
𝑖𝑛

(1)

𝑑𝑒𝑤

𝜔 −𝜔𝑜𝑢𝑡

𝑖𝑛
𝐷𝑒ℎ𝑢𝑚𝑖𝑑𝑖𝑓𝑖𝑐𝑎𝑡𝑖𝑜𝑛 𝑒𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒𝑛𝑒𝑠𝑠 𝜀𝑑𝑒ℎ = 𝜔 −𝜔
𝑖𝑛

𝑠𝑎𝑡,𝑇𝑠𝑜𝑙,𝑖𝑛

(2)

T stands for temperature and ω stands for humidity ratio of air, 𝜔𝑠𝑎𝑡,𝑇𝑠𝑜𝑙,𝑖𝑛 is the specific humidity
of air contacting with liquid desiccant at a given liquid inlet temperature under saturation condition.
Tin and Tout are air temperatures of entering air and leaving of the cooling system. The instrument
displays Relative humidity (∅) of air.
Vapour pressure in air, Pv is calculated by 𝑃𝑣 = 𝑃𝑣𝑠 × ∅

(3)

where Pvs is the vapour pressure in air under saturated conditions which is read from steam tables
corresponding to air temperature.
𝑃

𝑣
Humidity ratio can be calculated from 𝜔 = 0.622 × 𝑃 −𝑃
𝑡

𝑣

(4)

Where Pt is barometric pressure.
𝜔𝑠𝑎𝑡,𝑇𝑠𝑜𝑙,𝑖𝑛 can be calculated by

71

𝑃

𝑣
𝜔 = 0.622 × 𝑃 −𝑃
𝑡

𝑣

(5)

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where Pv in this equation is the vapour pressure in air that gets into contact with liquid desiccant
and comes to the liquid inlet temperature and becomes saturated. This is taken from the data
available in the literature [25].
3.

Results and discussion

Several factors affecting the performance of the cooling system are observed, and their effects are
tested experimentally. Performance is evaluated in terms of air exit temperature, air exit humidity
ratio, Dew point effectiveness and Dehumidification effectiveness. Inlet air velocity is kept at 1 m/s
throughout the experimental study.

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3.1 Effect of return air to supply air ratio
Air enters the supply air channels in the examined system and after passing through the channels, a
portion of the supply air is made to pass through return air channels and rest of the air leaves the
system, as outcome. This ratio of working air flow to product air flow ‘r’ influences the state of
the supply air and is varied in the range of 0.1 and 0.8. The relationship between working air to
product air ratio and exit air temperature and humidity ratio is shown in Figure 3.

Figure 3 : Outcome of working air to product air ratio
With higher values of the ratio ‘r’, outlet temperature is reduced. This is because greater quantity
of working air flowing through the working air channels, makes the evaporative cooling more
effective [26] . Greater working air flow can absorb most of the heat of condensation resulting from
the dehumidification process and significantly cool the product air. Dehumidification effectiveness
does not get affected significantly. This is due to the unvaried liquid desiccant film length. Entering
air temperature and specific humidity are kept at 30 oC and 16 g/kg. Extent of the desiccant solution
film is kept 0.5 m out of the total length of 1 m. These results are compared to theoretical results
of a more or less similar system in the literature [20] . Theoretical analysis was done using COMSOL
MultiPhysics. Average deviations of 16.6% in outlet temperatures, 42.6% in dew point
effectiveness, and 13.7% in dehumidification effectiveness are observed. These deviations can be
attributed to the assumptions taken in the theoretical analysis or to physical losses in
experimentation.
3.2 Effect of liquid desiccant flow length ratio
The relationship between exit air condition and liquid desiccant flow length is depicted in Figure 4.
Outlet specific humidity is directly affected by the length of liquid desiccant film, showing a
continuous reduction in humidity ratio. It is because of a greater area of desiccant film exposed to
air flow [27] . The intensity of the dehumidification process is directly proportional to area of
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desiccant film. This is also true in case of cross flow arrangement of air and desiccant liquid flows,
as in the examined system.

Figure 4 : Outcome of liquid desiccant flow length ratio

Figure 5 : Outcome of Liquid desiccant flow length
Outlet air temperature is lowered with an increase in desiccant flow length up to some length and
shows a rise in temperature beyond that. This is because greater exposure of air to desiccant
enhances the dehumidification process making air to become drier. Higher degree of dryness of
working air results in better evaporative cooling. Evaporative cooling is more effective with drier
air, to take away the heat condensation and to cool the product air. This is due to lower wet bulb
temperature of drier air. Later with further increase in desiccant flow length, condensation heat in
desiccant dehumidification dominates the enhanced evaporative cooling and results in a raise in
temperature. This change in the tendency is seen at 30% of the total length. Return air to supply
air flow rate ratio is maintained at 0.7. Inlet temperature and specific humidity are maintained as
30o C and 16 g/kg. Figure 5 depicts the effect of liquid desiccant flow length on dew point
effectiveness and dehumidification effectiveness. Dehumidification effectiveness is enhanced with
the increased length of desiccant flow. Dew point effectiveness is raised with increase in liquid
desiccant flow length up to some length and shows a fall beyond that. This is because dew point
temperature is inversely proportional to outlet air temperature if the inlet air condition is
maintained constant, according to the definition of dew point effectiveness.

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3.3 Effect of inlet air temperature and humidity ratio

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Working of the cooling system in varied conditions of ambient air is examined by providing inlet
air to the system through an air-conditioning unit. Refrigerant coils, heaters and steam injection
units bring the air to the test condition. Air is supplied at three different humidity ratios 12, 16 and
20 g/kg of dry air and at varied temperatures of 27.5, 30, 32.5, 35 and 37.5 o C. Return air to
supply air flow rate ratio is maintained as 0.7. Length of the liquid film is kept 0.5 m.

Figure 6 : Outcome of inlet air temperature and humidity ratio on outlet temperature
Figure 6 indicates the change of outlet temperature with inlet air temperature and humidity ratio.
Exit air temperature is proportional to inlet air temperature. Lower outlet air temperatures are
seen with low entering air humidity ratios. It is because with low humidity ratios, evaporative
cooling is more effective. Figure 7 shows the effect of inlet air temperature and specific humidity
on outlet humidity ratio and dew point effectiveness. At lower inlet air temperatures, dew point
effectiveness is higher because the condition of air is nearer to dew point. Dew point temperature
depends only on the humidity ratio and is independent of the dry bulb temperature of air. Any
decrease in temperature brings the condition of air close to its dew point at lower inlet air
temperatures, resulting in higher dew point effectiveness. This effect is more at higher entering air
specific humidity. At higher inlet humidity ratios, dew point effectiveness is obviously greater
because the entry condition of air is nearer to its dew point condition at a given temperature [28].
This can be observed from the psychrometric chart. Due to the positive slope of the saturation
curve, the inlet air condition is nearer to its dew point at higher humidity ratios. This effect is less
prominent at higher inlet temperatures. This because the closeness of the inlet air condition to its
dew point temperature due to the positive slope of the saturation curve, is proportionally small in
comparison to the large distance of

Figure 7 : Effect of inlet air condition on outlet humidity ratio and dew point effectiveness
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Figure 8 : Outcome of inlet air temperature and on dehumidification effectiveness
inlet condition from saturation curve at higher temperatures in the psychrometric chart. The
influence of inlet temperature of air on outlet air humidity ratio seen in Figure 7 depicts that, at
higher inlet air temperatures, dehumidification is not much effective resulting in higher outlet air
humidity ratios. Liquid desiccants are much more effective in dehumidification at lower
temperatures owing lower vapor pressures at the surface. Outlet air humidity ratios are obviously
higher at higher entry air humidity ratios. With reference to Figure 8, Dehumidification
effectiveness is higher at elevated inlet air temperatures. This is because of the fact that, at higher
temperatures, vapor pressures at liquid desiccant surfaces are higher and nearer to the vapor
pressure in inlet air. Any reduction in humidity brings the condition near to vapor pressure of the
liquid resulting in higher dehumidification effectiveness. Higher temperatures are favorable for
lower inlet air specific humidity with respect to dehumidification effectiveness. At higher
temperatures, vapor pressures are higher at the desiccant liquid surface and at lower humidity
ratios, vapor pressure in air is low, thus the vapor pressure difference is small and higher is the
dehumidification. For instance, with very low vapor difference in between inlet air and desiccant
liquid surface, dehumidification effectiveness is nearly 100% with little dehumidification, as per the
definition of dehumidification effectiveness.
3.4 Effect of bypass air flow rate
As an alteration to improve the performance of the plate type liquid desiccant assisted M-cycle
cooler, an opening is made in the wall separating the product air and working channels. Opening is
provided in various extents and at different locations in order to observe the effect of these
variations on dew point effectiveness and dehumidification effectiveness of the system. This
intermediate opening bypasses a fraction of supply air into the evaporative air channels before
reaching the rear end of the cooling system as seen in Figure 1. These bypass openings are kept at
0.6m from the front end of the cooling system. Rectangular openings are made through the entire
height of the channel and of different lengths so that varied quantities of bypass air are diverted into
working channels. The effect of bypass ratio, that is the ratio of quantity of air passed through the
bypass openings to the total quantity of working air, is observed. Figure 9 describes the outcome of
bypass air ratio on the leaving air condition at two varied working air ratios r=0.6 and r=0.7. A
drop in outlet air temperatures is observed with increasing bypass air ratio up to some value around
0.65, beyond which temperatures rise. The air passing through the working air channel to the left
of the bypass opening is a mixture of bypassed air and air coming from the upstream side. The
bypassed air is drier and at higher temperature as it passes over the liquid desiccant film. The air
approaching from upstream is relatively cooler and humid as it passes through product air channels
without liquid desiccant film and over the water film in the working air channel. Dryness results in
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better evaporative cooling in the working air channel downstream of bypass opening and lower
temperature of air results in better heat transfer across the channels. The air flowing through the
working air channel downstream of bypass opening is a mixture of these two streams and its
condition depends on the relative proportions of the constituent streams, resulting in the observed
variation of outlet air temperature. Outlet air humidity ratio is unaffected with varied bypass air
ratios as the length of the liquid desiccant film as well as working air to product air ratio are
constant.

Figure 9 : Effect of bypass airflow rate
3.5 Effect of position of bypass opening
The bypass openings provided which allow a fraction of supply air to pass into evaporative air
channels are made at different locations and the outcome of the position on the performance is
observed. Bypass openings are made at various distances from the front end of the system and the
ratio of this distance to the total length of the channels is taken as a parameter as seen in figure 10.
Liquid desiccant flow is limited to 50% of the total length. Bypass openings are provided at various
locations beyond desiccant liquid flow. Working air to product air flow rate is maintained 0.7 and
bypass air flow ratio as 0.65. A continuous rise in outlet air temperature is observed with the
location of bypass openings farther away towards the rear end. This is because the air flowing
downstream of the bypass opening is drier when the bypass opening is nearer to the front end of
the cooling system. Drier air undergoes evaporative cooling more effectively and absorbs most of
the heat of condensation. However, leaving air specific humidity is unaffected by the location of
bypass openings as the desiccant liquid film length is maintained constant.

Figure 10 : Effect of position of bypass opening
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Teknomekanik, Vol. 6, No. 2, pp. 67-81, December 2023
e-ISSN: 2621-8720 p-ISSN: 2621-9980

© The Author(s)
Published by Universitas Negeri Padang.
This is an open-access article under the: https://creativecommons.org/licenses/by/4.0/

4.

Conclusion

A Li-Cl liquid desiccant assisted M-cycle indirect evaporative cooler is investigated experimentally.
Performance of the cooler is examined against various parameters regarding air flow rates and
ratios, extent of liquid desiccant exposure to air, inlet air condition in terms of temperature and
humidity and also for the extent and location of intermediate openings provided in the plates
separating product air and working air channels. Performance of the cooling system is evaluated in
terms of dew point effectiveness and dehumidification effectiveness. Increased working air to
product air ratio resulted in enhanced dew point effectiveness but does not influence its
dehumidification effectiveness. Increased liquid desiccant flow length to total length ratio showed
a raise in dew point effectiveness up to some value around 0.35L and a fall beyond that and showed
a continued raise in dehumidification effectiveness. Higher inlet air temperatures resulted in a fall
in dew point effectiveness. This effect is more significant at higher inlet air specific humidity. Higher
entry air temperatures showed a rise in dehumidification effectiveness. This rise is steep at lower
inlet air humidity ratios. Higher inlet air humidity ratios resulted in higher dew point effectiveness
and lower dehumidification effectiveness. Wider bypass openings resulted in lower outlet air
temperatures up to some value of bypass air to working air flow ratio around 0.6 and showed a rise
in outlet air temperature beyond that. Dehumidification effectiveness is unaffected with bypass
openings. Position of bypass openings nearer to the exit of product air resulted in higher outlet
temperature continuously. These openings can only be provided beyond the length in which there
is liquid desiccant flow. However, dehumidification effectiveness is unaffected with the provision
of bypass openings. Most similar cooling systems combining evaporative cooling and liquid
desiccant dehumidification have two or three units. The discussed cooling system is incorporated
in a single unit in which air cooling, dehumidification and internal cooling to liquid desiccant are
performed. The incorporation of intermediate openings in between product air and working air
channels improved dew point effectiveness to a maximum of 19.2 %. However, dehumidification
is unaffected. The investigated cooling and dehumidification system can be used as a pre-airconditioner to conventional air-conditioning systems and also as a stand-alone air-conditioning
system.
Author contribution
Raja Naveen Pamu: data collection, data analysis, experimentation, draft preparation,
correspondence. Srinivas Kishore Pisipaty: supervision, reviewing and editing. Siva Subramanyam
Mendu: conceptualization, methodology, validation.
Funding statement
This research received no specific grant from any funding agency in the public, commercial, or notfor-profit sectors.
Acknowledgements
Left Blank
Competing interest
The authors declare that they have no known competing financial interests or personal relationships
that could have appeared to influence the work reported in this paper and they have not received
any research grants from finding agencies or financial support for attending symposia.

77

Teknomekanik, Vol. 6, No. 2, pp. 67-81, December 2023
e-ISSN: 2621-8720 p-ISSN: 2621-9980

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Teknomekanik, Vol. 6, No. 2, pp. 67-81, December 2023
e-ISSN: 2621-8720 p-ISSN: 2621-9980

Appendix
Uncertainty analysis
A methodical procedure described by Beckwith et al [32] is used to assess the flaws connected to
experimental analysis. The degree of uncertainty surrounding the data obtained using various
instruments is shown in Table 1. For each of the parameters utilized in the analysis, the maximum
potential error is calculated and compiled in Table 2.
Specific humidity, ω

a)

∅𝑝

𝑣𝑠
𝜔 = 0.622 × 𝑝 −𝜙𝑝
𝑡

© The Author(s)
Published by Universitas Negeri Padang.
This is an open-access article under the: https://creativecommons.org/licenses/by/4.0/

b)

,

𝑣𝑠

𝑈 2
𝑈𝜔
4𝑈 2
√( 𝜙 ) + ( 𝑇 ) = √(1.0101)2 + (4 × 0.1428)2 = 1.1604%
=
𝜔
𝜙
𝑇

Air flow rate, Q

𝑄 = 𝑙2 . 𝐶 ,

𝑈𝑄

𝑈

2

2𝑈

2

= √( 𝐶𝐶 ) + ( 𝑙 𝑙 ) = √(0.3334)2 + (2 × 0.1666)2 = 0.4702%
𝑄
𝑇 −𝑇

Dew point effectiveness, ϵdew

c)

2

𝑈𝑇 −𝑇

𝑈𝜖𝑑𝑒𝑤

𝑜
𝑖
𝜖𝑑𝑒𝑤 = 𝑇 −𝑇
𝑖

2

𝑈𝑇 −𝑇

𝑖 𝑑𝑒𝑤
= √( 𝑇 𝑖−𝑇 𝑜 ) + ( 𝑇 −𝑇
) = √(0.1835)2 + (−0.18348)2 = 0.2595%

𝜖𝑑𝑒𝑤

𝑖

𝑜

𝑖

𝑑𝑒𝑤

Dehumidification effectiveness, ϵdeh

d)

𝑈𝜖𝑑𝑒ℎ
𝜖𝑑𝑒ℎ

𝑑𝑒𝑤

𝑈𝜔 −𝜔

2

𝑈𝜔𝑖−𝜔𝑠𝑎𝑡,𝑇

𝑜
𝑖
= √( 𝜔 −𝜔
) + ( 𝜔 −𝜔
𝑖

𝑜

𝑖

𝜖𝑑𝑒ℎ =

𝜔𝑖 −𝜔𝑜
𝜔𝑖 −𝜔𝑠𝑎𝑡,𝑇𝑠𝑜𝑙

2
𝑠𝑜𝑙

𝑠𝑎𝑡,𝑇𝑠𝑜𝑙

) = √(1.007)2 + (−1.0502)2 = 1.455%

Table 1 : Uncertainties of instruments and properties

Instrument
name

Instrument’s
range

Measured
variable

LCD Digital
Thermometer 1
LCD Digital
Thermometer 2
LCD Digital
Humidity meter 1

-50 – 70o C

4

LCD Digital
Humidity meter 2

10 – 99 % RH

5

Fan anemometer

0 – 30 m/s

6

Steel rule

0 – 30 cm

Inlet air
temperature
Leaving air
temperature
Relative
humidity of
inlet air
Relative
humidity of
leaving air
Velocity of
air
Length

SNo
1
2
3

80

-50 – 70o C
10 – 99 % RH

0.1o C

Least. and
highest
values
measured in
the
experiment.
27.5 – 37.5o C

0.1428

0.1o C

17.6 – 28.8o C

0.1428

1 % RH

30.4 – 87.2%

1.0101

1 % RH

35.2 – 82.3%

1.0101

0.1 m/s

0 – 3 m/s

0.3334

0.5 mm

0 – 300mm

0.1666

Least
count of
the
instrument

Uncertainty
(%)

Teknomekanik, Vol. 6, No. 2, pp. 67-81, December 2023
e-ISSN: 2621-8720 p-ISSN: 2621-9980

Table 2 : Uncertainties of parameters and variables

© The Author(s)
Published by Universitas Negeri Padang.
This is an open-access article under the: https://creativecommons.org/licenses/by/4.0/

SNo
1
2
3
4

81

Variable
Specific humidity
Air flow rate
Dew point effectiveness
Dehumidification effectiveness

% Uncertainty error
1.1604
0.4702
0.2595
1.4549