A case study on energy savings in air conditioning system by heat recovery using heat pipe heat exchanger

IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
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Volume: 03 Issue: 01 | Jan-2014, Available @ http://www.ijret.org 12
A CASE STUDY ON ENERGY SAVINGS IN AIR CONDITIONING
SYSTEM BY HEAT RECOVERY USING HEAT PIPE HEAT
EXCHANGER
Tushar S. Jadhav1
, Mandar M. Lele2
1
Assistant Professor, Department of Mechanical Engineering, JSPM’s JSCOE, Pune, 411028, Maharashtra, India,
2
Professor, Department of Mechanical Engineering, MAEER’s MIT, Pune, 411038, Maharashtra, India,
Abstract
In air conditioning facilities with high outside air requirements such as cleanroom air conditioning systems, considerable energy
savings is possible by heat recovery using heat pipe heat exchanger (HPHX).The literature review indicated that the annual
energy saving analysis of air conditioning system with HPHX for Indian climatic conditions has not been performed. The paper
investigates the possible energy savings using HPHX for heat recovery in air conditioning system for a process air conditioning
facility in Pune city, India. The impact of number of rows of HPHX and variations in the operating air conditions on the savings
in cooling coil capacity is presented in this paper. The paper also reveals the comparative analysis of annual energy savings with
number of rows of HPHX for Pune weather conditions. The application of heat pipe heat exchanger for energy savings in air
conditioning system is strongly recommended.
Index Terms: Air conditioning, Energy savings, Heat recovery, Heat pipe heat exchanger
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1. INTRODUCTION
Heat pipe heat exchanger (HPHX) is an excellent device
used for heat recovery in air conditioning systems. Among
the many outstanding advantages of using the heat pipe as a
heat transmission device are constructional simplicity,
exceptional flexibility, accessibility to control and ability to
transport heat at high rate over considerable distance with
extremely small temperature drop [1]. Y.H. Yau and M.
Ahmadzadehtalatapeh [2] conducted a literature review on
the application of horizontal heat pipe heat exchangers
(HPHXs) for air conditioning in tropical climates. The
authors investigated the energy saving and dehumidification
enhancement aspects of HPHXs and made a summary of
experimental and theoretical studies on HPHXs. A literature
review on the application of HPHX for heat recovery
focused on the energy saving and the enhanced effectiveness
of the conventional heat pipe (CHP), two phase closed
thermosyphon (TPCT) and oscillating heat pipe (OHP) heat
exchanger was conducted by W. Srimuang and P.
Amatachaya [3]. G.D. Mathur [4] developed a computer
program to calculate the savings in the energy using HPHX
on the existing air conditioning systems. The investigation
was carried out for 33 United States cities with widely
different climatic conditions. J.W. Wan et al. [5]
investigated the effect of heat pipe air handling coil on
energy consumption in a central air conditioning system
with return air. Investigations were made to study the effect
of HPHX for energy savings in air conditioning applications
[6 – 10]. The literature review indicated that the annual
energy saving analysis of air conditioning system with
HPHX for Indian climatic conditions has not been
performed. This paper focuses on the use of HPHX for
energy savings in air conditioning system by considering a
case study of process air conditioning facility located in
Pune city, India. HPHX can be used for i) exchange of heat
between fresh outdoor air and conditioned return air (heat
recovery application) and ii) enhancing the dehumidification
capability of cooling coil as well as reheat savings
(dehumidification enhancement with reheat application)
[11]. However, the second application of dehumidification
with reheat is beneficial in situation wherein reheating is
necessary for maintaining required indoor air conditions.
This paper discusses the use of HPHX only for the heat
recovery application i.e. exchange of heat between fresh
outdoor air and conditioned return air, as it can be used for
all the air conditioning applications.
2. AIR CONDITIONING LOAD ANALYSIS
WITH AND WITHOUT HPHX
A case study on air conditioning load analysis with and
without HPHX for process air conditioning facility located
in Pune city, India is presented in this paper.
The process air conditioning facility under consideration has
an area of 590 m2
, height 3.6 m and occupancy 27. The Pune
outdoor air (OA) conditions used for air conditioning load
analysis is 40 0
C DBT and 28 % RH whereas the return
(room) air conditions is 23 0
C DBT and 50 % RH. The

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summary of the air conditioning load analysis without
HPHX (considered as Base case condition) is listed in Table
1.
Table - 1: Summary of air conditioning load analysis
without HPHX (Base case condition)
In conventional air conditioning plant, the return air and
outdoor air is mixed before the cooling coil. The cooled
supply air leaving the cooling coil is further delivered to the
room to pick up the sensible and latent loads in the room.
However by using HPHX, the cold exhaust air is used to
cool the incoming hot outdoor air. This results in cooling of
outdoor air which then gets mixed with return air. The
remaining process is similar to conventional air
conditioning.
The effect of number of rows of HPHX on the maximum
savings in cooling coil capacity for the base case condition
with HPHX is shown in Table 2. The values of effectiveness
for different number of rows of HPHX are referred using
product catalogue of S & P Coil Products Limited [11].
Table - 2: Effect of number of rows of HPHX on the
maximum savings in cooling coil capacity for base case
condition with HPHX
The effectiveness of HPHX is ratio of actual heat transfer to
the maximum possible heat transfer. Since HPHX involves
recovery of only sensible heat, therefore the effectiveness of
HPHX can also be defined as ratio of actual temperature
drop to maximum possible temperature drop [4, 10].
Since the savings in cooling coil capacity due to HPHX is
only due to sensible heat, hence the savings in kW is given
by
Savings in Cooling coil capacity, kW = 0.02044 x OA x 60
x (TOA – TLA)
where OA = Outside air in m3
/s.
Referring to Table 2, in comparison to the base case
condition, we see that there is a saving of more than 3 TR on
cooling coil capacity when HPHX with 4 or more rows is
installed. This results in significant savings in the initial cost
and more important in the operating cost. The variation in
maximum savings is between 6.9 to 8.2 % when number of
rows of HPHX is more than 6. To study the variations in
maximum cooling coil capacity and maximum savings in
cooling coil capacity, further investigations are performed
by varying the return air conditions whereas the outdoor air
conditions are maintained the same (40 0
C DBT, 28 % RH
and 0.8 m3
/s).
The following cases are studied.
Case I: Varying the return air DBT between 21 – 25 0
C,
keeping RH constant at 50 %. The summary of air
conditioning load analysis for various conditions of Case I is
shown in Table 3.
Table – 3: Summary of air conditioning load analysis for
various conditions of Case I
Details
DBT WBT RH W
Air
Qty
Maximum
Cooling
Coil
Capacity
0
C 0
C % g/kg m3
/s TR kW
OA 40.00 24.22 28.00 13.93 0.80
RA 23.00 16.07 50.00 9.39 8.03
Total 8.83 51.7 182
ROWS
of
HPHX
ε
HPHX
DBT of
Outside Air
leaving
HPHX, 0
C
Maximum
Savings in
Cooling
Coil
Capacity
%
Savings
kW TR
Without
HPHX
__ 40 __ __ __
1 0.33 34.4 5.50 1.56 3.0
2 0.49 31.7 8.17 2.32 4.5
3 0.59 30.0 9.84 2.80 5.4
4 0.66 28.8 11.01 3.13 6.1
6 0.75 27.3 12.51 3.56 6.9
8 0.8 26.4 13.34 3.79 7.3
10 0.83 25.9 13.84 3.94 7.6
12 0.85 25.6 14.18 4.03 7.8
14 0.87 25.2 14.51 4.13 8.0
16 0.89 24.9 14.84 4.22 8.2
Details
Return air (RA) conditions
23 0
C
DBT
and 50
% RH
24 0
C
DBT
and 50
% RH
25 0
C
DBT
and 50
% RH
22 0
C
DBT
and 50
% RH
21 0
C
DBT
and 50
% RH
Total air
required,
m3
/s
8.83 8.17 7.59 9.58 10.43
Maximum
Cooling coil
capacity, TR
51.7 50.3 48.9 53 54.3
% change in
air quantity
with
reference to
base case
__
- 7.47 - 14.04 + 8.49 + 18.12
% change in
cooling coil
capacity
with
reference to
base case
__ - 2.70 - 5.41 + 2.51 + 5.02

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Case II: Varying the return air RH between 45 – 55 %
keeping DBT constant at 23 0
C. The summary of air
conditioning load analysis for various conditions of Case II
is shown in Table 4.
Table – 4: Summary of air conditioning load analysis for
various conditions of Case II
Details
Return air (RA) conditions
23 0
C
DBT
and
50 %
RH
23 0
C
DBT
and
52.5 %
RH
23 0
C
DBT
and
55 %
RH
23 0
C
DBT
and
47.5 %
RH
23 0
C
DBT
and
45 %
RH
Total air
required,
m3
/s
8.83 8.83 8.83 8.83 8.83
Maximum
Cooling coil
capacity,
TR
51.7 51.3 51 52 52.3
% change in
air quantity
with
reference to
base case
__ __ __ __ __
% change in
cooling coil
capacity
with
reference to
base case
__ - 0.77 - 1.35 + 0.58 + 1.16
Fig – 1: Comparison of maximum savings in cooling coil
capacity in TR Vs No of rows of HPHX for different return
air (RA) conditions at same RH.
Figure 1 shows comparative analysis of maximum savings
in cooling coil capacity for various combinations of Case I.
The values of maximum savings in cooling coil capacity in
Fig. 1 are calculated similar to those shown in Table 2.
3. RESULTS AND DISCUSSIONS
The lower DBT (21 0
C) proves beneficial in lowering the
temperature of air entering the cooling coil via HPHX. This
results in more savings in the cooling coil capacity in
operating conditions, as seen from Fig. 1. However, from
Table 3, the increase in initial cooling coil capacity at RA
condition of 21 0
C DBT and 50 % RH compared to the base
case condition is 2.6 TR whereas from Fig. 1, the
comparative savings in cooling coil capacity using HPHX at
21 0
C DBT and 23 0
C DBT is 0.5 TR when number of rows
of HPHX is 16. Thus, considering the overall savings, lower
DBT is not beneficial. Referring to Table 4, we see that the
variation in maximum cooling coil capacity at 23 0
C DBT
and 55 % RH in comparison to the base case is 0.7 TR. This
will help in reducing the initial and operating cost of cooling
coil. From Table 3 and 4 and Fig. 1, it is observed that out of
all the RA conditions studied in this paper, the RA condition
of 23 0
C DBT and 55 % RH is the best possible condition
for getting maximum savings in the initial and operating
cost of cooling coil with HPHX.
The HPHX savings for heat recovery between outdoor air
and return air are associated with sensible heat. Hence in
Case II, the maximum savings in cooling coil capacity using
HPHX remains the same in comparison to the base case
condition, as the DBT is same.
The savings in cooling coil are significant when the rows of
HPHX are more than 6. Hence, further annual energy
savings will be estimated for HPHX with 6 and more rows
and with RA DBT = 23 0
C.
4. ANNUAL ENERGY SAVINGS FOR PUNE
CONDITIONS
Fig – 2: Annual DBT temperature variation for Pune city
[12, 13]
Figure 2 shows the annual DBT temperature variation for
Pune city [12, 13]. Referring to the weather data files for
Pune city [12, 13] we see that out of annual 8760 hours, the
total number of hours when the minimum outdoor DBT in
Pune is 25 0
C DBT or more is 3670 hours. This accounts for
approximately 42 % of the annual period. Hence we can
achieve tremendous energy savings by utilizing HPHX for
heat recovery application. The annual energy savings for
Pune city using HPHX considering that minimum outdoor

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air DBT = 25 0
C or greater is summarized in Table 4. As
seen from Table 4, the annual energy savings will be huge
when the outside air requirement is more and when the air
conditioning is 24 hours x 7 days application.
Table - 4: Annual energy savings for Pune conditions
CONCLUSIONS
The paper discusses the benefits of HPHX for a process air
conditioning facility located in Pune city, India.
The annual energy savings considering only heat recovery
application is significant for Pune city and thus proves
beneficial in facilities where ventilation air requirements are
huge such as cleanroom air conditioning.
Outdoor and return DBT, outdoor and return air quantities,
effectiveness of HPHX are the governing parameters that
affect the overall savings in cooling coil capacity. In
addition, HPHX used for dehumidification enhancement
along with reheat application will also help in reducing the
energy consumption of the air conditioning system.
The biggest advantage of using HPHX is that it does not
require any external power for its operation. Hence further
investigations on selection of working fluid, pressure drop
calculations, additional fan power consumption and payback
period needs to be done for different rows of HPHX for
both, heat recovery application as well as dehumidification
enhancement with reheat application.
REFERENCES
[1] S.W. Chi, Heat Pipe Theory and Practice: A Sourcebook,
Hemisphere Publishing Corporation, (1976).
[2] Yau Y.H and M. Ahmadzadehtalatapeh, A review on the
application of horizontal heat pipe heat exchangers in air
conditioning systems in the tropics, Applied Thermal
Engineering, Vol.30, (2010), pp. 77 – 84.
[3] A. Mardiana-Idayu and S.B. Riffat, Review on heat
recovery technologies for building applications, Renewable
and Sustainable Energy Reviews, Vol. 16 (2012), pp. 1241 –
1255.
[4] G.D. Mathur, Predicting yearly energy savings using
BIN weather data with heat pipe heat exchangers, in
Proceeding of the Intersociety Energy Conversion
Engineering Conference, Honolulu, USA, Vol. 2, (1997),
pp. 1391– 1396.
[5] J.W. Wan, J.L. Zhang, W.M. Zhang, The effect of heat
pipe air handling coil on energy consumption in central air-
conditioning system, Energy and Buildings, Vol. 39, (2007),
pp. 1035 – 1040.
[6] Yau Y.H and M. Ahmadzadehtalatapeh, Predicting
yearly energy recovery and dehumidification enhancement
with a heat pipe heat exchanger using typical meteorological
year data in the tropics, Journal of Mechanical Science and
Technology, Vol. 25, No.4, (2011), pp. 847 – 853.
[7] Y.H. Yau, Application of a heat pipe heat exchanger to
dehumidification enhancement in a HVAC system for
tropical climates – a baseline performance characteristics
study, International Journal of Thermal Sciences, Vol. 46,
(2007), pp. 164 – 171.
[8] Y.H. Yau, The use of a double pipe heat exchanger
system for reducing energy consumption of treating
ventilation air in an operating theatre–A full year energy
consumption model simulation, Energy and Buildings, Vol.
40, (2008), pp. 917 – 925.
[9] M. Ahmadzadehtalatapeh and Yau Y.H, The application
of heat pipe heat exchangers to improve the air quality and
reduce the energy consumption of the air conditioning
system in a hospital ward—A full year model simulation,
Energy and Buildings, Vol. 43, (2011), pp. 2344 – 2355.
[10] M.A. Abd El-Baky, M.M. Mohamed, Heat pipe heat
exchanger for heat recovery in air conditioning, Applied
Thermal Engineering Vol.27, (2007), pp. 795 – 801.
[11] Product Catalogue, S & P Coil Products Limited.
[12] Energy Efficiency and Renewable Energy (EERE),
Energy plus energy simulation software - Weather data.
[13] National Renewable Energy Laboratory (NREL),
Dview – Hourly simulation software.
Nomenclature
DBT Dry bulb temperature
HPHX Heat pipe heat exchanger
OA Outdoor air
RA Return (Room) air
RH Relative humidity
TLA DBT of air leaving the HPHX and
entering the cooling coil
TOA DBT of outdoor air entering the HPHX
Considering OA DBT = 25 0
C or greater
(Total 3670 hours out of 8760 hours)
City Pune
OA Air Qty in m3
/s 0.8 0.8 0.8 0.8 0.8 0.8
Return Air (RA)
DBT 0
C
23 23 23 23 23 23
No. of Rows of
HPHX
6 8 10 12 14 16
εHPHX
0.75 0.8 0.83 0.85 0.87 0.89
Total Energy
Savings, kWhr
16812 17933 18605 19054 19502 19950
Total Energy
Savings, Tonhr
4780 5099 5290 5418 5545 5672
% Savings with
reference to
6 row HPHX
__ 6.7 10.7 13.3 16.0 18.7

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TR Ton of refrigeration
TRA DBT of return (room) air
W Humidity ratio
WBT Wet bulb temperature
εHPHX Effectiveness of heat pipe heat exchanger
BIOGRAPHIES
Tushar S. Jadhav has completed his
Masters in Mechanical Engineering
with specialization in refrigeration
and air conditioning. At present, he
is pursuing his Ph.D. in the area of
energy savings in air conditioning.
His areas of interest include heat
pipes, evaporative cooling,
refrigeration and air conditioning.
Mandar M. Lele has received his
Ph.D. in 2006 from Indian Institute
of Technology, Bombay. His
teaching and research interests lie
in the areas of thermodynamics,
heat transfer, refrigeration and air
conditioning, cryogenics, energy
conservation.

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A case study on energy savings in air conditioning system by heat recovery using heat pipe heat exchanger