numerical investigation on phase change process of...
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* Corresponding author e-mail: [email protected] Journal access: www.adpublication.org Tel.: +91 261 220 1966 © 2016 A D Publication. All rights reserved
ID: ICFTESPM2016CP140254 Proceeding of Conference, 23rd December,2016
International Conference on
Futuristic Trends in Engineering, Science, Pharmacy and Management
ISBN: 978-81-933386-0-5
Numerical Investigation on Phase Change Process of Spherical and
Rectangular Shaped Macro-encapsulated Phase Change Material
Sagar D Chaudhari, Manish K Rathod *
Mechanical Engineering Department, S V National Institute of Technology, Surat, India-395007
A B S T R A C T : Macro-encapsulation is a common way of encapsulating the Phase Change Material (PCM) for thermal energy storage applications. The container shape may be spherical, tubular, cylindrical or rectangular. The study of melting phenomena of PCM needs to be understood for the design of thermal storage systems. The constrained melting of PCM inside rectangular and spherical capsule using paraffin wax is investigated by CFD analysis. Frontal area, volume is kept same in rectangular and spherical geometry so in order to keep the mass of PCM same in both the cases. This ensures the effective comparison can be done for optimization of macro-encapsulated system. It is observed that melting time required is less in case of rectangular as compared to spherical shaped macro-encapsulated PCM.
© 2016 A D Publication. All rights reserved
Keywords:
Macro-encapsulation, Phase Change Material, Melting Time
1. Introduction Energy plays a major role in the economic prosperity and the technological competitiveness of a nation.
World energy outlook reported that the total energy demand in the countries like India and China is
expected to increase from 55% in 2010 to 65% in 2035 [1]. The utilization of readily available energy of
fossil fuels is increasing almost exponentially due to multiplying population, rapid urbanization and
progressing economy. The resource augmentation and growth in energy supply have, however, failed to
meet this increasing energy demand. Further, the energy demand in the commercial, industrial, public,
residential and utility sectors varies on a daily, weekly and seasonal basis.
Thus, the usage of non-conventional energy sources especially solar energy is essential in wide
range of applications both in urban and rural regions. However, solar energy is intermittent, unpredictable,
and available only during the day. Hence, the successful application of solar energy depends to a large
extent on the method of energy storage used. The latent heat energy storage is the most promising
means of thermal energy storage. However due to low thermal conductivity of PCM and thermal stability
over extended thermal cycles the use of latent heat storage unit (LHSU) is not as per expected [2-3].This
requires the heat transfer enhancement in such systems. The main heat transfer enhancement
techniques are using fin configuration, inserting high thermal conductivity metal matrix into a PCM,
dispersing the PCM with a high thermal conductivity particles and by micro-encapsulation of the PCMs
[4].
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Out of many heat transfer enhancement techniques, macro-encapsulation of PCM is a new and
immersing technique [5]. Macro-encapsulation is in some form of self-assembled structure or a package
such as tubes, pouches, spheres, panels or other receptacle. These containers usually are larger than 1
cm in diameter and can be incorporated in building products as well. The main advantage of the macro-
encapsulation is its applicability to both liquid and air as heat transfer fluids and easier to ship and handle.
Macro-encapsulation of the PCM helps to overcome the barrier of low thermal conductivity by increasing
heat transfer rate. It is also helpful in forming a barrier and protecting the PCM from the outside
environment and controlling the volume changes of the PCM. It has developed interest in several
researchers especially because it can be cost effective comparative to other techniques. Spherical and
rectangular shape for encapsulation of PCM is mostly used. Since the heat transfer is dependent on
surface area there is need to investigate optimized shape for container.
Khot et al [6] investigates constrained and unconstrained melting of PCM inside a spherical
capsule using paraffin wax. They observed that, the solid PCM is restricted from sinking to the bottom of
the spherical capsule in constrained melting. They also reported that unconstrained melting results in
faster rate than constrained melting due to higher natural convection. Regin et al [7] experimentally and
numerically examined the heat transfer performance of a spherical capsule using paraffin wax PCM
placed in a convective environment during the melting process. They also observed that shorter time for
melting and higher time averaged heat flux occurs in the capsule of smaller radius and for higher Stefan
number. Maheswari and Reddy [8] investigated experimentally and numerically packed bed of spherical
macro-encapsulated PCM .They also compare results for paraffin wax and stearic acid with different sizes
of the spheres and a fin inserted in the sphere. It was observed that, the time taken to complete the
phase change in the sphere changes as the size changes and paraffin takes less time compared to
stearic acid in this cases. When a rectangular cross sectional copper as a fin is inserted into the sphere
radially the melting time taken is reduced. Khodadadi and Zhang [9] also considered the effects of natural
convection on the constrained melting of phase change materials within spherical containers, also states
that during the initial melting process, the conduction mode of the heat transfer is dominant. As the
buoyancy-driven convection is strengthened due to the increase in the melting zone, the process at top
region of the sphere is much faster than at the bottom due to the increment of the conduction mode of
heat transfer. Ismail and Henrique [10] developed parametric model for the study of the solidification of a
PCM in a spherical shell. Model is developed for pure conduction in PCM subjected to constant wall
temperature (CWT) boundary condition for spherical shaped macro-encapsulation. They found that the
increase of the size of the sphere leads to increasing the time for freezing. They also studied different
shell materials for encapsulation and concludes that shell material affects the solidification time. Freezing
was faster for metallic material (Cu, Al) followed by polyethylene, acrylic and PVC. However, the time
difference between these materials mainly metallic and non metallic was small, that still makes non
metallic capsules attractive.
Nomenclature
Cp Specific heat of PCM, Jkg-1 K-1 Liquid fraction, dimensionless
k Thermal conductivity, Wm-1 K-1 Density, kgm-3
H Specific enthalpy, Jkg-1 μ Dynamic viscosity, kgm-1 s-1
L Latent heat, Jkg-1 V fluid velocity vector
P Pressure, Pa C mushy zone constant
t Time, s g Gravitational acceleration m/s2
V Velocity, ms-1
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Lacroix [11] presented mathematical model for the contact melting of a sub-cooled PCM inside a
heated rectangular capsule. They observed that the melted fraction from close contact melting at the
bottom of the capsule is larger, by an order of magnitude, than that from the conduction dominated
melting at the top. The melting process is chiefly governed by the magnitude of the Stefan number (Ste).
It is also strongly influenced by the side dimensions of the capsule. Muhammed et al[12] analyzed
numerically and visualized the melting characteristics of a phase change material (PCM) in different
geometries i.e. rectangular block, sphere ,cylinder and configurations using paraffin wax. Authors studied
the effect of aspect ratio on melting time. They observed that melting time strongly depends on the wall
temperature and when wall temperature changes meting time also changes in all shapes and
configurations. Jellouli [13] analyzed numerically the melting process of PCM in a horizontal cavity heated
from below, driven by the coupling of transient heat conduction in the solid phase and steady state
laminar natural convection in the liquid phase with one of the boundaries of the solution domain that
moves. The agreement between the results and those of study reported earlier was found to be good.
They stated that, as the melt layer thickness increases with time, natural convection appears in the liquid
phase and the non-uniform heat transfer distribution along the interface which reaches a steady position
when the heat transfer from the liquid phase is compensated by the heat transfer to the solid phase.
Literature shows that most of researchers focused the work in the field of macro-encapsulation
using spherical and rectangular shaped capsule. Very few literatures are found in which other than these
two shapes are considered for the analysis. The performance of the macro encapsulated PCM is
established by the key parameters like aspect ratio, boundary conditions, geometries for encapsulation,
on melting rate of PCM. However, there is need to compare/optimise these shapes for application in
thermal energy storage systems for enhancement purpose. Thus, the main objective of this research
paper is to establish the thermal performance of the PCM filled in spherical and rectangular capsule using
numerical analysis. Conceptual understanding generated through the present investigations can help to
develop LHSU for solar applications, waste heat recovery, load leveling for power generation, building
energy conservation and air-conditioning applications.
2. CFD Modelling of Macro-encapsulated PCM
2.1 Model
In order to investigate performance of PCM encapsulated in spherical and rectangular geometry, a
numerical model is developed. The physical parameters of sphere and rectangle are chosen in such a
way that frontal area and volume of the container remains same. Thus, diameter of sphere is taken as 50
mm while dimensions for rectangle are considered as 40 mm x 50 mm. The model for the numerical study
was created using pre-processor software GAMBIT 2.4.6. The GAMBIT model i.e. meshed domain is then
exported to FLUENT for processing. The pressure based unsteady solver along with solidification/melting
model with mushy zone constant of 100000 (default value, suitable for most of the engineering
applications) in FLUENT 6.3.26 was utilized for solving the governing equations. The first order upwind
differencing scheme was used for solving the energy, momentum equations and presto for pressure
discretization.
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Fig 1. Physical model of containers
(a) (b)
Fig 2. Meshing of the model (a) Spherical Model, and (b) Rectangular Model
2.2 Governing equations
For transient 2-D heat transfer problem in latent thermal energy storage unit the governing equations are energy, momentum and continuity equations. The segregated solver is only available for solving the equations in solidification/melting model. In order to simulate phase change of PCM in above geometries, enthalpy-porosity method is used. The viscous dissipation term is considered negligible. Thus the viscous incompressible flow and the temperature distribution in the domain are described by the Navier-Stokes and thermal energy equations, respectively. The governing equations used in melting are as follows - Continuity equation :
.( ) 0Vt
(1)
Momentum equation :
2( ).( )
VV P V g S
t
(2)
2)
3
(1CS V
(3)
The momentum source term, S, contains contributions from the porosity of the mushy zone, the surface tension along the interface between the two phases, and any other external forces per unit volume. Momentum sink terms are added to the momentum equations to account for the pressure drop caused by the presence of solid material. Energy equation :
( ).( ) .( )
HVH k T
t
(4)
PCM PCM
Sphere D= 50 mm 40 mm
50
mm
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H is the specific enthalpy, which is defined as the sum of the sensible enthalpy (h) and the latent heat (ΔH)
H h H (5)
where,
ref
T
ref p
T
h h C dT (6)
The content of the latent heat can vary between zero (for a solid) and L (for a liquid):
H L (7)
The liquid fraction (β) can be written as:
0
1
solidus
liquidus
solidussolidus liquidus
liquidus solidus
if T T
if T T
T Tif T T T
T T
(8)
The above model is developed considering following assumptions [14].
PCM is homogeneous and isotropic.
Initially PCM is in the solid phase for melting with uniform temperature.
Thermo physical properties of the PCM are constant.
Boundary condition is constant wall temperature.
The flow in the molten PCM is considered laminar, incompressible.
The viscous dissipation term is considered negligible.
2.3 Validation
Figure 3 Validation results (a) Experimental result by Gau and Viskanta [16] (b) Numerical results
obtained by present study
In order to validate the numerical model developed for rectangular and spherical capsule filled with PCM,
the present model is first validated with the experimental results published in previous research papers.
Fig. 3 shows experimental result obtained by Gau and Viskanta [16] and numerical simulation result from
present study for different melt front position.The results obtained from developed code are validated with
results obtained by Gau and Viskantha [16]. According to this, a rectangular cavity of 8.89 cm width and
6.35 cm of height is considered. Gallium is used as phase change material. The value of Density, kg/m3;
Thermal conductivity, W/mk; Latent heat, J/kg; Specific Heat, J/kg K; Dynamic viscosity, kg/ms; Melting
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temperature, K; Coefficient of thermal expansion of Gallium are 6093, 32.0, 80160, 381.5, 0.00181,
302.78, 0.00012 respectively. Top and bottom wall are kept insulated. Left wall is given constant
temperature 311 K and right wall is kept at 301.3 K. Initial temperature of gallium is taken as 301.3 K.
Figure 4 Validation results (a) Numerical result by Darzi et al [17] (b) Numerical results obtained by present study
Fig. 4 shows numerical result obtained by Darzi et al [17] and numerical results obtained from present
study. The results obtained from developed code are validated with results obtained by Darzi et al [17].
According to this concentric cylinder with internal diameter and outer diameter as 20 mm, 40mm
respectively is considered. N-eicosane is used as PCM. The value of Density, kg/m3; Thermal
conductivity, W/mk; Latent heat, J/kg; Specific Heat, J/kg K; Dynamic viscosity, kg/ms; Melting
temperature, K; Coefficient of thermal expansion of N-eicosane are 770, 0.1505, 247600, 2460, 0.00385,
309, 0.0009 respectively. The solid PCM was sub-cooled at 308.15 K where the wall temperature of inner
cylinder fixed to the 329.15 K. Initial temperature is taken as 308.15 K.
From figs.3-4, it can be concluded that simulation results show good agreement with
experimental and numerical results. Thus, methodology used for solution is correct and further study is
based on same solution methodology.
3. Results and Discussion
The main objective of the present research paper is to develop the numerical models for rectangular and
spherical capsule filled with the PCM and compare the performance of the same in the form of melting
rate and heat transfer characteristics. For that a case study is considered in which paraffin wax is filled in
rectangular and spherical capsule as a PCM. Boundary wall of the encapsulated PCM is subjected to
620C and is assumed to be constant throughout the surface. Table 1 shows the thermo-physical
properties of paraffin-wax PCM.
Table 1 : Thermo-physical properties of Paraffin-wax [15]
Property Value
Density 861 kg/m3
Thermal conductivity 0.4 W/mK
Specific Heat 1850 J/kgK
Viscosity 0.00342 kg/m-s
Thermal expansion coefficient 0.002 /0C
Melting Heat 213000 J/kg
Solidus temperature 58 0C
Liquidus temperature 60 0C
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Fig 5 . Contours of static temperature for sphere and rectangle at 10 min
Fig 6. Contours of liquid fraction for sphere and rectangle at 10 min
Fig. 5 shows the temperature distribution of PCM filled in sphere and rectangle after 10 min. From the
figure it is observed that PCM in vicinity of boundary starts melting uniformly. Thus, it is concluded that
conduction mode of heat transfer is dominant compared to natural convection, initially. The same results
can also be reflected from the fig. 6. Fig. 6 shows contours of liquid fraction for sphere and rectangle after
10 min. From both the figs., it is observed that melting of PCM is faster at the top than the bottom portion.
This is because after sometimes PCM starts to melt near the wall and creates a thin layer of molten PCM.
The hot molten PCM rises to top due to temperature difference induced by buoyancy forces. Thus, as
natural convection currents are flowing upwards more rapidly, top portion of rectangular capsule melts
comparatively faster than bottom.
Fig 7. Contours of liquid fraction for sphere and rectangle at 40 min
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Fig. 7 shows contours of liquid fraction for sphere and rectangle after 40 min. From the figure it is
observed that the contours of liquid fraction for solid PCM are identical in nature after 40 min. However,
that solid PCM do not sink to bottom due to constant density assumption throughout the PCM i.e.
constrained melting is observed. Further, it is also observed that melting of PCM is faster in case of
rectangular compared to spherical one. This is due to the fact that the aspect ratio is higher in case of
rectangular. During the melting of PCM, the effect of natural convection heat transfer is significant.
Moreover, natural convection heat transfer is mostly influenced by the aspect ratio of the enclosure. This
may be the reason for higher heat transfer in case of rectangular capsule compared to spherical one.
Fig.8 Variation of temperature with respect to
time at location 10 mm below from the top
Fig.9 Variation of temperature with respect to time
at center location
Fig.10 Variation of temperature with respect to time at location 10 mm above from the bottom
Figs. 8-10 show variation of temperature with respect to time at location 10 mm below from the top, center
and 10 mm above from the bottom respectively. It is observed that melting rate at 10 mm above from the
bottom location in both the cases is same. This is due to the fact that conduction mode of heat transfer is
dominant at bottom of capsule. At location 10 mm below from the top, it is observed that initially melting
starts in spherical capsule rapidly compared to that of rectangular one. Later, after 16 min temperature of
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PCM at that point for both the cases remains same. This may be because after 16 min PCM gets
completely melted in both the cases at location 10 mm below from the top and change in temperature in
PCM is only due to convection heat transfer only. The center portion of PCM in rectangular capsule melts
faster than spherical capsule. This is due to the effect of natural convection as discussed above. Table 2
shows comparison of time required to start melting at various locations in spherical and rectangular
capsule.
Table 2 : Comparison of melting starting time at various locations
Location Melting starting time(Minutes)
Sphere Rectangle
10 mm below from the top 20 20
Center 28 24
10 mm above from the bottom 23 20
It has been observed from the simulations that total melting time for sphere is 56 minutes & that for
rectangle is 46 minutes. Thus, total 18% reduction in melting time is observed in case of rectangle
shaped macro-encapsulated PCM than spherical one.
Conclusion
In the present research work, thermal performance of PCM encapsulated in rectangular and spherical
capsule is carried out in terms of temperature distribution and total melting time required. A numerical
code is developed in Fluent and validated with experimental results published earlier. It is observed that
PCM melts faster at top than bottom portion of enclosure. It is also concluded that melting time required
in case of macro-encapsulated PCM having rectangular shape is less compared to spherical shape by
17.85%. This research work help us to understand the potential of using efficient LHSU incorporating
macro-encapsulated PCM. It also help to increase the effectiveness of current systems with application of
rectangular shape of encapsulated PCMs and to develop an efficient LHSU in applications like small
scale textile, chemical, sugar and other processing industries.
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