cfdmodelling of floor heating system in dome shape rooms according to the thermal comfort condition
TRANSCRIPT
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INTERNATIONAL
ENERGY AND ENVIRONMENT FOUNDATION
Computational Fluid Dynamics Applications in Green DesignEditor: Maher A.R. Sadiq Al-Baghdadi
www.IEEFoundation.org
Chapter Nine
Copyright 2014 International Energy and Environment Foundation. All rights reserved.
CFDMODELLING OF FLOOR HEATING SYSTEM IN
DOME SHAPE ROOMS ACCORDING TO THE THERMAL
COMFORT CONDITION
T. Khademinejad1, S. Rahimzadeh
2, P. Talebizadeh
1,
H. Rahimzadeh1,3
, H. Sarkardeh4
1Department of Mechanical Engineering, Amirkabir University of Technology, Tehran,
Iran.2School of design, Creative Industry Faculty, Queensland University of Technology,
Brisbane, Australia.3Member of energy and control, center of excellence, Amirkabir Univercity of
Technology, Tehran, Iran.4Civil Engineering Division, Department of Engineering, Hakim Sabzevari University,
Sabzevar, Iran.
Abstract
Population increase, loss of energy resources and consequently high energy demand in
recent years has caused countries to change their energy consumption policies. One of the
most important energy consumers in rural and urban areas are buildings. Therefore, the roleof heating and cooling systems is considerable in buildings with high level of energy usage.
Floor heating system is a form of central heating system which achieves indoor climate
control for thermal comfort using conduction, radiation and convection heat transfer. The
terms radiant heating is commonly used to describe this approach regarding to the role of
radiation in this system according to its significant portion of the resulting thermal comfort.
Radiant heating has much more advantages compared to conventional heating systems not
only in the case of energy efficiency, but also in preparing thermal comfort for settlements.
In addition, floor heating systems generate lower temperature gradients in compare with
other convective heating systems. In the present study, the CFD simulation is performed to
analyse floor heating system in a dome shape room to reach the thermal comfort condition
in the standard height of 1.8 meter above the floor. Moreover, the obtained results are
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278
compared to the floor heating system in an ordinary room with the same volume and
6m4m3m dimensions. The required energy to achieve the thermal comfort condition in
the simulated rooms has been calculated by simulating the velocity and temperature fields.
The constant temperature for the floor and convection with outside for walls, roof, door and
window are considered as the boundary conditions. The velocity and temperature
distribution as well as the floor temperature are compared in both systems. The primary
results showed that in the dome shape room, the required floor temperature for providing
thermal comfort condition is less than the ordinary room. However, the total area of the
floor is higher in the dome shape room than the ordinary room.Copyright 2014 International Energy and Environment Foundation - All rights reserved.
Keywords: Floor heating system; Dome shape rooms; CFD simulation; Energy
consumption; Indoor climate; Thermal comfort.
1. Introduction
The concept of sustainable building originates from the sustainable development which was
firstly defined by the World Commission on Environment and Development (WCED) as
the development that meet the needs of the present humanity without compromising the
ability of the future generation to meet their own needs [1].
The term sustainable buildings is introduced in the contexts of sustainability. As there are
many different viewpoints about sustainability, there are also various kinds of definition for
sustainable buildings [2-5]. For instance, Yashiro [2] defined sustainable buildings asbuilding that use resources efficiently and keep the environment healthy.
Energy consumption plays a significant role in analysing the performance of sustainable
buildings. According to U.S. statistical report, the buildings in the U.S. account for 36% of
the total primary energy consumption, of which residential buildings alone account for
21%. Moreover, a large proportion of greenhouse gases (GHG) emission, air pollutants and
solid wastes are produced by building sector due to the large amount of energy
consumption. In the U.S. the amount of CO2emission produced by buildings accounts for
38% in 2002 [6]. Consequently, energy consumption of buildings accounts for a large
proportion of primary energy use and GHG emissions. Thus, it has great impact on the
environment and affects the sustainability of human future life.Nature itself has evolved for billions of years and there should be lessons that can be
learned about, especially the habitats that have been built hormonally with the environment
by creatures [7]. Nature has provided us many solutions on various aspects of
sustainability, including building material properties, building envelope, environmental
considerations, sensors and monitoring, team integration and functionality [8]. Therefore, it
is possible to design sustainable buildings by learning from nature. Designing buildings by
learning from the optimum forms existing in nature is a possible way to fulfil this
endeavour since these forms have undergone billions of years of evolution and still exist in
nature.
Dome structure is based on self-generating forms in nature, bubble clusters being typicalexamples. It is based on the natural form-optimizing process in biological structures and
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279
can be translated into the architecture world in the form of new generation homes. The
dome configuration applies natures principles of forming a highly efficient system [9].
The aim of this research is to analyse the energy consumption of a dome house, as an
example of designing sustainable buildings by learning from the optimum biological forms
existing in nature, since energy consumption is an important indicator on the sustainability
of buildings.
Only a few thermal models have been presented for dome shape homes. More attention has
been given to the structural configuration than to the thermal performance of dome-like
homes. Nara [10] presented a 2D CFD model for calculating the air velocity and
temperature distribution due to thermal convection inside a reduced-model of a farm
building under adiabatic boundary condition. The Boussinesq approximation is combined
with the Navier-Stokes equation to describe the natural convection. Boulard et al. [11] used
a reduced-scale model of a greenhouse with high temperature of floors to simulate the
impact of solar radiation on the greenhouse. The k- model was added to simulate theturbulent flow. Grashof number (Gr) was used in these two papers to ensure the similarity
between the full scale model and reduced scale experimental model. Luttmann-Valencia
[12] developed a single node model that predicts the air temperature inside Biosphere II,
located in Arizona (US). T. Nishioka et al. [13] evaluated the indoor thermal environments
in a large domed stadium during the summer. To satisfy such purposes, they take into
account various intelligent mechanical systems to control and create a suitable space and
environment without consuming excessive energy. Their measurements included
temperature distribution, humidity, air flow and outdoor weather conditions for three
seasons. Shklyar and Arbel [14] examined the wind-driven isothermal flow patterns and
mass fluxes in a full-scaled, pitched-roof, single span glasshouse using standard and high-Reynolds-number k- models. Lin and Zmeureanu [15] presented a three-dimensionalthermal and airflow (3D-TAF) model that predicts the impact of large domes on the heating
load of the protected house. They focused on the airflow model and made a comparison
between their simulation and CFD model. Faghih and Bahadori [16] studied the thermal
performance of domed roofs in order to determine how they can be helpful in reducing the
maximum inside air temperature in buildings during the warm seasons of the year. They
considered various parameters such as air flow around dome roofs, solar radiation,
radiation heat transfer with the sky and the ground and openings on the building. They
concluded that the thermal performance of the investigated domed roof is better than the
building with flat roof. Moreover, they found that openings cause passive air flow insidebuilding, which is helpful for establishing thermal comfort
Croome and Moseley [17], Sharma et al. [18], Singh et al. [19] and Jain [20] presented
numerical models that predict the air temperature inside a dome with lots of simplifying
assumption. As an example, they considered the convective heat transfer coefficient to be
constant and neglected the air movement inside the dome.
Glazed domes have become increasingly popular in modern building designs. These kinds
of domes are used to bring daylight and solar heat into the indoor space. Faghih and
Bahadori [21] estimated the solar radiation received by several domed roofs, and
determined the effect of glazed tiles covering these domes on the total solar radiation
absorbed by such roofs. The results of this study can be useful in the thermal performanceevaluation of domed roofs, and particularly for determining their passive cooling effects for
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280
the buildings they serve. For domes with multiple spaced layers of glazing, there is little
information available on natural convection heat transfer within these layers. Laouadi and
Atif [22] presented a numerical study on heat transfer by laminar natural convection within
multi-layer domes with uniform spacing heated from the outside. They also obtained flow
and temperature fields within the domed enclosure using the control volume approach
combined with the fully implicit scheme.
During the last two decades, application of floor heating systems in building sector have
increased significantly [23, 24] as one of the most efficient systems to achieve thermal
comfort in buildings with low-energy requirement. Instead of warming air and circulating it
throughout the building, floor heating system heats the objects, atmosphere and occupants
directly. In comparison to the conventional forced warm air circulation systems, radiant
heating system needs lower energy [25]. In the recent years, there has been considerable
attention to floor heating system and their thermal performance in the literatures. In
addition of different investigation with respect to thermal properties [26], and dynamical
behaviour [27], there are extensive studies have been devoted to energy savings of this
system [28-30]. Buckley [31] studied the energy saving of floor heating systems and
concluded that these systems can reduce energy costs by 30% or more with equal comfort
condition compared to other conventional convective heating systems.
In the present study, the CFD simulation of a three dimensional dome room coupled with a
floor heating system has been developed and compared to a regular cubic room with the
same volume to predict the energy consumption of two different kinds of rooms. The
boundary conditions, heat transfer coefficients through building envelope and heat source
outputs are considered to be similar for both rooms. Thermal comforts at comfort height in
both rooms have been calculated by modelling the velocity and temperature fields using theFluent software.
2. Model description
In this study, floor heating system is simulated for a dome house by means of
Computational Fluid Dynamic (CFD) and results are compared to the regular cubic room in
order to indicate the energy saving capabilities and the comfort conditions of dome shapehouses. The simulated dome and cubic shape rooms are graphically presented in Figure 1.
In order to have a better definition of 3D rooms, two main sections that covered the entire
room are defined which are called door-mid-section and window-mid-section. Door-mid-
section is the plane of the 3D rooms which contains the effect of door on the temperatureand velocity profiles. And also the effect of window on the flow and thermal behaviour of
rooms can be seen in window-mid-section. Furthermore, at the middle of the room, areference line is defined in order to have a better understanding of temperature and velocity
gradients in the room. Door and window-mid-sections are graphically illustrated in Figures
2 and 3. Note that for the dome room, the mid sections are selected at the middle of the
window and door; however, for the cubic room, the mid sections are selected at the middle
of the walls.
Boundary conditions, material and thermodynamic properties of the problem for both dome
shape and cubic rooms are represented in Table 1. As tabulated in this table, the boundary
condition of walls, roof, window and door are the same; however, constant heat flux isassumed for the floor.
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The simulation is performed in the climate condition of Tehran, the capital city of Iran.
According to this consideration, the outdoor design temperatures is considered to be C0 .
Figure 1. Perspective view of (a) dome room and (b) cubic room with dimensions in meter.
Figure 2. (a) door-mid-section and (b) window-mid-section of the 3D dome shape room.
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Figure 3. (a) door-mid-section and (b) window-mid-section of the 3D cubic room.
Table 1. Boundary condition, material and thermodynamic properties of the problem.
Walls and Roof Floor Window Door
Boundary condition Convection to
outdoor air
Heat
flux
Convection to
outdoor air
Convection to
outdoor air
Material Lightweight
cement
Wood Glass Wood
Thickness ( m ) 0.2 0.05 0.05 0.07
Thermal Conductivity ( K.m/w ) 0.3 0.173 0.96 0.173
Specific Heat ( K.Kg/J ) 960 2310 840 2310
Density ( 3m/Kg ) 1600 700 2800 700
Absorption Coefficient ( m/1 ) 0.1 0 0.04 0
3. Numerical procedure
In this research, a finite-volume approach has been used to solve flow and heat transfer
equations of a floor heating system in two different room types. Numerical solutions were
obtained iteratively for each of cells to produce a solution that satisfies the conservation
laws for mass, momentum, and energy. For incompressible, steady state and three-
dimensional flow, the governing mass, momentum and energy equations are as follow.
mS)v.(t
=+
(1)
Fg.p)vv.()v(t
++
+=+
(2)
h
j
effjjeff Sv.JhTk.))pE(v.()E(
t
+
+=++
(3)
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Eq. (1) is the general form of the mass conservation equation where is density, v
is the
velocity vector and mS is the mass added to the continuous phase from the dispersed
second phase (e.g., due to vaporization of liquid droplets).
Eq. (2) is momentum conservation equation where pis the static pressure, is the stress
tensor (described below), and g
and F
are the gravitational body force and external body
forces (e.g., that arise from interaction with the dispersed phase), respectively.
The stress tensor is given by
( )
+= Iv.vv T
3
2 (4)
where is the molecular viscosity, I is the unit tensor and the second term on the righthand side is the effect of volume dilation.
In the energy equation (Eq. (3)), E is the total energy,eff
k is the effective conductivity
( teff kkk += , where tk is the turbulent thermal conductivity, defined according to the
turbulence model being used), and jJ
is the diffusion flux of speciesj. The first three terms
on the right-hand side of Eq. (3) represent the energy transfer due to the conduction,
species diffusion, and viscous dissipation, respectively. hS includes the heat of chemical
reaction, and any other volumetric heat sources.
In Eq. (3), the total energy (E) is equal to
2
2vp
hE +=
(5)
where his the sensible enthalpy.
3.1 Turbulence model
To get a correct vision of the flow field, the k turbulence model is chosen due to itsextensive use in various engineering applications. This model is a semi-empirical model
based on model transport equations for the turbulence kinetic energy ( k) and its specificdissipation rate ( ) which are obtained from the following transport equations:
( ) ( ) kkj
k
j
i
i
YGx
k
xku
xk
t++
=
+
(6)
( ) ( )
YGxx
uxt jj
i
i
++
=
+
(7)
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whichs
is the scattering coefficient, a is the absorption coefficient, n is the refractive
index, )s,s(
is the scattering phase function for the radiation from incoming direction
s
and confined within the solid angle d to scattered direction s
confined within the
solid angle d . )s,r(I
is the total radiation intensity function and Tis the air temperature.
In this study, the wall surfaces are assumed opaque. Furthermore, for considering the
buoyancy effect and the relation between the flow and energy equations, Boussinesq model
is used.
3.3 mesh structure
To obtain a physical pressure field, a non-uniform grid for the three dimensional model of
both dome shape and cubic shape rooms is generated. Figure 4. shows the meshed
midsection of the rooms. As it is clear from Figure 4, the cells near the walls are finer due
to the importance of these regions. For grid independence test, three different resolutionsshown in Table 2 are considered to compare the obtained numerical results.
When the temperature at the height of 1.8 meter above the floor reaches to 295.15 K, the
thermal comfort condition is established. The results obtained from the different grids
show that an increasing the grid numbers by 41% (case II to case III) has a small influence
( %. 41016 ) on the temperature in thermal comfort height. According to this refinement
study, all further simulations are performed with considering case II. Finally, it should be
declared that the maximum error of the residuals to reach to the steady state solution is
assumed to be of the order of 6101 .
Table 2. Grid independency test for two modelled rooms.
Dome room Cubic roomCase
Number of
grids
Temperature in thermal
comfort height (K)
Number of
grids
Temperature in thermal
comfort height (K)
I 295608 291.83 40257 291.35
II 404898 294.93 52801 294.88III 681926 295.11 89072 295.08
4. Results and discussion
As mentioned, the velocity and temperature distributions in a dome shape room heated by a
floor heating system are investigated. The results are compared to the velocity and
temperature profiles of a regular cubic room with the same heating method. The comfort
temperature (295.15 K) is determined at location 1.8m above the floor according to
ASHRER handbook as the comfort height [33]. As the comfort condition is achieved in the
room, it means that the steady state condition is established and the numerical simulation
has been converged. Then, the dissipated heat fluxes of all surfaces to the environment
have been calculated for both the dome and cubic shape rooms.
First, for the validation of the code, a cubic room with the dimension ofm.m.m. 819162 is simulated and the results are compared with the experimental data
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[34, 35]. By selecting the same condition between the simulation and the experimental
setup and also considering unsteady flow, the simulation is performed. Figure 3 shows the
temperature at the height of 1m above the floor for both the experimental data and the
present study. As shown in this figure, the results are in good agreement with each other.
Figure 4. Mesh structure on the midsection of (a) dome room and (b) cubic room.
Figure 5. The comparison of CFD simulation and experimental data.
Figure 6a and b illustrate the temperature profiles in the door-mid-section and window-
mid-section of dome shape room. It can be seen from this figure that temperature
distribution in room is clearly uniform both in door-mid-section and window-mid-section.
Furthermore, the temperature near window is relatively low which is due to high thermal
conductivity of glass in comparison to other parts of the room such as walls and floor.
Velocity vectors in the door-mid-section and window-mid-section of dome shape room can
be seen in Figure 7a and b, respectively. As shown, there is a big vortex approximately in
the center of the window-mid-section, while there are several smaller vortices in door-mid-
section due to the temperature difference between different parts of the room. It is
important that higher temperature difference will cause higher pressure difference andconsequently bigger vortices can be produced.
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Figure 6. temperature profiles in (a) door-mid-section and (b) window-mid-section of dome
shape room.
Figure 7. Velocity contours in (a) door-mid-section and (b) window-mid-section of dome
shape room.
For better understanding of flow patterns, three different mid-sections of the room in the
form of velocity vectors and velocity contours are graphically illustrated in Figure 8a and b,
respectively.
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Figures 9 and 10 display the velocity contour in the mid-sections of the cubic shape room.
As displayed in these figures, two big vortices are generated near the wall in both window
mid-section and door mid-section, expectedly [35]. The difference between the flow
patterns in the produced vortices is due to the existence of window and door.
Figure 8. (a) velocity vectors and (b) velocity contours for three different mid-sections of
dome shape room.
Figure 9. Velocity vectors for door-mid-section of cubic room.
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Figure 10. Velocity vectors for window-mid-section of cubic room.
Figure 11 display the air temperature at the reference line for the dome and cubic shape
rooms and Figure 12 display the air speed at the reference line for the dome and cubic
shape rooms. As displayed in Figure 11, in both systems, small temperature changes could
be seen along reference line due to the usage of floor heating system [36]. However, in the
dome type room, at the comfort height, the air temperature is higher than the aittemperature in the cubic room. As shown in Figure 12, the air speed at the comfort height is
smaller in the dome room than the cubic room. Having a higher air temperature and a lower
air speed at the comfort height is an advantage of dome type room related to the cubic type
room.
Figure 11. Air temperature at reference line for (a) dome room and (b) cubic room.
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Figure 12. air velocity at reference line for (a) dome room and (b) cubic room.
Table 3 and Table 4 list the total heat transfer from each surface of the dome type room and
cubic type room, respectively. As schematized in these tables, the total heat transfer from
the floor to the room is almost 6.5% higher in the dome type room than regular cubic type
room. However, the area of the floor is bigger in the dome shape room than the cubic room
so that the total heat transfer per surface area from the floor to the room is 23% smaller in
the dome type room than the cubic room.
Table 3. Total heat transfer for each surface of the dome type room.
Surface type Surface
area (m2)
Total heat
transfer (W)
Total heat transfer per
surface area (W/m2)
Floor 28.23 1954.1 69.23
Dome surface 52 -1104.2 -21.23
Window 1.6 -712.4 -445.52
Door 1.8 -50.3 -27.94
Door and window
connecting walls
5.39 -87.2 -16.18
Total 89.02 0 -
Table 4. Total heat transfer for each surface of the cubic type room.
Surface type Surface
area (m2)
Total heat
transfer (W)
Total heat transfer per
surface area (W/m2)
Floor 20.16 1827.7 90.66
Walls 46.4 -1162.3 -25.05Roof 20.16 -417.2 -20.69
Door 1.8 -52.3 -29.06
Window 2.4 -195.9 -81.65Total 90.92 0 -
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5. Conclusion
In the present study, the CFD simulation has been done to analyse the velocity and
temperature distribution of a dome type room in comparison with the regular cubic type
room with the same volume using the Fluent software. The floor heating system is
employed in order to reach the thermal comfort condition in the rooms. The results show
that in the dome type room, the air temperature and speed is more suitable according to the
comfort conditions. However, the average of air speed is higher in the dome shape room
than the cubic shape room. Furthermore, the total heat transfer from the floor is 6.5% more
in the dome shape room than the cubic shape room since the area of the dome rooms floor
is higher than the cubic room so that the total heat transfer per surface area is 23% smaller
in the dome shape room than the cubic shape room. Moreover, in both rooms, due to the
usage of floor heating system, the temperature gradients are low.
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Taha Khademinejad received B.Sc. degree in mechanical engineering minoring in
thermo fluid from University of Guilan, Rasht, Iran in 2011. He is currently pursuingthe M.Sc. degree with the school mechanical engineering, Amirkabir University of
Technology, Tehran, Iran. His current research interests include sustainable andrenewable energies, desalination, heat and mass transfer and thermodynamics.
Shahab Din Rahimzadehcompleted his Bachelor degree of Architect in 2010, at IUCin Iran. He is currently a master research student in school of design (Creative Industry
Faculty) at Queensland University of Technology in Brisbane, Australia. ShahabsMaster research focuses on parametric modeling, Climate based Daylight Metrics,
Complex Geometry and sustainability. His research aims to analysis and modelingUse of parametric modeling and climate-based metric for the efficient design of
daylight strategies in buildings with complex geometries.
Pouyan Talebizadeh received B.Sc. and M.Sc. degree in mechanical engineering from
Shahid Bahonar University of Kerman, Kerman, Iran in 2008 and 2011, respectively.He is currently pursuing the Ph.D. degree with the school mechanical engineering,
Amirkabir University of Technology, Tehran, Iran. He is a lecturer in mechanical
Engineering Department, Graduate University of advanced Technology, Kerman, Iran.His current research interests include two phase flow, environmental pollution control,
emission reduction, Non-thermal plasma technology, HVAC systems, optimization,and numerical modeling.
E-mail address: [email protected]; [email protected]
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8/9/2019 CFDMODELLING OF FLOOR HEATING SYSTEM IN DOME SHAPE ROOMS ACCORDING TO THE THERMAL COMFORT CONDITION
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Chapter 9 In: Computational Fluid Dynamics Applications in Green Design. pp.277-294
C i ht 2014 I t ti l E d E i t F d ti All i ht d
294
Hassan Rahimzadehreceived the B.Sc. and M.Sc. degrees in mechanical engineeringfrom the West Virginia Institute of Technology, Montgomery, WV, USA, and West
Virginia State University, Morgantown, WV, USA, and the Ph.D. degree ininstrumentation measurement from New South Wales University, Sydney, Australia, in
1977, 1978, and 1986, respectively. He has been with the Department of MechanicalEngineering, Amirkabir University of Technology, Tehran, Iran. His current research
interests include two phase flow (physical and numerical modeling), hydraulicsstructures, environmental pollution control, renewable energy, and instrumentation.
Hamed Sarkardeh received B.Sc. degree in civil engineering from FerdowsiUniversity of Mashhad, Mashhad, Iran, and M.Sc. from Amirkabir University of
Technology (Tehran Polytechnic) Tehran, Iran, and Ph.D. from Iran University ofScience and Technology, Tehran, Iran, in 2006, 2009 and 2013 respectively. He is a
lecturer in Civil Engineering Division, Department of Engineering, Hakim SabzevariUniversity, Sabzevar, Iran and also senior researcher in the Hydraulic Structures
Division, Water Research Institute, Tehran, Iran.