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FLOW AND HEAT TRANSFER ANALYSIS ON
SPIRAL COUNTER FLOW HEAT
RECIRCULATING BURNER
MUHAMMAD FIRDAUS BIN OTHMAN
A project report submitted in partial fulfillment of the
requirements for the award of the degree of
Master of Engineering (Mechanical)
Faculty of Mechanical Engineering
Universiti Teknologi Malaysia
JULY 2006
iii
To my beloved wife, Nina and
newborn princess Miza
iv
ACKNOWLEDGEMENT
I would like to thank many people for their help in completing this project,
but my foremost appreciation goes to my main thesis supervisor, Dr, Mazlan Abdul
Wahid for his guidance and thoughts throughout the hardship. I am also very
thankful to my co-supervisor Dr. Kahar Osman for the helpful suggestions and
advices during the project duration. Their continuous support, words of
encouragement and wisdom has lead to the completion of such a piece.
I am also taking this opportunity to recognize the companionship and
motivation from my fellow postgraduate friends in particular, Redhwan, Fuad and
Kamaruzaman that drives me towards completing the project. Also not to forget my
office colleagues for their understanding on how important for me to do what I have
to do.
Finally, my sincere and deepest appreciation to my wife, Nina for her love,
understanding, patience and sacrifices that need to be accommodated behind such
work. To my newborn daughter, Miza, you are the limelight of my life which hope to
turn as a strength for me to pursue further in life. Also, I am grateful to my parents,
siblings and in-laws family members on their non-exhaustive support for me to
achieve goals that I have planned for. Thank you all.
v
ABSTRACT
In order to establish a performance characterization of spiral counter flow
heat recirculating burner, an understanding of the chemical kinetics, heat transfer and
flow dynamics aspects of the combustor needs to be developed. Research would be
focusing on the micro-scaled square spiral counter flow configuration which is also
known as the “Swiss roll” micro-combustor with propane-air mixture as the case
study. A two-dimensional Computational Fluid Dynamics (CFD) with propane-air
premixed stoichiometric numerical based model is being adopted and focus of the
study would be in observing the thermal characteristic (i.e. heat recirculation rate) of
the combustor. This is the parameter that characterizes the preheat energy obtained
by the incoming reactants through combustion process and its high energy post-
combustion products. The performance of the combustor with respect to the thermal
characteristic is being analyzed at a range of 40<Re<1000 steady, laminar and
incompressible fluid flow velocity profile. In addition, a parametric study on
identifying the effect of different geometrical aspect ratio between channel wall
thickness to channel width is also being envisaged. Analysis has shown that a heat
recirculation method has managed to produce an excess enthalpy flame beyond the
adiabatic flame temperature which leads towards extending the limitation of the
combustion process feasibility in a miniaturization of a combustor system.
vi
ABSTRAK
Bagi mewujudkan ciri prestasi penunu aliran bertentangan yang berpusar
dengan peredaran semula haba, pemahaman dari aspek kinetik kimia, pemindahan
haba dan aliran dinamik pembakar perlu dibangunkan. Penyelidikan ini memberi
fokus terhadap penunu aliran bertentangan yang berpusar dengan peredaran semula
haba yang berbentuk segi empat dan berskala mikro yang juga dikenali sebagai
pembakar berskala mikro “Swiss roll” dengan bahan bakar campuran propana-udara
sebagai kes kajian. Kajian melibatkan model berangka pracampur stoikiomterik
propana-udara didalam dua dimensi dengan menggunakan kaedah dinamik bendalir
berkomputer (CFD) dimana fokus kajian tertumpu kepada ciri terma (kadar
peredaran haba) pembakar. Parameter ini menggambarkan tenaga prapanas yang
diperolehi oleh bahan bakar sebelum bertindak balas melalui proses pembakaran
dimana perolehan tenaga tinggi ini berpunca daripada hasil pembakaran bahan bakar
itu sendiri. Prestasi pembakar melalui ciri terma ini dianalisa pada keadaan bendalir
yang tak boleh mampat, mantap dan lamina dimana profil halaju sekitar
40<Re<1000. Selain daripada itu, kajian dalam mengenal pasti kesan perubahan
geometri diantara ketebalan dinding saluran dan lebar saluran terhadap ciri terma ini
turut dijalankan. Analisa telah membuktikan bahawa kaedah peredaran semula haba
berjaya menghasilkan lebihan entalpi yang melebihi suhu nyala adiabatik dimana ia
menjurus kepada memanjangkan had kebolehlaksanaan proses pembakaran didalam
pengecilan sistem pembakar.
vii
TABLE OF CONTENTS
CHAPTER TITLE PAGE
DECLARATION
ii
DEDICATION iii
ACKNOWLEDGEMENT iv
ABSTRACT v
ABSTRAK vi
TABLE OF CONTENTS vii
LIST OF TABLES ix
LIST OF FIGURES x
LIST SYMBOLS/ABBREVIATIONS xiv
LIST OF APPENDICES xvi
1 INTRODUCTION 1 1.1 Background 1
1.2 Scope of the Study 3
2 LITERATURE REVIEW 5 2.1 “Swiss roll” Experiment by Sitzki et al. (2001) 5
2.2 Numerical “Swiss roll” Model by Chen et al. (2004) 6
2.3 Exprimental and Numerical Model by Shinoda et al. (1998)
7
2.4 “Swiss-roll” Combustor with Catalyst Experiment by Ahn et al. (2005)
9
2.5 Numerical Model by Hua et al. in Micro-scaled Combustor (2005)
10
viii
3 METHODOLOGY 13 3.1 Analysis Framework 13
3.2 Model Validation 14
3.3 Numerical Modeling 16
3.3.1 Governing Equations 17
3.3.2 FLUENT Numerical Solver 19
3.3.3 Model Geometry and Mesh 20
3.3.4 Boundary Conditions 21
3.3.5 Reaction at Combustor 23
3.3.6 Heat Recirculation Rate 23
4 RESEARCH FINDINGS 25 4.1 Validation Model 25
4.2 Heat Recirculation Rate Analysis 28
4.2.1 Effects from Inlet Velocity 29
4.2.2 Effects from Geometrical Aspect Ratio 33
5 RECOMMENDATIONS AND CONCLUSIONS 37
REFERENCES 39 Appendix A 41-46
ix
LIST OF TABLES
TABLE NO. TITLE PAGE
1.1
Propane limiting combustible properties
4
4.1 Enthalpy from variation of inlet velocity
29
4.2 Heat recirculating rate for variation of inlet velocity
30
4.3 Enthalpy from variation of aspect ratio @ Re=1000
33
4.4 Rate of heat recirculation from variation of aspect ratio @ Re=1000
33
4.5 Enthalpy from variation of aspect ratio @ Re=400
34
4.6 Rate of heat recirculation from variation of aspect ratio @ Re=40
35
x
LIST OF FIGURES
FIGURE NO. TITLE PAGE
1.1
Concept of heat recirculation
2
1.2 “Swiss roll” configuration
3
2.1 Macro-scale combustor
5
2.2 Micro-scale combustor
6
2.3 Four passes of heat exchanger with one combustor pass
7
2.4 Heat recirculating rate and thermal efficiency
8
2.5 Independence of heat recirculation rate on equivalence
ratio (Re=180, l/d=7.5)
8
2.6 Dependence of heat recirculation rate on Re (Ø=0.25,
l/d=7.5)
9
2.7 Dependence of heat recirculation rate on aspect ratio
(Ø=0.25, Re=180)
9
2.8 Schematic diagram of micro-scale combustion chamber
10
xi
2.9 Distribution of hydrogen conversion rate along central axis
with various inlet diameter (D) in adiabatic wall
11
2.10 Contour of water production rate along central axis at inlet
diameter (a): 0.4mm, (b): 0.2mm, (c): 0.1mm, (d): 0.05mm
under adiabatic wall
11
2.11 Contour of temperature along central axis of the chamber
at inlet diameter (a): 0.4mm, (b): 0.2mm, (c): 0.1mm,
(d): 0.05mm under adiabatic wall
12
2.12 Temperature distribution along the outer wall of the
chamber with different wall conductivity properties
12
3.1 Case study parameter
14
3.2 Ahn et al. [5] extinction limit map for the Inconel “Swiss
roll” of propane-air mixture
16
3.3 Variation of equivalence ratio at extinction limit with Re
by Chen et al. [3]
16
3.4 Numerical model process flow in FLUENT
17
3.5 Segregated solver scheme process flow
19
3.6 Model drawing in GAMBIT
20
3.7 Meshing in GAMBIT
21
3.8 Boundary conditions parameter at the outer-most wall
21
xii
3.9 Inlet velocity boundary conditions with propane-gas
mixture ratio definition
22
3.10 Heat transfer modes in the channel
22
3.11 Sample of reaction phenomenon setup in FLUENT
23
3.12 Heat recirculation rate definition
24
4.1 Validation model results
26
4.2 Temperature profile for Re=1000
26
4.3 Temperature profile for Re=400
27
4.4 Temperature profile for Re=100
27
4.5 Temperature profile for Re=40
27
4.6 Reactant channel zones
28
4.7 Heat recirculation rate profile with respect to incoming
reactant channels
30
4.8 Combustion flame temperature of 3000K at inlet Re=40
31
4.9 Combustion flame temperature of 3660K at inlet Re=200
31
4.10 Combustion flame temperature of 3520K at inlet Re=1000
31
4.11 Shinoda et al. [4] configuration
32
xiii
4.12 Heat recirculation rate profile with respect to aspect ratio at
Re=1000
34
4.13 Heat recirculation rate profile with respect to aspect ratio at
Re=40
35
xiv
LIST OF SYMBOLS/ABBREVIATIONS
A - Surface area
CFD - Computational fluid dynamics
cp - Specific heat at constant pressure
D - Binary diffusion coefficient
D - diameter
d - Channel width
EFAB - Electrochemical fabrication
h - Coefficient of thermal convection
hfo - Enthalpy of formation
i - Species count
k - Coefficient of thermal conductivity
L - Thickness of channel wall
l - Channel length
MEMS - Micro-electro-mechanical system
m’’ - Mass flux
m’’’ - Mass production rate per unit volume
N - Number of passes
p - Pressure
q - Heat transfer rate
Re - Reynolds number
T - Temperature
t - Time
V - Velocity vector
Y - Mass fraction of species
α - Thermal radiation absorptivity
ε - Thermal radiation emissivity
xv
Ø - Equivalence ratio
ρ - Density
υ - Kinematic viscosity
xvi
LIST OF APPENDICES
APPENDIX TITLE PAGE
A
Sample analysis steps in FLUENT
41
CHAPTER 1
INTRODUCTION
1.1 Background
Evolution of micro-electro-mechanical system (MEMS) development has lead
to increasing demands on the essential need to search for a micro-power generation
devices that has such a high power density parameter. Battery technology currently
has a limited power density to cater for enhancement of MEMS industry power
requirement whereby it could be noted that an alkaline battery would only has a
specific energy of 0.6 kJ/g and lithium ion battery has an energy storage density of
around 1.2 kJ/g [1].
Understanding on this limitation has motivated research activities to look for an
micro-scale combustion-based power generation device which is understood that
hydrocarbon fuels has a high energy storage capacity that is typically in the range of
45 kJ/g [2]. That is why most vehicles such as automobiles, aircraft and even rocket
are relying on the combustion process to propel. Thus, taking the micro-combustor as
the alternative solution would lead to a longer operating time of the MEMS devices
or a lighter system with the same amount of power capability from those battery
solutions. In addition, since it is a refueling based system, a waste disposal will not
be an issue [3].
Based on conventional combustion theory, there is a major limitation with
regards to the geometrical miniaturization allowable factor namely the quenching
2
distance. This is due to the fact that flames will extinguish upon entering a narrow
passageway. In addition, with such miniaturization process, it would lead to a high
ratio of surface area to volume. Such a ratio value would prone for a significant heat-
loss behavior of the combustor that leads to affect the combustion stability parameter
such as the flammability limits or also known as extinction limit and the reaction rate
(i.e. ignition energy and time) for self-sustained combustion or decreases the
combustion efficiency itself.
In lieu with the limitation imposed by the combustion theory with respect to the
micro-scale combustor system, a heat recirculation mechanism is adopted as to
effectively recirculate the thermal energy from such a high temperature burnt gas
(exhaust heat) to the low temperature fresh fuel-air mixture which substantially
extend the extinction limit of the hydrocarbons[3]. It is understood that combustion
process would experience a finite heat loss that leads of not be able to achieve an
adiabatic flame temperature that governs the limitation on the combustion process
feasibility. Transferring the exhaust heat from the combustion product would
increase the reactants total enthalpy which leads to achieving excess enthalpy flame
that is beyond the adiabatic flame temperature. This excess enthalpy flame would
then extend the limitation on the flammability limit of the hydrocarbon reactants.
Figure 1.1 Concept of heat recirculation
With the energy optimization strategy is in place, a limitation on the
quenching distance has been put up to the test beyond the conventional limit where it
is known that quenching distance need to be at least larger than an adiabatic flame
3
thickness which is then dependent on the combustion reaction process. This
combustion reaction process in turn has a dependency on the thermal condition of the
chamber. Thus, a heat recirculation has substantial benefit of allowing a combustion
process to exist at a very low thermal power to attain similar combustion process
performance with the non-preheated reactants or better reaction process at similar
thermal ignition condition alternately [5].
Looking from a compact and effective heat exchanger design perspective, a
spiral, “Swiss roll” with counter flow heat recirculation configuration has been taken
by most researchers as the selected configuration to be implemented as the micro-
combustor whereby this set of heat exchanger would ensure the post-combustion
heated energy is transmitted to the very beginning of the reactants flow passage.
Figure 1.2 “Swiss roll” configuration
1.2 Scope of the Study
In characterizing the optimal design performance of a spiral counter flow heat
recirculating burner, there are three (3) major perspectives that need to be accounted
which are the chemical kinetics, the heat transfer and the flow dynamics. Based on
the past studies on “Swiss roll” configuration, a lot of effort has focused on analyzing
the chemical kinetics and associated heat transfer aspect of it. However, none has
indulged in terms of characterizing the thermal performance by observing the heat
recirculating effectiveness which leads to broaden the range of quenching distance
and equivalence ratio spectrum limit as reported from past studies. Below is the
Reactants Exhaust gas
Combustion region
4
conventional limitation on the propane chemical kinetics properties without any pre-
heating treatment:
The principle objective of the research is to study the relationship between
geometry and performance of spiral counter flow heat recirculating burner. As heat
recirculation is the main driver that established such “excess enthalpy” state to the
incoming reactants, it is the author’s motivation to study this parameter and adopt it
as the performance measurement by following an approach adopted by Shinoda et al.
[4] in characterizing the heat-recirculating ceramic burner . Thus, a fractional heat
recirculation rate is taken as the criteria that define the thermal performance of the
“Swiss roll” combustor that is being analyzed within the study rather than
temperature profile due to its non-representative in characterizing the heat
recirculation index [4]. Only one type of fuel being considered that is a propane-air
premixed mixture as to have means of validating the results with respect to the
experimental work done by Ahn et al [5]. This parameter is studied with respect to
different steady, laminar, incompressible fluid flow profile with geometrical
manipulation of the aspect ratio between wall thickness to the channel width and to
observe the extent of number of spiral loop limitation for effective heat recirculation
towards the incoming reactants. In addition, the study is limited to 2-D computational
approach with conduction, convection and radiation of heat transfer modes are being
considered. Having to understand the heat recirculation profile with respect to
different geometrical configuration (i.e. number of spiral loops and aspect ratio) with
different fluid flow properties would establish a platform that leads towards design
optimization of the combustor for future development.
Table 1.1 : Propane limiting combustible properties Flammability Limits Quenching Distance (mm)
Fuel Lean Limit
(Ø min)
Rich Limit
(Ø max)
Stoichiometric
Mass Air-Fuel Ratio
For Ø=1 Absolute
Minimum
Propane
(C3H8) 0.51 2.83 15.6 2 1.8
REFERENCES
[1] Hua, J., Wu, M. and Kumar, K. Numerical Simulation of the Combustion of
Hydrogen-air Mixture in Micro-scaled Chambers. Part I: Fundamental Study.
Chemical Engineering Sciences, 2005. 60: 3497-3506.
[2] Sitzki, L., Borer, K., Schuster, E., Ronney, P. and Wussow, S. Combustion in
Microscale Heat-recirculating Burner. The 3rd Asia-Pacific Conf. on Combustion.
June 24-27, 2001. Seoul, Korea.
[3] Chen, M. and Buckmaster, J. Modelling of Combustion and Heat Transfer in
“Swiss roll” Micro-scale Combustors. Combust. Theory Modelling, 2004. 8: 701-
720.
[4] Shinoda, M., Maihara, R., Kobayashi, N., Arai, N. and Churchill, S.W. The
Characteristics of a Heat-recirculating Ceramic Burner. Chemical Engineering
Journal, 1998. 71: 207-212.
[5] Ahn, J., Eastwood, C., Sitzki, L. and Ronney, P. Gas-phase and Catalytic
Combustion in Heat-recirculating Burners. Proc. Combust. Inst., 2005. 30: 2463-
2472.
[6] Hua, J., Wu, M. and Kumar, K. Numerical Simulation of the Combustion of
Hydrogen-air Mixture in Micro-scaled Chambers. Part II: CFD Analysis for a
Micro-combustor. Chemical Engineering Sciences, 2005. 60: 3507-3515.
[7] Turns, S.R. An Introduction to Combustion: Concepts and Applications. 2nd. ed.
Singapore: McGraw-Hill. 2000
[8] Wahid, M.A. Combustion Process. Class Notes (SMJ 5493). Universiti Teknologi
Malaysia; 2005
41
[9] Yuasa, S., Oshimi, K., Nose, H. and Tennichi, Y. Concept and Combustion
Characteristics of Ultra-micro Combustors with Premixed Flame. Proc. Combust.
Inst., 2005. 30: 2455-2462.
[10] Spadaccini, C.M., Zhang, X., Cadou, C.P., Miki, N. and Waitz, I. A. Preliminary
Development of a Hydrocarbon-fueled Catalytic Micro-combustor. Sensors and
Actuators, 2003. 103: 219-224.
[11] Shan, X.C., Wang, Z.F., Jin, Y.F., Wu, M., Hua, J., Wong, C.K. and Maeda, R.
Studies on a Micro Combustor for Gas Turbine Engines. J. Micromech.
Microeng., 2005. 15: S215-S221.
[12] Ronney, P.D. Analysis of Non-adiabatic Heat-recirculating Combustors.
Combust. and Flame, 2003. 135: 421-439.
[13] Leach, T.T. and Cadou, C.P. The Role of Structural Heat Exchange and Heat
Loss in the Design of Efficient Silicon Micro-combustors. Proc. Combust. Inst.,
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[14] Fluent Inc. Fluent Manual. Lebanon, N.H (USA). 2003.