thermal and fluid flow analysis of swirling flameless combustion...
TRANSCRIPT
THERMAL AND FLUID FLOW ANALYSIS OF SWIRLING FLAMELESS
COMBUSTION
RAID ABID ALWAN
A thesis submitted in fulfilment of the
requirements for the award of the degree of
Doctor of Philosophy (Mechanical Engineering)
Faculty of Mechanical Engineering
Universiti Teknologi Malaysia
MARCH 2016
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Dedicated to my beloved mother,
to the most precious persons in my life, my beloved wife Saja,
my sweetheart beautiful daughter Qamar and my darling son Mohammed.
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ACKNOWLEDGEMENT
Thanks to ALLAH, the Most Gracious, the Most Merciful, the Most
Bountiful who gave me the courage and patience to accomplish this research work.
Without his help and mercy, this would not have come into reality.
I would like to deeply express my gratitude for the help and support from my
supervisor, Associate Prof. Dr. Mazlan Abdul Wahid and my co-supervisor Dr.
Mohd Fairus Mohd Yasin on their fascinating guidance, encouragement, and
valuable comments throughout the research work. I was fortunate to be one of their
graduate students. Their experience and creativity gave me great profit for carving
my future career.
I want to acknowledge fellow colleagues at HiREF laboratory who have been
helpful and friendly, never fail to make the lab a pleasant place to work in. Many
thanks to Dairobi and Rosli for sharing valuable technical skills and knowledge. In
addition, special thank for their help to Prof. Dr. Arkan Al Taie and Dr. Abuelnuor. I
am grateful to the Iraqi Ministry of Electricity for the financial support and for
granting me the study leave to complete the doctoral degree.
Finally, but not the least, my greatest thanks from my heart to my family for
giving the unlimited supports and patience to complete my study. I would never ever
forget their sacrifice that they have done for me. I appreciate the sacrifice of my wife,
father, father-in-law and mother-in-law in helping me financially and morally to
finish my study.
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ABSTRACT
Flameless combustion is a novel combustion mode that is also to achieve ultra-low emissions of NOx and CO while producing a uniform temperature distribution and a stable combustion. In this work, a newly designed Internally Preheated Swirling Flameless Combustor (IPSFC) has been developed at the High Speed Reacting Flow Laboratory (HiREF), Faculty of Mechanical Engineering, Universiti Teknologi Malaysia (UTM) to achieve high performance combustion and low emission. The study examines the sequential development of a low emission swirling flameless vortex combustor operating from a thermal load of 7 kW to 15 kW. The swirling flameless combustor has been modified to include preheating where the fresh air passes through a helical tube that is fixed inside the combustion chamber before being injected into the flameless combustor for some experiments. The objective of this study is to investigate in detail the role of air inlet geometry with and without air preheating on the performance of the swirling flameless combustion without the addition of diluted gas. Investigation on the effect of multiple air–fuel injection configuration found that the case of SFR42 to be the best configuration for optimum flameless combustion performance. SFR42 is a swirling combustor with 4 inlets of tangential air and 12 inlets axial air with 11 inlets coaxial fuel. The lowest NOx and CO emissions are observed at the equivalence ratio of 0.8 with the value of 4 ppm and 24 ppm, respectively. In general temperature uniformity which is an important characteristic of flameless combustion is observed to vary from 0.03 to 0.06 at the different equivalence ratio. This work also demonstrated the achievement of swirling flameless combustion with and without preheated tangential air. Overall, preheated air has contributed to the increase of 5% thermal efficiency compared to the non-preheated case at the expense of 4 ppm maximum increment of NOx emission. In this thesis some simulation study is also performed to investigate the detail flow field inside the swirl combustor. The numerical investigation confirms the experimental finding on the outstanding performance of SFR42 configuration. It is found that in this configuration the bulk swirling motion was produced in the combustor for good mixing between fuel and oxidizer which in turn lead to complete combustion at low peak temperature. This results in the combustion process with low emission.
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ABSTRAK
Pembakaran tanpa api adalah mod pembakaran baru yang boleh menghasilkan
pelepasan NOx dan CO rendah di samping mendapatkan taburan suhu yang seragam dan pembakaran yang stabil. Dalam kajian ini, Internally Preheated Swirling Flameless Combustor (IPSFC) telah direka dan dibangunkan di Makmal Aliran Tidakbalas Berkelajuan Tinggi (HiREF), Fakulti Kejuruteraan Mekanikal, Universiti Teknologi Malaysia (UTM) bagi menghasilkan pembakaran yang berprestasi tinggi dengan pelepasan emisi yang rendah. Kajian ini memfokuskan pelepasan pembakar berpusar yang rendah beroperasi dari beban haba 7 kW kepada 15 kW. Pembakar berpusar tanpa api telah diubahsuai untuk prapemanasan di mana udara segar melalui satu tiub heliks yang diletakkan di dalam kebuk pembakaran lalu memanaskan udara tersebut sebelum dimasukan kedalam kebuk pembakaran dalam beberapa eksperiment. Objektif kajian ini adalah untuk menyiasat secara terperinci peranan geometri salur masuk udara dengan dan tanpa prapemanasan udara ke atas prestasi pembakaran berpusar tanpa api tanpa penambahan gas sebagai pencair. Siasatan ke atas kesan konfigurasi suntikan berganda udara-bahan api mendapati bahawa kes SFR42 adalah konfigurasi terbaik untuk prestasi pembakaran optimum. SFR42 adalah pembakar berpusar dengan 4 salur masuk udara tangen dan 12 salur masuk udara paksi dengan 11 salur masuk bahan api sepaksi. Pelepasan NOx dan CO paling rendah direkodkan pada nisbah kesetaraan 0.8 dengan masing-masing bernilai 4 ppm dan 24 ppm. Secara umum keseragaman suhu yang merupakan satu ciri penting dalam pembakaran tanpa api didapati berubah dari 0.03-0.06 pada nisbah yang kesetaran berlainan. Kajian ini juga menunjukkan pembakaran berpusar tanpa api dengan dan tanpa udara tangen yang diprapanaskan telah dicapai. Secara keseluruhan, udara yang diprapanaskan telah menyumbang kepada peningkatan sebanyak 5% kecekapan haba berbanding dengan kes udara yang tidak diprapanaskan tetapi dengan peningkatan pelepasan NOx maksima settingi 4 ppm. Dalam tesis ini beberapa kajian simulasi dijalankan untuk menyiasat medan aliran terperinci dalam pembakar pusaran. Kajian numerikal didapati menghalkan penemuan yang hampir sama dalam mempastkan prestasi tinggi yang dicapai oleh eksperiment pada konfigurasi SFR42. Dalam konfigurasi ini sebahagian besar gerakan berpusar dihasilkan dalam pembakar dan ini membantu pencampuran yang baik antara bahan api dan pengoksida yang seterusnya membawa kepada pembakaran lengkap pada suhu puncak rendah. Keadaan tersebut seterusnya menyebabkan proses pembakaran berlaku dengan pelepasan emisi yang rendah.
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TABLE OF CONTENTS
CHAPTER
1
TITLE
DECLARATION
DEDICATION
ACKNOWLEDGEMENT
ABSTRACT
ABSTRAK
TABLE OF CONTENTS
LIST OF TABLES
LIST OF FIGURES
LIST OF ABBREVIATIONS
LIST OF SYMBOLS
LIST OF APPENDICES
INTRODUCTION
1.1 Research background
1.2 Problem Statement
1.3 Research Objectives
1.5 Significance of Research
1.6 Research Scope
1.7 Thesis Outline
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2
LITERATURE REVIEW
2.1 Introduction
2.2 Pollutant Formation
2.2.1 Nitrogen Oxides Formation
2.2.1.1 Thermal (Zeldovich) Mechanism
2.2.1.2 Prompt (Fenimore Mechanism)
2.2.1.3 N2O Intermediate Mechanism
2.2.1.4 Fuel NO
2.2.1.5 Fuel NO2 Formation
2.2.2 CO Formation
2.3 NOx Abatement Strategies
2.3.1 Injection of Diluents
2.3.2 Exhaust Gas Recirculation (EGR)
2.3.3 Exhaust Clean-up
2.3.4 Lean Premixed Combustion
2.3.5 The Swirling Generation
2.3.5.1 Turbulent Vortex Flow
2.3.6 Asymmetric Vortex Combustion
2.4 Flameless Combustion
2.4.1 Development of Flameless Combustio
2.4.2 Principles of Flameless Combustion
2.4.3 Flameless Combustion Investigation by
Various Researchers
2.4.4 Swirling Flameless Combustor Considerations
2.4.4.1 Reactive Gas Recirculation
2.4.4.2 Swirling Flows
2.4.4.3 Thermal Intensity
2.4.5 Benefits of flameless Combustion
2.4.5.1 NOx Reduction
2.4.5.2 Energy Saving
2.4.5.3 CO2 Reduction
2.4.5.4 Noise Reduction
2.4.6 Preheated Air in NOx Emission under
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3
4
Flameless Combustion
2.4.7 Effect of Diluent Gas
2.5 Numerical Studies in Flameless Combustion
2.6 Summary
RESEARCH METHODOLOGY
3.1 Introduction
3.2 Research Methodology Flowchart
3.3 Experimental Setup of Swirling Flameless Combustion
System
3.3.1 Development of Asymmetric Swirling
Flameless Combustion
3.3. 2 The Combustion Air Supply System
3.3.3 The Fuel System
3.3.4 Experimental Measurement
3.3.4.1 Flow Measurement
3.3.4.2 Temperature Measurement
3.3.4.3 Exhaust Gas Measurement
3.3.5 Combustion Observation
3.4 Cases Investigated
3.5 Thermal Efficiency
3.6 Combustible Mixture and Preparation
3.7 Experimental Procedure
3.8 Computational Study of Swirling Flameless
3.8.1 Grid Independence Test
3.8.2 Computational Cases of Vortex , Swirl and
Swirling Flameless Combustion
RESULTS AND DISCUSSION
4.1 Introduction
4.2 Experimental Swirling Combustion
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4.2.1 Effect of Air and Fuel Entry on Swirling
Combustion
4.2.2 Effect of Axial Air Flow on Swirling
Combustor
4.2.3 Validation of the Computational Study on
Swirling Combustion
4.2.3.1 Temperature Distribution
4.2.3.2 Velocity and Swirl Number
4.3 Swirling Flameless Combustion
4.3.1 Effect of Axial to Tangential Air on Swirling
Flameless Combustion
4.3.1.1 Temperature Distribution and
Exhaust Emissions
4.3.1.2 Velocity and Swirl Number
4.3.2 Effect of Location Axial Air Entry on
Swirling Flameless Combustion
4.3.2.1 Temperature Distribution
4.3.2.2 Exhaust Gas Analysis
4.3.2.3 Computational Study on the Effect
of Axial Air Entry on Swirling
Flameless Combustion
4.3.3 Effect of Preheat Tangential Air on Swirling
Flameless Combustion
4.3.3.1 Temperature Distribution and
Exhaust Emissions
4.3.3.2 Velocity and Swirl Number
4.3.4 Effect of Fuel Type on Swirling Flameless
Combustion
4.4 Visual Observation
4.5 Thermal Efficiency
CONCLUSIONS AND RECOMMENDATIONS FOR
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FUTURE RESEARCH
5.1 Conclusion
5.2 Suggestions for Further Study
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REFERENCES
APPENDICES A-C
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168-177
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LIST OF TABLES
TABLE NO
2.1
2.2
3.1
3.2
3.3
3.4
3.5
3.6
3.7
4.1
4.2
4.3
4.4
4.5
4.6
TITLE
Various names given to flameless combustion
Contribution to total NO form different mechanisms
Natural gas composition
Nominal accuracies for gas analyzer
Experimental parameters used to investigate swirling
combustion.
Experimental parameters used to investigate swirling
flameless combustion.
Boundary conditions
Numerical parameters for investigating vortex and
swirling combustion.
Numerical parameters for investigating Swirling
Flameless Combustion
Different cases of asymmetric vortex depending on the
location of air and fuel entry.
Asymmetric and swirling vortex combustion cases.
Recirculation factor with different cases SA4F4,
SA4F10, and SA10F11
Different cases depend on the ratio of axial to tangential
air entry
Recirculation factor with different cases SFR4, SFR43,
and SFR41
Different cases at varying axial air locations with
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4.7
4.8
4.9
4.10
4.11
equivalence ratio (= 0.5-1.2).
Temperature uniformity ratio for different cases
(different axial air location).
Recirculation factor with different cases SFR4, SFR2,
and SFR42.
Different cases with and without preheated tangential air
at equivalence ratio (0.5-1.2).
NOX measured of flameless combustion with various
configurations combustion.
Summary of the results of thermal efficiency at
equivalence ratio = 1.0.
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LIST OF FIGURES
FIGURE NO.
2.1
2.2
2.3
2.4
2.5
2.6
2.7
2.8
2.9
2.10
2.11
2.12
2.13
2.14
2.15
TITLE
NOx formation
NOx abatment strategies
Internal EGR system
External EGR system
Lean premixed combustor
Tangential entry swirling generator
Guide vanes swirling generator
Jet flow (a) low swirl (Sn˂ 0.4) and (b) high swirl
(Sn˃0.6)
Qualitative representation of typical profiles of (a)
tangential and (b) axial velocities in a confined vortex
flow possessing central recirculation zone.
Schematic of the asymmetric vortex combustor reported
by Gabler
Schematic of the asymmetric vortex combustor reported
by Saqr
Center recirculation zone (CRZ)
Photographs of the reaction zone in the HiREF flameless
furnace, (a) represent visible flame and (b) flameless
modes
Flameless oxidation burner
The stability limits are A. stable flame zone; B. instability
zone; C. flameless combustion zone
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2.16
2.17
3.1
3.2
3.3
3.4
3.5
3.6
3.7
3.8
3.9
4.1
4.2
4.3
4.4
4.5
Shown are (a) Different combustor geometries, (b) NOx
emissions for different combustors, and (c) CO emissions
for different combustors
Temperature of the FLOX combustor with time
Flowchart of the research methodology
Experimental set-up for swirling flameless combustion
Schematic of the IPSFC combustor showing (a) isometric
view, and (b) side view.
Internally air preheated system
Shown are locations of air and fuel in swirling combustor
for (a) case SA4F4, (b) case SA6F4 , (c) case SA8F4 , (d)
case SA4F10, (e) case SA6F10, (f) case SA8F10 and (g)
case SA10F11.
Shown are locations of air and fuel in swirling flameless
combustor for (a) case SFR4, (b) case SFR2 and (c) case
SFR42
Schematic of the swirling flameless combustor isometric
view.
Grid independence test.
Computational domain of swirling vortex combustor
Temperature distribution along the central axis of
chamber at different inlet conditions of asymmetric
vortex combustor
Average NOx emission at different inlet conditions for
asymmetric vortex combustor at stoichiometric
equivalence ratio.
Average oxygen concentration at different inlet
conditions for asymmetric vortex combustor at
stoichiometric equivalence ratio.
Average CO emission at different inlet conditions for
asymmetric vortex combustor at stoichiometric
equivalence ratio.
Temperature distribution along the central axis of
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4.6
4.7
4.8
4.9
4.10
4.11
4.12
4.13
4.14
4.15
4.16
chamber for cases SA4F4, SA4F10 and SA10F11 in
swirling combustion.
Effects of the equivalence ratio on NOx emissions for
cases SA4F4, SA4F10 and SA10F11 in swirling
combustion.
Effects of the equivalence ratio on O2 concentrations for
cases SA4F4, SA4F10 and SA10F11 in swirling
combustion.
Effects of the equivalence ratio on CO emissions for
cases SA4F4, SA4F10 and SA10F11 in swirling
combustion.
Comparison of experimental and numerical data on
temperature distribution along the central axis.
Temperature Contour on plane (A) and plane (B) with
iso-surfaces of the maximum temperature in the domain
to represent flame structure for Cases SA4F4, SA4F10
and SA10F11.
The contours of velocity distribution in the chamber for
Cases SA4F4, SA4F10, and SA10F10: left on plane (A)
and right on plane (B).
The velocity vector fields in the chamber for Cases
SA4F4, SA4F10, and SA10F10: left on plane (A) and
right on plane (B).
Swirl number variation along the central axis.
Chamber temperature as a function of time from
conventional combustion (A) to flameless combustion (B)
for Φ =1 in swirling flameless combustion of case SFR4.
Temperature distribution along the central axis in cases
SFR4, SFR41 and SFR42 at stoichiometric equivalence
ratio.
Effect of axial to tangential air ratio on NOx emissions
for swirling flameless combustion for cases SFR41,
SFR4, and SFR43 at different equivalence ratios.
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4.17
4.18
4.19
4.20
4.21
4.22
4.23
4.24
4.25
4.26
4.27
4.28
4.29
4.30
Effect of axial to tangential air ratio on CO emissions for
swirling flameless combustion for case SFR43, SFR4,
and SFR41 at different equivalence ratios.
Effects of the equivalence ratio on NOx emissions for
swirling flameless combustion Case SFR4 and swirling
combustion Case SA10F11.
Effects of the equivalence ratio on CO emissions for
swirling flameless combustion Case SFR4 and swirling
combustion Case SA10F11.
Predicted tangential velocity profiles at different axial
distances with case SFR4.
Predicted tangential velocity profiles at different axial
distances with case SFR43.
Predicted tangential velocity profiles at different axial
distances with case SFR41.
Swirl number variation along the central axis for cases
SFR4, SFR43, and SFR41.
The contours of velocity distribution in the chamber for
Cases SFR4, SFR43, and SFR41: left to right on plane
(A), (B), and (C), respectively.
The contours of vector velocity distribution in the
chamber for Cases SFR4, SFR43, and SFR41: left to right
on plane (A), (B), and (C), respectively.
Temperature distribution along the central axis at
different equivalence ratios in case SFR4.
Temperature distribution along the central axis at
different equivalence ratios in case SFR2.
Temperature distribution along the central axis at
different equivalence ratios in case SFR42.
Temperature distribution along the central axis at
stoichiometric equivalence ratio for different cases SFR4,
SFR2, and SFR42.
Effects of the equivalence ratio on NOX emissions for
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4.32
4.33
4.34
4.35
4.36
4.37
4.38
4.39
4.40
4.41
4.42
4.43
swirling flameless combustion for case SFR4, SFR2, and
SFR42.
O2 concentrations emissions with equivalence ratio for
swirling flameless combustion for cases SFR4, SFR2, and
SFR42.
Effects of the equivalence ratio on CO2 emissions for
swirling flameless combustion for cases SFR4, SFR2, and
SFR42.
Effects of the equivalence ratio on CO emissions for
swirling flameless combustion for cases SFR4, SFR2, and
SFR42.
Comparison of experimental and numerical data on
temperature distribution along the central axis.
The contours of temperature distribution along the central
axis distribution in the chamber for cases SFR4, SFR2,
and SFR42: left on plane (A) and right on plane (B).
(a) The contours of O2 mass fraction and (b) CO2 mass
fraction distribution along the plane A of the chamber for
cases SFR4, SFR2, and SFR42, respectively.
(a) The contours of NOx mass fraction and (b) CO mass
fraction distribution along the plane A of the chamber for
cases SFR4, SFR2, and SFR42, respectively.
Predicted tangential velocity profiles at different axial
distances with case SFR2.
Predicted tangential velocity profiles at different axial
distances with case SFR42.
Swirl number variation along the central axis
The contours of velocity distribution in the chamber for
Cases SFR4, SFR2, and SFR42: left to right on plane (A),
(B), and (C), respectively.
The velocity of vortex core region in the chamber for
cases SFR4, SFR2, and SFR42
The velocity streamline fields in the chamber for Cases
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4.44
4.45
4.46
4.47
4.48
4.49
4.50
4.51
4.52
4.53
SFR4, SFR2, and SFR42: left to right on isometric, front
view and top view respectively.
The axial velocity fields in the chamber for Cases SFR4,
SFR2, and SFR42: left to right on plane (A), (B) and (C)
respectively.
Temperature distribution along the central axis for case
with and without preheat tangential air at stoichiometric
equivalence ratio.
Average NOX concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR4 and SFR4, respectively.
Average NOX concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR2 and SFR2, respectively
Average NOX concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR42 and SFR42, respectively.
Average CO concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR4 and SFR4, respectively.
Average CO concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR2 and SFR2, respectively.
Average CO concentrations plotted against equivalence
ratio for cases with and without preheated tangential air,
PSFR42 and SFR42, respectively.
Predicted tangential velocity profiles at different axial
distances, (a) for case PSFR4 (with preheated tangential
air) and (b) for case SFR4 (without preheated tangential
air).
Predicted tangential velocity profiles at different axial
distances (a) for case PSFR2 (with preheated tangential
air) and (b) for case SFR2 (without preheated tangential
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4.55
4.56
4.57
4.58
4.59
4.60
4.61
4.62
air).
Predicted tangential velocity profiles at different axial
distances with (a) for case PSFR42 (with preheated
tangential air) and (b) for case SFR42 (without preheated
tangential air).
Swirl number variation along the central axis for cases
SFR4, SFR2, and SFR42 (without preheated tangential
air) and cases PSFR4, PSFR2, and PSFR42 (with
preheated tangential air) at stoichiometric equivalence
ratio.
The velocity of vortex core region in the chamber for
Cases SFR4, SFR2, and SFR42 (without preheated
tangential air) and cases PSFR4, PSFR2, and PSFR42
(with preheated tangential air) at stoichiometric
equivalence ratio.
Temperature distribution along the central axis at
stoichiometric equivalence ratio.
Average NOX concentrations plotted against equivalence
ratio with different types of fuel.
Average O2 concentrations plotted against equivalence
ratio with different types of fuel.
Average CO concentrations plotted against equivalence
ratio with different types of fuel.
Photographs of propane flames at different O2
concentrations.
Photographs of natural gas flames at different O2
concentrations
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LIST OF ABBREVIATIONS
NOX - Nitrogen Oxide
CO - Carbon Monoxide
CO2 - Carbon Dioxide
N2O - Nitrous Oxide
O2 - Oxygen
N2 - Nitrogen
LPG - Liquefied Petroleum Gas
NG - Natural Gas
CH4 - Methane
ppm - Part Per Million
CFD - Computational Fluid Dynamics
FLOX - Flameless Oxidation
HiTAC - High Temperature Air Combustion
MILD - Moderate or Intense Low Oxygen Dilution
LNI - Low NOX Injection
FODI - Fuel/Oxidant Direct Injection
IPFC - Internal Preheated Flameless Combustion
COSTAIR - Continuous Staged Air Combustion
EGR - Exhaust Gas Recirculation
Rtu - Temperature Uniformity Ratio
LHV - Lower Heating Value
HRS - High Cycle Regenerative Combustion System
CGRI - Canadian Gas Research Institute Burner
IFRF - International Flame Research Foundation
SCFH - Standard Cubic Feet Per Hour
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LIST OF SYMBOLS
T - Temperature (K ,° C)
- Equivalence ratio
MF - Mass flowrate of fuel
MA - Mass flowrate of air
ME - Mass flowrate of exhaust gas
- Mass flowrate
Ta - Air temperature
- Average temperature within the combustion chamber
Qin - Input power
Qout - Output power
- Thermal efficiency
Cp - Higher specific heat ∆T - Difference of temperature between two points
HF - Final enthalpy
HO - Initial enthalpy A,a - Air
F,f - Fuel
Ø - Diameter
ρ - Density v - Volume
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LIST OF APPENDICES
APPENDIX
A
B
C
TITLE
Experimental procedure for the flameless combustion
Calibration sheet of apparatus
List of publications
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CHAPTER 1
INTRODUCTION
1.1 Research Background
Heat and power, which are integral parts of our daily lives, are generally
produced via combustion processes. Excessive heat production and elevated global
warming are consequences of the process. Global warming is a topic of great
importance. According to the Intergovernmental Panel on Climate Change, averaged
over all land and ocean surfaces, temperatures warmed roughly 0.85 degrees Celsius
from 1880 to 2012 (IPCC 2013). Due to the gradual increase in the average
temperature of the earth, a permanent change of the earth's climate is expected. This
change poses a significant threat to human civilization. Combustion of fossil fuels
which is the primary cause of global warming. Fossil fuels are hydrocarbons, primarily
coal, fuel oil or natural gas, formed from the remains of dead plants and animals. The
fossil fuels is the main source of energy production in the world. It is related to the
emissions of potential pollutants and green-house gases. Hence, reducing combustion
emissions and improving the thermal efficiency of combustion systems are critical
challenges in designing thermal energy and power systems. Several combustion
techniques were developed to reduce emissions of pollutant gases.
2
Flameless combustion is one of these techniques. The main feature of flameless
combustion is the absence high temperature of flame front. The reaction takes place
uniformly throughout the combustion chamber well below the dissociation
temperature of N2, hence minimizing NOx formation. This form of combustion
features a low concentration of oxygen around 5% (Lezcano 2013). Therefore, the
ignition process of flameless combustion is characterized by slower chemical reaction
rates, uniform temperature distribution, wider reaction zones, and invisible flame. The
main operation principle for this technique lies in the concept of exhaust gas and heat
recirculation. The heat from the exhaust gases is used to raise the temperature of the
oxidant stream while, the exhaust gases are used to dilute the oxidant stream and hence,
reduce the oxygen concentration to maintain low temperature in the combustion zone.
As a result of this technique, less NO is formed (Dally, Riesmeier et al. 2004). The
name flameless refers to a negligible visible signature from the flames as compared to
conventional ones.
The recirculation of flue gas means that combustion products are recirculated
and mixed with fresh fuel and air streams. It is a key parameter in flameless
combustion. Recirculation is divided into two categories: internal and external. The
former category depends on burner design, while the latter is based upon the returned
flue gas to the combustor by an external pipe. In the internal, the flue gases are
circulated back to the combustion due to the burner aerodynamics. Recirculation and
superior mixing of air and fuel are highly significant in combustion processes.
Common procedures are used to create the recirculation and stabilization of the
combustion during swirl flow. This plays a critical role to recirculate the section of the
hot combustion product back toward the flame origin. Several approaches are used for
that process; the generation of swirling combustion by a tangential air entry in a
cylindrical combustor is one of them.
Swirling flameless combustion is employed in a direct injection of both air and
fuel, without any need for a flame stabilizer. To generate an auto swirling process, the
air is injected tangentially and axially to impart swirling without the use of swirlers
that are typically used in conventional combustors. Benefits of flameless combustion
3
technology are the ultra-low pollutant emissions, homogeneous temperature inside the
combustion chamber, and stable combustion.
Flameless is a promising combustion technology that can achieve the
combination of high efficiency and ultra-low emissions. It is based on mixing of fuel
and oxidizer and high flue gas recirculation. The separated fuel has high momentum,
and air flows entrain the flue gas through internal recirculation. Thus, the oxygen
concentration in the combustion zone is diluted. This leads to a more distributed heat
release rate of the chemical energy, thus avoiding the high peak temperatures and
reducing the pollutant emissions.
1.2 Problem Statement
In the nowadays strict emission regulations, environmental issues of power
generation play an important role in the economic viability of modern power plants.
To reduce harmful emissions, the current trend is to design industrial combustion
devices that operate with high efficiency and low emissions. One of these harmful
emissions is NOx from combustion processes. One of the most effective method of
reducing NOx is the design and implementation of flameless combustion. To achieve
flameless combustion, there are two fundamental requirements to be achieved
(Wünning and Wünning 1997, Lille, Blasiak et al. 2005).
1. The combustion temperature within the chamber should be greater than the
auto ignition temperature of the mixture (E.g., 800 °C for natural gas/air)
(Wünning and Wünning 1997, Cavigiolo, Galbiati et al. 2003).
2. The flue-gas recirculation ratio (Kv) between fuel, oxidizer and diluted gas
(flue gas, N2 or CO2) should be greater than ‘three’ (>3) (Wünning and
Wünning 1997, Flamme 2001).
4
A key point necessary for efficient design of a flameless combustor is to ensure good
mixing between the incoming fresh fuel/air mixture and the re-circulated hot burnt
gases. Adequate and fast mixing between the injected air and the internally re-
circulated hot reactive gases to form hot and diluted oxidant is critical for flameless
combustion, followed by rapid mixing with fuel. Many researchers used diluted gases
like CO2 and/or N2 that are injected into the combustion chamber to achieve high
circulation required for flameless combustion. Swirl is a phenomenon known to help
combustion. Many researchers used vanes or tangential entry to generate swirl. Some
researcher proposed introduction of swirl with tangential entry using asymmetric
vortex combustor. In this study asymmetric vortex combustion (AVC) concept is used
as the basic design for the flameless combustion system (Saqr 2011). However the
(AVC) by Saqr has some problem regarding the low temperature region near the
center. In vortex combustion, where there are no axial air such as in AVC, the process
of flame stabilization and mixing in AVC is concentrated near the circumferential wall
of the combustor. The temperature at the center of the combustor is to be relatively
low compared with wall combustor. This is justified by the presence of CRZ which
entrains ambient air into the combustor (Saqr 2011). This situation is not good for
flameless combustion. The axial component of the reacting flow within the combustor
is essential, and this is normally achieved by introducing a swirl motion generated by
the interaction between axial and tangential air velocity components.
This study focuses on a new combustor that solves the problem by achieving a
swirling flameless combustion with high recirculation, and without gas dilution. A
modified design is proposed for a flameless combustor with a high recirculation for
fast mixing. This combustor configuration adopts the previous asymmetric vortex
geometry proposed by Saqr (Saqr 2011). The concept of vortex flame provides flame
stability by stabilizing the reaction zone on the boundary of a forced vortex field, which
allows rapid mixing between air and fuel upstream of the reaction zone. Therefore, the
vortex flame demonstrates the visual characteristics of a premixed flame, although it
is a non-premixed flame. Therefore, the stability is radically enhanced while avoiding
the typical drawbacks of premixed flames.
5
This involves the investigation of the effects of burner geometry, air preheating
and swirling on flameless combustion efficiency as well. Current research focuses
also on the development of combustion technology, aiming at reducing NOx emission
while increasing combustion efficiency.
1.3 Research Objectives
This study focuses on the newly designed asymmetric swirling flow
combustion system. The objectives of this present work are:
1. to analyze experimentally the effects of multiple air-fuel injection
configurations on swirling flameless.
2. to evaluate the effect of air preheating on thermal efficiency of
swirling flameless combustion.
3. to investigate numerically the gas recirculation and fuel-air mixing
characteristics for different flow configuration swirling flameless
combustion.
1.4 Significance of Research
In this study a new design of a flameless combustor called the Internally
Preheated Swirling Flameless Combustor (IPSFC) has been proposed, developed,
fabricated and investigated. This study has practical applications in production
industries in general. It also has a significant contribution in solving the problem of
global warming and reduction of depletion of ozone layer. It also contributes in
supporting the relevant industries such as gas turbines, to obtain more efficient
combustion process. A new combustor configuration is designed to achieve a swirling
6
flameless combustion without the addition of gas dilution (e.g N2, CO2 etc.). To the
best of author’s knowledge, the present study is the first study of its kind, in swirling
flameless combustion.
1.5 Research Scope
The research scope covers the design and manufacture of a laboratory scale
flameless combustor called HiREF Internally Preheated Swirling Flameless
Combustor (IPSFC-HiREF). Computational and experimental approaches are used in
this research. The experimental component is focused on the characteristics of swirling
flameless combustion under different locations of axial air inlets. Three types of
hydrocarbon gases are utilized: natural gas, propane, and diluted methane. Nitrogen
oxides (NOx), carbon monoxide (CO), carbon dioxide (CO2) emissions, and oxygen
(O2) concentrations are measured in the exhaust gas during the experiments. The effect
of axial to tangential air ratio induction on the swirling flameless combustion
performance for natural gas is studied. Effects of the equivalence ratios on the pollutant
emissions are determined. These equivalence ratios are in the range between 0.5 and
1.2. The effect of diluted methane (CO2 diluted) on the swirling flameless combustion
process is also investigated. Numerical investigations are performed to calculate the
recirculation ratio and swirling number of the combustor in each case study. In the
study, swirling flameless combustion was investigated for two cases: with and without
tangential air preheating.
7
1.6 Thesis Outline
This thesis consists of five chapters. Chapter one introduces the present study.
Chapter two is a twofold literature review covering: (i) pollutant emissions with an
emphasis on nitrogen oxides (NOx), and (ii) a review of past and current studies on
flameless combustion. In chapter three, the design criteria for swirling flameless
combustion are listed with emphasis on reactive gas recirculation and recirculation
enhancement, swirl generation, and mixing fuel and air. Chapter 3 also presents a
discussion of the equipment, as well as the methodology employed in all phases in the
present study. A thorough discussion of the results then follows in chapter four. The
thesis finishes with chapter five, which contains the conclusion that precedes
recommendations for future research based on our findings.
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