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Flame Fundamentals
KAUST CISS 2018
April 1, 2018
Kaoru MARUTA,
Institute of Fluid Science, IFS
Tohoku University, Sendai, Japan
KAUST SS 2018
Kaoru MARUTA
2
KAUST SS 2018
Kaoru MARUTA
Tohoku University, Sendai, Japan
• City of Trees, 300
km north of Tokyo
• Found as third
university in Japan
on 1907
• Mission statements
-Research first
-Open doors
-Practice-oriented
R&E
Tokyo
Sendai
3
KAUST SS 2018
Kaoru MARUTA
• Kaoru Maruta, Professor
Institute of Fluid Science
(IFS), Tohoku University
• 1993 -1999
IFS, Tohoku Univ.
• 1999 Akita Pref. U.
Visit: USC, UCB
• 2002-Present
IFS Tohoku U.
IFS: 25 laboratories, 30 Faculties,Fluid-related research instituteMolecules, Rarefied, FD, Combustion, Plasma, SW, Bio- & Med Flow, Energy, Aerospace
Microgravity experiments at 10 sec, 490 m freefall, droptower in JapanCounterflow flame, flammability limit mechanism, Radiative extinction2010- Comprehensive limitAirplane, will be in Space
High Temperature Air Combustion Tech. (HiCOT), mild combustionFurnace, Reformer, Incinerator2011- High Temp. Oxy. Comb.
Microscale combustion, MicrocombustionMicrocombustor for heat sourceMicro flow reactor with controlled temperature profileKinetics study, super lean E/G combustion
Acknowledgements to collaborators:
• Professor Emeritus Takashi Niioka, Tohoku Univ.
• Professor Yiguang Ju, Princeton Univ.
• Professor Sergey Minaev, Far Eastern Federal Univ.
• Dr. Roman Fursenko, ITAM, SB RAS
• Professor Nam IL Kim, KAIST
• Professor Takeshi Yokomori, Keio Univ.
• Professor Hisashi Nakamura, Tohoku Univ.
• Mr. Susumu Hasegawa, Mr. Takuya Tezuka, Tohoku Univ.
• All other collaboration researchers, postdocs, and students
4
KAUST SS 2018
Kaoru MARUTA
Prof. Niioka
Prof. Ju
Prof. Minaev
Prof. Nakamura Mr. Hasegawa Mr. Tezuka Prof. Yokomori
Prof. N.I. Kim
Dr. Fursenko
Contents of Flame Fundamentals
• Part 1 Flame basics
• Part 2 Flammability limits
• Part 3 Flames under extreme conditions
5
KAUST SS 2018
Kaoru MARUTA
Part 1: Flame basics
• Introduction
• S-curve
• Premixed flame
• Non-premixed flame
• Flame characteristics
6
KAUST SS 2018
Kaoru MARUTA
Flame classification
• Premixed and non-premixed
(diffusion) flames
• Laminar and turbulent flames
*: www.nasa.gov
*
*
7
KAUST SS 2018
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Premixed and non-premixed flame
Non-premixed flame Premixed flame
(Diffusion flame)
8
FOF + O
**: Energy dynamics laboratory
KAUST SS 2018
Kaoru MARUTA
Fuel + Air (oxidizer)
Stabilized and propagation flames 9
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10Laminar and turbulent premixed flames
Turbulent premixed flame (Schlieren image)
Laminar flame(Direct photo)
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11Combustion in practical devices
• Turbulent combustion
• Reciprocating engines
Premixed combustion in Otto-
cycle engine (Spark-Ignited
engine, Gasoline engine)
Auto-ignited non-premixed (or
partially premixed) combustion in
Diesel engine (Compression
ignition engine)
• Gas turbine engine
Different types of GT, Premixed
and non-premixed combustion
• Furnace, incinerator
Mostly non-premixed, specific
combustion-mode (Mild
combustion)
The Jet Engine, Rolls-Royce, 1992
KAUST SS 2018
Kaoru MARUTA
World first micro-G exp. (1954) Kumagai
High
speed
com
bu
stion
researchComb. Inst. 1954
12Science and technology developments and combustion research
1950
2020
2000
1900
Steam engine, IC engines Otto, Diesel
Manned powered flight
WW II
Ford Model T, mass production Prop plane
Jet engine
Laser, invention・・・
Applications
Computer, Invention・
DevelopmentSpread
Super computing
Ro
ckets, V-II, V
osto
k, Saturn
V…
….
Periodic table(1869)Dmitri Mendeleev
ElectronAtom, Molecule,Proton, Neutron,
Elementary particles
First Comb. Symp. 1928
Third, 1948
Co
mb
ustio
n th
eory (A
symp
totic an
alysis……
)
Co
mp
utatio
ns
Laser diagn
ostics
Stud
y on
Co
mb
ustio
n Lim
its(M
inin
g safety)
Microgravity experiments (drop tower,
airplane, space shuttle,
IIS)
The Chemical History of a Candle (1861) Michael Faraday
Chemical kineticsHydrogen, hydrocarbon, PAH
Quantum chemistry, Ab initio
KAUST SS 2018
Kaoru MARUTA
Part 1: Flame basics
• Introduction
• S-curve
• Premixed flame
• Non-premixed flame
• Flame characteristics
13
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14
Stable solution
Stable solution
Unstable solution
• Time scales of
transport and chemical
reaction
• Extensively applicable
to various phenomena,
e.g., candle flame,
burner flame,
counterflow flame,
supersonic combustion,
etc.
S-curve (Fendell curve)
IgnitionExtinction
Damköhler number, D
𝑇 𝑚𝑎𝑥
(
𝑚…
)
𝐷 =𝐹𝑙𝑜𝑤 𝑟𝑒𝑠𝑖𝑑𝑒𝑛𝑐𝑒 𝑡𝑖𝑚𝑒
𝐶ℎ𝑒𝑚𝑖𝑐𝑎𝑙 𝑡𝑖𝑚𝑒
Liñán, A., Acta Astro. 1(7) 1007 (1974).
Fendell, F.E., J. Fluid Mech. 21(2) 281 (1965).
KAUST SS 2018
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15Chemical reactor and combustion
• Ignition
• Combustion
• Extinction
CSTR
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16Analogy between combustor and reactor
Batch CSTR
The Modal Shop, Inc., 2017
Meere et al., J. Eng. Math. 44: 57, 2002.
ST
RCM
GT
The Jet Engine, Rolls-Royce, 1992
Dagaut, ICFD 2016
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Kaoru MARUTA
Time scales of reactive fluids 17
1 s
10-2s
10-4s
10-6s
10-8s
10-10s
Flow time
Transport timeMolecularTurbulent
NO formation
Product formation H2O
Radical formation H
Radical formation H2O2
quasi-steady state?
Radiation transferquasi-steady state
Chemical time Physical time
DNS Time-step
Physical interest
?
Ju, ICFD, 2008
KAUST SS 2018
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Time scales of chemical reactions
Lu et al., Prog. Energ. Comb. Sci. 35: 192 (2009).
18
• Distributions of ignition time scale (Residence time @1 ms, 2000 K)
• Pico-sec~milli-sec or even longer
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Seeking for “ideal” ignition phenomena 19
The Modal Shop, Inc., 2017
Meere et al., J. Eng. Math. 44: 57, 2002.
http://c3.nuigalway.ie
ST
RCM
High Purity
Photolysis Shock
Tube (NASA Tube), Stanford Univ.
Kinetics Shock
Tube (KST),
Stanford Univ.
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Seeking for “ideal” flames 20
?• Difficult to establish ideal
(probably one-dimensional,
adiabatic) flames without
influences of external factors
• Detailed data from ideal flames
are essential for establishing
computational tools, precise
kinetics, etc.
?
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21Chemical kinetics modeling
Homogeneous rector
0D model
Senkin, 1988
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Part 1: Flame basics
• Introduction
• S-curve
• Premixed flame
• Non-premixed flame
• Flame characteristics
22
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Fuel + Air
Flash back
Blow off
Bunsen flame
Flame propagation, laminar burning velocity, flame
quench, extinction, blow off, flame structure
23
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24
- Flame is interface separating unburned and
burned gases, thermodynamic equlibrium
- Transport in preheat
zone, diffusion
processes of mass and
heat
- Reaction sheet, source
of heat and sink of
reactant
- If Le =1, Y and T profiles
are mirror images
- Preheat and
Reaction zones
(Rankine-Hugoniot Relations,
→ detonation and deflagration waves)
Law, C.K., Combustion Physics, 2006.
Laminar premixed flame (Deflagration wave) KAUST SS 2018
Kaoru MARUTA
1-D steady propagating flame
Continuity
PREMIX, CHEMKIN
Forward rate
coefficient
25
Energy
Species
Equation of state
Governing equation for steady, isobaric, adiabatic one-dimensional flame propagation
For further details, refer, e.g., Poinsot, Theor. Num. Comb.
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26
! GRI-Mech Version 3.0 7/30/99 CHEMKIN-II format
! See README30 file at anonymous FTP site unix.sri.com, directory gri;
! WorldWideWeb home page http://www.me.berkeley.edu/gri_mech/ or
! through http://www.gri.org , under 'Basic Research',
! for additional information, contacts, and disclaimer
ELEMENTS
O H C N AR
END
SPECIES
H2 H O O2 OH H2O HO2 H2O2
C CH CH2 CH2(S) CH3 CH4 CO CO2
HCO CH2O CH2OH CH3O CH3OH C2H C2H2 C2H3
C2H4 C2H5 C2H6 HCCO CH2CO HCCOH N NH
NH2 NH3 NNH NO NO2 N2O HNO CN
HCN H2CN HCNN HCNO HOCN HNCO NCO N2
AR C3H7 C3H8 CH2CHO CH3CHO
END
!THERMO
! Insert GRI-Mech thermodynamics here or use in default file
!END
REACTIONS
2O+M<=>O2+M 1.200E+17 -1.000 .00
H2/ 2.40/ H2O/15.40/ CH4/ 2.00/ CO/ 1.75/ CO2/ 3.60/ C2H6/ 3.00/ AR/ .83/
O+H+M<=>OH+M 5.000E+17 -1.000 .00
H2/2.00/ H2O/6.00/ CH4/2.00/ CO/1.50/ CO2/2.00/ C2H6/3.00/ AR/ .70/
O+H2<=>H+OH 3.870E+04 2.700 6260.00
O+HO2<=>OH+O2 2.000E+13 .000 .00
O+H2O2<=>OH+HO2 9.630E+06 2.000 4000.00
O+CH<=>H+CO 5.700E+13 .000 .00
O+CH2<=>H+HCO 8.000E+13 .000 .00
O+CH2(S)<=>H2+CO 1.500E+13 .000 .00
O+CH2(S)<=>H+HCO 1.500E+13 .000 .00
O+CH3<=>H+CH2O 5.060E+13 .000 .00
O+CH4<=>OH+CH3 1.020E+09 1.500 8600.00
O+CO(+M)<=>CO2(+M) 1.800E+10 .000 2385.00
LOW/ 6.020E+14 .000 3000.00/
H2/2.00/ O2/6.00/ H2O/6.00/ CH4/2.00/ CO/1.50/ CO2/3.50/ C2H6/3.00/ AR/ .50/
O+HCO<=>OH+CO 3.000E+13 .000 .00
O+HCO<=>H+CO2 3.000E+13 .000 .00
O+CH2O<=>OH+HCO 3.900E+13 .000 3540.00
O+CH2OH<=>OH+CH2O 1.000E+13 .000 .00
O+CH3O<=>OH+CH2O 1.000E+13 .000 .00
O+CH3OH<=>OH+CH2OH 3.880E+05 2.500 3100.00
O+CH3OH<=>OH+CH3O 1.300E+05 2.500 5000.00
O+C2H<=>CH+CO 5.000E+13 .000 .00
O+C2H2<=>H+HCCO 1.350E+07 2.000 1900.00
O+C2H2<=>OH+C2H 4.600E+19 -1.410 28950.00
O+C2H2<=>CO+CH2 6.940E+06 2.000 1900.00
O+C2H3<=>H+CH2CO 3.000E+13 .000 .00
O+C2H4<=>CH3+HCO 1.250E+07 1.830 220.00
O+C2H5<=>CH3+CH2O 2.240E+13 .000 .00
O+C2H6<=>OH+C2H5 8.980E+07 1.920 5690.00
O+HCCO<=>H+2CO 1.000E+14 .000 .00
O+CH2CO<=>OH+HCCO 1.000E+13 .000 8000.00
O+CH2CO<=>CH2+CO2 1.750E+12 .000 1350.00
GRI-Mech 3.0 (1999)
53 species
327 reactions
+Transport dataThermodynamic data
GRI-Mech 3.0, <http://www.me.berkeley.edu/gri_mech/>.
Cont’d
KAUST SS 2018
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Example of reaction path, methane oxidation 27
Reactant
Product
Inte
rme
dia
tes
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Laminar burning velocity and burning flux
Laminar flame speed, SL Laminar burning flux, r SL
28
Figures: Law, C.K., Combustion Physics, 2006.
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Structure of laminar one-dimensional premixed flame
0
500
1000
1500
2000
0.000
0.050
0.100
0.150
0.200
0.250
0 0.05 0.1 0.15 0.2x, cm
Tem
pe
ratu
re, K
Mo
le f
ract
ion
, -
CH4/air, f = 1
O2
CH4
Temperature
H2O
CO2
CO
29
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Approximate analysis, Mallard-Le Chatelier, 1880’s
• Region of conduction(ZONE I)and region of burning(ZONE II)
• Intuitive recognition for reaction zone thickness, laminar burning velocity
30
Glassman, Combustion, 1987.
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31
Delete
Incoming flow speed = reaction rate
Temperature increase of unburned gas is due to conduction heat from reaction zone
Delete
: overall one-step reaction
Pressure dependence of SL
Glassman, Combustion, 1987.
Approximate analysis, Mallard-Le Chatelier, 1880’sKAUST SS 2018
Kaoru MARUTA
Laminar flames with different inert gas
• Thermal diffusivities of Ar and
N2 approximately equal
• Since Ar is monoatomic gas, its
specific heat is lower than N2.
• Since heat release is the same,
flame temperature, Tf, Ar > Tf, N2
• Ar and He are both
monoatomic and thus their
flame temperatures are equal,
however, thermal diffusivity of
He is much larger than Ar.
Consequently, SL of He case is
much larger than Ar.
Clingman et al., Symp. (Int.) Combust. 4, 310, (1953).
32
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33Simplification of governing equations
Zeldovich, Williams, Clavin,
Liñán, Matalon,
Poinsot, T., Theoretical and
Numerical Combustion, 3rd eds.
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35Simplification leads to “master equation” of LPF
Y = YF YF1 θ =
Cp T − T1)
QYF1 =
T − T1
T2 − T1
YF1
∕ CpT2 −T1
ρ1sLdYFdx
=d
dxρD
dYFdx
+ 𝜔𝐹
ρ1Cp sL
dT
d𝑥=d
dx𝜆dT
dx−Q 𝜔𝐹
ρ1sLd Y+ 𝜃
dx=d
dx𝜆d Y+ 𝜃
dx
𝜃 + Y = 1
ρ1sLd𝜃dx
=ddx
𝜆
𝐶𝑝
d𝜃dx
−B1 T1 + 𝜃 T2 − T1
𝛽1𝜌 1 − 𝜃 exp −
Ta1
T1+θ T2−T1
𝜔T
Scaled variables
If Le = 1 𝐷 =𝜆
𝜌𝐶𝑝
Only one variable left: reduced temperature, progress variable
Chemical enthalpy + sensible enthalpy = Constant
Spalding, D.B., Proc. Roy. Soc.
London. Ser. A 240(1220) 83 (1957).
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T. Poinsot, Princeton SS Lecture note, 2015.
36Flame characteristics and related topics
• Laminar burning velocity
• Adiabatic flame temperature
• Flame stretch
• Flame quench
• Flammability limits
• Quenching diameter
• Excess enthalpy combustion
• Flame instability
• Mild combustion
• Micro-scale combustion
37Adiabatic one-dimensional premixed flame
• Ideal flame is hard to realize because…
• Effect of heat loss
• Effect of flow non-uniformity
• Effect of wall (Thermal and chemical)
• Intrinsic flame instabilities
• Thus, measurement of laminar burning velocity needs various ideas & technique
• Laminar burning velocity → (eigenvalue of the governing equations) essential for chemical time determination, kinetics developments, etc.
Adiabatic (1-D planar flame)X
T
Non-adiabatic (1-D planar flame)
T
X
? ?
Adiabatic 1D planar premixed flame
Lowry, W., et al., J. Eng. Gas Turb. Power 133: 091501 (2011).
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Laminar burning velocity, methane-air flame
(1),(4),(7) Chamber (2) Flat flame (3) Propagating tube (5),(6) Burner flame
(7)
38
Equivalence ratio, f
Lam
inar
burn
ing
velo
city,
cm
/s Methane-air, 0.1 MPa
Fundamentals of Combustion Phenomena, Ohm. 2001 in Japanese.
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Variation of measured laminar flame speeds
Egolfopoulos et al., Prog. Energ. Combust. Sci. 43 (2014) 36.
39
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40Measurements of laminar burning velocity
• Burner method
• Flat flame
• Outwardly propagating
spherical flame
• Counterflow flames
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Bunsen flame and laminar burning velocity
• Flame propagate to flow
stream with angle a
• Laminar burning velocity could
be obtained from a and
41
Kobayashi lab., TOHOKU U.
Flame front
Mixture
Fundamentals of Combustion Phenomena, Ohm. 2001 in Japanese.
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𝑆𝑢 = 𝑈𝑢 sin 𝛼
𝑈𝑢
Burner stabilized flat flame
• Flame is stabilized above porous material where flow velocity profile is flat
• Once flame is stabilized, local flow velocity could be equal to laminar burning velocity
• Effect of heat loss from flame to porous material could not be ignored
• Effect of buoyancy is significant at low flow velocity
42
Figure: Law, C.K., Combustion Physics, 2006.
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Modern flat flame burner
• Effect of heat loss to the burner plate could be canceled
• High fidelity measurement of laminar burning velocity by flat flame is enabled
L.P.H. de Goey et al., Eindhoven TU, 2011-
43
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Counterflow premixed twin flames
• One dimensional flame
• No conductive heat loss
• Flow could be
characterized by an
unique parameter
– stretch rate
淀み面
火炎面
x
混合気
燃料
酸化剤+
44
Flame fronts
Stagnation
plane
Mixture
(Fuel +
Oxidizer)
Commonly used basic flame geometry,
general characterization of flame
→ Flame stretch!
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Counterflow premixed flame and laminar burning velocity
Egolfopoulos et al., Prog. Energ. Combust. Sci. 43 (2014) 36.
45
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Flame stretch and Lewis number effect
• Lewis number: ratio
of mass and thermal
diffusions
With the increase of stretch
rate, flame temperature
increases if Le < 1 and
decreases if Le > 1
46
Figures: Law, C.K., Combustion Physics, 2006.
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𝐿𝑒 =𝛼
𝐷𝛼 =
𝜆
𝜌𝐶𝑝where
• Local minimum of axial velocity profile corresponds to burning velocity at given stretch rate
• Linear extrapolation to zero stretch rate provides stretch-free laminar burning velocity of given mixture
Law, Symp. (Int.) Combust. 22, 1381, (1988).
47Counterflow premixed flame and laminar burning velocityKAUST SS 2018
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Outwardly propagating spherical flame
• If a quiescent mixture is
ignited, outwardly
propagating spherical
flame is observed
• When the size of the
spherical flame is small,
effect of the pressure
increase can be negligible
• Laminar burning velocity
can be measured if the
effect of flame stretch is
considered
• Applicable to high pressure
CH4/air, f=0.65
48
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• Estimating relative flame
speed Su to the mixture from
nominal flame velocity Sb
• Density ratio was estimated
from temperature ratio
• Need to consider the effects
of other factors, in particular,
effect of flame radius
49Outwardly propagating spherical flame
Commonly used basic flame geometry
Simple but essential flame physics involved
Flame front
Burned gas
Mixture
Need to consider the effects of other factors,
e.g., ignition energy, stretch rate, etc.
→ Flame stretch!
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Stretch rate
• Effects of flow non-
uniformity, flame
curvature, and flame/flow
unsteadiness can be
described by the single
parameter
• Three factors for flame
stretch are aerodynamic
strain, flame curvature
and flame motion
Flame stretch rate
50
Law, C.K., Combustion Physics, 2006.Chung and Law, CNF 55(1), 123-125, 1984.
Matalon, CST 31(3-4), 169-181, 1983.
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Examples of stretched flames 51
Figures: Law, C.K., Combustion Physics, 2006.
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52Determination of laminar burning velocity by linear extrapolation
𝑘 =2
𝑅𝑓
𝑑𝑅𝑓
𝑑𝑡
Figure: Law, C.K., Combustion Physics, 2006.
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53
0.0 1.0 2.0 3.0 4.0 5.00.0
1.0
2.0
3.0
4.0
5.0
6.0
Time after Ignition t [ms]
Mean
Fla
me R
ad
ius
rm
[m
m]
H2/N2/AIRP0 =0.101MPa
T0 =298K
SL0 =25cm/s
:0.3, 11.4:0.5, 11.4
:H2
D =0.1mm
W =0.5mm
:0.7, 11.4:0.9, 16.2
f
:1.2, 193.6
Ei[mJ]
0 5 10 150.0
0.5
1.0
1.5
2.0
2.5
3.0
Mean Flame Radius rf [mm]
SL
l /
SL∞
[-]
H2/N2/AIR
P0=0.101MPa
T0=298K
SL0=25cm/s 0.3
0.50.70.9
f
1.0
Ei =53 mJ (f=1.0) Ei =35 mJ (f=0.9) Ei =11 mJ (f=0.3,0.5,0.7)
Ei =194 mJ (f=1.2)
1.2 D[mm] 0.1 1.2 W[mm] 0.5, 4
For Meso rf < 5 mm
forf =0.3 -0.9
forf=1.0 forf=1.2
Meso Macro
Derivation of LBV from outwardly propagating spherical flame
Theoretical prediction Experimental results
Chen, Burke, Ju, PCI 33, 1219 (2011). Nakahara, M., et al., PCI 34, 703 (2013).
Figures: courtesy of Prof. Nakahara of Ehime U.
𝑘 =2
𝑅𝑓
𝑑𝑅𝑓
𝑑𝑡
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54
Figures: Ju, Y., Princeton SS, 2017.
Chen, Burke, Ju, PCI 33, 2011.
Derivation of LBV from outwardly propagating spherical flameKAUST SS 2018
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Spherical propagating flame at high pressure conditions
Burke et al., Combust. Flame, 156-4, 2009, 771.
55
Lead to realize comprehensive H2/O2 kineticsBurke, M.P., et al., Int. J. Chem. Kinet. 44(7) 444 (2012).
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Part 1: Flame basics
• Introduction
• S-curve
• Premixed flame
• Non-premixed flame
• Flame characteristics
56
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Non-premixed flames
• Fuel and oxidizer initially
spatially separated
• If subsequent mixing is
not sufficiently fast, the
mixing and reaction occur
in thin reaction zone
• Fuel and oxidizer are
mainly transported
thorough diffusion
processes
57
Fundamentals of Combustion Phenomena, Ohm. 2001 in Japanese.
FuelOxidizer
Temperature
FO
Mixing
layer
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Non-premixed flames
• a. Typical configuration of
non-premixed flame
• b. Fuel and oxidizer are
transported through
diffusion (+ convection).
Since reactions occur at
finite rate and reaction zone
thickness is finite, some
reactants are leaked
• c. Reaction of non-premixed
flame often regarded as
infinitely fast and thus
reaction zone is regarded
as a sheet and no leakage
of reactants from there
58
Figures: Law, C.K., Combustion Physics, 2006.
a.
b.
c.
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Counterflow non-premixed flames
• Non-premixed flame
established in
counterflow field or in
forward stagnation
region in front of a
porous cylinder
(Tsuji burner)
• one-dimensional
stretched flame for basic
flame study, structure,
extinction limits, etc.
http://yoshidaweb.web.fc2.com
59
Figures: Law, C.K., Combustion Physics, 2006.
Tsuji burner
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Energy Dynamics Lab. Tohoku U.
Structure of counterflow non-premixed flame
Stretch rate, 56 sec-1
Temperature and species concentration profiles were measured.
Contribute to the development of computational code, e.g., CHEMKIN.
Tsuji, Yamaoka, Symp. (Int.) Combust. 13, 723, 1971.
Tsuji, H., Prog. Energ. Combust. Sci. 8(2), 93, 1982.
60
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61
Non-premixed flame of methane and air
stabilized in a forward stagnation region
in front of a porous cylinder
Tsuji burner
Prof. Tsuji
Droplet combustion
• One of the representative
fundamental non-premixed
flames
• The world’s first scientific
experiments conducted
under microgravity (1950’s)
by Seiichiro Kumagai of
Univ. of Tokyo
• Find D2-law
• And…then
62
Isoda, Kumagai, Symp. (Int.) on Combust. 7, 523 (1958).
Kumagai, Isoda, Symp. (Int.) Combust. 6. 726 (1957).
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Droplet combustion in Space
• Droplet combustion has been extensively contributed to the understandings of spray combustion to date
• Finally, cool burning flames of free droplet observed in International Space Station (ISS) in 2008-2009 (Prof. F.A. Williams of UCSD & collaborators)
63
http://jacobsschool.ucsd.edu/news/news_releases/release.sfe?id=1548
https://www.youtube.com/watch?v=BxxqCLxxY3M
Nayagam, V., et al., Combust. Flame 162(5) 2140 (2015).
Nayagam, V., et al., Combust. Flame 159(12): 3583 (2012).
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Part 1: Flame basics
• Introduction
• S-curve
• Premixed flame
• Non-premixed flame
• Flame characteristics
64
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65Flame characteristics
• Flame quench
• Flammability limits
• Quenching diameter
• Excess enthalpy combustion
• Flame instability
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0
0.5
1
0 0.2 0.4
Heat loss parameter, l
Bu
rnin
g ve
loci
ty p
aram
eter
, μ
𝜇2 ln 𝜇2 = − 𝑙
1 𝑒
1 𝑒
Theory of flame quench, thermal
Adiabatic (1-D planar flame)X
T
Non-adiabatic (1-D planar flame)
T
X
20
2 p
d T dTmc q L
dx dx
Flow direction
66
Adiabatic 1D planar premixed flame
Non-adiabatic 1D planar premixed flame
Zel’dovich, Y.B., Zhurn. Eksp. Teoret. Fiz. 11, 159 (1941).
Spalding, D.B., Proc. Royal Soc., Ser. A 240(1220) 83 (1957).
Clavin, P., Acta Astronautica 3(3): 223 (1976).
Williams, F.A., Combustion Theory, 1985.
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67
• Mixture is only
flammable within a
certain range of the
equivalence ratio
• What is the mechanism
of fundamental
flammability limits?
Equivalence ratio← Fuel lean Fuel rich →
Lam
inar
bu
rnin
g ve
loci
ty (
cm/s
)
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68Flame quench and fundamental flammability limit
Burning velocity against mixture ratio.
a, experimental findings;
b, prediction of all theories neglecting heat losses;
c, prediction of present theory, taking account of heat losses;
d, prediction of Weinberg's theory, neglecting heat losses and radicle-
generation other than branching reaction.
Spalding, D.B., Proc. Royal Soc., Ser. A 240(1220) 83 (1957).
What is the loss mechanism?
The question of a long time; solved by microgravity experiments in 1990’s.Part 2
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Quenching diameter
• Determined from the
ratio of heat generation
and heat loss
• Analogy with
flammability limit
2
2 2( ) ( 4)( )
4( ) ( )
p f u f
f
f f u
c T T dHeat lossH Nu d
Heat generation d h T T
2q fd e Nu
69
Part 3
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70Excess enthalpy combustion
Weinberg, F.J., Symp. (Int.) Combust. 15(1) 1 (1975).
a. Ordinary combustion
1→2→3→4→5
b. Excess enthalpy combustion
1→1’→2’→3’→3’’→4→5
T
X
12
34 5
1’2’
3’ 3’’
Adiabatic flame temp.
Ambient temperature
Weinberg, F.J., Combustion temperatures: The
future ?, Nature 233, 239 (1971).
• Higher maximum temperature than adiabatic flame temperature
• Wider flammability limits
• Fuels with low calorific values applicable Part 3
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71
Flame instability
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Spherical flames under intrinsic instabilities
• Not all spherically
propagating flames
are ideal
• Some are wrinkled
and cracked due to
intrinsic instability
• Diffusive-thermal
instability
• Hydrodynamic
instability54 mm
Law, C.K., Combustion Physics, 2006.
72
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• Hydrodynamic instability
Flame instabilities, phenomenology
Williams, Combustion Theory, 1985.
73
• Diffusive-thermal instability
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Joulin and Clavin, Combust. Flame 35, 139 (1979).Clavin, PECS 11, 1 (1985).
Sivashinsky, Acta Astronaut. 4, 1177 (1977).
Sivashinsky, Annu. Rev. Fluid Mech. 15, 179 (1983).
SABATHIER et al., Prog. Aeronaut.
Astronaut. 76, 246 (1981).
Theory
74
End of Part 1
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1Part 2: Flammability limit
• History
• Theory and experiment
• Counterflow flames
• Flame ball
• Toward comprehensive
combustion limit theory
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2History of study on combustion limits
Flammability limit
theory (Planar flame)
Low speed
counterflow flame
Flame ball
Flame ball was predictedBasic limit theory presented1950
The world first experiment
in microgravity (Kumagai)
Requirement for fire safety in coal mines1800
1990
2000
Drop tower(NASA, JAMIC)
Space experiments
2010
Large variations on
combustion limit study
Unified combustion limit theory
Lean burn
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3Flammability limit theory (1940’s-)
Concept of flammability limit for one-dimensional planar flame
Zel’dovich, Y.B., Zhurn. Eksp. Teoret. Fiz. 11, 159 (1941).
Spalding, D.B., Proc. Royal Soc., Ser. A 240(1220) 83 (1957).
Clavin, P., Acta Astronautica 3(3): 223 (1976).
Williams, F.A., Combustion Theory, 1985.
0
0.5
1
0 0.2 0.4
Heat loss parameter, l
Bu
rnin
g v
elo
city p
ara
me
ter,
μ
𝜇2 ln 𝜇2 = − 𝑙
1 𝑒
1 𝑒
20
2 p
d T dTmc q L
dx dx
• Flammability limit
may be induced by
a certain heat loss
• What is loss
mechanism?
• Conduction loss?
Radiative loss? If
adiabatic, no limit?
What is the mechanism of fundamental flammability limit?
• Fact: mixture is only
flammable within a certain
range of equivalence ratio
• Loss mechanism?
4
Equivalence ratio← Fuel lean Fuel rich →
La
min
ar
bu
rnin
g v
elo
city (
cm
/s)
Spalding, D.B., Proc. Royal Soc., Ser. A 240(1220) 83 (1957).
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×
5Conventional methods of combustion limit study
Constant volume
chamber
Propagation
tube
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6
COWARD, H.F. and JONES, G.W., Limits of Flammability of Gases and vapors, BUREAU OF MINES Bulletin 503, (1952).
Fire safety in mines, “standard” propagation tube
H2-air
• Flame propagation tube, Bureau of Mines, US
• Flammability limits significantly differ in the
upward and downward propagating H2-air flames
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7
COWARD and JONES, BUREAU OF MINES Bulletin 503, (1952).
CH4-airExperiments by propagation tube
• Flammability limits of the upward and
downward propagating flames not
significantly differ as hydrogen but still
significant effects of the tube directions
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8
Self Extinguishing Flames (SEFs) in microgravity
Ronney, P.D., Combust. Flame 62(2) 121 (1985).
Ronney, P.D. and Wachman, H.Y., Combust. Flame 62(2) 107 (1985).
• Self extinguishing flames
(SEFs) were observed in
microgravity
• Effect of ignition energy,
flame curvature and
radiative loss were
discussed
• SEFs could be
interpreted through
counterflow flames under
microgravity
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9Low-speed counterflow flames under microgravity
Fuel concentration at
extinction
Fla
me s
tretc
h r
ate-Heat losses
-Buoyancy
-Flame stretch
-Wall effect
-Curvature
淀み面
火炎面
x
混合気
燃料
酸化剤+
Flame
Stagnation plane
Mixture
(Fuel +
Oxidizer)
Maruta, K., et al., Symp. Int. Combust. 26, 1283 (1996).
Maruta, K., et al., Japanese Symp. Combust. 33, 137 (1995).
Law, Egolfopoulos, Symp. Int. Combust. 23, 413 (1990).
Concept
Microgravity experiments
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Microgravity experiments at drop tower
10 seconds microgravity
during 490 meters free fall,
facility closed on 2003.
10
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11Counterflow flame experiments in the ten-second drop tower, CH4/air
Counterflow twin flames at small stretch rates under microgravity (mid 90’s)
Maruta et al., International Symposium on Combustion 26, (1996).
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Results of microgravity experiments
C-shaped curve for CH4 (unexpected!)
and monotonic curve for C3H8
12
0
10
20
30
0.45 0.5 0.55 当量比(燃料の濃度)
火炎伸長率(速度に関するパラメータ)[1/s]
微小重力場実験
メタン/空気プロパン/空気
Flammability limits of
planar flames
C3H8/air
CH4/air
Microgravity experiments
Fla
me s
tretc
h r
ate
[1/s
ec]
Equivalence ratio
Flammable
Non-
flammable
Flammable
Non-
flammable
Maruta, Yoshida, Ju, Niioka, Symp. Int. Combust. 26, 1283 (1996).
Maruta, et al., Japanese Symp. Combust. 33, 137 (1995).
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Ju, Guo, Maruta, J. Fluid Mech. 342 (1997)
Maruta et al., Int. Symp. Combust. 27 (1998)
13
淀み面
火炎面
x
混合気
燃料
酸化剤+
Flame
Stagnation plane
Mixture
(Fuel +
Oxidizer)
Mass diffusion
Thermal diffusion
Experimental C-shaped extinction curve and comprehensive “G-curve”
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Ju, Guo, Maruta, J. Fluid Mech. 342 (1997)
Maruta, Ju, Honda, Niioka, Symp. Int. Combust. 27, 2611 (1998)
14
Another extinction limit
appeared when radiative heat
loss is considered
Experimental C-shaped extinction curve and comprehensive “G-curve”
Guo, Ju, Maruta, Niioka, Liu, Combust. Flame 109(4) 639 (1997).
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Another extinction limit
appeared when radiative heat
loss is considered
Despite low flame temperature,
volume effect makes the role
of radiative heat loss dominant
Experimental C-shaped extinction curve and comprehensive “G-curve”
Guo, Ju, Maruta, Niioka, Liu, Combust. Flame 109(4) 639 (1997).
𝑟𝑓 = −𝐿
𝐿
𝑞𝑟𝑑𝑦 −𝐿
𝐿
𝑘=1
𝐾𝐾
ℎ𝑘𝜔𝑘𝑀𝑘𝑑𝑦
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If equivalence ratio was
changed, island responses with
different size were appeared
Experimental C-shaped extinction curve and comprehensive “G-curve”
Ju, Guo, Maruta, J. Fluid Mech. 342 (1997)
Experimental C-shaped extinction curve and comprehensive “G-curve”
Ju, Guo, Maruta, J. Fluid Mech. 342 (1997)
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Flame separation distance
Experimental C-shaped extinction curve and comprehensive “G-curve”
Ju, Guo, Maruta, J. Fluid Mech. 342 (1997).
Buckmaster, J., Combust. Theory Model. 1(1): 1 (1997).Non-adiabatic (counterflow twin flames)
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Effects of Lewis number on extinction curves
G- to K-shaped transformation
19
Lewis number
Le = 0.67
Le = 1.0
Le = 1.25
Le = 1.43
Le = 1.82
Le = a/D
Ju, Guo, Maruta, Niioka, Combust. Flame 113, 603 (1998).
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Flammability limits of planar flames obtained but sublimit mixture is flammable …
20
Le = 1.0 Le = 1.43
0
10
20
30
0.45 0.5 0.55 当量比(燃料の濃度)
火炎伸長率(速度に関するパラメータ)[1/s]
微小重力場実験
メタン/空気プロパン/空気C3H8/air
CH4/air
Microgravity experiments
Fla
me s
tretc
h r
ate
[1/s
ec]
Equivalence ratio
Flammable
Non-
flammable
Flammable
Non-
flammable
• Limit of planar flame
≠ “flammability limit”
• Definition?
Maruta, Yoshida, Ju, Niioka, Symp. Int. Combust. 26, 1283 (1996).
Maruta, et al., Japanese Symp. Combust. 33, 137 (1995).
Ju, Guo, Maruta, Niioka, Combust. Flame 113, 603 (1998).
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21Peculiar flame in microgravity: Flame ball
Zel’dovich predicted (1944) stationary spherical flame only
sustained by heat and mass transports in molecular diffusions
and reaction without any convective flows
Flame ball
Flame ball (Predicted theoretically at first in 1940’s)
Zel’dovich
Mathematical analysis indicated that it is unstable
but radiative heat loss was not considered
Zeldovich, Y.B., Theory of Combustion and Detonation, NN Semenov, 71, 1944.
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22Flame ball solution, adiabatic
Flame ball
Zeldovich, Y.B., Theory of Combustion and Detonation, NN Semenov, 71, 1944.
0 =1
𝑟2𝑑
𝑑𝑟𝑟2𝑑𝑇
𝑑𝑟+ B exp −𝜃/2𝑇∗ 𝛿 𝑛 −
1
𝜃𝐹
0 =1
Le
1
𝑟2𝑑
𝑑𝑟𝑟2𝑑𝑌
𝑑𝑟− B exp −𝜃/2𝑇∗ 𝛿 𝑛
F = θR02Cp f
λQ, θ=
ECp
RQ
𝑑
𝑑𝑟𝑟2
𝑑
𝑑𝑟𝑇 +
1
Le𝑌 = 0
𝑇 +1
Le𝑌 = 𝑇𝑖 +
1
Le𝑌𝑖
𝑇𝑏 = 𝑇𝑖 +1
Le𝑇𝑎 − 𝑇𝑖 𝑅𝑧 =
𝑌𝑖𝜆 exp 𝜃/2𝑇𝑏
Le 𝐵𝐶𝑝
r < 1 T = T𝑏, Y = 0
r > 1 T = Ti +YiLe
1r
, Y = Yi 1 −1r
Deshaies, Joulin, Combust. Sci. Technol. 37, 99 (1984).
Buckmaster, Weeratunga, Combust. Sci. Technol. 35, 287 (1983).
• Stationary spherical
flame sustained by heat
and mass diffusions
• Stable only if radiative
heat loss exists
Discovery of flame ball
Ronney(1990) Observation of spherical flames
in microgravity experiments at 2.2 sec drop tower
Ronney(1993) Observation of the flames in
aircraft experiments, longer time microgravity
duration but with severe gravity fluctuations
Three essentials: microgravity, low Lewis number,
vicinity of flammability limits
Ronney(USC)+ Tohoku (1996) collaboration at
Japanese 10 sec drop tower (JAMIC)
steady and stable flame balls observed
Space experiments in the Shuttle, 1997 STS-
83/MSL-1, STS-94/MSL-1R, and 2003 STS-107
Ronney
23
Buckmaster, Joulin, Ronney, Combust. Flame 79, 381 (1990).
Ronney, Combust. Flame 82, 1 (1990).
Ronney, Symp. Int. Combust. 27, 2485 (1998).
Abid, M., et al., Combust. Flame 116, 348 (1999).
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Flame ball in aircraft, KC-135 24
Ronney, early 90’s
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25
Flame ball, drop tower in Japan
Microgravity experiments at 10 sec drop tower (~10-4G)
Late 90’s, USC + Tohoku, Combustion and Flame 116, 348 (1999).
26
Flame ball in Space Shuttle
Experiments in the Space Shuttle (STS-107, Ronney, 2003)
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27
Regime of flame ball and planar flame
Wu, M.-S., et al., Combust. Flame 116(3) 387 (1999).
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(a) (b)
Flammable regions of H2-air
counterflow premixed flame.
Point K is the flammability limit
of a planar premixed flame.
Guo et al., Combust. Theor. Model. 4, 459 (2000).
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28
Estimation of lean flammability limits by computations
• Radiative heat transfer
considered in energy
equation
• Case of heat loss only
(optically thin model)
• Case of heat reabsorption
(Grey, SNB, etc.)
Ju et al., Symp.(Int.) Combust. 27, 1998, 2619
Low-speed Counterflow Flame Experiments
under Microgravity for Constructing
Comprehensive Combustion Limit Theory
Kaoru MARUTA1,2
Collaborators: T. Okuno1, T. Akiba1, H. Nakamura1, T. Tezuka1, S. Hasegawa1, R.
Fursenko3, S. S. MINAEV2, M. Katsuta4, M. Kikuchi4
1: Tohoku Univ., 2: FEFU, 3: SB RAS, 4: JAXA
KAUST SS, 1 April 2018
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30Low-speed counterflow flame experiments in microgravity for comprehensive
combustion limit theory (2010-)
Constructing comprehensive combustion limit theory
which covers both conventional flames and flame ball
based on low speed counterflow flames under microgravity
Counterflow
flames Flame ball
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31Hypothesis for unified combustion limit theory
・If long and high quality microgravity condition is available,
counterflow flames with extremely low speed can be realized.
It enables flow condition close to stationary mixture for FB.
・Using heavy dilution gases, mixtures with low Lewis numbers
can be realized. (CH4/O2/N2 -> e.g., CH4/O2/Xe or Kr, CH4/O2/CO2)
淀み面
火炎面
x
混合気
燃料
酸化剤+
FlameMixture
(Fuel +
Oxidizer)
Extremely low
speed flows +
Possible to observe both ordinary flame and flame ball?
Long and high
quality microgravity
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32Preliminary computations
GRI-Mech 3.0[1] without reactions of N (37 species, 221 reactions)
[1] http://www.me.berkeley.edu/gri_mech.
[2] Moore, Physical Chemistry, Tokyo Kagaku Dojin (1974).
[3] Ohno, Quantum Physical Chemistry, University of Tokyo Press (1989).
[4] NIST Chemistry Webbook (http://webbook.nist.gov/chemistry/).
• Collision: value of Ar in GRI-Mech 3.0
• Transport: Data of Moore[2] (Kr polarity: Ohno[3])
• Thermodynamic: NIST Chemistry Webbook[4]
Mixtures
Chemical kinetics
Fuel lean CH4/O2/Xe (Le ~ 0.5)
Fuel lean CH4/O2/Kr (Le ~ 0.7)
Pressure: 1.0 atm
Dilution ratio: fraction of O2 / fraction of inert = 0.141
(Fuel leanCH4/Air : Le ~ 1)
Xe and Kr parameters:
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L 𝑇 =1
𝑐𝑝
𝜕
𝜕𝜒𝜆𝜕𝑇
𝜕𝜒−1
𝑐𝑝
𝐾=1
𝐾
𝜌 𝑌k𝑉k𝑐𝑝k𝜕𝑇
𝜕𝜒−1
𝑐𝑝
𝐾=1
𝐾
𝜔kℎk𝑊k −1
𝑐𝑝𝑞𝑟𝑎𝑑
33Computations: counterflow flame
Premix based flame code[1]
・ Optically thin radiation model[1]
・ Domain: 10 cm
Energy equation
Radiation term
-5 5
Flame
Mixture Mixture
T
0
YreactantYreactant
Flame
Location, x (cm)
[1] Takase, K., et al., Combust. Flame 160, 1235 (2013).
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0 =1
𝑐𝑝
𝜕
𝜕𝑟𝜆Α
𝜕𝑇
𝜕𝑟−Α
𝑐𝑝
𝐾=1
𝐾
𝜌 𝑌k𝑉k𝑐𝑝k𝜕𝑇
𝜕𝑟−Α
𝑐𝑝
𝐾=1
𝐾
𝜔kℎk𝑊k −Α
𝑐𝑝𝑞𝑟𝑎𝑑
Premix based code
・Optically thin radiation model[1]
・Domain radius: 100 cm
・Definition of flame ball radius: peak of heat release rate
Energy equation
(A=4pr2)
Radiation term
Gas temperature T
rT
1
Reaction zoneBurned gas Unburned gas
T* :Burned gas temperature
T0 :Unburned gas temperature
Fuel fraction Y
rY
11
T0
T*
Reactants
Products+Heat
34Computations: flame ball
Takase, K., et al., Combust. Flame 160, 1235 (2013).
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35C-shaped extinction curve: counterflow flames
.2 constX
XZ
Inert
O
CH4/O2/Xe mixture
CH4/O2/Kr mixture
OTM
300 K, 1.0 atm
0.141
0.1
1
10
100
1000
0.3 0.4 0.5 0.6S
tret
ch r
ate
at
exti
nct
ion
lim
it (
1/s
)
Equivalence ratio
Kr
Xe
Flammable
region
Radiative extinction
f = 0.37 f = 0.41
・C-shaped extinction curves both for Xe and Kr flames
・Flammable region: Xe flames (Le~0.5) > Kr flames (Le~0.7)
Takase, K., et al., Combust. Flame 160, 1235 (2013).
Radius of flame balls
.2 constX
XZ
Inert
O
CH4/O2/Xe mixture
CH4/O2/Kr mixture
OTM
300 K, 1.0 atm
0.141
0
0.1
0.2
0.3
0.3 0.4 0.5 0.6F
lam
e b
all
ra
diu
s (c
m)
Equivalence ratio
Kr
Xe
f = 0.34 f = 0.45
・Flame radius: Xe flames (Le ~ 0.5) > Kr flames (Le ~ 0.7)
・ER at limits: Xe flames (f = 0.34) < Kr flames (f = 0.45)
36
Takase, K., et al., Combust. Flame 160, 1235 (2013).
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0.1
1
10
100
1000
0
0.1
0.2
0.3
0.3 0.4 0.5 0.6
Str
etch
ra
te a
t ex
tin
ctio
n lim
it (
1/s
)
Fla
me
ba
ll r
ad
ius
(cm
)
Equivalence ratio
Flame ball Counterflow
.2 constX
XZ
Inert
O
CH4/O2/Xe mixture
OTM
T0=300 K, 1.0 atm
0.141
0.34 0.37
Counterflow flame and flame ball
Possible experimental procedure can be made by the diagram
37
Takase, K., et al., Combust. Flame 160, 1235 (2013).
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38Microgravity experiments by aircraftKAUST SS 2018
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Establish counterflow flames in microgravity
↓Quasi-steadily reduction of fuel
concentration in the mixture
Apparatus and experimental procedure
Counterflow
burner
8mm
VCR
Settling
chamber
Mass flow controllers
Notebook
PC
Oxidant
FuelIgniter
D/A A/Dconverter
and
(a) 対向流予混合火炎用
0.2
0.3
0.4
0.5
0.6
0.7
0 5 10 15 20
Eq
uiv
ale
nce
ra
tio
Time (s)
U Ud d
Premixed flames Flow
L
39
Takase, K., et al., Combust. Flame 160, 1235 (2013).
Okuno et al., Combust. Flame 172, 13 (2016).
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40
© 2004 Diamond Air Service Inc. All rights reserved.
Parabolic
motion
Experiment in cabin Outside view
Microgravity experiment by airplane, MU-300KAUST SS 2018
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41Result (Twin flames -> ball-like flame)Equivalence ratio gradually decreased (Kr case)
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1150
1200
1250
1300
1350
1400
0.3 0.4 0.5
Ma
xim
um
tem
per
atu
re (
K)
Equivalence ratio
Tmax_Counterflow_3.2s-1 (K)
Tmax_Flameball (K)
対向流平面火炎 (伸長率3.2 s-1)
Flame ball
42Flame transition: mechanism
Maximum temperature:
Experiment (CH4/O2/Xe)
Counterflow flames < Flame ball
Computation (CH4/O2/Xe)
Stretch rate: 3.2 s-1
.2 constX
XZ
Inert
O
OTM
T0=300 K, 1.0 atm
0.141
10.85 s
Extinction of
planar flame
10.89 s
Formation of
ball-like flame
(f = 0.46)
11.39 s
Disappeared in
next moment
10.89 s
Extinction of
planar flame
10.93 s
Formation of
ball-like flame
(ER ~ 0.45)
Counterflow flames
Flame ball
Stretch rate: 3.2 s-1
Takase, K., et al., Combust. Flame 160, 1235 (2013).
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43Result (Xe cellular flames)Stretch rate 2.5 (1/s), ER:0.58→0.3
44Sporadic cellular flames by 3D computations
Contour of C=0.15 (top) and concentration distributions in z=0 (bottom) for Le=0.3;
(a) h=0, a=0.067, (b) h=0.6, a=0.033 (c) h=0.8, a=0.033.
Fursenko et al., Combust. Flame 162, 1712 (2015).
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Unified combustion limit theory? 45
Regime diagram of flame transitions 46
0.3 0.4 0.5 0.6 0.7 0.8 0.90.01
0.1
1
10
100 1D limit
Planar flame
Wrinkled flame
Sporadic flame
Transition to ext.
Extinction
S4 S3
S2 S1
(a)
(b)
(c)
a
(1/s)
φ
Numerical prediction by diffusive-thermal model
CH4/O2/Xe
Equivalence ratio
Str
etch
rat
e
Fursenko et al., Combust. Flame 162, 1712 (2015).
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Regime diagram of flame transitions 47
0.3 0.4 0.5 0.6 0.7 0.8 0.90.01
0.1
1
10
100 1D limit
Planar flame
Wrinkled flame
Sporadic flame
Transition to ext.
Extinction
S4 S3
S2 S1
(a)
(b)
(c)
a
(1/s)
φ
CH4/O2/Xe
Fursenko et al., Combust. Flame 162, 1712 (2015).
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Regime diagram of flame transitions 48
Microgravity experiments
CH4/O2/Xe
Equivalence ratio
Str
etch
rat
e
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49Flame structures (f = 0.42)
• Computations by 3D
thermo-diffusive model
• Flame structure of
counterflow flame, flame
ball and sporadic flames
are compared
• Temperature profiles
showed sporadic flame is
an intermediate mode of
combustion between
counterflow flame and
flame ball 0
0.2
0.4
0.6
0.8
1
1.2
0.0
0.2
0.4
0.6
0.8
1.0
1.2
-20 -15 -10 -5 0
Tem
per
ature
(-)
Fu
el c
on
centr
atio
n (
-)
Location (-)
SporadicFlame
Counterflow planar flame
Flame ball
Okuno et al., Combust. Flame, accepted
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50Summary
• Study on flammability limits was initiated due to safety
requirements and enormous amount of experimental data
obtained
• Scientific studies which were trying to clarify fundamental
limit mechanism have been conducted but data are with
large and unacceptable uncertainties
• Theory and experiments under microgravity significantly
contributed the understandings on fundamental limit
mechanisms (counterflow flame, flame ball, sporadic flame)
• Fundamental flammability limit mechanism is radiative heat
loss and this induced rich varieties of near-limit flame
phenomena with Lewis number effects
• Still many unknowns and open questions to be solved
51
End of Part 2
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Part 3: Flames under extreme conditions
• Flame quench
• Excess enthalpy combustion
• Mild combustion
• Microcombustion (microscale combustion)
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Quenching diameter
• Determined from the
ratio of heat generation
and heat loss
• Analogy with
flammability limit
2
2 2( ) ( 4)( )
4( ) ( )
p f u f
f
f f u
c T T dHeat lossH Nu d
Heat generation d h T T
2q fd e Nu
2
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Quenching diameter
• Spalding theory and microgravity
experiments suggest the flammability
limits are not an flame property but a
heat loss induced flame event
• What happen if heat loss is insulated,
compensated by heat recirculation or
high-temperature wall …
2
2 2( ) ( 4)( )
4( ) ( )
p f u f
f
f f u
c T T dHeat lossH Nu d
Heat generation d h T T
2q fd e Nu
3
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4Flame in small channel
Length and time scales: L=(DT)1/2,T=L2/D Non-dimensional numbers: Kn, Pe, Da, Bi, Fo, Le …
Channel diameter
Wall thickness
Flame thickness
Effective radius
Mean free pathQuenching diameteretc….
Time scalesResidence timeReaction timeDiffusion time in solid/gasetc…
Heat recirculation Heat loss…
Fresh mixture
Burned gas
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5
Takeno, Sato, Combust. Sci. Technol. 20, 73 (1979). Ju, Choi, Combust. Flame 133, 483 (2003).
Hanamura, Echigo & Zhdanok, Int. JHMT 36, 3201 (1993).
Hoffmann et al., Combust. Flame 111, 32 (1997).
Wood, S. and Harris, A.T., Porous burners for
lean-burn applications, PECS 34, 667 (2008).
Excess enthalpy combustion
• Essential heat transfer condition for excess enthalpy combustion could be attained not only in Swiss roll geometry but also in radiant emitter and receiver, porous media, small channel, etc.
• Fundamental studies of EEC have been conducted
• Super-adiabatic combustion, super-lean combustion available
Kim, N.I., et al., Combust. Flame 141, 229 (2005).
Ronney, 3D Swiss roll
(2001).
Maruta,
Microcombustor (2005).
Echigo, Porous media (1990’s).
Weinberg (1972).
Ronney, P.D., Combust. Flame 135, 421 (2003).
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Exergy loss during combustion process
6
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Combustion device
Mixture Burned gas
Yoshida et al., Exergy engineering, Kyoritu, 1999, in Japanese.
Higher inlet and outlet temperatures preferable
Comprehensive understanding is challenging due to various conditions and parameters
Exergy loss during combustion process
Inlet temperature
Outlet temperature
Inlet temperatureOutlet temperature
7
Lo
ss o
f e
xe
rgy r
ate
, %
Lo
ss o
f e
xe
rgy r
ate
, %
Tsutsumi, Clean
Coal Day, 2010
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8
Exergy (or availability)
Exergy efficiencySecond law efficiency
Ratio of effective work to total exergy
max Carnot01Q
H
H H
TE Q
TL Q
flow 1 0 0 1 0 JE H H T S S T
he
rma
l e
ne
rgy,
Q
Exe
rgy,
E
Anergy
Reversible process
Exergy loss, Llost
Irreversible process
Work, L
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Normal combustion
802.3kJ
Exergy efficiency of normal combustion 9
ηH: Ratio of the utilized thermal
energy to the heat generation
ηE: Ratio of the utilized exergy to
the fuel exergy
ηE heat: Ratio of the utilized exergy to
the total exergy
Yoshizawa, J Combust. Soc. Japan 50, 2008
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AB
E
C
D
Exergy efficiency of excess enthalpy combustion
Combustion with
heat recirculation
10
ηH: Ratio of the utilized thermal
energy to the heat generation
ηE: Ratio of the utilized exergy to
the fuel exergy
ηE heat: Ratio of the utilized exergy to
the total exergy
Yoshizawa, J Combust. Soc. Japan 50, 2008
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11Adiabatic, non-adiabatic & excess enthalpy flames
X
T
T
T
• We have made
scientific discussion
on adiabatic and
non-adiabatic
flames
• Third status is
excess enthalpy
flames and it would
be better for higher
thermal efficiency
Adiabatic
Non-adiabatic
Excess
enthalpy
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High Temperature Air Combustion Technology Project(HiCOT)
12
HiCOT test furnace by NFK Co. Ltd.
-Major industrial companies (IHI, JFE, Kobelco, Chiyoda, NFK, etc),
Major universities (Hokkaido, Tohoku, Tokyo, Toyohashi, Osaka pref.)
and National institute (AIST)
- Fundamentals phase in early 90’s and development phase till 2004
- Mild combustion, Flameless combustion
-Fundamental phase 1991-1999
-Development phase 1999-2004,
Budget: 50 million USD for 5 yr
By METI
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13
CO2 reduction up to 30%Extremely low NOx
emissions No combustion
noise Downsizing
High temperature air combustion technology (Concept and technical merits)
Oxygen concentration (%) Distance
HiCOT Distance
Conventional combustion
Tem
p.
Tem
p.
Tair < 600 ˚CTair > 800 ˚C
Conventional combustion
New combustion regime
Unstable combustion
regime
High Temp combustion
Dilu
ted
air
tem
per
atu
re (
˚C) Diluted air temperature and combustion mode
FOF
FOF
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R
N F K
“A” Burner
“B” Burner
Fuel
Fan
4-way
Valve
Exhaust
1100oC
1200oC
1200oC
200oC
20oC
Fuel1100oC
1200oC
Periodic Switching in
every 30 sec
A pair of
Regenerator
High Temperature Air Combustion Technology(Flameless combustion, Mild combustion)
14
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Ceramic Honeycombs for Regenerator Media
Square Type Cylindrical Type
R
N F K
15
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Air Temperature= 1080ºC
Air Ratio, =1.3
Air Temperature= 600ºC
Air Ratio, =2.0
HiCOTNon-HiCOT
R
NFK
16High Temperature Air Combustion Technology(Flameless combustion, Mild combustion)
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17
17
Exergy efficiency of excess enthalpy combustion
Combustion with
heat recirculation
ηH: Ratio of the utilized thermal
energy to the heat generation
ηE: Ratio of the utilized exergy to
the fuel exergy
ηE heat: Ratio of the utilized exergy to
the total exergy
Yoshizawa, J Combust. Soc. Japan 50, 2008
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Typical configuration of
HICOT flame
Hot airHot air
Fuel jet
Fujimori et al., PCI 27, 1998
High speed fuel jet lifted flame
Advantage of lifted flame (Neither Premixed nor Diffusion flames)
18
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Achievements of HiCOT project
-Up to 1200 conventional furnaces converted into HiCOT furnaces
-Around 10 HiCOT incineration furnaces and steam reformers
(0.1 billion USD/furnace) in sales contracts in the world
-HiCOT coal boiler
19
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Microcombustion study
20
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21
Microcombustion study 1
Swiss roll combustor for
heat sources
Micro flow reactor with
controlled temperature profile
Heat recirculation for realizing small flame
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P roducts
R e a cta nts
C om bus tion
volum e
1 6 00 1 20 0 40 0 3 00 K5 0 0
14 0 0 60 0 50 07 001 6 0 0
Combustion
room
Fuel + Air
Exhaust gas
Exhaust gas
Fuel + air
Principle of Swiss roll microcombustor 22
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100 60~85
40~15
100 63.4
36.6
Heating by microcombustor
Heating by electric resistive heater
Total loss during power
generation and transmission loss
Heat recirculation
Usable for heating
Usable for heating
Primary energy
(Fossil fuel)
Exhaust
loss
Energy saving by microcombustor 23
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24Swiss roll microcombustor as heat sources
Disk-type heaters: D = 64, 46, 26, 20 mm
Surface temperature: 650 - 1250K
Temperature controllability: within 1 K at 1173K
Thermal efficiency as a heater: up to 85% 100W-1kW for various industrial heating, heat source for TE, TPV…..
Kim et al., CNF 141 (2005)Kim et al., PCI 31 (2007)
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Possible application of microcombustors (Proto-type industrial heating furnace)
70 % reduction of fuel consumption
• Baking and drying food
• Drying for painting
• Thermal treatment of glass panel, polymer film
and material with low melting point
Specification
Length 7 m
Width 0.9 m
Temperature Max 400℃
Control 3 zone
Number of
heaters68
Bed speed 0.6m~12m/min
25
×68
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26
Microcombustion study 2
Swiss roll combustor for
heat sources
Micro flow reactor with
controlled temperature profile
For fundamental kinetics studies
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Micro flow reactor with a controlled temperature profile
27
Stationary wall-temperature profile
Diameter of tube < conventional quenching diameter
Gas phase temperature dominated by wall temperature profile
Laminar flow and constant pressure
T
xoTest section xo
TmaxT
xoTest section xo
Tmax
dd
T
Mixture
Room temp
Tmax = 1300 K
d < Quenching
diameter
External heat source
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Premixture
Flame behaviors in a meso-scale channel with a prescribed temperature profile
Normal flame
Oscillatory flame
High velocity region
Weak flame
Low velocity region
Intermediate velocity region
28
Maruta et al., PCI 30 (2005).
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29Three kinds of flame responses
(1) Normal flame
(3) Weak flame
(2) Oscillatory flame
V=50cm/s
V=20cm/s
V=0.2cm/s-12 -10 -8 -6 -4 -2 0 2 4 6 8 10
0
20
40
60
80
100
120
= 1.0
Normal flame
FREI
Estimated points
of ignition
Location (mm)
Mean f
low
velo
city (
cm
/s)
400
600
800
1000
1200
1400
1600
Wa
ll Te
mp
era
ture
, Tw (K
)Ignition
Extinction
Tw
Flow
Normal flame, oscillatory flame, weak flame
CH4/air
Maruta et al., PCI 30 (2005)
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30Theoretical S-shaped response
V
v
Stable
xStable
v
Unstable
Flow
Two stable and one unstable solutions were predicted theoretically
Minaev et al., Combust. Theory Model. (2007)
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31
Stable branch
Stable branch: weak flame
Unstable branch
timeChemical
time residense Flowa D
• Normal flame:
preheated premixed
flame
• Oscillatory flame:
flames with
repetitive extinction
and ignition, FREI
• Weak flame: stable
weak flame which
represent ignition
Analogy between S-curve and conventional Fendell-curve
Da: Damköhler number
Max
imu
m t
emp
erat
ure
Ign
itio
n
Exti
nct
ion
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32Lower limit of weak flames identified
0.0 0.2 0.4 0.6 0.8 1.0 1.2 1.4 1.6
0
5
10
15
20
25
30
Tem
pera
ture
diffe
rence (
K)
Mean flow velocity (cm/s)
= 1.2
= 1.0
= 0.85
= 0.6
Tg - Tw
At V = 0.2 cm/s, Tw = 1225 K, Tg-Tw< 2 K
Extremely small temperature increase near the limit
Flame position close to the ignition point
Lowest flame temperature → ignition temperature
0.0 0.2 0.4 0.6 0.8 1.0 1.2 1.4 1.6 1.8 2.00
10
20
30
Tem
pera
ture
diffe
rence (
K)
Mean flow velocity (cm/s)
Tg-T
w
Experiment
Computation
Tsuboi et al., PCI 31 (2009).
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33Limit mechanism
Species dissipation at low velocity region significantly
larger than that at higher velocity region
Lower limit of weak flame by diffusive dissipation
5.0 5.5 6.0 6.5 7.0 7.5 8.0-1.0x10
-3
-5.0x10-4
0.0
5.0x10-4
1.0x10-3
1.5x10-3
2.0x10-3
Flu
x (
g/c
m2s)
Location (cm)
OH flux (Vm=134cm/s)
Diffusion
Convection
4.0 4.5 5.0 5.5 6.0 6.5 7.0-1.2x10
-6
-1.0x10-6
-8.0x10-7
-6.0x10-7
-4.0x10-7
-2.0x10-7
0.0
2.0x10-7
4.0x10-7
Flu
x (
g/c
m2s)
Location (cm)
OH flux (Vm=1.82cm/s)
Diffusion
Convection
V =134 cm/s V =1.8 cm/s
OH flux by convection & diffusion
Tsuboi et al., PCI 31 (2009).
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34Three flames are utilized for:
(1) Normal flame
(3) Weak flame
(2) Oscillatory flame
Measurements of laminar burning
velocity of highly preheated mixtures
Investigations of non-linear dynamics of
given fuels
Investigations of ignition relevant
properties of various fuels, validation
and modifications of kinetics,
particularly at low temperature
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35Triple weak flames, n-heptane
U = 3 cm/s
Triple stationary weak flames observed
Weak flame location insensitive to flow velocity
= 1
Yamamoto et al., PCI 33
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Code PREMIX-based
Reaction scheme: n-heptane, reduced mechanism from LLNL
(159 species, 1540 steps)
Conditions: Stoichiometric gaseous n-heptane/air mixture
Experimental wall temperature profile was provided as Tw(x)
Gas-phase energy equation
Heat transfer with the wall
Flame position: Peaks of heat-release-rate (HRR) [W/cm3] profile
Computation (one-dimensional)
Seiser et al., PCI 28 (2000)
36
Μ𝑑𝑇
𝑑𝜒−1
𝑐𝑝
𝑑
𝑑𝜒𝜆Α
𝑑𝑇
𝑑𝜒+Α
𝑐𝑝
𝐾=1
𝐾
𝜌𝑌k𝑉k𝑐𝑝k𝑑𝑇
𝑑𝜒+Α
𝑐𝑝
𝐾=1
𝐾
𝜔kℎk𝑊k −Α
𝑐𝑝
4𝜆𝑁𝑢
𝑑2𝑇𝑤 − 𝑇 = 0
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37Triple weak flames, n-heptane
U = 3 cm/s
Three-stage heat releases
Computational
Yamamoto et al., PCI 33
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U = 3 cm/s
Three-stage heat releases
38Triple weak flames, n-heptane
Computational
Yamamoto et al., PCI 33
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300
400
500
600
700
800
900
1000
1100
1200
1300
0
5
10
15
20
25
3.5 4 4.5 5 5.5 6
Wa
ll t
em
pera
ture
[K
]
Mo
le f
ra
cti
on
[%
]
x [cm]
O2
CO2
CH2O×10 CO
CH4×20
n-C7H16×10
H2O2×10
Tw
U = 2.0 cm/s
Computational species profiles 39
Three peaks of heat release rateYamamoto et al., PCI 33
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300
400
500
600
700
800
900
1000
1100
1200
1300
0
5
10
15
20
25
3.5 4 4.5 5 5.5 6
Wa
ll t
em
pera
ture
[K
]
Mo
le f
ra
cti
on
[%
]
x [cm]
O2
CO2
CH2O×10 CO
CH4×20
n-C7H16×10
H2O2×10
Tw
LTO: CH2O, H2O2, CO, CH4 produced
U = 2.0 cm/s
Computational species profiles
First HRR peak
40
Yamamoto et al., PCI 33
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300
400
500
600
700
800
900
1000
1100
1200
1300
0
5
10
15
20
25
3.5 4 4.5 5 5.5 6
Wa
ll t
em
pera
ture
[K
]
Mo
le f
ra
cti
on
[%
]
x [cm]
O2
CO2
CH2O×10 CO
CH4×20
n-C7H16×10
H2O2×10
Tw
U = 2.0 cm/s
CH2O + OH ⇒ HCO + H2O
H2O2 (+M) ⇒ 2OH (+M) HCO + O2⇒ CO + HO2
Computational species profiles
Partial oxidations:
Second HRR peak
41
Yamamoto et al., PCI 33
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300
400
500
600
700
800
900
1000
1100
1200
1300
0
5
10
15
20
25
3.5 4 4.5 5 5.5 6
Wa
ll t
em
pera
ture
[K
]
Mo
le f
ra
cti
on
[%
]
x [cm]
O2
CO2
CH2O×10 CO
CH4×20
n-C7H16×10
H2O2×10
Tw
U = 2.0 cm/s
Full oxidations: CO + OH ⇒ CO2 + H
Computational species profiles
Third HRR peak
42
Yamamoto et al., PCI 33
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0
0.01
0.02
0.03
0.04
0.05
0.06
0.07
0.08
0.09
0.1
0
5
10
15
20
25
300 500 700 900 1100 1300
Ma
ss c
on
cen
tra
tio
n o
f C
H2O
[%
]
Vo
lum
etr
ic c
on
cen
tra
tio
n [
%]
Wall temperature [K]
O2
CO2
CH2O
CO
CH4×20
300
400
500
600
700
800
900
1000
1100
1200
1300
0
5
10
15
20
25
3.5 4 4.5 5 5.5 6
Wa
ll t
em
pera
ture
[K
]
Mo
le f
ra
cti
on
[%
]
x [cm]
O2
CO2
CH2O×10 CO
CH4×20
n-C7H16×10
H2O2×10
Tw
Measurement by GC
Measurements and computations
Three-stage oxidation process was
confirmed by gas sampling experiment
(U = 2.0 cm/s)
Computations
43
Yamamoto et al., PCI 33
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44Interpretation of triple weak flames
Conventional two-stage ignition converted into steady,
three-stage, spatially-separated weak flames in MFR
Cool flame
Hot flame
Hea
t re
leas
e ra
te
time
Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
n-heptane/air = 1
1 mm
Ignition in
RCM and ST
(transient)
Cool flame Separated hot flames
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45MFR applied for gasoline PRF
n-heptane + iso-octane (PRF)
Appearances of multiple weak flames
represent Research Octane Number
Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
= 1U0 = 2 cm/s
Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
1 mm
Hori, et al., CNF 2012
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U=1.2 cm/sec
Weak flames at different RON
Significant LTO in smaller RON
Weak flame behaviors reproduced
46
Computation
Hori, et al., CNF 2012
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Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200
Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
(a)
(d)
Flow direction
700 800 900 1000 1100 1200Wall temperature (K)
2 mm
120
Flow direction
PRF0
PRF20
PRF50
PRF100
700 800 900 1000 1100 1200
Wall temperature (experiment) [K]
-1.5 -1.0 -0.5 0 0.5Location [cm]
methanetoluene
propane
ethane
n-heptane, PRF 0
iso-octane, PRF 100n-butane
PRF 50
PRF 20
120
112
108
100
94
50
20
0
RON
Weak flame appearances for various RON
Weak flame locations: monotonic function of RON
Second weak flame: visible when RON < 100
First weak flame: visible when RON < 20
P = 1 atm
47
Hori et al., CNF 159, 2012.Hori et al., PCI 34, 2013.Kamada et al., CNF 161, 2014.
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Structure of a separated cool flame in MFR 48
0
0.1
0.2
0.3
0.4
0
0.05
0.1
0.15
0.2
0.25
5 6 7 8 9 10 11 12 13M
ole
fra
ctio
n (
-)
HR
R (
J/s/
cm3)
1st flame
nC7H16×10
O2
H2O2×10
CH2O×10
CO×10
CO2×10
(cool flame)
KUCRS mech. Location (cm)
600 700650 600550
Wall Temperature [K]
Tatsumi et al., Heat Transfer Symposium 2017.Tatsumi et al., TFEC9, 2017.
Vertical MFR
Small temperature gradient
Symmetry & higher resolution
KUCRS mech.
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49Structure of a cool flame, computation
600 700650 600550
Conditions : nC7H16/air, f = 1, P = 1 (atm), V = 2 (cm/s), Exposure time 30 (minutes)
Wall temperature (K)
0
0.2
0.4
0.6
0
0.01
0.02
5 6 7 8 9 10 11 12 13 HR
R (
J/s/
cm3)
0
0.2
0.4
0.6
0
0.01
0.02
5 6 7 8 9 10 11 12 13
Mo
le f
ract
ion (
-)
Location (cm)
00.6
00.02
KUCRS mech.
LLNL mech.
nC7H16
H2O2CH2O
nC7H16 H2O2
CH2O
Tatsumi et al., Heat Transfer Symposium 2017.Tatsumi et al., TFEC9, 2017.
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50Reaction paths in a cool flame
RH
R
ROO
QOOH
OOQOOH
OQ-HOOH Cyclic ethers
Aldehydes + ester or ketone group
Alkenes + ester or ketone group
CH2O, H2O2
R : C7H15
Q : C7H14
Q-H : C7H13
(Ketohydroperoxide)
OQ-HO
← OH
← O2
→ OH
→ OH← OH
← O2
→ OH
Radical branching path
Radical propagation path
CO, CO2Tatsumi et al., TFEC9, 2017.
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56PRFs, ultra lean, higher resolution
Vertical-type reactorGrajetzki, et al., 36 Symp, WIPP. 2016.Grajetzki, et al., COMODIA, 2017.
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57CH4, ultra lean and Xe dilution
Okuno et al., PCI 36.
Conducted for analyzing
microgravity experiments
on interaction between
flameball and
counterflow flames
Fuel: CH4; O2/Inert = 0.141; = 0.3
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LIF for CH2O and OH applied 58
Shimizu et al., Energ. & Fuels 31, 2017.
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59LIF of CH2O & OH and Chemiluminescence methane/air
Shimizu et al., Energ. & Fuels 31, 2017.
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Soot and PAH formations at temperature below 1400 K
60
CH4 CH3
CH2O
HCO
CO
CO2
CH3O
C2H6
C2H3
C2H2
C2H4
C2H5
CH2CHO
CH2COHCCO
+ CH3(+M)
+H
+OH
+ CH3
+ HO2
+O
+OH
+H
+O
+ HO2
+O2
+O2
+(M)
+H2O
+OH
+HO2
+O2
+(M)
+OH
+H
+ CH3
+O
+OH
+H
+CH3
+O
+(M)
+O2
+(M)
+O2
+O2
+H
+OH
+(M)+O
+O
+ HO2
Dubey et al., CNF 174, 2017.
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Soot and PAH formations at temperature below 1400 K
61
Dubey et al., CNF 174, 2017.
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62Effect of radical quenching at wall
0
0.005
0.01
0.015
0.02
0.025
0.03
0.035
0.04
0.045
0.05
0.7 0.8 0.9 1 1.1 1.2 1.3
Mo
le f
ract
ion
[-]
φ
Inert wall
Quench wall
Experiment
Inert wall (computation)
Quench wall (computation)
Experiment
• CO mole fraction of burned gas:
Quench case > Inert case
• Experimental results agree with Inert case
→ radical quenching effect negligible
Inert: GRI3.0Quench: GRI 3.0 + Raimondeau
CH4/air; = 1; d = 1.5 mm, 1 atm
Kizaki, et al., PCI 35 (2015).
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63Quantitative measurement of wall chemical effect
Quartz plate Coated plate
20 mm
Thermocouple hole
• 100 nm-thick thin films on quartz plate
Metal: Sputtering/Arc plasma gun
Al2O3: Atomic Layer Deposition
Saiki, Fan & Suzuki,
Combust. Flame
(2015).
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Micro flow reactor with controlled temperature profile
64
Micro flow reactor with controlled temperature profile
would be a new platform for study on chemical kinetics
particularly for low temperature conditions
Acknowledgements
IHI, IIC, HONDA R&D, MAZDA
IHI, NEDO, HITACHI, TOKYO GAS, JSPS, JST
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Applications of MFR for future
By MEMS(?) MFROn board combustion controlOn board fuel reformingEfficient engines with higher fuel flexibility
Fuel reforming for reaction controlChemical reaction control designing
MEMS MFR+ECU
65
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66
Let us work together for tomorrow through clean combustion science & technology!
Thank you very much!
67
End of Part 3
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