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Numerical Study of the Swirl Effect on a Coaxial Jet Combustor Flame
Including Radiative Heat Transfer
Taoufik Gassoumi a; Kamel Guedri a; Rachid Said a
Unité de Recherche: Etude des Milieux Ionisés et Réactifs (EMIR), IPEIM, Monastir, Tunisie
a
Online publication date: 21 December 2009
To cite this Article Gassoumi, Taoufik, Guedri, Kamel and Said, Rachid(2009) 'Numerical Study of the Swirl Effect on a
Coaxial Jet Combustor Flame Including Radiative Heat Transfer', Numerical Heat Transfer, Part A: Applications, 56: 11,
897 — 913
To link to this Article: DOI: 10.1080/10407780903466535
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Numerical Heat Transfer, Part A, 56: 897–913, 2009
Copyright # Taylor & Francis Group, LLC
ISSN: 1040-7782 print=1521-0634 online
DOI: 10.1080/10407780903466535
NUMERICAL STUDY OF THE SWIRL EFFECT ON A
COAXIAL JET COMBUSTOR FLAME INCLUDING
RADIATIVE HEAT TRANSFER
Taoufik Gassoumi, Kamel Guedri, and Rachid Said
Downloaded By: [Gassoumi, Taoufik] At: 20:45 23 December 2009
Unité de Recherche: Etude des Milieux Ionisés et Réactifs (EMIR),
IPEIM, Monastir, Tunisie
A numerical study of the swirl effect on a coaxial jet combustor flame including radiative
heat transfer is presented. In this work, the standard k-e model is applied to investigate
the turbulence effect, and the eddy dissipation model (EDM) is used to model combustion.
The radiative heat transfer and the properties of gases and soot are considered using a
coupled of the finite-volume method (FVM), and the narrow-band based weighted-sumof-gray gases (WSGG-SNB) model. The results of this work are validated by experiment
data. The results clearly show that radiation must be taken into account to obtain good
accuracy for turbulent diffusion flame in combustor chamber. Flame is very influenced by
the radiation of gases, soot, and combustor wall. However, swirl is an important controlling
variable on the combustion characteristics and pollutant formation.
1. INTRODUCTION
Combustion chambers designs have been optimized for years to increase
efficiency and minimize pollution for steady regimes. Currently, one of the challenges
of computational combustion in real engines is the radiative heat transfer.
In the literature, three approaches are used to simulate turbulence. First, the
direct numerical simulation (DNS) approach treats the complete equations of
Navier-Stokes which are solved without any closure model. The DNS has an expensive computational time, but it is used as a reference to test other forms of simulation
of turbulence [1]. Secondly, the large eddy simulation (LES) is used to calculate
directly the large eddy or scale and to model the small scale. In combustion technology, LES is useful for combustion instabilities [2] and flame stabilization [3],
but, it is very expensive and needs high performance processors for calculation.
Finally, the Reynolds-averaged Navier-stokes (RANS) is also developed [1]. Many
closure models are available, but they divide into two categories depending on the
modeling of turbulence stresses, based either on an eddy-viscosity model (EVM)
or a Reynolds-stresses model (RSM). The EVM, for example the standard k-e model
described by Launder and Spalding [4], and the Renormalization Group theory
(RNG k-e) model [5, 6], are used to treat the isotropic turbulence. However, the
Received 30 June 2009; accepted 15 October 2009.
Address correspondence to Taoufik Gassoumi, Etude des Milieux Ionisés et Réactifs (EMIR),
IPEIM, Rue Ibn El-Jazzar, 5019, Monastir, Tunisie. E-mail: Taoufik_Gassoumi@yahoo.fr
897
898
T. GASSOUMI ET AL.
NOMENCLATURE
A
Cp
Ce1 ; Ce2 ; Cm
Dmn
fv
G
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h
I
i
K
k
q
<
RF
S
SW
T
u, v, w
us
x, r
Y
yþ
Z
a
amn1=2
b
C/
e
ew
f
j
m
mmn, gmn, nmn
t
q
rs
s
U
area of control volume face, m2
constant pressure specific heat
constants of the standard k-e
model
directional weight
soot volumetric fraction
production term of turbulent
kinetic energy
enthalpy
radiant intensity, W=m2 sr
stoichiometric oxygen to fuel
mass ratio
Van-Karman constant
turbulent energy, m2=s2
radiative heat flux, W=m2
incident radiation, W=m2
reaction rate, kg=m3 s
source term
swirl number
temperature, K
axial, radial and tangential
velocity component,
respectively, m=s
wall friction velocity, m=s
coordinate axes in cylindrical
geometry
mass fraction
adimensional distance in wall
coordinate
mixture fraction
Prandtl number
coefficient of the angular
derivative term
extinction coefficient ¼ j þ
rs, m1
diffusion coefficient for
transport variable
dissipation rate of energy, m2=s3
wall emissivity
equivalence ratio
absorption coefficient, m1
viscosity, kg=m s
direction cosines
wave number, m1
density, kg=m3
scattering coefficient, m1
shear stress
Scattering phase function
/
!
X
DXmn
x
Subscripts
b
cr, cx
E, W, T, B
e, w, t, b
eff
F
g
i
k
l
O
P
pr
r
s
t
t
Superscripts
m, n, m0 , n0
w
þ,
Abbreviations
CFD
DNS
DOM
EVM
FVM
LES
RANS
RNG
RSM
RTE
WSGG- SNB
general dependent variable
direction
discrete control angle
scattering albedo
blackbody
radial and axial direction,
respectively
east, west, top and bottom
neighbors points of P
east, west, top, and bottom
control faces
effective exchange coefficient
fuel
gas
species
kth gray gas
laminar transport coefficient
oxygen
nodal point in which intensities
are located
product
radiation
soot
turbulent transport coefficient
spectral parameter
radiation direction
wall
leaving and arriving intensity
directions, respectively
computational fluid dynamic
direct numerical simulation
discrete ordinate method
eddy-viscosity model
finite volume method
large eddy simulation
Reynolds-averaged NavierStokes
Renormalization Group
Reynolds-stresses model
radiative transfer equation
narrow-band based
weighted-sum-of-gray-gases
RSM are more adapted to anisotropic turbulence, as in bed flows [7]. The RSM are
tested to isothermal flows without chemical reaction and heat transfer. The standard
wall-function approach is used to solve the near-wall region to achieve a better
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SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
899
prediction of wall effects. The wall functions are available in the literature [8]; there is
a semi-empirical formula expressing the well known logarithmic law [9].
Generally, flames are influenced by the radiative properties of combustion
gases and their surroundings [10]. A computational analysis of radiation avoids an
under-or over-prediction of the temperature distribution in combustion systems.
Zimberg et al. [11] showed, in the case of a cylindrical non-premixed flame, that there
is a strong interaction between chemistry, turbulence, and radiation. For that reason,
to obtain a coherent work radiation must be taken into account. In such work, when
combustion and radiation are coupled we must choose the suitable methods and
models for simulation. When radiation dominates in combustion systems, we must
also take into account the geometry and the computational time cost. In the literature, there are many methods cited to solve the radiative transfer equation: the discrete ordinate, the discrete transfer, the flux, the Monte Carlo, the zone, the P–N,
and the finite-volume methods (FVM). Several researchers, like Kim et al. [12],
showed that FVM has the best accuracy and performance by comparing it with
DOM. In addition, FVM shares the same computational grid with computational
fluid dynamics solvers (CFD). Previously, FVM has been is used in structured grids,
particularly with cylindrical coordinates [13], but it is also applied in unstructured
grids for axisymmetric geometries [14].
In the present article, to solve the radiative transfer equation (ETR), the
finite-volume method (FVM) will be coupled to the narrow-band based weightedsum-of-gray gases (WSGG-SNB) model of Kim and Song [15]. This radiation
procedure is implemented on a combustion code using the eddy dissipation model
(EDM) proposed by Magnussen and Hjertager [17] for combustion and a combination
between k-e model and wall function for turbulence. The swirl is produced by adding
a tangential component on the injection of the fluid (fuel or air). Thus, the effect of
the swirl number is investigated. The results showed that radiation of the combustor
wall, gases, soot, and swirl number played an important role in combustion.
2. MATHEMATICAL MODEL
2.1. Governing Equations
In this article, to simulate the turbulent flow and chemical reaction in the burner, a two-dimensional axisymmetric mathematical model is applied. In the axisymmetric coordinate, a generalized form of the equations of motion can be expressed as
1 q
q
q
q/
q
q/
ðrqu/Þ þ ðrqv/Þ
rCeff
rCeff
ð1Þ
¼ S/
r qx
qr
qx
qx
qr
qr
The diffusion coefficients Ceff and the source terms S/ of conservation law of
each dependent variable / with the correspondent laminar a/l, and turbulent, a/t,
Prandtl numbers are shown in Table 1. Ceff is the sum of both the laminar and turbulent transport coefficients. It is interpreted as the effective viscosity for / ¼ u, v, w,
and the effective diffusivity for / ¼ h, Z, Yi. In Eq. (1), Ceff is calculated as
Ceff ¼
ml
m
þ t
a/l a/t
ð2aÞ
900
T. GASSOUMI ET AL.
Table 1. Diffusion coefficients, laminar, and turbulent Prandtl numbers and source terms of conservation
laws [10]
Equation
Continuity
/ Ceff a/l
1
0 1.0
a/t
1.0
Axial momentum
u
meff 0.7
0.9
Radial momentum
v
meff 0.7
0.9
Tangential momentum
w
meff 1.0
1.0
Kinetic energy of turbulence
k
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Dissipation of turbulence energy e
Energy (enthalpy)
h
Fuel mass fraction
YF
Mixture fraction
Z
meff
rk
meff
re
meff
rh
meff
rYF
meff
rZ
0.7
0.7
S/
0.0
q
qu
1q
qv
qp
meff
rmeff
þ
qx
qx
r qr
qx
qx
q
qu
1q
qv
v
meff
rmeff
þ
2meff 2
qx
qr
r qr
qr
r
qw2 qp q 2
2
qu qv
qk þ meff
þ
þ
r
qr qr 3
3
qx qr
2q
ðrwmeff Þ
r qr
mt G
1.0
Cm q 2 k 2
mt
2
2
K pffiffiffiffiffi
C GCm qk Ce2 qek
ðCe2 Ce1 Þ Cm e1
0.5
r qr
0.7
0.5
Rf
0.7
0.5
0.0
0.7
The constants of the standard k-e model are Cm ¼ 0.09, Ce1 ¼ 1:44, and Ce2 ¼ 1:92. K ¼ 0.4187 is the
Van-Karman constant.
with
meff ¼ ml þ mt
ð2bÞ
where ml and mt represent, respectively, the laminar and the turbulent viscosity. a/l
and a/t are the laminar and turbulent Prandtl number corresponding to the variable
/, respectively.
2.2. Turbulence Model
To compute turbulence, the two equations (k-e) model, developed by Launder
and Spalding [4] was used. The turbulent viscosity is determined from the time-mean
values of the kinetic energy of turbulence, k, and the volumetric turbulent kinetic
energy dissipation rate, e, by the expression
mt ¼ C m q
k2
e
ð3Þ
where Cm is a constant and the quantities k and e are determined from Eq. (1). Where
for the k equation
Sk ¼ mt G
Cm q2 k2
mt
ð4Þ
and for the e equation
Se ¼ Ce1 GCm qk Ce2
qe2
k
ð5Þ
SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
901
In Eqs. (4) and (5), G represents the production of turbulent kinetic energy by
the mean motion and given by
G ¼2
"
qu
qx
2 2 #
2
qv
v 2
qu qv 2
qw
q w 2
þ
þ
þ
þ
þ
þ r
qr
r
qr qx
qx
qr r
ð6Þ
Boundary Conditions: Wall Function
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The treatment of the region near the wall is very necessary, because the standard k-e model is a high-Reynolds model and cannot be applied in this region due
to viscous effects. The wall distance in wall coordinate yþ is defined as [4]
yþ ¼
qyp us
ml
ð7Þ
where, yP is the normal distance from the center of the cell at the point P to the wall.
us is the wall friction velocity
rffiffiffiffiffi
sw
ð8Þ
us ¼
q
yþ represents the grid adimensional distance from the wall and it is given according
to Launder and Spalding [4] at node P, as
!
1=4 pffiffiffi
qCm
ky
þ
y ¼
ð9Þ
ml
P
Knowing that the laminar sublayer extends from the wall to yþ ¼ 11.63 [4].
Using the logarithmic law, the axial velocity in wall coordinate, uþ, is given by
uþ
1
¼ LnðEyþ Þ
us K
ð10Þ
u
s w ¼ ml
y P
ð11Þ
Then, the shear stress is given by
Otherwise, the point P is within the turbulent flow region and the shear stress is calculated using the logarithmic law of the wall so that
pffiffiffi
u
ð12Þ
sw ¼ qCm1=2 K k
lnðEyþ Þ P
with K ¼ 0.4187 and E ¼ 9.0 are the Van-Karman and the smooth wall constants [4],
respectively. In Table 2, the source terms of the turbulent kinetic energy k and the
902
T. GASSOUMI ET AL.
Table 2. Boundary wall conditions [4]
k
/
e
3=4
Cm kp3=2
sp
1=2
Kyp
qCm
S/
lnðEyþ Þ
for yþ 11:63
mt G Cm3=4 qk3=2
ðKyÞ P
yþ
for yþ < 11:63
mt G Cm3=4 qk3=2
y P
1030þ1030eP
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turbulent dissipation rate e are given. The shear stress evaluated above is used in the
generation term G to compute ðmðquÞ=ðqyÞÞ. Se is computed by assuming that
the rates of the turbulent kinetic energy generation and dissipation are equal, and
the value of e is given at the edge of the Couette flow region.
2.2. Combustion Model
For combustion, a single step reaction of methane (CH4) and air is considered.
To simplify calculations, the argon is not included. The equation for combustion of a
lean mixture is given as [16]
2
1f
7:52
CH4 þ ðO2 þ 3:76N2 Þ ! CO2 þ 2H2 O þ 2
N2 for 0 f 1
O2 þ
f
f
f
ð13Þ
The fuel mass fraction, YF, is obtained using Eq. (1) where
SYF ¼ RF
ð14Þ
h ¼ YF HR þ Cp;m T
ð15Þ
The enthalpy, h, is defined as
when Cp,m is the mean specific heat and it is obtained, with the summation over all
species, from
X
Cp;m ¼
Yk Cp;k
ð16Þ
k
The eddy dissipation model (EDM) proposed by Magnussen et Hjertager [17], is
used to calculate the reaction rate Rf from
YO
Ypr
e
RF ¼ CR CA q min YF ; 2 ; CB
k
1þi
i
ð17Þ
where CR ¼ 4.0 (for collision mixing model), CA ¼ 1.0 (for infinite rate chemistry),
and CB ¼ 0.5 (an empirical mixing constant). After obtaining YF, the mixture
fraction model is used to calculate the mass fraction of other species.
SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
903
2.4. Radiation Model
In this work, the finite-volume method (FVM), known by its simplicity and its
adaptation to flows simulation particularly to turbulent combustion code, is used.
The radiative transfer equation (RTE) in an absorbing-emitting and scattering gray
medium can be written as [18, 19]
ðX rÞIðr; XÞ ¼ jðrÞIb ðrÞ bðrÞIðr; XÞ þ
rs ðrÞ
4p
Z
X0 ¼4p
UðX0 ! XÞIðr; X0 ÞdX0 ð18Þ
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However, in non-gray medium when the absorption j, the extinction b, and the
scattering rs, coefficients depend on frequency t, the RTE becomes
ðX rÞIt ðr; XÞ ¼ jt ðrÞIbt ðrÞ bt ðrÞIt ðr; XÞ þ
rs ðrÞ
4p
Z
X0 ¼4p
Ut ðX0 ! XÞIt ðr; X0 ÞdX0
ð19Þ
where It(r, X) is the spectral radiation intensity at any position r and along a direction X. Ibt is the spectral blackbody radiation intensity. Ut(X0 ! X) represents the
spectral scattering phase function from the incoming direction X0 to the outgoing
direction X. Knowing that using the weighted-sum-of-gray gases (WSGG), the total
intensity I is obtained by summing up all the kth gray gas intensities, represented in
the following expression.
I mn ¼
X
Ikmn
k
ð20Þ
For a two-dimensional axisymmetric problem, the spatial derivative term in Eq. (18)
in the cylindrical coordinates becomes according to reference [18]
ðX rÞI mn ðr; XÞ ¼
mmn qðrI mn Þ 1 qðgmn I mn Þ
qI mn
þ nmn
qr
r
qW
r
qx
ð21Þ
where mmn, gmn, and nmn are the direction cosines, and W is the azimuthal angle
measured from the direction, as shown in Figure 1. The direction cosines are
defined by
mmn ¼ sin h cos W
ð22aÞ
gmn ¼ sin h sin W
ð22bÞ
nmn ¼ cos h
ð22cÞ
The integration of the RTE for an absorbing-emmiting-scattering medium over a
volume cell and a solid angle, and its discretization in spatial and angular domains
and along a discrete direction Xmn ¼ (mmn, gmn, nmn) using the finite-volume method,
Downloaded By: [Gassoumi, Taoufik] At: 20:45 23 December 2009
904
T. GASSOUMI ET AL.
Figure 1. Direction cosines and control solid angle.
can be obtained in the point P at the control volume according to reference [20] as
mn1=2
IPmn ¼
mn
mn mn
mn
Aw Dmn
þ SmP
DV DXmn
cr IW þ Ab Dcx IB ðAe Aw Þamn1=2 IP
mn
mn
mn
mn
Ae Dcr IW þ At Dcx ðAe Aw Þamnþ1=2 þ bmod DV DXmn
ð23Þ
with
DXmn ¼
Z
hmþ1=2
Z
Wmþ1=2
sinh dh dW
Dh 1 h
i
amnþ1=2 ¼ sin Wnþ1=2
sin 2hmþ1=2 sin 2hm1=2
2
4
Z
r
0 0
0
0
0 0
s
Um n >mn IPm n dXm n
SPmn ¼ jIbPþ
0
0
4p Xm n ¼ 4p
Z
ðX er ÞdX
Dmn
cr ¼
mn
ZDX
ðX ex ÞdX
Dmn
cx ¼
hm1=2
wm1=2
DXmn
ð24aÞ
ð24bÞ
ð24cÞ
ð24dÞ
ð24eÞ
and
At ¼Ab ¼ p r2e r2w
Ae ¼ 2pDxre
Aw ¼ 2pDxrw
ð24f Þ
ð24gÞ
ð24hÞ
mn
In these equations, Dmn
cr and Dcx are the direction cosines regarding the r and x
directions, respectively. At, Ab, Aw, and Ae are the top, bottom, west, and east faces
SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
905
of the control volume, respectively, as shown in Figure 2. DV is the control volume
and bmn
mod is the modified extinction coefficient [20].
The combustor wall is assumed gray surface characterized by an emissivity ew
and nw its unit normal vector. This surface emits and reflects diffusely, and then the
radiative boundary condition for Eq. (18) is written as [18]
Z
ð1 ew Þ
Iðrw ; Xþ Þ ¼ ew Ib ðrw Þ þ
ð25Þ
Iðrw ; Xþ Þjnw X jdX
p
nw X 0
when X and Xþ indicate the arriving and leaving radiative intensity directions,
respectively. The radiative heat flux at the wall can be estimated by
X
qwr ¼
IPmn Dmn
ð26Þ
cwall
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mn
The radiation source term, Sr, is given by
Z 1
jt ð4pIbt <n Þdn
Sr ¼ r qr ¼
ð27Þ
0
where the incident radiation, <, is written as
Z 1
Z 1Z
<¼
It dXdn
<n dn ¼
0
0
ð28Þ
4p
In the present work, the narrow-band based weighted-sum-of-gray-gases
(WSGG-SNB) model of Kim and Song [15] is used. This model uses the design of
the weighted-sum-of-gray-gases model (WSGGM) with the database of the statistical
narrow band model (SNB) to model the radiative properties of gas mixture [15, 21].
At present, this new model is one of the best models which offers a good compromise
Figure 2. Variables related to grid system.
906
T. GASSOUMI ET AL.
between precision and computing time [15, 21]. The extinction coefficient is
bt ¼ jt þ rst
ð29aÞ
and the single scattering albedo, xt, is defined as
xt ¼
rst
rst
¼
jt þ rst
bt
ð29bÞ
For the kth gray gas, the absorption coefficient is
jk ¼ jg;k þ js;k
ð30aÞ
Here, soot are treated as gray so Eq. (30a) becomes
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jk ¼ jg;k þ js
ð30bÞ
Indeed, the WSGG model assigns to a non-gray gas an equivalent finite number of
gray gases with appropriate weighting factors strongly dependent on the local
temperature [22].
Radiative Properties of Gases and Soot
The absorption coefficient of any gas species i for the partial pressure P and
temperature T is given by [21]
ji ¼ j0i
P ai =T
e
T2
ð31Þ
where j0i and ai are the modeling parameters for species i. In this work, the soot
absorption coefficient is taken in the Rayleigh scattering limit and it is defined like
references [21–24] as
js ¼
3:72fv C0 T
C2
ð32Þ
where C0 ¼ 36pnk=[(n2 k2 þ 2)2 þ 4n2k2], n ¼ 1.85 C2 ¼ 1.4388 cm K. n represents
the real part of the complex index of refraction, and k ¼ 0.22 represents the absorptive index. fv is the soot volumetric fraction. In this article, fv ¼ 105.
3. RESULTS AND DISCUSSION
To validate our numerical model, the experiment of Spadaccini et al. [25] is
considered (Figure 3). The experimental inputs are summarized in Table 3.
The swirl is produced by adding a tangential component on the injection of air.
The most commonly used parameter is the swirl number, SW, and it is defined as the
ratio of axial flux of angular momentum and axial flux of linear momentum [26].
SW ¼
R
2p wrqurdr
R
2pR uqurdr
ð33Þ
SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
907
Downloaded By: [Gassoumi, Taoufik] At: 20:45 23 December 2009
Figure 3. Coordinate system of the coaxial jet combustor (the dimensions are not to scale).
where w represents the tangential component of velocity. In this study, the level of
swirl strength is represented in terms of swirl number.
3.1. Gas Temperature
Figure 4 shows the temperature contours with without radiation. Two cases are
illustrated: a case without swirl (SW ¼ 0.0) and a case with swirl where SW ¼ 0.6. It
is shown that the temperature is very influenced by the swirl. Indeed, the maximum
temperature was increased from 2000 K to 2200 K when the swirl number, SW, was
increased from 0.0 to 0.6. In addition, radiation heat transfer has an important effect
on flame. The effect of radiation heat losses from hot gases to cold wall is less
remarkable when swirl is applied. It is also shown that radiation reaches the injection
zone and overheats the fuel which facilitates, consequently, its ignition.
Table 3. Dimensions and flow conditions
The Dimensions
(cm)
Central pipe radius (r1)
Annular inner radius (r2)
Annular wall thickness (r2r1)
Annular outer radius (r3)
Combustor radius r4
Combustor length (L)
Flow conditions
Mass flow rate (kg=s)
Bulk velocity u(m=s)
Temperature T (K)
Swirl number SW
CH4 mass fraction YCH4
O2 mass fraction YO2
N2 mass fraction YN2
Overall equivalence ratio f
Combustor pressure (atm)
3.157
3.175
0.018
4.685 R
6.115
100.0
Inner jet (fuel)
Outer jet (air)
0.00720
0.9287
300
0.0
1
0.0
0.0
0.137
20.63 U
750
0.6
0.0
0.2329
0.7671
0.9
1.0
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Figure 4. Isotherm contours in the combustor chamber with and without radiation for two different swirl
number: SW ¼ 0.0 (case without swirl) and SW ¼ 0.6 (case with swirl). (a) Temperature contours without
radiation: up without swirl and down with swirl; (b) isotherm contours without radiation: up without swirl
and down with swirl; (c) temperature contours with radiation: up without swirl and down with swirl; and
(d) isotherm contours with radiation: up without swirl and down with swirl.
In the case without swirl (SW ¼ 0.0), Figures 4b and 4d clearly show the disparaition of the isotherm 2000 K when radiation is taken into account (Figures 4b and
4d: up). However, when swirl is introduced (SW ¼ 0.6), the 2200 K isotherm
(Figure 4b: down) is still there when radiation is applied but in a reduced zone
(4d: down). In light of these observations, one can conclude that swirl offers a good
mixing of the mixture, which increases the temperature significantly. This is observed
in Figure 4, when temperature increases about 200 K when swirl is applied. Indeed,
swirl can create a recirculation zone: this offers a good mixing of the fuel and air.
In addition, a portion of the unburned gases will go back to the combustion zone
where temperature reaches its maximum and will be in a favorable condition of
ignition. However, the intensity of turbulence and the flame speed vary proportionally with the swirl number. So, we must take care because a high swirl number can
lead to the lift-off or even to the occurrence of flame flashback.
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Figure 5. Temperature contours with swirl (SW ¼ 1.0): without radiation (up) and with radiation (down).
When the swirl number increases, the intensity of turbulence increases and the
flame length decreases. However, the use of high swirl number can lead to flame
flashback. With swirl, there is a compensation of the radiative heat transfer effect.
However, it is important to note that the computational power of any numerical
code can be evaluated near the bluff-body by solving any scale motion.
Figure 5 clearly shows that the size of the high temperature regions of the flame
was reduced significantly when radiation is taken into account. Figure 6 illustrates the
radial profile of temperature compared with experimental data [24] at four different
axial locations and for a swirl number SW ¼ 0.6. At the two positions x=R ¼ 0.887
and x=R ¼ 1.57, convection is the important transfer mode because of strong fluctuations in this region. The error found in Figures 6a and 6b is due to this strong dynamic
behavior. The reflections about the centerline of data points taken on the opposite side
of the combustor are considered. For the third station, x=R ¼ 4.52, and the fourth
station, x=R ¼ 5.19, the profiles agree with the experimental data. The radiative heat
transfer effect is clearly observed from the main combustion zone, where temperature
reaches its maximum towards the combustor outlet (see Figures 6c and 6d).
3.2. CO2 Mass Fraction
Figure 7 presents the CO2 mass fraction contours with and without radiation
for two different swirl numbers: SW ¼ 0.6 and SW ¼ 1.0. It shows the good mixing
due to swirl and the variation of the CO2 mass fraction in the same location due to
the recirculation zone where fluctuations are important (see Figure 8). Figure 7
clearly shows the recirculation of products from reactions occurring farther
downstream. The important observation is that the CO2 mass fraction decreases
from the main combustion zone towards the combustor outlet when the swirl number increases. It is shown in the literature, that the decrease was very small compared
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Figure 6. Radial profile of temperature compared with experimental data. (a) Temperature at
x=R ¼ 0.887; (b) temperature at x=R ¼ 1.57; (c) temperature at x=R ¼ 4.52; and (d) temperature at x=
R ¼ 5.19.
Figure 7. CO2 mass fraction contours with and without radiation for SW ¼ 0.6 and SW ¼ 1.0. (a) Case
without radiation: up SW ¼ 0.6 and down SW ¼ 1.0; (b) case with radiation: up SW ¼ 0.6 and down
SW ¼ 1.0.
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SWIRL EFFECT ON A COAXIAL JET COMBUSTOR FLAME
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Figure 8. The different recirculation zones in the combustor.
to the reduction of NOx emissions [27]. Generally, the swirl can stabilize the flame
and increase the combustion efficiency. Furthermore, the good mixing significantly
reduces the NOx emissions.
4. CONCLUSION
A numerical simulation of the swirl effect in a combustor chamber is investigated. To correctly judge the influence of swirl, radiation is taken into account by
solving the radiative transfer equation using the finite-volume method and the
narrow-band based weighted-sum-of-gray gases (WSGG-SNB) model. In this work,
the effect of swirl is analyzed, including radiative heat transfer, which helps us understand the behavior of the flame under various operating conditions and avoids the
under- or over-prediction of heat transfer in a combustion system. The results show
that the convective exchange in swirling flow is very important in the region close to
the inlet. For more accuracy, radiation of gases, soot, and wall must be taken into
account from the high temperature regions of the flame towards the combustor outlet. The results show that applying swirl can be a solution to improving combustion
efficiency and, consequently, reducing NOx emission.
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