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7/30/2019 A Janus Orn Research
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Numerical and Experimental Studies onHeat Transfer in Circulating Fluidized BedBoilers
6thsemester
Asian Institute of Technology Energy
Anusorn Chinsuwan
Examination Committee: Prof. Sivanappan Kumar (Chairman)
Dr. Animesh Dutta (Co-chairman)
Dr. Hemantha P Jayasuriya
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Hydrodynamics in CFB furnace
Most combustion take place in fast fluidized bed zone
The majority of bed particle move upwards through core, but they flowdownwards along the wall.
Turbulent or Bubbling
Fluidized Bed
F
astFluidized
Bed
Swirl
Flow
Moving
PackBed
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Heat Transfer in CFB Boilers
fraction of wall receiving
heat from clusters
fraction of wall receiving
heat from clusters
Heat transfer surface
Cluster moving
upward
Cluster moving
downward
Cluster moving
downward
Convection from
dilute phase
Conduction from
particles
Radiation of dense
and dilute phase
CFB water walls
Particles flow down
along
the wall in
form of
clusters
Particle Convection plays most important role in heat transfer.
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Advantages of CFB boilers
Fuel Flexibility
The special
hydrodynamics
condition inCFB furnace
Excellent gas-solid
andsolid-solid mixing
Fuel particles are
rapidly heated aboveignition temp.
CFB furnace
can burnany fuel
High Combustion Efficiency
Better gas-solid mixing
A majority of unburned fuel
particles are recycled backto the furnace
High combustionefficiency
Efficient Sulfur Removal
More residence time
for sulfur
dioxide to contact withsorbents
Smaller particle size ofsorbents
Efficient
sulfurremoval
Low NO2 Emission
Fuel
Nitrogen does not find O2 in
the immediate vicinity forproduce oxides
Fuel nitrogen transfer tomolecular nitrogen
Sub-
stoichiometri
c air supplied
as primary
air
Reducingzone
Secondary air
Limited opportunity forformation of NO2
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Heat Transfer Coefficient
Summary of empirical correlations of heat transfer in large scale CFBboilers (Dutta and Basu, 2003)
The heat transfercoefficient is a function of
cross section averagesuspension density.
b
h a
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Model for Predicting Suspension Density
I t seems to b e more practical but it can not exp lain the inf luence of bed diameter and it have been
yet validated with o ther commercial CFB boilers
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Statement of Question 1
Are there models for
predicting the suspension
density along the height ofcommercial CFB boilers?
What are the
limitations of eachavailable model?
Could the suspension density along
the height of commercial CFB boilersbe developed in more practical?
Yes, there are Kunii and
Levenspiel Model(1991),
Johnsson and Leckner
Model(1995) and Teplitskiy andRyabov Model(1999)
The models need some measured
values which are not available anddifficult to measure.
?
Statement of Question 3
Statement of Question 2
Is there
information of
heat transfer
behavior in
membrane water
wall along the
height of
commercial CFB
boilers ?
No, there is not.
Is there any way to increase the heat
absorption from CFB furnace with less costlyand less risk of material erosion ?
Is it easy to manufacture and revamp from anexisting boiler ?
Yes, by weldinglongitudinal fins on tube.
?
Does longitudinal fin
orientation have any effecton heat transfer behavior?
Is there literature reporting heat transfer
behavior in membrane water wall with two fins at45 deg on both sides of the tube crest ? No
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Rational
Heat transfer coefficientHeat transfer coefficient correlation:
b c
h a T
Model for predicting cross sectional
average suspension density alongCFB furnace height
Temperature
distribution alongthe height of
CFB furnaceswall
Heat flux along
the height of CFBfurnaces wall
Opt imum designofCFB boilers
Numerical investigation of heat
transfer behavior in membrane
water wall tube along the height ofCFB boilers
Heat generation bycombustion
Water wall of CFBfurnace
Small heat absorbedby wall
Large heat absorbedby wall
High furnacetemp
Low furnacetemp
To mainta in the combust ion temp at an
opt imum level , i t is required for the wal l of
CFB furnace to absorb a certain fraction o f
the heat input
Enhancement of heatabsorption in CFB furnace
Additional heat transferequipments
Additional heating surface areaon membrane water wall
Wing wall, omega tubes,external heat exchangers
Cost ly and may enhance the
r isk of tube sur face erosion
Simple to manufacture and
less cost ly and i t may be
used to revamp an exist ingboiler
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Objective
1. Develop an empirical model for predicting the cross sectional averagesuspension density in commercial circulating fluidized bed boilers.
2. Numerical simulations on heat transfer behavior along the height ofmembrane water wall of CFB boilers. The specific objectives are:
a) Numerical simulations on temperature distribution in membrane waterwall tubes of commercial CFB boilers
b) Numerical simulations on heat flux distribution on membrane water walltubes of commercial CFB boilers
3. Experimental study and numerical analysis on the effect oflongitudinal fin orientation on heat transfer in membrane water walls.The specific objectives are:
a) Experimental investigation of the effect of longitudinal fin orientation onheat transfer in membrane water wall tubes in a circulating fluidizedbed.
b) Investigation of the heat transfer behavior of longitudinal finnedmembrane water wall tubes in CFB boilers.
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Scope and Limitations
Objective 1
The empirical model is developed and
validated based on measured data ofcommercial CFB boilers reported inliterature.
The model is developed as a function:
Fr , ,p
t
s
d zf
D H
z
Airdistributor
Secondary air
injectors
Center of
furnace exit
Fuel feed Return
D
z
Z H
Objective 2
Numerical simulations are performed in3D under normal operating conditions ofCFB boilers:
Tb =850CFrt = 0.0007, 0.125 and 0.250
dp/D= 15,125 and 250 mm/m
Membrane tube configurations
25.4 , 6w mm t mm 50.8 30.8mmOD mmID
Objective 3
Experiments are performed on 3 tube types in acold model CFB riser.
Tb =75C,
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Research Methodology
Experimental data from
Andersson (1996)
Grouping based on
Proposed model based on dimensionless
groups:
Error analysis based on
RMS differences
Error analysis based on
RMS
differences for the model
of Johnsson and Leckner
(1995)
Error analysis based on
RMS
differences for the model
of Teplitskiy and Ryabov
(1999)
Model
assessment
Available measured data of
large scale CFB boilers from
literature
Development of m odel
Comparison
of error
Error analysis based
on RMS differences
for the obtained
model
Error analysis based
on RMS differences
for model of
Johnsson and
Leckner(1995)
Error analysis based
on RMS differences
for model of
Teplitskiy and
Ryabov (1999)
Conclusions
Comparisonof error
Model val idat ion
3 3
3
3
c d
pb
t
s
d za Fr
D H
pd
Objective 1
A i I tit t f T h l
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Research Methodology
Objective 2
GAMBIT
Geometry setup Grid generation Boundary setup
Develop User Defined (UDF)
Function using C language
FLUENT Material definition Boundary definition Calculation Postprocessing
Problems
Solution
Available data from literaturesModel validationNo
Grid dependence studyNo
Yes
Yes
Computational model
Geometry
Operating and geometric conditions of
CFB boilereported in literature:
Fr , / , /t p
d D z H andZ
Physicalmodel
Obtained model from Study #1
3 3
3
3
c d
pb
t
s
d za Fr
D H
Available model for predicting localheat transfer coefficient in literature
(Dutta and Basu, 2002)
Development of
computational model
Simulation
Perform the simulation
Fr , / , /t p
d D z H andHin therange of simulation
Model of Dutta and Basu (2002)
Obtained model from Study #1
3 3
3
3
c d
pb
t
s
d za Fr
D H
Results
Temperature profiles
Fr , / , /o t pf d D z H
Material limit based
on allowable stress
Material limit based
on oxidation
A i I tit t f T h l
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Research Methodology
Objective 3
Experimental study
Study #3
Compare the obtained
data with data in
literature
Conclusion
H drod namics
Heat transfer study
Compare the obtained
data with data in
literature
Heat transfer coefficient
Ratio of heat transfer in
longitudinal fin to the combination
of tube and membrane fins portion
Ratio of heat transfer coefficient at
longitudinal fin to the combination of
tube and membrane fins portion
Membrane water
wall with a
longitudinal fin at
the tube crest
Membrane water
wallMembrane water wall
with two longitudinal
fins at 45 on both sides
of the tube crest
Ratio of heat transfer of membrane
tube with longitudinal fin(s) to
without longitudinal fin
Ratio of heat transfer coefficient of
membrane tube with longitudinal
fin(s) to without longitudinal fin
Available
heat transfer
coefficientin
commercial
CFB boilers
in literature
Hin
m
a
tu
Cfl
m
a
tuAgree
Disagree DisagreePre are a aratus
A i I tit t f T h l
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Research Methodology
Objective 3, Experimental setup
EL. 00
Distributor
plate
300
300
300
300
300
400
400
400
400
400
400
400
To bag filter
From bag filterFrom air
compressor
Water manometer
Temperature
indicator
Pressure gauge
Pressure gauge
Pressure regulator
Pitot tube
Rotameter
Storage
column
EL. 1800
EL. 3000
EL. 4200
EL. 4800
Particle
measuring valve
Particle control valve
Test section
Bypass
Air heater box
Blower
T
Circulating
pump
Bypass
Drain
Water storage
tank
Rotameter
Flow control
valve
T
To
test
tube
type
B
To
test
tube
type
A
To water manometer
To
test
tube
type
C
Test
tube
400Particle measuring
column
Bed material sand
Mean diameter,p
d 231 mm
Density,s
31515kg m Bed properties
Bulk density 32774kg m
Superficial velocity, U 18ms
Suspension density, 325 75kg m
Bed inventory, I 15kg
Solid circulation rate, sG 2 122 110kgm s
Operating conditions
Bed temperature, bT 70 75 C
Experimental conditions
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Research Methodology
Objective 3, Experimental setup
Plywood
6mm thk
Tube type A
2 inch thick Glass Wool
Pressure tap
Temperature
probe
Tube type B
Tube type C
SECTION C-C
Temperature
measuring point400
400
EL. 1800
EL. 3000
E E
E E
C C
Pressure tapping
2 inch
Glass Wool
For clarity, one test tube is shown.
Plywood
6mm thk
Tube type A
Pressure tap
Tube type B
Tube type C
SECTION E-E
Temperature
measuring point
2 inch thick Glass Wool
(a) (b) (c)
InsulationInsulation Insulation
Membrane
fin Longitudinal
finTube type A Tube type B Tube type C
3 3 3
14 14
14
14 14
14 14
3
3 3
7 7
45o
31.8 OD x 6.5 thk.31.8 OD x 6.5 thk.
31.8 OD x 6.5 thk.
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Schedule
Tentative Schedule
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Results
Objective 1
Air distributor
Secondary air injectors
Center of furnace
exit
Fuel
feed
Return
DZ H
z
z/H
.001 .01 .1 1
(
/s)/[Frt
0.4193(d
p/D)-
0.998]
.01
.1
1
10
100
dp=224mm, U=1.83m s-1, U
t=1.25m s
-1
dp=224mm, U=2.65m s-1, U
t=1.32m s
-1
dp=329mm, U=3.58m s-1, U
t=2.26m s
-1
dp=329mm, U=2.68m s-1, U
t=2.39m s
-1
dp=432mm, U=4.53m s-1, U
t=3.33m s
-1
dp=432mm, U=6.39m s-1, U
t=3.45m s
-1
0.4326
0.9980.4193
/2.5513 /
Fr /
s
t p
z H
d D
Boiler No.Equation (Equation no.)RMS
1 2 3 4 5
overallRMS 8.890.998 0.4326
0.41932.5513Fr (4.6)p
t
s
d z
D H
Present work RMS 5.60 11.50 14.51 1.77 1.94
overallRMS 24.900.45
0.620.053Fr (4.3)t
s
z
H
Teplitskiy and Ryabov (1999) RMS 21.93 30.45 15.58 2.49 7.84
overallRMS na( ) ( )
2,( ) (4.2)x
x
a z H b H z
x H exit ge e
Johnsson and Leckner(1995) RMS 14.6 na na na na
RMS is the Root Mean Squared Deviations and 2
/predicted measuredRMS N , where N is number of data.
na: not applicable
The numbers in italic show the lowestRMS .
Boiler specification Operating conditionsBoilerNo.
AuthorsCapacity
Furnace size
( W L Z )[ 3m ]bT [ C] pd [ mm ]
U
[ 1ms ]tU
[ 1ms ]
1 Andersson(1996) 12 thMW 1.5 1.7 13.5 865 288 3.68 1.90
2 Johnsson and Leckner (1995) 12 thMW 1.5 1.7 13.5 850 320 2.7,4.7 2.2
3 Yang et al. (2005) 135 eMW 6.6 13.1 38 885,896,892 332,318,300 3.5 3.02,2.89,2.73
4 Kavidass et al. (1997) 35 thMW 3.1 3.66 24.4 870 350 5.0-6.0 3.2
5 Kavidass et al. (1997) 81 thMW 4.32 4.57 30.5 870 350 5.0-6.0 3.64
0.998 0.4326
0.41932.5513Frp
t
s
d z
D H
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Suspension density [ kg m-3
]
0 10 20 30 40 50 60
0
2
4
6
8
10
12
14
16
18Data from boiler no. 4 (Kavidass, 1997)
Present predicted curve eq. (4.6)
Teplitskiy and Ryabov (1999) model eq. (4.3)
Suspension density [ kg m-3
]
0 10 20 30 40
Heightaboveinflectionpoint[m]
0
5
10
15
20
25
30
Data from boiler no. 3 (Yang et al.,2005)
Present predicted curve eq. (4.6)
Teplitskiy and Ryabov (1999) model eq. (4.3)
Suspension density [ kg m-3
]
0 10 20 30 40 50 60
Heightabovesecondaryairports[m]
0
5
10
15
20
25
Data from boiler no. 5 (Kavidass et al., 1997)
Present predicted curve eq. (4.6)
Teplitskiy and Ryabov (1999) model eq. (4.3)
Suspension density [ kg m-3
]
0 20 40 60
Heightaboveairdistributor[m]
0
2
4
6
8
10
12
Data from boiler no. 1 (Andersson, 1996)
dp=288 mm, U=3.68m s-1, U
t=1.90m s
-1
Present predicted curve eq. (4.6)
Johnsson and Leckner (1995) model eq.(4.2)predicted by Andersson (1996)
Teplitskiy and Ryabov (1999) model eq.(4.3)
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Results
Objective 2
Parameters Symbol Unit Values
Water tube diametero
d mm 60 Tube thickness t mm 6 Tube pitch P mm 78 Membrane fin thickness
ft mm 6
The height from secondary air ports to furnace exit H m 10,20,30
Thermal conductivity k 1 1Wm K 20 Inner heat transfer coefficient of the water tube
ih 2 1Wm K 5500
External heat transfer coefficient of the water tubeo
h 2 1Wm K As Dutta and Basus Model
Cross sectional average suspension density 3kg m As result from Study #1
Inner fluid temperaturefT C 342.25 15MPa
Bed temperatureb
T C 850 Froude number Frt - 0.0007,0.125,0.25
Particle to furnace diameter ratio /pd D
1mmm 15,125,250
Adiabatic surface
External surface
Internal convection
surface
Symmetric surface
Symmetric surface
Symmetric surface
Insulation
CFB or PC furnace
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Temperature distribution at the top of water wall
Temperature distribution at the bottom of
water wall
Heat flux distribution at the top ofwater wall
Grid Scheme
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Height along furnace, z[m]
0 5 10 15 20 25 30
Heatflux[k
W/m2]
0
200
400
600
800
1000
Steam
quality[-]
0.00
.05
.10
.15
.20
.25
.30
72MWth, Chatham unit
109MWth, Flensburg unit
Predicted steam quality165MW
th, Orebro unit
Heat flux absorbed of 165MWth, Orebro unit
Design heat flux of 158MWth PC boiler,(Payan-Rodriguez et al., 2005)
Design steam quality of 158MWth PC boiler,
(Payan-Rodriguez et al., 2005)
Temperature Distribution
0.324
0.1414
,0.8976Fr
p
o m t
d
D
0.13985
0.3240.1414
0.8147Fr /
o
t p
z
Hd D
Frt= (U-Ut)2/gH
.01 .1
o,m/(d
p/D)-
0.324
.01
.1
1
10
100
, 0.1414
0.3240.8976Fro m
t
pd
D
Numerical predicted curve
Chalmers, 12MWth (Andersson, 1996)
Chatham, 72MWth (Couturier et al., 1993)
Flensburg, 109MWth (Werdermann and Werther, 1994)
Orebro, 165MWth
(Andersson et al., 1997)
0.13984
0.324
0.1414
5.2244
Fr
o
p
t
z
Hd
D
Heat Flux Distribution
0.86016
xx F z
0.324
0.1414
0.13984
Fr /26.0738
b f t p
x
fg
T T d DF k
Gdh d H
Steam Quality
Material Limits
,
, 0.3240.1414
0.8976Fr /
max stress
stress
t p
Fd D
,
, 0.3240.1414
0.8976
Fr /
max ox
ox
t p
F
d D
Common steel tubes used
in boiler industrial can be
used to as evaporator tube
in CFB boilers.
Tube Burnout
Parameters
for DesigningCFB Furnaces
Next page
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z[m]
0 5 10 15 20 25 30
Heatflux[k
W/m
2]
0
200
400
600
800
1000
1200
1400
1600
1800
Frt=0.125, d
p/D=15mm/m, 15MPa
Frt=0.125, d
p/D=15mm/m, 20MPa
Frt=0.250, d
p/D=15mm/m, 20MPa
Frt=0.250, d
p/D=15mm/m, 15MPa
Frt=0.125, d
p/D=15mm/m, 15MPa
Frt=0.250, d
p/D=15mm/m, 15MPa
Frt=0.125, d
p/D=15mm/m, 20MPa
Frt=0.250, d
p/D=15mm/m, 20MPa
H= 30m
Heat flux absorbed
Critical heat flux
Height along CFB furnace, z[m]
0 5 10 15 20 25 30
Heatflux[k
W/m
2]
0
1000
2000
3000
4000
72MWth, Chatham unit
109MWth, Flensburg unit
165MWth, Orebro unit
72MWth, Chatham unit
109MWth, Flensburg unit
165MWth, Orebro unit
Critical heat flux
Heat flux absorbed
z[m]
0 5 10 15 20
Heatflux[kW
/m2]
0
200
400
600
800
1000
1200
1400
1600
1800
Frt=0.125, d
p/D=15mm/m, 15MPa Fr
t=0.125, d
p/D=15mm/m, 20MPa
Frt=0.250, d
p/D=15mm/m, 20MPaFrt=0.250, dp/D=15mm/m, 15MPa
Frt=0.125, d
p/D=15mm/m, 15MPa
Frt=0.250, d
p/D=15mm/m, 15MPa
Frt=0.125, d
p/D=15mm/m, 20MPa
Frt=0.250, d
p/D=15mm/m, 20MPa
H= 20m
Heat flux absorbedCritical heat flux
Parameters for
Designing CFB
Furnaces
Tube Burnout
0.0007 Fr 0.250, 10 ,20 ,30t H m m m
15 / / 250 /pm m d D m mm m
max
300 20
6 8
pd m D m
D m m
m
Fr 0.12520
Fr 0.250
Fr 0.12530
Fr 0.25
20
/ 15 /
0
t
t
t
t
p
H
MPa
d
H
m
m
D
m
mm
Real situation
4 cases of tube burnoutare found.
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Height above secondary air ports, z(m)
0 2 4 6 8 10
0.0
.5
1.0
1.5
2.0
2.5
3.0
Frt=0.0007, dp/D=15mm/m
Frt=0.0007, dp/D=125mm/mFrt=0.0007, dp/D=250mm/m
Frt=0.125, dp/D=15mm/m
Frt=0.125, dp/D=125mm/m
Frt=0.125, dp/D=250mm/m
Frt=0.250, dp/D=125mm/m
Frt=0.250, dp/D=250mm/m
Frt=0.250, dp/D=15mm/m
H=10m
Height above secondary air ports, z(m)
0 5 10 15 20
0
1
2
3
4
5
6
Frt=0.0007, dp/D=15mm/m
Frt=0.0007, dp/D=125mm/mFrt=0.0007, dp/D=250mm/m
Frt=0.125, dp/D=15mm/m
Frt=0.125, dp/D=125mm/m
Frt=0.125, dp/D=250mm/m
Frt=0.250, dp/D=15mm/m
Frt=0.250, dp/D=125mm/m
Frt=0.250, dp/D=250mm/m
H=20m
Height above secondary air ports, z(m)
0 5 10 15 20 25 30
0
2
4
6
8
10
Frt=0.0007, d
p/D=15mm/m
Frt=0.0007, dp/D=125mm/mFrt=0.0007, dp/D=250mm/m
Frt=0.125, dp/D=15mm/m
Frt=0.125, dp/D=250mm/m
Frt=0.250, dp/D=15mm/m
Frt=0.250, dp/D=125mm/m
Frt=0.250, dp/D=250mm/m
Frt=0.125, dp/D=125mm/m
H=30m
Hot water CFBboilers
/ 125 /
/ 15010 Fr 0. 0
/00 7
p
t
p
Hd D m m
d Dm
m m
m
m
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Results
Objective 3
Suspension density, (kg m-3)20 40 60 80
Heattransfercoefficient,
h(Wm
- 2o C-1)
20
40
60
80
100
Test tube type A
Test tube type B
Test tube type C
Suspension density, (kg m-3)10 20 30 40 50 60 70 80
Heattransferratio(-)
0.0
.2
.4
.6
.8
1.0
Qt-mf,lf/QT,lf
Qt-mf,2lf/QT,2lf
Suspension density, (kg m-3)20 40 60 80
Heattransfercoefficient,
h(W
m-2oC-1)
20
40
60
80
100
120
hlf
ht-mf,lf
h2lf
ht-mf,2lf
havg,mf hlf
ht-mf,lf
ht-mf,2lf
h2lf
havg,mf
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Suspension density, (kg m-3)0 20 40 60 80
Heattransferrateandheattransfer
coefficientratio
.2
.4
.6
.8
1.0
1.2
1.4
1.6
QB / QA
QC / QA
hB / hA
hC/ hA
1.25CB
A A
Q Q
0.8CB
A A
hh
h h
Measured heat transfer coefficient, h(W m-2 oC-1
)
80 100 120 140 160
Predictedheattransfercoefficient,
h(W
m-2oC-1)
80
100
120
140
160
+10%
-10%
Angle from the tube crest, [degree]0 45 90 135 180
Innerwallheatflu
x,
qi(kWm
-2)
0
50
100
150
200
250
300
Tube type A
Tube type B
Tube type C
Angle from the tube crest, [degree]0 45 90 135 180
Temperatu
re[oC]
200
250
300
350
400
450
500
550
Tube type A
Tube type B
Tube type C
Membrane fin tip of tube type A
Membrane fin tip of tube type B
Membrane fin tip of tube type C
Longitudinal fin tip of tube type B
Longitudinal fin tip of tube type C
Membrane fin base
Membrane fin base
Longitudinal fin base
Longitudinal fin base
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Chinsuwan, A. and Dutta, A. (2008). An empirical model for predicting thecross sectional averaged suspension density in commercialcirculating fluidized bed boilers, Journal of the Energy Institute,81(2).
Chinsuwan, A. and Dutta, A. An experimental investigation on the effectof longitudinal fin orientation on heat transfer in membrane water
wall tubes in a circulating fluidized bed. Submitted to InternationalJournal of Heat and Mass Transfer, 2008.
gy EnergyWorks Published
Paper in Refereed International Journal
Papers in Refereed International Conference
Chinsuwan, A. and Dutta, A. (2006). A Developing of EmpiricalCorrelation for Predicting the Axial Suspension Density Distribution
in Circulating Fluidized Bed Boiler. Proceeding of Sustainable
Energy and Environment: Technology and Policy Innovations.
November, Bangkok, 761-765.
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Chinsuwan, A. and Dutta, A. Investigation of the heat transfer behaviorof longitudinal finned membrane water wall tubes in circulatingfluidized bed boilers. Submitted to Powder TechnologysinceJanuary, 2008.
Chinsuwan, A. and Dutta, A. Investigation of the temperature distributionand material limits of membrane water wall tubes of circulatingfluidized bed boilers. Submitted to Canadian Journal of ChemicalEngineeringin April, 2008.
gy EnergyWorks under Review
Under Review in Refereed International Journals(2 papers)
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Summary of Present Studygy Energy
Experimental
Literature review; Chapter 2
Summary of thestudy
Numericalsimulations
Membrane waterwall tube
Chapter 7
Membrane water wall tube
with a longitudinal finChapter 7
Membrane water walltube with two
longitudinal finsChapter 7
Develop model for predicting
suspension densityChapter 4
Temperature
distribution in
membrane wallChapter 5
Heat flux
distribution on
membrane wallChapter 6
Heat behavior
in membrane
water wall with
and without
longitudinal finChapter 8
The
empiricalmodels
Total heat transfer
Heat transfer on fin portion
Heat transfer on the combination of tube
and fin portion
Heat transfer and heat transfer coefficientratio
Average heat transfer
coefficient
Heat transfer coefficient on
fin portion
Heat transfer coefficient onthe combination of tube andmembrane fins portion
Temperature profile
Material limits base on
strengthMaterial limits base onoxidation
Temperature and heat flux distribution on inner tube wall of membrane
tubes with and without longitudinal fin under normal operating conditions ofCFB boilers
Heat flux profile
Steam qualityCHF and DNB
Critical height of hotwater CFB boilers
Theoretical
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Summary of the Resultsgy Energy
Descriptions Equation Operating/Test ConditionsError
(%)
Reference/
Nature of
investigation
Model for predicting average suspension
density
Section 4.3/
Theoretical
Model for predicting temperature profile at the
membrane tube crest.
Section 5.5.1/
Numerical
Model for predicting mean temperature profile
at the membrane tube crest.ditto
Section 5.5.1/
Numerical
Model for predicting temperature limits of tubes
based on allowable stressditto
Section 5.5.2/
Numerical
Model for predicting temperature limits of tubes
based on oxidationditto
Section 5.5.2/
Numerical
Model for predicting heat flux profile at the
membrane tube crest of steam CFB boilersditto
Section 6.3.1/
Numerical
Model for predicting heat flux profile at the
membrane tube crest of hot water CFB boilersditto
Section 6.3.1/
Numerical
Model for predicting steam quality in
membrane water wall tubeditto
Section 6.3.2/
Numerical
Heat transfer ratio
Section 8.4/
Theoretical
0.998 0.43260.41932.5513Fr
p
t
s
d z
D H
0.00092 Fr 0.075t 1 134.17 / 200.75
pmm d D mmm m
25%
0.13985
0.3240.1414
0.8147Fr /
o
t p
z
Hd D
0.0007 Fr 0.250t 1 115 / 250
pmm d D mmm m
24.80%
12.08%
0.324
0.1414
, 0.8976Frp
o m t
d
D
24.80%
12.08%
, 0.8976stressF
, 0.8976oxF
0.13984
0.324
0.1414
5.2244
Fr pt
z
HdD
0.1181
0.2722
0.1227
3.3747
Frp
t
z
Hd
D
0.86016xx F z
/ / 0.8B A C A
h h h h
35.61 6.62kg m
858 918bT C 10%
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Summary of the ResultsEnergy
Descriptions Table/Figure Operating/Test Conditions
Reference/
Nature of
investigation
Limits of water wall
tube material based on
allowable stress
Table 5.5Section 5.4.4/
Theoretical
Limits of water wall
tube material based on
oxidation
Table 5.6Section 5.4.4/
Theoretical
Steam quality factor Table 6.1 and Table 6.2Section 6.3.3/
Numerical
Tendency of water wall
tubes burnoutFigure 6.8-6.10
Section 6.3.3/
Numerical
Critical height of hotwater CFB boilers
Figure 6.14-6.16 Section 6.3.3/Numerical
Comparison of heat
flux on inner tube wall
among tubes type A, B
and C
Figure 8.4Section 8.4/
Numerical
Comparison of
temperature on outer
tube wall among tubes
type A, B and C
Figure 8.5-8.8Section 8.4/
Numerical
0.0007 Fr 0.250t
1 115 / 250pmm d D mmm m
0.0007 Fr 0.250t 1 115 / 250
pmm d D mmm m
15MPa
20MPa
15MPa
20MPa
0.0007 Fr 0.250t
1 115 / 250pmm d D mmm m
10 30H m
0.0007 Fr 0.250t
1 115 / 250p
mm d D mmm m
10 30H m
850bT C315kg m
15p MPa
850bT C315kg m
15p MPa
Asian Institute of Technology Energy
http://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Limits%20of%20Water%20Wall%20Tubes.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Limits%20of%20Water%20Wall%20Tubes.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Steam%20Quality%20Factors.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Tube%20Burnout.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Critical%20Height.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux%20and%20Temp..ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux%20and%20Temp..ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux%20and%20Temp..ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux%20and%20Temp..ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Comparison%20of%20inner%20heat%20flux.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Critical%20Height.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Critical%20Height.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Critical%20Height.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Tube%20Burnout.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Tube%20Burnout.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Tube%20Burnout.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Steam%20Quality%20Factors.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Limits%20of%20Water%20Wall%20Tubes.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Limits%20of%20Water%20Wall%20Tubes.ppt7/30/2019 A Janus Orn Research
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Summary of the ResultsEnergy
0.8CB
A A
hh
h h
,,,,
riserdimension:
Descriptions Equation/Figure Operating/Test Conditions
Reference/
Nature of
investigation
Ratio of heat transfer
through the tube and
membrane fins portion
of the tubes type B and
C
Figure 7.9Section 7.4/
Experimental
Heat transfer
coefficient of the
longitudinal fin and the
combination of tube
and membrane
portions of the tube
type B and C
Figure 7.10 dittoSection 7.4/
Experimental
Average heat transfer
capacity, heat capacity
of the longitudinal fin
portions of the tubes
type A, B and C
Figure 7.11 dittoSection 7.4/
Experimental
Heat transfer ratio of
membrane tube withlongitudinal fin to
membrane tube
ditto Section 8.4/Experimental
Heat transfer
coefficient ratio of
membrane tube with
longitudinal fin to
membrane tube
dittoSection 8.4/
Experimental
18U m s 231pd mm
325 75kg m 2 122 110sG kg m s
70 75bT C
100 100 4.8mm mm m
Test tube: 31.8 1000mmOD mm
1.25CBA A
QQQ Q
Asian Institute of Technology Energy
http://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppthttp://e-learning.kku.ac.th/file.php/467/6th%20semester%20progress%20Backup/Fig7.9-7.11.ppt7/30/2019 A Janus Orn Research
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Contribution of Present StudyEnergy
Heat transfer
There is no literature thatreported:
temperature and heat
flux profile along the
height of CFB boilers
limit of tube materials
base on stress and
oxidation
steam quality in
membrane water wall
tubes
tendency of tube burnout in CFB boilers
critical height of hotwater CFB boilers
There is no
practical model
for predicting
averagesuspension
which includesthe effect of
The average heat transfercoefficient is not available
Present study
Modify the model which was
developed as a function of
dimensionless parameters
based on operating
conditions by taking intoaccount of the effect of
First reported the study on temperature and heat
flux profile on CFB water wall tubes, limits of tube
based on stress and oxidation, steam quality in
tube along the height of CFB boilers, tendency of
tube burn out in CFB boilers and critical height ofhot water CFB boilers.
First reported the study on heat transfer
behavior in membrane water wall tube
with two longitudinal fins at on both sides
of the tube crest and comparison of inner
wall heat flux of membrane tube with andwithout longitudinal fins
C
O
N
T
R
I
B
U
TI
ON
B
A
C
K
G
RO
U
ND
Hydrodynamics
Membrane wall tube Membrane water walltube with a
longitudinal fin
The comparison of heat transfer rate
and heat transfer coefficients between
membrane tube with longitudinal finand without the fin is not available
The heat transfer from
longitudinal fin portion is not
available
The heat transfer from the
combination portion of tube
and membrane fins is notavailable
The heat transfer coefficient of
longitudinal fin portion is notavailable
The heat transfer
coefficient of the
combination portion of
tube and membrane finsare not available Heat flux profile on inner
wall tube is not available
Membrane water walltube with twolongitudinal fins
/pd D
/pd D
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Contribution of Study #1Energy
Hydrodynamics in CFB boilers
There is no practical model forpredicting cross sectional average
suspension density in commercialCFB boilers
Back ground
Modify the model which was developed as a function of
dimensionless parameters based on operatingconditions by taking into account of the effect ofContribution
/pd D
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Contribution of Study #2Energy
Numerical Analysis
TemperatureProfile
Heat FluxProfileModel for predictingTemp. and heat flux profiles
along the CFBfurnace height
Steam Quality
Critical Heat Flux
Tube Burnout
Materials
limits
Material Limits
Based onStress
Material Limits Based
onOxidation
The model for predicting
steam quality
Critical heat flux
Critical height of H/W CFB boilers
Contribution
Result fromStudy #1
Steam BoilersH/W Boilers
Critical Height
Tendency of tube burnout
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Contribution of Study #3Energy
Experimental
Heat Transfer Heat TransferCoefficients
First reported the heat
transfer behavior in
membrane tubes with a
longitudinal fin at thetube crest and two
longitudinal fins at 45o
on both sides of thetube crest
First reported the
comparison of the heat
transfer behavior among
the 3 tube types under
normal operating
conditions of CFB boilers
ContributionHeat Transfer
Capacity
B
A
Q
Q
,
,
t mf lf
T lf
Q
Q
,2
,2
t mf lf
T lf
Q
Q
C
A
Q
Q
B
A
h
h
C
A
h
hlfh 2lfh ,t mf lfh ,2t mf lf h
,avg mfhA ,avg lfhA ,2avg lfhA lfhA 2lfhA
Numerical simulations on heat transfer behavior of 3
tube types under normal operating conditions of CFB
boilers
Temperature distribution Heat Flux distribution
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THANK YOU
Energy