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Design of Oil Burners
Oil BurnersFuel: Furnace Oil
Advantages:– Easy transportation– Simple and less expensive design makes it very
attractive.Design of Oil supply System:
Considerations in Design of oil supply system–Safety–Cost–Convenience–Emergency provision
Heating loop:To minimize the energy consumed in pumping,
viscosity is reduced by heating the fuel. •Single Unit heating loop•Centralized heating loop
-Needed where a common header (mother piece) is placed between heater and pump.
Oil supply system with two stages of pumps:The heater must bear the very high oil pressure at the pump
exit. The oil pressure at the pump exit should be higher than 2Mpa for 120 T/H. As the pressure increases the complication of design increases.So Two Stage systems are used.
Atomizer Oil is injected through oil gun. To increase the contact area of fuel with air, fuel is spitted into fine droplets. This process is called as Atomization of Fuel.
“Finer the atomized oil droplets, the faster they Burn.”Types of Atomizer:• Mechanical Atomizer
• Steam or Compressed air Atomizer
• Low pressure air Atomizer
• Rotary Cup Atomizer
Mechanical Atomizer:
Pressure of the fuel oil itself atomizes the Fuel, also called as pressure jet atomizer.
Main Components:•Atomizer•Swirler•Flow distributor arranged along the burner axis
Oil flows through 1.set of small holes of flow distributor.2.Tangential grooves of oil swirler, where oil gets swirled.3.oil swirls rapidly in swirl room and spurt out from atomizing nozzle.
Mechanical Atomizer:
Angle of AtomizationAtomization Angle:
Atomized oil spurts out of Nozzle forming a Cone Shape. Angle of this cone is Atomization Angle.
Exit Atomizing angle(α):
Draw a line at the exit of atomizer nozzle tanent to the edge of the spray. Angle between the two tangents is Exit Atomizing angle.
Conditioned Atomized angle:At certain distance “x”from atomizing nozzle a line is drawn
perpendicular to the axis of oil spray. If we draw two lines from atomizer inlet to the points of intersection of perpendicular line with the spray profile we get a smaller cone, angle of this cone is Conditioned Atomized angle
“Conditioned angle is less than the Exit atomizing angle. The difference can be 20o or greater”
Atomizer
Spray atomizing size, (Size of Droplets): Larger droplet size dm depends on the relative velocity, Wrel, between the oil droplet and the air as follows
143.03
P
FNdm
5.0
P
GFN
2rel
m W
Kd
Where, dm = largest droplet diameter,
K = coefficient depending on the oil viscosity and surface tension( about 600)
Sauter mean diameter,
FN is flow number ratio given by
AtomizerOil Flux density:
Volume of fuel flowing through unit area perpendicular to the dierection of oil spray in unit time.
•It should be uniform around the periphery otherwise result in poor Combustion
• Also very high flux density is not desirable at spray center a Recirculation Zone.
Design Methods
Calculation of Oil Flow Rate:
Assumptions:
•Oil is an ideal liquid with out any frictional resistance.
(A) Oil Enters tangentially and leaves in the shape of a conical jet
(B) High pressure produces a wide cone
(C) Low oil pressure produces a twisted narrow jet
(A) (B) (C)
• Centrifugal force acts on the liquid, By applying Bernoulli's Equation and law of conservation of mass, flow rate of
oil can be derived as
Design Methods
hKgPrG op 2.3600 2
Where µ is the flow coefficient given by
2
2 1
1
1
A
Where the ratio of oil flow area and the nozzle area,
2
2
1p
w
r
r
Design Methods
rp= nopzzle radius, m
rw= radius of oil film vortex inside the nozzle,m
PO= oil pressure at the inlet of nozzle above that at the exit,Pa
ρ = oil density, Kg/m3.
A = Characteristics flow constant given by
f
RrA p
f
0dAd
Total area of tangential grooves and R is swirl radius
For maximum flow rate We get,
Substituting we get,2
1
A
2
3
Design Methods
2.Calculation of Atomizing Angle:
11
81
2 w
utan
Where, u = tangential velocity & w = swirl velocity.
The actual cone angle is slightly different from that calculated
3.Emprical Method of Calculation of Flow Coefficient µ:
from tests carried out following relationship are established 88.0p
87.0p
Where,
μp= practical flow coefficient
αp= practical exit atomizing angle
µ, α = Theoretical values calculated from the above formula
Design Methods
Empirical formula method:
If A = 0.8 - 0.1.8; inlet oil pressure = 2.0 Mpa, oil viscosity = 3oE & Nozzle Diameter < 5 mm.
1.137.0 ApreeAR deg57200 37.0
Nozzle characteristics may also be obtained to allow calculation of more practical values of the flow coefficient µ using the equation
2
2 1
1
1
A
AR
rA p
p
862.0
094.2
Where, Ap is a modified practical value of the characteristics coefficient
By using the practical flow coefficient and friction loss we can calculate oil flow rate as follows
hKgPPrG opp 23600 2
Design Methods
Frictional Loss of the Atomizer can be calculated as
Pa 22 vP
Where the velocity in the swirl chamber is
fg
Gv
3600
Wd
Re
Reynolds number is based on the groove dimension
Where, 5.02 OPW
bhhbd 2
Circle Mechanical( Return Flow) Atomizer
The Oil pipe arrangement for a return oil or circle oil atomizer
Cross sectional view of a return oil inner circle type atomizer
C. Circle Mechanical( Return Flow) AtomizerInlet Area Charging Atomizer:
Flow rate is adjusted by changing the inlet area of tangential groove
Circle Atomizer:
Oil Enters swirl chamber through tangential holes in swirl section. one part of oil swirls out from the atomizer nozzle: the other part returns from the swirl chamber through a number of circle holes on the baack of the swirl chamber. This oil returns to the pump. It is called inner circle atomizer.
There is another design known as outer circle atomizer, where oil enters through the central hole and returns through peripheral holes.
Multiple holes for return oil can be drilled in a circle on the back plate of the swirl chamber. When the diameter of the holes is 1.3 times the diameter of the atomizer nozzle, the maximum adjustment ratio nmax an be about 3.
min
maxmax G
Gn
Steam (or compressed Air) Atomizer
•Consumes High steam
•Atomization is assisted by either high –pressure air or high pressure steam. Accordingly they are of the steam-mechanical atomizer or pure steam atomizer type.
Types:-•Pure steam Atomizer•Steam-mechanical Atomizer type
Pure Steam Atomizer
Steam Mechanical atomizers are two types:
Inner mixing type– Steam and Oil meet in the mixing chamber at the tip of burner.
Outer mixing type– Oil meets the steam outside the atomizer, chances of high
pressure oil entering the steam to contaminater steam is minimum
Design of Y-Type Atomizer
1.Number of Holes, n:
Between 5 and 30 per atomizer
2.Oil hole diameter, d1:
For chosen number of holes, n, the hole diameter d2 can be found from the total cross sectional area of the oil holes
Design of Y-Type AtomizerRequired Oil flow rate G,
3
30
1
Kg/m oil, ofDensity
0.7 Usually t,Coefficien Flow
Kg/h Atomizer, of rate flow Oil
Where,
.23600
G
PPP
PFG
3.Steam or Air Hole Diameter,d2
The diameter d2 is based on the mass flow rate m2
air compressedfor 2.14 saturated,for steam,1.99 heatedsuper for 09.2
mholes,air of area onalcrosssecti TotalF
tcoefficien flow
where,
Kg/h)(3600
22
222
sPFm
Design of Y-Type Atomizer
23 PP
Graph represents:
Flow coefficient µ for flow of oil through oil holes plotted as a function of oil hole exit velocities and different ratios of areas of air/steam hole(F1),oil hole area (F2) and mixing hole area (F3) for Y-Type manometer.
4.Mixing Hole Diameter d3:
Ratio of mixing hole diameter and steam hole diameter (d3/d2) is of the range 1.4-1.8.
Design of Y-Type Atomizer5.Length of Mixing Hole: l3 :
The distance between the exit ioil holes and steam holes l2 is an important parameter, allowing good mixing of steam..
Following ratio’s may be used:
0.50.4
7.0
33
31
dl
dl
6.Angle between Oil and steam Hole:
Recommended range of angle is 50-65o
7.Atomizing Angle:
Preferred range: 70-900.Actual atomizing may be about 15-250 larger than the Value.
8. Diameter , Dair, of steam hole center line:
12
dnDair
Design of Y-Type Atomizer9.Annular Diameter, Dmix of the Mixing Hole:
For geometry it is given by
2
sin2 321a
airmix lllDD
10.Droplet sizes:
mmW
dq
mv
drsteam
oil
drop 3.0
2.01.03
5.0
1.05.0 11200
at density steam
dyne/cm oil, theof tension surface
cm hole, mixing ofdiameter d
oil gsteam/ grate,n consumptio Steam
g/s holr,flower oilm
(Cst) oil ofViscosity
where,
steam
3
oil
oil
oil
q
v
air compressedfor 38.3
steam saturatedfor 22.3
steam heatedsuper for 33.0
/5.0
k
k
k
smvPkw steamsteamcr
Low pressure Air Atomizer
Design Procedure:
1.Diameter Doil:
mmWG
mWGDoil
5.0
5.0
.8.18
36004
2.Cross sectional Area of Nozzle:
2196 mmP
GA
O
oil
Where,
µ= Oil Nozzle flow coefficient = 0.2-0.3,
Po= Oil Pressure before Nozzle in Pa, N/m2
ρ = Oil Density Kg/m3
3.The Diameter of air inlet tube is found to be,
Where, Da= Air Consumption rate Kg/h
ρa = Air Density Kg/m3
Wa = Air Velociy10-15 m/s
4.Exit Section Area, Aa of air nozzle
Where, Va = air flow rate, m3/h
Pa = Air pressure befoe the nozzle, Pa
µ = Air nozzle exit for flow rate coefficient = 0.6- 0.8
Low pressure Air Atomizer
mmW
GD
aa
aa
8.18
2196 mmP
VA
a
aaa
5.Theorotuical size (radius) of the spread of atomized oil droplets, r
6.The approximate flame lengthis given by
Where, L = flame length in m,
Vair = air flow rate per unit of fuel, m3/Kg
dnoz = diameter of atomizer nozzle,m
Other Types,
1. K-type atomizer
2. R-type atomizer
3. RK-type low-pressure atomizer
4. TB-type low-pressure atomizer
Low pressure Air Atomizer
mm
Pr
a
300200
mdV
L nozair
60422
Cross sectional view :
b) Operating principles and Design Calculation:1.Radial velocity um,
Where,
Q = Oil flow rate,m3/sDdrop = Inner diameter of the rotary cup, mN = Rotary speed of cup, rpmV = kinetic viscosity of oil, m2/sθ = Slope of inner surface of the cup
Rotary cup Atomizer
3
122 sin66.0
cupm vD
NQu
• Substituting the value of um
1.Oil Film Thickness
Where, DL= Diameter of the cup mouth
VT = tangential velocity of the oil
a = radial distance from the cup mouth from the axis of the cup
Rotary cup Atomizer
mcup uhDQ .
31
22 sin
0484.0
nD
Qvh
21
22
22
42
aaD
V
uD
V
QS L
mL
T T
363.0. 81.0
19.014.167.081.0
LD
vQN
Critical condition to form a continuous oil film is
Where, ρ = oil Density
Q = critical oil flow rate
σ = surface tension( 2.5 Kg/m when ρ = 900 kg/m3
N = Revolution
v = Viscosity2.The tapering angle, θ,of the rotary cup:
To avoid larger droplet size, θ is selected to be larger than 35o
3.Effect of air nozzle position and the impact on the quality, valid for a >5 mm
Where , σ = Surface tension g/cm
ρa = air density, g/cm2
Mr = Weight ratio of air and oil
Vr = Velocity ratio of air and oil
VT = tangential velocity of oil, cm/s
cmVVV
Q
MaaD
Vd
rrTrLa
rs
5.0
235.125.025.0
21.05.04
15.0
065.01
59.0106
Rotary cup Atomizer
• Swirl air register:
Classification:
Turbo air Registers
Tangential moveable vane air registers
Axial movable impeller air registers
Fixed Tangential impeller air registers
Advection-Flow Air Register:
• Simple Design
• Small resistance and low NOx formation
Air Register
Air Register
Venturi-type advection- flow air register Without root air primary air passing through flame holder around atomizer.
With Root Air where primary air is premixed with the oil in the gun
Air Register
Good atomization and good air arrangement are primary Objectives
•Root air is necessary
•Early mixing should be Intense
Effect of position of the oil nozzle with respect to air register exit on mixing of air with fuel
• Size and location of Recirculation Zone should be appropriate
•Later stage Mixing should be intense Too
A good practical design of air register should have
•Root air
•Flame holder in center air to help stabilize the flame and increasing early mixing.
•Improvement adjustment of the secondary air and reduction in its swirl intensity.
Design of other types of Swirl Air Register
• Turbo Air Register
• Tangential Vane Air Register
• Axial Vane Air Register
Tangential Vane Air Register Axial movable Swirl type Air Register
Design of other types of Swirl Air Register
Design for Advection-Flow Air Register:
In venturi type air register, flow through the air register q,
Where, Q = Air flow rate through the register, m3/h
ξ = resistance coeffficient
Fin= Annular setion area at the inlet, m2
Fh = Section area of the throat, m2
P1-P2 = Pressure difference between inlet and throat
222
22211 hhh VVPVP
2
1
1
236003600
in
h
hhhh
F
F
PPFFVQ
11
12
fh
dw
w
d
DQ
Q
Design for Advection-Flow Air Register:
Where, Qw =outlet near tuyre
Q = Total flow
dfh = diameter of flame holder, m
Dd = diameter of duct where flame holder is located, m
22
111
1
D
d
w
r
Over all resistance coefficient,
Where, ξr = Resistance Coefficient at inlet of Advection flow air register
ξw = Resistance coefficient of the flame-holder
Design for Advection-Flow Air Register:
Resistance coefficient corresponding to the tuyere outlet is
Where, F = Calculating Section area, m2
F0 = Outlat area of tuyere, m2
2
22
2
0
111
1
F
F
D
dF
F O
w
rO
Design Principles of oil fired Boilers:
a)Combustion Volume:
To quantify residence time of fuel air in the furnace, Furnace volume heat release rate is used represented by
Where, B = fuel flow rate,kg/s
LHV = heating value, KJ/Kg wet
Vf = Furnace volume, m3
αx= excess air coefficient
Volume of gas,
Where, Tf = Average temperature of gas in furnace ,o k
Pf ,Patm = pressure of gas in furnace and in standard atmosphere.
)KW/m(. 3
fv V
LHVBq
KgNmLHV
V xfg /4186
08.01.1 3
)/(273
3 KgmP
PTVV
f
atnffgg
Effective Utilization volume,
Where, φeff = Volume effectiveness
Retention period of the fuel in the furnace,
Average temperature of the gas in the furnace,
Where, Tth = Theoritical Adiabatic flame temperature, o K
Tou= gas temperature at the furnace exit, o K
Where Tpre= preheat temperature of combustion, oC
Correlation of Pressure drop with volumetric Heat release:
feffeff VV
)(4186273
08.01.1s
PqT
V
BV
V
atmvxf
feff
g
feff
KTTT outhf 925.0
KTT prex
th
2737.03.0
2730
m
vqKP
Design Principles of oil fired Boilers:
Correlation of Pressure drop with volumetric Heat release:
ΔP = pressurte loss of the burner
K’ = Coefficient; value depends on arrangement of burner
m = empirical constant: value lies sin the range 0.9- 1.1
Furnace Cross sectional area:
Cross sectionbal area depends on the characteristics parameter known as Furnace grate heat release , qf
Where, B = Fuel flow rate, Kg/s
LHV = Lower heating value of fuel, KJ/Kg
Fs = Cross sectional area of furnace, m2
m
vqKP
2
sec
/.
mKWF
LHVBq f
Design Principles of oil fired Boilers:
Design Principles of oil fired Boilers:
Ratio of grate and the volumetric heat release rate gives the furnace height, h
Average Heat release rate for oil fired Boilers
Burner zone heat flux is also used at times for design. This index is defined by
furf
v
f HF
V
VLHVBFLHVB
q
q
sec
sec
.
.
2/.
mKWS
LHVBq
rb
Steam Capacity(t/h)
130 220 400 670-950 1000-1600
Qf( MW/m2) <4.0 4.07 - 4.77 4.19 - 5.23 5.23 - 6.16 <9.0
Arrangement of the burners
There are different burner arrangements:
Front wall, opposite wall, Tangential and Bottom Arrangements
•To avoid flame interference in swirl type burners a minimum distance is maintained between the burners.
•Clearance is provided to avoid impingement on the side and bottom of furnace
The minimum distance are
•The distance between center lines of adjacent Burners(2.5-3.0)d0
•The distance between the burner and the side walls (30-3.5) d0
•The distance between the burner and the furnace bottom 3.0 d0
where do is diameter of the mouth of the Burner.
Arrangement of the burners
Arrangement of Burners on the furnace wall of a 500MW Oil fired boiler, the direction of swirl in individual burner is shown by the arrow
Arrangement of the burners
A plot of total resistance coefficient of a mechanical atomizer against log(ARe), where A is the Characteristic nozzle co-efficient and Re is the Reynolds number on the Basis of the Groove:
1. Tangential groove atomizer
2. Tangential hole cylinder Atomizer
Thank you