course title: heat and combustion technology … ntnu course title: heat and combustion technology...
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Course title: Heat and Combustion Technology(Combustion and Emissions)
Course number: TEP 4170
Dr. Md. Nurun NabiSenior Postdoc ResearcherEnergy and Process Engineering DeptNTNU, NORWAY
Dr. Md. Nurun NabiProfessor
Mechanical Engineering DeptRUET, BANGLADESH
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Text books
Title Author ISBN
1. An Introduction to Combustion S R Turns 978-007-126072-52. IC Engine Fundamentals J B Heywood 0-07-100499-83. IC Engines V Ganesan 0-07-462122-X
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LECTURE CONTENT
Overview
Introduction to diesel and gasoline combustion
Pollutants from combustion
Quantification of emissions
Emissions from premixed combustion
Emissions from nonpremixed combustion
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PROCESS
Fuel is injected into compressed air Fuel evaporates and mixes with the hot air Auto-ignition with the rapid burning of the fuel-air (Premixed) This is followed by Diffusion burning
CHARACTERISTICS OF DIESEL COMBUSTION
Heterogeneous Turbulent Diffusion flame
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DIESEL COMBUSTION PROCESS
Sour
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eyw
ood
(p-5
04)
Diffusion
Premixed
1 & 2 A rich fuel mixture with no premixed oxygen produces a yellow sooty diffusion flame
3 & 4 Oxygen premixed flame produces no soot and the flame color is produced by molecular radical band emission.
Premixed flame is a flame in which the oxidizer mixes with the fuel before it reaches the flame front. This creates a thin flame front as all of the reactants are readily available.
Diffusion flame is a flame in which the oxidizer mixes with the fuel by diffusion. Flame speed is limited by the rate of diffusion. Diffusion flames tend to burn slower and to produce more soot than premixed flames. There may not be sufficient oxidizer for the reaction to go to completion.
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Sou
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Premixed and diffusion flames
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FUEL INJECTION
PURPOSES OF FUEL SPRAY
Atomization
Fuel distribution
Fuel-air mixing
TYPICAL INJECTOR
Currently high injection pressure to reduce emission
Single or multiple holes with very small hole diameter
Injection timing is set before TDC for best torque
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Lean A/F mixture
Rich A/F ratio
Spray plume from injector
Stoichiometric A/F
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EXAMPLE OF INJECTION PROCESS
(Cummins six-cylinder engine, rated at 160 kW, 2500 rpm)
Typical injection duration 22
Typical BSFC 220 g/kWh
Typical fuel deliver per cylinder per injection
- 0.078 gm (100 mm3)
Average fuel flow rate during injection
- 68 mm3/ms
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AUTO IGNITION PROCESS
PHYSICAL PROCESSES (Physical delay)
Droplet atomization
Evaporation
CHEMICAL PROCESSES (Chemical delay)
Chemical reaction
To reduce ignition cetane improver is added to diesel fuel
EHN (ethyl hexyl nitrate), DTBP (Di tertiary butyl peroxide)
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Diesel knockN
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TDC
Injection point
Normal combustion
Diesel knock
I. delay
Compression pressure
Cyl
inde
r pre
ssur
e
Crank angle degree
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Gasoline combustion
A/F mixture is compressed
Ignition occurs with a spark plug
Homogeneous combustion
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100 80 60 40 20 TDC 20 40 60 800
10
20
30C
ylin
der p
ress
ure
(bar
)
B
I II III
A
C
Crank angle (degree)
A Start of spark B Start of ignitionC Maximum pressureI Ignition lagII Flame propagationIII After burning
Stages of gasoline combustion
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Normal combustion Slight knock Heavy knock
CA
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Combustion Chamber
Crank Shaft
Piston
Connecting Rod
TDC
BDC
Gasket
VC
VS Stroke
Stroke
Bore
Crank Radius (crank throw)
Crank Radius
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Details of an engine
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TDCatpistonaboveVolumeBDCatpistonaboveVolume
cr
cVsVcV
cr
Bore
VS
TDC
BDC
Ve = k.Vs rc = compression ratioVc = clearance volumeVs = displacement or swept volume = d2l/4l = stroked = bore diameterVe = capacity of the enginek = number of cylinders
Stroke
Compression ratio and capacity of an engine
VC
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Power and mean effective pressure
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Torque and brake power
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b = (BP*100)/(mf * CV)b = (BP*100)/(vf * CV)i= (IP*100)/(mf * CV)i= (IP*100)/(vf * CV)
i : indicated thermal efficiency (%)b : brake thermal efficiency (%)m : mechanical efficiency (%)mf : fuel mass flow rate (kg/sec)v : volumetric efficiency (%)Vf : fuel volume flow rate (m3/sec)CV: calorific value of fuel CV is kJ/kg for mf in kg/secCV is kJ/m3 for vf in m3/sec
m = (BP*100)/IP = (Pb l a N k/) / (Pi l a N k/)
m = (BP*100)/IP = (Pb *100)/Pi
Efficiencies of an engine
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IPrateflowfuelisfc
BPrateflowfuelbsfc
Powerrateflowfuelsfc
sfc: specific fuel consumption (kg/kWh)bsfc: brake specific fuel consumption (kg/kWh)isfc: indicated specific fuel consumption (kg/kWh)
Specific fuel consumption
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Problem
During a trial (60 minutes) on a single cylinder oil engine having cylinder diameter 300 mm, stroke 450 mm and the working on the four stroke cycle. The following observations were made:
Total fuel used=9.6 liters; calorific value of fuel=45000 kJ/kg. Total number of revolutions=12624; indicated mean effective pressure (imep)=6.9 bar. Net load on the brake=1575N; diameter of the brake wheel drum=1.82 m; density of the fuel=0.8 g/cm3. Determine (i) indicated power; (ii) brake power; (iii) mechanical efficiency and (iv) BSFC
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LECTURE CONTENT
Overview
Introduction to diesel and gasoline combustion
Pollutants from combustion
Quantification of emissions
Emissions from premixed combustion
Emissions from nonpremixed combustion
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Overview
Control of pollutants is a major factor in the design of modern combustion systems.
PollutantsParticulate matter (PM) (soot, fly ash, aerosols, etc), SOx (SO2 and SO3 ), NOx (NO and NO2 , N2 O, unburnt hydrocarbons, CO and CO2
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Concern (International Treaty/US regulation
Combustion generated or related species
Local/regional air quality (national ambient air quality standards)
Criteria pollutants: particles (PM10)a, O3 , NO2 , SO2 , CO, lead
Air toxics/hazardous air pollutants(1990 clean air act amendments)
189 substances: selected aliphatic, aromatic hydrocarbons; selected halogenated hydrocarbons; various oxygenated organics; metals and other compounds
Greenhouse effect/global warming(Kyoto protocol, 1997)
CO2 , CH4 , N2 O, water vapor, tropospheric and stratospheric O3 , C (carbon soot), sulfatesb
Stratospheric O3 destruction(Montreal protocol, 1987)
CH4 , N2 O, CH3 Cl, CH3 Br, stratospheric H2 O, atmospheric O3
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bSulfates (SO2 /SO42-) act as anti-greenhouse gases.
Table 15.1 Combustion generated or related air pollution concerns
Overview
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Effect of pollutantsPrimary pollutants (emitted directly from sources) Secondary pollutants (formed via reactions with primary pollutants)
Effects- Reduced visibility; resulting from carbon based PM, sulfates, nitrates, organic compounds and NO2.
- Increased fog formation and precipitation; resulting from high SO2 that form H2 SO4
- Altered temperature and wind distributions- Acid rain (regional climate for HNO3 )
- Global climate (greenhouse gases: water vapor, CO2 , CH4 , O3 , CFCs, N2 O)
Harm to vegetation- SO2 , peroxyacetal nitrate (PAN), C2 H4 destroy chlorophyll and disrupt photosynthesis
NO2 + H2 O →
HNO2 + HNO3HNO2 →
HNO3 + 2NO + H2 O 4NO + 3O2 + 2H2 O →
4HNO3
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O(g)NO(g)Sunlight(g)2NO
NO2 (g) + O2 + hydrocarbons CH3 CO-OO-NO2 (g) (PAN) Sunlight
Effect of pollutants
Soiling and deterioration of materialsPM soils clothing, building, reducing aesthetic quality, acid and alkaline particle those containing sulfur corrode paint, electrical contacts and textiles.
Increase sickness and mortality- Aggravate pre-existing respiratory ailments- Carbon based particles contain adsorbed carcinogens- Effect of CO to health is well documented - Secondary pollutants (O3 , organic nitrates, oxygenated hydrocarbons, aerosol formed primary by the reaction of NO and different hydrocarbons) create photochemical smog in presence of sunlight.N2 (g) + O2 (g) = 2NO(g); 2NO(g) + O2 (g) = 2NO2 (g); O + O2 = O3 ; NO(g) + O3 (g) = NO2 (g) + O2 (g)
Stratosphere- Catalytic destruction of stratospheric ozone by NO+O3 = NO2 + O2 (Increased UV
radiation on the earth)
Photochemical smog is a mixture of pollutants which includes particulates, nitrogen oxides, ozone, peroxyacetyl nitrate (PAN), unreacted hydrocarbons, etc. The smog often has a brown haze due to the presence of nitrogen dioxide. It causes painful eyes.
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LECTURE CONTENT
Overview
Introduction to diesel and gasoline combustion
Pollutants from combustion
Quantification of emissions
Emissions from premixed combustion
Emissions from nonpremixed combustion
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Quantification of emissionsEmissions indices: Emission index for species i is the ratio of the mass of species i to the mass of fuel burned
MWFiMWx
2XCOXCOiX
iEI (15.2)
Xs = mole fractions; MW = molecular weightx = number of moles of carbon in a mole of fuel
mi = mass of species imF = mass of fuel
burntFmemittedim
iEI (15.1)
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Example 15.1
A SI engine is running on a dynamometer test stand and the following measurements of exhaust products are made: CO2 = 12.47%, CO = 0.12%, O2 = 2.3%, C6 H14 (equivalent) = 367 ppm, NO = 76 ppm. All concentrations are by volume on a dry basis. The engine is fuelled by isooctane. Determine the emission index of the unburned hydrocarbons expressed as equivalent hexane.
Solution: We know
MWF
MWix2XCOXCO
XiEIi
EIi = (367 *10-6)/(0.1247+0.0012) * (8*86)/(114)
EIC6H14 = 0.0176 kg/kg or 17.6 g/kg
MWF
MWix14H6XC2XCOXCO
XiEIi
Considering unburned hydrocarbons
EIC6H14 =(367 *10-6)/(0.1247+0.0012+6*367*10-6) * (8*86)/(114)
EIC6H14 = 0.0173 kg/kg or 17.3 g/kg (considering UBHC)
Xi = 367 ppm = 367 *10-6
XCO = 0.12% = 0.0012XCO2 = 12.47% = 0.1247x = 8MWi = C6H14 = 72+14=86 g/molFuel: C8H18
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Mass specific emissions are expressed as g/kWh
(15.11) (g/kWh)15.1) (from
outputpowerbrake pollutantofrateflowmass(MSE) emissionspecificMass
WiEIFm
i(MSE)
Quantification of emissions
EIi = mi emitted / mF burnt
(MJ/kg) combustion of heat fuel Δhc
(g/kg)indexemissioniEI(kW)outputpowerW
(kg/hr)ratemassfuelF.
m
(g/MJ)Δhc
iEIfuel in Energy
iEI
(15.12)
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Equivalence ratio () is the ratio of actual fuel air to the stoichiometric fuel air.
Excess air ratio or excess air factor () is the ratio of actual air fuel to the stoichiometric air fuel.
)2.Mand1.MeqsFrom(
)2.M(st)F/A(
mixture)F/A(
)1.M(st)A/F(
mixture)A/F(
1
=1=
stoichiometric mixture
1(1) rich mixture
1(1) lean mixture
Definition of equivalence ratio and excess air factor/ratio
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Quantification of emissions
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Quantification of emissionsNmix,dry = x+b+3.76a (A)Nmix,wet = x+b+3.76a+y/2 (B)
(B)/(A) we have Nmix,wet / Nmix,dry = (x+b+3.76a+y/2) / (x+b+3.76a)=1+y/2(x+b+3.76a) (C)From equation 15.3 (CxHy + aO2 + 3.76aN2 →
xCO2 + (y/2)H2 O + bO2 + 3.76aN2 )2a = 2x+y/2+2b (balancing O atoms)b = a-x-y/4
Putting the value of b in equation (C) we have,
Nmix,wet / Nmix,dry = 1 + y/2(4.76a-y/4) (15.5)
From equation 15.4b [Xi ,wet = Ni / (x + y/2 + b + 3.76a)]
XO2,wet = NO2 /(x+b+3.76a+y/2) = b/(x+b+3.76a+y/2) = (a-x-y/4)/(x+b+3.76a+y/2)
a = [x+ (1+XO2,wet )y/4] / (1-4.76XO2,wet ) (15.6a)Similarly,
a = [x+ (1-XO2,dry )y/4] / (1-4.76XO2,dry ) (15.6b)
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Quantification of emissions
Xi,dry = Ni / Nmix,dry (15.4a)Xi,wet = Ni / Nmix,wet (15.4b)
(15.4b) / (15.4a)
Xi,wet / Xi,dry = Nmix,dry /Nmix,wet
Xi,wet = Xi,dry Nmix,dry / Nmix,wet
Similarly, (15.7)
Xi,dry = Xi,wet Nmix,wet / Nmix,dry
Nmix,wet = x+y/2+b+3.76a (from 1) = x+y/2+(a-x-y/4)+3.76a = 4.76a + y/4
Nmix,wet = 4.76[x+(1+XO2,wet )y/4 / 1-4.76XO2,wet )] + y/4 (from 15.6a) (15.9a)
Similarly,
Nmix,dry = 4.76[x+ (1-XO2,dry )y/4 / 1-4.76XO2,dry )] - y/4 (from 15.6b) (15.9b)
(substituting the value of a)
(putting the value of b)
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In premixed combustion, fuel and oxidizer are mixed at the molecular level prior to ignition, that is the fuel and oxidizer are intimately mixed before they enter the combustion device. Reaction then takes place in a combustion zone that separates unburnt reactants and burnt combustion products. Combustion occurs as a flame front propagating into the unburnt reactants.
Concept of premixed combustion
Air + Fuel
Air
Fuel
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Emissions from premixed combustion
Figure: Nature of premixed emissions
NOx
HC
CO
S
Em
issi
ons
Rich Lean
(Sou
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SA
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per #
7501
20)
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Emissions from premixed combustion
The primary pollutants from premixed combustion are oxides of nitrogen, carbon monoxide, unburned and partially burned hydrocarbon and soot. Oxides of sulfur are very low or zero for premixed combustion.
There are a number of nitrogen oxides, but only three of these are of interest for combustion processes
Nitrogen monoxide or nitric oxide, NO
Nitrogen dioxide, NO2
Di-nitrogen oxide or nitrous oxide or laughing gas, N2 OThe first two, NO and NO2 are collectively referred to as NOx.
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(N.12)HNOOHN(N.11)2HNHNH
(N.10)CONHHNCO(N.9)HNCOOHCN
(N.8) NCN2NC (N.7)NHCN2NCH
2. N2 O mechanism is important for fuel lean (1), low temperature condition
mixture the in species the ofbody third otherany M
(N.6) NONOO2NO
(N.5) NHNOO2NH
(N.4) MO2NM2NO
Emissions from premixed combustion
Nitric oxide (NO) emission (Three mechanisms)
(N.3)HNOOHN(N.2)ONO2ON(N.1)NNO2NO
3k
2k
1k
1. Zeldovich mechanism (Thermal mechanism, Zeldovich)
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Emissions from premixed combustionNO formed from fuel N2 is less important for premixed combustion as most fuels used in premixed combustion has little or no N2 .
NO formation depends on (i) reaction time; (ii) gas temperature and (iii) oxygen in the mixture of products.
Figure Effect of excess oxygen on NOx emission
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Emissions from premixed combustion
From equations N.1, N.2 and N.3 we may write
But for quasi steady state of N atom the term d/dt[N] becomes zero. Eqs R.1 and R.2 becomes
)13.15(2NO2dNOd
1t k
)2.R(OHN2ON22NOdNd
)1.R(OHN2ON22NOdNOd
31t
31t
kkk
kkk
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Emissions from premixed combustionNOx reduction technique
Reducing peak temperature can reduce NOx. FGR (flue gas recirculation) or EGR (exhaust gas recirculation) can reduce peak temperature. FGR/EGR circulates a part of the exhaust gas to the combustion chamber
Effect of FGR/EGRincreases heat capacity of burnt gases
dilutes flue gas
i.e. reduces the peak temperature
Figure 15.3 Effect of EGR on NOx emissions
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Figure 15.4 Correlation of NO reduction with diluent heat capacity
Emissions from premixed combustionNOx reduction technique
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Emissions from premixed combustion
NOx reduction technique
Figure 15.4a Effect of injection timing on NOx emission(Source: SAE paper number 2005-01-3677)
Injection timing retardation: lower peak temperature lower NOx emission.
Figure 15.4a shows the effect of injection timing on NOx emission. Injection timing is retarded by 4. Base fuel is used as standard diesel fuel. The result is compared with PME (pongamia methyl ester, a biodiesel). 4
retarding injection timing with 100% PME shows lower NOx emission compared to that of diesel fuel.
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Emissions from premixed combustion
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Emissions from premixed combustion
Unburned hydrocarbons
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Emissions from premixed combustion
Figure 15.7 Schematic representation of unburned hydrocarbon emission mechanism
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Emissions from premixed combustion
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Premixed combustion emission control
Catalytic treatment
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Catalytic treatment of premixed emissions
Figure 15.8 Pellet bed type catalytic converter
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Catalytic treatment of premixed emissions
Figure 15.9 Monolith catalytic converter
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Conversion efficiency of a three-way catalyst
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Emissions from premixed combustion
Particulate matter (PM)
PM = DS (dry soot) + SOF (soluble organic fraction)
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In nonpremixed combustion, fuel and oxidizer enter the reaction zone in distinct streams. Examples of non- premixed combustion include methane combustion, pulverized coal furnaces.
Concept of nonpremixed combustion
FuelAir
Air
Fuel
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NOx emissions from nonpremixed combustion
Figure 15.2 NOx emission as functions of air-fuel and equivalence ratio for various spark timings
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Effect of FGR on NOx emission
Figure 15.14 Effect of FGR on NOx emission from staged fuel burners using ambient or preheated air
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Figure 15.15 Low NOx burner employing fuel staging (lean rich combustion)
Emissions from nonpremixed combustion
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Figure 15.19 illustrates the temperature dependence
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