Spark Assisted Compression Ignition (SACI) - OSTI.GOV
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Transcript of Spark Assisted Compression Ignition (SACI) - OSTI.GOV
HCCI collaborative taskMONDAY, September 21, 2009
07:00-08:40 Breakfast
08:40 Opening remarks
08: 50 RPC for high fuel efficiency engine operation, Bengt Johansson, Lund University, Sweden
09:10 Research into the fuel properties for HCCI, Hongming Xu, University of Birmingham, UK
09:30 Dual fueled HCCI operation with DM E/LPG/gasoline/hydrogen, Choongsik Bae, Korea Advanced Institute ofU1ro Science and Technology (KAIST), Korea
09:50i—o Effect of cetane number on HCCI combustion efficiency and emissions, Vahid Hosseini, W Stuart Neill,
e>-M Hongsheng Guo, Wallace L. Chip pi or, National Research Council Canada, Craig Fa irb ridge, Natural ResourcesfU&-o
Canada, and Ken Mitchell, Shell Canada Limited, Canada
10:10-Om Utilization of HCCI concept - behavior of autoignition of end gas without knock in an engine, Eiji Tomita and
*5 Nobuyuki Kawahara, Okayama University, Japan
10:30-10:50L>t/tQ>
LL
Break
10:50 Active fuel design and management for homogeneous charge compression ignition (HCCI), Huang Zhen,
u Shanghai Jiao Tong University, China
11:10ui Preliminary results on HCCI implementation with high cetane number fuel, Martti Larmi, Helsinki University
of Technology, Finland
11:30 Study of advanced combustion mechanisms for clean engines at Istituto Motori, Felice E. Corcione, Istituto
Motori CNR, Italy
Partially Premixed Combustion, PPC, for high fuel efficiency engine
operation
Prof. Bengt Johansson
Division of Combustion Engines Department of Energy Sciences
Lund University
Path to high efficiency gasoline engineSI HCCI RFC
Prof. Bengt JohanssonDivision of Combustion Engines Department of Energy Sciences
Lund University
Path to high efficiency gasoline engine
• Lean HCCI in three engines, 0.3-2 l/cyl- 50-54% thermal efficiency
• PRC in Volvo Cars diesel engine, 0.51/cyl- 56% thermal efficiency, 51% indicated
• PRC in Scania, 2 l/cyl, 17:1- 57% indicated efficiency
• PPC in Scania 2 l/cyl, 14.3:1- 55% indicated efficiency with high
5
Energy flow in an IC engineFuelMEP
Combustion efficiency)-----► QemisMEP
QhrMEPQhtMEP
QlossMEPThermodynamic efficiency,
QexhMEP^Gross Indicated efficienc^) IMEPgross
(^Gas exchange efficiency PMEP Pump MEP
Net Indicated efficiency^ IMEPnet
Mechanical efficiency^ FMEP
Brake efficiency BMEP
Brake Combustion Thermodynamic GasExchange Mechanical
Three test engines; five cases:
5 cyl of 0.32 I 4 cyl of 0.5 I 6 cyl of 1.95 I
• Saab SVC variable compression ratio, VCR,1. HCCI, Rc= 10:1-30:1;
• General Motors L850 "World engine"2. HCCI, Rc=18:l3. SI, Rc=18:l4. SI, Rc=9.5:l (std)
• Scania D12 Heavy duty diesel engine,5. HCCI, Rc=18:l;
Ther
mod
ynam
ic E
ffici
ency
[-]
0.55
0.50
0.45
0.40
0.35
0.30
0.25-
Thermodynamic efficiencySaab SVC variable compression ratio, VCR, HCCI, Rc=10:1-30:1;General Motors L850 "World engine", HCCI, Rc=18:l, SI, Rc=18:l, SI, Rc=9.5:l (std)Scania D12 Heavy duty diesel engine, HCCI, Rc=18:l;
Fuel: US regular Gasoline
SAE2006-01-0205
2 4BMEP [bar]
Gas
Exc
hang
e Ef
ficie
ncy [
-] C
ombu
stio
n Effi
cien
cy [-
]
-2
All four efficiencies
2 4BMEP [bar]
0.6
= 0.5
| 0.4 bHI•§ 0.3COf 0.2i0)jE 0.1
0.0-2
L850 HCCI VCR HCCI L850 high CR SI L850 SI standard ScaniaD12 HCCI
2 4BMEP [bar]
-2 0 2 4 6 8BMEP [bar]
11
S'c0)obLU
sc03-50)
1.0
0.9
0.8
0.7
0.6
0.5
0.4-2 0 2 4 6 8
BMEP [bar]
Partially P remixed Combustion
-180 -160 -140 -120 -100 -80 -60 -40 -20SOI [ATDC]
Def: region between truly homogeneous combustion, HCCI and diffusion controlled combustion, dieselTrade-off between NOx and HC, soot typicalCombustion process not well known Soot a key feature
12
Effect of EGR with diesel fuelLoad 8 bar IMEP
Abs. Inlet Pressure 2.5 bar
Engine Speed 1090 rpm
Swirl Ratio 1.7
Compression Ratio 12.4:1 (Low)
DEER2005
RoH
r [J/
CAD
], C
yl pr
ess
[bar
] Nee
dle L
ift [A
U] RoH
r [J/
CAD
], C
yl pr
ess [
bar].
Nee
dle
Lift
[AU
] 1350
300
250
200
150
100
50
soot = 0.13FSN HC = 66ppm NOx = 142npm CO = 0.00% CombEff = 99.8% IMEPn = 8,6bar EGR = 40% lambda = 2.5 pin I - 2.5bar Tinl = 2S4X speed = 1090rpm CR = 12.4 CA50 = 7.7<ATDC
0--40
Cyl pres [bar] RoHr [J/CAD] Needle Lift [AU]
-20
350
300
250
200
150
100
50
-40 -20 0CAD
20 40 RoH
r [J/
CAD
], C
yl pr
ess [
bar] N
eedl
e Li
ft [A
U] RoH
r [J/
CAD
], C
yl pr
ess [
bar] N
eedl
e Li
ft [A
U] 2
350
300
250
200
150
100
50
0-40 -20 0 20 40
CAD
soot = 3 2FSN HC = 220ppm NOx = 5.6ppm CO = 0.30% CombEff = 98.2% IMEPn = 3,2bar EGR = 68% lambda = 1.35 pinl - 2.5bar Tinl = 36,0*C speed = 1090rpm CR = 12.4 CA50 = T.O'ATDC
Cyl pres [bar]----- RoHr [J/CAD]----- Needle Lift [AU]
350 soot = 0.12FSN 4 - Cyl pres [bar]HC =1472ppm -—- RoHr [J/CAD]
300 NOx = 1,1ppmCO = 2.4%
---- Needle Lift [AU]
250CombEff = 88.2%IMEPn = 7.6bar -
200EGR = 75%lambda = 1.07 Apinl = 2.5bar / \Tinl = 34.3X '
150 speed = 1090rpm /CR = 12.4 /
100 CA50 = 7.5°ATDC /—
50
0-40 -20 20 400
CAD
PPC with low cetane diesel„ Nozzle 8x0.18x120, SOI -33 ATDC, 1200 rpm, CR-pres 1500 bar | 280
_0~o00
Q<O
!QonXo
CH
co.Q
(/)0
>O
260240220200180160140120100
80604020
0
EGR = 52 %
IMERn = 15.6 bar
CA50 = 6.9 CAD
COV = 2.0
CombEffEm = 97:1 %
NOx = 8 ppm
247 ppm
0.7 %
I I I I ICyl pres [bar]
...... RoHR/5 [J/CAD]NeedleLift [AU]
....i Pinl = 2.42 bari*ii Pexh = 2.46 i bar
...... ii■i Tinl = 22 °C
= 1.05iii Texh = 377 °C
vVsAA/ViaAayV K yy:yfy wV*/vy-60 -50 -40 -30 -20 -10 0 10 20 30 40 50 60
CADLie. Thesis by Henrik Nordgren 2005 and presented at DEER2005 YtLXliUi
N 2000 [rpm]
IMEPg 13.38 [bar]
Pin 2.57 [bar]
Tin 354 [K]
EGR 39 [%]
lambda 1.75 [-]
Injection SOI [TDC] Fuel MEP [bar] Percentage [%]
1 -64.00 10.88 41.28
2 -29.20 7.74 29.36
3 0.80 7.74 29.36
-40 -20CAD [TOO]
Efficiencies & EmissionsI
dPmax 7.20 [bar/CAD]
CAS 3.40 [TDC]
ID -1.00 [CAD]
CA50 11.35 [TDC]
CA90-10 13.00 [CAD]
Experimental setup, Scania D12Bosch Common RailPrailmax 1600 [bar]
Orifices 8 [-]
Orifice Diameter [mm]
Umbrella Angle ( 120 Fe9]X ---------- - /
Engine / Dyno SpecBMEPmax 15 [bar]
Vd 1951 [cm3]
Swirl ratio 2.9 [-]
Injection StrategyIt consists of two injections. The first one is placed @ -60 TDC to create a homogeneous mixture while the second around TDC. The stratification created by the second injection triggers the combustion.The first injection must not react during the compression stroke, this is achieved by using EGR.
Const. Load & CA50
It must not react during compression
CAD [TDC]
Fuel amount in the pilot is a function of:1. Rc2. RON/MON3. EGR
20
Running Conditions
Gross IMEP [bar]
Inlet Temperature Exhaust Temperature
2.25
O Inlet Pressure □ Exhaust Pressure
Gross IMEP [bar]
Efficiencies
\xBMEP
100
95
90
85
80
75
70
65
60
55
50
O Combustion Efficiency □ Thermal Efficiency
4 5 6 7 8 9 10 11 12 1vGross IMEP [bar]
22
Efficiencies
Emission MEPQhr MEP
Heat Transfer MEP
Exhaust MEP
O Gross Ind. Efficiency □ Net Ind. Efficiency
—|— Brake EfficiencyPump MEP
Friction MEP
Gross IMEP [bar]BMEP
23
Emissions
O Gross-B-Net—X— Brake
2 0.2
z 0.15
Gross IMER [bar]
O Gross-B-Net—X— Brake
Gross IMEP [bar]
HC
[g/k
Wh]
Sm
oke
[FS
N]
Gross IMEP [bar]
O Gross-B- Net—X— Brake
Gross IMEP [bar]
Efficiencies
# Combustion Efficiency Thermal Efficiency
X Gas Exchange Efficiency _____ Mechanical Efficiency
Pump MEP
Gross IMEP [bar]
NO
x [g
/kW
h]Emissions
—X— Gross -©- Net —X— Brake
Gross IMFP Fbarl
04 10
Gross IMEP12[bar]
6 8 14 16 18
Gross IMFP Fharl
Summary:Path to high efficiency gasoline engine
• Lean HCCI in three engines, 0.3-2 l/cyl- 50-54% thermal efficiency
• PRC in Volvo Cars diesel engine, 0.51/cyl- 56% thermal efficiency, 51% indicated
• PRC in Scania, 2 l/cyl, 17:1- 57% indicated efficiency
• PRC in Scania 2 l/cyl, 14.3:1- 55% indicated efficiency with high
29