Path to High Efficiency Gasoline Engine
SI HCCI PPC
Prof. Bengt Johansson
Division of Combustion Engines Department of Energy Sciences Lund University 1 Scania diesel engine running on gasoline
Group 3, 1300 [rpm] 60 !
55
50 FR47333CVX 45 FR47334CVX FR47336CVX 40
35
30 Gross Indicated Efficiency [%] Efficiency Indicated Gross
25
20 0 2 4 6 8 10 12 14 Gross IMEP [bar]
ηi=57% = Isfc =147 g/kWh (@43 MJ/kg heating value)
2 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 3 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 4 Efficiencies?
5 Energy flow in an IC engine
FuelMEP
Combustion efficiency QemisMEP
QhrMEP QhtMEP
Thermodynamic efficiency QlossMEP
QexhMEP Gross Indicated efficiency IMEPgross
Gas exchange efficiency PMEP
Net Indicated efficiency lMEPnet
Mechanical efficiency FMEP
Brake efficiency BMEP
= * * * η Brake η Combustion ηThermodynamic η GasExchange η Mechanical Thermodynamic efficiency Saab SVC variable compression ratio, VCR, HCCI, Rc=10:1-30:1; General Motors L850 “World engine”, HCCI, Rc=18:1, SI, Rc=18:1, SI, Rc=9.5:1 (std) Scania D12 Heavy duty diesel engine, HCCI, Rc=18:1; Fuel: US regular Gasoline
7 SAE2006-01-0205 All four efficiencies
8 Problem with HCCI: Too fast combustion
9 Phasing HCCI combustion late helps burn rate but
reduce ηC
10 Magnus Christensen Ph.D. thesis 2002 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 11 + Clean with 3-way Background + High efficiency Catalyst Combustion concepts - Emissions of NO and - Poor low & part load x soot efficiency
Spark Ignition (SI) Compression Ignition engine (Gasoline, (CI) engine (Diesel) Otto)
+ High efficiency Homogeneous Charge -Combustion control Compression Ignition + Ultra low NOx -Power density (HCCI)
Spark Assisted Partially premixed Compression Ignition combustion (PPC) (SACI) Diesel HCCI Gasoline HCCI + Injection controlled - Less emissions advantage Partially Premixed Combustion, PPC p y 6000 1200 CI HCCI PCCI 5000 PPC 1000
4000 800
3000 600 HC [ppm] NOx [ppm]
2000 400
1000 200
-180 -160 -140 -120 -100 -80 -60 -40 -20 SOI [ATDC] Def: region between truly homogeneous combustion, HCCI, and diffusion controlled combustion, diesel
13 PPC: Effect of EGR with diesel fuel
Load 8 bar IMEP Abs. Inlet Pressure 2.5 bar Engine Speed 1090 rpm Swirl Ratio 1.7 Compression Ratio 12.4:1 (Low)
Scania D12 single cylinder
14 DEER2005 1 2
3 4 Lund/Delphi/Volvo PPC Project Volvo D13 Multi-cylinder engine
NOx <0.3 g/kWh PM < 2 FSN using Swedish MK1 diesel fuel
Adapted from 16 SAE paper 2009-01-1127 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 17 PPC with low cetane diesel
Lic. Thesis by Henrik Nordgren 2005 and 18 presented at DEER2005 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 19 VOLVO D5 with Gasoline
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
150
Cyl Pressure [bar] Inj Signal [a.u.] RoHR [J/CAD]
100
Load & CA50 N 2000 [rpm] Noise Load IMEPg 13.38 [bar] 50 Pin 2.57 [bar] Tin 354 [K] EGR 39 [%] 0 lambda 1.75 [-] -8020 -60 -40 -20 0 20 40 CAD [TDC] Efficiencies & Emissions
! D60 project goal 60 40 0.46 % 58 35 56 30 54
52 25 4598 ppm 50 20
48 Emissions 13 ppm Efficiency [%] 91 % 15 46 10 44 Below 42 5 Detectable Level 40 0 Indicated Gross Thermal Combustion/2 NOx*100 [g/kWh] CO [g/kWh] HC [g/kWh] Soot [FSN]
dPmax 7.20 [bar/CAD] CA5 3.40 [TDC] ID -1.00 [CAD] CA50 11.35 [TDC] CA90-10 13.00 [CAD] 21 Burn rate and ηT
Optimum Thermodynamic efficiency
150
Cyl Pressure [bar] Inj Signal [a.u.] Low effective RoHR [J/CAD] High heat expansion 100 losses ratio
50
0 -80 -60 -40 -20 0 20 40 CAD [TDC]
Premixedness 22 Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 23 Experimental setup, Scania D12
Bosch Common Rail
Prailmax 1600 [bar] Orifices 8 [-] Orifice Diameter 0.18 [mm] Umbrella Angle 120 [deg]
Engine / Dyno Spec BMEPmax 15 [bar] Vd 1951 [cm3] Swirl ratio 2.9 [-]
Fuel: Gasoline or Ethanol
24 Two Test Series: High & Low Compression Ratio
rc: 14.3:1 rc: 17.1:1
Low Compression Ratio PPC High Compression Ratio PPC
25 Injection Strategy
It consists of two injections. The first Const. Load & CA50 one is placed @ -60 TDC to create a 1 homogeneous mixture while the second 0.8 around TDC. The stratification created 0.6
by the second injection triggers the [a.u.] combustion. The first injection must not 0.4 It must not react during the compression stroke, react during 0.2 this is achieved by using EGR. compression
0 -60 -50 -40 -30 -20 -10 0 10 CAD [TDC]
Fuel amount in the pilot is a function of: 1.rc 2.RON/MON 3.EGR 26 SAE 2009-01-0944 High Compression Ratio PPC
IMEP sweep @ 1300 [rpm] EGR ~ const throughout the sweep, 40-50 [%] λ~ const throughout the sweep, 1.5-1.6 [-] Tin = 308 [K]
Standard piston bowl, rc: 17:1
27 SAE 2009-01-2668 Running Conditions
2.5 350 2 60
Inlet Temperature 300 1.9 Exhaust Temperature 55 2.25 1.8 250 50 1.7 200 Inlet Pressure
2 [-] 1.6 45 [C]
Exhaust Pressure λ [bar]
150 EGR [%] 1.5 40 100 1.75 1.4 35 50 1.3
1.5 0 1.2 30 4 5 6 7 8 9 10 11 12 13 4 5 6 7 8 9 10 11 12 13 Gross IMEP [bar] Gross IMEP [bar]
28 Efficiencies
100
95
90
85
80 Combustion Efficiency 75 [%] Thermal Efficiency 70 Gas Exchange Efficiency Mechanical Efficiency 65
60
55
50 4 5 6 7 8 9 10 11 12 13 Gross IMEP [bar]
29 Efficiency
57%
60 Too much rate Too much heat transfer controlled combustion 55
50
45 [%]
Gross Ind. Efficiency 40 Net Ind. Efficiency Brake Efficiency
35
30 2 4 6 8 10 12 14 Gross IMEP [bar]
30 Emissions
0.5 5 Obsolete injection 0.45 Gross 4.5 Net system 0.4 Brake 4 EU VI Not well tuned EGR-λ 0.35 3.5 US 10 combination 0.3 3
0.25 2.5
NOx [g/kWh] 0.2 2 Smoke [FSN] Smoke 0.15 1.5
0.1 1
0.05 0.5
0 0 2 4 6 8 10 12 14 2 4 6 8 10 12 14 Gross IMEP [bar] Gross IMEP [bar]
5 18
4.5 16 Gross 4 Gross 14 Net 3.5 Net Brake Brake 12 EU VI 3 EU VI US 10 US 10 10 2.5 8
HC [g/kWh] 2 CO [g/kWh] 6 1.5
1 4
0.5 2
0 31 0 2 4 6 8 10 12 14 2 4 6 8 10 12 14 Gross IMEP [bar] Gross IMEP [bar] Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 32 Low Compression Ratio PPC
IMEP sweep @ 1300 [rpm] EGR ~ const throughout the sweep, 40-50 [%] λ~ const throughout the sweep, 1.5-1.6 [-] Tin = 308 [K]
Custom piston bowl, rc: 14.3:1
33 SAE 2010-01-0871 Efficiencies
100
95
90
85
80 Combustion Efficiency
[%] 75 Thermal Efficiency 70 Gas Exchange Efficiency Mechanical Efficiency 65
60
55
50 4 6 8 10 12 14 16 18 Gross IMEP [bar]
34 Emissions
0.6 2 1.8 λ Gross Better tuned EGR- 0.5 Net 1.6 combination Brake 1.4 0.4 EU VI US 10 1.2
0.3 1
NOx [g/kWh] 0.8 Smoke [FSN] Smoke 0.2 0.6
0.4 0.1 0.2
0 0 2 4 6 8 10 12 14 16 18 4 6 8 10 12 14 16 18 Gross IMEP [bar] Gross IMEP [bar]
1.5 10 Gross 9 Gross Net Net 1.2 Brake 8 Brake EU VI EU VI US 10 7 US 10 0.9 6
5
HC [g/kWh] 0.6 CO [g/kWh] 4
3
0.3 2
1
0 35 0 2 4 6 8 10 12 14 16 18 2 4 6 8 10 12 14 16 18 Gross IMEP [bar] Gross IMEP [bar] Emissions – different fuels
Ethanol 2.5 0.5 FR47330CVX 0.45 FR47331CVX Ethanol FR47333CVX FR47330CVX 0.4 FR47334CVX 2 FR47331CVX FR47335CVX FR47333CVX 0.35 FR47336CVX FR47334CVX 0.3 FR47338CVX 1.5 FR47335CVX FR47336CVX 0.25 FR47338CVX Soot [FSN]
NOx [g/kWh] 0.2 1
0.15
0.1 0.5
0.05
0 0 2 4 6 8 10 12 14 16 18 20 2 4 6 8 10 12 14 16 18 20 Gross IMEP [bar] Gross IMEP [bar]
12 10 Ethanol Ethanol FR47330CVX 9 FR47330CVX 10 FR47331CVX 8 FR47331CVX FR47333CVX FR47333CVX FR47334CVX 7 FR47334CVX 8 FR47335CVX FR47335CVX FR47336CVX 6 FR47336CVX 6 FR47338CVX 5 FR47338CVX
CO [g/kWh] HC [g/kWh] 4 4 3
2 2 1
0 36 0 2 4 6 8 10 12 14 16 18 20 2 4 6 8 10 12 14 16 18 20 Gross IMEP [bar] Gross IMEP [bar] Outline
• HCCI and fuel efficiency – 50% thermal efficiency • Partially premixed combustion, PPC – Background – Why gasoline is the best diesel engine fuel – 56% thermal efficiency in car size engine – 57% thermal efficiency in truck size engine – Why 55% thermal efficiency is better than 57% – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out 37 Experimental Apparatus, Scania D13
XPI Common Rail Orifices 8 [-] Orifice Diameter 0.19 [mm] Umbrella Angle 148 [deg]
Engine / Dyno Spec BMEPmax 25 [bar] Vd 2124 [cm3] Swirl ratio 2.095 [-]
38 Standard piston bowl, rc: 17.3:1 Efficiency
50% brake efficiency seems viable!!!
60
55
50
45 η brake η net 40 [%] η gross 35
30
25
20 5 10 15 20 25 30 Gross IMEP [bar]
39 Efficiency
50% brake efficiency maximization of all intermediate efficiencies
= ⋅ ⋅ ⋅ η Brake η Combustion ηThermodynamic η GasExchange η Mechanical
100
90 η combustion η gas exchange 80 η thermal η mechanical 70 [%]
60
50
40 5 10 15 40 20 25 30 Gross IMEP [bar] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 26 [bar] IMEPg: 20 [bar] IMEPg: 16 [bar] lambda: 1.32 [-] Abs Pin: 3.64 [bar] lambda: 1.37 [-] Abs Pin: 3.21 [bar] lambda: 1.36 [-] Abs Pin: 2.35 [bar] 250 EGR: 47.98 [%] Abs Pex: 4.01 [bar] 250 EGR: 53.22 [%] Abs Pex: 3.48 [bar] 250 EGR: 46.69 [%] Abs Pex: 2.88 [bar] CA50: 13.9 [TDC] Tin: 293 [K] CA50: 9.27 [TDC] Tin: 293 [K] CA50: 7.6 [TDC] Tin: 292 [K] COV: 0.56 [%] Tex: 673 [K] COV: 0.7 [%] Tex: 606 [K] COV: 0.58 [%] Tex: 623 [K] 200 200 200 eta comb: 99.89 [%] eta comb: 99.89 [%] eta comb: 99.82 [%] NOx: 0.264 [g/kWh] NOx: 0.201 [g/kWh] NOx: 0.281 [g/kWh] 150 HC: 0.091 [g/kW] 150 HC: 0.082 [g/kW] 150 HC: 0.1 [g/kW] CO: 0.31 [g/kW] CO: 0.31 [g/kW] CO: 0.63 [g/kW] RoHR/3 [J/CAD] RoHR/3 [J/CAD] RoHR/3 [J/CAD] Soot: 0.26 [FSN] Cylinder Pressure [bar] Soot: 0.21 [FSN] Soot: 0.31 [FSN] 100 100 Cylinder Pressure [bar] 100 Cylinder Pressure [bar] Injection Current [a.u.] Injection Current [a.u.] Injection Current [a.u.] 50 50 50
0 0 0 -60 -40 -20 0 20 40 60 -60 -40 -20 0 20 40 60 -60 -40 -20 0 20 40 60 CAD [TDC] CAD [TDC] CAD [TDC]
IMEPg: 11 [bar] IMEPg: 5 [bar] lambda: 1.48 [-] Abs Pin: 1.76 [bar] lambda: 1.57 [-] Abs Pin: 1.07 [bar] 250 EGR: 46.41 [%] Abs Pex: 2.73 [bar] 250 EGR: 42.66 [%] Abs Pex: 1.15 [bar] CA50: 6.82 [TDC] Tin: 291 [K] CA50: 9.71 [TDC] Tin: 308 [K] COV: 1.2 [%] Tex: 612 [K] COV: 2.2 [%] Tex: 521 [K] 200 200 eta comb: 99.4 [%] eta comb: 94.16 [%] NOx: 0.317 [g/kWh] RoHR/3 [J/CAD] NOx: 0.108 [g/kWh] RoHR/3 [J/CAD] 150 HC: 0.22 [g/kW] Cylinder Pressure [bar] 150 HC: 2.7 [g/kW] Injection Current [a.u.] Cylinder Pressure [bar] CO: 2.6 [g/kW] CO: 23 [g/kW] Injection Current [a.u.] Soot: 0.05 [FSN] Soot: 0.0033 [FSN] 100 100
50 50
0 0 -60 -40 -20 0 20 40 60 -60 -40 -20 0 20 40 60 CAD [TDC] CAD [TDC] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 5 [bar] lambda: 1.57 [-] Abs Pin: 1.07 [bar] 250 EGR: 42.66 [%] Abs Pex: 1.15 [bar] CA50: 9.71 [TDC] Tin: 308 [K] COV: 2.2 [%] Tex: 521 [K] 200 eta comb: 94.16 [%] NOx: 0.108 [g/kWh] RoHR/3 [J/CAD] 150 HC: 2.7 [g/kW] Cylinder Pressure [bar] CO: 23 [g/kW] Injection Current [a.u.] Soot: 0.0033 [FSN] 100
50
0 -60 -40 -20 0 20 40 60 CAD [TDC] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 11 [bar] lambda: 1.48 [-] Abs Pin: 1.76 [bar] 250 EGR: 46.41 [%] Abs Pex: 2.73 [bar] CA50: 6.82 [TDC] Tin: 291 [K] COV: 1.2 [%] Tex: 612 [K] 200 eta comb: 99.4 [%] NOx: 0.317 [g/kWh] RoHR/3 [J/CAD] 150 HC: 0.22 [g/kW] Cylinder Pressure [bar] CO: 2.6 [g/kW] Injection Current [a.u.] Soot: 0.05 [FSN] 100
50
0 -60 -40 -20 0 20 40 60 CAD [TDC] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 16 [bar] lambda: 1.36 [-] Abs Pin: 2.35 [bar] 250 EGR: 46.69 [%] Abs Pex: 2.88 [bar] CA50: 7.6 [TDC] Tin: 292 [K] COV: 0.58 [%] Tex: 623 [K] 200 eta comb: 99.82 [%] NOx: 0.281 [g/kWh] 150 HC: 0.1 [g/kW] CO: 0.63 [g/kW] Soot: 0.31 [FSN] RoHR/3 [J/CAD] 100 Cylinder Pressure [bar] Injection Current [a.u.] 50
0 -60 -40 -20 0 20 40 60 CAD [TDC] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 20 [bar] lambda: 1.37 [-] Abs Pin: 3.21 [bar] 250 EGR: 53.22 [%] Abs Pex: 3.48 [bar] CA50: 9.27 [TDC] Tin: 293 [K] COV: 0.7 [%] Tex: 606 [K] 200 eta comb: 99.89 [%] NOx: 0.201 [g/kWh] 150 HC: 0.082 [g/kW] CO: 0.31 [g/kW] Soot: 0.21 [FSN] RoHR/3 [J/CAD] 100 Cylinder Pressure [bar] Injection Current [a.u.]
50
0 -60 -40 -20 0 20 40 60 CAD [TDC] RoHR, Cylinder Pressure & Injection Signal
IMEPg: 26 [bar] lambda: 1.32 [-] Abs Pin: 3.64 [bar] 250 EGR: 47.98 [%] Abs Pex: 4.01 [bar] CA50: 13.9 [TDC] Tin: 293 [K] COV: 0.56 [%] Tex: 673 [K] 200 eta comb: 99.89 [%] NOx: 0.264 [g/kWh] 150 HC: 0.091 [g/kW] CO: 0.31 [g/kW] RoHR/3 [J/CAD] Soot: 0.26 [FSN] 100 Cylinder Pressure [bar] Injection Current [a.u.]
50
0 -60 -40 -20 0 20 40 60 CAD [TDC] Combustion Noise & Stability
10 5
9 HD Engine Treshold 4.5 8 4
7 3.5 HD Engine Treshold 6 3
5 2.5
4 2 COV of IMEP [%] 3 1.5
2 1
1 0.5
Relative Maximum Pressure Rise [bar/CAD] Rate Pressure Relative Maximum 0 0 0 5 10 15 20 25 30 0 5 10 15 20 25 30 Gross IMEP [bar] Gross IMEP [bar]
47 Emissions
0.6 0.5
Brake NOx 0.45 0.5 US10 0.4 EU VI 0.35 0.4 0.3
0.3 0.25
Soot [FSN] 0.2
Brake NOx [g/kWh] NOx Brake 0.2 0.15
0.1 0.1 0.05
0 0 0 5 10 15 20 25 30 5 10 15 20 25 30 Gross IMEP [bar] Gross IMEP [bar]
2 25
1.8 Brake HC Brake CO 1.6 US 10 20 US 10 EU VI EU VI 1.4
1.2 15
1
0.8 10
Brake HCBrake [g/kWh] 0.6 [g/kWh] CO Brake
0.4 5
0.2
0 48 0 0 5 10 15 20 25 30 0 5 10 15 20 25 30 Gross IMEP [bar] Gross IMEP [bar] Summary
49 Brake Efficiency
58 56 D12 High rc, G. 80/75 D12 Low rc, G. 69/66 54 D13 Standard, G. 69/66 52 50 48 46 44 Brake Efficiency [%] 42 40 38 36 0 5 10 15 20 25 30 Gross IMEP [bar]
Brake efficiency in the range of 48-50% seems to be viable between 12.5 and 26 bar gross IMEP. 50 D13 Running on Diesel & Gasoline
52 D13 Gasoline 50 D13 Diesel 48
46
44
42
40 Brake Efficiency [%]
38
36
34 5 10 15 20 25 30 Gross IMEP [bar] D13 Diesel was calibrated by Scania and the calibration was done to meet EU V legislation. Average improvement of 16.6% points @ high load!!! 51 Brake Emissions
0.6 4.5 D12 High rc 0.55 D12 High rc 4 D12 Low rc 0.5 D12 Low rc D13 Standard 3.5 0.45 D13 Standard EU VI 0.4 US 10 3 0.35 2.5 0.3 2 0.25 Soot [FSN] 0.2 1.5 0.15 Brake Specific NOx [g/kWh] SpecificNOx Brake 1 0.1 0.5 0.05 0 0 0 5 10 15 20 25 30 0 5 10 15 20 25 30 Gross IMEP [bar] Gross IMEP [bar]
4 35 D12 High rc D12 High rc 3.5 D12 Low rc 30 D12 Low rc D13 Standard D13 Standard 3 EU VI EU VI US 10 25 US 10 2.5 20 2 15 1.5 10 Brake SpecificHC Brake [g/kWh]
1 Specific[g/kWh] CO Brake
0.5 5
0 52 0 0 5 10 15 20 25 30 0 5 10 15 20 25 30 Gross IMEP [bar] Gross IMEP [bar] Engine combustion - direction
+ Clean with 3-way Catalyst + High efficiency - Poor low & part load - Emissions of NOx efficiency and soot
Compression 1900-1995 Spark Ignition (SI) Ignition (CI) engine engine (Gasoline, (Diesel) Otto)
Homogeneous + High Efficiency 1995-2005 Charge Compression + Ultralow NOx & soot Ignition (HCCI) - Combustion control - Power density 2005-2010 Diesel PPC + Injection controlled + High Efficiency - Efficiency at high load + Low NOx & soot 2010- Gasoline PPC 53 The End
Thank you
54 Path to High Efficiency Gasoline Engine
SI HCCI PPC
Prof. Bengt Johansson
Division of Combustion Engines Department of Energy Sciences Lund University 55 Outline
• Partially premixed combustion, PPC – Summary of • 56% thermal efficiency in car size engine • 57% thermal efficiency in truck size engine • Why 55% thermal efficiency is better than 57% – Fuel effects in Scania D12 engine – How to reach 26 bar IMEP with US10 NOx, PM, HC and CO engine out, Scania D13 – Fuel effects in Scania D13 engine
56 Fuel Matrix
RON MON C H/C O/C LHV [MJ/kg] A/F stoich Group 1 FR47335CVX 99.0 96.9 7.04 2.28 0.00 44.30 15.10 FR47332CVX 97.7 87.5 6.61 2.06 0.07 39.70 13.44 FR47337CVX 96.5 86.1 7.53 1.53 0.00 42.10 14.03 Group 2 FR47338CVX 88.6 79.5 7.21 1.88 0.00 43.50 14.53 FR47330CVX 87.1 80.5 7.20 1.92 0.00 43.50 14.60 FR47331CVX 92.9 84.7 6.90 1.99 0.03 41.60 14.02 Group 3 FR47336CVX 70.3 65.9 7.10 2.08 0.00 43.80 14.83 FR47334CVX 69.4 66.1 7.11 1.98 0.00 43.80 14.68 FR47333CVX 80.0 75.0 7.16 1.97 0.00 43.70 14.65 Group 4 PRF20 20 20 7.2 2.28 0 44.51 15.07 MK1 n.a. 20 16 1.87 0 43.15 14.9
57 Results
58 Tested Load Area
Stable operational load vs. fuel type
25
20
15
10 IMEP gross [bar] gross IMEP
5
0 20 30 40 50 60 70 80 90 100 RON [-]
59 NOx - ηcomb Trade – Off Solution
100
99
98 G. ON 99/97 G. ON 98/88 97 G. ON 97/86 96 G. ON 93/85 G. ON 89/80 95 G. ON 87/81 G. ON 80/75 94 G. ON 70/66 93 G. ON 69/66
Combustion Efficiency [%] Efficiency Combustion PRF20 92
91 HC/CO F/A EQUIVALENCE RATIO EQUIVALENCE F/A 90 0 0.2 0.4 0.6 0.8 1 TEMPERATURE NOx [g/kWh] Adiabatic Flame Temperature 2400 λ=1 λ=1.1 2200 λ=1.2 λ=1.3 λ=1.4 2000 λ=1.5 λ=1.6 λ 1800 =1.7 It is possible to achieve λ=1.8 λ=2 low NOx and still keep 1600 λ=2.5
Temperature [K] λ=3 λ=3.5 high combustion 1400 λ=4 efficiency in the whole 1200 load range! 60 1000 30 35 40 45 50 55 60 65 70 EGR Ratio [%] Efficiency & Emissions
0.05 60 G. ON 99/97 0.045 59 G. ON 98/88 G. ON 99/97 G. ON 97/86 0.04 G. ON 98/88 58 G. ON 93/85 G. ON 97/86 G. ON 89/80 0.035 G. ON 93/85 57 G. ON 87/81 G. ON 89/80 0.03 56 G. ON 80/75 G. ON 87/81 G. ON 70/66 0.025 G. ON 80/75 55 G. ON 69/66 G. ON 70/66 PRF20 0.02 G. ON 69/66 54 [g/kWh] Soot D. CN 52 0.015 53 PRF20 EU VI
Gross Indicated Efficiency [%] Efficiency Indicated Gross 0.01 52 US10 0.005 51 0 50 0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 1 0 0.2 0.4 0.6 0.8 1 Indicated NOx [g/kWh] NOx [g/kWh]
In certain operating range, some fuels are capable to comply EU VI & US10 legislations and still keep high efficiency without compromising the efficiency!
61 Soot Emissions
3
2.5 G. ON 99/97 G. ON 98/88 G. ON 97/86 2 G. ON 93/85 G. ON 89/80 G. ON 87/81 Diesel vs. Gasoline 1.5 G. ON 80/75 G. ON 70/66 Soot [FSN] G. ON 69/66 1 D. CN 52 PRF20 0.5
0 0 5 10 15 20 25 30 Gross IMEP [bar]
62 Higher Power Density
IMEPg: 20 & 25 [bar] 3
2.5
G. ON 99/97 2 G. ON 98/88 G. ON 97/86 G. ON 93/85 1.5 G. ON 89/80
Soot [FSN] G. ON 87/81 1 G. ON 80/75 G. ON 70/66 G. ON 69/66 0.5 D. CN 52 PRF20
0 1 1.1 1.2 1.3 1.4 1.5 λ [-] Low soot even @ λ 1.3 higher power density without producing smoke!
63 Acoustic Noise
G. ON 99/97 Motored Engine 15 G. ON 98/88 5 G. ON 97/86 Measured 4.5 13 G. ON 93/85 Normalized G. ON 89/80 G. ON 87/81 4 11 G. ON 80/75 G. ON 70/66 3.5 9 G. ON 69/66 D. CN 52 3 7 PRF20 Treshold 2.5 5 2
3 Rise [bar/CAD] Rate Pressure Max 1.5 Relative Max Pressure Rise [bar/CAD] Rate Pressure Relative Max 1 64 1 0 5 10 15 20 25 30 1 1.5 2 2.5 3 3.5 4 Gross IMEP [bar] abs Inlet Pressure [bar] Idle
65 Efficiencies & Emissions
G. ON 69/66 G. ON 69/66 50 100 0.4 50 Gross Indicated Efficiency [%] NOx 48 99 45 Thermal Efficiency [%] 0.35 Soot 46 98 Combustion Efficiency CO 40 0.3 44 97 HC 35
42 96 0.25 30
40 95 0.2 25 [%] [%]
38 94 0.15 20 CO / HC [g/kWh] 36 93 NOx / Soot [g/kWh] 15 0.1 34 92 10 0.05 32 91 5
30 90 0 0 3 4 5 6 7 8 9 10 3 4 5 6 7 8 9 10 Combustion Phasing [TDC] Combustion Phasing [TDC]
66 Viability of Low ON Gasolines for PPC?
67 Oil Refineries Production Layout
50%
50 < ON < 75 90 < ON < 99
20%
Octane Number of the gasoline streams span68 from 99 to 50 RON Gasolines with 70 RON are already produced!!! 30% Oil Refineries Perspectives
Oil refineries are a very stiff system and their kerosene, diesel and gasoline production can not be easily varied without major investments we need to build highly efficient vehicles with the available fuels… 69 High ON Gasolines in Scania D13
What to do with these 25 fuels?! Still to be used in SI 20 engines?!
15
10 IMEP gross [bar] gross IMEP
5
0 20 30 40 50 60 70 80 90 100 RON [-]
70 Page 70 Minimum Turbo Efficiency
71 Ideal burn rate?
Conditions: 1. CA50: 8 [ATDC]. 2. CA90-10: 15 [CAD]. 3. Engine geometry: custom Scania D13. 4. Inlet temperature: 303 [K]. 5. Reference temperature: 298 [K]. 6. Engine speed: 1250 [rpm]. 7. Differential pressure exhaust minus inlet: 0.25 [bar]. 8. Cylinder wall temperature: 450 [K]. 9. Heat transferred modeled with the Woschni equation and tuned to match the experimental results 10. The rate of heat release has been approximated with a Wiebe function. 11. EGR is added in order to have 1.35 as λ. If the inlet pressure was not enough to have λ without EGR higher than 1.35, EGR was set to zero. 12. The combustion efficiency was assumed to be 100%. 13. Lower heating value 43.8 MJ/kg, stoichiometric air fuel ratio 14.68.
72 Exhaust Loss
73 Heat transfer loss
74 The rest (useful work)
75 Boosting reduce heat losses
76 A-B-C of Fuel Consumption
A. Car size B. Engine size C. Engine efficiency in right operating conditions
77 Porsche 911 performance with 100+ mpg?
• Two persons • 100 liter of storage capacity
78 Porsche 911 data
M=1550 kg Cr=0.012 Av=1.96 m2 Cd=0.33
Vd=3.8 liter P=355 PS (hp) T=400 Nm Performance 0-60: 4.6 s V,max=300 km/h ( 186.5 mph) Fuel consump.= 12.0 l/100 km (19.6 mpg)
79 Power needed @300 km/h (186.5 mph)
2 P = (CRmg + 0.5ρaCD Avv )v = 2 300 300 + 0.012x1550x9.81 0.5x1.2x0.33x1.96x x 3.6 3.6 = 239.8kW = 326.1hp
80 The ”Cigar” Two person capacity is often enough
UK National Office of Statistics: “The average car occupancy is 1.6 people per car and for commuting it's 1.2 “
A carpool in California is a car with ONE person if the car is fuel efficient…
82 The ”Cigar” Existing large model use large BMW 1200 cc MC engine. With turbo a top speed of 315 km/h and fuel consumption of 3.5 l/100 km (67 mpg) http://www.peraves.ch/ Power needed @300 km/h (186.5 mph)
Cigar design specifications Cd=0.1 Av=0.5-1 m2 m= 250 kg Cr=0.012 (two wheels)
2 P = (CRmg + 0.5ρaCD Avv )v = 2 300 300 + 0.012x250x9.81 0.5x1.2x0.10x1.0x x 3.6 3.6 = 37.2kW = 49.7hp
84 Power needed at 50 and 100 km/h (31- 62 mph)
Porsche 911 vs. cigar Speed (km/h) 911 Cigar Unit Ratio 50 3.57 0.57 kW 6.28 100 13.4 2.1 kW 6.36 300 239.8 37.2 kW 6.45
50 4.86 0.77 hp 6.28 100 18.2 2.9 hp 6.36 300 326.1 49.7 hp 6.45
Acceleration proportional to power/mass ratio: Cigar: 250/49.7=5.03 kg/hp 911: 1550/355=4.37 kg/hp
85 A. Car size • With more correct car size the engine size can be reduced a factor of 6 i.e. single cylinder version of 911 engine with 633 cc displacement is enough • Porsche 911 has a fuel consumption of 12 l/100 km (19.6 mpg) • Cigar would have 12/6=2 l/100 km (117.6 mpg) without any need of new engine technology. (Scaling both engine and car size)
86 B. Engine size • A Porsche 911 does not operate at optimum load points in normal driving. • At 50 km/h the estimated load is only 2 bar BMEP or less • Bsfc=400 g/kWh
(ηb=21 %)
0 20 40 60 80 100 120 140 160 180 200 220 87 Bilhast. [km/h] Engine downsizing Three options 1. Turbo or supercharge a small engine 2. Cylinder deactivation of large engine 3. Variable displacement i.e. variable engine size
88 B.1. Mercedes CDI 250, 2.1 liter
Vd=2143 cc Torque= 500 Nm (369 lb-ft)
89 Two stage turbo
90 Engine downsizing- MB 250 CDI Displacement of 2.1 liter giving 224 hp and 500 Nm of torque : 30 bar BMEP is now full load NOT 10 or 20 bar Fuel consumption; CO2: C-class 5.1 l/100 km (46.1 mpg), C-class 139 g/km E-class 5.3 l/100 km (44.4 mpg), E-class 143 g/km S-class 5.9 l/100 km (39.9 mpg) S-class 155 g/km
91 B2: Dual engine concept
• Use one small and one large engine • As an example: – One 2 cylinder 1 liter engine – One 4 cylinder 2 liter engine • This gives us 1, 2 or 3 liter to choose from
92 Layout 4 +2 cyl Fiat 2-cylinder production engine
FAS
Transm.
93 Operation
• 2-cyl at low loads • 4-cyl operation at higher load operation (Autobahn) • 6-cyl operation at highest loads • 6-cyl + FAS at transients (with FAS start of 4-cyl) • FAS for regenerative braking • FAS for lowest speed operation ( < 5 km/h) • Manual selection should be possible
94 B3: Variable displacement engine
• If we can change displacement, Vd, engine load, P, can be controlled without reducing BMEP! N P = bmep Vd nt
Displacement from 0.15 to 0.85 l per cylinder gives 0.6 to 3.4 l four cylinder engine at full load (@max BMEP)
96 Atkinson engine with variable displacement
97 Atkinson engine efficiency
98 Atkinson engine thermal efficiency
99 A-B-C of Fuel Consumption
A. Car size B. Engine size C. Engine efficiency in right operating conditions (Maximum engine efficiency)
100 Summary /ABC of fuel consumption
A. Correct car size gives factor of 6 in fuel consumption B. Correct load point gives factor 2 in fuel consumption (21%-42% or 400-200 g/kWh) C. Partially Premixed Combustion have the potential to extend brake efficiency to 50% with US10/Euro emissions. With further optimization 55% could be reached D. With waste heat recovery 60% should be possible giving a factor of 3 from today.
A total reduction potential of factor 18!
101 Cars and traffic situation
102