low temperature combustion and diesel emission reduction ... · low temperature combustion and...
TRANSCRIPT
Low Temperature Combustion and Diesel Emission Reduction Research
by Rolf D Reitz Manuel A Gonzalez D
Dave Foster Jaal Ghandhi Chris Rutland and Scott Sanders Engine Research Center UW-Madison
August 24 2006
Acknowledgements DOE LTC Consortium project DE-FC26-06NT42628 Industry Partners
British Petroleum Caterpillar Diesel Emission Reduction Consortium (DERC) GM-ERC Collaborative Research Laboratory (CRL)
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel CombustionJanuary 2006 to December 2008
bull Overall goal mdash develop methods to further optimize and control LTC engines with emphasis on diesel-fueled engines
bull Engine technologies to be considered include operation on LTC-D with transition to conventional Compression Ignition Direct Injection (CIDI) combustion at higher loads and starting conditions (ldquomixed-moderdquo operation)
bull Approach ndash develop and apply high fidelity computing and high-resolution engine experiments synergistically to create and apply advanced tools needed for low emissions engine design
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion January 2006 to December 2008
12th DEER Conference August 24 2006
12th DEER Conference August 24 2006
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
32 Investigation ofoptimal spray
characteristics forHSDI LTC D combustion
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
Guidelines for LTC Dengine control
methodologies withconsideration of fuelproperty and mixturepreparation effects
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injectionand fuel effects onignition delay and
mixing in a High Speed DI LTC D engine
Assessment of therole of heat transfer
and wall fuel films onLTC D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
51 Multi cylinderHSDI engine control
strategies withmixed mode
combustion regimetransitions
41 Thermal analysisin LTC D engines using detailed CFD coupled
with 3 D metalcomponent heat
conduction
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injection51 Multi cylinder
HSDI engine controlstrategies with
41 Thermal analysisin LTC D engines using detailed CFD coupled
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray andcombustion chamber
designrecommendations forlow emissions LTC-D
engines
Guidelines for LTC-Dengine control
methodologies with consideration of fuelproperty and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC-D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
Research Approach
Research Objectives
Fundamentals Applications
E x p e r i m e n t a l
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
-
-
-
-
-
-
-
-
--
-
-
-Research Approach
Research Objectives
Fundamentals Applications
Experimental
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
32 Investigation of optimal spray
characteristics for HSDI LTC-D combustion
-
-
-
-
-Guidelines for LTC D engine control
methodologies with consideration of fuel property and mixture preparation effects
and fuel effects on ignition delay and
mixing in a High Speed DI LTC D engine
Assessment of the role of heat transfer
and wall fuel films on LTC D engine
combustion phasing and emissions
Demonstration of successful LTC D
engine system transient control algorithms and
strategies appropriate for mode transitions
mixed mode combustion regime
transitions
with 3 D metal component heat
conduction
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFD codes that can be
used for combustion system concept
evaluation
Optimum spray and combustion chamber
design recommendations for low emissions LTC-D
engines
Guidelines for LTC-D engine control
methodologies with consideration of fuel property and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration of successful LTC-D
engine system transient control algorithms and
strategies appropriate for mode transitions
-
-
--
-
-
-
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion - Issues
Ignition too fast
Enablers
Variable Geometry Sprays Fuel vaporization enhancement ndash FT fuels
Combustion phasing Compression ratio control Enablers Advanced controls Variable Valve Timing Two-stage turbo-charging CoolingEGR Two stage combustion Fuel CN reduction
Vaporization too slow
Charge preparation Prevent wall fuel - unburned drops
Advanced injection concepts Ultra-high injection pressure small holes Narrow angle spray ndash geometry Multiple pulse injections
Diesel LTC
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Optimizing Low Temperature Diesel CombustionJanuary 2006 to December 2008
bull Overall goal mdash develop methods to further optimize and control LTC engines with emphasis on diesel-fueled engines
bull Engine technologies to be considered include operation on LTC-D with transition to conventional Compression Ignition Direct Injection (CIDI) combustion at higher loads and starting conditions (ldquomixed-moderdquo operation)
bull Approach ndash develop and apply high fidelity computing and high-resolution engine experiments synergistically to create and apply advanced tools needed for low emissions engine design
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion January 2006 to December 2008
12th DEER Conference August 24 2006
12th DEER Conference August 24 2006
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
32 Investigation ofoptimal spray
characteristics forHSDI LTC D combustion
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
Guidelines for LTC Dengine control
methodologies withconsideration of fuelproperty and mixturepreparation effects
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injectionand fuel effects onignition delay and
mixing in a High Speed DI LTC D engine
Assessment of therole of heat transfer
and wall fuel films onLTC D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
51 Multi cylinderHSDI engine control
strategies withmixed mode
combustion regimetransitions
41 Thermal analysisin LTC D engines using detailed CFD coupled
with 3 D metalcomponent heat
conduction
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injection51 Multi cylinder
HSDI engine controlstrategies with
41 Thermal analysisin LTC D engines using detailed CFD coupled
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray andcombustion chamber
designrecommendations forlow emissions LTC-D
engines
Guidelines for LTC-Dengine control
methodologies with consideration of fuelproperty and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC-D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
Research Approach
Research Objectives
Fundamentals Applications
E x p e r i m e n t a l
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
-
-
-
-
-
-
-
-
--
-
-
-Research Approach
Research Objectives
Fundamentals Applications
Experimental
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
32 Investigation of optimal spray
characteristics for HSDI LTC-D combustion
-
-
-
-
-Guidelines for LTC D engine control
methodologies with consideration of fuel property and mixture preparation effects
and fuel effects on ignition delay and
mixing in a High Speed DI LTC D engine
Assessment of the role of heat transfer
and wall fuel films on LTC D engine
combustion phasing and emissions
Demonstration of successful LTC D
engine system transient control algorithms and
strategies appropriate for mode transitions
mixed mode combustion regime
transitions
with 3 D metal component heat
conduction
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFD codes that can be
used for combustion system concept
evaluation
Optimum spray and combustion chamber
design recommendations for low emissions LTC-D
engines
Guidelines for LTC-D engine control
methodologies with consideration of fuel property and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration of successful LTC-D
engine system transient control algorithms and
strategies appropriate for mode transitions
-
-
--
-
-
-
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion - Issues
Ignition too fast
Enablers
Variable Geometry Sprays Fuel vaporization enhancement ndash FT fuels
Combustion phasing Compression ratio control Enablers Advanced controls Variable Valve Timing Two-stage turbo-charging CoolingEGR Two stage combustion Fuel CN reduction
Vaporization too slow
Charge preparation Prevent wall fuel - unburned drops
Advanced injection concepts Ultra-high injection pressure small holes Narrow angle spray ndash geometry Multiple pulse injections
Diesel LTC
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Optimizing Low Temperature Diesel Combustion January 2006 to December 2008
12th DEER Conference August 24 2006
12th DEER Conference August 24 2006
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
32 Investigation ofoptimal spray
characteristics forHSDI LTC D combustion
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
Guidelines for LTC Dengine control
methodologies withconsideration of fuelproperty and mixturepreparation effects
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injectionand fuel effects onignition delay and
mixing in a High Speed DI LTC D engine
Assessment of therole of heat transfer
and wall fuel films onLTC D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
51 Multi cylinderHSDI engine control
strategies withmixed mode
combustion regimetransitions
41 Thermal analysisin LTC D engines using detailed CFD coupled
with 3 D metalcomponent heat
conduction
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injection51 Multi cylinder
HSDI engine controlstrategies with
41 Thermal analysisin LTC D engines using detailed CFD coupled
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray andcombustion chamber
designrecommendations forlow emissions LTC-D
engines
Guidelines for LTC-Dengine control
methodologies with consideration of fuelproperty and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC-D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
Research Approach
Research Objectives
Fundamentals Applications
E x p e r i m e n t a l
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
-
-
-
-
-
-
-
-
--
-
-
-Research Approach
Research Objectives
Fundamentals Applications
Experimental
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
32 Investigation of optimal spray
characteristics for HSDI LTC-D combustion
-
-
-
-
-Guidelines for LTC D engine control
methodologies with consideration of fuel property and mixture preparation effects
and fuel effects on ignition delay and
mixing in a High Speed DI LTC D engine
Assessment of the role of heat transfer
and wall fuel films on LTC D engine
combustion phasing and emissions
Demonstration of successful LTC D
engine system transient control algorithms and
strategies appropriate for mode transitions
mixed mode combustion regime
transitions
with 3 D metal component heat
conduction
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFD codes that can be
used for combustion system concept
evaluation
Optimum spray and combustion chamber
design recommendations for low emissions LTC-D
engines
Guidelines for LTC-D engine control
methodologies with consideration of fuel property and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration of successful LTC-D
engine system transient control algorithms and
strategies appropriate for mode transitions
-
-
--
-
-
-
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion - Issues
Ignition too fast
Enablers
Variable Geometry Sprays Fuel vaporization enhancement ndash FT fuels
Combustion phasing Compression ratio control Enablers Advanced controls Variable Valve Timing Two-stage turbo-charging CoolingEGR Two stage combustion Fuel CN reduction
Vaporization too slow
Charge preparation Prevent wall fuel - unburned drops
Advanced injection concepts Ultra-high injection pressure small holes Narrow angle spray ndash geometry Multiple pulse injections
Diesel LTC
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
12th DEER Conference August 24 2006
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
32 Investigation ofoptimal spray
characteristics forHSDI LTC D combustion
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
Guidelines for LTC Dengine control
methodologies withconsideration of fuelproperty and mixturepreparation effects
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injectionand fuel effects onignition delay and
mixing in a High Speed DI LTC D engine
Assessment of therole of heat transfer
and wall fuel films onLTC D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
51 Multi cylinderHSDI engine control
strategies withmixed mode
combustion regimetransitions
41 Thermal analysisin LTC D engines using detailed CFD coupled
with 3 D metalcomponent heat
conduction
Modeling
11b Experimentalverification
measurements ofspecies composition in an optical LTC D
engine
12b Fine scaleMixing
Measurements ofGas and Spray Jets
in Engines
11a LTC D and premixed
combustion models
12a Large eddysimulation
turbulence models
31 Optimization ofHD engine piston bowl
geometry using GACFD with detailed
chemistry andexperimental validation
33 Investigation ofimproved mixing
strategies using early injection and LES
42 Experimentalmeasurements of
piston temperatureand heat flux for
LTC D combustionanalysis
52 Engine systemanalysis and
optimization withmixed mode
combustion regimetransitions
Validated predictiveLTC D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray and combustion chamber
designrecommendations for low emissions LTC D
engines
21 Use of VariableValve Timing and
Variable GeometrySprays for mixing and
combustion control in aHeavy Duty LTC-D
engine
22 Exploring injection51 Multi cylinder
HSDI engine controlstrategies with
41 Thermal analysisin LTC D engines using detailed CFD coupled
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFDcodes that can be
used for combustionsystem concept
evaluation
Optimum spray andcombustion chamber
designrecommendations forlow emissions LTC-D
engines
Guidelines for LTC-Dengine control
methodologies with consideration of fuelproperty and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration ofsuccessful LTC-D
engine systemtransient controlalgorithms and
strategies appropriate for mode transitions
Research Approach
Research Objectives
Fundamentals Applications
E x p e r i m e n t a l
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
-
-
-
-
-
-
-
-
--
-
-
-Research Approach
Research Objectives
Fundamentals Applications
Experimental
Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
Deliverables
-
-
-
-
32 Investigation of optimal spray
characteristics for HSDI LTC-D combustion
-
-
-
-
-Guidelines for LTC D engine control
methodologies with consideration of fuel property and mixture preparation effects
and fuel effects on ignition delay and
mixing in a High Speed DI LTC D engine
Assessment of the role of heat transfer
and wall fuel films on LTC D engine
combustion phasing and emissions
Demonstration of successful LTC D
engine system transient control algorithms and
strategies appropriate for mode transitions
mixed mode combustion regime
transitions
with 3 D metal component heat
conduction
Validated predictive LTC-D combustion
and ignition submodels for use in
multidimensional CFD codes that can be
used for combustion system concept
evaluation
Optimum spray and combustion chamber
design recommendations for low emissions LTC-D
engines
Guidelines for LTC-D engine control
methodologies with consideration of fuel property and mixture preparation effects
Assessment of the role of heat transfer
and wall fuel films on LTC-D engine
combustion phasing and emissions
Demonstration of successful LTC-D
engine system transient control algorithms and
strategies appropriate for mode transitions
-
-
--
-
-
-
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion - Issues
Ignition too fast
Enablers
Variable Geometry Sprays Fuel vaporization enhancement ndash FT fuels
Combustion phasing Compression ratio control Enablers Advanced controls Variable Valve Timing Two-stage turbo-charging CoolingEGR Two stage combustion Fuel CN reduction
Vaporization too slow
Charge preparation Prevent wall fuel - unburned drops
Advanced injection concepts Ultra-high injection pressure small holes Narrow angle spray ndash geometry Multiple pulse injections
Diesel LTC
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
12th DEER Conference August 24 2006
Optimizing Low Temperature Diesel Combustion - Issues
Ignition too fast
Enablers
Variable Geometry Sprays Fuel vaporization enhancement ndash FT fuels
Combustion phasing Compression ratio control Enablers Advanced controls Variable Valve Timing Two-stage turbo-charging CoolingEGR Two stage combustion Fuel CN reduction
Vaporization too slow
Charge preparation Prevent wall fuel - unburned drops
Advanced injection concepts Ultra-high injection pressure small holes Narrow angle spray ndash geometry Multiple pulse injections
Diesel LTC
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Low Temperature Diesel Combustion EmissionsLow Temperature Diesel Combustion Emissions
New regimes
CO HC Soot and NOx
LTC-D design guidelines Assume homogeneous charge KIVA-CHEMKIN ERC n-heptane Park amp Reitz CST (Submitted)
Engine specifications - Bore x stroke 820 x 904 mm - Compression ratio 1601 - Displacement 477cm3
Calculation conditions- Fuel amount 200 mg- Engine speed 2000 rpm- EGR 0-70 - Tin 320-440K
12th DEER Conference August 24 2006
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
-300
-210
-270
-270
-12
0
-1165
-45
1 100 0
0 0
005 5
05
14550
2288
000 0
109000 0
16300
126
24
7 974
10
140
09
16300
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
20 20220 Soot LTC-D design guidelinesCOCOCO Soot(gkg-f) Assume homogeneous charge
55 48 KIVA-CHEMKIN ERC n-heptane41 34 Park amp Reitz CST (Submitted)26 19 12 Engine specifications 05 - Bore x stroke 820 x 904 mm
- Compression ratio 1601 (gkg-f)NONO(gkg-f) - Displacement 477cm3
17001700
55 EG55 E RGR15115515
qqui
qu
iui
vale
e
ratio
i i EE E E
quiv
alen
ce ra
tv
eva
lenc
rat
alen
cera
tnc
ioo o
10 10110 14581458 Calculation conditions - Fuel amount 200 mg
SOC12161216 97974 4(degATDC)73731 1 48489 9 - Engine speed 2000 rpm-3024247 7
NONO -605 - EGR 0-70005 -90 - Tin 320-440K
05005505 -120(gkg-f)COCO(gkg-f)CO(gkg-f)-1501900019000190016300016300-1801630136000136001360-210109000-2401090 0010900
82082008205505500 00-2705502802800 00-300280 00101000000 000 1600 1800 2000 22001400 1600 220014001400 1600 18001800 20002000 2200 240024002400 100
1400 1600 1800 2000 2200 2400 Peak cyl em erat re (K)Peakakcylinder temperater uatuuree(KKK)PPe cylinder tinder tempp r ( ))eak cylinder temperature (
EGR (Phi=06)70 60 50 40 30 20 10 0
EGR (Phi=08)70 60 50 40 30 20
EGR (Phi=10) 70 60 50 40 30 12th DEER Conference August 24 2006
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
15
18
7
77
8
5
509
5
14
0
Equ
ival
ence
ratio
09
12
8
9
7
1
0
8
2 9
4
26
7
1
1Equ
ival
ence
ratio
Peak cycle temperature (K)
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
2100 350
1800 φ=14
300
1500 250
CO (
gkg
-f)
1200 200
900 φ=10 150 NO
(gk
g-f)
CO=10 gkg-fuelNO=05 gkg-fuel
φ=06 φ=06 600 100
Low emission 18 window φ=10 300 50 75φ=14
0 0 1200 1500 1800 2100 15 2400 2700 3000
104
12
Total Heat 09Release (J) Pmax (MPa)
782 Combustion 645 177 Max Cyl 148 509 efficiency 373 06
Pressure221236 100
1400 1600 1800 2000 2200 1400 1600 1800 2000 2200
12th DEER Conference August 24 2006 Peak cycle temperature (K) Peak cycle temperature (K)
06
235 206
118 89 60
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
30
50
40
40 50
60
-8-8446 6-5-5338 8
--22331 1
00777 7
33885 5669
91 1 2 200000 0
--1177669 9
--1144662 2
--88446 6
--5533
8 8
Equ
ival
ence
ratio
Equ
ival
ence
ratio
on CA30
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
18181818
ldquoSweet IVC effect IVC -142o ATDCIVC -100o ATDCspotrdquo 15151515
Equ
ival
ence
ratio
Equ
ival
ence
ratio
12121212
-1154-1154SOCSOCSOCSOC(ATDC deg)(ATDC deg)(ATDC deg)(ATDC deg)
09090909 05ltΦlt095 696 292070 777
692692077077
-538-538 -53-5 838Low eLow missione mission06 window06 window -1154-1154
-1769-1769 0606-115-11 454-176-17 969-238-23 585-2385-2385
-3000-3000 -300-30 0001600 1800 2000 2200 24001600 1800 2000 2200 2400 1600 181600 00 20000 0 20 200 2200 40018 200 2 2400
Peak cycle temperature (K)Peak cycle temperature (K) PeakP cyc clc e te empem ere ata uru e (Ke )eak y l t p r t r (K)18 18
ldquoSweet CO Required CO
spotrdquo 15 EGR 15 IVC -142o ATDC
IVC -100o ATDC NO (gkg-f)
Equ
ival
ence
ratio
NO (gkg-f)
8894 12 6683
4472
09 CO (gkg-f)
Equ
ival
ence
ratio
8894 12 6683
4472 2261 050
09 50ltEGRlt60 CO (gkg-f) EGR () 17282NO EGR () 1728213845 NO1040906
6973 063536
100 1600 1800 2000 2200 2400
1600 1800 2000 2200 2400Peak cycle temperature (K) 12th DEER Conference August 24 2006Peak cycle temperature (K)
13845 10409
6973 3536
100
2261 050
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Task 1 Understanding of LTC-D amp advanced model development 11a LTC-D and premixed combustion models
Required boost
12th DEER Conference August 24 2006
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
0405
02
01
03
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
01000001
0200
0300
04000500
Peak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
PP
Pin (MPa)P
Impractical zone (PingtPout)Impra
Practical zone (PinltPout)Pract
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
11
2
3
45
eak cycle temperature (K)
Equ
ival
ence
ratio
1000 1500 2000 2500 3000
05
1
15
2
in (MPa)
ctical zone (PingtPout)
ical zone (PinltPout)
IVC -100o ATDC IVC -142o ATDC
Pin
IVC EVO
Pout
ldquoSweet spotrdquo
025ltPinlt03
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
12th DEER Conference August 24 2006
Engine
Caterpillar 3401 SCOTE (Single Cylinder Oil Test Engine) - single cylinder - direct injection - 4 valve
Bore x Stroke 1372 mm x 1651 mm
Compression Ratio 161 1
Displacement 244 liters Combustion
Chamber Quiescent
Piston Mexican Hat with Sharp Edge Crater
Injection System
Cat HEUI 300B
bull Multiple injections PCCI ndash Hardy bullIVA system ndash Nevin Gonzalez Sun bull VGS two injector system ndash Weninger Gonzalez
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
16
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Motored engine ndash GT-Power and KIVA
10 950
Pre
ssur
eTD
C [M
Pa]
8 920
6 890
4 ~70K 860 Mode2 Expt P Mode2 Simulation P
2 Mode5 Expt P 830 Mode5 Simulation P Mode2 Simulation T
0 Mode5 Simulation T 800-150 -130 -110 -90 -70
Mode5 valve lift curve
IVC143 IVC130 IVC115 IVC10012 IVC085
Val
ve li
ft [m
m] IVC070
8
IVC [Deg ATDC]-360 -310 -260 -210 -160 -110 -60 Mode2 821revmin no boost
CA [Deg ATDC] Mode5 1737revmin 184kPa boost
12th DEER Conference August 24 2006
Tem
pera
ture
TD
C [K
]
0
4
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Early injection ndash 0 EGR ndash light load - constant AF ratio
Pres
sure
(bar
)
140
120
100
80
60
40
20
0
-20
05
045
04
035
03
025
02
015
01
005
0
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 355 (30 Load) Air Flow (kgmin) 447 Intake Temperature (K) 305 SOI (CA-BTDC) 55 Φ 02 EGR Rate 0N
AH
RR
IVC (CA-ATDC) Intake Pressure (kPa) -143 1841 -130 1937 -115 2000 -100 2103 -85 2275 -70 2441
-25 -20 -15 -10 -5 0 5 10 15 20 25
CA-ATDC
IVC143 P IVC115 P IVC85 P IVC70 P IVC143 HR IVC115 HR IVC85 HR IVC70 HR
12th DEER Conference August 24 2006
Nevin R MS Thesis 2006
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Factor Value Speed (revmin) 1737 Fuel Flow (kghr) 30 (25 Load) EGR 40 SOI (CA-BTDC) 55 IVC Timings (CA-BTDC) 143 85 (Solenoid) Intake Temperature (K) 305
Task 2 Experimental investigation of LTC-D combustion control 21 Use of Variable Valve Timing and Variable Geometry Sprays
Low loadEarly Injection40 EGR
3
68
9
0
0005
001
0015
002
0025
0 02 04 06 08 1
NOx (gkW-hr) PM
(gk
W-h
r)
Case 3 (IVC143) Case 6 (IVC85) Case 8 (IVC85) Case 9 (IVC85) 2010-NTE
12th DEER Conference August 24 2006
Run 3 6 8 9 Intake Pressure (kPa) 18409 18409 1792637 1723689 Intake Flowrate (kgmin) 252 203 196 186 IVC (CA-ATDC) -143 -85 -85 -85 NOx (gkW-hr) 08323 03387 02516 02392 HC (gkW-hr) 0932 14232 17734 16085 PM (gkW-hr) 00103 00206 00201 0018 CO (gkW-hr) 323173 278242 265183 23051 BSFC (gkW-hr) 42919 49267 49191 43114 Equivalence Ratio Φ 0265 02886 0298 03391
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Summary and Conclusions
Task 1 Fundamental understanding of LTC-D and advanced model development
11 Formulation of combustion models and reaction mechanisms 11a LTC-D and premixed combustion models ndash Reitz Idealized HCCI emission characteristics reveal a low emission window
(lower than 10 gkg-f CO 05 gkg-g NO and almost soot-less) ldquoSweet spotrdquo operation IVC=100o ATDC- 06ltΦlt095 50ltEGRlt60 025ltPinlt03
11b Experimental verification measurements of species composition in an optical LTC-D engine ndash Sanders
Fiber-optic access to metal engine tested successfully Acquired temperature H2O mole fraction histories for 17 engine operating conditions
12 Formulation of turbulence and mixing models for LTC-D 12a Large Eddy Simulation Models for Mixing in Engine Applications ndash Rutland LES explains cyclic variability due to intake flow and fuel vaporization unsteadiness
12b Fine-scale Mixing Measurements of Gas and Spray Jets in Engines ndash Ghandhi Optical system designed to achieve high resolution scalar dissipation rate
12th DEER Conference August 24 2006
measurements
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Summary and Conclusions
Task 2 Experimental investigation of LTC-D combustion control concepts 21 Use of Variable Valve Timing and Variable Geometry Sprays for mixing and combustion
control in a Heavy Duty LTC-D engine ndash Reitz Successful implementation of VVA system ndash combustion phasing control (~ 10 CA deg) Two injector variable geometry spray concept ready for testing
22 Exploring injection and fuel effects on mixing and combustion regimes in a High Speed DI LTC-D engine ndash Foster New single cylinder Diesel HCCILTC laboratory commissioned Initiated exploration of LTC conditions with high EGR rate (gt 55) Demonstrated emissions results consistent with expected trends
12th DEER Conference August 24 2006
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Summary and Conclusions
Task 3 Application of detailed models for Optimization of LTC-D combustion and emissions
31 Optimization of HD engine piston bowl geometry using GA-CFD with detailed chemistry and experimental validation ndash Reitz High load bowl geometry optimization in progress
32 Investigation of optimal spray characteristics for HSDI LTC-D combustion ndash Reitz
Low and high injection pressure sprays and multi-holenozzle arrangements are being explored for optimal chargepreparationMethodology established for evaluating spray configurations
33 Investigation of improved mixing strategies using early injection and LES ndash Rutland CHEMKIN speed up technique DOLFA implemented into KIVA-3V ERC and applied to achieve a 3~4 X speed up in full engine combustion simulationsGrid sensitivity study performed using LES
12th DEER Conference August 24 2006
LES resolves finer geometric details in engine than RANS with increased resolution
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Summary and Conclusions
Task 4 Impact of heat transfer and spray impingement on LTC-D combustion
41 Thermal analysis of LTC-D engines using detailed CFD coupled with 3-D metal component heat conduction ndash Reitz Wall heat transfer under LTC conditions being studied Effect of wall impingement model on film formation is being assessed for low and high pressure sprays with early injection
42 Experimental measurements of piston temperature and heat flux for LTC-D combustion
12th DEER Conference August 24 2006
analysis ndash Ghandhi A linkage system is being designed to acquired piston temperature and heat flux daa in Caterpillar SCOTE
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
Summary and Conclusions
Task 5 Transient engine control with mixed-mode combustion 51 Multi-cylinder HSDI engine control strategies with mixed-mode combustion regime
transitions ndash Foster Transient engine test cell has been installed with19L Common Rail Direct Injection HSDI diesel engine close coupled DOC and a DOC-DPF exhaust aftertreatment system Low inertia dynamometer system with a bandwidth of 20 HzDynamometer control and data acquisition system Fast NOx and HC analyzers response time (lt 4ms) Heated emission bench Smoke meter Combustion noise
52 Engine system analysis and optimization with mixed-mode combustion regime transitions - Rutland Engine system level simulation tool enhanced by validating emission models with experimental data from LTC-Diesel engineEffect of different actuators on emissions evaluated during transientsGT-Power model of 19L four-cylinder HSDI turbocharged engine replicating experimental facility of Task 51 has been built
12th DEER Conference August 24 2006
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-
------------------------------------------------------------------------
Acknowledgements
DOE LTC Consortium project DE-FC26-06NT42628 British Petroleum Caterpillar Inc DOE Sandia Labs General Motors CRL Diesel Emissions Reduction Consortium (DERC) 24 member companies
AVL Powertrain BorgWarner Caterpillar CD-Adapco Corning Cummins Delphi Corporation Detroit Diesel Donaldson Co FEV Engine Tech Fleetguard Fluent Ford Motor Co General Motors Hyundai Motor Co ITEC John Deere MotoTron Nippon Soken Nissan Paccar Thomas Magnete USA Toyota Tech Center Volvo Powertrain
ERC Students Staff and Faculty
12th DEER Conference August 24 2006
- Low Temperature Combustion and Diesel Emission Reduction Research
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion
- Optimizing Low Temperature Diesel Combustion (LTC-D) Sub-tasks linkages
- Optimizing Low Temperature Diesel Combustion - Issues
- Low Temperature Diesel Combustion Emissions
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 1 Understanding of LTC-D amp advanced model development
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Task 2 Experimental investigation of LTC-D combustion control
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Summary and Conclusions
- Acknowledgements
-