low temperature combustion and diesel emission reduction ... · low temperature combustion and...

20
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) 12 th DEER Conference August 24, 2006

Upload: buikien

Post on 21-Jul-2018

219 views

Category:

Documents


0 download

TRANSCRIPT

Page 1: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 2: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 3: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 4: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 5: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 6: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 7: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

-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
Page 8: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 9: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 10: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 11: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 12: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 13: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 14: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 15: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 16: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 17: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 18: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 19: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

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
Page 20: Low Temperature Combustion and Diesel Emission Reduction ... · Low Temperature Combustion and Diesel Emission Reduction Research by ... 3.1. Optimization of HD engine piston bowl

------------------------------------------------------------------------

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