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Fuel Chemistry and Emissions Research
Fuel Chemistry and Emissions Research
W. Stuart Neill
Canadian Petroleum Products Institute March 3, 2010
Outline
• ICPET’s Oil Sands Program
• Clean combustion research
• Engine research facilities
• Experimental results
– Conventional diesel combustion of biodiesel blends
– HCCI combustion of oil sands and CRC FACE fuels
• Summary
• Future Work
• Final Remarks
Oil Sands Program
(Lead- Thom McCracken)
From resource production and processing … to end-use
Oil Sands Processing
Bitumen Production Upgrading
Blending & Pipelining
Clean Transportation Fuels Refining
Sustainability for Canadian Oil Sands
International
Competitiveness
(detailed emissions data available in Jacobs and TIAX
Goal Process change Fuels & technology for clean combustion
Research Areas
•
Oil sands chemistry and processing
– Luba Kotlyar, Patrick Mercier, Deepak Kirpalani
– John Woods, Floyd Toll, Judy Kung, Bussaraporn Patarachao, Indu Gedara
– Adam Donaldson & Adam Goodmurphy (U of O), Tetsuya Naito & Koichi Haneda (Nagoya U) – Shahrzad Hashimi (RA)
– Om Patange and Aakash Ravi (students) – Bryan D. Sparks (Project Consultant)
•
Fuel chemistry for clean combustion
– Stuart Neill, Hongsheng Guo
– Vahid Hosseini, Cosmin Dumitrescu (RA)
– Wally Chippior, Roland Vaivads, Simon Lafrance – Ronak Choudhary (student)
•
Carbon Capture & Sequestration (CCS) chemistry
(new area)Fundamental understanding for improvement to commercial operations
Oil Sands Processing
Upper Rag Layer
Clear Water
Lower Rag Layer Samples from pilot and
commercial operations
Lab sample preparation
1000 1400 1800 2200 2600 3000 Temperature (K) 0 1 2 3 4 5 6 Equivalence Ratio (φ )
soot
NOx
Source: Akihama et al., SAE 2001-01-0655
LTC
Compression Ignition
•High efficiency
•Produces soot & NOx •Requires aftertreatment PFI Spark-Ignition •Low efficiency •Produces NOx, HC & CO •Requires 3-way catalytic converter Homogeneous Charge CI •High efficiency
•Ultra-low soot & NOx •High HC & CO
•Combustion phasing control?
Research Facilities
Clean Diesel Combustion
Caterpillar SCOTE engine with Ganser CRS fuel injector
Premixed Combustion
Cooperative Fuel Research (CFR) engine with air-assist port fuel injector/vaporizer
Common rail fuel injector
Diesel Combustion
Biodiesel Blends 1 2 3 4 5 6 7 8 9 10 11 12 13 14 Exhaust Fuel Air1 Single-cylinder diesel engine
2 Exhaust surge tank
3 Exhaust back-pressure valve
4 Diluter, heater
5 Filter enclosure
6 Rupture disk
7 EGR cooler
8 EGR valve
9 Intake surge tank
10 Intake heater
11 Air mass flow meter
12 Fuel mass flow meter
13 Dynamometer
(
)
8 1 8 1 i i i i b i iE
WF
BSE
P
WF
• • = =⎛
×
⎞
⎜
⎟
⎝
⎠
=
×
∑
∑
35.01% 6.34% 2.91% 3.34% 7.34% 10.21% 10.45% 8.40%Test Procedure
Biodiesel Properties
Component Density (kg/m3) Cetane Number T10 (°C) T90 (°C) LHV (MJ/kg) ULSD 817 45 43.18 Tallow 877 67 340 354 Canola 884 57 350 354 41.95 (B20) Soy 885 52 347 352 Mustard 884 60 369 412PM Emissions
• All four B20 blends had significantly lower PM
emissions than the ULSD base fuel, a commercial diesel fuel with 15 ppm S
• PM measurement repeatability
issues were encountered during these experiments Biodiesel Blend (%) 0 5 10 15 20 P M Emi ssi ons (g/ hp-hr) 0.03 0.04 0.05 0.06 0.07 Canola Soy Tallow Mustard
NO
xEmissions
• NOx emissions for all B20
blends were higher than those of the ULSD fuel
• NOx emission measurement
repeatability with the reference fuel was very good
• Biodiesels with the lowest PM emissions had the highest NOx emissions
Fuel Consumption
• The B20 biodiesel blends had
~2.3% higher BSFC on a mass basis due to the lower heats of combustion of the biodiesel blending components
• However, fuel consumption was
approximately equivalent on an energy basis
Heat Release
(mode 7)
Summary
Biodiesel Blends
• Biodiesel blends (
≤ B20) derived from four feedstocks showed
satisfactory performance, emissions and combustion
characteristics in a MY 2004 heavy-duty diesel engine
– BSFC was similar on an energy basis
– PM emissions were reduced by 20% on average with B20
– NO
xemissions were increased by 9% on average with B20
• The main issues regarding the use of biodiesel blends in current
diesel engine technology are:
– Biodiesel quality (ASTM D6751), especially oxidative stability
– Cold climate issues (cloud point, blend concentration, blending
procedures)
Emission Standards
Heavy-Duty Diesels, MY 2010
• Engine designers have two
options to meet the new
diesel emission standards
o Reduce in-cylinder pollutant formation using advanced combustion strategies
o Emissions control systems
PM - NOx Emission Trade-off (Modes 5-8)
2010 Emission Standards 0.01 g/hp-hr PM limit 0.20 g/hp-hr NOx limit NOx Emissions (g/hp-hr) 0.0 0.5 1.0 1.5 2.0 2.5 3.0 PM Emissions (g/hp-hr) 0.00 0.05 0.10 0.15 0.20 0.25 ULSD B5 Canola B10 Canola B20 Tallow B20 Soy B20 Canola B20 Mustard
Experimental Setup
Experimental Setup
Fuel Injector/Vaporizer Air assist Fuel Intake air Intake Mixture atomizer vaporizer Injector Heaters• Fuel vaporizer allows us to preheat and partially vaporize middle distillate fuels upstream of the intake port
• Ability to vary Tvap from 140 to 300°C while
maintaining fuel-air
mixture constant (75°C) at the intake port
HCCI Combustion
Oil Sands Diesel Fuels
• A minimally processed and low cetane number (36.6) fuel
derived from oil sands (OS-CN36) was used as the base fuel in
the study
• Three different methods were applied to modify the base fuel to
achieve higher CN fuels:
• Hydroprocessing
• Addition of cetane improver
• Blending with a Supercetane™ renewable diesel fuel
• The base fuel (OS-CN36) was hydroprocessed in two stages.
Cetane numbers were 39.4 (OS-CN39) and 41.4 (OS-CN41),
respectively
Procedure
Controlled Input Conditions
• The air-fuel ratio (AFR) and exhaust gas recirculation (EGR) were
varied and the resultant engine combustion behavior (power, efficiency, emissions) was measured
• Other initial conditions were fixed for this experiment:
Fuel vaporizer temperature (Tvap, °C) 220
Intake mixture temperature (Tmix, °C) 75
Compression ratio 13:1
Engine speed (rpm) 900
Results
AFR-EGR Operating Region
• Increasing the oil sands
hydroprocessing severity shifted the operating region for HCCI combustion towards leaner mixtures
The base fuel (OS-CN36) OS-CN39 OS-CN41
Summary
Oil Sands Diesel Fuels
• Increasing the fuel cetane number shifted the AFR-EGR operating window for HCCI combustion towards higher AFR (leaner mixtures) and reduced the cyclic variations
• Higher EGR rates were required to operate the higher cetane number fuels at lower AFR (richer mixtures). This led to a significant decrease in the maximum engine power produced for the higher cetane number fuels with a fixed boost pressure
• The hydroprocessed fuels had more stable and complete HCCI combustion than the base fuel, which resulted in reduced CO, HC, and NOx emissions and lower ISFC
• The addition of a nitrate cetane improver increased ISFC and led to substantially higher NOx emissions on a relative basis, but the absolute emissions were still very low. Blending a renewable diesel component increased the ISFC and HC emissions
HCCI Combustion
CRC FACE Fuels
• Develop a fundamental understanding of fuel chemistry effects on the compression ignition behavior of homogeneous mixtures of diesel fuel, air and recycled exhaust products
FACE Cetane Number
Aromatic Content
T90
1 Low Low Low
2 Low Low High
3 Low High Low
4 Low High High
5 High Low Low
6 High Low High
7 High High Low
8 High High High
T
vapSweep
Input Parameter Value
Speed 900 rpm λ 3.5 CR 12.25:1 MAP 110 kPa EGR 0 % Tmix 75 °C Tair variable Tvap variable
Soot Emissions
AVL Filter Smoke Number (FSN)• HCCI combustion produces
soot if fuel-air mixture
preparation is not completed prior to autoignition
• The nine FACE fuels had
different vaporizer temperature requirements to achieve 0 FSN
• The two high CN, high T90
fuels (6 & 8) had the highest soot emissions
• The two low CN, low T90 fuels
(1 & 3) had the lowest soot emissions
isNO
x
Emissions
• isNOx emissions were
<0.015g/kW-hr for all FACE fuels when the vaporizer temperature was 270°C or higher
• isNOx emissions decreased
simultaneously with soot
emissions as the fuel vaporizer temperature increased (i.e.
there was no soot-NOx emission trade-off)
CR Sweep
Input Parameter Value
Speed 900 rpm λ 1.2 CR variable MAP 110 kPa EGR 60% Tmix 75°C Tair variable Tvap 270°C
Combustion Phasing
• HCCI combustion phasing
(CA50) is a strong function of engine CR
• The four low CN fuels exhibited significantly delayed CA50
phasing compared to the
Mean Effective Pressure
• The four low CN fuels (Face No.
1-4), as well as the two high CN, low T90 fuels (Face No. 5 & 7) were able to achieve the highest peak IMEPs at fixed
MAP, λ and EGR
• The operating range, in terms of CR, was wider for the high CN fuels
• The high CN, high aromatic,
high T90 fuel (FACE No. 8) had the lowest achievable peak
Fuel Consumption
• The minimum ISFC for the four
low CN fuels occurred when CA50 was ~5°ATDC
• The minimum ISFCs for the
lower CN fuels were better than those for the high CN fuels, but ISFCs of the low CN fuels
seemed to be more sensitive to CA50 phasing
• The two low CN, low aromatic
fuels (FACE No. 1 & 2) had the lowest minimum ISFCs
• The two high CN, high T90
fuels (FACE No. 6 & 8) had the highest minimum ISFCs
Typical HCCI Results
Parameter Measured Level 2010 Standard
ISFC ~240 g/kW-hr
Soot <0.1 FSN 0.013 g/kW-hr (PM)
isNOx ~0.005 g/kW-hr 0.27 g/kW-hr
isHC ~5 g/kW-hr 0.19 g/kW-hr
Summary
HCCI Combustion
The preliminary findings from our HCCI combustion experiments
with the oil sands derived and FACE fuels are as follows:
• For pure HCCI combustion, improving the homogeneity of the fuel-air
mixture (by increasing the vaporizer temperature) simultaneously
reduced soot, NOx, HC and CO emissions
• Soot emissions (AVL FSN) increased with increasing CN and T90
• The four low CN fuels (Face No. 1-4), as well as the two high CN, low T90 fuels (Face No. 5 & 7) achieved the highest peak IMEPs at fixed
MAP, λ and EGR
• The two low CN, low aromatic fuels (FACE No. 1 & 2) had the lowest minimum ISFCs
Future Work
• Compare clean diesel combustion (CDC) of oil sands derived and
FACE fuels in Caterpillar engine with the HCCI combustion results
• Compare CDC & HCCI combustion of oil sands and CRC FACE fuels
• Compare direct hydrogen gas enrichment of HCCI combustion to
hydroprocessing of liquid fuels
PCCI1 HCCI2 SFC, g/kW-hr 239 240 NOx, g/kW-hr <0.04 0.005 HC, g/kW-hr 1.2 ~5 CO, g/kW-hr 9.0 ~10 1 brake, 2 indicated
Final Remarks
• Advanced diesel combustion strategies offer the potential for
high fuel conversion efficiency without the problematic PM and
NO
xemissions associated with conventional diesel combustion
• However, engine designers must deal with low temperature
oxidation of HC and CO exhaust emissions using aftertreatment
• In clean diesel combustion, objective is to achieve rapid fuel-air
mixing using very high fuel injection pressures in conjunction
with high levels of charge dilution to slow down the reaction
kinetics
• HCCI combustion results suggest that high volatility (low T90)
and a relatively low cetane number are desirable fuel properties
Acknowledgements
• The
authors
gratefully
acknowledge
the
following
contributions:
o The financial support provided by the Government of Canada’s
PERD/AFTER and ecoETI programs
o The technical expertise (fuel analyses, pilot plant) provided by the National Centre for Upgrading Technology (NCUT)
o The financial support, technical expertise, fuels, and fuel analyses provided by the Canadian Petroleum Products Institute (CPPI)