p&e development -jlr lecture 2011
TRANSCRIPT
Gasoline Base Engine Development for Performance and Fuel Economy
Matthew McAllister – Jaguar Land Rover Gasoline Engines
Birmingham University Lecture - 2011 1
Introduction
Birmingham University Lecture - 2011 2
Introduction
Contents
• The Development Process
• Performance Theory
• Fuel Consumption Theory
• Development Tools
Birmingham University Lecture - 2011 3
• Development Tools
• Summary
The Development Process
Birmingham University Lecture - 2011 4
The Development Process
The Development Process
“How does base engine design & development fit into the company structure?”
Vehicle
Body&Exterior Chassis Interior Systems Powertrain Electrical
Birmingham University Lecture - 2011 5
Systems Transmissions Base Engines
Design
Calibration
Development
The Development Process
Responsibilities
Engine Design
• Design components on CAD
• Manage all aspects of component delivery (suppliers, cost,
weight, manufacture, package)
Engine Development
Birmingham University Lecture - 2011 6
Engine Development
• Manage all aspects of verifying design of components &
systems
• Focus on function and attributes
The Development Process
The System Engineering “V”
Vehicle Level
Start Job1
Birmingham University Lecture - 2011 7
System Level
Component Level
Define Design Verify
The Development Process
System Engineering – DEFINE
• Set targets at customer level and then cascade down to component level
e.g. Customer level target: 0-60mph < 6.2sec
0-60mph time
Vehicle Aero Tractive Effort Vehicle Mass Traction
Vehicle Level
System Level
Birmingham University Lecture - 2011 8
Vehicle Aero Tractive Effort Vehicle Mass Traction
T/M FDR T/M Efficiency Engine Torque
Displacement
Engine Technology
Compression Ratio
Int & Exh System
System Level
Sub-systemLevel
ComponentLevel
The Development Process
System Engineering - DESIGN
Design Guidelines
Corporate/Legal Requirements
Manufacturing Requirements
Recycling Requirements
Birmingham University Lecture - 2011 9
Component Attribute Targets(from cascade)
Quality & Durability Targets
Cost & Weight Targets
Packaging Constraints New Design
Vehicle Level
Durability
Hot/Cold Climate
Performance/NVH
CAE
System Level
The Development Process
System Engineering – VERIFICATION
Birmingham University Lecture - 2011 10
System Level
1-D Engine simulation
Engine dynamometer testing
NVH CAEComponent Level
Rig Testing
Component CAE (e.g.
FEA/CFD)
The Development Process
The System Engineering “V”
Vehicle Level
Start Job1
Birmingham University Lecture - 2011 11
System Level
Component Level
Define Design Verify
The Development Process
Build Phases
1. Mule Demonstrator (often reworked/modified existing
hardware)
Design
Verify
ManufactureOptimise
Birmingham University Lecture - 2011 12
hardware)
2. Attribute Demonstrators (first dedicated prototypes, non
production process)
3. Confirmation Prototype (final prototypes, should be
production process & off production tool)
4. Production Verification (off production line at production
rate)
Base Engine P&E
Birmingham University Lecture - 2011 13
Base Engine P&E
P&E Attributes
Engine P&E
Incorporates:
•Engine Performance
•Engine Fuel Consumption (Economy)
•Engine Emissions
Birmingham University Lecture - 2011 14
P&E typically considered separate to Mechanical or NVH
Development and in some companies part of Calibration
department
P&E Attributes
Performance & Fuel Consumption Challenge
Birmingham University Lecture - 2011 15
Source: COMMISSION OF THE EUROPEAN COMMUNITIES - SEC(2007) 1723
Performance Theory
Possible Scenario
• Existing engine with following specification:
-2.6L V6 – 180bhp
-Fixed intake manifold
-Intake variable cam timing
-10:1 compression ratio
Birmingham University Lecture - 2011 16
-10:1 compression ratio
-6000rev/min peak power speed
• What is required to increase power to 200bhp without
increasing displacement?
Performance Theory
2
)/( AFQVNPower
airHVdvolumetricsionfuelconver ××××××=
ρηη
Birmingham University Lecture - 2011 17
2
Performance Theory
2
)/( AFQVNPower
airHVdvolumetricsionfuelconver ××××××=
ρηη
Air Mass TrappedVolumetric Efficiency
(manifold & port ∆P, tuning)
Intake System LossesFuel-Air Ratio
Birmingham University Lecture - 2011 18
2
Thermal efficiencyHeat losses
Mechanical losses
Pumping losses
Mixing
Ignition efficiency
Engine Speed Fuel EnergyDisplacement
Performance Theory
Displacement
• Power ~ proportional to displacement
• Often easiest way of achieving power
increase but increases fuel economy,
engine mass and package requirements
• Can limit maximum engine speeds0
100
200
300
400
500
600
700
0 1 2 3 4 5 6 7 8Displacement [litres]
Po
we
r [h
p]
Birmingham University Lecture - 2011 19
• Can limit maximum engine speeds
Engine Speed• Power is “rate of doing work”, therefore
proportional to engine speed
• Requires changes to engine design to
ensure volumetric efficiency does not drop
• Can involve significant costs to achieve
durability
Displacement [litres]European Gasoline Engines 2007
0
20
40
60
80
100
120
4000 5000 6000 7000 8000
Max Power Speed [rev/min]
Sp
ecific
Po
we
r [h
p/L
]
European Gasoline Engines 2007
Performance Theory
Intake lossesPerformance vs Intake Loss
194
196
198
200
202
204
206
208
Pow
er
[bh
p]
Hig
h p
erf
orm
an
ce
typ
ical fa
mily
ca
r
Birmingham University Lecture - 2011 20
• Minimize losses – rule of thumb: 1.2% power / 10mbar
intake ∆P increase
• Minimize detrimental tuning effects as a result of layout
AIS CFD 194
10 20 30 40 50 60
Intake Loss [mbar]
Hig
h p
erf
orm
an
ce
Performance Theory
Volumetric Efficiency - ∆ ∆ ∆ ∆P
• Minimize pressure losses (throttle
sizing, manifold runner R/D,
manifold detail design, managing
interfaces, surface finish, port
design, valve design, valve seat
design)
RD
R/D
Birmingham University Lecture - 2011 21
design)
0.0
0.2
0.4
0.6
0.8
1.0
0.0 0.1 0.2 0.3 0.4 0.5
Valve Lift/Diameter
Flo
w C
oe
ffic
ien
t
Port flowThrottle ∆P (CFD)
Performance Theory
Volumetric Efficiency – Intake Tuning
• Objective: maximise mass of air trapped at specific
speeds or across speed range by harnessing wave and
inertial tuning effectsPLENUM
Runner
Cylinder
Depression Wave
Reflected Pressure Wave
• WAVE tuning –
dependent on intake cam
period & runner length
Birmingham University Lecture - 2011 22
PLENUM
Runner
Cylinder
Reflected Pressure Wave
period & runner length
• Inertia tuning – inertia of air column in runner/port continues
charging process past piston BDC - dependent on runner
diameter, volume and intake valve closing time
Performance Theory
110%
130%
150%V
olu
metr
ic E
ffic
ien
cy [
%]
150
200
250
To
rqu
e [
Nm
]
Typical production I4 performance curve…
Closed Valve Tuning
Birmingham University Lecture - 2011 23
50%
70%
90%
0 1000 2000 3000 4000 5000 6000 7000
Engine Speed [rev/min]
Vo
lum
etr
ic E
ffic
ien
cy [
%]
0
50
100 To
rqu
e [
Nm
]
Primary tuning
Secondary Tuning
Performance Theory
Volumetric Efficiency – Optimum Runner Lengths
• Theoretical optimum runner length vs engine speed:
1500
2000
2500
Op
tim
um
Ru
nne
r L
eng
th [m
m]
Intake Length
Exhaust Length
Birmingham University Lecture - 2011 24
0
500
1000
1500
2000 3000 4000 5000 6000 7000
Engine Speed [rev/min]
Op
tim
um
Ru
nne
r L
eng
th [m
m]
Performance Theory
Volumetric Efficiency – Exhaust Tuning
• Objective: maximise extraction of residuals by harnessing
wave tuning effects in exhaust / minimise negative tuning
effects between cylinders
• Limited opportunity in modern passenger vehicles as
design is dominated by emissions requirements (catalyst)
and under-bonnet package Log Manifold
Birmingham University Lecture - 2011 25
and under-bonnet package
Cylinder
Collector
Blow-down pulse
Cylinder
Collector
Reflected extraction wave
Log Manifold
4:2:1 Manifold
Performance Theory
Fuel Air Ratio (1/AFR)
• Maximum performance at ~12:1-13:1 AFR (Power
Enrichment)
• AFR settings at higher engine speeds generally dictated
by component (e.g. exhaust valves, turbine, catalyst)
protection requirements
Birmingham University Lecture - 2011 26
Engine speed
Load
λ=1 (AFR~14.6:1)
(for max. catalyst eff.)
PE - AFR~13:1
-4%
-3%
-2%
-1%
0%
10 11 12 13 14 15AFR
% P
erf
orm
ance d
egra
datio
n
Performance Theory
Thermal Efficiency
Friction:
• At max power speed friction is approximately 15% of brake power
• 10% reduction in friction � 1.5% increase in power
• Not only contact friction – need to Typical SI engine heat
balance at peak power
Birmingham University Lecture - 2011 27
• Not only contact friction – need to consider windage / inter-bay breathing
Heat losses:
• At max power ~22% of fuel energy lost in heat transfer to air/oil/coolant
• 10% reduction in heat loss � 8% increase in power (!)
Brake power
28%
Exhaust
enthalpy
50%
Coolant/oil
15%
Ambient
7%
balance at peak power
Performance Theory
Thermal Efficiency
Exhaust Back Pressure – 3 effects:
1.Increases pumping work to expel charge
2.Reduces amount of fresh charge induced
3.Increases knock sensitivity (ignition retard from optimum)
Performance vs Exhaust Back Pressure208
Birmingham University Lecture - 2011 28
194
196
198
200
202
204
206
208
200 300 400 500
Exhaust Back Pressure [mbar]
Po
wer
[bh
p]
Hig
h p
erf
orm
ance
fam
ily c
ar
Performance Theory
Thermal Efficiency
Ignition Efficiency:
• Objective – operate ignition
at MBT (Maximum advance for
Best Torque)
• Good resistance to 340
360
380
400
420
0102030
MBT DBL
To
rqu
e [N
m]
Birmingham University Lecture - 2011 29
• Good resistance to
detonation (detail chamber
design, head cooling)
• Key parameters:
compression ratio & fuel RON
(trade-off with fuel economy)
0102030Ignition [°btdc]
Engine speed
Loa
d
WOT
Knock limited IGN MBT IGN
Engine speed
Loa
d
WOT
Knock limited IGN MBT IGN
Performance Theory
Robustness…
• It is not enough simply to demonstrate performance under
ideal homologation conditions (low temperature, high RON
fuel, best build condition)
• Also need to consider
worst case…
Birmingham University Lecture - 2011 30
• Need to understand
sensitivities to these
parameters and ensure
adequate performance
under all conditions to
avoid customer
complaints
Performance Theory
Back to performance optimisation scenario …
• 200bhp = 11% increase
• Increasing engine speed to 6600rev/min at constant
volumetric efficiency would deliver ~10% = 198bhp
• Increasing compression ratio to 11:1 would deliver ~2-3% =
4bhp = 202bhp (providing engine is not knock limited)
Birmingham University Lecture - 2011 31
4bhp = 202bhp (providing engine is not knock limited)
• To deliver good volumetric efficiency at higher engine
speed will require re-optimised runner length
• May need to consider variable geometry manifold to not
sacrifice too much low speed performance
Performance Theory
Back to performance optimisation scenario …
•2.6L, 180BHP
160
200
240
280
To
rqu
e [
Nm
]
Birmingham University Lecture - 2011 32
0
40
80
120
160
1000 2000 3000 4000 5000 6000 7000
Engine Speed [rev/min]
To
rqu
e [
Nm
]
BASELINE
Performance Theory
Back to performance optimisation scenario …
•2.6L, 198/202BHP – but poor driveability
160
200
240
280
To
rqu
e [
Nm
]
BASELINE
Birmingham University Lecture - 2011 33
0
40
80
120
160
1000 2000 3000 4000 5000 6000 7000
Engine Speed [rev/min]
To
rqu
e [
Nm
]
BASELINE
INCR ENG SPD
INCR CR
Performance Theory
Back to performance optimisation scenario …
•2.6L, 202BHP – Optimised Torque Curve
160
200
240
280
To
rqu
e [
Nm
]
BASELINE
INCR ENG SPD
Birmingham University Lecture - 2011 34
0
40
80
120
160
1000 2000 3000 4000 5000 6000 7000
Engine Speed [rev/min]
To
rqu
e [
Nm
]
INCR CR
TWIN STAGE
MANIFOLD
Fuel Consumption Theory
Fuel economy break-downLog P
Gross EfficiencyFuel required to generate GIMEP
Pumping work
Birmingham University Lecture - 2011 35
Log P
Pumping work
PMEP
Log V
Net IMEP = GIMEP + PMEP (-ve)
BMEP = Net IMEP - FMEP
Pumping workFuel “lost” to pumping work
Friction workFuel “lost” to friction work
Brake work
induction
exhaust
Fuel Consumption Theory
Maximize Gross Efficiency (1)
• Maximize compression
ratio (trade-off with low
speed / low RON / high
air temp performance)-4%
-2%
0%
2%
4%
6%
8%
10%
9:1 10:1 11:1 12:1 13:1 14:1Compression Ratio
ch
an
ge
in
BS
FC
Theory
Reality
Birmingham University Lecture - 2011 36
• Minimize heat transfer
(surface to volume ratio,
charge motion, coolant
temperature)
Compression Ratio
-3%
-2%
-1%0%
1%
2%
3%
0.90 0.95 1.00 1.05 1.10Bore/Stroke Ratio
Ch
an
ge
in
ηη ηηth
erm
al
Fuel Consumption Theory
Maximize Gross Efficiency (2)
• Ensure complete burn (good atomisation, complete mixing)
• Ensure optimum spark efficiency (resistance to knock, fast
burn, correct calibration)
40%
Incre
ase i
n F
uel
Co
nsu
mp
tio
n
MBT
Birmingham University Lecture - 2011 37
0%
10%
20%
30%
0 10 20 30 40Ignition Timing [°btdc]
Incre
ase i
n F
uel
Co
nsu
mp
tio
n
MBT
(opt eff)
Fuel Consumption Theory
Minimize Pumping
Pumping Reduction Routes:
1.Charge dilution (stratified DI / lean
homogeneous / EGR)
2.Reduction of trapped volume (very
early or very late intake valve closing)
Log P
PMEP
Birmingham University Lecture - 2011 38
3.“Down-sizing”
�With all these approaches the volume of trapped air is
reduced requiring the manifold pressure (MAP) to be raised,
i.e. throttle to be opened further, to recover the lost mass �This reduces the pumping work
Log V
Old MAP
New MAP
Fuel Consumption Theory
Dilution by air (Stratified Direct Injection)
Example: MB 3.5L V6 DI
Birmingham University Lecture - 2011 39
• Significant fuel economy potential 5-15% depending on
engine size/application
• BUT major emissions compliance challenge involving
complex and expensive after-treatment system (maybe not
possible beyond EU5 in Europe and ever in US?)
• Benefit diminishes significantly for smaller engines
Fuel Consumption Theory
Reduction of trapped volume
Example – BMW Valvetronic
Birmingham University Lecture - 2011 40
• Pumping benefit achieved by virtue of controlling load
(mass trapped) through variable valve lift/duration instead
of throttle
• Limited fuel economy benefit (2-5%) due to reduced
combustion efficiency - particularly at light load (effective
compression ratio reduced, poor charge motion)
• Expensive technology and major manufacturing challenge
Fuel Consumption Theory
Minimize Friction• Typical friction break-down vs engine speed for SI engine:
40%
60%
80%
100%F
ricti
on
Bre
ak-d
ow
nValvetrain
Coolant Pump +Unloaded Alternator
Oil pump
Piston group & con-rod
Birmingham University Lecture - 2011 41
0%
20%
1000 2000 3000 4000 5000 6000
Engine Speed [rev/min]
Fri
cti
on
Bre
ak-d
ow
n
Piston group & con-rodbearings
Crankshaft
• For drive-cycle fuel economy (below 3000rev/min) focus
should be on reduction of valvetrain and piston friction
• A 10% reduction in piston friction could reduce part load fuel
consumption by ~1%
1) Higher Compression Ratio (no knock limitation)
Fuel Consumption Theory
Based on fuel consumption theory just presented what are the two main reasons for the improved fuel consumption of Diesel vs. Gasoline engines?
Birmingham University Lecture - 2011 42
2) Minimized pumping work (load control through level of dilution with air, qualitative vs. quantitative load control)
Compression Ratio
22.520.017.515.012.510.07.5
Diesel
Gasoline
Each symbol represents up to 3 observations.
Application of Fuel Consumption Theory
Birmingham University Lecture - 2011 43
Application of Fuel Consumption Theory
Fuel Consumption – CO2 challenge for manufacturers
How to make vehicles that comply with the EU Legislative framework:
• From 2012 to 2019 a vehicle mass based CO2 limit will be applied to all new vehicles.
• How to address this in a cost effective manner, whilst maintaining key vehicle attributes?
Options available:
• Vehicle level optimisation for increased efficiency:
Birmingham University Lecture - 2011 44
• Vehicle level optimisation for increased efficiency:
• Advances predominantly aimed at reducing weight and aerodynamic drag.
•Powertrain level:
• Mild or micro hybrid technologies.
• Full hybridisation.
• Technologies aimed at reduced friction, pumping and increased combustion efficiency.
�Gasoline engines downsizing and boosting – focus of our paper.
Fuel Consumption – Downsizing and Boosting
•Presented at IMechE Internal Combustion Engines: Performance, Fuel & Emissions Conference - Dec 09
•Paper title: Future gasoline engine downsizing technologies – C02 improvements and engine design considerations. Authors: M.J.McAllister & D.J.Buckley.
• Downsizing - The principle behind this approach is to de-throttle the engine to reduce pumping work by making the displacement and/or number of cylinders smaller.
Birmingham University Lecture - 2011 45
• Boosting – provides a means of increasing the specific performance of the downsized engine, thus maintaining the power and torque of the engine it replaces, typically with a supercharger, turbocharger or combined boosting systems.
���� Gasoline engine downsizing and boosting offers manufacturers significant CO2 reductions without major vehicle modifications such as those required by full hybrid technologies.
Fuel Consumption – Challenges of downsizing
• Robust DI combustion system.
• An advanced boosting system.
• Emissions countermeasures.
• Effective integration of downsized engines with complementary CO2
reduction strategies.
• Refinement.
• Customer acceptance of smaller engines.
Birmingham University Lecture - 2011 46
• Customer acceptance of smaller engines.
���� The above challenges are considerable due to competing
attributes. Customer acceptance is a problem that requires more
than just an engineering solution!
Fuel Consumption – CO2 benefits of engine downsizing
0
5
10
15
20
25
% C
O2 r
ed
uctio
n
SC
TC
4L V8
3.5L V6
3L V6
2.4L I42L I4
Deviation from the trend line is due to BMEP resolution in
the fuel map analysis
Birmingham University Lecture - 2011 47
0
0% 10% 20% 30% 40% 50% 60% 70%
Level of Downsizing [%]
• For a >10% CO2 benefit a significant level of downsizing is necessary (35%) requiring a change in architecture, i.e. V6 vs. V8 or I4 vs. V6.
• A moderate level of downsizing (e.g. 4.5L SC vs. 5L NA) does not yield a meaningful CO2 benefit (<3%).
• Difference between boosting systems is small compared to overall downsizing effect so other factors will be decisive (e.g. transient response, emissions etc.).
P&E Development Tools
Birmingham University Lecture - 2011 48
P&E Development Tools
Overview
P&E Specific Tools
Level Virtual Real
Vehicle • Vehicle performance and FE
simulation
• Drive cycle FE and emissions
testing
• Performance testing
Engine • 1-Dimensional Gas Exchange
Modelling
• Combustion Modelling
• Single-cylinder engine testing
• Multi-cylinder engine testing
Birmingham University Lecture - 2011 49
• Combustion Modelling
Component • CFD flow modelling
• Friction modelling
• Flow bench testing
CAE
Steady State CFD – Port Flow
• Allows detailed “desktop” optimisation of port design for
flow / charge motion prior to evaluation on flow bench test
Pressure
Inlet
Birmingham University Lecture - 2011 50
Ports
Bell MouthValve
Seats
Pressure Outlet
Chamber
& Tube
CAE
Steady State CFD – Intercooler Flow Distribution
Birmingham University Lecture - 2011 51
CAE
1-D Simulation
• 1-D Simulation (Ricardo WAVE) used to analyze the
dynamics of pressure waves, mass flows, and energy
losses in the engine intake and exhaust
• Engine intake & exhaust geometry broken down into 1-
dimensional components (ducts and junctions)
• Mass, momentum and energy conservation equations
Birmingham University Lecture - 2011 52
• Mass, momentum and energy conservation equations
solved for each sub-volume to obtain solution
• Used to predict key engine operating characteristics, e.g.
volumetric efficiency, torque, mass flows, etc.
CAE
WAVE 1-D model – SC V8
A-bank
Catalyst
Birmingham University Lecture - 2011 53
Airbox
SC & IC
B-bank
Exhaust Manifold
B-Bank Exhaust System
CAE
WAVE 1-D vs Test Data CorrelationT
orq
ue
WAVE model
Test Data
Birmingham University Lecture - 2011 54
1000 2000 3000 4000 5000 6000
Engine Speed [rev/min]
To
rqu
e
CAE
Advantage of 1-D simulation
1. Time – possible to run multiple simulations 24/7
2. Cost – conducting engine testing is expensive (test facility, tester,
engineer, fuel, maintenance), 1-D simulation only requires 1 engineer and 1 PC
3. In-depth understanding – with 1-D simulation detailed
information of pressures, temperatures, mass flows, etc. is available
Birmingham University Lecture - 2011 55
information of pressures, temperatures, mass flows, etc. is available throughout the engine and at every point in the cycle
Disadvantages
1. Need for correlation to existing test data
2. Model does not always behave like real engine
3. 1-D approximation of complex 3-D geometries
Testing
Engine Dynamometer
• Durability & functional testing
• Steady state & transient dynamometers
• High/low temperature capabilities
Birmingham University Lecture - 2011 56
Testing
Typical dynamometer instrumentation
1. Thermocouples � e.g. coolant, oil, intake air temperature
2. Pressure transducers � e.g. oil gallery, boost pressure
3. Fuel flow (mass/volumetric) � used to infer air mass flow
4. Emissions analyser � O2, CO, CO2, HC, NOx
5. Smoke meter (Diesel, GDI)
Birmingham University Lecture - 2011 57
6. Fluid flow meters � e.g. engine or intercooler coolant flow
7. Combustion analyser � used to measure cylinder
pressures and calculate IMEP, PMEP, burn data
8. EMS break out equipment � to control engine settings
9. Automated testing controller � to schedule automated
testing and interface with dyno & EMS
10. Knock monitoring equipment � audio/visual
Testing
Key Challenges
• Maximum utilisation of dynamometers – expensive
investment
• Efficient processing of (ever) increasing quantities of test
data – up to 250 data channels per test point
• Increased use of design of experiments and data
modelling
Birmingham University Lecture - 2011 58
modelling
• Increased use of automated testing
• Increased awareness of the statistical nature of test data
Testing
Rapid Prototype Parts
> key technology in enabling
reduced development time
• SLA – Stereolithography
–3D CAD model is converted into a series of 2D slices (~0.1mm thick). Laser cures photosensitive resin in a tank layer by layer
Birmingham University Lecture - 2011 59
photosensitive resin in a tank layer by layer
• Laser Sintering
–Similar principal to SLA but very thin layers of heat fusible powder are repeatedly deposited. Laser sinters the fresh powder to form a new layer.
• Applications: intake manifolds, air
induction systems, moulds for casting,
etc.
Summary
Birmingham University Lecture - 2011 60
Summary
Summary
Overview
• Methodology used in vehicle/engine development –
System Engineering “V”
• Fundamental performance and fuel consumption theory
• Overview of tools used in development
Birmingham University Lecture - 2011 61
Future Challenges
• Dramatic fuel consumption / CO2 reduction required
• More stringent emissions legislation
• Higher performance (?)
• Reduced development time
• Lower cost (?)
225 mph Bonneville Speed Record
BonnevilleMaster.mov
Birmingham University Lecture - 2011 62
2010 Jaguar XK GT2
Birmingham University Lecture - 2011 63
Thank You