SI Engine Mixture Preparation 2. 3. 4. - MIT OpenCourseWare · 2020-01-04 · SI Engine Mixture...

SI Engine Mixture Preparation

1. Requirements

2. Fuel metering systems

3. Fuel transport phenomena

4. Mixture preparation during engine transients

5. The Gasoline Direct Injection engine

MIXTURE PREPARATION

Fuel Air

Fuel Air

EGR

Engine

Metering Metering

EGR ControlMixing

Combustible Mixture

1

MIXTURE PREPARATION

Parameters

-Fuel Properties -Air/Fuel Ratio -Residual/Exhaust Gas Fraction

Impact

- Driveability - Emissions - Fuel Economy

Other issues: Knock, exhaust temperature, starting and warm-up, acceleration/ deceleration transients

Fuel properties (Table D4 of text book)

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2

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Tem

pera

ture

(C

)

Gasoline evaporative characteristics

Distillation curve (ASTM D86) of UTG91 (a calibration gasoline)

200200 Cumene (Methyl-ethyl benzene)

160160 (NBP(NBP 152.4152.4oC)

Toluene 120120 (NBP 110oC)

Iso-octane

8080 (NBP 99.2oC)

Iso-hexane

4040 (NBP 60.3oC)

00 2020 4040 6060 8080 100100 % distilled

• Reid Vapor pressure (ASTM D323):

– equilibrium pressure of fuel and air of 4 x liquid fuel volume at 37.8oC

• T10, T50, T90

– Temperature at 10, 50 and 90% distillation points

• Driveability Index (DI) – For hydrocarbon fuels: DI = 1.5 T10 + 3 T50 + T90 (T in oF)

RVP: winter gasoline ~ 11 psi (0.75 bar); Summer gasoline ~ 9 psi (0.61 bar); California Phase 2 fuel = 7 psi (0.48 bar) DI: range from 1100 to 1300; Phase II calibration gasoline has DI=1115; High DI calibration fuel has DI 1275.

Equivalence ratio and EGR strategies (No emissions constrain)

Enrichment to preventEnrichment to knocking at high loadimprove idle stability

Rich

=1

Lean for good fuel economyLean Load

EGR to decrease NO emission and

EGR pumping loss No EGR to

No EGR to maximize airimprove idle flow for powerstability

Load

3

Requirement for the 3-way catalyst

Air/fuel ratio Rich Lean

Cat

alys

t ef

fici

ency

%

Fig 11-57

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FUEL METERING

• Carburetor – A/F not easily controlled

• Fuel Injection – Electronically controlled fuel metering

Throttle body injection

Port fuel injection

Direct injection

4


Injectors

PFI injectors

• Single 2-, 4-,…, up to 12-holes

• Injection pressure 3 to 7 bar

• Droplet size: – Normal injectors: 200 to 80 m

– Flash Boiling Injectors: down to 20 m

– Air-assist injectors: down to 20 m

GDI injectors

• Shaped-spray

• Injection pressure 50 to 250 bar

• Drop size: 10 to 50 m

PFI Injector targeting

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5

INTAKE PORT THERMAL ENVIRONMENT 140

120 Tvalve

100

80

60 Tport

40

20 Tcoolant

0 0 15 30 45 60 75 90 105 120 135 150 165 180 195 210

Time (sec)

Tem

per

atu

re (

deg

C)

Engine management

system

From Bosch Automotive Handbook

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Fuel Metering

• A/F ratio measured by sensor (closed loop operation) – feedback on fuel amount to keep =1

• Feed-forward control (transients): – To meter the correct fuel flow for the targeted A/F target, need to

know the air flow • Determination of air flow (need transient correction)

– Air flow sensor (hot film sensor) – Speed density method

Determine air flow rate from MAP (P) and ambient temperature(Ta) using volumetric efficiency (v) calibration

N m V (N,)a D v Displacement vol. VD,2

rev. per second N, P gas constant R RTa

FEATURES OF ELECTRONICALLY CONTROLLED FUEL INJECTION SYSTEM

• Sensors – Air temperature

– Engine Speed

– Manifold air pressure (MAP) / air flow rate

– Exhaust air/ fuel equivalence ratio (): EGO (and UEGO)

– Coolant temperature

– Throttle position and throttle movement rate

– Crank and cam positions

• Controls – Injection duration

– Spark timing

– Other functions

Idle air, carbon canister venting, cold start management, transient compensation, ….

7

ENGINE EVENTS DIAGRAM

0 180 360 540 720 900 1080 1260 1440

Cyl. #1 CA (0 o is BDC compression)

Cyl.#1

Cyl.#2

Cyl.#3

Cyl.#4

BC BC BC BC BCTC TC TC TC

TC TC TC TC TCBC BC BC BC

TC TC TC TC TCBC BC BC BC

BC BC BC BC BCTC TC TC TC

Intake Exhaust Injection

Ign Ign

Ign Ign

Ign Ign

Ign Ign

Effect of Injection Timing on HC

Emissions

SAE Paper 972981

Stache and Alkidas

Engine at 1300 rpm

275 kPa BMEP

Injection timing refers to start of injection

8

Mixture Preparation in PFI engine

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Intake flow phenomena in mixture preparation (At low to moderate speed and load range)

Reverse Blow-down Flow • IVO to EVC:

– Burned gas flows from exhaust port because Pe>Pi

• EVC to Pc = Pi:

– Burned gas flows from cylinder into intake system until cylinder and intake pressure equalize

Forward Flow • Pc = Pi to BC:

– Forward flow from intake system to cylinder induced by downward piston motion

Reverse Displacement Flow • BC to IVC:

– Fuel, air and residual gas mixture flows from cylinder into intake due to upward piston motion

Note that the reverse flow affects the mixture preparation process in engines with port fuel injection

9


Mixture Preparation in Engine Transients

Engine Transients • Throttle Transients

– Accelerations and decelerations

• Starting and warm-up behaviors – Engine under cold conditions

Transients need special compensations because:

• Sensors do not follow actual air delivery into cylinder

• Fuel injected for a cycle is not what constitutes the combustible mixture for that cycle

Manifold pressure charging in throttle transient

Aquino, SAE Paper 810484

m

v d/cyl fire

V

V N


10


Fuel-Lag in Throttle Transient

The x- Model dM Mf f xm fdt

Mfm (1- x)m c f

m Injected fuel flow ratef

m Fuel delivery ratec

to cylinder

M Fuel mass in puddlef

Fuel transient in throttle opening

mair

cm

Model prediction Observed results

Fig 7-28 Uncompensated A/F behavior in throttle transient

11

sig

nal

1st peak 2nd peakIntegrated HC emissions: 16 mg 55 mg Total: 71 mg (SULEV:

FTP total is < 110 mg) 4

2 x104 ppm C1 Pre-cat HC

0 4

2 x104 ppm C1 Post-cat HC

0 Engine start 2 up behavior Pintake (bar) (e) (f)

x1000 RPM0

50 (d)

2.4 L, 4-cylinder 60 (c) engine

(a) Cylinder 4 pressure

(b) Engine starts with Cyl#2

40 piston in mid stroke of

Ign 2&3 30 compression

Ign 1&4

Firing order 20 Inj 3 1-3-4-2

Inj 1 10

Inj 4

Inj 2 0 0 0.5 1 1.5 2 2.5 3

time(s)

Engine start up behavior

0 2 4 6 8 10

0

1

2

3

time(s)

MA

P(b

ar),

o

r R

PM

/100

RPM

MAP

Crank start

1st round of firing

Speed run up

Speed decay

Engine gradual warm up

Speed Flare

12

Pertinent Features of DISI Engines

1. Precise metering of fuel into cylinder – Engine calibration benefit: better driveability and

emissions

2. Opportunity of running stratified lean at part load – Fuel economy benefit (reduced pumping work; lower

charge temperature, lower heat transfer; better thermodynamic efficiency)

3. Charge cooling by fuel evaporation – Gain in volumetric efficiency – Gain in knock margin (could then raise compression

ratio for better fuel economy) – Both factors increase engine output

DISI technology penetration

• Significant market penetration of DISI – Homogeneous

charge configuration

– As enabler of the boosted-downsizing strategy

0%

10%

20%

30%

40%

Production

Share 2008

2013

DISI Boosted

13

Toyota DISI Engine (SAE Paper 970540)

Straight port

0 1000 30002000 4000 5000

Engine speed (rpm)

Ou

tpu

t to

rqu

e

High pressure injector


Mitsubishi DISI Engine

End of injection

Piston

Fuel spray impingement

Vaporization and transport to spark plug Reverse tumble Swirling spray

Spherical piston cavity

(SAE 960600)


14



Wall-guided versus spray-guided injection

Wall-guided injection Spray-guided injection(injector relatively distant (injector relatively close to spark plug)

from spark plug)

SAE 970543 (Ricardo) SAE 970624 (Mercedes-Benz)


Charge cooling by in-air fuel evaporation

Intake air temperature (oC)Intake air temperature (oC)

Tem

per

atu

re d

iffe

ren

ce (

o C

)

Charge cooling effect Lowering of intake volume

Anderson, Yang, Brehob, Vallance, and Whiteabker, SAE Paper 962018


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Full load performance benefit

Torq

ue

Full loadFull load

SAE 970541 (Mitsubishi)


Part load fuel economy gain

SAE Paper 960600 (Mitsubishi)


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DISI Challenges

1. High cost 2. With the part-load stratified-charge concept :

– High hydrocarbon emissions at light load – Significant NOx emission, and lean exhaust not amenable to

3-way catalyst operation

3. Particulate emissions at high load 4. Liquid gasoline impinging on combustion chamber walls

– Hydrocarbon source – Lubrication problem

5. Injector deposit – Special fuel additive needed for injector cleaning

6. Cold start behavior – Insufficient fuel injection pressure – Wall wetting

Comparison of cold start HC emissions(Koga, Miyashita, Takeda, and Imatake, SAE Paper 2001-01-0969)

Cumulative engine out HC in the first 10 seconds of cold-start

Rel

ativ

e


17


Significant particle numbers in cold start

SAE 2011-01-1219


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SI Engine Mixture Preparation 2. 3. 4. - MIT OpenCourseWare · 2020-01-04 · SI Engine Mixture...

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